engineering bulletin - trane · engineering bulletin rlc-prb009-en ... 350 std 77.0 72.0 375 std na...

EngineeringBulletin

RLC-PRB009-EN

Sound Data and Application Guide

For the New and Quieter Air-Cooled

Series R™ Chiller

Model RTAC

140-500 Tons (60 Hz)

140-400 Tons (50 Hz)

©2002 American Standard Inc. All rights reserved. RLC-PRB009-EN

Introduction

The New, Quieter Air CooledSeries R™ Chiller – Model RTAC

The sound levels of the air-cooledSeries R™ Model RTAA chillers havebeen steadily improved since theirintroduction in 1990. With the advent ofthe Model RTAC, sound levels arereduced significantly by addressingthree major sources: the compressor, therefrigerant piping, and the condenserfans.

The compressor has been designed tominimize sound at its point of creation.This was accomplished by conductingfinite element analysis on thecompressor housing to find areas thatwould amplify the frequencies generatedfrom compression. These areas werethen redesigned to reduce soundtransmission.

The refrigerant components and pipinghave been optimized to reduce vibrationand sound propagation throughout thesystem.

Another source of sound originates fromthe condenser fans. Fan sound powercan be as much as half of the overall unitsound power levels. Carefulconsideration was taken when designingand selecting the next generationcondenser fans to be engineered into theModel RTAC. The sound levels achievedon the Model RTAC represent the lowestsound levels ever on Trane air-cooledscrew compressor water chillers.

When installing any chiller, forethoughtshould be given to the chiller and itsrelationship with the structure. Issuessuch as sound and vibration should beconsidered and factored into thebuilding design and chiller locationwithin a given structure. These issuesare not unique to chillers but should beconsidered when any mechanical deviceis located in or on a structure.

This bulletin is not intended to be areplacement for a sound consultant, butrather a tool for you to advise owners,engineers and contractors of useful tipswhen designing and installing chillerinstallations. This engineering bulletinprovides guidelines for addressing bothunit location and airborne sound wheninstalling air-cooled Series R™ chillers.

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Contents

RLC-PRB009-EN

Introduction

Contents

Unit Location

Ground Level Equipment

Roof-Mounted Equipment

Airborne Noise

Sound Levels

Appendix A

Appendix B

2

3

4

4

4

7

8

16

18

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UnitLocation

Outdoor HVAC equipment must belocated to minimize noise and vibrationtransmission to the occupied spaces ofthe building structure it serves. Also, theequipment must be located to preventobjectionable noise levels at adjacentproperty lines or building structures.When choosing a location for theequipment, consider the followingapplication material for both groundlevel and roof mounted equipment.

An additional concern for the designer isthe resulting noise level at adjacentproperty lines. When commercial sizeequipment is installed near a residentiallot line, there is potential for a soundproblem. In this situation, the problem isnot the commercial equipment butrather locating the equipment too closeto a quiet zone! For equipment operatingadjacent to residential areas, zoneordinances require maximum lot linedBA levels of 50-55/45 (day/night). Incommercial areas 60-65/55-60 (day/night). In industrial areas typical levelsmandated by local code authorities are65-70/65-70 (day/night). The reader iscautioned that the foregoing valueslisted are those typically seen acrossmajor cities of the U.S. The requirementsvary by locality so the designer iscautioned to always check thecriteria and local requirementsbefore selecting equipmentlocations

A. Ground Level Equipment1. If the equipment must be located in

close proximity to a building, it shouldbe placed next to an unoccupied spacesuch as a storage room, mechanicalroom, switch gear/electrical room orother typically unoccupied space. It isnot recommended to locate theequipment near occupied, soundsensitive areas of the building or nearwindows. Also, do not locate theequipment adjacent to other buildingwalls or large objects which mayreflect the sound back to the soundsensitive receiver.

2. Seal all piping and electrical conduitpenetrations in the building envelopewith an approved fire safe sealant.Utilize insulated, dielectricallycompatible sleeves at wallpenetrations to properly support thepiping and provide vibration damping.Provide flexible couplings andvibration isolators for the watercirculating pump and connections toprevent the transmission of soundthroughout the building.

3. Install the unit on a pad isolated fromthe building or install the unit withproper vibration isolation underneaththe unit to prevent machine vibrationsfrom being transmitted to thestructure of the building.

B. Roof Mounted Equipment

1. Roof Location

• The single most effectiverecommendation to prevent soundproblems within a building is to locatethe unit over non-critical areas such ascopy rooms, restrooms, storagerooms, and other similar non-occupiedareas of the building. It is notrecommended to locate a unit directlyover or in close proximity to soundsensitive areas such as conferencerooms, executive office spaces,libraries, etc.

• It is not recommended to locate theequipment near occupied, soundsensitive areas of the building or nearwindow glass. Also, do not locate theequipment adjacent to other buildingwalls or large objects which may reflectthe sound back to the sound sensitivereceiver.

2. Building Structure

• When mounting the chiller on theroofline, it is not recommended tolocate the unit on a beam or structureat mid-span of the column grid. Rather,directly support the unit over columns.Nor is it recommended to locate theunit in the middle of a horizontal beam.Try to avoid large column spans. Thiswill minimize the roof deflectionvibration transmission.

• When directly mounting chillers onI-beams that are above the roofline andmounted to the building supportcolumns, there exists the potential for aresonant frequency at which higherthan normal vibration may betransmitted to the rest of the building.Be cognizant of this application. Aconsultant may be required forevaluation.

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Building Support

PoorConcentration of equipment weightbetween beams causes excessive roofdeflection and vibration transmission,even for isolated equipment.

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GoodFurther addition of housekeeping padand additional beams add mass andstiffness to roof.

Very GoodA column directly under the equipmentgives the roof a very high local stiffness,but some equipment vibration stillenters the roof slab.

When directly mounting chillers on I-beams (at the roofline) that are mounted to thebuilding, support columns potentially can transmit higher than normal vibration at aresonant frequency to the rest of the building. The following drawing depicts whattype of prevention methods can be taken.

3. Base• It is not recommended to bolt down

vibrating equipment directly tofoundation without using isolators.

• Install the unit upon an inertia base orconcrete pad structure with vibrationisolation to match the characteristics ofthe roof structure. Beware oflightweight roof structures which aredifficult to isolate from vibration.

• Use an inertia base or solid concretepad as a base for the chiller. This mass,properly supported, will maximizevibration dampening and help preventnoise from penetrating through theroof directly below the unit. Floors andceiling should be concrete slabs.

4. Isolators• Isolate chiller on ELASTOMERIC

isolators. Originally intended forreciprocating compressors, springisolators are not as effective atabsorbing movement and vibration onair-cooled Series R chiller installations.This is because air-cooled Series Rchillers have higher frequency vibration(900 Hz) than reciprocating chillers (lessthan 125 Hz).

• Isolate the unit on elastomeric isolatorsselected to match the characteristics ofthe roof structure. It is not

recommended that equipment beapplied to buildings with a lightweightroof structure unless column supportsare provided which are independent ofthe roof structure.

5. Chilled Water Piping• Provide flexible couplings and vibration

isolators for the water circulating pumpconnections to prevent thetransmission of sound throughout thebuilding.

• Isolate chilled water piping from thechiller with ELASTOMERIC vibrationeliminators. Metal braided eliminatorshave proven to be much less effectivethan elastomeric isolators in reducingvibration transmission to the buildingthrough the piping.

• Isolate pipe hangers withELASTOMERIC isolators. This reducesvibration transmission to the building.Do not let the chiller support the weightof the chilled water piping. Isolatingpipe hangers this way reducesvibration transmission to the building.

6. Electrical• Electrical connections to the chiller

should be in flex conduit. Hardelectrical conduit is another vibrationpath that should be eliminated in chillerinstallations.

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7. Sealing Penetrations• Seal all piping and electrical conduit

penetrations in the building envelopewith an approved fire safe sealant.Utilize insulated, dielectricallycompatible sleeves at wall penetrationsto properly support the piping andprovide vibration damping.

• Acoustically treat all wall penetrations(piping, conduit, duct, outdoor vents,etc.)

Sound PressureTable 1 gives the overall A-weightedsound pressure levels for the air-cooledSeries R™ chiller. Information given inthis bulletin along with the data in Table1 may be used to estimate the soundpressure levels of common installations.Estimations made using this bulletin areconsidered typical of what may bemeasured in a free field with a hand-heldsound meter, in the absence of a nearbyreflective surface.

UnitLocation

Sound power octave band data aregiven in Appendix 1. Acousticalconsultants may require the data inAppendix 1 to perform a detailedacoustical analysis. Acoustical analysismay also be done using the TraneAcoustics Program (C.D.S.).

Note: The sound power data inAppendix 1 cannot be compared directlyto SOUND PRESSURE data given inTable 1 above.

Table 1 — Sound Pressure Levels Series R™ Air-Cooled Chiller

Unit Size A-Weighted Sound Pressure Level, dBA, ref 20 micro PaRTAC 60 Hz @ 30 ft 50 Hz @ 10 m

140 STD 72.0 68.0155 STD 73.0 69.0170 STD 74.0 69.0185 STD 74.0 70.0200 STD 75.0 71.0225 STD 75.0 NA250 STD 75.0 71.0275 STD 76.0 72.0300 STD 76.0 73.0350 STD 77.0 72.0375 STD NA 73.0400 STD 78.0 74.0450 STD 78.0 NA500 STD 78.0 NA140 HIGH 73.0 69.0155 HIGH 74.0 69.0170 HIGH 74.0 70.0185 HIGH 75.0 71.0200 HIGH 75.0 71.0225 HIGH 75.0 NA250 HIGH 75.0 71.0275 HIGH 76.0 72.0300 HIGH 77.0 73.0350 HIGH 77.0 73.0375 HIGH NA 74.0400 HIGH 78.0 74.0

Note: 30 ft or 10 m is measured from the side of the chiller. Sound radiation at this distance will approximate a line noisesource.

Sound measurements taken closer than30 ft/10 m may be greatly distorted dueto the large chiller lengths and multiplenoise sources within the chiller.

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UnitLocation

Noise Control of Air-Cooled

Series R™ Chillers

Three techniques are available for takingfull advantage of the sound properties ofthe air-cooled Series R™ chiller andminimizing the potential for noiseproblems. These are:

• Unit orientation

• Distance factor

• Sound attenuation through use ofbarrier walls

Unit OrientationThe air-cooled Series R™ chillers sound isdirectional in nature, allowing thecontractor/engineer to position the unitto minimize potential noise problems.The chiller may be oriented such that thecontrol box end or end opposite thecontrol box faces the direction where anoise problem is expected; refer toFigure 1.

Figure 1 – Orientation of the Chiller to Minimize Noise Problems

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Table 2 — Sound Pressure Levels End Opposite Control Box



Table 3 — Sound Pressure Levels Control Box End



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Figure 2 – Sound Attenuation Due to Distance

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Note: Top Curve and Axis for 50 Hz UnitsBottom Curve and Axis for 60 Hz Units

Note: Sound measurements taken closer than 30 ft/10 m may be greatly distorted when compared to an estimation made usingTable 1 and Figure 2 due to large chiller lengths and multiple noise sources within the chiller.

Note: Beyond 100 ft or 30 meters, the sound pressure will continue to decrease 5 dBA for each doubling of the distance from theunit to the place of measurement. For example, the sound pressure at 200 ft will be 5 dBA lower than the sound pressure at 100 ft.

Distance FactorThe distance between a source of sound and the receiver or place of sound measurement plays an important part in minimizingpotential noise problems. Figure 2 gives the reductions in sound pressure level, dBA based on increasing distance from the chiller.Sound levels at a specific location can be minimized by correctly orienting the chiller (see Figure 1) and placing the chiller as faraway from the location as possible (see Figure 2).

RLC-PRB009-EN10

UnitLocation

Sound Attenuation Using Barrier WallsReciprocating chillers are characterizedby a low frequency pounding sound thatis typically difficult to attenuate. Thedirect drive Series R™ compressor andcondenser fans have a medium and highfrequency characteristic that may beattenuated with simple, inexpensivebarrier walls.

A barrier wall constructed to only ½ inchexterior grade plywood gives a dramatic10 dBA reduction in sound. Refer toFigure 3 for minimum wallrequirements. Solid walls of brick orother more robust outdoor materials areequally acceptable and can be expectedto give better attenuation. Masonry blockwalls with special sound absorbingcavities should be considered for criticalapplications.

A minimum distance of 4 ft isrecommended, but the chiller may beplaced closer than 4 ft to a barrier wall.Some loss of performance will occur.Refer to Trane engineering bulletinRLC-PRB004-EN.

Louvered panels or decorative walls withany amount of open area should not beused to attenuate sound. They have littleor no sound reflecting or attenuatingbenefit. Also, an insulated sheet metalbox covering the compressors alone willprovide minimal sound attenuation andis not recommended.

Figure 3 – Suggested Barrier Wall for Sound Attenuation

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UnitLocation

Figure 4 – Installation ExampleAn ExampleAn example will demonstrate how touse the preceding information tominimize potential problems for noisesensitive installations. For purposes ofthis example, assume that theinstallation is represented by Figure 4.The objective is to design an installationthat will yield 65 dBA or less at the lotline.

The estimation of sound pressure at thelot line is made as follows:

75 dBA – from Table 1, sound pressure@ 30 ft for RTAC 200 STD @ 60 Hz

- 4 dBA – Deduct 4 dBA because ofchiller orientation from Figure 1, @80 ft

- 5 dBA – Deduct 5 dBA due to distancefactor from Figure 2, @ 80 ft

+3 dBA – Addition of 3 dBA due to soundreflection of building wall 12 ft fromchiller1

69 dBA – Estimated Sound Pressure atthe lot line (with no barrier wall)

69 dBA exceeds the requirement of 65dBA at the lot line. An acousticalbarrier wall as shown in Figure 3 willreduce the sound pressure anadditional 10 dBA, to 59 dBA, thusmeeting the requirement.

69 dBA – Estimated sound power at thelot line with no barrier wall

-10 dBA – Reduction due to acousticalbarrier wall

59 dBA – Estimated Sound Pressure atthe lot line with a barrier wall.

1Note that a building wall in closeproximity to the unit, 15 ft or less, reflectsthe sound towards the lot line. In effectthis causes the building to act like asecond sound source raising themeasured sound at the lot line by asmuch as 3 dBA.

Building Upper Story Sound ProblemsAir-cooled chillers are sometimesinstalled adjacent to and below theoccupied space of larger buildings,where the noise sensitivity of the upperstories of the building may be a concern.Once again, use of an acoustical barrierwall can be very effective. Refer toFigure 5.

The acoustical barrier wall placed asshown in Figure 5 attenuates bothcompressor and fan noise and will yieldan estimated 10 dBA sound pressurereduction in the “shadow” area createdby the wall. In order to create the largestpossible “shadow” area, the acousticalbarrier wall should be as tall as possible,with the unit placed as close as possible

to the barrier wall and the unit placed asfar from the building as possible. Theunit should be located a minimum of15 ft from the building to minimize thepotential for reflected sound. Also sealany electrical or water assemblies thatpenetrate the barrier wall to avoid“sound leaks” towards the building.Refer to Figure 3 for minimumconstruction requirements of barrierwalls.

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Figure 5 – Use of Attenuation for Upper Story Building Sound Problems

Acoustical Fan Discharge StacksUse of acoustical fan discharge stacks bythemselves will produce only marginalsound attenuating benefits. It isimportant to remember that both thecompressors and the fans contribute tothe sound of the air-cooled Series R™

chiller. Compressor noise is notattenuated by a fan discharge stack anda locally built and installed acoustical“box” around the compressors is not aneffective means of compressor soundattenuation.

However, acoustical fan discharge stackscan be used with an acoustical barrierwall. Selection and installation ofacoustical fan discharge stacks must bedone by a competent acousticalengineer in order to be effective.

Please note that chiller performance isadversely affected by the use ofacoustical fan discharge stacks. Refer toFigures 6 through 8. The length andopen area of acoustical fan dischargestacks must be designed to produce nomore than 0.5 inch of additional staticpressure on the condenser fans. Alsonote that care must be taken to properlysupport discharge fan stacks againstsevere cross winds.

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Figure 6 – Static Pressure Capacity Reduction

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Static Pressure (in. Wg)

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Figure 7 – Static Pressure kW Increase


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Figure 8 – Static Pressure EER Decrease


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Appendix A

Sound Power Octave Band DataSound power octave band data can be used for purposes of describing the basic acoustical properties of the air-cooled Series R™

chiller. However, there are two cautionary notes. First, if the engineer is using the data as a criteria in a bid evaluation, make surethat the data from all competitors is on an equal basis. Insist that all competitors present data terms of SOUND POWER (notsound pressure), in a consistent format, according to ARI Standard 370.

>>>Sound power data CANNOT be compared directly to sound pressure data. <<<

Second, the sound power data does not provide sufficient information to correctly position the chiller or attenuate its sound totake full advantage of the characteristics of the air-cooled Series R chiller. Unlike most reciprocating chillers that exhibit a lowfrequency, pounding sound, the air-cooled Series R chiller sound is directional in nature and has a higher frequency characteristicthat is more easily attenuated. The specific application information given in the preceding parts of this bulletin can be used tocreate a significant competitive advantage over competitive air-cooled reciprocating chillers.

NOTE: Sound Power Rating data given in Tables A-1 through A-2 may vary ± 2 dB in any specific octave band due to normalvariations in chiller construction.

Table A-1 (60 Hz) – Octave Band Sound Power Levels, dB ref, 1 pw

Octave Band & Center Frequency, Hz OverallModel RTAC 63 125 250 500 1000 2000 4000 8000 A’ Wtd

140 STD 101 102 98 97 96 91 86 83 100155 STD 102 102 98 98 97 93 86 83 101170 STD 102 103 99 99 98 94 87 84 102185 STD 102 103 99 100 98 93 87 84 102200 STD 103 104 100 101 98 93 88 85 103225 STD 103 104 100 101 98 93 88 85 103250 STD 104 104 101 101 98 94 88 85 103275 STD 104 105 101 101 100 95 89 86 104300 STD 105 105 101 102 100 95 90 87 104350 STD 105 106 102 103 100 95 90 87 105400 STD 106 107 103 104 101 96 91 88 106450 STD 106 107 103 104 101 96 91 88 106500 STD 107 107 104 104 101 97 91 88 106140 HIGH 102 103 99 98 97 92 87 84 101155 HIGH 102 103 99 99 97 93 87 84 102170 HIGH 103 104 99 100 98 94 87 85 102185 HIGH 103 104 100 100 98 94 88 85 103200 HIGH 104 104 100 101 98 93 88 86 103225 HIGH 104 104 100 101 98 94 88 85 103250 HIGH 104 105 101 102 99 94 88 86 103275 HIGH 105 105 101 102 100 96 89 86 104300 HIGH 105 106 102 103 100 95 90 87 105350 HIGH 106 107 102 103 101 97 90 88 105400 HIGH 107 107 103 104 102 96 91 89 106

Sound Power is a calculated quantity and cannot be measured directly like SOUND PRESSURE. Sound power is the amount of acoustical power produced at the source, and thus is anabsolute quantity and not dependent on the surrounding environment or distance, as is sound pressure. 32 measurements are taken over a prescribed area around the unit. Data isthen mathematically reduced to give the sound power level, dB.

Appendix A

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Appendix A

Table A-2 (50 Hz) – Octave Band Sound Power Levels, dB ref, 1 pw


140 STD 96 97 93 93 93 89 82 78 96155 STD 97 98 95 93 93 89 83 80 97170 STD 87 98 96 94 93 90 84 81 97185 STD 98 98 96 94 95 90 83 80 98200 STD 98 99 96 95 96 90 83 80 99250 STD 99 99 96 95 96 91 84 81 99275 STD 99 100 98 96 96 92 85 82 100300 STD 100 100 98 97 98 92 85 82 100350 STD 100 101 99 97 96 93 87 84 100375 STD 101 101 99 97 98 93 86 83 101400 STD 101 102 99 98 99 94 86 83 102140 HIGH 97 98 94 93 93 89 83 79 97155 HIGH 98 98 95 94 93 90 83 80 97170 HIGH 98 99 96 94 93 90 84 81 98185 HIGH 98 99 96 95 95 90 84 81 99200 HIGH 99 99 97 95 96 91 83 80 99250 HIGH 99 100 96 96 96 91 84 81 99275 HIGH 100 101 98 96 96 92 85 82 100300 HIGH 100 101 98 97 98 92 85 82 101350 HIGH 101 102 99 97 96 93 87 84 101375 HIGH 101 102 100 98 98 93 87 84 102400 HIGH 102 102 100 98 99 94 86 84 102


RLC-PRB009-EN18

Appendix B

Appendix B

Attenuation Option Information and Sound DataFor acoustically sensitive installations, compressor and fan noise are equallyimportant and should be addressed together to achieve optimal unit sound. TheRTAC was designed to have the sound balanced between the compressors and fans.Two options are available for applications needing further attenuation, theComprehensive Acoustic Solution and the Compressor Sound Enhancemnetpackage. NOTE: Attenuation of one component may adversely distort the sound ofthe other.

Comprehensive Acoustic SolutionThe Comprehensive Acoustic Solution consists of ultra quiet seven blade fans and anenclosure package that reduces the high-frequency, tonal compressor sound. Thecombination of condenser and compressor attenuation provides a noticeablereduction while keeping the unit sound balanced. Unit reliability and performance willnot be affected by the sound attenuation package. Unlike other industry units, theRTAC will not experience any capacity or efficiency decrease due to attenuating fansor compressors.

Compressor Sound EnhancementScrew compressors create most of their tonal sound at high-frequencies. Inapplications where the tonal qualities of screw compressors are the focus of noisereduction, compressor attenuation may be all that is required. The CompressorSound Enhancement package provides a weatherproof compressor enclosure andpiping wraps to reduce compressor sound levels, especially aimed at the highfrequencies. The 1-2 dBA sound reduction realized with the compressor soundenhancement package does not reflect the total attenuation achieved because thefans will then contribute more of the overall "A" weighted sound.

Table B-1 — Sound Pressure Levels 30 ft. From Side of ChillerA-Weighted Sound Pressure with Compressor Sound Enhancement

Unit Size Level, dBA, ref 20 micro PaRTAC 60 Hz @ 30 ft 50 Hz @ 10 m

140 STD 71 66155 STD 71 67170 STD 72 67185 STD 73 68200 STD 73 68225 STD 73 NA250 STD 73 69275 STD 74 69300 STD 74 70350 STD 75 70375 STD NA 71400 STD 76 71450 STD 76 NA500 STD 76 NA140 HIGH 71 67155 HIGH 72 68170 HIGH 73 68185 HIGH 73 68200 HIGH 73 69225 HIGH 73 NA250 HIGH 74 69275 HIGH 74 70300 HIGH 75 70350 HIGH 76 71375 HIGH NA 71400 HIGH 76 72

Note: 30 ft or 10 m is measured from the side of the chiller. Sound radiation at this distance will approximate a linenoise source.

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Appendix B

Table B-2 — Sound Pressure Levels End Opposite Control BoxA-Weighted Sound Pressure with Compressor Sound Enhancement



Table B-3 — Sound Pressure Levels Control Box EndA-Weighted Sound Pressure with Compressor Sound Enhancement



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Appendix B

Table B-4 — Sound Pressure Levels 30 ft. From Side of ChillerA-Weighted Sound Pressure with Comprehensive Acoustic Solution



Note: 30 ft or 10 m is measured from the side of the chiller. Sound radiation at this distance will approximate a linenoise source.

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Appendix B

Table B-5 — Sound Pressure Levels End Opposite Control BoxA-Weighted Sound Pressure with Comprehensive Acoustic Solution



Table B-6 — Sound Pressure Levels Control Box EndA-Weighted Sound Pressure with Comprehensive Acoustic Solution



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Table B-7 (60 Hz) — Octave Band Sound Power Levels, dB ref, 1 pw WITH COMPREHENSIVE ACOUSTIC SOLUTION




Table B-8 (50 Hz) — Octave Band Sound Power Levels, dB ref, 1 pw WITH COMPREHENSIVE ACOUSTIC SOLUTION


140 STD 86 91 91 89 86 85 78 72 92140 HIGH 86 91 92 89 87 85 78 73 92155 STD 86 91 93 89 87 86 79 74 92155 HIGH 86 92 93 90 87 86 79 74 93170 STD 85 91 94 90 87 86 80 75 93170 HIGH 85 92 95 90 87 86 80 75 93185 STD 84 92 94 90 88 86 79 74 93185 HIGH 85 92 95 91 88 87 80 75 94200 STD 84 92 94 91 89 87 79 74 94200 HIGH 84 93 95 91 89 87 79 74 94250 STD 87 93 94 91 89 88 80 74 94250 HIGH 87 93 95 92 89 88 80 75 95275 STD 86 93 96 92 89 88 81 76 95275 HIGH 87 94 96 92 90 88 81 77 95300 STD 86 94 96 92 91 89 80 75 96300 HIGH 86 94 96 93 91 89 81 76 96350 STD 88 94 97 93 90 89 83 78 96350 HIGH 88 95 98 93 90 89 83 78 96375 STD 88 95 97 93 91 90 82 77 96375 HIGH 88 95 98 94 91 90 83 78 97400 STD 87 95 97 94 92 90 82 77 97400 HIGH 87 96 98 94 92 90 82 77 97


Appendix B

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Appendix B

Table B-9 (60 Hz) — Octave Band Sound Power Levels, dB ref, 1 pw WITH COMPRESSOR SOUND ENHANCEMENT




Table B-10 (50 Hz) — Octave Band Sound Power Levels, dB ref, 1 pw WITH COMPRESSOR SOUND ENHANCEMENT


140 STD 96 97 93 92 89 86 81 78 94155 STD 97 98 94 92 90 87 82 79 95170 STD 97 98 95 93 90 87 82 79 95185 STD 98 98 95 93 91 88 82 79 96200 STD 98 99 96 94 91 88 82 79 96250 STD 99 99 96 94 92 89 83 80 97275 STD 99 100 97 95 92 89 84 81 97300 STD 100 100 97 95 93 90 84 81 98350 STD 100 101 98 96 93 90 85 82 98375 STD 101 101 98 96 94 91 85 82 99400 STD 101 102 99 97 94 91 85 83 99140 HIGH 97 98 93 93 90 87 82 79 95155 HIGH 98 98 95 93 90 87 82 79 96170 HIGH 98 99 96 93 91 88 83 80 96185 HIGH 98 99 96 94 91 88 83 80 96200 HIGH 99 99 96 94 92 88 83 80 97250 HIGH 99 100 96 95 92 89 84 81 97275 HIGH 100 100 97 95 93 90 84 82 98300 HIGH 100 101 98 96 94 90 84 82 98350 HIGH 101 102 99 96 94 91 86 83 99375 HIGH 101 102 99 97 94 91 86 83 99400 HIGH 102 102 99 97 95 91 86 83 100


Literature Order Number

File Number

Supersedes

Stocking LocationTraneA business of American Standard Companieswww.trane.com

For more information contact your local districtoffice or e-mail us at [email protected]

Trane has a policy of continuous product and product data improvement and reserves the right to changedesign and specifications without notice.

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