HVAC SYSTEMS FOR THE REPLACEMENT OF EXISTING WALL MOUNTED AND INDOOR CABINET TYPE CLASSROOM UNITS
Appendix B Related Studies 1. HVAC Systems Acoustical, Cost and Energy Study, June 6, 2005 2. Duct Free Split System Heat Pumps as Alternative for Wall Mounted Heat Pumps In existing classrooms, March 21, 2005 3. Measured Classroom Sound Levels, May 30, 2005
HVAC SYSTEMS ACOUSTICAL, COST & ENERGY STUDY Prepared for the
Los Angeles Unified School District Facilities Services Division
June 6, 2005
By
Maroko & Shwe, Inc., Professional Engineers With
Schaffer Acoustics Inc
Table of Contents Executive Summary
PAGE
Introduction & Methodology
i
Conclusions for Basic Systems
i
Conclusions for Other Systems
ii
Other Factors
iii
New Developments
iii
Recommendations
iv
School HVAC Systems Comparison (Basic Systems)
vii
School HVAC Systems Comparison (Other Systems)
viii
HVAC Systems Acoustical Cost & Energy Study Introduction
1
Basic Systems Description
1
Standard Design Measures for HVAC Sound Attenuation
2
Air Inlet / Outlet Connection Details – Figure 0.1
4
Acoustical Improvement Measures
4
Basic Systems System 1 : Rooftop Packaged Air Conditioning with Gas Heating
6 7
System 2 : Split System Heat Pumps
14
System 3 : Four Pipe Fan Coil Units with Remote Central Plant
21
System 4 : Central Air Handling Units with Remote Central Plant
27
System 5 : Radiant Panels with Remote Central Plant
32
PAGE
Other Systems
36
System A : Water Source Heat Pump
37
System B : Wall-Mounted Packaged Heat Pumps with Ducted Supply
42
System C : Duct Free Systems
45
Acoustical Requirements of LAUSD Design Guidelines
51
Acoustical Measures in the Guide Specifications
52
Acoustical Measures in the School Design Guide
62
Different Perspectives
67
Acoustical Engineer’s Report & Calculations Report of Schaffer Acoustics Inc Calculations made by Schaffer Acoustics Inc
70
EXECUTIVE SUMMARY
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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EXECUTIVE SUMMARY Introduction and Methodology This study was initiated to explore the costs and benefits of five basic classroom air conditioning systems for new schools, specifically relative to the background sound levels generated by each system, their relative capital cost, and energy usage. The methodology used was to: (1) Define clearly each HVAC system, so that costs, energy use, and acoustic performance could be calculated; (2) Define noise-reduction options for each system; (3) Calculate the energy use for each system using the Trane Company’s TRACE 700 simulation program; (4) Calculate the acoustical performance and classroom sound levels for each system and its options, using the Trane Acoustical Program (TAP); (5) Summarize the findings and make recommendations for LAUSD design standards to improve energy and acoustical performance with minimal increase in capital cost. To amplify and verify the mechanical engineering acoustical simulations, the services of Mark Schaffer, P.E., were engaged. He is one of the nation’s leading authorities on the sound and vibration effects of air conditioning equipment, and was chair of the ASHRAE committee on HVAC sound and vibration. His findings are an integral part of the conclusions of this report. Five Basic Systems are described in the report. The first two are unitary systems which are in common use in Southern California. The next three all involve a central energy plant. Two of these are currently in use in some LAUSD schools. The last system, Ceiling Radiant Heating and Cooling Panels, is relatively new and not currently in common use in California. In addition, a brief analysis of several other systems was included in the study. Conclusions for Basic Systems The comparative results of the study of the five systems are summarized in the table, “School HVAC Systems Comparison (Basic Systems), on page vii.” The general conclusion of the five system study is that improvement in the background sound levels in the classroom can be achieved with more centralized HVAC systems in lieu of unitary systems, but at considerable increase in capital and operating costs. In addition, the following conclusions could also be made: •
Systems with remote central-station air handling units (AHU) and central energy plants (Systems 4 and 5) will yield the quietest classroom sound levels, falling in the range of i
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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35 to 37 dBA – thus meeting the ANSI Standard criteria. They also have a higher capital cost of about two times (or more) that of the unitary systems. •
The added cost for central AHU’s does not include the cost for building equipment rooms, if they are not located on the roof.
•
A key finding of the study was that the acoustical performance was controlled by excessive duct “breakout” sound at the lowest octave bands, and that increasing the duct wall thickness from the usual 26 gage to 18 gage reduced the classroom sound levels by 4 to 5 dBA. This finding is theoretical only and has not yet been verified by field tests.
•
Rooftop (System 1) or split unitary systems (System 2), designed in accordance with current LAUSD practice can achieve a background sound level of approximately 45 dBA. If the thicker duct gage is incorporated, a level approaching 40 dBA can theoretically be achieved. The additional capital cost for increasing the duct gage is approximately $1,900 per classroom above that of the District’s current practice.
•
The cost of the central energy plant for the four-pipe fan-coil unit in the classroom (System 3) is not justified by sound-level improvement or energy savings. It might only be useful in multi-story buildings not practical for split-system unitary equipment.
•
Fan-coil units located above the classroom ceiling will always generate fan noise that reduces the ability to lower background sound levels. If fan-coil units can be located outside the classroom area – for example, above an adjoining work-room ceiling – sound levels can be improved, but with some additional cost.
Conclusions for Other Systems In addition to the five Basic Systems for new schools, several other systems currently used in existing schools were analyzed and evaluated as a supplement to the major study. The comparative results of the study of the three additional systems are summarized in the table “School HVAC Systems Comparison (Other Systems)”on page viii. Because the fans and air openings, and often the compressors, are within the classroom space, the noise generated is sufficiently loud that none meet the District’s standard for New Schools of 45 dBA background sound level as recommended by the Collaborative for High Performing Schools (CHPS). Within ten feet of the unit, these systems produce at best a sound level of 50 dBA, and closer to the unit the levels reach 55 and 60 dBA in most cases. As an adjunct to this study, a completed classroom installation was investigated that has been measured and reported to have achieved a background sound level of 37 dBA or less with unitary rooftop equipment. It is characterized by an existing one-story wood-frame building, with a rooftop unit and all the distribution ducts for four diffusers and two return grills supported above the roof levels. Thus, the duct breakout noise does not reach the classroom. This is an appropriate installation for the DHH classroom it serves. However, exposing all the ducts on the roof is not a practical solution for all classrooms in a school. Multiple roof penetrations increase the chances of leakage. Re-roofing is complicated. It is ii Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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unsightly. And it works only for the top-floor classroom. Also, it is significantly more costly to construct. (A separate report will be prepared on this installation.)
Other Factors Apart from basic system selection and design, HVAC systems sometimes produce excessive classroom noise levels because of oversights or errors in design or construction. Some of these are: •
Over estimating in design the duct static pressures (SP). Because the fan noise is proportional to the static pressure, if the fan SP is higher than needed, the installer is likely to choke the system by closing the manual volume dampers (and sometimes the opposed blade dampers at the diffusers and registers) rather than the longer and correct process of adjusting the fan speed by replacing the fan drive sheaves. The result: significantly increased noise.
•
Improper air balance can also cause the situation described above, even when the system is properly designed.
•
High air-flow velocities in the ducts and through the diffusers and grills – a definite noise increase. It is often caused by reducing duct sizes to fit into space that is inadequate.
•
Insufficient duct length between the diffusers and grills – that is, they are located too close to the fan, not permitting some attenuation of the fan noise.
•
Locating the manual volume dampers and control dampers too close to the diffuser and grill outlets.
•
Insufficient sound insulation for equipment rooms – or between the rooftop units and the ceiling space below.
•
Insufficient vibration isolation of major equipment.
•
Structures that are not strong and stiff enough to absorb or dampen the equipment vibrations, even when vibration isolators are provided.
•
Locating large equipment too close to classrooms.
These have been addressed in the District’s design guidelines, as well as being part of sound engineering practice. New Developments Even as this study has progressed, manufacturers have introduced new and improved units. Both Carrier and Trane now have new packaged rooftop HVAC units with substantial improvements in both acoustical performance and energy efficiency.
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The new Carrier Centurion unit may be able to reduce classroom background sound levels from 46 dBA to 38 dBA – although this has not been verified. A comparable unit, the Trane XL1600, seems to have similar capability. Full acoustical data on these units, though, has so far not been available. They also appear to have a significant cost increase. One of these was used in the special classroom described above. Recommendations Follow Standard Design Measures The following Standard Design Measures for HVAC Sound Attenuation should be incorporated in all new systems designs: 1. Size diffusers and registers for NC – 25 or less. 2. Provide proper duct connections at diffusers and registers as indicated in Figure 0.1 of this report. 3. Provide a minimum 5’-0” of flexible duct at all air inlets and outlets. 4. Provide an adequate number of manual volume dampers. Locate the dampers a minimum 3 duct diameters up stream or downstream of air inlets and outlets. Maximize the distance between dampers and take-offs and elbows. 5. Size ducts per velocities recommended by project acoustical consultants, but not to exceed in Systems 1, 2 and 3, 850 feet per minute for main ducts and 450 feet per minute for branch ducts. 6. Provide turning vanes at all rectangular elbows. 7. Provide ducted returns with the air inlet registers at a minimum 15’-0” from the main duct risers in Systems 1, 2 and 3 and as recommended by project acoustical consultants in Systems 4 and 5. 8. Provide vibration isolators for all rotating or reciprocating HVAC equipment including packaged units, fans and compressors. 9. Provide sound barriers and acoustic sealant at the inside of the curb and duct roof penetrations, and beneath the unit (similar to in Figure 1.2).
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10. Provide duct lining and duct silencers (as required by the project acoustical consultant) for the larger fans, air handling units and larger packaged units (generally larger than 6 Tons) serving areas such as multi-purpose rooms and gymnasiums. 11. Do not locate duct sound attenuators inside the building above (the ceiling of) occupied spaces where the breakout noise will increase indoor sound levels above acceptable limits. 12. Do not provide duct lining for the classroom packaged units and fan coil units of less than 5 Tons capacity unless directed by the project acoustical consultant for unique conditions. 13. Do not over estimate the fan static pressures or system capacities. 14. Specify the allowable sound levels for all HVAC equipment. Select fans for optimum sound levels. The specified sound levels shall be rated in accordance with the current industry standards. (Standards by ARI - Air Conditioning and Refrigeration Institute; AMCA – Air Movement and Control Association, etc.) as published in the Codes and Standards Chapter of the current ASHRAE (American Society of Heating Refrigerating and Air Conditioning Engineers) Handbook on HVAC Systems and Equipment. 15. Provide flexible connectors for ducts at fan connections and pipes at all pumps and air handling equipment connections. 16. Ensure that the systems are balanced properly. 17. Carefully consider the location of HVAC equipment. 18. Ensure that the Architects provide sufficient space for the proper installation, performance and service of ductwork and equipment. Detailed requirements that include the above measures are already part of the LAUSD design guidelines and guide specifications. These guidelines and guide specifications related to HVAC Acoustics are included in the later part of this report as reference. The designers should make themselves familiar with the latest LAUSD design guidelines and specifications before starting a new project.
Field Test the Effectiveness of the Increase in Duct Wall Thickness Find two existing classroom locations, the first with an existing curb mounted, down shot, rooftop gas/ electric packaged unit and the second with a split system fan coil unit above the ceiling. Measure the sound levels as installed. Replace all the ducts. Replace the main v Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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supply and return air ducts from the unit to the first branch take off with 18 gage sheet metal ducts. Reconfigure the duct system layout to comply with the standard system design measures in the preceding paragraph. Measure the sound levels again and compare with the previous measurements. Adopt the increase in duct wall thickness to 18 gage as a standard if it is found to be effective.
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vii Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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viii Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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HVAC SYSTEMS ACOUSTICAL, COST & ENERGY STUDY Introduction For this study and evaluation, five basic systems for air conditioning school classrooms were selected. Four of these systems are currently used extensively throughout California. The last system, ceiling radiant heating and cooling panels, is relatively new and is not commonly used in California. The acoustical performance relative to classroom background noise of each system was evaluated, in conjunction with different optional attenuation measures. Also evaluated were capital cost and energy efficiency. Basic Systems Description Following is a brief description of each of the five basic systems. These are described in much greater detail in the drawings and narrative for each system in the following pages. 1.
Unitary Rooftop Packaged Air Conditioning System Roof-mounted units installed directly above a classroom and serving one classroom each, with gas heating and electric direct-expansion cooling. Ducted to four supply-air diffusers and two return-air registers. Non-recirculated air is relieved to the outside thru a register ducted to a dampered opening in the exterior wall.
2.
Unitary Heat-Pump Split-System Condenser unit is installed on the roof directly above a classroom (or in some other remote location) and serving one classroom each. Fan-coil unit is located above the ceiling in the classroom, mounted on vibration isolator hangers. Ducts are the same as System 1, except there is also an outside-air opening in the wall and duct to the unit.
3.
Four Pipe Fan Coil Unit System Fan-coil unit, serving one classroom, provided with hot and chilled water from a remote central plant with air- or water-cooled chillers and gas-fired hot water boilers. Fan-coil unit is located above the ceiling in the classroom, mounted on vibration isolator hangers. Ducts are the same as System 2. (There is no local condenser unit, and noise from the piped water system is negligible.)
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4.
Remote Air Handling Unit (AHU) System Remote air-handling unit (rooftop or equipment room), serving several classrooms and provided with hot and chilled water from a remote central plant with air- or water-cooled chillers and gas-fired hot water boilers. Each classroom is provided with a variable-air-volume zone control terminal. AHU has built-in sound attenuators for both supply and return fans. The fans are mounted on vibration isolators internal to the unit, and are also optimized for both energy efficiency and sound. If not installed in an equipment room, the unit is typically installed above a corridor adjacent to student toilets so that the roof penetrations for the supply and return air ducts are separated from the classroom with significant lengths of ductwork. The variable air volume terminal is located above the classroom ceiling and serves four diffusers. The return air is ducted through two registers.
5.
Ceiling Radiant Heating and Cooling Panel System Ceiling -mounted panels are provided with hot and chilled water from a remote central plant with air- or water-cooled chillers and gas-fired hot water boilers. Classrooms have a dedicated outdoor-air ventilation system with pre-treated air, cooled and dehumidified or heated as demand requires, provided from a remotely located air-handling unit with built-in sound attenuators. The fan is mounted on vibration isolators internal to the unit, and is also optimized for both energy efficiency and sound. The AHU is installed similarly to System 4. The supply air is distributed through only two ceiling diffusers, due to the lower volume of air for ventilation only.
Standard Design Measures for HVAC Sound Attenuation The following conditions and sound attenuation measures have been assumed for the analyses of this report, and apply to all five basic systems. 1. Diffusers and registers sized for NC – 25 or less. 2. Proper duct connections at diffusers and registers as indicated in Figure 0.1. 3. Minimum 5’-0” of flexible duct at all air inlets and outlets. 4. Proper placement of manual volume dampers. Minimum 3 duct diameters up stream or downstream of air inlets and outlets. Maximize the distance between dampers and take-offs and elbows. 5. Ducts sized per velocities recommended by project acoustical consultants, but not to exceed in Systems 1, 2 and 3, 850 feet per minute for main ducts and 450 feet per minute for branch ducts. 2 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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6. Turning vanes at all rectangular elbows. 7. Ducted returns with the air inlet registers at a minimum 15’-0” from the main duct risers in Systems 1, 2 and 3 and as recommended by project acoustical consultants in Systems 4 and 5. 8. Vibration isolators for mounting units. 9. Sound barrier and acoustic sealant at the inside of the curb and duct roof penetrations, and beneath the unit (similar to Figure 1.2). 10. The effects of items 8 and 9 above cannot be calculated with the TAP program, but in previous projects, a difference of about 3 dBA was measured between rooftop units mounted on curbs without vibration isolators with unsealed roof penetrations and rooftop units mounted on isolator curbs with sealed penetrations. The above attenuation measures and some others are indicated in Figures 0.1 and 1.2 following in the report.
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Air Inlet / Outlet Connection Details - Figure 0.1 Acoustical Improvement Measures The following measures to improve acoustical performance and to reduce background sound levels were investigated: Step-1:
Add duct lining (1-inch and 2-inch were investigated).
Step-2:
Add duct silencers at supply and return ducts above the ceiling for the rooftop unitary packaged unit only.
Step-3:
Increase duct thickness (investigated in steps from 26, 24, 22, and 18 gage).
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Step-4:
Add gypsum-board duct enclosures from the roof penetrations of supply and return ducts extending to enclose the first duct elbow (to reduce fan or air sound leakage or breakout noise into the ceiling cavity).
The significant effects of each of the above measures on sound levels, energy use, and other building components were simulated using the TAP Acoustical Analysis and Trace 700 Energy Analysis Program. Findings from the analysis include: •
Of these, it was found through the TAP acoustical analysis of Systems 1, 2 and 3 that the acoustical improvement measures of Step 1 duct lining, and Step 2 duct silencers, offered insignificant improvements in the background sound levels. This is due to the fact that Systems 1, 2 and 3 have individual supply fans that discharge directly into main ducts located above the classroom ceiling and the breakout portion of the fan noise through the duct walls dominates over the airborne noise. For larger packaged units, (6 Tons and above) installed with the main ducts outside of the building, duct lining and duct silencers are still effective. Duct silencers and internal lining are proven to be effective in Systems 4 and 5. The air handling units used in the analysis for Systems 4 and 5 are provided with integral duct silencers and 2” acoustical lining constrained with perforated steel sheets at the fan sections.
•
In Step 3 increasing duct thickness, only the increase in duct-wall thickness to 18 gage offered significant sound-level improvement for Systems 1 and 3 and insignificant improvement for System 2. This is discussed with numerical results later in the report. This finding has not been substantiated through actual installation and measurement.
•
The enclosure of Step 4 is not subject to the TAP analysis, but has been measured to demonstrate improved acoustical performance for System 1.
•
The provision of vibration isolators for the rooftop unit and a sound barrier between the unit and the ceiling space for System 1 also offer significant improvements, but cannot be analyzed with the TAP program. Comparative field measurements in other buildings indicate that these can reduce the background sound level by approximately 3 dBA.
After preliminary calculations and analysis, the five Basic Systems were analyzed further by the acoustical consultant Mark Schaffer, using the sound-attenuation measures described for System 1 for ducts, diffusers, dampers, air velocity, and structural attenuation.
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BASIC SYSTEMS
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SYSTEM 1: Roof Top Packaged Air Conditioning with Gas Heating
Typical Roof Top Unit Air Distribution System Figure-1.1
This system is preferred by most districts and is LAUSD’s system of choice for smaller schools with multiple single or two story buildings that are less than 50,000 square feet each. A dedicated HVAC unit is provided for each classroom. The HVAC unit is typically installed directly on top of the classroom it serves, to avoid combination smoke / fire damper in the ducts. For two story buildings, two units are typically installed on the roof of the second floor classroom. The ducts for the first floor classroom are routed above the 7 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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ceiling of the second floor classroom from the HVAC unit to a shaft that goes into the space above the first floor ceiling. The majority of the units are 4 Tons capacity. The supply airflow rate is 1,600 CFM of which 1,000 CFM is returned and 600 CFM is relieved to outdoors through gravity relief openings. The typical basic design of this system for LAUSD consists of a rooftop packaged air conditioning unit mounted on a factory curb with vibration isolators and minimal ductwork serving two to four supply diffusers and one to two return registers. The measured background sound levels for installed systems of this type typically range between 42 and 49 dBA, depending on attenuation methods adopted, the type of construction of the building, and the quality of the design and installation. Measurements for a Type V, wood-frame building is usually higher than for a steel and concrete building. The lowest sound levels for this system were measured at a new high school building with steel frames where some sound attenuation measures were incorporated into the design and the quality of the construction and air balance was more controlled. These measures have already been adopted into the LAUSD design guidelines. The standard sound attenuation measures for this system are indicated in Figure 1.2.
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Typical Section of Down Discharge Rooftop A/C Unit Figure-1.2
The Trane Acoustical Program (TAP) Version-2 is used to estimate the classroom sound levels of each system type using sound data from two different manufacturers and the standard design measures for sound attenuation. The cost of each system with the standard design measures for sound attenuation is estimated using the Means Cost Estimating program with manufacturer provided equipment cost. Additional attenuation measures are then added to the standard system singly and in combinations to evaluate the attenuation of each arrangement.
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The following measures are found to have little or no effect on improving the acoustical performance of Roof Top Packaged Units of the 3, 4 and 5 Ton sizes that are typically used for classrooms (in the down discharge configuration). 1. Duct lining 1-inch thick 2. Duct lining 2-inch 3. Duct enclosures near the duct roof penetrations installed in conjunction with 1” lining 4. Installing duct silencers on both the supply and return near the duct roof penetrations at the cost of $ 1,450.00 for each classroom (i.e. about a 12% increase in overall HVAC cost). Also, duct silencers are effective only when the selfgenerated noise could be minimized by using silencers with thick (20 gage minimum) sheet steel casings or providing enclosures around the silencers that will add more cost. According to the TAP analysis, the most effective measure for improving acoustical performance is to use 18-gage ductwork for the rectangular main ducts. The overall increase in cost is about 20%. The theoretical attenuation is significant, but it has not been verified through field tests. The results are tabulated for easy comparison on the next page.
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Cost Benefit Analysis of Roof Top Gas/Electric Unit System Attenuation Cost Vs Sound Level
Equipment Carrier 48HJ rooftop unit Trane Precedent rooftop unit
26 gauge Ducts Throughout
18 gauge Rect. Main Ducts & 26 gauge Round Branches
NC
dBA
System Cost
NC
dBA
System Cost
47
46
$9,971.00
39
41
$11,871.00
46
47
$9,736.00
36
42
$11,636.00
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OTHER CONSIDERATIONS Energy Efficiency We estimated the following annual energy usage for a typical 960 square foot classroom with Trace 700 using typical school operating schedules:
Manufacturer Model Cooling Eff. SEER1 AFUE2 % Energy Use
Annual Energy Usage 900 Square feet area classroom Rooftop Air Conditioning Unit with Gas Heating Trane Precedent
Carrier HJ
12
13
81.4
80
Cooling
Heating
Cooling Heating Total Total kWh $/kWh Total $ Therms $/Therm kWh $/kWh Total $ Therms $/Therm $ $ 4,133.7 0.15 620.06 2.55 1.00 2.55 3,611.7 0.15 541.76 2.63 1.00 2.63
1.
Seasonal Energy Efficiency Ratio
2.
Annual Fuel Utilization Efficiency
Indoor Air Quality Air Filters:
2” thick air filters of MERV 8 (30%) efficiency
Indoor air circulation rate:
10 air changes per hour
100% outdoor air economizers:
Provided
Indoor air circulation rate:
10 air changes per hour
Maintenance Cost: Level of Difficulty:
$ 550.00 per classroom per year Low
Reliability Very reliable. Also, the breakdown of one unit will not affect the entire school.
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After-hours operation Easy to operate after hours and also very energy efficient as individual units can be started from the thermostat through a preprogrammed by-pass timer and the activation of a central plant is not necessary.
Interface with operable windows Individual units can be stopped through a special preprogrammed switch provided on the thermostat. The thermostats for unitary equipment in the current LAUSD guide specifications is provided with a 0 - 6 hours after hours override button. Holding down the override button for 5 seconds will deactivate the unit. This feature is included to avoid costly and unreliable proximity switches that will automatically deactivate the unit when the windows are opened. Environmental impact Cooling: The current refrigerant, R–22 will be phased out in 2020. Units with environmentally friendly (non-CFC/HCFC) refrigerants are available from a few manufacturers but they are not recommended as yet because the refrigerants are reported to be unstable mixtures and the required lubricants are so extremely hygroscopic that extra drying of the entire system is required before charging. We should wait until industry standards are more stable. Heating:
Low NOx burners are provided with units sold in California.
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SYSTEM 2: Split System Heat Pumps
Typical Split System Heat Pump Unit Air Distribution System Figure-2.1 This system is used for the lower floors of a classroom building of three stories or more and for modernization projects. A dedicated system is provided for each classroom. The majority of the units are 4 Tons capacity. The supply airflow rate is 1,600 CFM of which 1,000 CFM is returned and 600 CFM is relieved to outdoors through gravity relief openings or an exhaust system. The typical basic design of this system consists of an outdoor section that consists of a scroll compressor, an air cooled condenser and a condenser fan and an indoor section that 14 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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is a fan coil unit with a DX coil. Minimal ductwork serving four supply diffusers and two return registers is provided. Outdoor air is typically obtained through wall louvers or a dedicated outdoor air system. The outdoor section of the system is typically installed on the roof on a vibration isolator frame in new construction as indicated in Figure 2.2. On grade installation is preferred for modernization of single story to save the expense of the vibration isolators and roof structural upgrades. The indoor section is typically suspended above the ceiling of the classroom from hangers provided with vibration isolators as indicated in Figure 2.3.
Typical Vibration Isolator Rail for Outdoor Unit Figure-2.2
15 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Typical Suspended Fan Coil Mounting Above Ceiling Figure-2.3
Sound attenuation measures similar to the rooftop unit in the preceding section were taken as a standard for LAUSD in designing the ductwork. The measured background sound level for this system with 1” of duct lining throughout in a Type 1 steel frame building is about 43 dBA. The sound level estimates with TAP for various additional sound attenuation measures and their associated costs are tabulated on the next page.
16 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Cost Benefit Analysis of Split System Heat Pump Unit Attenuation Cost Vs Sound Level
Equipment
26 gauge Duct Throughout NC
dBA
35
42
46
46
Carrier FB4B split system Trane Odyssey split system
System Cost $8,414.00 $8,550.00
18 gauge Rect. Main Ducts & 26 gauge Round Branches NC
dBA
35
41
42
45
System Cost $10,314.00 $10,450.00
17 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
OTHER CONSIDERATIONS Energy Efficiency We estimated the following annual energy usage for a typical 960 square foot classroom with Trace 700 using typical school operating schedules:
Annual Energy Usage 900 Square feet area classroom Split System Heat Pump Unit Trane TWE
Manufacturer Model Cooling Eff. SEER1 HSPF2 Energy Use
11.25
9.55
7.85
7.5
Cooling kWh 3,881.5
Heating
$/kWh Total $ 0.15
Carrier FB4B
582.22
kWh
$/kWh
22.7
0.15
1.
Seasonal Energy Efficiency Ratio
2.
Heating Seasonal Performance Factor
Cooling Total kWh $/kWh Total $ $ 3.41 4,216.9 0.15 632.54
Heating kWh
$/kWh
20.6
0.15
Indoor Air Quality Air Filters:
2” thick air filters of MERV 8 (30%) efficiency is typically provided when outdoor air is obtained directly by the indoor section through wall louvers or roof vents. Higher efficiency filters can be provided when a dedicated outdoor air system is provided.
Indoor air circulation rate:
10 air changes per hour
100% outdoor air economizers:
Can be provided for individual systems but usually are omitted due to space limitations and higher cost. 100% outdoor air economizer systems cannot be provided with dedicated outdoor air systems.
18 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Total $ 3.09
Maintenance Cost:
$ 650.00 per classroom per year
Level of Difficulty:
Low but not as convenient as the rooftop units as the service person has to enter the classroom and lift up the ceiling tiles to service the indoor unit. Secondary drain pans, evaporator freeze stats and high condensate level shut-off switches are necessary to prevent ceiling damage from condensate overflow.
Reliability This system is quite reliable. The breakdown of one unit will not affect the entire school but the refrigerant lines are usually hidden in permanent construction and are difficult to access. When they leak, it is as difficult as repairing a water pipe leak between building studs. When a dedicated outdoor air or a common exhaust system is provided the breakdown of these added system components could affect an entire building and renders the systems less reliable After-hours Operation If a dedicated outdoor air or a common exhaust system is not provided, this system is easy to operate after hours and also energy efficient as individual units can be started from a programmable thermostat through a preprogrammed by-pass timer and the activation of a central plant is not necessary. An energy management system is not required. Additional controls are necessary when a dedicated outdoor air or a common exhaust system is provided. Also, air moving energy is wasted if only a few fan coils units among the many served by the system are necessary to operate. Interface with Operable Windows Individual units can be stopped through a special preprogrammed switch provided on the thermostat. The thermostats for unitary equipment in the current LAUSD guide specifications are provided with a 0 - 6 hours after hours override button. Holding down the override button for 5 seconds will deactivate the unit. This feature is included to avoid costly and unreliable proximity switches that will automatically deactivate the unit when the windows are opened. Some energy waste occurs when a dedicated outdoor air or a common exhaust system is provided. 19 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Environmental Impact Cooling: The current refrigerant, R-22 will be phased out in 2020. Units with environmentally friendly (non-CFC/HCFC) refrigerants are available at present from a few manufacturers but they are not recommended as yet because the refrigerants are reported to be unstable mixtures and the required lubricants are so extremely hygroscopic that extra drying of the entire system is required before charging. We should wait until industry standards are more stable. Heating:
Heat pumps produce no combustion products at the site.
20 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
SYSTEM 3: Four Pipe Fan Coil Units with Remote Central Plant
Typical Four Pipe Fan Coil Unit with Remote Central Plant Air Distribution System Figure-3.1 This is an older system that preceded reliable packaged equipment, and is still used extensively for larger buildings. A fan coil is provided for each classroom and is typically suspended above the ceiling of the classroom from hangers provided with vibration isolators as indicated in Figure 2.3. Minimal ductwork serving four supply diffusers and two return registers is provided. Outdoor air is typically obtained through wall louvers or a dedicated outdoor air system. Each fan coil unit is provided with a chilled water coil for cooling and a hot water coil for heating. Chilled water and hot water is pumped to the fan coil from a remote central plant that is provided with air or water cooled chillers and gas fired hot water boilers. 21 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
The majority of the classroom fan coil units are about 4 Tons capacity. The supply airflow rate is 1,600 CFM of which 1,000 CFM is returned and 600 CFM is relieved to outdoors through gravity relief openings or through an exhaust system. Sound attenuation measures similar to the rooftop unit in the preceding section were taken as a standard for LAUSD in designing the ductwork. The measured background sound level for this system in a Type 1 steel frame building is about 46 dBA. The sound level estimates with TAP for various additional sound attenuation measures and their associated costs are tabulated on the next page.
22 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Cost Benefit Analysis of 4 Pipe Fan Coil Unit System Attenuation Cost Vs Sound Level
26 gauge Ducts Throughout Equipment Carrier 42BH 4-pipe fan coil unit Trane BCHC 4-pipe fan coil unit
NC
dBA
49
46
52
48
System Cost (per classroom) $21,817.00 $20,442.00
18 gauge Rect. Main Ducts & 26 gauge Round Branches NC
dBA
40
42
42
43
System Cost (per classroom) $23,717.00 $22,342.00
23 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
OTHER CONSIDERATIONS Energy Efficiency We estimated the following annual energy usage for a typical 960 square foot classroom with Trace 700 using typical school operating schedules:
Annual Energy Usage 900 Square feet area classroom Four Pipe Fan Coil Unit Trane BCHC
Manufacturer Model Energy Use
Cooling 1
1
Heating
kWh
$/kWh
Total $
Therm
$/Therm
5,991.7
0.15
898.76
4.00
1.00
Carrier 42BH Cooling
Total kWh $/kWh $ 1 4.00 5,935.6 0.15
Heating Total $ Therms $/Therm 890.34
4.00
1.00
Total $ 4.00
. With 30% Filters.
Indoor Air Quality Air Filters:
2” thick air filters of MERV 8 (30%) efficiency is typically provided when outdoor air is obtained directly through wall louvers or roof vents. Higher efficiency filters can be provided when a dedicated outdoor air system is provided.
Indoor air circulation rate:
10 air changes per hour
100% outdoor air economizers:
Can be provided for individual systems but usually are omitted due to space limitations and higher cost. 100% outdoor air economizer systems cannot be provided with dedicated outdoor air systems.
24 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Maintenance Cost:
$ 800.00 per classroom per year
Level of Difficulty:
Higher as the service person has to enter the classroom and lift up the ceiling tiles to service the fan coil unit. Secondary drain pans and high condensate level shut-off switches are necessary to prevent ceiling damage from condensate overflow. The central plant requires a higher level of expertise and effort to service.
Reliability The breakdown of one chiller or boiler can affect the entire school especially in smaller schools where there is no redundancy and only one chiller or boiler is provided. When a dedicated outdoor air or a common exhaust system is provided the breakdown of these system components could affect an entire building and renders the systems less reliable.
After-hours Operation An energy management system or the assistance of a plant operator is required. Additional controls are necessary when a dedicated outdoor air or a common exhaust system is provided. Also, considerable energy is wasted if only a few fan coils units among the many served by the system are necessary to operate as the dedicated outdoor air fan, Central exhaust fan a chiller or boiler and related circulating pumps are necessary to be in operation, especially in smaller schools where a small dedicated chiller for after hours operation is not provided. Interface with Operable Windows Individual units can be stopped through a special preprogrammed switch provided on the thermostat. The thermostats for unitary equipment in the current LAUSD guide specifications are provided with a 0 - 6 hours after hours override button. Holding down the override button for 5 seconds will deactivate the unit. This feature is included to avoid costly and unreliable proximity switches that will automatically deactivate the unit when the windows are opened. Some energy waste occurs when a dedicated outdoor air or a common exhaust system is provided. 25 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Environmental Impact Cooling:
Chillers with environmentally friendly (non-CFC/HCFC) refrigerants are available at present from all manufacturers.
Heating:
Boilers are required by code to be provided with best available technology to comply with the Air Quality Management District Low Pollutant Emission Standards.
26 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
SYSTEM 4: Central Air Handling Units with Remote Central Plant
Typical Central Air Handling Unit with Remote Central Plant Air Distribution System Figure-4.1
27 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
This is an older system that preceded reliable packaged equipment, and is still used extensively for larger buildings. A central air handling unit is provided on the roof or inside an air handling unit room preferably one unit for each floor of the building. A variable air volume (VAV) terminal is provided for each classroom and is typically suspended above the ceiling of the classroom. Minimal ductwork serving four supply diffusers is provided downstream of the VAV terminal. The space above the ceiling is traditionally used as a return air plenum but due to CHPS indoor air quality requirements and the need to prevent high space air pressure fluctuations to maintain ADA door closer forces, ducted return air systems are used for current LAUSD projects. Each air handling unit is provided with a chilled water coil for cooling and a hot water coil for heating. Chilled water and hot water is pumped to the fan coil from a remote central plant that is provided with air or water cooled chillers and gas fired hot water boilers. The majority of the classroom VAV terminals are about 4 Tons capacity. The supply airflow rate is 1,600 CFM of which 1,000 CFM is returned and 600 CFM is relieved to outdoors through the return or relief fans at the air handling unit. This system is not as effective in controlling space humidity as systems with individual cooling coils. Also, the outdoor air to each room will also be reduced with VAV modulation unless special controls are provided to maintain a constant outdoor air flow rate at the cost of $ 3,000.00 for the smallest system. Sound attenuation measures similar to the rooftop unit in the preceding section were taken as a standard for LAUSD in designing the ductwork. The air handling units are provided with computer selected fans optimized for sound and internal vibration isolators. Duct silencers are provided on the roof or in the air handling unit room at both supply and return air main ducts. Custom air handling units with quieter fans, cabinets with higher sound absorption and built-in duct silencers are also available at substantial additional cost. The calculated background sound level for this system with a custom rooftop air handler with 5 feet long duct silencers in the supply and 3 feet long duct silencers in a Type 1 steel frame building is about 44dBA with the VAV terminal inside the classroom at the classroom closest to the air handler which is located on the roof above the corridor. The sound level is reduced to 37 dBA for the classroom farthest from the air handler with the VAV terminal located in the corridor. The sound level estimates with TAP for various additional sound attenuation measures and their associated costs are tabulated on the next page.
28 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Central Air Handling Unit System Cost and Acoustical Performance
Equipment
System Cost (per classroom)
Corridor NC dBA
Classroom NC dBA
Temtrol ITF-RDHRE43 AHU
46
44
31
37
$19,135.00
Energy Labs AHU
31
37
31
37
$20,135.00
29 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
OTHER CONSIDERATIONS Energy Efficiency We estimated the following annual energy usage for a typical 960 square foot classroom with Trace 700 using typical school operating schedules:
Annual Energy Usage 900 Square feet area classroom Central air handling units with VAV System Unit Manufacturer Temtrol Unit Model ITF-RDHRE43 Energy Use Cooling kWh $/kWh Total $ Therms 1 0.15 693.86 Minimal 4,625.7 1. Two Stages of Air Filtration with 30% Pre Filters and 95% Final Filters.
Heating $/Therm _
Total $ Minimal
Indoor Air Quality Air Filters:
Higher efficiency filters can be provided without any limitations.
Indoor air circulation rate:
10 air changes per hour or more at full load if duct space is available. A classroom with a VAV system will receive only about 4 or 5 air changes of re-circulated air during part load and heating. The outdoor air to each room will also be reduced unless special controls are provided to maintain a constant outdoor air flow rate. Air filter manufacturers recommend higher air changes to limit indoor particle counts. The coil leaving temperature could be reset higher to satisfy the zone with the highest cooling demand at the sacrifice of air moving energy savings from VAV and also reheat for humidity controls during periods of high humidity.
100% outdoor air economizers:
Provided.
30 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Maintenance Cost:
$ 800.00 per classroom per year
Level of Difficulty:
Higher. The central plant requires a higher level of expertise and effort to service.
Reliability The breakdown of one chiller or boiler can affect the entire school especially in smaller schools where there is no redundancy and only one chiller or boiler is provided. The breakdown of one air handler could affect an entire floor or building. After-hours Operation An energy management system or the assistance of a plant operator is required. Considerable energy is wasted if only a few rooms among the many served by the system are necessary to operate as the central air handler, exhaust fan, a chiller or boiler and related circulating pumps are necessary to be in operation. Interface with Operable Windows Individual VAV terminals can be closed from a programmable thermostat through a preprogrammed switch. The thermostats for unitary equipment in the current LAUSD guide specifications are provided with a 0 - 6 hours after hours override button. Holding down the override button for 5 seconds will deactivate the unit. This feature is included to avoid costly and unreliable proximity switches that will automatically deactivate the unit when the windows are opened. A similar method could be applied to a VAV system through the Energy Management System. Interface with an energy management system through proximity switches at the windows is not absolutely necessary. Environmental Impact Cooling:
Chillers with environmentally friendly (non-CFC/HCFC) refrigerants are available at present from all manufacturers.
Heating:
Boilers are required by code to be provided with best available technology to comply with the Air Quality Management District Low Pollutant Emission Standards.
31 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
SYSTEM 5: Radiant Panels with Remote Central Plant
Typical Radiant Panels with Remote Central Plant Air Distribution System Figure-5.1
32 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
This system is a relatively new type of system in the United States though it has been extensively used in Europe and Canada. This system is very quiet and energy efficient due to drastically reduced air movement since air moving energy is the major component of HVAC energy use. However, the design and installation of this system, requires a much higher level of expertise and cost. A central air handling unit is provided on the roof or inside an air handling unit room preferably one unit for each floor of the building to provide de-humidified outdoor air to each classroom. Radiant panels integrated with the ceiling are provided for each classroom to provide heating and cooling. Minimal ductwork for two outdoor air diffusers is provided for each classroom. All the supply air to the room is relieved through gravity to outdoors or is exhausted through a central exhaust fan system. The space above the ceiling can be used as a relief or exhaust air plenum but the need to prevent high space air pressure fluctuations to maintain ADA door closer forces may necessitate ducted exhaust air systems for larger buildings with fan assisted relief. Each dedicated outdoor air unit is provided with a chilled water coil for cooling and a hot water coil for heating. Chilled water and hot water is pumped to the air handling unit from a remote central plant that is provided with air or water cooled chillers and gas fired hot water boilers. The radiant panels are also provided with chilled water and hot water from a remote central plant. Sound attenuation measures similar to the rooftop unit in the preceding section were taken as a standard for LAUSD in designing the ductwork. Duct silencers are provided on the roof or in the air handling unit rooms at both supply and return air main ducts. The air handling units are provided with computer selected fans optimized for sound and internal vibration isolators. Duct silencers are provided on the roof or in the air handling unit room at both supply and return air main ducts. Custom air handling units with quieter fans, cabinets with higher sound absorption and built-in duct silencers are also available at substantial additional cost. The background sound level for this system with a custom rooftop air handler with 5 feet long duct silencers in the supply and 3 feet long duct silencers in the return in a Type 1 steel frame building is expected to be about 37dBA at the classroom closest to the air handler which is located on the roof above the corridor.
33 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
OTHER CONSIDERATIONS Energy Efficiency We estimated the following annual energy usage for a typical 960 square foot classroom with Trace 700 using typical school operating schedules:
Annual Energy Usage 900 Square feet area classroom Radiant Heating and Cooling Panels with Dedicated Outside Air System Manufacturer Temtrol DOA Air Handler with TWA Radiant Panels Model ITF-RDH17 Energy Use Cooling Heating kWh $/kWh Total $ Therms $/Therm 1 0.15 1,027.07 4.27 1.00 6,847.1 1. Two Stage Filtration with 30% Pre Filters and 95% Final Filters.
Total $ 4.27
Indoor Air Quality Air Filters:
Higher efficiency filters can be provided without any limitations.
Indoor air circulation rate:
100% outdoor air (No return) but 3 to 4 air changes per hour only. Air filter manufacturers recommend higher air changes to limit indoor particle counts. Interior zones of office buildings with VAV systems normally receive less than 4 air changes of re-circulated air. A classroom with a VAV system will receive only about 4 or 5 air changes of re-circulated air during part load and heating. 4 air changes of 100% outdoor air should be sufficient.
Maintenance Cost:
$ 800.00 per classroom per year
Level of Difficulty:
Higher. The central plant requires a higher level of expertise and effort to service.
34 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Reliability The breakdown of one chiller or boiler can affect the entire school especially in smaller schools where there is no redundancy and only one chiller or boiler is provided. The breakdown of one dedicated outdoor air handler or central exhaust fan could affect an entire floor or building. Condensation problems could occur with control system failure or operator error. After-hours Operation An energy management system or the assistance of a plant operator is required. Considerable energy is wasted if only a few rooms among the many served by the system are necessary to operate as the central dedicated outdoor air handler, central exhaust fan, a chiller or boiler and related circulating pumps are necessary to be in operation. Interface with Operable Windows Individual zone heating and cooling valves to the room radiant panels can be closed from a programmable thermostat through a preprogrammed switch. The thermostats for unitary equipment in the current LAUSD guide specifications are provided with a 0 - 6 hours after hours override button. Holding down the override button for 5 seconds will deactivate the unit. This feature is included to avoid costly and unreliable proximity switches that will automatically deactivate the unit when the windows are opened. A similar method could be applied to a VAV system through the Energy Management System. When outdoor humidity is high, condensation problems could occur with control system failure or operator error. Environmental Impact Cooling:
Chillers with environmentally friendly (non-CFC/HCFC) refrigerants are available at present from all manufacturers.
Heating:
Boilers are required by code to be provided with best available technology to comply with the Air Quality Management District Low Pollutant Emission Standards.
35 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
OTHER SYSTEMS
36 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
SYSTEM A: Water Source Heat Pumps
Typical Water Source Heat Pump Unit System Figure-6.1 Water source heat pump systems are considered hybrid systems, where a common water loop for condensing or heat exchange is provided from a central source for a building or a campus, while primary cold or heat generators may be distributed. A water source heat pump is provided for each classroom and is typically suspended above the ceiling of the classroom from hangers provided with vibration isolators as indicated in Figure 6.1. Minimal ductwork serving four supply diffusers and two return registers is provided. Outdoor air is typically obtained through wall louvers or a dedicated outdoor air system. The water source heat pumps are provided with a common water loop for condensing or heat exchange pumped from a campus wide central condenser water system. A minimum of two independent cooling towers, two boilers, and associated 37 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
accessories must be provided for a campus wide central condenser water system for redundancy. Positive means for fresh air make-up and sufficient means of relief to maintain door opening and closing pressures that comply with California Building Code accessibility requirements must be provided for classroom units. The majority of the classroom units are about 4 Tons capacity. The supply airflow rate is 1,600 CFM of which 1,000 CFM is returned and 600 CFM is relieved to outdoors through gravity relief openings or through an exhaust system. Sound attenuation measures similar to the rooftop unit in the preceding section were taken as a standard for LAUSD in designing the ductwork. The measured background sound level for this system exceeds 50 dBA for most installations when measured per current ANSI standard methods.
38 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
OTHER CONSIDERATIONS Energy Efficiency We estimated the following annual energy usage for a typical 960 square foot classroom with Trace 700 using typical school operating schedules:
Manufacturer Model Cooling Eff. EER1 Heating Eff. COP2 Energy Use kWh 6,928.6 1.
Energy Efficiency Ratio
2.
Coefficient of Performance
Annual Energy Usage 900 Square feet area classroom Water Source Heat Pumps Carrier 50 R Series 14.6 4.9 Cooling $/kWh Total $ kWh 0.15 1,039.29 23.1
Heating $/kWh 0.15
Total $ 3.47
Indoor Air Quality Air Filters:
2” thick air filters of MERV 8 (30%) efficiency is typically provided when outdoor air is obtained directly through wall louvers or roof vents. Higher efficiency filters can be provided when a dedicated outdoor air system is provided.
Indoor air circulation rate:
10 air changes per hour
100% outdoor air economizers:
Can be provided for individual systems but usually are omitted due to space limitations and higher cost. 100% outdoor air economizer systems cannot be provided with dedicated outdoor air systems.
Maintenance Cost:
$ 800.00 per classroom per year 39
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Level of Difficulty:
Higher as the service person has to enter the classroom and lift up the ceiling tiles to service the unit. Secondary drain pans, and high condensate level shut-off switches are necessary to prevent ceiling damage from condensate overflow. The central cooling tower and boiler plant requires a higher level of expertise and effort to service.
Reliability The breakdown of one cooling tower or boiler can affect the entire school especially in smaller schools where there is no redundancy and only one tower or boiler is provided. When a dedicated outdoor air or a common exhaust system is provided the breakdown of these system components could affect an entire building and renders the systems less reliable.
After-hours Operation An energy management system or the assistance of a plant operator is required. Additional controls are necessary when a dedicated outdoor air or a common exhaust system is provided. Also, considerable energy is wasted if only a few fan coils units among the many served by the system are necessary to operate as the dedicated outdoor air fan, central exhaust fan, a tower or boiler and related circulating pumps are necessary to be in operation.
40 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Interface with Operable Windows Individual units can be stopped through a special preprogrammed switch provided on the thermostat. The thermostats for unitary equipment in the current LAUSD guide specifications are provided with a 0 - 6 hours after hours override button. Holding down the override button for 5 seconds will deactivate the unit. This feature is included to avoid costly and unreliable proximity switches that will automatically deactivate the unit when the windows are opened. Some energy waste occurs when a dedicated outdoor air or a common exhaust system is provided.
Environmental Impact Cooling:
The current refrigerant, R-22 will be phased out in 2020.
Heating:
Boilers are required by code to be provided with best available technology to comply with the Air Quality Management District Low Pollutant Emission Standards.
41 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
SYSTEM: B Wall-Mounted Packaged Heat Pumps with Ducted Supply
Typical Wall Mounted Heat Pump Unit System Fig 7.1
42 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Section for Typical Wall Mounted Heat Pump Unit Fig 7.2
43 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Wall mounted packaged heat pumps are the lowest cost and least invasive (least disruptive to existing Architecture to install) for modernization projects. They are also very inexpensive to operate. These advantages are offset by the significantly higher sound levels. Within ten feet of the unit, these systems produce at best a sound level of 50 dBA, and closer to the unit the levels reach 55 and 60 dBA in most cases. Because there is usually no ductwork exterior to the units (though the above drawings indicate a ducted supply air installation with no ductwork on the return), no opportunity to attenuate the units externally exists. The only option is to improve the design of these units to make them quieter. The following items should be considered for unit improvement: 1. Make indoor air supply fans quieter by using bigger fans operating at a lower speed. 2. Make condenser fans quieter by using centrifugal fans or specially designed quieter propeller fans in lieu of the noisy propeller fans that are currently used. 3. Make compressors quieter by using scroll compressors in thicker gauge housings, provide higher density insulation for the housings or provide external lagging. 4. Provide vibration isolators at fans and compressors. 5. Provide flexible connectors for pipes at compressors. 6. Provide flexible connectors at fan outlets. 7. Make the unit cabinet quieter by using a double wall cabinet of thicker gauge sheet metal with gaskets at all joints and thicker insulation. The locations of these units also have a substantial impact on the classroom sound level. The typical location on a classroom wall in a modernization project is at a window that is adjacent to or between existing windows that are usually of 1/8” glass as indicated in Figure 7.1. These windows offer very little sound attenuation and the radiated noise from the unit entering through the windows, contributes significantly to the classroom sound level. The manufacturer’s recommended installation as indicated in Figure 7.2 suggests that these units are intended for installation against a solid wall.
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SYSTEM C: Duct Free Systems
Typical Hi Wall System Fig 8.1
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Typical Ceiling Suspended System Fig 8.2 46 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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Typical Console Unit System Fig 8.3
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Typical in Ceiling Cassette System Fig 8.4 48 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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The above systems are variations of split-system heat pumps that were studied as System 2 in an earlier section, with ductless indoor units. They are less invasive (least disruptive to existing Architecture to install) than rooftops or conventional split systems for modernization projects. They are also relatively less expensive as installation of ductwork is not required. They are also quite energy efficient and match those of the split system heat pumps. They are available in three typical configurations: High Wall as indicated in figure 8.1. The indoor sound pressure level measured 1 meter away from the indoor unit of this system is about 48.3 dBA at low speed for a 2 ton Unit. Indoor sections of high wall systems are only available up to 2 Tons capacity. Two indoor units will be required for a typical LAUSD classroom thus increasing the indoor sound level to about 51 dBA. Ceiling suspended (valance) as indicated in figure 8.2. The indoor sound pressure level measured 1 meter away from the indoor unit of this system is about 58.0 dBA at medium speed for a 4 ton Unit. This unit is not available in low speed. Console as indicated in figure 8.3. The indoor sound pressure level measured 1 meter away from the indoor unit of this system is about 40.0 dBA at low speed for a 2 1/2 ton Unit. Indoor sections of console systems are only available up to 2 ½ Tons capacity. Two indoor units will be required for a typical LAUSD classroom thus increasing the indoor sound level to about 43 dBA. A Ceiling Cassette System is shown in figure 8.4. The indoor sound pressure level measured 1 meter away from the indoor unit of this system is about 45.6 dBA at medium speed for a 4 ton Unit. This unit is not available in low speed. Some severe limitations exist with these systems. Indoor sections of high wall systems are only available up to 2 Tons capacity and console systems up to 2 ½ Tons capacity. Therefore, two indoor units would be required for a typical LAUSD classroom. These systems are also only available with low-efficiency; cleanable air filters (filters that are required to be periodically cleaned). The current LAUSD standard is minimum 30% efficiency, low-pressure drop, pleated, disposable air filters, which are more effective and less costly to maintain. Outdoor air ventilation is not readily available through the unit with high wall, console and ceiling suspended systems. Classrooms are required by code to be provided with 20 cubic feet per minute of outdoor air per student. This limitation alone precludes three configurations of this type of system from classroom applications in new construction. For modernization projects, these units may be used in conjunction with a dedicated outdoor-air ventilation system after careful analysis. However, the cost and invasiveness of the dedicated outside air system may render the systems impractical. 49 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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These systems cannot provide a 100% outdoor-air economizer cycle. The maintenance cost is higher and the level of difficulty to service is also considerably higher. The indoor sections have to be practically totally dissembled for service. After-hour operation and interface with operable windows is relatively easy and is similar to split-system heat pumps. Environmental impact is similar to split-system heat pumps.
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ACOUSTICAL REQUIREMENTS OF LAUSD DESIGN GUIDELINES
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ACOUSTICAL REQUIREMENTS of LAUSD DESIGN GUIDELINES General Requirements in the LAUSD Design Guidelines that relate to the acoustic and noise aspects of HVAC systems are contained in the “Guide Specifications” that specify equipment, installation measures and testing methods, and in the “School Design Guide” that present design criteria for the AE firms. Following are excerpts from those documents illustrating the measures related to HVAC acoustics that the District requires. These include all of the noise mitigation measures included in this study and report, with the exception of the increase in duct wall thickness to 18 gage. Actual field testing of this measure is recommended prior to its adoption as a standard.
Acoustical Measures in the Guide Specifications Section 01450 Test and Balance, Article 3.02 E and F: E.
Verification: The Test and Balance Agency shall recheck ten percent (minimum ten) of the measurements listed in the report. The locations shall be selected by the IOR/OAR. The recheck will be witnessed by the IOR/OAR. If twenty percent of the measurements that are retested differ from the report and are also out of the specified range, an additional ten percent will be tested. If twenty percent fall outside the specified range, the report will be considered invalid and all test and balance work shall be repeated.
F.
Due to more stringent acoustical requirements in the educational environment, the Test and Balance Agency shall recheck the air systems where the sound level is higher than the design intent or district standard and demonstrate compliance with the methodology specified in this document with emphasis on fan speed adjustment and balancing for optimum acoustical performance. The recheck will be witnessed by the IOR/OAR. When there are multiple air systems, a system selected by the IOR/OAR shall be rechecked. If this system is found to be not in compliance, a second system shall be checked. If the second system if also found to be not in compliance, the report will be considered invalid and all test and balance work shall be repeated.
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Section 01450 Test and Balance, Article 3.06 Q and R: Q.
R.
The following sound test data is required: 1.
Area or location
2.
Sound level in dB(A) as specified in Section 3.20
3.
Sound level at the center band frequencies of eight non-weighted octaves with equipment on and off for 5 rooms selected by the OAR/IOR.
4.
Plot corrected sound-level reading on Noise Criteria (NC) curve for the measurements in Q 3 above.
The following vibration test data is required: 1.
Equipment identification number
2.
Vibration levels at all accessible bearings, motors, fans, pumps, casings, and isolators
3.
Measurements in mils defection and velocity in inches per second as specified per section XIV of this document Each measurement taken in horizontal, vertical, and axial planes as accessible.
4.
Section 01450 Test and Balance, Article 3.09 (k 1 – 5): k.
Fan speed adjustments and balancing for optimum acoustical performance: 1)
As the very first step, the speed of all fans (supply, return, exhaust, inside packaged equipment or air handling units) shall be adjusted to deliver the required fan total air quantity with all volume dampers and other flow rate control devices fully open. Adjustments shall be made with the outdoor air intake dampers, return air dampers and relief air dampers in the minimum outdoor air position. The adjustments shall be made again in the100% outdoor air position in systems with 100% outdoor air economizers.
2)
The above adjustment shall be done with wet cooling coils where cooling coils are provided.
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3)
The airflow rates at each branch duct shall be adjusted as the second step with air with all volume dampers and other flow rate control devices fully open.
4)
The airflow rates at each air inlet and outlet shall be adjusted as the final step. The volume damper in the branch duct shall be used for balancing. Opposed blade dampers at air inlets and outlets where provided shall only be used for fine adjustments and shall not be closed beyond 60% open or when the dampers start to generate audible noise.
5)
Contractor shall provide the labor and materials for all dampers, pulleys and belt changes required for balancing. The design documents indicate the worstcase scenario with safety factors in fan static pressures for contingency. Properly coordinated and installed air systems may require a lower static pressure and a reduction in fan speed.
Section 01450 Test and Balance, Article 3.18, 3.19: 3.18.
VIBRATION TESTING A.
Furnish instruments and perform vibration measurements if specified in Division 15. Provide measurements for all rotating HVAC equipment half horsepower and larger, including reciprocating/centrifugal/screw/scroll compressors, pumps, fans and motors.
B.
Record initial and final measurements for each unit of equipment on test forms. Where vibration readings exceed allowable tolerance and efforts to make corrections have proved unsuccessful, forward a separate report to Architect.
3.19
SOUND TESTING A.
Perform and record sound measurements as specified in this section and if specified in Section 15240: Sound Vibration and Seismic Control. Take additional readings if required by Architect.
B.
Take measurements with a calibrated Type 1 sound level meter and octave band analyzer. 54
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C.
Sound reference levels, formulae and coefficients shall be according to ASHRAE handbook, Current Systems Volume; Chapter: Sound and Vibration Control.
D.
Determine compliance with the Contract Documents as follows: 1.
Where sound pressure levels are specified as noise criteria or room criteria in Section 15070: Sound, Vibration and Seismic Control. a.
Reduce background noise as much as possible by shutting off unrelated audible equipment.
b.
Measure octave band sound pressure levels with specified equipment "off".
c.
Measure octave band sound pressure levels with specified equipment "on".
d.
Use difference in corresponding readings to determine sound pressure due to equipment. DIFF.: 0 1 2 3 4 5 9-10 or More FACTOR: 10 7 4 3 2 1 0 Sound pressure level, due to equipment, equals sound pressure level with equipment "on" minus factor. e.
2.
3.
Plot octave bands of sound pressure level due to equipment for typical rooms, on a graph, which also shows, noise criteria (NC) curves.
When sound power levels are specified: a.
Perform steps in Section 3.20, D, 1.a. through 1.d.
b.
For indoor equipment: Determine room attenuating effect; i.e., difference between sound power level and sound pressure level. Determine sound power level will be sum of sound pressure level due to equipment, plus room attenuating effect.
c.
For outdoor equipment: Use directivity factor and distance from noise source to determine distance factor, i.e., difference between sound power level and sound pressure level. Measured sound power level will be sum of sound pressure level due to equipment, plus distance factor.
Where sound pressure levels are specified in terms of dBA, measure sound levels using the "A" scale of meter. Single value readings will be used instead of octave band analysis. 55
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E.
Where measured sound levels exceed specified level, Contractor shall take all remedial action and necessary sound tests shall be repeated.
F.
Measure and record sound levels in decibels at each diffuser, grille or register in occupied areas. Sound levels shall be measured approximately 5'-0" above floor on a line approximately 45 degrees to center of opening, on the "A" and "C" scales of a General Radio Company sound level meter, or similar instrument. E. G. Report shall also include ambient sound levels of rooms in which above openings are located, taken without air-handling equipment operating. A report shall also be made of any noise caused by mechanical vibration.
Section 15010 Basic Mechanical Requirements, Article 1.01 M: M.
Noise and Vibration Reduction 1.
Correct noise or vibration problems caused by failure to install work in accordance with Contract Documents. Include all labor and materials required as a result of such failure. Pay for re-testing of corrected noise or vibration problems by the project acoustical consultant including travel, lodging, test equipment expenses, etc.
Section 15070 Mechanical Sound, Vibration, and Seismic Control: Entire Section Section 15700 Heating, Ventilating and Air Conditioning Equipment, Article 2.02 A (1. c and d): 2.02
AIR CONDITIONING UNITS A.
AC-1a (2.5 Tons-20 Tons): (Specify when higher energy efficiency, higher air filtration efficiency or lower sound levels are required) Furnish packaged air conditioning unit with gas heating for roof top installation. Unit shall be self-contained, completely factory assembled, with complete internal wiring and controls. Unit shall also be provided with a fully piped refrigerant circuit, fully charged with an environmentally friendly refrigerant that is not scheduled for phase out. Unit shall be field configurable for down-flow or horizontal discharge. Cooling and heating capacities, electrical characteristics, indoor sound levels, outdoor sound levels and operating conditions shall be as indicated on Drawings. 56
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1.
Quality Assurance: c.
Unit outdoor sound levels shall also be rated in accordance with ARI sound standards 270 and 370.
d.
Unit indoor sound levels shall also be rated in accordance with ARI sound standards 260.
Section 15800 Air Distribution, Article 1.03 : 1.03
QUALITY ASSURANCE A.
Installer's and Manufacturer's Qualifications: Comply with provisions stated under Section 15010: Basic Mechanical Requirements.
B.
All sound power level measurements and Manufacturers' NC value calculations shall be conducted in complete accordance with the latest version of ASHRAE Standard 70 and ADC Standard 1062: GRD-84. Equivalent test and calculation procedures may be substituted for the above procedures if approved in advance by the Architect.
Section 15800 Air Distribution, Article 2.01 E and H 4 and 5: E.
Galvanized steel ducts gage thickness and permissible joints and seams of concealed ductwork shall conform to requirements in HVAC Duct Construction Standards of Sheet Metal and Air Conditioning Contractor’s National Association (SMACNA) and the California Mechanical Code (CMC) unless noted otherwise on the drawings. The more stringent requirements shall prevail. Galvanized steel ducts gage thickness and permissible joints and seams of exposed ductwork shall conform to requirements in Table 2, Minimum Metal Gages, of this section. When more stringent requirements are noted on the drawings the most stringent requirement shall prevail.
H.
Round and Oval Galvanized Steel and Aluminum Ducts: 4.
Minimum duct wall thickness for concealed flat oval duct construction shall conform to requirements in HVAC Duct Construction Standards of Sheet Metal and Air Conditioning Contractor’s National Association (SMACNA) and the California Mechanical Code (CMC). The more stringent requirements shall prevail. Gage thickness and permissible joints and seams of exposed ductwork shall conform to requirements in Table 1, of this section. 57
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5.
Flexible duct shall be non-metallic, insulated for conditioned air supply and return. The flexible ducts shall be factory fabricated with exterior reinforced laminated vapor barrier, 1-1/2 inch thick fiber glass insulation (K=0.25 @ 75 degrees F.), encapsulated zinc-coated spring steel wire helix and impervious, smooth, non-perforated interior vinyl liner and factory fabricated steel connection collars. For the composite assembly, including insulation and vapor barrier, comply with NFPA Standard 90 A or 90 B and tested in accordance with UL Standard, UL-181. Noninsulated metallic ducts shall be provided for exhaust only.
Section 15800 Air Distribution, Article 2.03 A , 2.05 A (1 – 3) , 2.06 : 2.03
ACOUSTICAL DUCT AND PLENUM LINERS A.
2.05
Duct liners shall conform to requirements of Section 15080: Mechanical Insulation. AIR DISTRIBUTION DEVICES
A.
General: 1.
Grilles, registers, diffusers and appurtenances shall conform to requirements specified herein and shall be of type and sizes as specified and indicated on Drawings. Performance shall be in accordance with Air Diffusion Council Test Code 1602R2 including airflow velocity, pressure, temperature, and sound measurements.
2.
Sponge neoprene, rubber, vinyl or felt border gaskets shall be provided for surface-mounted registers, grilles or diffusers.
3.
The noise generating characteristics of all specified grilles, registers, and diffusers shall be tested to, and comply with, all requirements of this specification. Representative samples shall be subjected to tests in accordance with applicable standards and procedures in order to demonstrate such compliance. A special test for this project is not required if the manufacturer has previous certified test results that can be made applicable to this project. Maximum Sound Levels of diffusers, grilles and registers shall be as follows:
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Administrative office area: Classrooms: Libraries and other noise sensitive areas: Gymnasiums, cafeterias, lockers areas: 2.06
NC 30 NC 20 NC 25 NC 30
SOUND ATTENUATING EQUIPMENT - DUCT SILENCERS A.
Provide factory fabricated duct silencers of tubular or rectangular type, for high or low velocity service, with arrangements, sizes and capacities as indicated on Drawings. Construct silencers of galvanized steel with casing seams sealed or welded to be airtight at a pressure differential of 8 inches water gauge between inside and outside of unit, and stiffen or brace as required to prevent structural failure or deformation at same condition, or audible vibration during normal operation. Filler material shall comply with the following: Fire Safety Standards: NFPA 90A & B Temperature: ASTM C 411 Air velocity: ASTM C 1071, UL 181 Fire Hazard Classification: ASTM E 84, UL 723-Class 1, NFPA 255 Corrosion Resistance: ASTM C 739, C 665 Fungi Resistance: ASTM G21 Bacteria Resistance: ASTM G22 Water Vapor Sorption: ASTM C 1104, less than 1% by weight Formaldehyde, Phenoloc Resins or other Volatile Organic compounds: 0%
B.
Select and provide silencers from acoustical and aerodynamic rating tables based on actual test readings or interpolated values of such readings obtained from tests made by recognized independent laboratories. Tests shall be in accordance with ASTM E 477.
C.
Select and provide silencers for air pressure drops not exceeding those indicated on Drawings, and of types, sizes and models for which noise reduction values, dynamic insertion loss, in decibels reference 10-12 watts, are not less than indicated on Drawings.
Section 15800 Air Distribution, Article 3.02 F: F.
Construct and install ducts to be completely free from vibration under operating conditions.
Section 15800 Air Distribution, Article 3.10 A:
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3.10
FLEXIBLE CONNECTIONS A.
At points where sheet metal connections are installed to fans or air handling units, or where ducts of dissimilar metals are connected, a flexible connection of commercial grade, Duralon by Duro-Dyne Corporation, or equal, noncombustible material shall be installed and securely fastened by zinc-coated steel clinch-type bands or a flange type connection. Inlet and outlet openings shall be axially in-line, maximum deviation of centerline shall be less than 5 percent of diameter or shortest dimension of a rectangular inlet of fan or air handling unit, with system at rest. Duct end of connection shall be seismically restrained if more than 4 feet from last support.
Section 15800 Air Distribution, Article 3.12 A: 3.12
DAMPERS A.
Manually operated dampers, gravity dampers, fire dampers, and motor operated dampers shall be furnished and installed as specified and indicated. Upon completion of installation, dampers shall be checked, lubricated, and adjusted so that they operate freely, without binding. Dampers shall be of standard commercial manufacture, complete with damper frame. Where painting is required, they shall be shop finished unless otherwise noted. 1.
Provide and install manual volume dampers per current SMACNA standards to allow balancing per current AABC, NEBB or TABB Procedures and Standards whether indicated on the drawings or not.
2.
Balancing dampers shall be installed in main supply ducts from fan discharge plenums, where 2 or more ducts are connected to each plenum, although such balancing dampers may not be indicated. Each zone shall be provided with a manual volume damper. Sheet metal screws shall be installed through handles and into ducts to lock damper in place after test and balance.
3.
Each Supply, return, and exhaust branch shall be provided with manual volume dampers.
4.
Do not provide opposed blade dampers at air inlets and outlets.
5.
Each supply, return, and exhaust inlet or outlet shall be provided with a manual volume damper. This damper shall be a minimum of 5 feet upstream of the air outlet/inlets. An acoustic flexible duct should be provided between the outlet/inlet and the damper for concealed ducts. 60
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6.
Dampers installed in accessible locations shall be provided with locking and indicating quadrants. Ventlock, Duro-Dyne, or equal.
7.
Dampers installed in ductwork in furred ceiling spaces or in roof spaces with less than 30 inches of clearance below beams, joists, or other construction, and where access panels are not provided shall be furnished with damper rods extended below ceiling and terminated with a concealed damper regulation. Ventlock, Young, or equal.
8.
Dampers not identified as splitter, extractor, or butterfly dampers shall be of multi-louver type arranged for opposed blade operation. Damper shall be same dimension as adjoining duct and be tight closing. Blades shall not be greater than 9 inches. Dampers shall be not less than 18 gage steel.
9.
Motor operated dampers shall be furnished by temperature control manufacturer as part of temperature control equipment and shall conform to requirements of Section 15900: HVAC Instrumentation and Controls.
10.
Dampers shall be provided with accessible operating mechanisms. Where operators are exposed in finished portions of building, operators shall be chromium-plated with exposed edges rounded. Splitter dampers are not permitted unless specified and reviewed by the Architect.
11.
Dampers shall not be installed in combustion air ducts.
12.
Access panels shall be installed for access at each damper’s operating mechanism.
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Acoustical Measures in the School Design Guide Book 3 Technical Criteria, Section 3.6 HVAC SYSTEMS, Article C, HVAC System Selection, 1. Criteria 14, page 5: 1.
Criteria 14. Acoustically compatible with occupied spaces
Book 3 Technical Criteria, Section 3.6 HVAC SYSTEMS, Article E, Air Distribution, page 11-12: E
Air Distribution Ventilation and Outside Air a.
Provide outside air to each room through the HVAC system in compliance with current CEC Standards and ASHRAE recommendations. .
b.
Clearly indicate outside-air provisions and flow rates for each HVAC unit, and relief provisions to balance the fresh outside air make-up and to relieve exhaust air in all operating cycles.
c.
Fresh Air Intakes: 1. Locate fresh air intakes to prevent contamination from kitchen exhaust, garage exhaust, or any process exhaust by locating the intakes on the upstream (prevailing wind) side of exhaust openings, as distant as possible. 2. Limit intake velocity to 750 FPM through net free louver area at 100 percent fresh air quantities to keep noise, pressure drop and rain carryover to a minimum.
Ducts: a.
Comply with current code and SMACNA Guidelines for duct construction. Thicker metal gages for ducts and hanger straps, as specified in the Guide Specifications, must be used for exposed ductwork and other special considerations.
b.
Size ductwork for conditioned air on equal-friction 0.08" WC per 100 feet with a high velocity limit of occupied areas and 1,500 FPM inside shafts, or as by the Project Acoustical Consultant. Changes
method based on 1,000 FPM above directed otherwise in sizes at every 62
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branch or every interval are not warranted economically unless branch represents a substantial percentage. c.
Size return-air and exhaust air ducts on equal-friction method based on 0.08" WC per 100 feet with a high velocity limit of 1,000 FPM above occupied areas and 1,500 FPM inside shafts or as directed otherwise by the Project Acoustical Consultant..
d.
Allowable air velocities for ducts above acoustically sensitive areas shall be determined by an Acoustical Engineer.
e.
Duct the return air. Ceiling plenum return is not allowed as a means to improve indoor air quality.
f.
Sound attenuators or lined ducts should be installed on inlet and outlet side of fans, and between fans and ducts, to prevent fan noise entering rooms through the duct system. Do not locate duct sound attenuators inside the building above (the ceiling of) occupied spaces where the breakout noise will increase indoor sound levels above acceptable limits.
Fans 1.
Select fans to minimize noise and to meet noise level criteria in occupied spaces.
2.
Commissioning Measures 1. Air Balance: Systems must be balanced for both the regular and economizer modes.
Most unitary systems are specified with a safety factor in the static pressure. The Contractor must be required by the specifications to replace the drive sheaves and slow the fan down to achieve the required air balance and prevent energy waste and noise. If this is not done, the air flow is left higher creating higher static pressure and noise levels. Cooling Towers: a.
Size cooling towers for 120% to 150% of required capacity, to guarantee full capacity from chiller at any wet bulb conditions and to allow for fouling of tower.
b.
Provide a bleed-off system and a chemical feeder to prevent mineral build-up and to maintain water quality.
c.
Provide for make-up water to replace evaporation and bleed.
Locate cooling towers to avoid unsightly conditions and so that noise generated by fan will not be objectionable in adjoining buildings. Provide louvered screens, masonry walls, or planting for concealment. 63 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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Book 3 Technical Criteria, Section 3.6 HVAC SYSTEMS, Article I, Sound and Vibration Control, page 22: B SOUND AND VIBRATION CONTROL: 1.
2.
Criteria: a.
Because mechanical systems and equipment are a major source of disturbing noise within buildings, sound and vibration control measures must be incorporated to the maximum extent economically practical. In general, refer to current ASHRAE guidelines, District Guide Specifications, chapter 2.4 “Environment and Sustainability” of this Guide, and the following recommendations.
b.
Since the District desires to achieve noise levels from HVAC systems better than 45 dBA, especially in instructional spaces, plan and describe in the “Basis of Design” narrative how this improved acoustical quality will be achieved together with the associated cost impacts.
Equipment Sound Levels: Schedule the sound level of the design base HVAC equipment on the drawings. These sound levels must be at the design conditions and tested per applicable current standards such as ARI Standards 260, 270, 370 and AMCA 300.
Duct and Fan Noise: a.
Ductwork: 1. Use ducts of thicker sheet metal gage and sound attenuators to reduce fan and equipment noise. Lined ductwork may be used when recommended by the Project Acoustical Engineer. Duct lining, acoustical panels in ductwork and sound attenuator media when used shall be of the type that inhibits the growth of mold, mildew and fungi, contain harmful VOC’s or contain glass fiber. 2. Provide flexible connectors for ducts at fan connections 3. Do not locate sound attenuators above spaces where the self generated noise of the attenuator will increase the space sound level above requirements.
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b.
Fans: 1. Fan-noise in occupied spaces is typically caused by poorly constructed roof fans, roof fans operating at too great a tip speed, fan noise traveling through air intake louvers and then into adjoining spaces, and fan noise traveling to occupied spaces through inadequately treated return systems. Fan noise also comes from rooms without sound-attenuating walls or from roof-top units with inadequate sealing of roof openings and duct chases. 2. Locate fan and equipment rooms away from classrooms and other noise-sensitive spaces. 3. Make fan and equipment room walls of dense material, poured concrete or concrete block with all voids filled where feasible – or sound-attenuating walls of studs and gypsum board. 4. Provide details to assure adequate sealing of duct penetrations through roof or mechanical equipment room walls. 5. At roof fans exhausting from ceiling plenums over occupied areas, provide a sound attenuator installed at fan inlet.
Equipment Mounting and Isolation: a.
For roof-top HVAC units, no roof penetrations are allowed except the minimum necessary for ducts and electrical conduit. All such openings shall be sealed with acoustical sealant. In addition, beneath the units provide a sound-isolation barrier of a close-fitting layer of ¾” waterproof plywood or cement board, sealed with acoustical tape to the curb.
b.
For fans over 24" provide inertia type concrete bases with spring isolators. For smaller fans provide spring-type vibration isolator rails under fan and motor.
c.
Floor-mounted pumps shall be bolted directly to concrete bases and shall have flexible pipe connections, except when located over or under an occupied area where noise could be transmitted by piping or building structure to occupied space. In this case, they shall be mounted on inertia type concrete bases with spring-type vibration isolators and shall have flexible connections rigidly anchored and braced to prevent elongation of the flexible connections.
d.
Air compressors shall be mounted on spring-type vibration isolators, except larger sizes shall also have concrete inertia bases and flexible pipe connections. 65
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Pipe, Conduit and Duct Connections to HVAC Equipment a.
Pipe, duct and electrical conduit connections to HVAC equipment with rotating or reciprocating components shall be provided with flexible connectors.
b.
Provide spring, neoprene or rubber in shear type hangers as required for pipes and ducts near connections to HVAC equipment that are located near or serve acoustically sensitive spaces as directed by an acoustical engineer.
Classroom HVAC Sound Control: a.
To meet District standards, HVAC systems must be designed so that noise from the system does not cause the ambient noise in a classroom to exceed the level of 45 dBA as measured in accordance with ANSI Standard 12-60. Make design recommendations to the District to achieve a lower sound level, within reasonable economic limits
b.
ASHRAE recommended design criteria for classroom HVAC sound control is Noise Criteria (NC) Curve NC-35. An HVAC system will probably meet the District 45 dBA criteria when no portion of octaveband spectrum of noise lies above NC-35 curve. (This is approximately equivalent to a sound level of 45 dBA from a standard sound level meter reading,)
c.
Refer also to the “Environment and Sustainability” chapter of this Design Guide for additional standards and reference to CHPS Best Practices.
66 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Different Perspectives Two articles published in 2004 HVAC trade magazines stating two very different points of view are also attached. An acoustical engineer thinks that the ANSI S12.6 is impractical but a duct lining manufacturer strongly supports the standard.
67 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
68 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
69 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
ACOUSTICAL ENGINEER’S REPORT & CALCULATIONS
70 Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
Schaffer Acoustics Inc 869 Via de La Paz, Suite A Pacific Palisades, CA 90272 tel 310-459-6463 fax 310-459-1406
[email protected] Mr. James Shwe Maroko & Shwe 10200 Sepulveda Blvd., #380 Mission Hills, CA 91345 Subject:
January 31, 2005
LAUSD HVAC Cost, Energy and Acoustical Study
James: At your request, and with your assistance, Schaffer Acoustics Inc performed acoustical calculations for several classroom HVAC system alternatives. This report summarizes the calculation results for the following HVAC system designs: System 1A
Carrier 48HJ rooftop package unit
System 1B
Trane Precedent rooftop package unit
System 2A
Carrier FB4B DX split system fan coil unit in classroom ceiling plenum
System 2B
Trane Odyssey DX split system fan coil unit in classroom ceiling plenum
System 3A
Carrier 42BH 4-pipe fan coil unit in the classroom ceiling plenum
System 3B
Trane BCHC 4-pipe fan coil unit in the classroom ceiling plenum
System 4A
Remote central station air handling unit (Energy Labs custom unit) with a 1600 CFM VAV terminal unit in the classroom ceiling plenum System 4B Remote central station air handling unit (Temtrol ITF-RDHRE43) with a 1600 CFM VAV terminal unit in the classroom ceiling plenum System 5 Remote central station air handling unit (Temtrol ITF-RDH17) constant air volume system (720 CFM per classroom) with radiant cooling panels in the classroom – this system was not analyzed but is discussed in this report
All calculations assumed a 960 sq. ft. classroom with an acoustical tile ceiling at 9 feet above the floor. CRITERIA
LAUSD HVAC Acoustical Study January 31, 2005 Page 2 of 6
Schaffer Acoustics Inc Consulting, Testing & Design
The new ANSI Classroom Acoustics Standard S12.60-2002 recommends maximum A-weighted and Cweighted classroom sound levels of 35 dBA and 55 dBC, respectively. The LAUSD currently uses a maximum sound level limit of 45 dBA for classrooms that are served by ducted HVAC systems. The sound levels in many LAUSD classrooms are less than the 45 dBA limit. This report analyzes the 5 basic systems to determine their classroom sound levels, and to determine the most cost-effective sound attenuation measures for reducing the classroom levels. Comparing various systems’ A-weighted sound levels work best where the systems’ sound energy is mostly above 250 hertz. However, since the highest sound levels from most HVAC systems are usually at frequencies of 250 hertz or less, a rating system that considers the octave bands with center frequencies from 63 to 4000 hertz is more useful for estimating the acceptability of HVAC system designs. The 1957 Noise Criteria (NC) rating system was the first popular system that looked at octave band sound levels, and it is still the most popular among acoustical professionals; and we recommend using it for assessing classroom system designs. Newer rating systems are being tested, and will be recommended in the future if they prove to be more reliable than the NC system. For now, we recommend that the classroom NC ratings not exceed the NC-35 curve, which is equivalent to about 44 dBA, only 1 dBA less than LAUSD’s current 45 dBA sound level limit. We will notify the district in the future when cost-effective attenuation measures are available. As you will see from the calculation results summarized herein, there is not a direct correlation between a sound spectrum’s dBA and NC values. In most cases the dBA value is higher, but a spectrum that has a low frequency octave band that is especially out of balance with the other octave bands can create the rare situation in which the NC value is higher. One feature of a well-balanced spectrum is that its dBA value is 5 to 9 points higher than its NC rating. CALCULATION RESULTS SUMMARY All of the calculations were done using Version 2.3 of the Trane Acoustics Program, which is based on the algorithms published in the 1991 ASHRAE special publication titled “Algorithms for HVAC Acoustics.” In some cases we used our field experience to modify a calculation parameter to obtain a more reliable calculation result. We assumed the following for all calculations: 1. The supply and return air sheet metal duct gauges were assumed to be the lowest cost alternative per the SMACNA Duct Design Guide – 26 gauge for Systems 1, 2 & 3; 24 gauge for the trunk ducts in Systems 4 & 5. 2. The systems delivered 1600 CFM to the classroom, except for the System 5, which used radiant ceiling panels. This system needed only about 640 CFM per classroom. 3. The systems had ducted return air.
LAUSD HVAC Acoustical Study January 31, 2005 Page 3 of 6
Schaffer Acoustics Inc Consulting, Testing & Design
4. All connections to ceiling grilles and diffusers were made with a 5’ length of Casco Silent-Flex II acoustical flex duct. Several other flex duct manufacturers make a similar product that uses a spunbond nylon inner liner. 5. All grilles and diffusers are selected for a catalog Noise Criteria rating of NC-25 or less. 6. All system components that are remote from the classroom (e.g., central plant for the 4-pipe systems and condensing units for the split systems) are installed and treated so that they create insignificant sound exposures in the classrooms. 7. All equipment was mounted on the proper vibration isolators so that structure-borne sound due transmission was not significant. The attached Figures 1 through 8 compare the calculated classroom octave band sound level spectra for each system alternative with the NC-35 octave band Noise Criteria curve, which has an equivalent A-weighted sound level of 44 dBA. Systems 1, 2 & 3 are similar in that each system’s prime air mover is very close to the classroom being served and their ductwork layouts are similar. We have, therefore, summarized the calculation results for these systems in Table 1 below. The table refers to the attached Figures 1 through 6, which show the octave band spectra associated with each calculation. TABLE 1 – Summary of Classroom NC and dBA ratings for Systems 1, 2 & 3 26 gauge ducts
18 gauge ducts
NC
dBA
NC
dBA
Carrier 48HJ rooftop unit
47
46
39
41
1B
Trane Precedent rooftop unit
46
47
36
42
3
2A
Carrier FB4B split system
35
42
35
41
4
2B
Trane Odyssey split system
46
46
42
45
5
3A
Carrier 42BH 4-pipe fan coil unit
49
46
40
42
6
3B
Trane BCHC 4-pipe fan coil unit
52
48
42
43
Figure #
System #
1
1A
2
Equipment
Table 1 includes NC and dBA results for both 26 and 18 gauge ductwork. We included both duct gauges because our initial calculations using 26 gauge sheet metal ductwork showed that the acoustical ratings were controlled by excessive “breakout” sound at the lowest octave bands, and our experience has shown that increasing a duct’s thickness (decreasing its gauge number) is the most economical way to reduce breakout noise.
LAUSD HVAC Acoustical Study January 31, 2005 Page 4 of 6
Schaffer Acoustics Inc Consulting, Testing & Design
The table above shows that the school district’s 45 dBA limit is exceeded for all of the tabulated systems, except the Carrier FB4B split system, if 26 gauge ducts are used. The table also shows that increasing the ductwall thickness to 18 gauge brings all of the systems into compliance with the 45 dBA limit. More noteworthy is the fact that none of the calculation results, except for the Carrier FB4B split system, complies with our suggested NC-35 limit; a close review of Figures 1 through 6 shows that the excesses are comprised of residual 63 and 125 hertz band noise, even with the 18 gauge ductwork. Controlling this residual low frequency noise will require one or more of the following mitigation alternatives: 1. Require that the equipment sound power level (LW) values not exceed certain values (each type of equipment would have its own set of LW value limits). 2. Move the equipment so that it is not directly over a classroom. 3. Insert duct silencers in the supply and return air ductwork. Re the rooftop units (System Type #1) - We considered rooftop equipment from manufacturers other than Carrier and Trane, but we did not carry out a complete system analysis with them because the alternative manufacturers provided estimated acoustical performance rather than measured performance. All of the calculation results in this report are based on measured equipment performance in accordance with ARI Standard 260-2001, which is the only test standard that is accepted for determining the acoustical performance of air handling units, fan coil units and other ducted air-moving equipment. Figures 7 & 8 show the octave band sound spectra for central station variable air volume systems that use Energy Labs and Temtrol air handling units, respectively. The solid curve in each figure shows the acoustical spectrum in the corridor directly beneath the AHU’s large trunk ducts; the acoustical phenomenon here is called “duct breakout noise”. The dot-dashed curve in each figure is the classroom spectrum due to the in-duct noise that is generated by the AHU, the terminal unit and the diffusers & grilles. Table 2 below summarizes the NC and dBA results for these units. TABLE 2 – Summary of NC and dBA Values for Systems 4A & 4B Figure #
System #
7
4A
8
4B
Equipment
Corridor
Classroom
NC
dBA
NC
dBA
Energy Labs AHU
31
37
31
37
Temtrol ITF-RDHRE43 AHU
46
44
31
37
LAUSD HVAC Acoustical Study January 31, 2005 Page 5 of 6
Schaffer Acoustics Inc Consulting, Testing & Design
The calculation results in Table 2 show that the classroom sound level with either system will be much lower than the LAUSD 45 dBA limit, and will even approach the ANSI S12.60 limit of 35 dBA. The classroom noise exposures for both systems are identical because the classroom sound levels are controlled not by the AHU, but by the low pressure air distribution system that serves the room, and this part of the system is identical for the two AHU alternatives that were analyzed. The corridor sound exposures for the Temtrol AHU are higher than those for the Energy Labs AHU because the Energy Labs unit had internal sound traps, which were not included in the Temtrol unit. However, the NC-46 and 44 dBA noise exposures are not considered excessive for a corridor, so thickened duct gauges are not needed for the supply and return air trunk ducts above the corridor. System 5, which uses reduced airflow to each classroom along with radiant cooling panels, will have classroom noise exposures that are very close to the NC-31 and 37 dBA values for the 2 central station systems in Table 2 above if the relevant system design assumptions are followed; that is, the diffusers and grilles are selected for a maximum catalog noise rating of NC-25 and are connected to their ducts with 5’ long sections of a flexible duct that uses a spunbond nylon inner liner. The corridor noise ratings will fall midway between the ratings for the 2 units tabulated in Table 2, even without the internal sound traps, so further mitigation of this noise is not needed for the example of the Temtrol ITF-RDH17 air handling unit. General Comments The calculation results in this report suggest that the systems with remote central station air handling units will yield the quietest classroom sound levels. This is confirmed by our field experience, as well. The results in Table 1 indicate that all of the systems that use a single fan-based unit for each classroom will meet the school district’s 45 dBA sound level limit if 18 gauge supply and return trunk ducts are used. Re our comment on measured versus estimated factory noise data – all of the major equipment manufacturers are continually improving their product lines, so the school district can expect to see quieter equipment in the near future. We’ve also just learned that York has recently begun running acoustical tests on their Sunline rooftop product and will be submitting measured sound power level data for consideration by the district in the very near future. Summary No matter what type of system is used to condition classroom air, the following design steps are important for controlling the classroom noise exposure: 1. Install 4-pipe and DX fan coil units in the ceiling plenums over corridors, work areas, or other non-sensitive rooms. Do not install them over classrooms. 2. Select the air-moving equipment for the lowest possible set of discharge and inlet sound power levels, as measured per the latest revisions of ARI Standard 260. Do not accept sound data obtained from any other test standard or estimation method. It is beyond the scope of this
LAUSD HVAC Acoustical Study January 31, 2005 Page 6 of 6
Schaffer Acoustics Inc Consulting, Testing & Design
report to present specific sound power level limits because they will be different for each type of unit selection and installation, but a general rule of thumb is that larger fans at lower RPM rates are quieter than smaller fans at higher rotation speeds. Also, a unit whose fan is mounted on spring isolators inside of the cabinet will produce less noise than a unit whose fan is either directly bolted to the cabinet or installed with neoprene grommets or bushings. 3. Use 18 gauge sheet metal for all rectangular ducts that run directly over classrooms. A thinner duct gauge is OK for circular ducts. 4. Select classroom diffusers and grilles for a catalog sound rating of NC-25 or less. 5. Use a 5-foot long section of Casco SilentFlex II or Toro-Aire Toroflex flex ductwork to connect each diffuser and grille to its sheet metal ductwork. 6. Install all diffuser and grille balancing dampers at the metal/flex interface, not at the connection of the flex duct to the diffuser or grille collar. At your request we will provide the summary and detailed calculations sheets that we used to develop the octave band spectra that are shown in Figures 1 through 8. Please call if you have any questions. Yours truly, Schaffer Acoustics Inc
Mark E. Schaffer, P. E. President MES:bh Encl.
DUCTFREE SPLIT SYSTEM HEAT PUMPS AS ALTERNATIVE HVAC SYSTEMS FOR THE WALL MOUNTED HEAT PUMPS IN EXISTING CLASSROOMS Prepared for the
Los Angeles Unified School District August 18, 2005
by
Maroko & Shwe, Inc., Professional Engineers
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
1
Contents Executive Summary
3
Unit Sizing & Possible Sound Level
8
Description and Characteristics of Duct Free Split Systems System 1 - High wall
9
System 2 - Ceiling Suspended
11
System 3 - Console
13
System 4 - In Ceiling Cassette
15
Environment Impact
15
Recent Developments
15
Typical Installation Drawings (Utah School) Acoustical Consultant’s Report Air Balance Report Load Calculations (Utah School) Catalog Data
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
2
EXECUTIVE SUMMARY This study was initiated to explore the feasibility of the various types of “Duct-free Split System Heat Pumps” as an alternative for classroom air conditioning for existing schools in lieu of the wall mounted heat pumps that are currently used. The background sound levels generated by each type of system, the energy efficiency, indoor air quality that could be maintained and the easiness of installation and maintenance are studied. The methodology used was to: (1) Define each system clearly with comparative equity, so that costs, energy use, and acoustic performance could be calculated: (2) Calculate the cooling loads using the Trane Company’s TRACE 700 simulation program; The calculations will be performed multiple times using different design temperatures as follows: a. ASHRAE 0.5% outdoor and 75°F indoor design temperatures b. ASHRAE 0.5% outdoor and 78°F indoor design temperatures c. ASHRAE 2.0% outdoor and 75°F indoor design temperatures d. ASHRAE 2.0% outdoor and 78°F indoor design temperatures The HVAC equipment is selected based on the results of each of the above calculations. (3) Summarize the acoustical performance and classroom sound levels for each equipment selection. (4) Summarize the findings including the energy efficiency of the equipment and also other considerations such as outdoor air capability, air filters and easiness of installation so that an informed management decision could be made; The major determining factor for the feasibility of these systems is unit sizing as only limited unit sizes are available at lower sound levels. We applied the following reasoning in sizing the units: 1. A typical LAUSD school day concludes at 3:00 pm daylight saving time (2:00 pm sun time) during the summer months when cooling is required. 2. Outdoor temperatures peak at 1:00 pm sun time or 2:00 pm daylight saving time. Due to the time delay effect of the building mass, the cooling loads in an average building, that has a mass of 70 lb/sq. ft will peak a minimum of two hours after the outdoor temperature peaks at 3:00 pm sun time or 4:00 pm daylight savings time. Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
3
3. Because the classrooms are not typically occupied when the cooling loads peak, it is justifiable to use the Building Cool Heat Demand Tables calculated with the Trace 700 software (See the load calculations section of this report) to size the units using the ASHRAE 0.5% Design Temperatures. The units should be sized for the highest load during the occupied period. 4. If the Trace 700 software is not available, calculating the cooling loads with ASHRAE 2.0% outdoor design temperatures to size the units will produce very close results and is justifiable.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
4
Conclusions We could make the following conclusions: (1)
The smallest possible equipment selection for a classroom with outdoor air load is 3 Tons when the cooling loads are calculated with ASHRAE 2.0% outdoor and 78°F indoor design temperatures.
(2)
The smallest possible equipment selection for a classroom without outdoor air load is 2.5 Tons when the cooling loads are calculated with ASHRAE 2.0% outdoor and 78°F indoor design temperatures. Applications of this type will require a dedicated outdoor air system.
(3)
The lowest possible sound level with duct free systems is 45 dBA with a 2.5 or 3 Ton Mitsubishi ceiling suspended unit operating at low speed. At high speed the sound level increases to 51 dBA.
(4)
The biggest disadvantage of these systems is the limited outdoor air capability. a.
The high wall systems are not provided with any outdoor air connections. An existing central heating and ventilating system could be modified to a dedicated outdoor air system to provide filtered outdoor air. Cooling coils could be added to this existing central heating and ventilating unit to temper the outdoor air and reduce the capacity of the classroom unit. The classroom unit fans could then be cycled with load demand to reduce energy use.
b.
The ceiling suspended and in ceiling systems are provided with outdoor air connections but out door air booster fans are required in some cases and the air capacity is limited in some cases to a much lower level than classroom requirements. For instance, a 3 Ton in-ceiling system is limited to 250 cfm outdoor air by one manufacturer and requires a booster fan that could be as noisy as 3 Sones or 45 dBA.
c.
The console and exposed ceiling cabinet systems could not accommodate the required outdoor air requirements except for one manufacturer.
(5)
The high wall, under ceiling and in-ceiling systems can only accommodate cleanable filters of very low efficiency.
(6)
These systems cannot accommodate 100% outdoor-air economizer operation and are also too small for to benefit from economizers.
(7)
The level of difficulty to service is also considerably higher. The indoor sections have to be practically totally dissembled for service.
(8)
Due to the above limitations, further investigation could only be done through actual field installation to determine whether the outdoor air limitation could be overcome through innovation.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
5
Test Installations Two classrooms at Utah Elementary School are selected for test installations. The high wall and the under ceiling systems are selected for installation because they could be installed with minimum invasiveness into existing construction and they could be provided with outdoor air through the following two different means. The high wall will be provided with a dedicated outdoor air fan with an air filter and the under ceiling system will be studied with just the nominal outdoor air intake without a booster fan. Calculations and Drawings for the installation of the above systems are included later in this report. Test Results The ceiling suspended unit is better than the high wall unit in the following areas: 1. Easier to install 2. Easier to maintain (M & O HVAC personnel opinion after reviewing the installation) 3. Has outdoor air capability 4. Quieter The following measurements are reported by the Air Balancing Agency: Sound High Wall Unit @ high speed 3’-0” from unit
51.3 dBA
Ceiling Suspended Unit @ high speed 3’-0” from unit
48.9 dBA
Bard Wall Mount unit in adjacent room 3’-0” from unit
51.6 dBA
The following measurements are reported by the Delta H Design: Sound High Wall Unit @ high speed 10’-0” from unit
51.2 dBA
Ceiling Suspended Unit @ high speed 10’-0” from unit
50.2 dBA
Bard Wall Mount unit before replacement 10’-0” from unit
52.5 dBA
The above reports are attached.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
6
We have not received the sound measurements per ANSI Standards at all the fan speed settings (high, medium and low) as yet. Outdoor Air Required per code:
350 cfm
Ceiling suspended unit:
120 cfm
High Wall Unit:
0
cfm through unit
260 cfm (from a separate window mounted fan outside of unit) The outdoor air capability of the ceiling suspended unit could be increased if the intake opening size is increased by the manufacturer. The scheme to supply outdoor air directly into the room with a wall mounted fan for the high wall system is not very satisfactory. The wall fan air flow performance is not very reliable and decreases very rapidly with filter loading. The effect of the un-tempered outdoor air in cold weather is still unpredictable. The wall fan noise is also considerable at about 51 dBA. Further conclusions based on the test results We are of the opinion that the additional cost incurred does not justify the 2 dBA sound reduction realized. The following additional disadvantages are also apparent: 1. Limited outdoor air capability. 2. Filters of very low efficiency. 3. Higher level of service difficulty. 4. The ductless units are limited to single phase electrical power.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
7
Unit Sizing All the calculations were done for the three locations with different climatic conditions within the district: 1. Los Angeles Area (City Office) 2. Coastal Area (Santa Monica) 3. Valley Area (San Fernando)
Unit Sizing Comparison Location
Thermostat Setting
1
Los Angeles (Convention Center)
2
Coastal (Santa Monica)
3
Valley (San Fernando)
75°F 78°F 75°F 78°F 75°F 78°F
Unit Size (Ton) Weather Data 0.50% 2.00% 4 4 3 3 3 3 3 2 5 4 4 4
Possible Sound Level Manufacturer 1
High Wall
Ceiling Suspended
Console
In Ceiling
3 Ton
48
55low speed
na
43 med speed
4 Ton
NA
58 med speed
na
na
3 Ton
41
45
na
45
4 Ton
na
na
na
na
3 Ton
54 low speed
63
61
45 low speed
4 Ton
na
64
63
48 low speed
3 Ton
46 low speed
45low speed
na
37 low speed
4 Ton
na
45low speed
na
37 low speed
Carrier
2
Fujitsu
3
EMI
4
Unit Size
Mitsubishi
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
8
System 1: High Wall Type
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
9
High Wall Split Heat Pump Unit Mitsubishi PKH Indoor w/PUH outdoor Energy Efficiency
9.8 EER/10.3 SEER
Air Filter
Cleanable
Lowest Possible Sound Level
46 dBA low speed
Maintenance
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
10
System 2: Ceiling Suspended Type
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
11
Ceiling Suspended Split Heat Pump Unit Mitsubishi PCH Indoor w/PUH outdoor Energy Efficiency
9.9 EER/10.5 SEER
Air Filter
Cleanable
Lowest Possible Sound Level
45 dBA low speed
Maintenance
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
12
System 3: Console Type
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
13
Console Split Heat Pump Unit EMI FHP Indoor w/SHC outdoor Energy Efficiency
9.0 EER/10.0 SEER
Air Filter
Cleanable
Lowest Possible Sound Level
61 dBA
Maintenance Similar to ceiling suspended unit.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
14
System 4: In Ceiling Cassette Type
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
15
In Ceiling Cassettes Split Heat Pump Unit Mitsubishi PLGH Indoor w/PUGH outdoor Energy Efficiency
9.5 EER/10.0 SEER
Air Filter
Cleanable
Lowest Possible Sound Level
37 dBA low speed
Maintenance
Environmental impact The current refrigerant, R–22 will be phased out in 2020. Units with environmentally friendly (non-CFC/HCFC) refrigerants are available from a few manufacturers but they are not recommended as yet because the refrigerants are reported to be unstable mixtures and the required lubricants are so extremely hygroscopic that extra drying of the entire system is required before charging. We should wait until industry standards are more stable. Recent Developments Duct free units with air cooled mini-chillers of 5 tons capacity or less have become available recently and their acoustical performances are within acceptable range. { 42~48 dBA high wall and 42~48 dBA for universal mounted, (interchangeable between console or ceiling suspended) indoor units}.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345 MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
16
July 29, 2005 ROSEMARIE DE OCAMPO C/O LAUSD UTAH ELEMENTARY SCHOOL 255 GABRIEL GARCIA MARQUEZ ST. LA, CA 90033 213-633-7407 DEAR ROSEMARIE. THANK YOU FOR REQUESTING FOR ACOUSTICAL TESTING FROM DELTA H DESIGN. WE ARE PLEASED AND HONORED TO BE WORKING WITH THE LAUSD TO HELP PROVIDE A BETTER ENVIRONMENT FOR THE CHILDREN OF LOS ANGELES IN WHICH TO FURTHER THEIR EDUCATION. THIS REPORT WAS CONTRACTED TO DETERMINE THE HVAC NOISE LEVELS OF TWO CLASSROOMS AT THE LAUSD UTAH ELEMENTARY SCHOOL LOCATED AT 255 GABRIEL GARCIA MARQUEZ ST., LA, CA 90033. THE SCHOOL’S INTENTION WAS TO DECREASE THE NOISE LEVELS BY REPLACING THE HVAC UNITS WITH QUIETER UNITS. THIS REPORT SERVES AS A BEFORE AND AFTER MEASUREMENT OF CLASSROOMS NUMBER 43 AND 44. THE HVAC UNITS INSTALLED BETWEEN JUNE 28TH AND JULY 27TH WERE BOTH MADE BY MITSUBISHI. CLASSROOM 43 RECEIVED A HIGH WALL SPLIT SYSTEM. CLASSROOM 44 RECEIVED A CEILING MOUNTED SPLIT SYSTEM. MEASUREMENTS TAKEN BEFORE THE REPLACEMENT OF HVAC UNITS: ON JUNE 28TH, 2005 MEASUREMENTS OF CLASSROOMS 43 AND 44 WERE TAKEN FROM 10:00AM TO 11:30 AM WITH IDENTICAL SITUATIONS. THE EXTERNAL AMBIENT NOISE LEVEL WAS EQUIVALENT, ALL THE DOORS AND WINDOWS WERE CLOSED TO ISOLATE THE INTERNAL ENVIRNONMENT FROM THE EXTERNAL NOISE, THERE WAS AN ELECTRIC CLOCK AND FLOURESCENT LIGHTS WITH NON-ELECTRONIC BALLASTS, AND THE HVAC UNITS WERE ENGAGED AND SET TO 65 DEGREES IN ORDER TO INSURE MAXIMUM COMPRESSOR ACTIVITY DURING THE MEASUREMENT. MEASUREMENTS WERE TAKEN AT A DISTANCE OF 10 FEET IN ORDER TO ALLOW FOR THE DISPERSION PATTERN OF THE NOISE GENERATED BY THE HVAC UNIT TO BECOME HOMOGENEOUS FOR ACCURATE MEASUREMENT. ALL TESTING WAS PERFORMED WITH A CALIBRATED MICROPHONE AND SOUND PRESSURE LEVEL METER. -CLASSROOM 43: -52.5 DB SPL [A WEIGHTED] -67.6 DB SPL [UNWEIGHTED] -CLASSROOM 44 -52.2 DB SPL [A WEIGHTED]. -72.7 DB SPL [UNWEIGHTED]
UtahAccousticalReport_Rosemarie.doc8/18/05 7:18 PM
Gas Loft -∆H
Utah Elementary Acoustical Report Page 2.0
July 29, 2005
MEASUREMENTS TAKEN AFTER THE REPLACEMENT OF HVAC UNITS: ON JULY 27TH, 2005 MEASUREMENTS OF CLASSROOMS 43 AND 44 WERE TAKEN AGAIN FROM 10:00 AM TO 12 :00 PM WITH THE EXACT SAME CONDITION SAVE THE FOLLOWING: -THE CHILDREN WERE AT RECESS DURING THE MEASUREMENTS, WHICH CREATED AN UNUSUALLY HIGH LEVEL OF AMBIENT NOISE EXTERNAL TO THE AREA BEING MEASURED. MEASUREMENTS WERE TAKEN AT A DISTANCE OF 10 FEET IN ORDER TO ALLOW FOR THE DISPERSION PATTERN OF THE NOISE GENERATED BY THE HVAC UNIT TO BECOME HOMOGENEOUS FOR ACCURATE MEASUREMENT. ALL TESTING WAS PERFORMED WITH A CALIBRATED MICROPHONE AND SOUND PRESSURE LEVEL METER. -CLASSROOM 43: -51.2 DB SPL [A WEIGHTED] -65.6 DB SPL [UNWEIGHTED] -CLASSROOM 44: -50.2 DB SPL [A WEIGHTED] -70.4 DB SPL [UNWEIGHTED] CHANGE IN AMBIENT NOISE LEVELS: (BETWEEN BEFORE AND AFTER) -CLASSROOM 43: -A WEIGHTED: -UNWEIGHTED:
1,3 DB SPL 2.0 DB SPL
-CLASSROOM 44: -A WEIGHTED: -UNWEIGHTED:
2.0 DB SPL 2.3 DB SPL
CONCLUSIONS + DETERMINATIONS The changes in ambient noise levels in both classrooms were insignificant for both the weighted and unweighted measurements. Granted, the unweighted changes were greater, but as the unweighted unit measures a wider range of sound energy that is to be expected. It is clear by extrapolating from the data that the new HVAC units installed are probably generating noise levels of between 40 – 50 dB spl A weighted if measured in an anechoic environment. Unfortunately, given the environment, these tests are not truly a measure of the HVAC units but rather a measure of the acoustic environment. There are several mitigating factors in the acoustical envelope that cumulatively add to the ambient noise levels. This raises the ambient noise levels to a point, which masks the noise generated by the HVAC units. The acoustic envelope itself is not sealed nor controlled. In order to decrease the ambient noise levels in these classrooms to a degree where the HVAC units would become the loudest element in the room the basic acoustic issues of sound and vibration isolation would have to be addressed first.
UtahAccousticalReport_Rosemarie.doc8/18/05 7:18 PM
Gas Loft -∆H
Utah Elementary Acoustical Report Page 3.0
July 29, 2005
Specific areas to treat would be the following: -Doors -Windows -Wall Fans -Electric-Mechanical Devices (Clocks) -Electrical lighting devices (Fluorescent lighting) Summary: Without repeating the ANSI testing already performed by the HVAC manufacturers it can be extrapolated from the testing data that the noise generated by said units is within the 40 – 50 dB spl A weighted range. The ambient noise levels in classrooms 43 and 44 are largely due to factors besides the HVAC units. (See above: top of page 3.0) In order to decrease the ambient noise levels the acoustic envelope must be treated. (See conclusions + Determinations: Specific areas to treat….) It is possible to treat all of the specific areas of the acoustic envelope. Please contact us to discuss creating a report to address these issues.
Thank you.
Sincerely,
Hanson Hsu Principal/Owner
UtahAccousticalReport_Rosemarie.doc8/18/05 7:18 PM
Gas Loft -∆H
Ceiling Suspended Unit
2
2
Background sound Level. Includes Heating Fan Energy 3 Excludes Fan Energy
1
Wall Mounted Unit
1
System Description
Mitsubishi PKH36FK Indoor w/ PUH36EK Outdoor Mitsubishi PCH36GK Indoor w/ PUH36EK Outdoor
Manufacturer
3,090.1
45low speed
$
463.52
407.88
Cooling
2,719.2
kWh
2
4.3
4.9
kWh
3
Heating
0.65
0.74
$
Annual Energy Usage per Classroom
46low speed
Possible Acoustical Performance dBA
1
(UTAH ELEMENTARY SCHOOL PROTOTYPE INSTALLATION)
HVAC ENERGY COMPARISON
31,830
Grand Total ==>
35,153
0 2,054 0 -551 100 0 0 0
3,612 8,125 1,781 13,519
0 0 1,201 15,216 1,123 98 0 0 2,396 20,032
100.00
0.00 5.84 0.00 -1.57 0.28 0.00 0.00 0.00
10.28 23.11 5.07 38.46
0.00 0.00 3.42 43.28 3.19 0.28 0.00 0.00 6.81 56.99
59.0 0.0 0.0
69.9 0.0 0.0
Utah Elementary School W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah School.TRC
62.6 0.0 0.0
Project Name: Dataset Name:
65.5 72.2 0.0 0.0 0.0 0.0
35.2
80.1 0.0 0.0
2.9
1,680 0 0
Leave DB/WB/HR °F °F gr/lb Floor Part ExFlr Roof Wall
100.00 Grand Total ==>
Total
32.4 0.0 0.0
0 0 0 0
Internal Loads Lights People Misc Sub Total ==>
864 0 0 864 600
Gross Total
AREAS
-6,638
-173 0 0
0 0 0 0 -4,892 -1,573 0 0 0 -6,465
Space Peak Space Sens Btu/h
0 153
Cooling Heating 300 300 350 0 1,680 1,680 0 0 2,030 1,680 650 300 0 0 0 0
% OA cfm/ft² cfm/ton ft²/ton Btu/hr·ft² No. People
Humidif Opt Vent Total
Main Htg Aux Htg Preheat
0.0 0.0 -17.9
-17.9 0.0 0.0
0 0
1,680 0 0
0.0 0.0
66.0 0.0 0.0
Capacity Coil Airflow Ent MBh cfm °F
0.0 0.0
75.6 0.0 0.0
Lvg °F
Cooling Heating 17.9 17.9 1.94 1.94 573.41 294.94 40.69 -20.66 20
ENGINEERING CKS
Vent Infil Supply MinStop/Rh Return Exhaust Rm Exh Auxil
AIRFLOWS
Cooling Heating 62.6 75.6 78.8 71.4 78.8 71.4 80.1 66.0 0.0 0.0 0.0 0.0 0.0 0.0
HEATING COIL SELECTION
100.00
0.00 57.43 0.00 -1.17 0.00 0.00 0.00 0.00
0.00 0.00 0.00 0.00
0.00 0.00 6.17 0.00 27.41 10.15 0.00 0.00 0.00 43.74
SADB Plenum Return Ret/OA Fn MtrTD Fn BldTD Fn Frict
TEMPERATURES
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 Room Checksums report Page 1 of 1
0 26
Glass ft² (%)
-17,848
0 -10,251 0 209 0 0 0 0
0 0 0 0
0 0 -1,102 0 -4,892 -1,812 0 0 0 -7,806
Coil Peak Percent Tot Sens Of Total Btu/h (%)
Mo/Hr: 13 / 1 OADB: 41
HEATING COIL PEAK
Envelope Loads Skylite Solar Skylite Cond Roof Cond Glass Solar Glass Cond Wall Cond Partition Exposed Floor Infiltration Sub Total ==>
0.74 Ceiling Load 0.00 Ventilation Load 0.00 Ov/Undr Sizing Exhaust Heat OA Preheat Diff. RA Preheat Diff. Additional Reheat System Plenum Heat
10.13 14.46 6.25 30.84
0.00 0.00 0.00 53.35 3.94 0.31 0.00 0.00 10.82 68.42
35.2 0.0 0.0
Enter DB/WB/HR °F °F gr/lb
28,520
211 0 0
2,890 4,125 1,781 8,796
0 0 0 15,216 1,123 90 0 0 3,086 19,514
2.9 0.0 0.0
Sens Cap. Coil Airflow MBh cfm
COOLING COIL SELECTION
1,169
0 0
-551
-211 0
0 722
722
1,208
0 0 1,201 0 0 8
Space Percent Sensible Of Total Btu/h (%)
Mo/Hr: 9 / 15 OADB: 86
CLG SPACE PEAK
Main Clg Aux Clg Opt Vent
Total Capacity ton MBh
211 0 0
2,890 8,125 1,781 12,796
Internal Loads Lights People Misc Sub Total ==>
Ceiling Load Ventilation Load Ov/Undr Sizing Exhaust Heat Sup. Fan Heat Ret. Fan Heat Duct Heat Pkup Reheat at Design
0 0 0 15,216 1,123 90 0 0 2,396 18,824
Envelope Loads Skylite Solar Skylite Cond Roof Cond Glass Solar Glass Cond Wall Cond Partition Exposed Floor Infiltration Sub Total ==>
Net Percent Total Of Total Btu/h (%)
Mo/Hr: 9 / 15 OADB/WB/HR: 86 / 67 / 70
Space Plenum Sens. + Lat. Sens. + Lat Btu/h Btu/h
Peaked at Time: Outside Air:
COOLING COIL PEAK
Classroom 43
By Maroko & Shwe
Room Checksums
30,009
Grand Total ==>
33,444
0 2,054 0 -384 93 0 0 0
3,612 8,125 1,781 13,519
0 0 1,195 15,216 1,123 96 0 0 532 18,162
100.00
0.00 6.14 0.00 -1.15 0.28 0.00 0.00 0.00
10.80 24.29 5.33 40.42
0.00 0.00 3.57 45.50 3.36 0.29 0.00 0.00 1.59 54.31
58.9 0.0 0.0
69.7 0.0 0.0
Utah Elementary School W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah School.TRC
62.5 0.0 0.0
Project Name: Dataset Name:
65.6 72.1 0.0 0.0 0.0 0.0
33.4
80.3 0.0 0.0
2.8
1,569 0 0
Leave DB/WB/HR °F °F gr/lb Floor Part ExFlr Roof Wall
100.00 Grand Total ==>
Total
30.2 0.0 0.0
0 0 0 0
Internal Loads Lights People Misc Sub Total ==>
864 0 0 864 600
Gross Total
AREAS
-6,648
-183 0 0
0 0 0 0 -4,892 -1,573 0 0 0 -6,465
Space Peak Space Sens Btu/h
0 153
Cooling Heating 300 300 78 0 1,569 1,569 0 0 1,647 1,569 378 300 0 0 0 0
% OA cfm/ft² cfm/ton ft²/ton Btu/hr·ft² No. People
Humidif Opt Vent Total
Main Htg Aux Htg Preheat
0.0 0.0 -17.8
-17.8 0.0 0.0
0 0
1,569 0 0
0.0 0.0
65.5 0.0 0.0
Capacity Coil Airflow Ent MBh cfm °F
0.0 0.0
75.8 0.0 0.0
Lvg °F
Cooling Heating 19.1 19.1 1.82 1.82 562.99 310.01 38.71 -20.64 20
ENGINEERING CKS
Vent Infil Supply MinStop/Rh Return Exhaust Rm Exh Auxil
AIRFLOWS
Cooling Heating 62.6 75.8 78.9 71.3 78.9 71.3 80.3 65.5 0.0 0.0 0.0 0.0 0.0 0.0
HEATING COIL SELECTION
100.00
0.00 57.48 0.00 -1.24 0.00 0.00 0.00 0.00
0.00 0.00 0.00 0.00
0.00 0.00 6.17 0.00 27.43 10.16 0.00 0.00 0.00 43.76
SADB Plenum Return Ret/OA Fn MtrTD Fn BldTD Fn Frict
TEMPERATURES
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 2 Room Checksums report Page 1 of 1
0 26
Glass ft² (%)
-17,834
0 -10,251 0 221 0 0 0 0
0 0 0 0
0 0 -1,101 0 -4,892 -1,811 0 0 0 -7,804
Coil Peak Percent Tot Sens Of Total Btu/h (%)
Mo/Hr: 13 / 1 OADB: 41
HEATING COIL PEAK
Envelope Loads Skylite Solar Skylite Cond Roof Cond Glass Solar Glass Cond Wall Cond Partition Exposed Floor Infiltration Sub Total ==>
0.99 Ceiling Load 0.00 Ventilation Load 0.00 Ov/Undr Sizing Exhaust Heat OA Preheat Diff. RA Preheat Diff. Additional Reheat System Plenum Heat
10.84 15.47 6.68 32.98
0.00 0.00 0.00 63.30 1.82 -0.35 0.00 0.00 1.25 66.03
33.4 0.0 0.0
Enter DB/WB/HR °F °F gr/lb
26,669
264 0 0
2,890 4,125 1,781 8,796
0 0 0 16,882 486 -92 0 0 334 17,609
2.8 0.0 0.0
Sens Cap. Coil Airflow MBh cfm
COOLING COIL SELECTION
1,288
0 0
-384
-252 0
0 722
722
1,202
0 0 1,195 0 0 7
Space Percent Sensible Of Total Btu/h (%)
Mo/Hr: 10 / 15 OADB: 82
CLG SPACE PEAK
Main Clg Aux Clg Opt Vent
Total Capacity ton MBh
252 0 0
2,890 8,125 1,781 12,796
Internal Loads Lights People Misc Sub Total ==>
Ceiling Load Ventilation Load Ov/Undr Sizing Exhaust Heat Sup. Fan Heat Ret. Fan Heat Duct Heat Pkup Reheat at Design
0 0 0 15,216 1,123 90 0 0 532 16,961
Envelope Loads Skylite Solar Skylite Cond Roof Cond Glass Solar Glass Cond Wall Cond Partition Exposed Floor Infiltration Sub Total ==>
Net Percent Total Of Total Btu/h (%)
Mo/Hr: 9 / 15 OADB/WB/HR: 86 / 67 / 70
Space Plenum Sens. + Lat. Sens. + Lat Btu/h Btu/h
Peaked at Time: Outside Air:
COOLING COIL PEAK
Classroom 44
By Maroko & Shwe
Room Checksums
3. Tuesday
4. Wednesday
2. Monday
5. Thursday
8
85-80 3,007
80-75 5,483
7. Saturday
90-85 149
70-65 0
8. Sunday
75-70 121
60-55 0
< 50° 0
10. Weekday
55-50 0
1
7
11. Weekend
70
1
----- Minimum ----Temp Mo Hr Day
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Temp Profiles Report Page 1 of 1
9. Holiday
65-60 0
--- Number of Hours at each Temp Range (°F) --95-90 0
6. Friday
>100° 100-95 0 0
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah School.TRC
19
Daytypes 1. Design
9
87
---- Maximum---Temp Mo Hr Day
Classroom 43
Room Description
By Maroko & Shwe
SYSTEM TEMPERATURE PROFILES
47.1 46.1 45.5 44.9 43.9 43.5 43.5 43.5 44.9 46.8 48.3 49.9 51.6 53.1 53.7 53.1 52.8 52.3 51.9 51.5 50.5 48.7 48.3 47.9
53.0 53.0 53.0 52.0 51.0 51.0 51.0 51.0 53.0 58.0 60.0 62.0 64.0 67.0 67.0 65.0 64.0 63.0 62.0 61.0 60.0 58.0 56.0 55.0
47.8 43.3 43.0 42.4 41.7 41.2 41.2 41.2 42.2 49.4 50.6 52.0 53.2 54.9 55.1 54.5 54.5 54.2 54.1 53.7 53.2 52.5 51.3 50.4
Typical Weather (°F) OADB OAWB
52.0 52.0 51.0 51.0 50.0 49.0 49.0 49.0 52.0 56.0 58.0 60.0 62.0 64.0 65.0 64.0 63.0 62.0 61.0 60.0 58.0 54.0 54.0 53.0
Typical Weather (°F) OADB OAWB 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.3 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.6 0.8 0.7 1.7 1.9 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Design Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 -11,058 -11,064 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Design Htg (Btuh) Clg (Tons) 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.1 0.3 0.1 0.8 1.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.6 0.0 0.1 0.2 0.3 0.2 0.9 1.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Weekday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 -1,296 -1,890 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Weekday Htg (Btuh) Clg (Tons)
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah Scho
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
February Hour
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
January Hour 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Saturday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Saturday Htg (Btuh) Clg (Tons)
By Maroko & Shwe
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.7 1.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.2 0.9 1.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Monday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Monday Htg (Btuh) Clg (Tons)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Load Profiles report Page 1 of 6
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
BUILDING COOL HEAT DEMAND
50.5 49.9 49.2 48.8 47.8 47.0 46.2 46.6 47.0 49.7 51.2 52.7 53.8 55.5 55.0 55.5 55.2 55.0 54.9 54.4 54.2 54.0 52.8 51.8
58.0 57.0 56.0 55.0 54.0 54.0 55.0 58.0 60.0 64.0 68.0 70.0 71.0 71.0 70.0 69.0 68.0 66.0 65.0 64.0 62.0 61.0 60.0 59.0
54.0 53.2 52.0 51.3 50.3 50.2 50.2 52.0 53.0 54.6 56.6 57.5 58.6 59.0 59.0 68.6 68.1 57.6 57.3 57.0 56.2 56.0 55.4 55.0
Typical Weather (°F) OADB OAWB
54.0 53.0 53.0 52.0 51.0 51.0 51.0 52.0 53.0 59.0 61.0 63.0 65.0 68.0 66.0 66.0 65.0 64.0 63.0 62.0 61.0 59.0 57.0 55.0
Typical Weather (°F) OADB OAWB 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.4 0.7 0.8 0.7 1.6 1.8 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.6 0.5 0.7 0.9 0.9 0.7 1.4 1.7 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Design Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 -160 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Design Htg (Btuh) Clg (Tons) 0.0 0.0 0.0 0.0 0.0 0.0 0.0 1.3 0.0 0.4 0.3 0.4 0.3 1.1 1.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.3 0.1 0.4 0.7 0.7 0.4 1.1 1.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Weekday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Weekday Htg (Btuh) Clg (Tons)
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah Scho
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
April Hour
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
March Hour 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Saturday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Saturday Htg (Btuh) Clg (Tons)
By Maroko & Shwe
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.4 0.3 0.4 0.3 1.1 1.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.7 0.2 0.4 0.7 0.7 0.4 1.1 1.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Monday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Monday Htg (Btuh) Clg (Tons)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Load Profiles report Page 2 of 6
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
BUILDING COOL HEAT DEMAND
52.9 50.8 49.9 48.7 48.4 48.4 49.0 49.6 52.0 53.8 54.7 55.3 55.8 55.9 55.7 55.3 55.2 55.7 55.6 56.1 55.7 55.8 54.8 54.0
60.1 59.1 58.1 57.1 56.1 56.1 57.1 60.1 62.1 66.1 70.1 72.1 73.1 73.1 72.1 70.1 69.1 68.1 66.1 65.1 64.1 63.1 62.1 61.1
55.1 54.3 53.7 53.0 52.1 51.8 52.1 53.5 54.5 56.1 57.8 58.8 59.3 59.4 59.2 58.6 58.3 58.1 57.4 57.3 57.2 57.0 56.5 55.8
Typical Weather (°F) OADB OAWB
59.1 56.1 55.1 53.1 53.1 53.1 54.1 55.1 60.1 64.1 66.1 67.1 68.1 68.1 67.1 66.1 65.1 65.1 64.1 64.1 62.1 62.1 60.1 60.1
Typical Weather (°F) OADB OAWB 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.2 0.3 1.0 1.2 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.1 0.7 1.3 1.6 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Design Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Design Htg (Btuh) Clg (Tons) 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.2 0.4 0.1 0.5 0.6 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.3 0.2 0.2 0.3 0.4 0.5 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Weekday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Weekday Htg (Btuh) Clg (Tons)
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah Scho
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
June Hour
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
May Hour 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Saturday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Saturday Htg (Btuh) Clg (Tons)
By Maroko & Shwe
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.1 0.6 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.2 0.4 0.5 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Monday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Monday Htg (Btuh) Clg (Tons)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Load Profiles report Page 3 of 6
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
BUILDING COOL HEAT DEMAND
56.8 56.3 56.2 55.8 55.6 55.8 55.9 56.5 58.3 60.0 61.5 62.3 62.8 62.6 62.0 61.4 61.2 60.8 60.2 58.8 58.1 58.3 57.6 57.0
63.1 62.1 62.1 61.1 61.1 61.1 64.1 66.1 70.1 74.1 76.1 78.1 79.1 79.1 78.1 76.1 75.1 74.1 72.1 68.1 66.1 65.1 64.1 63.1
58.0 57.5 57.2 56.6 56.4 56.4 57.7 58.5 60.1 61.5 62.5 63.3 63.8 64.0 63.8 63.2 62.8 62.5 61.8 60.4 59.6 59.3 58.8 58.0
Typical Weather (°F) OADB OAWB
62.1 61.1 61.1 60.1 60.1 61.1 62.1 64.1 68.1 72.1 76.1 78.1 79.1 78.1 76.1 74.1 73.1 72.1 70.1 66.1 64.1 64.1 63.1 62.1
Typical Weather (°F) OADB OAWB 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 1.0 1.4 1.1 1.6 2.1 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.6 1.4 1.5 1.3 2.0 2.5 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Design Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Design Htg (Btuh) Clg (Tons) 0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.4 0.4 0.4 0.5 0.6 0.6 0.7 0.8 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.5 0.6 0.4 0.6 0.7 0.8 1.0 1.2 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Weekday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Weekday Htg (Btuh) Clg (Tons)
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah Scho
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
August Hour
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
July Hour 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Saturday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Saturday Htg (Btuh) Clg (Tons)
By Maroko & Shwe
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.4 0.4 0.4 0.5 0.6 0.6 0.7 0.8 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.7 1.7 0.4 0.6 0.7 0.8 1.0 1.2 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Monday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Monday Htg (Btuh) Clg (Tons)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Load Profiles report Page 4 of 6
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
BUILDING COOL HEAT DEMAND
56.8 55.7 55.0 54.3 54.2 54.1 55.2 57.0 58.9 60.7 62.4 63.0 63.6 63.8 63.4 62.9 62.6 62.1 61.4 59.9 59.0 58.6 58.1 57.2
62.0 61.0 61.0 60.0 60.0 59.0 59.0 62.0 66.0 70.0 72.0 74.0 76.0 76.0 74.0 72.0 70.0 68.0 66.0 66.0 64.0 64.0 64.0 63.0
57.3 56.5 56.3 55.4 55.0 54.6 54.6 56.0 57.8 59.8 60.5 61.2 62.1 62.3 62.0 61.3 60.7 60.0 59.3 59.3 58.5 58.5 58.4 58.0
Typical Weather (°F) OADB OAWB
62.0 61.0 61.0 60.0 60.0 60.0 62.0 66.0 70.0 74.0 78.0 79.0 80.0 80.0 78.0 76.0 75.0 74.0 72.0 68.0 66.0 65.0 64.0 62.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.5 1.2 1.5 1.5 2.4 2.9 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 1.6 0.4 0.7 1.1 1.4 1.3 2.2 2.6 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Design Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Design Htg (Btuh) Clg (Tons) 0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.1 0.4 0.8 1.1 1.3 1.1 1.9 1.9 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.9 0.5 0.5 0.9 1.1 0.9 1.6 1.8 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Weekday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Weekday Htg (Btuh) Clg (Tons)
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah Scho
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
October Hour
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
September Typical Weather (°F) Hour OADB OAWB 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Saturday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Saturday Htg (Btuh) Clg (Tons)
By Maroko & Shwe
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.8 2.5 1.9 1.1 1.3 1.1 1.9 1.9 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 2.9 2.4 1.6 0.9 1.1 0.9 1.6 1.8 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Monday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Monday Htg (Btuh) Clg (Tons)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Load Profiles report Page 5 of 6
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
BUILDING COOL HEAT DEMAND
50.5 49.8 49.1 48.1 47.6 47.1 46.9 48.0 49.8 52.0 54.4 55.5 56.6 58.4 58.2 58.0 57.3 56.5 55.3 54.2 53.8 52.5 52.2 51.0
54.0 54.0 53.0 53.0 52.0 51.0 50.0 54.0 58.0 62.0 66.0 67.0 68.0 68.0 68.0 66.0 64.0 62.0 60.0 59.0 58.0 57.0 56.0 56.0
48.3 47.6 46.7 46.5 46.0 45.0 44.4 46.5 47.7 50.7 52.8 53.5 54.4 54.8 55.5 55.7 54.0 53.1 52.4 51.4 50.9 50.0 49.7 49.5
Typical Weather (°F) OADB OAWB
58.0 57.0 56.0 55.0 54.0 54.0 54.0 56.0 60.0 64.0 68.0 69.0 70.0 72.0 71.0 70.0 68.0 66.0 64.0 62.0 62.0 60.0 60.0 58.0
Typical Weather (°F) OADB OAWB 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.8 0.1 0.4 0.9 1.2 1.1 2.1 2.3 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.6 1.0 0.9 1.8 2.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Design Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Design Htg (Btuh) Clg (Tons) 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.4 0.0 0.5 0.6 0.7 0.6 1.3 1.4 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.5 0.6 0.4 1.1 1.2 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Weekday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Weekday Htg (Btuh) Clg (Tons)
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah Scho
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
December Hour
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
November Hour 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Saturday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Saturday Htg (Btuh) Clg (Tons)
By Maroko & Shwe
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.7 0.0 0.5 0.6 0.7 0.6 1.3 1.4 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.5 0.4 1.1 1.2 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0 0.0
Monday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Monday Htg (Btuh) Clg (Tons)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 System Load Profiles report Page 6 of 6
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0
Sunday Htg (Btuh) Clg (Tons)
BUILDING COOL HEAT DEMAND
4,870.4
915.4
2,151.2
166.0
166.0
169.7 1,633.0
1,307.7 155.6
4.9
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah School.TRC
* Note: Resource Utilization factors are included in the Total Source Energy value. ** Note: This report can display a maximum of 6 utilities. If additional utilities are used, they will be included in the total.
Totals**
Totals
Cogeneration
Cogeneration
Base Utilities
Heating plant load
Receptacles
Receptacle
Lighting
Lighting
Supply Fans Circ Pumps Base Utilities Aux Subtotal....
Auxiliary
Cooling Compressor Tower/Cond Fans Condenser Pump Other CLG Accessories Cooling Subtotal....
Primary cooling
Primary heating
Primary heating
Elect Cons. kWh
By Maroko & Shwe
% % % %
% % % % %
100.0 %
0.0 %
0.0 %
18.8 %
44.2 %
3.4 0.0 0.0 3.4
26.9 3.2 0.0 3.5 33.5
0.1 %
Percent of Total Energy
49,872.7
0.0
0.0
9,373.2
22,027.9
1,699.6 0.0 0.0 1,699.6
13,390.8 1,593.0 0.0 1,737.7 16,721.6
50.4
Total Source Energy* (kBtu/yr)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 1 Energy Consumption Summary Report Page 1 of 1
ENERGY CONSUMPTION SUMMARY
5,241.3
915.4
2,151.2
358.1
358.1
181.3 1,812.4
1,458.2 172.9
4.3
Project Name: Utah Elementary School Dataset Name: W:\LAUSD Alternative HVAC Systems Study\Calculation\Latest\Utah School.TRC
* Note: Resource Utilization factors are included in the Total Source Energy value. ** Note: This report can display a maximum of 6 utilities. If additional utilities are used, they will be included in the total.
Totals**
Totals
Cogeneration
Cogeneration
Base Utilities
Heating plant load
Receptacles
Receptacle
Lighting
Lighting
Supply Fans Circ Pumps Base Utilities Aux Subtotal....
Auxiliary
Cooling Compressor Tower/Cond Fans Condenser Pump Other CLG Accessories Cooling Subtotal....
Primary cooling
Primary heating
Primary heating
Elect Cons. kWh
By Maroko & Shwe
% % % %
% % % % %
100.0 %
0.0 %
0.0 %
17.5 %
41.0 %
6.8 0.0 0.0 6.8
27.8 3.3 0.0 3.5 34.6
0.1 %
Percent of Total Energy
53,670.8
0.0
0.0
9,373.2
22,027.9
3,666.6 0.0 0.0 3,666.6
14,932.2 1,770.4 0.0 1,856.5 18,559.0
44.1
Total Source Energy* (kBtu/yr)
TRACE® 700 v4.1 calculated at 09:37 AM on 05/20/2005 Alternative - 2 Energy Consumption Summary Report Page 1 of 1
ENERGY CONSUMPTION SUMMARY
SPECIFICATIONS WITH HORIZONTAL AIR SLIM-LINE OUTDOOR UNIT
PK/PKH WALL-MOUNTED
AIR CONDITIONERS AND HEAT PUMPS
0°F LOW AMBIENT CAPABLE †
SYSTEM
PK18FK/FL
PK24FK/FL
PK30FK/FL
Cooling Btu/h *1
12,500
18,500
24,000
30,000
34,200
18,000
Capacity
Heating Btu/h *1,*3
——
——
——
——
——
18,600 (24,100/25,100)
25,000 (30,500/31,500) 33,000 (39,100/40,500) 38,000 (44,100/45,500)
Capacity
14,700 (20,200/21,200) 19,000 (25,100/26,500) 19,600 (25,700/27,100)
24,000
30,000
34,200
Heating Btu/h *2,*3
——
——
——
——
——
10,700 (16,200/17,200)
Power Consumption
Cooling kW *1
1.21
1.75
2.34
3.06
3.47
1.79
Power Consumption
Heating kW *1,*3
——
——
——
——
——
1.56 (3.16/3.46) 2.37 (3.97/4.27) 3.02 (4.82/5.22) 3.54 (5.34/5.74)
Power Consumption
Heating kW *2,*3
——
——
——
——
——
1.34 (2.94/3.24) 1.92 (3.52/3.82) 2.48 (4.28/4.68) 2.65 (4.45/4.85)
Cooling
10.3
10.6
10.3
9.8
9.9
10.1
10.2
9.6
9.9
11.5
11.3
10.6
10.7
10.2
11.1
10.2
10.6
10.5
EER SEER
2.36
3.12
3.44
——
——
——
——
——
7.2
6.8
7.1
6.9
COP
Heating *1
——
——
——
——
——
3.5
3.1
3.2
3.1
COP
Heating *2
——
——
——
——
——
2.3
2.2
2.2
2.2
PK12FK
PK18FK/FL
PK24FK/FL
PK30FK/FL
HSPF
INDOOR UNIT External Finish
PK36FK/FL PKH18FK/FL PKH24FK/FL PKH30FK/FL PKH36FK/FL
Munsell 3.4Y7.7/0.8Munsell 3.4Y7.7/0.8
Power Supply
V, Phase, Hz
115,1,60
115,1,60
115,1,60
115,1,60
115,1,60
208/230,1,60
208/230,1,60
208/230,1,60
208/230,1,60
Max. Fuse Size
(Time Delay) Amp
15
15
15
15
15
15
15
15
15
Min. Ampacity
Amp
1
1
1
2
2
12
12
13
13
Fan Motor
F.L.A.
0.7
0.7
0.7
1
1
0.5
0.5
0.6
0.6
A (kW)
——
——
——
——
——
7.6/8.4 (1.6/1.9)
7.6/8.4 (1.6/1.9)
Airflow Lo-Hi
Dry CFM
350-490
530-710
530-710
780-990
780-990
530-710
530-710
780-990
780-990
Airflow Lo-Hi
Wet CFM
320-440
480-640
480-640
700-890
700-890
480-640
480-640
700-890
700-890
Moisture Removal
Pints/h
3.8
5.3
7.2
9.6
10.5
5.3
7
9.1
10.5
Sound Pressure Level Lo-Hi
dB(A)
38-45
41-48
41-48
44-49
44-49
41-48
41-48
44-49
46-50
Cond. Drain Connection
Inches
Indoor Unit Width
Inches
49-1/4
55-1/8
55-1/8
66-3/16
66-3/16
55-1/8
55-1/8
66-3/16
66-3/16
Indoor Unit Depth
Inches
7-7/8
9-1/4
9-1/4
9-1/4
9-1/4
9-1/4
9-1/4
9-1/4
9-1/4
Indoor Unit Height
Inches
11-13/16
13-3/8
13-3/8
13-3/8
13-3/8
13-3/8
13-3/8
13-3/8
13-3/8
Weight
Pounds
Auxiliary Heater
OUTDOOR UNIT† External Finish Sound Pressure Level
37
53
53
62
62
57
57
66
66
PU12EK
PU18EK
PU24EK
PU30EK
PU36EK
PUH18EK
PUH24EK
PUH30EK
PUH36EK
Munsell 5Y 7/1 Munsell 5Y 7/1 Munsell 5Y 7/1 dB(A)
8.7/9.6 (1.8/2.2) 8.7/9.6 (1.8/2.2)
1.0” O.D. (3/16 I.D.)
50.0
53.0
55.0
208/230,1,60 208/230,1,60 208/230,1,60
Munsell 5Y 7/1
Munsell5Y5Y7/1 7/1 Munsell 5Y 7/1 Munsell
Munsell 5Y 7/1 Munsell 5Y 7/1 Munsell 5Y 7/1
55.0
55.0
53.0
55.0
55.0
55.0
208/230,1,60
208/230,1,60
208/230,1,60
208/230,1,60
208/230,1,60
208/230,1,60 30.0
Power Supply
V, Phase, Hz
Max. Fuse Size
(Time Delay) Amp
15.0
20.0
20.0
30.0
30.0
20.0
20.0
30.0
Min. Ampacity
Amp
11.0
16.0
16.0
20.0
22.0
16.0
16.0
20.0
22.0
Fan Motor
F.L.A.
0.65
0.75
0.65+0.65
0.65+0.65
0.75+0.75
0.75
0.65+0.65
0.75+0.75
0.75+0.75
Compressor
Model (Type)
RH167NAB
RH247NAB
NH33NBD
NH41NAD
NH47NAD
RH247NAB
NH33NBD
NH41NAD
NH47NAD
Compressor
R.L.A.
8.9
12.0
11.5
14.0
17.5
12.0
11.5
14.0
17.5
Compressor
L.R.A.
29.0
37.0
54.0
73.0
87.0
37.0
54.0
73.0
87.0
Crankcase Heater
A(W)
0.11/0.12 (23/28) 0.11/0.12 (23/28) 0.16/0.17 (33/39)
0.16/0.17 (33/39)
Refrigerant Control
0.16/0.17 (33/39) 0.11/0.12 (23/28) 0.16/0.17 (33/39) 0.16/0.17 (33/39) 0.16/0.17 (33/39) Capillary Tube
Defrost Method
Reverse Cycle
——
——
——
——
——
Outdoor Unit Width
Inches
34-1/4
34-1/4
34-1/4
34-1/4
38-3/16
34-1/4
34-1/4
38-3/16
38-3/16
Outdoor Unit Depth
Inches
11-5/8
11-5/8
11-5/8
11-5/8
13-9/16
11-5/8
11-5/8
13-9/16
13-9/16
Outdoor Unit Height
Inches
25-9/16
33-1/2
49-9/16
49-9/16
49-9/16
33-1/2
49-9/16
49-9/16
49-9/16
Weight
Pounds
105.0
154.0
207.0
208.0
220.0
131.0
202.0
245.0
246.0
Remote Controller Control Voltage Refrigerant Piping Size
Hard-wired (FK) or Wireless (FL) With Indoor Unit (By Built-In Transformer)
12VDC
12VDC
12VDC
12VDC
12VDC
12VDC
12VDC
12VDC
12VDC
(Liquid x Gas) Inches
3/8 x 5/8
3/8 x 5/8
3/8 x 5/8
1/2 x 3/4
1/2 x 3/4
3/8 x 5/8
3/8 x 5/8
1/2 x 3/4
1/2 x 3/4
*1,*2,*3 See page 27 for rating conditions. †
PK36FK/FL PKH18FK/FL PKH24FK/FL PKH30FK/FL PKH36FK/FL
PK12FK
Capacity
0°F low ambient operation possible on slim-line horizontal discharge outdoor units with optional wind baffle.
LIMITED WARRANTY Six-year warranty on compressor. One-year warranty on parts. Specifications subject to change without notice.
19
SPECIFICATIONS WITH HORIZONTAL AIR SLIM-LINE OUTDOOR UNIT
PC/PCH CEILING-SUSPENDED 0°F LOW AMBIENT CAPABLE †
*1,*2,*3 See page 27 for rating conditions. †
22
0°F low ambient operation possible on slim-line horizontal discharge outdoor units with optional wind baffle.
AIR CONDITIONERS AND HEAT PUMPS
LIMITED WARRANTY Six-year warranty on compressor. One-year warranty on parts. Specifications subject to change without notice.
MEASURED CLASSROOM SOUND LEVELS IN RECENTLY COMPLETED SCHOOLS
AN INDEPENDENT STUDY
by
Maroko & Shwe, Inc., Professional Engineers
Contents Introduction
3
Valley New High School #1
4
Measured Sound Spectrum
Burbank High School #1 Martin Newson’s Report
Paradise Canyon Elementary School
7
10 11
23
Catalog Data
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
2
Introduction This report is a compilation of the actual background sound level measurements in the classrooms of recently completed schools. The HVAC plans and equipment data is also included.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
3
Valley New High School #1 We visited the Valley New High School # 1 of LAUSD together with Mark Schaffer of Schaffer Acoustics on April 8, 2005 and again with some engineers (Dave Phillips and Dan Hill) from The Trane Company on May 3, 2005 to measure the classroom sound levels. The classrooms are provided with Trane Precedent YHC Model 4 Ton units at the top floor and Trane Odyssey TWE 4 Ton Split System fan coil units in the lower level classrooms. The HVAC floor and roof plans of the measured Classrooms are attached. The following sound levels were measured:
Classroom No. 1
1-416
1-420 2
1-424
Measured Sound Level (dBA) 1
47.5
45.6 2
1-216 2
Measured Sound Spectrum attached. Measured Sound Spectrum attached.
31.5
1-421 1
Remark
Measured Sound Spectrum attached.
42.1
Measured Sound Spectrum attached.
Sound level is high because return air opening is close to return riser. Compressor is off.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
4
Classroom 1-216
Classroom 1-416
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
5
Classroom 1-420
Classroom 1-424
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
6
Measured Sound Spectrum
Classroom 216
Classroom 420
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
7
Classroom 416
Classroom 421
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
8
The following Standard Design Measures for HVAC Sound Attenuation were incorporated in the system designs: 1. Size diffusers and registers for NC – 25 or less. 2. Provide proper duct connections at diffusers and registers as indicated in Figure 1.4 of this report. 3. Provide a minimum 5’-0” of flexible duct at all air inlets and outlets. 4. Provide an adequate number of manual volume dampers. Locate the dampers a minimum 3 duct diameters up stream or downstream of air inlets and outlets. Maximize the distance between dampers and take-offs and elbows. 5. Size ducts per velocities as recommended by project acoustical consultants 850 feet per minute for main ducts and 450 feet per minute for branch ducts. 6. Provide turning vanes at all rectangular elbows. 7. Provide ducted returns with the air inlet registers at a minimum 15’-0” from the main duct risers. 8. Fully lined supply and return air ducts. 9. Provide vibration isolators for all rotating or reciprocating HVAC equipment including packaged units, fans and compressors. 10. Provide sound barriers and acoustic sealant at the inside of the curb and duct roof penetrations, and beneath the unit (similar to in Figure 1.5). 11. Not over estimating the fan static pressures or system capacities. 12. Ensure that the systems are balanced properly. 13. Carefully consider the location of HVAC equipment. 14. Ensure that the Architects provide sufficient space for the proper installation, performance and service of ductwork and equipment. Detailed requirements that include the above measures except duct lining are already part of the LAUSD design guidelines and guide specifications. The duct lining was excluded because Mark Schaffer of Schaffer Acoustics determined through calculations that the benefits are not significant for small rooftop packages and individual classroom fan coil units.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
9
Burbank High School #1 We visited the Burbank High School # 1 of Burbank Unified School District together with Joe Celano of Martin Newsom and Associates, Acoustical Engineers on March 24, 2003 to measure the classroom sound levels. The classrooms are provided with Carrier HJL Model 4 Ton units at the top floor and Carrier Model FB4A 4 Ton Split System fan coil units. The HVAC floor and roof plans of the measured Classrooms are attached. The following sound levels were measured:
Classroom No. 1
210 (212)
44~46
206
43
1
142 (154) 1
1
Measured Sound Level (dBA)
44~45
Office 124 (112)
35~45
Library (Main)
44
Library (Mezz)
52~54
Room Name on Plan.
The Design Measures similar to the LAUSD Standards for HVAC Sound Attenuation were incorporated in the system designs.
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
10
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
11
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
12
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
13
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
14
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
15
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
16
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
17
Library
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
18
Office 1-112
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
19
Classroom 154
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
20
Classroom 206
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
21
Classroom 212
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
22
Paradise Canyon Elementary School We visited the special quite classroom intended for children with cochlear implants at the Paradise Canyon Elementary School in the La Canada School District together with some engineers (Dave Phillips and Dan Hill) from The Trane Company on December 7, 2004. We made measured drawings of the HVAC equipment and ductwork as installed on the roof and inside the classroom. We also took photographs. These drawings and photographs are included as figures 3.1a, 3.1b and 3.1c. Drawings and photographs of a typical LAUSD installation is also included as figures 3.2a, 3.2b and 3.2c for easy comparison. Indoor sound levels less than 40dBA were measured during our visit by the Trane engineers though 35 dBA was not achieved probably due to the higher outdoor ambient sound levels as school was in session. We concluded that the HVAC system of the classroom is quieter because of the following: 1. The entire air distribution duct system is on the roof thus eliminating the breakout portion of the noise generated by the duct system totally. The location of the ductwork on the roof is incidental as the classroom building does not have sufficient space above the ceiling to accommodate the ductwork. Multiple roof penetrations are avoided by most Architects due to the higher possibility of leakage. Location of ductwork and piping on the roof is also avoided due to the added difficulty in reproofing. 2. The entire duct system is provided with 2” lining. Outdoor ductwork conveying heated or refrigerated cool air is required to be provided with a minimum of 2” insulation per Title-24 code requirements. The 2” lining is also incidental. 3. The air outlet ceiling diffusers and air inlet ceiling return air registers are of a more expensive type that generates substantially less noise. The catalog data of these air inlets and outlets are included as figures 3.3a and 3.3b. The catalog data of industry prevalent air inlets and outlets are also included as figures 3.4a and 3.4b for easy comparison. The supply air diffusers are substantially quieter by about 6 dBA for the same air flow rate. We will incorporate these diffusers and registers into the LAUSD standard specifications. 4. We also ran a Trane Acoustics Program (TAP) for the classroom with the ductwork configuration as installed but with the sound level of a 4 Ton Trane Precedent unit for which we have the unit sound levels. We calculated 38 dBA with this duct arrangement when we got 47 dBA with our typical arrangement. We could conclude that the effect of the
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
23
installation especially the elimination of the break out noise of the ductwork by having the ductwork on the roof attenuated 9 dBA.
PARADISE CANYON SCHOOL - CLASSROOM ROOF PLAN FIG 3.1a
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
24
PARADISE CANYON SCHOOL - TRANE ROOFTOP UNIT FIG 3.1b
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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25
PARADISE CANYON SCHOOL - TRANE ROOFTOP UNIT FIG 3.1c
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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26
TYPICAL LAUSD CLASSROOM LAYOUT FIG 3.2a
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
27
TYPICAL LAUSD CLASSROOM ROOF LAYOUT FIG 3.2b
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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28
TYPICAL GAS/ELECTRIC ROOFTOP UNIT FIG 3.2c
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
29
TITUS CEILING DIFFUSER FIG 3.3a
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
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30
TITUS CEILING DIFFUSER PERFORMANCE DATA FIG 3.3b
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
31
KRUEGER CEILING DIFFUSER FIG 3.4a
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
32
KRUEGER CEILING DIFFUSER PERFORMANCE DATA FIG 3.4b
Maroko & Shwe, Inc. , 10200 Sepulveda Blvd., Suite 380, Mission Hills, CA 91345
MSi Tel: (818) 830-1161, Fax: (818) 830-6121, e-mail:
[email protected]
33
(3 - 4Tons) General Data
High Efficiency
Table GD-5 — General Data
Cooling Performance1 Gross Cooling Capacity SEER2 Nominal CFM / ARI Rated CFM ARI Net Cooling Capacity System Power (KW) Heating Performance3 Heating Models Heating Input (Btu) Heating Output (Btu)7 AFUE %4 8 Steady State Efficiency (%)8 No. Burners No. Stages Gas Supply Line Pressure Natural (minimum/maximum) LP (minimum/maximum) Gas Connection Pipe Size (in.) Compressor No./Type Outdoor Sound Rating (dB)5 Outdoor Coil - Type Tube Size (in.) OD Face Area (sq ft) Rows/FPI Indoor Coil - Type Tube Size (in.) Face Area (sq ft) Rows/FPI Refrigerant Control Drain Connection No./Size (in.) Outdoor Fan - Type No. Used/Diameter (in.) Drive Type/No. Speeds CFM No. Motors/HP Motor RPM
20
3-Ton Convertible Units YHC036A1, A3, A4, AW
4-Ton Convertible Units YHC048A1, A3, A4, AW
38,000 12.50 1,200 / 1,200 36,600 3.33
49,800 12.0 1,600/1,600 47,500 4.48
Low 60,000 48,000 81 81 2 1
Medium 80,000 64,000 81 81 2 1
1/2
4.5/14.0 10.0/14.0 1/2 1/Climatuff Scroll 83 Lanced 0.3125 7.19 2/17 Lanced 0.3125 6.68 3/16 Short Orifice 1/¾ NPT Propeller 1/22 Direct/1 2,550 1/0.20 1,075
High 120,000 96,000 81 81 3 1
1/2
Low 60,000 48,000 81 81 2 1
Medium 80,000 64,000 81 81 2 1
High 120,000 96,000 81 81 3 1
1/2
4.5/14.0 10.0/14.0 1/2
1/2
1/Climatuff Scroll 85 Lanced 0.3125 9.59 3/17 Lanced 0.3125 6.68 4/16 Short Orifice 1/¾ NPT Propeller 1/22 Direct/1 3,050 1/0.33 1,075
RT-PRC006-EN
(3 - 4Tons) General Data
High Efficiency
Table GD-5 — Continued
Direct Drive Indoor Fan - Type No. Used/Diameter (in.) Drive Type/No. Speeds No. Motors Motor HP (Standard/Oversized) Motor RPM (Standard/Oversized) Motor Frame Size (Standard/Oversized) Belt Drive Indoor Fan - Type No. Used/Diameter (in.) Drive Type/No. Speeds No. Motors Motor HP (Standard/Oversized) Motor RPM (Standard/Oversized) Motor Frame Size (Standard/Oversized) Filters - Type Furnished 13 (No.) Size Recommended Refrigerant Charge (Lbs of R-22)6
3-Ton Convertible Units YHC036A1, A3, A4, AW FC Centrifugal 1/10 x10 Direct/2 1 0.33/0.50 950/1,1009 48/48 FC Centrifugal 1/11 x 11 Belt/Variable Sheave 12 1 1.00/— 1,750/— 56/— Throwaway (2) 20 x 25 x 110 5.311
4-Ton Convertible Units YHC048A1, A3, A4, AW FC Centrifugal 1/11 x 11 Direct/2 1 0.60/0.80 930/1,0009 48/48 FC Centrifugal 1/11 x 11 Belt/Variable Sheave 12 1 1.00/— 1,750/— 56/— Throwaway (2) 20 x 25 x 110 7.711
NOTES: 1. Cooling Performance is rated at 95 F ambient, 80 F entering dry bulb, 67 F entering wet bulb. Gross capacity does not include the effect of fan motor heat. ARI capacity is net and includes the effect of fan motor heat. Units are suitable for operation to ±20% of nominal cfm. Certified in accordance with the Unitary Air-Conditioner Equipment certification program, which is based on ARI Standard 210/240. 2. SEER are rated at ARI conditions and in accordance with DOE test procedures. 3. Heating Performance limit settings and rating data were established and approved under laboratory test conditions using American National Standards Institute standards. Ratings shown are for elevations up to 2000 feet. For elevations above 2000 feet, ratings should be reduced at the rate of 4% for each 1000 feet above sea level. 4. AFUE and Steady State Efficiency is rated in accordance with DOE test procedures. 5. Outdoor Sound Rating shown is tested in accordance with ARI Standard 270. For additional information refer to Table PD-85. 6. Refrigerant charge is an approximate value. For a more precise value, see unit nameplate and service instructions. 7. YHC036A1 and YHC048A1 Heating Output (Btu) is Low 47,000, Medium 63,000, High 95,000. 8. YHC036A1 and YHC048A1 AFUE (%) and Steady State (%) is Low, Medium and High 80.0. 9. Motor RPM shown is low speed. High speed Motor RPM is : YHC036A 1,060/1,145, YHC048A 1,000/1,100. 10. Filter size shown is for low and medium heat models. High heat model filter size recommended is 20 x 30 x 1. 11. Refigerant charge shown is for three phase. YHC036A1 Refrigerant Charge is 4.5, YHC048A1 refrigerant charge is 8.1. 12.Belt Drive motor is not available for YHC036A1, YHC048A1 13.Optional 2” pleated filters also available.
RT-PRC006-EN
21
Performance Data Table PD-88 — Static Pressure Drops Through Accessories (Inches Water Column) Unit Tons
Model No YSC036A
3 YHC036A
4
Y#C048A
YSC060A 5 YHC060A
6
Y#C072A
YSC090, 092A 7½ YHC092A
8½
Y#C102A
10
Y#C120A
Economizer with OA/RA Dampers2 2” Pleated 100% OA 100% RA 100% OA
Standard CFM 960 1200 1440 960 1200 1440 1280 1600 1920 1600 2000 2400 1600 2000 2400 1920 2400 2880 2400 3000 3600 2400 3000 3600 2720 3400 4080 3200 4000 4800
Filters1 0.03 0.04 0.06 0.02 0.03 0.04 0.04 0.05 0.08 0.10 0.15 0.22 0.04 0.06 0.09 0.04 0.06 0.09 0.06 0.10 0.14 0.04 0.06 0.09 0.05 0.08 0.12 0.07 0.11 0.16
Filters 0.05 0.07 0.10 0.04 0.05 0.07 0.06 0.09 0.12 0.15 0.22 0.29 0.07 0.10 0.14 0.07 0.09 0.12 0.09 0.13 0.18 0.06 0.09 0.13 0.08 0.11 0.16 0.10 0.15 0.20
Downflow 0.05 0.07 0.10 0.05 0.07 0.10 0.08 0.12 0.17 0.12 0.18 0.26 0.12 0.18 0.26 0.10 0.11 0.13 0.11 0.14 0.21 0.11 0.14 0.21 0.12 0.19 0.30 0.17 0.26 0.34
0.01 0.02 0.03 0.01 0.02 0.03 0.03 0.04 0.06 0.04 0.07 0.10 0.04 0.07 0.10 0.01 0.02 0.04 0.02 0.05 0.07 0.02 0.05 0.07 0.03 0.06 0.07 0.05 0.07 0.09
0.05 0.07 0.10 0.05 0.07 0.10 0.08 0.12 0.17 0.12 0.18 0.26 0.12 0.18 0.26 0.06 0.08 0.10 0.08 0.12 0.25 0.08 0.12 0.25 0.09 0.18 0.31 0.14 0.30 0.35
100% RA
Horizontal 0.00 0.01 0.01 0.00 0.01 0.01 0.01 0.01 0.02 0.01 0.02 0.04 0.01 0.02 0.04 0.02 0.02 0.04 0.02 0.05 0.08 0.02 0.05 0.08 0.04 0.06 0.09 0.05 0.08 0.10
Notes: 1. Tested with standard filters (3-5 tons 1”, 6-10 tons 2”) . Difference in pressure drop should be considered when utilizing optional 2” pleated filters. 2. OA = Outside Air and RA = Return Air.
Table PD-89— Outdoor Sound Power Level - dB (ref. 10 -12 Watts) Tons 3 4
5 6 7½
8½ 10
Unit Model No. Y*C036A YSC048A1 YSC048A3,A4,AW YHC048A YSC060A YHC060A YSC072A YHC072A YSC090A YSC092A YHC092A YSC102A YHC102A YSC120A YHC120A
63. 86 92 90 92 94 94 90 91 92 89 92 88 91 91 94
125 83 87 84 86 87 87 94 95 95 93 96 92 95 88 89
250 81 84 78 83 83 82 90 90 91 88 92 87 90 84 87
Octave Center Frequency 500 1000 2000 80 78 74 83 81 76 77 76 72 82 81 75 82 79 75 81 78 74 87 83 78 87 84 79 88 84 80 85 81 76 89 85 80 84 80 75 87 84 79 82 81 76 85 84 78
4000 69 72 70 72 73 72 74 75 75 72 76 72 75 73 75
8000 68 69 68 69 69 69 67 68 68 66 69 65 68 67 69
Overall dBA 83 86 82 85 84 84 88 89 90 87 91 86 89 86 88
Note: Tests follow ARI270-95.
RT-PRC006-EN
71
General Data OUTDOOR UNIT 12 SOUND RATING (DECIBELS) 2 POWER CONNS. — V/PH/HZ 3 MIN. BRCH. CIR. AMPACITY BR. CIR. MAX. (AMPS) PROT. RTG. MIN. (AMPS) COMPRESSOR NO. USED - NO. SPEEDS VOLTS/PH/HZ R.L. AMPS 7 - L.R. AMPS FACTORY INSTALLED START COMPONENTS 8 INSULATION/SOUND BLANKET COMPRESSOR HEAT OUTDOOR FAN — TYPE DIA. (IN.) - NO. USED TYPE DRIVE - NO. SPEEDS CFM @ 0.0 IN. W.G. 4 NO. MOTORS - HP. MOTOR SPEED R.P.M. VOLTS/PH/HZ F.L. AMPS OUTDOOR COIL — TYPE ROWS - F.P.I. FACE AREA (SQ. FT.) TUBE SIZE (IN.) REFRIGERANT CONTROL REFRIGERANT (O.D. UNIT) NP CHRG. 5 FACTORY SUPPLIED LINE SIZE - IN. O.D. GAS 6 LINE SIZE - IN. O.D. LIQ. 6 FCCV RESTRICTOR ORIFICE SIZE DIMENSIONS OUTDOOR UNIT CRATED (IN.) UNCRATED WEIGHT SHIPPING (LBS.) NET (LBS.)
}
2TWA0048A3000A 81 200/230/3/60 19 30 30 CLIMATUFF® 1-1 200/230/3/60 13.7 - 101
2TWA0048A4000A 81 460/3/60 10 15 15 CLIMATUFF® 1-1 460/3/60 7.1 - 51
NO NO YES PROPELLER 23 - 1 DIRECT - 1 3700 1 - 1/4 825 200/230/3/60 1.9 SPINE FIN™ 1 - 24 15.18 3/8 EXPANSION VALVE R-22 8/06-LB/OZ YES 1-1/8 3/8
NO NO YES PROPELLER 23 - 1 DIRECT - 1 3700 1 - 1/4 825 460/3/60 1 SPINE FIN™ 1 - 24 15.18 3/8 EXPANSION VALVE R-22 8/06-LB/OZ YES 1-1/8 3/8
0.083 H X W X D 38 X 30.1 X 33.8 SEE OUTLINE DWG.
0.083 H X W X D 38 X 30.1 X 33.8 SEE OUTLINE DWG.
254 226
254 226
2TWA0048A3/4000A
1 CERTIFIED IN ACCORDANCE WITH THE AIR-SOURCE UNITARY HEAT PUMP EQUIPMENT CERTIFICATION PROGRAM WHICH IS BASED ON A.R.I. STANDARD 210/240. 2 RATED IN ACCORDANCE WITH A.R.I. STANDARD 270. 3 CALCULATED IN ACCORDANCE WITH NATIONAL ELECTRIC CODE. ONLY USE HACR CIRCUIT BREAKERS OR FUSES. 4 STANDARD AIR - DRY COIL - OUTDOOR 5 THIS VALUE APPROXIMATE. FOR MORE PRECISE VALUE SEE UNIT NAMEPLATE AND SERVICE INSTRUCTION. 6 MAX. LINEAR LENGTH: 80 FT WITH RECIPROCATING COMPRESSOR 60 FT WITH SCROLL. MAX. LIFT - SUCTION 60 FT; MAX LIFT - LIQUID 60 FT. FOR GREATER LENGTH REFER TO REFRIGERANT PIPING SOFTWARE PUB. NO. 32-3312-01. 7 THE VALUE SHOWN FOR COMPRESSOR RLA ON THE UNIT NAMEPLATE AND ON THIS SPECIFICATION SHEET IS USED TO COMPUTE MINIMUM BRANCH CIRCUIT AMPACITY AND MAXIMUM FUSE SIZE. THE VALUE SHOWN IS THE BRANCH CIRCUIT SELECTION CURRENT. 8 NO MEANS NO START COMPONENTS YES MEANS QUICK START KIT COMPONENTS PTC MEANS POSITIVE TEMPERATURE COEFFICIENT STARTER.
SPLIT SYSTEM
OUTDOOR UNIT WITH HEAT PUMP COILS
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.)
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.) ✝
TXA042C4 CHG TO 83
TXA043C4 CHG TO 83
TXA048C4 FACT INS 83
TXA049C4 FACT INS 83
TXA050C4 FACT INS 83
TXA060C5 TXV-B
TXA061C5 TXV-B
44000 29400 1200 4.61 9.55/10.25
46500 33700 1575 4.87 9.55/10.25
46000 31900 1350 4.74 9.70/10.25
47500 34600 1600 4.92 9.65/10.25
47500 34600 1600 4.92 9.65/10.25
48000 35300 1700 4.95 9.70/10.50
49500 37700 1800 5.08 9.75/10.75
43500 4.14 3.08 7.40
44500 4.10 3.18 7.40
44000 4.05 3.18 7.40
45000 4.04 3.26 7.50
45000 4.04 3.26 7.50
45500 4.02 3.32 7.60
46000 4.06 3.32 7.60
TXC042C4 CHG TO 83
TXC043C4 CHG TO 83
TXC048C4 FACT INS 83
TXC049C4 FACT INS 83
TXC050C4 FACT INS 83
TXC054S3 TXV-B
TXC060C5 TXV-B
44000 29400 1200 4.61 9.55/10.25
46500 33700 1575 4.87 9.55/10.25
46000 31900 1350 4.74 9.70/10.25
47500 34600 1600 4.92 9.65/10.25
47500 34600 1600 4.92 9.65/10.25
48000 35600 1700 4.97 9.65/11.00
48000 35300 1700 4.95 9.70/10.50
43500 4.14 3.08 7.40
44500 4.10 3.18 7.40
44000 4.05 3.18 7.40
45000 4.04 3.26 7.50
45000 4.04 3.26 7.50
45500 4.02 3.32 7.60
45500 4.02 3.32 7.60
See pages 24 and 25 for combinations with Auxiliary Devices.
16
22-1738-01-1002 (EN)
General Data
2TWA0048A3/4000A
OUTDOOR UNIT WITH HEAT PUMP COILS
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.)
TXC061C5 TXV-B
TXC065S3 TXV-NB
TXH041A4 CHG TO 83
TXH054A4 FACT INS 83
TXH063P3-A TXV-NB
TXH063P3-B TXV-NB
49500 37700 1800 5.08 9.75/10.75
50000 38000 1800 5.10 9.80/11.00
47500 34900 1575 4.90 9.70/10.50
50500 38500 1700 5.10 9.90/10.50
51000 39500 1800 5.10 10.00/11.25
51500 40100 1800 5.12 10.05/11.25
46000 4.06 3.32 7.60
46000 3.99 3.38 7.65
44500 4.10 3.18 7.40
45500 3.99 3.34 7.65
46000 3.92 3.44 7.75
46000 3.92 3.44 7.75
OUTDOOR UNIT WITH AIR HANDLERS
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.)
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.)
TWE042C14 CHG TO 83
TWE042P13 TXV-NB
TWE048C14 FACT INS 83
TWE048P13 TXV-NB
TWE049E13 TXV-NB
TWE060A TXV-B
TWE060C/D15 TXV-B
46500 34200 1575 4.95 9.40/10.25
47500 34800 1575 4.95 9.60/10.50
47500 35100 1600 4.92 9.65/10.50
50500 37400 1600 5.05 10.00/11.00
50500 36800 1500 4.76 10.60/11.50
48000 36000 1800 4.82 9.95/11.00
48500 36800 1800 5.22 9.30/10.25
44500 4.26 3.06 7.25
44500 4.10 3.18 7.40
45500 4.11 3.24 7.40
45500 3.90 3.42 7.70
45000 3.77 3.50 8.00
45000 4.00 3.30 7.60
46500 4.28 3.18 7.50
TWE060P13 TXV-NB
TWE063P13 TXV-NB
TWE065E13 TXV-NB
TWG042A14 CHG TO 83
TWG048A14 FACT INS 83
TWG060A15 TXV-B
51000 39700 1800 5.13 9.95/11.00
50000 36900 1600 5.15 9.70/11.00
51500 38800 1640 4.93 10.45/11.50
44000 31300 1500 4.73 9.30/10.00
47500 35000 1600 4.95 9.60/10.50
49000 37100 1800 5.16 9.50/10.50
46000 3.94 3.42 7.70
46500 4.05 3.36 7.60
45500 3.74 3.56 8.00
43500 4.28 2.98 7.25
44500 4.15 3.14 7.40
46000 4.19 3.22 7.50
OUTDOOR UNIT WITH FURNACES AND COILS
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.) ✝See
TDD100R9V5 +TXC054S3 TXV-NB
TDD100R9V5 +TXH063P3 TXV-NB
TDD120R9V5 +TXH063P3 TXV-NB
TUD100R9V5 +TXC054S3 TXV-NB
TUD100R9V5 +TXH063P3 TXV-NB
TUD120R9V5 +TXH063P3 TXV-NB
TUD140R9V5 +TXC065S3 TXV-NB
48000 35100 1620 4.85 9.90/11.00
51000 37800 1600 4.93 10.35/11.50
51000 38100 1625 4.86 10.50/11.50
48000 35400 1670 4.95 9.70/11.00
50500 37400 1600 4.98 10.15/11.25
51000 38100 1625 4.88 10.45/11.50
49500 36200 1600 4.81 10.30/11.50
45000 3.97 3.32 7.65
45500 3.85 3.46 7.85
45000 3.75 3.52 8.00
45500 4.06 3.28 7.60
45500 3.90 3.42 7.70
45000 3.77 3.50 7.80
45000 3.86 3.42 7.80
pages 24 and 25 for combinations with Auxiliary Devices.
22-1738-01-1002 (EN)
17
General Data
2TWA0048A3/4000A
OUTDOOR UNIT WITH FURNACES AND COILS
EXPANSION TYPE RATINGS (COOLING) 1 BTUH (TOTAL) BTUH (SENSIBLE) INDOOR AIRFLOW (CFM) SYSTEM POWER (KW) EER/SEER (BTU/WATT-HR.) RATINGS (HEATING) 1 (HIGH TEMP.) BTUH SYSTEM POWER (KW) COP HSPF (BTU/WATT-HR.) ✝See
TUD140R9V5 +TXH063P3 TXV-NB 51000 37900 1600 4.86 10.50/11.50 45000 3.77 3.50 7.80
pages 24 and 25 for combinations with Auxiliary Devices.
18
22-1738-01-1002 (EN)
Model number nomenclature 48HJ004-014 (3 to 121/2 Tons) — ASHRAE 90.1 Compliant Example:
48
HJ D
006
48 – Packaged Rooftop Electric Cooling/ Natural Gas Heat
P
M
F
6
4
1
HA FIOPs ** Packaging 1 – Domestic 3 – Export
HJ – Constant Volume, High Efficiency Design Changes Heat Options: 49 States D – Low Heat E – Medium Heat F – High Heat California Compliant G – Non NOx Low Heat (3 Ph, Single Stg) H – Non NOx Medium Heat (3 Ph, Single Stg) K – Non NOx High Heat (3 Ph, Single Stg) L – Low NOx Low Heat (Single Stg) M – Low NOx Medium Heat (Single Stg) N – Low NOx High Heat (Single Stg)
Voltage 1 – 575-3-60 3 – 208/230-1-60 5 – 208/230-3-60 6 – 460-3-60
Coil Protection Options (fin/tube) – – Al/Cu Cond & Evap B – Cu/Cu Cond & Evap C – Cu/Cu Cond & Al/Cu Evap E – E-Coat Al/Cu Cond, E-Coat Al/Cu Evap F – E-Coat Al/Cu Cond & Al/Cu Evap G – E-Coat Cu/Cu Cond & Al/Cu Evap V – Al/Cu Pre-Coat Cond Fin & Al/Cu Evap
48HJ004-014
Tons Nominal Capacity 004 – 3 Tons 005 – 4 Tons 006 – 5 Tons 007 – 6 Tons 008 – 7-1/2 Tons 009 – 8-1/2 Tons 012 – 10 Tons 014 – 12-1/2 Tons
Indoor Motor Options – – Standard Motor & Drive M – High-Static Indoor Motor S – MoistureMi$er™ Dehumidification Pkg. T – MoistureMi$er & High Static Indoor Motor W – MoistureMi$er – Cu/Cu Coil X – MoistureMi$er, Cu/Cu w/High-Static Motor
Controls and Sensors* – – None G – Hinged Access Panels H – Hinged Panels & PremierLink™ Control K – Novar ETM2024 Control† L – Novar ETM2024 Control & Hinged Panels† N – Novar ETM3051 Control† P – PremierLink™ DDC Control R – Novar ETM3051 & Hinged Panels† Y – Apollo Control & Hinged Panels Z – Apollo Control
**Refer to 48HJ Price Pages or contact your local Carrier Representative for FIOP code table. NOTE: Hinged Access Panels include: Filter Panel, Control Box Panel, Fan Motor Panel, Compressor Panel.
LEGEND Al — Aluminum Cu — Copper FIOP — Factory-Installed Option *See below for options available for the 48HJ unit with 62AQ FIOP. †Contact factory for availability and applications. Controls and Sensors (62AQ/RTU) B — 62AQ + Std. RTU Controls C — 62AQ + Hinged Access Panels D — 62AQ + Hinged Panels & PremierLink E — 62AQ + PremierLink Coil Protection Options (fin/tube) (62AQ/RTU) H — 62AQ060 Al/Cu Supply + Exhaust / Al/Cu Cond & Evap J — 62AQ100 Al/Cu Supply + Exhaust / Al/Cu Cond & Evap K — 62AQ200 Al/Cu Supply + Exhaust / Al/Cu Cond & Evap L — 62AQ300 Al/Cu Supply + Exhaust / Al/Cu Cond & Evap M — 62AQ060 Cu/Cu Supply + Exhaust / Cu/Cu Cond & Evap N — 62AQ100 Cu/Cu Supply + Exhaust / Cu/Cu Cond & Evap P — 62AQ200 Cu/Cu Supply + Exhaust / Cu/Cu Cond & Evap Q — 62AQ300 Cu/Cu Supply + Exhaust / Cu/Cu Cond & Evap R — 62AQ060 Cu/Cu Supply + Exhaust / Al/Cu Cond & Evap S — 62AQ100 Cu/Cu Supply + Exhaust / Al/Cu Cond & Evap T — 62AQ200 Cu/Cu Supply + Exhaust / Al/Cu Cond & Evap W — 62AQ300 Cu/Cu Supply + Exhaust / Al/Cu Cond & Evap
132
X Y Z 1 2 3 4 5 6 7 8 9
— — — — — — — — — — — —
62AQ060 E-Ctd Al/Cu Supply, Std. Al/Cu Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ100 E-Ctd Al/Cu Supply, Std. Al/Cu Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ200 E-Ctd Al/Cu Supply, Std. Al/Cu Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ300 E-Ctd Al/Cu Supply, Std. Al/Cu Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ060 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ100 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ200 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ300 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Std. Al/Cu Evap 62AQ060 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Evap 62AQ100 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Evap 62AQ200 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Evap 62AQ300 E-Ctd Al/Cu Supply & Exhaust / E-Ctd Al/Cu Cond & Evap
ARI* capacity ratings UNIT 48HJ 004 005 006 007 008 009 012 014 Bels EER IPLV SEER
— — — —
NOMINAL TONS 3 4 5 6 7.5 8.5 10 12.5
COOLING (Btuh) 36,000 46,000 61,000 73,000 90,000 102,000 120,000 138,000
TOTAL kW 3.2 4.1 5.5 6.7 8.2 9.4 10.9 14.4
LEGEND Sound Levels (1 bel = 10 decibels) Energy Efficiency Ratio Integrated Part-Load Value Seasonal Energy Efficiency Ratio
SEER†
EER
13.0 13.0 13.0 — — — — —
11.2** 11.1** 11.0** 11.0 11.0 10.8 11.0 9.6
SOUND RATING (Bels) 7.6 7.6 8.0 8.0 8.2 8.2 8.4 8.6
IPLV†† N/A N/A N/A N/A 11.6 10.9 11.4 10.3
2. Ratings are net values, reflecting the effects of circulating fan heat. Ratings are based on: Cooling Standard: 80 F db, 67 wb indoor entering-air temperature and 95 F db outdoor entering-air temperature. IPLV Standard: 80 F db, 67 F wb indoor entering-air temperature and 80 F db outdoor entering-air temperature.
*Air-Conditioning & Refrigeration Institute. †Applies only to units with capacity of 65,000 Btuh or less. **ARI does not require EER ratings for units with capacity below 65,000 Btuh. For these units, the EER rating at ARI standard conditions is provided for information only. ††The IPLV is not applicable to single-compressor units. NOTES: 1. Rated in accordance with ARI Standard 210/240 (004-012 units) or 360 (014 units) and 270 (004-014 units).
Sizes 004-012 Only
Sizes 014 Only
HEATING CAPACITIES AND EFFICIENCIES 208/230-1-60 — SINGLE STAGE GAS HEAT UNIT 48HJ E004 F004 D005 E005 F005 D006 E006 F006
INPUT CAPACITY 1st Stage 2nd Stage 72,000 — 115,000 — 72,000 — 115,000 — 150,000 — 72,000 — 115,000 — 150,000 —
OUTPUT CAPACITY 1st Stage 2nd Stage 58,000 — 90,000 — 58,000 — 92,000 — 118,000 — 58,000 — 92,000 — 118,000 —
TEMPERATURE RISE (°F)
MINIMUM HEATING AIRFLOW (CFM)
15-45 55-85 15-45 35-65 50-80 15-45 35-65 50-80
1200 980 1200 1320 1370 1200 1320 1370
EFFICIENCY Steady State (%) 82.0 80.0 82.0 81.0 80.0 82.0 81.0 80.0
AFUE (%) 80.2% 81.0% 80.2% 81.0% 80.7% 80.2% 81.0% 80.7%
EFFICIENCY Steady State (%) 81.2 81.4 81.2 81.4 82.4 81.2 81.4 82.4
AFUE (%) 80.2% 81.0% 80.2% 81.0% 80.7% 80.2% 81.0% 80.7%
EFFICIENCY Steady State (%) 81.2 81.4 81.2 81.4 82.4 81.2 81.4 82.4
208/230-1-60 — SINGLE STAGE GAS HEAT — LOW NOx UNIT 48HJ M004 N004 L005 M005 N005 L006 M006 N006
INPUT CAPACITY 1st Stage 2nd Stage 60,000 — 90,000 — 60,000 — 90,000 — 120,000 — 60,000 — 90,000 — 120,000 —
OUTPUT CAPACITY 1st Stage 2nd Stage 50,000 — 74,000 — 50,000 — 74,000 — 101,000 — 50,000 — 74,000 — 101,000 —
TEMPERATURE RISE (°F)
MINIMUM HEATING AIRFLOW (CFM)
20-50 30-60 20-50 30-60 40-70 20-50 30-60 40-70
930 1150 930 1150 1340 930 1150 1340
208/230/460-3-60 — SINGLE STAGE GAS HEAT — LOW NOx UNIT 48HJ M004 N004 L005 M005 N005 L006 M006 N006
INPUT CAPACITY 1st Stage 2nd Stage 60,000 — 90,000 — 60,000 — 90,000 — 120,000 — 60,000 — 90,000 — 120,000 —
OUTPUT CAPACITY 1st Stage 2nd Stage 50,000 — 74,000 — 50,000 — 74,000 — 101,000 — 50,000 — 74,000 — 101,000 —
TEMPERATURE RISE (°F)
MINIMUM HEATING AIRFLOW (CFM)
20-50 30-60 20-50 30-60 40-70 20-50 30-60 40-70
930 1150 930 1150 1340 930 1150 1340
133
48HJ004-014
AFUE (%) 82.8% 80.0% 82.8% 81.0% 80.4% 82.8% 81.0% 80.4%
ARI* capacity ratings (cont) HEATING CAPACITIES AND EFFICIENCIES (cont) 208/230/460-3-60 — SINGLE STAGE GAS HEAT UNIT 48HJ H004 K004 G005 H005 K005 G006 H006 K006
INPUT CAPACITY 1st Stage 2nd Stage 72,000 — 115,000 — 72,000 — 115,000 — 150,000 — 72,000 — 115,000 — 150,000 —
OUTPUT CAPACITY 1st Stage 2nd Stage 59,040 — 93,150 — 59,040 — 93,150 — 120,000 — 59,040 — 93,150 — 120,000 —
TEMPERATURE RISE (°F)
MINIMUM HEATING AIRFLOW (CFM)
25-55 55-85 25-55 30-60 50-80 15-45 35-65 50-80
1000 1020 1000 1440 1390 1220 1330 1390
AFUE (%) 82.0% 80.0% 82.0% 81.0% 80.0% 82.0% 81.0% 80.0%
EFFICIENCY Steady State (%) 82.0 81.0 82.0 81.0 80.0 82.0 81.0 80.0
AFUE (%) 82.0% 80.0% 82.0% 81.0% 80.0% 82.0% 81.0% 80.0% 82.0% 81.0% 80.0% 82.0% 82.0% 82.0% 82.0% 82.0% 82.0% 82.0% 82.0% 80.0% 82.0% 80.0%
EFFICIENCY Steady State (%) 82.0 80.0 82.0 81.0 80.0 82.0 81.0 80.0 82.0 81.0 80.0 82.0 82.0 82.0 82.0 82.0 82.0 82.0 82.0 80.0 82.0 80.0
208/230/460/575-3-60 — 2 STAGE GAS HEAT UNIT 48HJ
48HJ004-014
E004 F004 D005 E005 F005 D006 E006 F006 D007 E007 F007 D008 E008 F008 D009 E009 F009 D012 E012 F012 D014 E014
134
INPUT CAPACITY 1st Stage 2nd Stage 50,000 72,000 82,000 115,000 50,000 72,000 82,000 115,000 120,000 150,000 50,000 72,000 82,000 115,000 120,000 150,000 50,000 72,000 82,000 115,000 120,000 150,000 90,000 125,000 120,000 180,000 180,000 224,000 90,000 125,000 120,000 180,000 180,000 224,000 120,000 180,000 180,000 224,000 200,000 250,000 180,000 224,000 200,000 250,000
OUTPUT CAPACITY 1st Stage 2nd Stage 41,000 59,040 65,600 93,150 41,000 59,040 66,420 93,150 96,000 120,000 41,000 59,040 66,420 93,150 96,000 120,000 41,000 59,040 66,420 93,150 96,000 120,000 73,800 102,500 98,400 147,600 147,600 183,680 73,800 102,500 98,400 147,600 147,600 183,680 98,400 147,600 147,600 183,680 160,000 200,000 147,600 183,680 160,000 200,000
TEMPERATURE RISE (°F)
MINIMUM HEATING AIRFLOW (CFM)
15-45 55-85 15-45 35-65 50-80 15-45 35-65 50-80 15-45 35-65 50-80 20-50 35-65 45-75 20-50 35-65 45-75 35-65 35-65 40-70 35-65 40-70
1220 1020 1220 1330 1390 1220 1330 1390 1220 1330 1390 1900 1440 2230 1900 1440 2230 1440 2570 2650 2570 2650
Physical data HJE/F/H/K/M/N004 3
HJD/E/F/G/H/K/L/M/N005 4
HJD/E/F/G/H/K/L/M/N006 5
HJD/E/F007 6
530 548 50 115
540 558 50 115
560 578 50 115
635 653 50 115
1 42
1 53
1 50
1 60
10- 0 12-13
12-8 15-6
Scroll
R-22 Acutrol™ Metering Device 5- 8 8-13 1...22 3500 1/ ...825 4 180 1...17 14.6 1...17 3.9 2...15 5.5 1...10 x 10 1200 1.20 2.40 48 56 760-1090 1075-1455 Ball 2100 1.9/2.9 2.8/3.8 1/ 2 5/ 8 4.5 4.5 1...A...36 1...A...39 10.0-12.4 65 65 5 6 3 31/2 890 1233 5/ 8
LEGEND Bhp — Brake Horsepower *Single phase/three phase. †Indicates automatic reset. **60,000 and 72,000 Btuh heat input units have 2 burners. 90,000 and 120,000 Btuh heat input units have 3 burners. 115,000 Btuh heat input units and 150,000 Btuh Heat input units have 3 burners. ††An LP kit is available as an accessory.
10-2 13-2
Propeller 1...22 1...22 3500 4100 1/ ...825 1/ ...1100 4 4 180 320 Enhanced Copper Tubes, Aluminum Lanced Fins 2...17 16.5
2...17 16.5
1...17 1...17 3.9 3.9 Enhanced Copper Tubes, Aluminum Double-Wavy Fins 2...15 4...15 5.5 5.5 Centrifugal Type, Belt Drive 1...10 x 10 1...10 x 10 1600 2000 1.20 1.30/2.40* 2.40 2.90 48 48/56* 56 56 840-1185 1020-1460/1120-1585* 1075-1455 1300-1685 Ball Ball 2100 2100 1.9/2.0 2.4/3.4 2.8/3.8 3.4/4.4 1/ 5/ 2 8 5/ 5/ 8 8 4.0 4.0 4.0 4.5 1...A...36 1....4...40 1...A...39 1...A...40 10.0-12.4 14.7-15.5 70 75 65 60 5 6 6 5 3 3 1 3 /2 31/2 980 1240 1233 1396 5/ 5/ 8 8
1...22 4100
1/ ...1100 4
320
2...17 21.3 1...17 3.9 4...15 7.3 1...10 x 10 2400 2.40 2.90 56 56 1120-1585 1300-1685 Ball 2100 2.4/3.4 3.4/3.4 5/ 8 7/ 8 4.0 4.5 1...A...38 1...A...40 14.7-15.5 95 60 5 5 3 31/2 1304 1396 5/ 8
||Three-phase standard models have heating inputs as shown. Single-phase standard models have one-stage heating with heating input values as follows: HJD005-006,HJE004 — 72,000 Btuh HJE005-006,HJF004 — 115,000 Btuh HJF005-006 — 150,000 Btuh ***California compliant three-phase models. †††California SCAQMD compliant low NOx models have combustion products that are controlled to 40 nanograms per joule or less.
135
48HJ004-014
BASE UNIT 48 NOMINAL CAPACITY OPERATING WEIGHT (lb) Unit With MoistureMi$er™ Dehumidification Package EconoMi$er2 Roof Curb COMPRESSOR Quantity Oil (oz) REFRIGERANT TYPE Expansion Device Operating Charge (lb-oz) Standard Unit Unit With MoistureMi$er Dehumidification Package CONDENSER FAN Quantity...Diameter (in.) Nominal Cfm Motor Hp...Rpm Watts Input (Total) CONDENSER COIL Standard Unit Rows...Fins/in. Total Face Area (sq ft) Unit with MoistureMi$er Dehumidification Package Rows...Fins/in. Total Face Area (sq ft) EVAPORATOR COIL Rows...Fins/in. Total Face Area (sq ft) EVAPORATOR FAN Quantity...Size (in.) Nominal Cfm Maximum Continuous Bhp Std Hi-Static Motor Frame Size Std Hi-Static Fan Rpm Range Std Hi-Static Motor Bearing Type Maximum Fan Rpm Motor Pulley Pitch Diameter A/B (in.) Std Hi-Static Nominal Motor Shaft Diameter (in.) Std Hi-Static Fan Pulley Pitch Diameter (in.) Std Hi-Static Belt — Type...Length (in.) Std Hi-Static Pulley Center Line Distance (in.) Speed Change per Full Turn of Std Movable Pulley Flange (rpm) Hi-Static Movable Pulley Maximum Full Std Turns from Closed Position Hi-Static Factory Setting — Full Turns Open Std Hi-Static Factory Speed Setting (rpm) Std Hi-Static Fan Shaft Diameter at Pulley (in.)
Physical data (cont) BASE UNIT 48 FURNACE SECTION Rollout Switch Cutout Temp (F)† Burner Orifice Diameter (in. ...drill size)** Natural Gas — Std
Liquid Propane — Alt††
Thermostat Heat Anticipator Setting (amps) 208/230/460/575 v First Stage Second Stage Gas Input (Btuh) First Stage/Second Stage
Efficiency (Steady State) (%)
48HJ004-014
Temperature Rise Range
Manifold Pressure (in. wg) Natural Gas — Std Liquid Propane — Alt†† Maximum Static Pressure (in. wg) Field Gas Connection Size (in.)
HJE/F/H/K/M/N004 195 HJE .113...33 HJF .113...33 — HJH .113...33 HJK .113...33 — HJM .102...38 HJN .102...38 — HJE .089...43 HJF .089...43 — HJH .089...43 HJK .089...43 — HJM .082...45 HJN .082...45 — .14 .14 HJE|| 50,000/ 72,000 HJF|| 82,000/115,000 — HJH*** —/ 72,000 HJK***—/115,000 — HJM††† —/ 60,000 HJN††† —/ 90,000 — HJE 82 HJF 80 — HJH 82 HJK 81 — HJM 81.2 HJN 81.4 — HJE 15-45 HJF 55-85 — HJH 25-55 HJK 55-85 — HJM 20-50 HJN 30-60 — 3.5 3.5 1.0 1/ 2
HIGH-PRESSURE SWITCH (psig) Standard Compressor Internal Relief Cutout Reset (Auto.) LOSS-OF-CHARGE SWITCH/LOW-PRESSURE SWITCH (Liquid LIne) (psig) Cutout Reset (Auto.) FREEZE PROTECTION THERMOSTAT Opens (F) Closes (F) OUTDOOR-AIR INLET SCREENS Quantity...Size (in.) RETURN-AIR FILTERS Quantity...Size (in.) LEGEND
Bhp — Brake Horsepower *Single phase/three phase. †Indicates automatic reset. **60,000 and 72,000 Btuh heat input units have 2 burners. 90,000 and 120,000 Btuh heat input units have 3 burners. 115,000 Btuh heat input units and 150,000 Btuh Heat input units have 3 burners. ††An LP kit is available as an accessory. Kit may be used at elevations as high as 2000 ft.
136
HJD/E/F/G/H/K/L/M/N005
HJD/E/F/G/H/K/L/M/N006
195
195
HJD .113...33 HJE .113...33 HJF .129...30 HJG .113...33 HJH .113...33 HJK .129...30 HJL .102...38 HJM .102...38 HJN .116...32 HJD .089...43 HJE .089...43 HJF .104...37 HJG .089...45 HJH .089...45 HJK .102...38 HJL .082...45 HJM .082...45 HJN .094...42
HJD .113...33 HJE .113...33 HJF .129...30 HJG .113...33 HJH .113...33 HJK .129...30 HJL .102...38 HJM .102...38 HJN .116...32 HJD .089...43 HJE .089...43 HJF .104...37 HJG .089...43 HJH .089...43 HJK .104...37 HJL .082...45 HJM .082...45 HJN .094...42
.14 .14
.14 .14
HJD|| 50,000/ 72,000 HJE|| 82,000/115,000 HJF|| 120,000/150,000 HJG*** —/ 72,000 HJH*** —/115,000 HJK*** —/150,000 HJL††† —/ 60,000 HJM††† —/ 90,000 HJN††† —/120,000 HJD 82 HJE 81 HJF 80 HJG 82 HJH 81 HJK 80 HJL 81.2 HJM 81.4 HJN 82.4 HJD 15-45 HJE 35-65 HJF 50-80 HJG 25-55 HJH 35-65 HJK 50-80 HJL 20-50 HJM 30-60 HJN 40-70
HJD|| 50,000/ 72,000 HJE|| 82,000/115,000 HJF|| 120,000/150,000 HJG*** —/ 72,000 HJH*** —/115,000 HJK*** —/150,000 HJL††† —/ 60,000 HJM†††—/ 90,000 HJN††† —/120,000 HJD 82 HJE 81 HJF 80 HJG 82 HJH 81 HJK 80 HJL 81.2 HJM 81.4 HJN 82.4 HJD 15-45 HJE 35-65 HJF 50-80 HJG 15-45 HJH 35-65 HJK 50-80 HJL 20-50 HJM 30-60 HJN 40-70
3.5 3.5 1.0 1/ 2
3.5 3.5 1.0 1/ 2
HJD/E/F007 195 HJD .113...33 HJE .113...33 HJF .129...30 — — — — — — HJD .089...43 HJE .089...43 HJF .104...37 — — — — — — .14 .14 HJD|| 50,000/ 72,000 HJE|| 82,000/115,000 HJF|| 120,000/150,000 — — — — — — HJD 82 HJE 81 HJF 80 — — — — — — HJD 15-45 HJE 35-65 HJF 50-80 — — — — — — 3.5 3.5 1.0 1/ 2
450 ± 50 428 320 7±3 22 ± 5 30 ± 5 45 ± 5 Cleanable 1...20 x 24 x 1 Throwaway 2...16 x 25 x 2 ||Three-phase standard models have heating inputs as shown. Single-phase standard models have one-stage heating with heating input values as follows: HJD005-006,HJE004 — 72,000 Btuh HJE005-006,HJF004 — 115,000 Btuh HJF005-006 — 150,000 Btuh ***California compliant three-phase models. †††California SCAQMD compliant low NOx models have combustion products that are controlled to 40 nanograms per joule or less.
Performance data (cont) SOUND POWER (TOTAL UNIT) ARI OCTAVE BANDS A-WEIGHTED RATING (db) 63 125 250 500 1000 2000 (Bels) 7.6 76.0 55.9 66.0 64.0 66.2 68.4 64.5 004,005 8.0 80.0 59.1 68.9 68.7 71.9 74.0 68.9 006,007 8.2 82.0 62.2 69.3 71.5 74.7 76.2 72.9 008,009 8.4 84.0 64.6 71.1 73.3 76.9 77.6 73.7 012 8.6 86.0 63.7 69.9 72.5 78.2 81.1 77.3 014 UNIT 48HJ
4000 8000 61.7 65.7 68.7 70.6 73.3
57.3 59.0 61.5 63.7 66.8
LEGEND ARI — Air Conditioning and Refrigeration Institute Bels — Sound Levels (1 bel = 10 decibels)
ACCESSORY ECONOMIZER STATIC PRESSURE DROP (in. wg) 48HJ004-007 UNIT Durablade
900 0.05
1200 0.05
1400 0.05
CFM 1800 0.05
1600 0.05
2000 0.05
2200 0.05
2400 0.05
2600 0.05
ACCESSORY ECONOMIZER STATIC PRESSURE DROP (in. wg) 48HJ008-014 UNIT Durablade
2200 0.02
2500 0.02
3000 0.03
CFM 4000 0.05
3500 0.04
4500 0.06
5000 0.07
5500 0.08
6000 0.09
ACCESSORY/FIOP ECONOMI$ER2 STATIC PRESSURE* (in. wg) — 48HJ004-007 CFM
COMPONENT
1250 0.045 —
Vertical EconoMi$er2 Horizontal EconoMi$er2
1500 0.065 —
48HJ004-014
LEGEND FIOP — Factory-Installed Option
1750 0.08 0.1
2000 0.12 0.125
2250 0.145 0.15
2500 0.175 0.18
2750 0.22 0.225
3000 0.255 0.275
*The static pressure must be added to external static pressure. The sum and the evaporator entering-air cfm should be used in conjunction with the Fan Performance tables to determine indoor blower rpm and watts.
ACCESSORY/FIOP ECONOMI$ER2 STATIC PRESSURE* (in. wg) — 48HJ008-014 COMPONENT Vertical EconoMi$er2 Horizontal EconoMi$er2
2250 0.06 —
2500 0.075 0.1
2750 0.09 0.125
3000 0.115 0.15
LEGEND FIOP — Factory-Installed Option
UNIT NOMINAL TONS
004 005 006 007 008 009 012 014
3 4 5 6 71/ 2 81 / 2 10 121/2 LEGEND
FIOP — Factory-Installed Option
166
3500 0.15 0.21
CFM 3750 4000 0.17 0.195 0.25 0.275
4250 0.22 0.3
4500 0.25 0.34
4750 0.285 0.388
5000 0.325 —
5250 0.36 —
6250 — —
*The static pressure must be added to external static pressure. The sum and the evaporator entering-air cfm should be used in conjunction with the Fan Performance tables to determine indoor blower rpm and watts.
FIOP MOISTUREMI$ER™ DEHUMIDIFICATION PACKAGE STATIC PRESSURE DROP (in. wg) UNIT SIZE 48HJ
3250 0.13 0.18
300 .04 .07 .09 .12 .08 .10 .08 .11
CFM PER TON 400 .07 .12 .15 .20 .13 .15 .13 .18
500 .09 .15 .21 .28 .18 .22 .18 .26
EVAPORATOR-FAN MOTOR EFFICIENCY UNIT SIZE 48HJ 004,005 006 007 008,009 012 014
EFFICIENCY% 75 74/84* 84 80 85 87
*Single phase/3 phase. NOTE: Convert bhp to watts using the following formula: bhp (746) watts = motor efficiency
Physical data MODEL FA4B FB4B FC4C* SHIPPING WT (Lb) FA FB/FC REFRIGERANT METERING DEVICE PISTON SIZE TXV SIZE † COIL Rows and Fins Per In. Face Area (Sq Ft) Configuration FAN Air Discharge CFM (Nominal) Motor Hp (PSC) FILTER‡
018 018 — 92 96
024 024 024 100
030 030 030 117
036 036 036 118
042 042 042 137
048 048 048 150
060 060 060 167
— — 054 —
— 070 070 —
112
120
127
146
157
175
—
201
55 —
63 2 ton
— 4 ton
101 5 ton
2 and 14.5
3 and 14.5
3 and 14.5
3 and 14.5
3 and 14.5
3 and 14.5
3 and 14.5
3 and 14.5
3 and 14.5
2.23 Slope
2.23 Slope
2.97 Slope
2.97 Slope
3.46 Slope
4.45 A
5.93 A
7.42 A
7.42 A
1100 1300 1/3** 1/3 21-1/2 x 16-3/8
1500 1/2
1700 3/4 21-1/2 x 19-7/8
2000 3/4
1700 2000 1/2 3/4 21-1/2 x 23-5/16
650 850 1/5** 1/4 21-1/2 x 13
Bypass AccuRater (FA4B, FB4B); TXV Factory Installed on FC4C 70 76 84 88 96 2-1/2 ton 3 ton 3 ton 4 ton 5 ton
Fan coil units with hard shut-off TXV may require compressor hard start components. Refer to outdoor unit specifications. FC4C factory-installed TXV is hard shut-off, bypass flow-type for heat pump application. Filter must be field supplied for FA4B units. (See Accessory Kits.) FA4B018 fan coil has a 1/10 Hp motor FA4B030 fan coil has a 1/4 Hp motor NOTE: Descriptions and dimensions apply to all versions (FA4B, FB4B, FC4C, etc.), unless otherwise specified. * † ‡ **
Cabinet configuration options 018
024
030
036
042
048
060
054
070
FA4B
1-piece
1-piece
1-piece
1-piece
1-piece
1-piece
1-piece
—
—
FB4B
1-piece
1-piece
1-piece
1-piece
1-piece or Modular
1-piece or Modular
1-piece or Modular
—
Modular
FC4C
—
1-piece
1-piece
1-piece
1-piece
1-piece
1-piece
Modular
Modular
SIZE MODEL
6
FACTORY-INSTALLED HEATER OPTIONS** MODEL
018
024
030
036
042
048
FA4BNF
5, 8, 10
5, 8, 10
5, 8, 10, 15
5, 8, 10, 15
8, 10, 15
8, 10, 15
060 10
FA4BNC*
5, 8, 10
5, 8, 10
5, 8, 10
5, 8, 10
8, 10
8, 10
10
FB4BNF
5, 8, 10
5, 8, 10
5, 8, 10, 15
5, 8, 10, 15
8, 10, 15
8, 10, 15
10
* Includes factory-installed disconnect ** For field-installed heater/fan coil combinations, see Accessory electric heaters on pg. 11.
FAN COIL ELECTRICAL DATA (UNITS WITHOUT ELECTRICAL HEAT) BRANCH CIRCUIT
FLA‡
MIN CKT AMPS
Min Wire Size Awg*
Fuse Amps
208/230
1.5
1.9
14
15
208/230
1.8
2.3
14
15
030
208/230
2.4
3.0
14
15
036
208/230
2.7
3.4
14
15
042, 054
208/230
2.9
3.7
14
15
UNIT SIZE
VOLTS (1 PHASE)
018 024
048
208/230
4.3
5.4
14
15
060, 070
208/230
5.4
6.8
14
15
070
208/230
5.2
6.5
14
15
* Use copper wire only. Use 75°C only in this application. When using non-metallic (NM) sheathed cable, wire size required should be based on that of 60°C conductors, instead of wire sizes shown in table above per NEC Article 336-26. ‡ Based on FB4B. FLA — Full Load Amps NOTE: If branch circuit wire length exceeds 100 ft, consult NEC 215-2 to determine maximum wire length. Use 2% voltage drop.
ELECTRIC HEATER INTERNAL PROTECTION* HEATER KW
FUSE QTY/SIZE
PHASE
CKT BKR QTY/SIZE†
3
1
—
—
5
1
—
1/60
8
1
—
1/60
10
1
—
1/60
15
1
2/30 — 2/60
2/60
20
1
4/60
2/60
24
3/1
6/60
—
30
3/1
6/60
—
9
1/3
—
—
15
3
—
—
18
3
—
—
* 5-, 8-, 10-kw factory-installed heat has no internal protection. 15-kw factory-installed heat is internally protected with fuses. † Circuit breakers are 2 pole.
ESTIMATED SOUND POWER LEVEL (dBA) CONDITIONS UNIT SIZE
CFM
Ext Static Pressure
OCTAVE BAND CENTER FREQUENCY* 63
125
250
500
1000
2000
4000
FA, FB, FC-018
600
0.25
64.7
60.7
56.7
53.7
51.7
49.7
45.7
FA, FB, FC-024
800
0.25
66.0
62.0
58.0
55.0
53.0
51.0
47.0
FA, FB, FC-030
1000
0.25
67.0
63.0
59.0
56.0
54.0
52.0
48.0
FA, FB, FC-036
1200
0.25
67.8
63.8
59.8
56.8
54.8
52.8
48.8
FA, FB, FC-042
1400
0.25
68.4
64.4
60.4
57.4
55.4
53.4
49.4
FA, FB, FC-048
1600
0.25
69.0
65.0
61.0
58.0
56.0
54.0
50.0
FA, FB, FC-060
2000
0.25
70.0
66.0
62.0
59.0
57.0
55.0
51.0
FA, FB, FC-070
2000
0.25
70.0
66.0
62.0
59.0
57.0
55.0
51.0
* Estimated sound power levels have been derived using the method described in the 1987 ASHRAE HVAC Systems & Applications Handbook, Chapter 52, p. 52.7.
12