Compressor Evaluation CHERRY CREEK RESERVOIR AERATION ...

Cherry Creek Reservoir Aeration Compressor Evaluation

EATON Energy Solutions Group 1 2/29/12

CHERRY CREEK

RESERVOIR AERATION

SYSTEM

GREENWOOD VILLAGE,

CO

Aeration Compressor Evaluation

6/28/2012 Cherry Creek Reservoir Aeration System, Greenwood Village, CO

Electrical Sector Eaton’s Electrical Services & Systems Energy Solutions Group 143 Union Blvd, Suite 350 Lakewood, CO 80228 tel: 303-974-1200 fax: 303-974-1239

This report has been prepared to present the results of our analysis

of the operation of the air compressor serving the aeration system at

the Cherry Creek Reservoir. The report addresses findings and

potential solutions.



DISCLAIMERS

This report has been prepared at the request of the client, and the observations, conclusions, and

recommendations contained herein constitute the opinions of Eaton Energy Solutions, Inc. In preparing

this report, Eaton Energy Solutions has relied on some information supplied by the client, the client’s

employees, and others which we gratefully acknowledge. Because no warranties were given with this

source of information, Eaton Energy Solutions cannot make certification or give assurances except as

explicitly defined in this report.



TABLE OF CONTENTS

1.1 EXECUTIVE SUMMARY ............................................................................................................ 4

1.2 ESTIMATES OF PROBABLE COST ........................................................................................ 6

1.3 OVERVIEW OF PROJECT......................................................................................................... 6

1.4 CONTACT INFORMATION ........................................................................................................ 7

1.5 BACKGROUND INFORMATION ............................................................................................... 8

1.6 AERATION SYSTEM ANALYSIS .............................................................................................. 9

1.7 COMPRESSOR INSTALLATION ANALYSIS ....................................................................... 12

1.8 ELECTRICAL DISTRIBUTION SYSTEM ANALYSIS .......................................................... 18

1.9 COMPRESSOR ROOM COOLING RECOMMENDATIONS .............................................. 19

1.10 COMPRESSED AIR DISTRIBUTION SYSTEM RECOMMENDATIONS ......................... 23

1.11 COMPRESSOR REPLACEMENT. ......................................................................................... 24

1.12 BIBLIOGRAPHY - DOCUMENTS FROM OWNER .............................................................. 25

1.13 BIBLIOGRAPHY – ATLAS COPCO DOCUMENTS ............................................................. 26

1.14 BIBLIOGRAPHY – PROJECT CONTACTS .......................................................................... 26

APPENDICES

APPENDIX A – CURRENT DIFFUSER LOCATIONS

APPENDIX B – PRESSURE DROP CALCULATIONS

APPENDIX C – ASHRAE CLIMATIC INFORMATION FOR LITTLETON, CO

APPENDIX D – COMPRESSED AIR HEAT GAIN CALCULATIONS

APPENDIX E – GREENHECK FAN SELECTIONS-VENTILATION SOLUTION

APPENDIX F – GREENHECK MAU SELECTION - EVAPORATIVE COOLING SOLUTION

APPENDIX G – GREENHECK MAU SELECTION - MECHANICAL COOLING SOLUTION

APPENDIX H – GREENHECK FAN SELECTIONS - MECHANICAL COOLING SOLUTION

APPENDIX I – INGERSOLL RAND COMPRESSOR SELECTIONS

APPENDIX J – ACOUSTICAL ANALYSIS

APPENDIX K – ESTIMATES OF PROBABLE COST



Cherry Creek Reservoir Aeration System, Greenwood Village, CO

A E R AT I O N C O M P R E S S O R E V AL U A T I O N

1.1 Executive summary

Problem Statement:

Existing air compressor has been shutting down due to overheating. The compressor also creates

intrusive noise in the surrounding park.

Approach:

To investigate the issues the client was experiencing, Eaton Energy Solutions performed the

following:

Reviewed original design documents prepared by AMEC.

Reviewed compressor manufacturer installation instructions and compressed air guidelines.

Spoke with compressor manufacturers’ representatives.

Collected pressure, temperature, and amperage data in the field.

Performed calculations to compare installed system to manufacturers requirements

Hired Acoustical consultant to analyze noise issue and propose solutions.

Created estimates of probable cost of proposed solutions.

Findings:

Since the existing compressor was only selected for 51 psig (54.4 psig maximum), design

airflow cannot be achieved at all outlets in zone 4.

A general requirement of any loading/unloading compressed air system is the presence of a

storage tank, or air receiver.

A shortcoming in the Cherry Creek reservoir compressed air system is the low delta between

upper and lower system pressures.

The required receiver volume to achieve a 30 second compressor cycle time is 4,874 gallons

resulting in a receiver volume shortage of 2,762 gallons.

From field measurements we have verified that adequate service clearance has been provided



Due to diminishing returns, it is impractical to attempt to cool the building with ventilation air

only, at outdoor temperatures above 93°F, and would not be possible to achieve indoor air

temperatures below 104°F for 100% of the year.

In conclusion, the compressor ventilation system is moving less air than design and at a higher

temperature. This is the main cause of the current compressor overheating.

The Water Quality Authority Board has documented positive results on the effect of the aeration

system on algae in the reservoir, and therefore does not want any solutions to interfere with the

distribution system or airflow rate to the reservoir.

The following table summarizes the actions required to be taken and the feasibility of each action

to continue providing the current aeration to the lake and to meet Atlas Copco’s minimum

installation and operation requirements for the existing compressor:

Issue Action Required Feasibility Compressor Jacket

Overheating

In order to maintain the compressor

running at an outdoor air

temperature of 104°F, either

evaporative or mechanical cooling is

required for the compressor building

This action is feasible, however does not

solve the low cycle time issue and needs

to be implemented in conjunction with a

measure that addresses the low cycle

time condition

Lower than

recommended cycle

time, 13 seconds vs. 30

seconds

Reduce pressure drop in piping

system

Not feasible, too intrusive on lake

aeration and can possibly change current

lake conditions

Install a 2,762 gallon receiver tank Feasible, however requires the

compressor building cooling solution to

also be implemented

Increase the current compressor

discharge pressure to at least 62 psig

Not feasible with current compressor

Conclusion:

The installation of a new compressor as detailed in section 1.9, would likely result in the highest

solution cost, however we believe this would solve both the ventilation and the minimum cycle time

conditions. The proposed compressor is rated by the manufacturer to operate at 115°F and at a

discharge pressure of 100 psig. The current compressor building louvers do not require any

modifications to allow for the appropriate compressor ventilation and the higher discharge

pressures will allow for a large load/unload delta which will increase the required cycle time

significantly above the minimum manufacturer’s requirements.



1.2 Estimates of probable cost

Option Estimate of Probable Cost A – Install Ventilation Fans & Receiver Tank

*WILL ONLY SAFEGUARD COMPRESSOR OPERATING CONDITIONS UP TO 93°F OUTDOOR AIR TEMPERATURE

$104,640.00

B - Install Evaporative Cooling MAU & Receiver Tank $146,784.00

C- Install Mechanical Cooling MAU, Fans, & Receiver Tank $165,490.00

D - Install New 100 HP, 100 psig compressor $157,130.00

FIGURE-16: ESTIMATES OF PROBABLE COST

(SEE APPENDIX K FOR DETAILS)

1.3 Overview of Project

Eaton Energy Solutions was engaged by the client to complete an evaluation of the aeration

compressor at Cherry Creek Reservoir. Specifically, the scope of this project will include the root cause

analysis of the aeration compressor overheating and the noise issues caused by the same compressor.



1.4 Contact Information

This Report Prepared For:

Cherry Creek Basin Water Quality Authority

6399 S Fiddlers Green Circle

Greenwood Village, CO 80111-9474

William P Ruzzo

303.985.1091

[email protected]

Terry Cunningham

303.350.0611

[email protected]

Ricardo J.F. Gonçalves

303.468.8484

This Report Prepared By:

EATON Energy Solutions, INC.

143 Union Blvd.

Suite 350

Lakewood, CO 80228

303.974.1200

Juan M. Moreno

Project Manager – Lead Designer

303.328.3412

[email protected]

Scott McQuoid

Project Engineer

303.328.3426

[email protected]

Andrew Grover

Design Team Leader

303.974.1216

[email protected]

Brian Bowyer

Sr. Electrical Engineer

303.328.3431

[email protected]

mailto:[email protected]








1.5 Background Information

Introduction

In order to evaluate the root causes for the aeration compressor overheating, the compressed air

distribution system has been analyzed. In addition, the compressor selected to serve this system as

well as the compressor installation has been evaluated. This was done through a combination of

calculations, manufacturer’s recommendations, and data collected in the field. Eaton Energy Solutions

subcontracted Shen Milsom & Wilke as acoustical consultants to evaluate the nuisance radiated noise

associated with the compressor. The existing electrical distribution service in the compressor building

was investigated to determine if adequate capacity existed for the various solutions presented.

Problem Statement

The Cherry Creek Basin Water Quality Authority completed construction of the aeration system in late

2007, and officially started the system in April of 2008. Since its initial startup, the compressor has

repeatedly shut down due to compressor jacket overheating. Consequently, the authority made

improvements to the ventilation system of the compressor building. This reduced shut downs from

overheating, but has not solved the problem. In addition, the compressor emits an unacceptable high

pitched whine which can be heard in the surrounding area.

Compressor Installation Parameters

The compressor installed is an Atlas Copco model# ZE3F350, the following information was provided

by the manufacturer:

Adequate clearance published by the manufacturer must be maintained for compressor

service and maintenance

The compressor can operate in ambient temperatures from 32°F to 104°F.

The compressor ventilation intake grids require 10,371 SCFM (12,507 ACFM) of air to serve

the compressor oil heat exchanger and aftercooler.

The compressor’s internal ventilation fans can handle a maximum of 0.12” wc of total external

static pressure.

Limit local air velocity to ventilation inlet grids to 16 fps.

The minimum pressure difference between the loading and unloading limits should be at least

0.6 bar or 9 psig.

An air receiver should be selected and installed to limit the number of loading cycles to 1

cycle per 30 seconds.

Compressor must be selected based on pressure drop calculations to ensure that adequate

pressure is available at all points in the aeration system.

The compressor specified and installed has a capacity of 455 SCFM at 51 psig, operating at

an elevation of 5,550 feet.



1.6 Aeration System Analysis

Reservoir Aeration Distribution System Analysis

The design documents for the aeration system were prepared by AMEC and published in October of

2006. These documents lay out the compressed air piping, as well as provide selections for the

compressor, diffusers, and accessories. Based on this layout of the distribution system (pipe sizes,

flow rates, accessories used) we were able to calculate the pressure drop from the compressor to the

furthest diffuser. The original 2006 design documents called for a total of (102) 9” Sanitaire LP

diffusers at 2.4 SCFM each, or 245 SCFM total. However, 14 additional diffusers were added in 2009,

to zones 1 & 4, for a total of 278.4 SCFM (See Appendix A for the diffuser layout provided by Cherry

Creek Basin Water Quality Authority). Corrected for altitude, this equals a total of 341 ACFM of Free

Air Delivery required at the compressor inlet. Figure 1 shows a rough schematic of the distribution

system:

FIGURE-1: SCHEMATIC OF COMPRESSED AIR DISTRIBUTION SYSTEM



Using Methodology outlined by Atlas CopCo, we were able to calculate expected pressure drops based

on the following formula for friction losses in straight lengths of pipe:

Where:

pressure drop (bar)

Airflow, FAD (l/s)

internal pipe diameter (mm)

length of pipe (m)

absolute initial pressure (bar(a))

The aeration system has (5) branches serving diffusers from a manifold near the northern end of the

reservoir. Figure 2 summarizes the total pressure drop for each branch, from the compressor outlet, to

the diffuser assembly:

Zone (As labeled on

2006

Drawings)

4” Main

Pressure

Drop

(psig)

Manifold to

Furthest Diffuser

Pressure Drop

(psig)

Pressure Drop

from Diffuser

assembly

(psig)

Static Water

pressure

(psig)

Total Pressure

Requirement

(psig)

1 1.73 18.44 7.91 7.80 35.88

2 1.73 22.48 7.91 8.67 39.06

3 1.73 26.34 7.91 9.54 45.52

4 1.73 46.92 7.91 10.40 66.96

5 1.73 33.05 7.91 9.97 52.65

FIGURE-2: AERATION SYSTEM PRESSURE DROP.

SEE APPENDIX B FOR CALCULATION DETAILS.

As seen in figure 2, in addition to the pressure needed to overcome piping friction, an additional 7.91

psig of pressure is needed to overcome the diffuser assembly. This is based on the assumption that

the AMEC regulator installed at each diffuser has a pressure drop of 7.25 psi, the lowest pressure drop

stated in the original design documents.

Since the existing compressor was only selected for 51 psig (54.4 psig maximum), design airflow

cannot be achieved at all outlets in zone 4.

It should be noted that these pressure drop calculations are based on the modified distribution system.

From the original design documents, the highest calculated pressure required is 51.93 psig, for zone 5.

The compressor installed at Cherry Creek Reservoir is a “load/unload” type. The principle of a

load/unload compressor relies on a distribution system that can operate between two pressure limits.

The upper and lower pressure limits (load and unload pressures) are programmed into the compressor.

The compressor first pressurizes the system to the upper pressure limit at which point, an unloading

valve closes and creates a vacuum at the compressor inlet while the motor continues to run. The

system pressure is then allowed to drop (in this case by supplying air to the reservoir diffusers) to the



lower pressure limit. Once this lower limit is reached, the unloading valve opens, starting the cycle

again. Atlas Copco recommends a minimum of 9 psig between the upper and lower pressure limits.

Part of EATON’s investigation included measuring the air pressure in the main compressed air delivery

pipe:

FIGURE-3: FIELD COLLECTED SYSTEM PRESSURE

DATA COLLECTED 11/09/2011 – 11/11/2011

From this plot, we can see the system pressure tends to vary between 49 and 55 psig. Per the

manufacturer, the maximum rated outlet pressure of the compressor is 54.4 psig.

Reservoir Aeration Air Receiver

A general requirement of any loading/unloading compressed air system is the presence of a storage

tank, or air receiver. The purpose is to ensure enough system volume is present to limit the number of

loading/unloading cycles, and therefore prolong the life of critical compressor components. In a

standard design, the operating pressure in the air receiver varies between the set upper and lower

limits, with a regulator supplying the main distribution system with the lower, constant pressure limit.

A shortcoming in the Cherry Creek reservoir compressed air system is the low delta between upper and

lower system pressures. Per the pressure drop calculations shown in figure 2, the compressed air

system’s lower limit should be 51.93 psi to comply with original design piping layout and 66.96 psi to

deliver 2.4 ACFM at each one of the original project diffusers and at each one of the diffusers added in

45

46

47

48

49

50

51

52

53

54

55

56

12

:00

:01

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:30

:21

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:00

:41

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:31

:01

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:01

:21

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:02

:01

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:32

:21

0:0

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:33

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:33

:41

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:34

:21

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:08

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:41

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9:0

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:09

:21

7:3

9:4

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:10

:01

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:40

:21

System Pressure at Compressor Outlet (psig)

SystemPressure atCompressorOutlet (psig)



2009. Per Atlas Copco, a minimum upper/lower pressure differential of 9 psi and a properly selected

receiver tank should result in a minimum compressor cycle time of 30 seconds. Currently the cycle time

is approximately 13 seconds and the pressure differential is approximately 4 to 6 psi.

We have calculated the SCFM being delivered by the compressor to be approximately 354 SCFM. Our

calculation is based on a measured bleed time of 13 seconds, 2112 gallons of air stored in the 4” main,

4 psi upper/lower pressure delta and an atmospheric pressure of 12 psi.

Per the equation below, taken from the U.S. Department of Energy (DOE) “Compressed Air Challenge”

sourcebook for the compressed air industry, a total receiver volume of 4,874 gallons would be required,

at the current operating conditions, to comply with the manufacturer’s 30 second compressor cycle time

The DOE has published the following method for sizing air receivers:

(Equation: 1)

Where:

Air Receiver Volume (cubic feet)

Bleed time allowed (minutes)

Air demand, cubic feet per minute

Absolute atmospheric pressure,

(psia)

Initial receiver pressure (psig)

Final receiver pressure (psig)

As stated above, the current 4” main pipe acting as a receiver tank for the system has a total volume of

2,112 gallons. The required receiver volume to achieve a 30 second compressor cycle time is 4,874

gallons resulting in a receiver volume shortage of 2,762 gallons.

1.7 Compressor Installation Analysis

Compressor Room Layout

Atlas Copco has published maintenance clearances that are required to be maintained around the

compressor. From field measurements we have verified that adequate service clearance has been

provided:



FIGURE-4: COMPRESSOR REQUIRED AND EXISTING CLEARANCES

Compressor Room Ventilation Analysis

Atlas Copco has established ambient environmental conditions that must be met in order for the

compressor to operate properly, as expressed in section 1.3. Most importantly:

The compressor can operate in ambient temperatures from 32°F to 104°F.

The compressor ventilation intake grids require 10,371 SCFM (12,507 ACFM) of air to serve

the compressor oil heat exchanger and aftercooler.

The compressor internal exhaust fans can handle a maximum of 0.12” wc of total external

static pressure.

Refer to the following schematic for temperatures referred to in the following section:



FIGURE-5: SCHEMATIC OF REFERENCE TEMPERATURES

According to ASHRAE climate data, the outdoor air temperature will reach 93°F or higher for 35 hours

every year (0.4% design condition). The 0.4% design temperature is the temperature that can be

anticipated at the reservoir for 0.4% of the hours in a year, according to ASHRAE data, see appendix B.

When the compressor is running, the ambient temperature in the compressor house will always be

greater than outdoor air temperature, due to the heat rejection from the compressor. In order to

maintain an ambient temperature below 104°F, an 11°F maximum increase in temperature (104°F-

93°F) of the ventilation air is allowed.

Since the exhaust is currently ducted to the outdoors, a certain amount of heat is directly removed from

the compressor house. This is equal to the heat removed from the compressed air aftercooler and oil

heat exchanger. See appendix D for details on this calculation. The remaining compressor heat is

equal to 148 MBH and needs to be removed by ventilation of the building enclosure.

The principle of removing heat from a space with air is to supply a mass flow rate of air capable of

removing a specific amount of heat. As the air passes through a space and removes heat, its

temperature increases. The high limit of this temperature before the mass of air is removed from the

space will equal the space temperature. This means that the space temperature will always be higher

than the temperature of the supply air in order to enable heat transfer from the space to the ventilation

air. The following chart illustrates the energy balance of the compressor house, assuming a ventilation

system with no mechanical cooling. The chart shows a temperature difference of 11°F at 12,545 ACFM.

At this condition, the compressor house ambient air temperature will be 104°F when the outdoor

temperature is 93°F. The temperature deltas were determined using a calculated total heat load in the

compressor house of 148.5 MBH, broken down as follows:

Load Component MBH

Compressor Load 148

Envelope Load 0.5

Total 148.5



FIGURE-6: ENERGY BALANCE GRAPH OF COMPRESSOR HOUSE AMBIENT AIR

Due to diminishing returns, it is impractical to attempt to cool the building with ventilation air only, at

outdoor temperatures above 93°F, and would not be possible to achieve indoor air temperatures below

104°F for 100% of the year.

0

5

10

15

20

25

30

35

40

0

10

,00

0

20

,00

0

30

,00

0

40

,00

0

50

,00

0

60

,00

0

De

la T

(F)

Air Flow (CFM)

Air Flow vs Delta T

Design Condition: Delta T = 11°F Required Airflow = 12,545



Currently, an approximately 16” diameter propeller fan is exhausting the compressor house:

FIGURE-7: EXISTING COMPRESSOR HOUSE EXHAUST FAN.

All the air entering the compressor house is being drawn thru (2) 29”x57” door louvers and (1) 15”x16”

louver above the door, as shown in the schematic below:

FIGURE-8: EXISTING VENTILATION SYSTEM SCHEMATIC



The air compressor internal exhaust fan is only capable of overcoming 0.12” wc of external static

pressure. This includes all pressure drops associated with moving air through the intake louvers,

ductwork, transitions, and exhaust louver. Using the exhaust air temperatures measured in the

field, we can perform another heat balance calculation to determine the exhaust air flow rate. This

assumes that 100% of the compressor motor energy has been transferred to the exhaust air.

FIGURE-9: FIELD MEASURED EXHAUST TEMPERATURES

DATA COLLECTED 11/09/2011 – 11/11/2011

OUTDOOR AIR TEMPERATURE DATA OBTAINED FROM

WEATHERUNDERGROUND.COM

0

20

40

60

80

100

120

T exhaust

T oa



FIGURE-10: ENERGY BALANCE GRAPH OF COMPRESSOR HOUSE EXHAUST AIR

From this analysis, we can conclude that a maximum of 8,975 of the required 12,507 ACFM of

ventilation air is currently being moved through the compressor. This is due to the limited external

static capacity of the compressor ventilation fan. In conclusion, the compressor ventilation system is

moving less air than design and at a higher temperature. This is the main cause of the current

compressor overheating.

1.8 Electrical Distribution System Analysis

The compressor facility is served by a 277/480V, 3-phase, 75 kilo-volt amps (kVA) pad-mounted

transformer from Xcel Energy. Feeders originating from the transformer are routed underground to the

utility CT cabinet enclosure mounted on the exterior of the building. The feeders are then tapped and

spliced with one feeder terminating in a 400 amp, 600 volt fused disconnect switch, with 250 amp fuses

and the other terminating in a 30 amp, 600 volt fused disconnect switch (fuse size not known). The 30

amp switch feeds a 480 – 120/240 volt, 1-phase, 10 kVA transformer. The fused switches and 10 kVA

transformer are located inside the compressor building.

The transformer feeds a 120/240 volt, 1-phase, 60 amp, eight (8) circuit panel board. The panel board

serves convenience outlets, lighting, the auto-dialer and exhaust fan. The disconnect switch serves the

compressor.

0

10

20

30

40

50

60

70

80

90

0

10

,00

0

20

,00

0

30

,00

0

40

,00

0

50

,00

0

60

,00

0

De

la T

(F)

Air Flow (CFM)

Air Flow vs Delta T

Field Conditions: Delta T = 38°F Airflow = 8,975, CFM



Utility electrical demand information was requested from the owner and it should be noted that currently

the demand is exceeding the rated kVA of the utility transformer. From the records reviewed, the peak

demand load on the 75 kVA transformer is approximately 86 kVA or 15% over its nominal rating. Using

a standard power factor of 0.8 the transformer rating translates into a more recognizable value of 60

kilo-watts (kW) or 60,000 watts. The peak demand then translates into 69 kW.

1.9 Compressor Room Cooling Recommendations

To meet manufacturers installation requirements the following options should be considered:

OPTION A – Ventilation Solution

Will allow operation of the compressor up to a maximum outside air temperature of 93°F:

The Cherry Creek Basin Water Quality authority has stated an expectation to operate this system as

close to 100% of the time as possible, with outdoor air temperatures up to 104°F. Option A, as

presented here, is expected to allow operation to 93°F only (based on 0.4% ASHRAE weather data).

This means an average of 35 hours per summer in which the compressor may have to shut down to

keep from overheating.

Installation of new supply fans to positively pressurize the compressor house with the

necessary 12,545 ACFM. This would include removing the current exhaust fan, and

installing (2) 24” Greenheck SBS Propeller fans, each with a 1 HP motor . (See

Appendix E for fan selections) Each fan would operate at 6,300 ACFM at an

estimated .25” WC of external static pressure.

Installation of Atlas Copco condensate freeze protection option, to allow operation of the

compressor at outdoor air temperatures below 32°F.

Modification of existing compressor ductwork and exhaust louver to lower external

pressure drop.

See next page for a schematic of this potential design solution:



FIGURE-11: PROPOSED VENTILATION SCHEMATIC

Representatives of Atlas Copco have emphasized the importance of maintaining design conditions for

the compressor. This includes maintaining appropriate ambient air conditions and limiting the external

static pressure seen by the compressor exhaust fan to 0.12” wc. By positively pressurizing the

compressor house: a) air is delivered to the compressor ventilation intake grids with 0” wc external

static pressure and b) manufacturers ambient air conditions are maintained.

OPTION B – Evaporative Cooling Solution

Will allow operation of the compressor all summer:

Installation of new make-up air unit to positively pressurize the compressor house with

evaporatively cooled air. This would include removing the existing exhaust fan and installing a

Greenheck MSX Make-Up Air Unit on a new concrete equipment pad located next to the

compressor house. (See Appendix F for MAU selection). A small section of ductwork would

need to be provided

Water would need to be provided to the MUA unit from a domestic water line near the marina,

the exact location has not been determined. This would involve substantial trenching to bury

the water line from the marina to the compressor house. Revisions to the existing electrical

distribution system would be recommended to accommodate this solution.

Recommend demolishing the connections from the utility CT cabinet to the 400 amp fused

disconnect switch and from the utility CT cabinet to the 10 kVA transformer.

Recommend demolishing the 400 amp fused disconnect switch and installing a new service

entrance rated, 277/480 volt 3 phase, 250 amp panel board, with a 250 amp main breaker, in its

place. This would allow multiple loads (compressor, evaporative cooler, etc.) to be served from

a single panel board. The existing 10 kVA transformer and existing panel board would be re-fed

from new 250 amp panel.

The size and condition of the existing wiring and the conduit condition and size from Xcel’s

transformer to the CT cabinet could not be verified, however the wiring observed from the CT

cabinet to the 400 amp fused disconnect switch appears to be adequately sized to

accommodate this solution. The wiring between the CT cabinet and the fused disconnect switch



is 250,000 circular-mills (KCMILS). Per the National Electric Code, this wire has an ampacity of

255 amps and would be acceptable to feed the new proposed 250 amp panel.

Install new conduit and wiring from new 250 amp panel to air compressor.

Install new conduit, wiring from new 250 amp panel to new make-up air unit.

Install new 30 amp, 3-pole fused disconnect switch for new make-up air unit.

Xcel Energy would need to determine if upsizing the existing service transformer is warranted

as this option would add approximately 10 kW of load to the transformer.

The following is a schematic of this potential design solution:

FIGURE-12: PROPOSED EVAPORATIVE COOLING SCHEMATIC

OPTION C – Mechanical Cooling Solution

Will allow operation of the compressor up to a maximum outside air temperature of 104°F:

Installation of new make-up air unit to supply direct evaporative (DX) cooling to the compressor

house. This would include installing a Greenheck RV packaged make-up air unit (See appendix

G for MAU selection). A small section of ductwork would need to be provided. This unit would

provide the necessary cooling capacity, but not sufficient airflow to pressurized the compressor

house.

Installation of new supply fans to positively pressurize the compressor house. This would

include removing the current exhaust fan, and installing (2) 24” Greenheck SBS Propeller fans,

each with a 1/2 HP motor . (See appendix H for fan selections) Each fan would operate at

3,775 ACFM at an estimated .25” WC of external static pressure.



Revisions to the existing electrical distribution system would be recommended to accommodate

this solution.

Recommend demolishing the connections from the utility CT cabinet to the 400 amp fused

disconnect switch and from the utility CT cabinet to the 10 kVA transformer.

Recommend demolishing the 400 amp fused disconnect switch and installing a new service

entrance rated, 277/480 volt 3 phase, 250 amp panel board, with a 250 amp main breaker, in its

place. This would allow multiple loads (compressor, evaporative cooler, etc.) to be served from

a single panel board.

Recommend demolishing existing 10kVA transformer and existing 8-circuit panel board.

The size and condition of the existing wiring and the conduit condition and size from Xcel’s

transformer to the CT cabinet could not be verified however the wiring from the CT cabinet to

the 400 amp fused disconnect switch appears to be adequately sized to accommodate this

solution. The wiring between the CT cabinet and the fused disconnect switch is 250,000

circular-mills (KCMILS). Per the National Electric Code, this wire has an ampacity of 255 amps

and would be acceptable to feed the new 250 amp panel board.

Install new wiring from new 250 amp panel to air compressor.

Install new 15kVA 480-120/208V, 3-phase transformer.

Install new 120/208V, 3-phase, 60 amp, 12-circuit panel board.

Re-connect circuits to existing lights and receptacles.

Install new conduit and wiring to new supply fans, quantity 2.

Install new conduit and wiring to new make-up air unit.

Xcel Energy would need to determine if upsizing the existing service transformer is warranted

as this option would add approximately 28 kW of load to the transformer.

See next page for a schematic of this potential design solution:



FIGURE-13: PROPOSED MECHANICAL COOLING SCHEMATIC

1.10 Compressed Air Distribution System Recommendations

Reducing System Pressure Drop

Pressure drop in compressed air piping is a significant consumer of energy. Atlas Copco has

published recommendations for maximum pressure drop across all piping to be 0.1 bar or 1.45 psig. As

seen if figure 2, every piping branch at Cherry Creek Reservoir has much a higher pressure drop than

recommended by the compressor manufacturer.

During our investigation, we were informed that a larger distribution system with a lower pressure drop

was considered during the design phase. However, due to the initial cost of the underwater piping, the

large pressure drop and current pipe sizing were deemed acceptable by the designers.

Reducing the current 51.93 psig pressure drop to 1.45 psig would save approximately 23% in utility

bills, or $6,471 per year (Based on 2011 utility data). It is the opinion of Eaton Energy Solutions that

replacing existing underground and underwater piping to achieve the stated recommended pressure

drop would result in a 20 year or simple payback based on energy savings. Additionally, the impact of

the aeration system on the lake has been under evaluation for over 4 years and the results have been

deemed acceptable by the owner. A change in the pipe sizing could change the current operating

conditions and we understand this is not desirable, therefore we recommend not to pursue this option.



Air Receiver

As discussed in Section 1.4, an air receiver is a crucial component of any load/unload compressed air

system, and the current Cherry Creek compressed air system requires an air receiver with a minimum

volume of 4,874 gallons. Currently there are 2,112 gallons available at the 4” main pipe and a shortage

of 2,762 gallons. The installation of a tank of sufficient size for holding 2,762 gallons of air at an

average of 51 psig can be a solution. The proposed receiver tank would allow the current compressor

to continue operating and comply with the 30 second minimum cycle time required by the manufacturer.

The receiver tank and the cooling solution must be implemented together in order to comply with the

manufacturer’s minimum installation and operation recommendations.

1.11 Compressor Replacement.

At the request of the client, Eaton investigated possible compressor replacements.

Various selections for air cooled compressor were obtained from Ingersoll Rand. After evaluating

the existing distribution system and electrical capacity, the following compressor was selected by

Eaton as a potential replacement (See Appendix I for selection details):

Ingersoll Rand Sierra L100 (100 HP) Oil Free Rotary Screw Compressor

o Load/Unload operation, similar to existing compressor

o Capable of 419 CFM of Free Air Delivery at 100 psig

o 2 Stage compression system (achieves 100 psig compared to 54 psig with

the existing single stage compressor, while the motor size remains the same)

o 115°F maximum ambient temperature rating (compared to the current 104°F)

o Internal ventilation fan capable of overcoming .25” of external static pressure

and requiring 9650 CFM of intake air (compared to the existing .12” ESP &

12,507 CFM)

The installation of a new compressor will require the following:

Demolition and removal of: existing compressor, associated intake & exhaust

ductwork, condensate drain, compressed air main to point leaving compressor

house.

Installation of new compressor, including new intake & exhaust ductwork,

condensate drain piping, and a new 4” compressed air line connecting the

compressor to the existing main.

Installation of a new pressure regulator downstream of the existing 4” main pipe at

the current location of the existing distribution manifold . The pressure regulator is

necessary upstream of the existing manifold if a new compressor is to be installed to

maintain the current underwater piping loop pressure and not affect the current

aeration conditions. The increase in compressor pressure will allow for the system to

have a much larger difference in load/unload pressures increasing the compressor

cycle time.



Factory startup of compressor

1 Year minimum comprehensive warranty

Demolish the existing 400 amp fused disconnect switch

Install a new 600 volt, 3-pole, 200 amp fused disconnect switch with 200 amp fuses

Install new conduit and wiring between new fused switch and compressor

1.12 Bibliography - Documents from Owner

Given the history of this project, many documents were made available to EATON by the water quality

authority. The following table lists which documents were used in the compressor Analysis:

FIGURE-16: OWNER DOCUMENTS USED BY EATON IN COMPRESSOR ANALYSIS

Author Date File Name Comments

AMEC 27-Oct-06 Aeration System Final Plans –

2006.pdf

Final aeration system construction

documents.

AMEC 11-Aug-09 AMEC Summary 11 Aug09.pdf Summary of Compressor Design Issues, in the

opinion of AMEC.

AMEC 4-Mar-09 Compressor Systems Analysis 04

Mar 09.pdf

Calculations of airflow requirements and

compressor selection.

CCBWQA TAC 8-Oct-09 TAC SubCmte-

SupplementalReport 01-13-

10.pdf

TAC report to board regarding overheating

problems.

TC Consulting

Services

6-Jan-09 '08_CCBWQA_Annual_O&M.pdf Summary of O&M activities.

TC Consulting

Services

28-Feb-09 TC Cost_Analysis.pdf Technical memorandum describing analysis

of operating costs. Listed as draft but no

changes were made.

TC Consulting

Services

14-Sep-09 Element_Shut_Down.pdf Technical memorandum describing the

element hard fault. Listed as draft but no

changes were made.

TC Consulting

Services

8-Jan-11 10_Draft_Annual_Report.pdf Summary of Compressor O&M activities,

Noted as a draft but no changes were made.

Ruzzo 2-Sep-11 CompressorRunTime 2009-2011 Summary and analysis of compressor run-

time.

TC Consulting

Services

1-May-09 PowerServiceMeeting-MInutes Meeting between Power Service, AMEC, and

TC Consulting

Ruzzo 27-Feb-12 2009AeratorHeadLocationds.pdf When compared to design document shows

where new aerator heads were added in

2009.



1.13 Bibliography – Atlas Copco Documents

The following documents published by Atlas Copco were used in the compressor analysis:

FIGURE-17: MANUFACTURER DOCUMENTS USED BY EATON IN COMPRESSOR

ANALYSIS

1.14 Bibliography – Project Contacts

The following people provided information to Eaton used in the compressor analysis:

Name Contact Phone Number Organization Bill Ruzzo (303) 985-1091 CCBWQA

Terry Cunningham (303) 350-0611 TC Consulting Services

Chad Holmes (303) 986-2244 Atlas Copco

Aaron Wiley (510) 413-5203 Atlas Copco

Clark Tuck (303) 477-1970 Water Control Corporation

Bob McGregor (303) 975-2191 AMEC

Jake Mcstivens (303) 394-4440 Power Service, Inc

FIGURE-18: PROJECT CONTACTS

Author Date File Name Comments

Atlas

Copco

14-Aug-07 Instruction Manual Z3

AIF111932.pdf

Z3 instruction manual provided critical

information on compressor installation

requirements.

Atlas

Copco

03-Jan-12 Compressed_Air_Manual_tcm45-

1249312.pdf

Compressed air manual published by Atlas

Copco. Provided critical information on

calculating pressure drop, sizing air

receivers, as well as many other compressed

air design practices.

Atlas

Copco

2006 Z3 and Z4 Parts Manual AIF111932

2930147400 2006.pdf

Compressor Parts Information

Atlas

Copco

Unknown Service_Checklist_Z_

Compressors.pdf

Inspection checklist for 2, 4, 8, 16, and

24,000 hour operations.


APPENDIX A

CURRENT DIFFUSER LOCATIONS

feetkm

30001


APPENDIX B

PRESSURE DROP CALCULATIONS

SCFM FAD L/S Pipe Diameter (inches) Pipe Length (ft) Initial Pressure (PSI) Bars Local Velocity (fps) Section Friction Loss (Bars) ΔP (PSI) inches WC278.4 341.04 160.2888 4 3400 63 4.3407 13.09 0.1191 1.7279 47.80 includes: 4x2 T, (6) Transitions, Flow Meter, Pressure Gage57.6 70.56 33.1632 1.25 1150 61.2721 4.221644638 27.74 0.7533 10.9325 302.40 Includes: (4) 90's, (1) T45.6 55.86 26.2542 1.25 100 50.3395 3.468394203 21.96 0.0517 0.7511 20.78 Includes: (1) 90, (1) T43.2 52.92 24.8724 1.25 220 49.5885 3.416645659 20.80 0.1046 1.5177 41.98 Includes: (1) 90, (1) T40.8 49.98 23.4906 1.25 215 48.0708 3.31207513 19.65 0.0948 1.3765 38.08 Includes: (1) 90, (1) T38.4 47.04 22.1088 1.25 215 46.6942 3.21723302 18.49 0.0873 1.2668 35.04 Includes: (1) 90, (1) T28.8 35.28 16.5816 1.25 210 45.4275 3.129953904 13.87 0.0515 0.7469 20.66 Includes: (1) 90, (1) T26.4 32.34 15.1998 1.25 100 44.6806 3.078490432 12.71 0.0212 0.3079 8.52 Includes: (1) 90, (1) T16.8 20.58 9.6726 1.25 100 44.3727 3.057278946 8.09 0.0093 0.1343 3.72 Includes: (1) 90, (1) T14.4 17.64 8.2908 1 100 44.2384 3.048022831 10.83 0.0213 0.3092 8.55 Includes: (1) 90, (1) T12.0 14.70 6.909 1 215 43.9292 3.026719668 9.03 0.0329 0.4778 13.22 Includes: (1) 90, (1) T9.6 11.76 5.5272 1 215 43.4514 2.993800924 7.22 0.0220 0.3197 8.84 Includes: (1) 90, (1) T7.2 8.82 4.1454 1 215 43.1317 2.971776274 5.42 0.0130 0.1891 5.23 Includes: (1) 90, (1) T4.8 5.88 2.7636 1 215 42.9426 2.958745231 3.61 0.0062 0.0897 2.48 Includes: (1) 90, (1) T2.4 2.94 1.3818 1 215 42.8529 2.952563375 1.81 0.0017 0.0249 0.69 Includes: (1) 90, (1) T

Pressure @ Diffuser Assembly (PSI)

42.8279 20.1721Total Pressure drop @ diffuser assembly

18.4441 Pressure Drop Without Main

psi inches wc0.12 3.26 Globe Valve

In‐line Filter7.25 69.25 Regulator

Diffuser Holder0.54 15 Diffuser

7.91 87.51 Total

7.8 Static Pressure

35.8813 Total Pressure Required (psig)

Pressure drop from Diffuser Assembly

ZONE 1 PRESSURE DROP CALCULATION

SCFM FAD Pipe Diameter (inches) Pipe Length (ft) Initial Pressure (PSI) Local Velocity (fps) Section Friction Loss (Bars) ΔP (PSI) inches WC278.4 341.04 4 3400 63 13.09 0.1191 1.7279 47.80 includes: 4x2 T, (6) Transitions, Flow Meter, Pressure Gage43.2 52.92 1.25 1000 61.2721 20.80 0.3847 5.5832 154.44 Includes: (4) 90's, (1) T40.8 49.98 1.25 200 55.6888 19.65 0.0762 1.1053 30.57 Includes: (1) 90, (1) T38.4 47.04 1.25 210 54.5835 18.49 0.0729 1.0585 29.28 Includes: (1) 90, (1) T36.0 44.10 1.25 210 53.5250 17.34 0.0660 0.9579 26.50 Includes: (1) 90, (1) T33.6 41.16 1.25 210 52.5671 16.18 0.0592 0.8585 23.75 Includes: (1) 90, (1) T31.2 38.22 1.25 210 51.7086 15.02 0.0524 0.7609 21.05 Includes: (1) 90, (1) T28.8 35.28 1.25 315 50.9477 13.87 0.0688 0.9990 27.63 Includes: (1) 90, (1) T26.4 32.34 1.25 315 49.9487 12.71 0.0598 0.8675 24.00 Includes: (1) 90, (1) T24.0 29.40 1.25 315 49.0812 11.56 0.0510 0.7401 20.47 Includes: (1) 90, (1) T21.6 26.46 1.25 315 48.3411 10.40 0.0426 0.6184 17.10 Includes: (1) 90, (1) T19.2 23.52 1 315 47.7228 14.45 0.1059 1.5373 42.52 Includes: (1) 90, (1) T16.8 20.58 1 710 46.1855 12.64 0.1927 2.7966 77.36 Includes: (1) 90, (1) T14.4 17.64 1 315 43.3890 10.83 0.0684 0.9930 27.47 Includes: (1) 90, (1) T12.0 14.70 1 400 42.3959 9.03 0.0635 0.9210 25.48 Includes: (1) 90, (1) T9.6 11.76 1 315 41.4749 7.22 0.0338 0.4907 13.57 Includes: (1) 90, (1) T7.2 8.82 1 315 40.9843 5.42 0.0201 0.2916 8.07 Includes: (1) 90, (1) T4.8 5.88 1 315 40.6926 3.61 0.0096 0.1387 3.84 Includes: (1) 90, (1) T2.4 2.94 1 315 40.5539 1.81 0.0027 0.0386 1.07 Includes: (1) T


40.5153 22.4847 Total Pressure drop @ diffuser assembly





7.91 87.51 Total

8.67 Static Pressure



SCFM FAD Pipe Diameter (inches) Pipe Length (ft) Initial Pressure (PSI) Local Velocity (fps) Section Friction Loss (Bars) ΔP (PSI) inches WC278.4 341.04 4 3400 63 13.09 0.1191 1.7279 47.80 includes: 4x2 T, (6) Transitions, Flow Meter, Pressure Gage38.4 47.04 1.25 2500 61.2721 18.49 0.7734 11.2252 310.50 Includes: (4) 90's, (1) T36.0 44.10 1 315 50.0469 27.09 0.3231 4.6897 129.72 Includes: (1) 90, (1) T33.6 41.16 1 315 45.3572 25.28 0.3138 4.5546 125.98 Includes: (1) 90, (1) T26.4 32.34 1 315 40.8026 19.86 0.2233 3.2407 89.64 Includes: (1) 90, (1) T16.8 20.58 1 315 37.5619 12.64 0.1051 1.5256 42.20 Includes: (1) 90, (1) T9.6 11.76 1 315 36.0363 7.22 0.0389 0.5647 15.62 Includes: (1) 90, (1) T7.2 8.82 1 315 35.4716 5.42 0.0232 0.3369 9.32 Includes: (1) 90, (1) T4.8 5.88 1 315 35.1346 3.61 0.0111 0.1607 4.44 Includes: (1) 90, (1) T2.4 2.94 1 315 34.9740 1.81 0.0031 0.0448 1.24 Includes: (1) 90, (1) T


34.9292 28.0708Total Pressure drop @ diffuser assembly





7.91 87.51 Total


45.5200 Total Pressure Required

43.7921 Manifold Pressure Required



SCFM FAD Pipe Diameter (inches) Pipe Length (ft) Initial Pressure (PSI) Bars Local Velocity (fps) Section Friction Loss (Bars) ΔP (PSI) inches WC278.4 341.04 4 3400 63 4.3407 13.09 0.1191 1.7279 47.80 includes: 4x2 T, (6) Transitions, Flow Meter, Pressure Gage74.4 91.14 1.25 1800 61.2721 4.221644638 35.83 1.8930 27.4741 759.96 Includes: (4) 90's, (1) T50.4 61.74 1.25 100 33.7980 2.328680474 24.27 0.0928 1.3462 37.2424.0 29.40 1 315 32.4518 2.23592742 18.06 0.2354 3.4160 94.49 Includes: (1) 90, (1) T21.6 26.46 1 315 29.0358 2.000565963 16.25 0.2165 3.1417 86.90 Includes: (1) 90, (1) T19.2 23.52 1 315 25.8941 1.784100401 14.45 0.1952 2.8332 78.37 Includes: (1) 90, (1) T16.8 20.58 1 315 23.0609 1.588895719 12.64 0.1712 2.4849 68.73 Includes: (1) 90, (1) T14.4 17.64 1 315 20.5760 1.417685759 10.83 0.1443 2.0940 57.92 Includes: (1) 90, (1) T12.0 14.70 1 315 18.4820 1.273410162 9.03 0.1146 1.6638 46.02 Includes: (1) 90, (1) T9.6 11.76 1 315 16.8182 1.158774632 7.22 0.0834 1.2100 33.47 Includes: (1) 90, (1) T7.2 8.82 1 315 15.6082 1.075405544 5.42 0.0528 0.7657 21.18 Includes: (1) 90, (1) T4.8 5.88 1 315 14.8425 1.022646721 3.61 0.0262 0.3803 10.52 Includes: (1) 90, (1) T2.4 2.94 1 315 14.4622 0.996442401 1.81 0.0075 0.1083 2.99 Includes: (1) T


14.4547 48.6461 Total Pressure drop @ diffuser assembly





7.91 87.51 Total


66.9553 Total Pressure Required

65.2274 Manifold Pressure Required



SCFM FAD Pipe Diameter (inches) Pipe Length Initial Pressure (PSI) Local Velocity (fps) Section Friction Loss (Bars) ΔP (PSI) inches WC278.4 341.04 4 3400 63 13.09 0.1191 1.7279 47.80 includes: 4x2 T, (6) Transitions, Flow Meter, Pressure Gage

64.8 79.38 1.25 1200 61.2721 31.20 0.9774 14.1852 392.37 Includes: (4) 90's, (1) T38.4 47.04 1.25 220 47.0868 18.49 0.0886 1.2854 35.56 Includes: (1) 90, (1) T36.0 44.10 1.25 315 45.8014 17.34 0.1157 1.6792 46.45 Includes: (1) 90, (1) T33.6 41.16 1.25 315 44.1223 16.18 0.1057 1.5342 42.44 Includes: (1) 90, (1) T31.2 38.22 1.25 315 42.5881 15.02 0.0955 1.3858 38.33 Includes: (1) 90, (1) T28.8 35.28 1.25 315 41.2022 13.87 0.0851 1.2353 34.17 Includes: (1) 90, (1) T26.4 32.34 1.25 315 39.9669 12.71 0.0747 1.0841 29.99 Includes: (1) 90, (1) T24.0 29.40 1.25 315 38.8828 11.56 0.0644 0.9342 25.84 Includes: (1) 90, (1) T21.6 26.46 1.25 315 37.9486 10.40 0.0543 0.7877 21.79 Includes: (1) 90, (1) T19.2 23.52 1.25 315 37.1609 9.25 0.0446 0.6469 17.89 Includes: (1) 90, (1) T16.8 20.58 1.25 315 36.5140 8.09 0.0354 0.5143 14.22 Includes: (1) 90, (1) T14.4 17.64 1 1425 35.9998 10.83 0.3730 5.4143 149.76 Includes: (1) 90, (1) T12.0 14.70 1 315 30.5855 9.03 0.0693 1.0054 27.81 Includes: (1) 90, (1) T9.6 11.76 1 315 29.5801 7.22 0.0474 0.6880 19.03 Includes: (1) 90, (1) T7.2 8.82 1 315 28.8921 5.42 0.0285 0.4137 11.44 Includes: (1) 90, (1) T4.8 5.88 1 315 28.4785 3.61 0.0137 0.1982 5.48 Includes: (1) 90, (1) T2.4 2.94 1 315 28.2803 1.81 0.0038 0.0554 1.53 Includes: (1) T

Pressure @ Diffuser Assembly (PSI) 28.2249

34.7751 Total Pressure drop @ diffuser assembly





7.91 87.51 Total




APPENDIX C

ASHRAE CLIMATE INFORMATION FOR LITTLETON, CO

2009 ASHRAE Handbook - Fundamentals (IP) © 2009 ASHRAE, Inc.

WMO#: 724695

Lat: 39.72N Long: 104.75W Elev: 5663 StdP: 11.93 Time Zone: -7.00 (NAM) Period: 82-06 WBAN: 99999

Annual Heating and Humidification Design Conditions

99.6% 99% DP HR MCDB DP HR MCDB WS MCDB WS MCDB MCWS PCWD

12 -0.2 6.5 -8.7 4.2 5.9 -2.2 6.0 16.1 26.6 35.5 23.1 36.9 5.7 180Annual Cooling, Dehumidification, and Enthalpy Design Conditions

DB MCWB DB MCWB DB MCWB WB MCDB WB MCDB WB MCDB MCWS PCWD

7 26.6 93.0 59.0 90.4 58.8 87.8 58.6 64.1 79.3 62.7 78.4 61.6 77.6 8.0 30

DP HR MCDB DP HR MCDB DP HR MCDB Enth MCDB Enth MCDB Enth MCDB

60.6 97.6 66.7 58.5 90.6 66.5 56.7 84.7 66.4 32.2 78.7 31.1 78.3 30.2 77.6 752Extreme Annual Design Conditions

1% 2.5% 5% Min Max Min Max Min Max Min Max Min Max Min Max

23.4 19.4 16.8 70.5 -8.2 98.4 6.7 2.4 -13.0 100.2 -16.9 101.6 -20.6 102.9 -25.5 104.7Monthly Climatic Design Conditions

Annual Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov DecTavg 50.7 32.1 33.7 40.6 47.3 57.0 66.5 73.4 71.5 62.7 51.0 39.1 31.8Sd 10.76 11.55 9.77 9.62 8.30 7.34 5.48 4.82 8.83 9.64 11.19 11.43

HDD50 2567 556 460 315 161 33 2 0 0 17 103 352 568HDD65 5920 1019 877 757 532 267 70 7 10 138 437 776 1030CDD50 2804 2 3 23 80 250 495 725 665 399 134 25 3CDD65 685 0 0 0 1 19 114 267 210 70 4 0 0CDH74 8036 0 0 3 44 359 1484 3016 2090 907 131 2 0CDH80 3264 0 0 0 3 83 605 1437 831 289 16 0 0

DB 63.7 66.1 73.0 78.8 87.2 94.6 97.5 94.7 90.8 82.1 72.5 64.0MCWB 42.0 43.7 46.6 50.0 56.1 58.1 59.4 58.9 58.5 51.8 46.5 42.8

DB 57.2 60.8 67.9 74.5 81.8 90.5 94.5 90.7 86.7 77.9 67.0 57.4MCWB 39.6 41.4 44.6 48.7 54.5 57.8 59.4 59.0 56.5 50.4 45.0 40.0

DB 52.4 55.3 63.2 70.3 78.0 87.2 91.3 88.1 83.4 73.0 62.1 52.3MCWB 37.5 39.1 42.7 47.5 53.4 57.4 59.3 59.0 55.6 48.9 43.1 37.9

DB 47.7 50.4 57.9 65.4 73.7 83.0 88.5 84.8 79.7 68.2 55.5 46.9MCWB 35.7 37.1 40.9 45.9 52.5 57.5 59.4 59.3 54.7 47.5 40.3 35.3

WB 43.4 44.4 47.8 52.9 60.4 63.7 66.4 65.8 62.1 54.4 48.2 43.5MCDB 61.7 63.6 70.4 70.4 73.0 78.9 80.5 80.2 79.1 74.4 68.0 61.7

WB 40.5 41.9 45.3 50.6 57.5 61.7 64.4 64.0 59.8 52.0 45.7 40.9MCDB 55.4 58.6 64.7 69.2 73.8 77.4 79.6 79.1 77.1 71.5 65.0 56.9

WB 38.3 39.6 43.5 48.7 55.6 60.3 63.1 62.5 58.2 50.3 43.6 38.3MCDB 51.1 54.0 60.8 66.1 72.6 77.1 79.0 77.9 75.4 69.3 61.1 51.5

WB 36.0 37.5 41.6 46.9 54.0 59.1 61.9 61.4 56.7 48.5 41.1 35.5MCDB 47.0 49.3 57.1 62.7 70.2 76.6 78.4 77.0 73.8 65.8 55.1 46.4

MDBR 21.5 21.5 23.3 23.7 24.2 26.0 26.6 25.3 25.9 25.1 22.3 21.1MCDBR 27.3 28.6 31.0 31.0 30.1 31.5 30.7 29.5 30.6 31.5 29.4 27.2MCWBR 14.8 15.0 14.7 13.2 11.7 10.3 8.9 9.0 10.3 13.1 14.3 14.7MCDBR 25.6 26.6 29.2 28.1 26.9 26.7 25.5 24.5 26.7 28.3 28.5 26.2MCWBR 14.7 14.7 14.4 13.0 11.5 11.1 9.2 9.1 10.2 12.6 14.3 14.7

0.251 0.278 0.303 0.368 0.382 0.397 0.423 0.399 0.340 0.302 0.267 0.2492.567 2.351 2.293 2.043 2.081 2.082 2.020 2.122 2.334 2.431 2.520 2.602299 301 303 287 284 279 270 274 286 288 288 29225 34 39 52 51 51 54 48 37 31 26 23

CDDn Cooling degree-days base n°F, °F-day Lat Latitude, ° Period Years used to calculate the design conditions CDHn Cooling degree-hours base n°F, °F-hour Long Longitude, ° Sd Standard deviation of daily average temperature, °F DB Dry bulb temperature, °F MCDB Mean coincident dry bulb temperature, °F StdP Standard pressure at station elevation, psi DP Dew point temperature, °F MCDBR Mean coincident dry bulb temp. range, °F taub Clear sky optical depth for beam irradiance Ebn,noon } Clear sky beam normal and diffuse hori- MCDP Mean coincident dew point temperature, °F taud Clear sky optical depth for diffuse irradiance Edh,noon } zontal irradiances at solar noon, Btu/h/ft2 MCWB Mean coincident wet bulb temperature, °F Tavg Average temperature, °F Elev Elevation, ft MCWBR Mean coincident wet bulb temp. range, °F Time Zone Hours ahead or behind UTC, and time zone code Enth Enthalpy, Btu/lb MCWS Mean coincident wind speed, mph WB Wet bulb temperature, °F HDDn Heating degree-days base n°F, °F-day MDBR Mean dry bulb temp. range, °F WBAN Weather Bureau Army Navy number Hours 8/4 & 55/69 Number of hours between 8 a.m. PCWD Prevailing coincident wind direction, °, WMO# World Meteorological Organization number

and 4 p.m with DB between 55 and 69 °F 0 = North, 90 = East WS Wind speed, mph HR Humidity ratio, grains of moisture per lb of dry air

Hours8 to 4 &55/69

2%

Coldest month WS/MCDB

2%

MCWS/PCWDto 99.6% DB0.4%

1%

1%

MCWS/PCWDto 0.4% DB

Enthalpy/MCDB1% 2%0.4%

ColdestMonth

HottestMonth

Humidification DP/MCDB and HR99.6% 99%Heating DB

0.4%

5% DB

taub

Monthly Design Dry Bulb

and Mean Coincident

Wet BulbTemperatures

Monthly Design Wet Bulb

and Mean Coincident

Dry BulbTemperatures

Mean DailyTemperature

Range

0.4%

2%

5%

10%

1% 2%0.4%

Clear Sky Solar

Irradiance

Dehumidification DP/MCDB and HR

Ebn,noonEdh,noon

ExtremeMaxWB

Extreme Annual DB n-Year Return Period Values of Extreme DB

0.4%

Extreme Annual WS

taud

10%

0.4%

2%

5%

n=10 years

1%

5% WB

n=20 years n=50 years

BUCKLEY ANGB/DENVER, CO, USA

Temperatures,Degree-Days

and Degree-Hours

HottestMonth

DB Range

Cooling DB/MCWB Evaporation WB/MCDB

Mean Standard deviation n=5 years


APPENDIX D

COMPRESSED AIR HEAT GAIN CALCULATIONS


Where

Heat removed from compressed air in aftercooler

mass flow rate of compressed air =

⁄ = 32.76 lb/m

Average of specific heats of air (at constant pressure) at

aftercooler entering and leaving air temperatures = .2425 (BTU/lb * °R)

Change in compressed air temperature through aftercooler =

338.4 °R


APPENDIX E

GREENHECK FAN SELECTIONS

VENTILATION SOLUTION

SUBMITTAL

P.O. Box 410 Schofield, WI 54476 (715) 359-6171 FAX (715) 355-2399 www.greenheck.com

Job Title: Cherry Creek Reservoir

Engineer: Eaton's Energy Solutions

Consultant: Scott McQuoid

Elevation: (ft) 5,500

Date: 01/27/12

Submitted By: Larry Gelin

CFM COMPANY1440 SOUTH LIPAN ST

DENVER , CO 80223

US

Phone: (303)761-2291Fax: (303)761-0325Email Address: [email protected]

CAPS 4.8.958 H:\Greenheck\2012 LJG\Cherry Creek Reservoir.gcj Page 1 of 6

SUPPLY FANS CAN CARRY RAIN OR SNOW INTO THE BUILDING

AIR FLOWSee the Assembly Drawing For

Selected Accessories

32

1.25

20.5

24.625

Model: SBS-3L24-10Sidewall Belt Drive Supply FanStandard Construction Features:- Galvanized steel fan panel - Die formed, galvanized steel drive frame assembly- Fabricated steel propeller for Levels 1 and 2, welded and painted steel for Level3 - Adjustable motor pulley - Ball bearing motors - Fan shaft mounted in ballbearing pillow blocks - Static resistant belts - Corrosion resistant fastenersOptions & Accessories:Spare Belt(s) - 1 Set (Attached)UL/cUL 705 Listed - "Power Ventilators"Damper, VCD-23-PB-26X26, End Switch (Mounted)Damper Actuator, 24 VAC ActuatedLong Wall Hsg, Flush Ext, (1B-Sup), w/ OSHA Grd.Switch, NEMA-1, Toggle, Junction Box Mounted & WiredClosure AnglesBearings with Grease FittingsOne Point wiring

Dimensional

QtyWeight w/oAccessories

(lb)

Weight withAccessories

(lb)

WallOpening

(in)

OptionalDamper

(in)1 96 267 33.75 x 33.75 26 x 26

PerformanceRequested

Volume(CFM)

ActualVolume(CFM)

RequestedSP

(in wg)

ActualSP

(in wg)

FanRPM

OperatingPower(hp)

Elevation(ft)

AirstreamTemperature

(F)

DriveLoss(%)

TipSpeed(ft/min)

SE(%)

6,300 6,300 0.2 0.2 989 0.71 5,500 70 7.1 6213 29.9

Sound Power by Octave BandSoundData 62.5 125 250 500 1000 2000 4000 8000 LwA dBA Sones

Inlet 89 91 82 78 76 73 72 69 83 71 23

MotorMotor

MountedSize(hp) V/C/P Encl. Motor

RPM WindingsNECFLA*

(Amps)Yes 1 208/60/3 TEFC 1725 1 4.6

Notes:All dimensions shown are in units of in.*FLA - based on tables 150 or 148 of National ElectricalCode 2002. Actual motor FLA may vary, for sizing thermaloverload, consult factory.LwA - A weighted sound power level, based on ANSI S1.4dBA - A weighed sound pressure level, based on 11.5 dBattenuation per Octave band at 5.0 ft - dBA levels are notlicensed by AMCA InternationalSones - calculated using AMCA 301 at 5.0 ft

1/27/2012Printed Date: Cherry Creek ReservoirJob:

FanProduct Type: SF-1 REV2Mark:


Assembly DrawingType: Sidewall Belt Drive Supply Fan

HOUSINGMOUNTING

FLANGE

OSHAAPPROVED

GUARD

AIR FLOWWALL OPENING 33.75 SQ.

LONG WALLHOUSING

WA

LL

-INTE

RIO

R-

-EX

TER

IOR

-

WA

LL

CLOSURE ANGLES

supply fans can carry rain or snow into the building

DAMPER WITHACTUATOR

32.25

38.25

43

Notes: All dimensions shown are in units of in.




DAMPER

TYP. SECTION VIEW

2626

5.010.0Min.

1.3max. 1.3

max.

Standard Construction Features:- Model VCD-23 is a well built low leakage control damper for automatic control or manual balancing applications - Galvanized16 ga channel frame - Galvanized blades with reinforcements - Side mounted steel linkage is concealed in the frame to preventadditional pressure drop - Axles are steel and 0.5 in dia.- Synthetic axle bearings - Width and height furnished approximately0.25 in undersized - Field wiring is required to individual components

Accessory ConfigurationActuator Type: 24 VACEnd Switch: Yes

Notes: All dimensions shown are in units of inWidth And height furnished approximately 0.125 in undersize

Control DamperModel: VCD-23





APPENDIX F

GREENHECK MAU SELECTIONS

EVAPORATIVE COOLING SOLUTION

SUBMITTAL






Date: 04/11/12



DENVER , CO 80223

US



MSX Modular Supply Fan MSX-120-H32CONSTRUCTION FEATURES• Exterior housing constructed of galvanized steel • Weatherization • Removable access panels • Painted orgalvanized steel blower and bearing supports • Forward curved steel blower and motor • Fan assembly ismounted on vibration isolators • Motor pulleys are adjustable through 10 hp and fixed for 15 hp and greater •Fan shaft is mounted in permanently lubricated ball bearings (up through size 118) or ball bearing pillow blocks(size 120 and greater) • Static free belts • Corrosion resistant fasteners are standard.

Selection Performance Job PropertiesCoolingAirflow ArrangementDamperUnit Arrangement

EvaporativeOutdoor Air OnlyInlet DamperHorizontal

ModelVolumeTotal SPExternal SPPowerFan RPM

MSX-120-H3212,550 CFM1.376 in wg0.8 in wg7.55 hp813

ElevationWinter Dry BulbSummer Dry BulbSummer Wet Bulb

5,500 ft-3 F93 F65 F

Unit Configuration Electrical ConfigurationDischarge PositionCoatingInsulation TypeInsulation LocationIsolationWeatherizationMounting Options1 Set Spare Belt(s) *Unit Warranty

DownblastGalvanizedDouble WallEntire UnitNeopreneYesCurbYes1 Yr (Standard)

Control CenterCooling Inlet Air Sensor1 NO, 1 NC on Supply StarterService Receptacle *

YesYesYesYes

*Options shipped loose

Outlet Sound Power by Octave Band

62.5 125 250 500 1000 2000 4000 8000 LwA dBA Sones99.8 89.2 86.8 85.7 83.4 82.9 79.2 74.2 89.5 78.5 33.2

• LwA - A weighted soud power level based on ANSI S1.4• dBA - A weighted sound pressure level base on 11.5 dB attenuation per octave band at 5.0 ft.• Noise Criteria (NC) based on an average attenuation of 11.5 dB per octave band at 5.0 ft.


Make Up AirProduct Type: MUA-1Mark:


MSX Modular Supply Fan MSX-120-H32

Heating InformationHeating Type No Heat

Cooling InformationCooling Type EvaporativeEvap. Cooling MediaEvap. FiltersEvap. Cooling ControlControl ValvesEvap LDBEvap LWB

CELdek2" Aluminum MeshAuto Drain & FlushBy Factory67.8 F65.0 F

Required Flow** 1.2 GPM

Motor DataMark Fan HP V/C/P Mtr. Amps RPM Enclosure Efficiency

- Supply Fan 10 460/60/3 14 1725 ODP Premium

MCA/MOP: 18.7 / 30

WeightsUnit Weight* : 1,697 lb

Unit Wet Weight*: 2,093 lb* Weight does not include accessories external to the unit(curb, exhaust fan(s), diffuser, etc).** Required flow and inlet pressure are for supply linesizing only. They do not represent water usage duringnormal operation. Consult factory for water usage.




MSX Modular Supply Fan MSX-120-H32

38.098 65.948

48.722

ELEVATION VIEW* Standard configuration for unit access is on the right-hand side, when looking into the unit intake in the direction of airflow.

38.098

96.532

65.948

53.119

PLAN VIEW




* Standard configuration for unit access is on the right-hand side, when looking into the unit intake in the direction of airflow.

52.166

END VIEW

2.049

44.625

49.772

2.059

96.721

1.049

INTAKE VIEW




ELECTRICALCONNECTION

15.000

63.997

Electrical Connections




EQUIPMENT SCHEDULE

GreenheckModel

Operating Power V/C/P Encl:

Volume Total SP FRPMQty

Non-Tempered Make-Up Air Unit

MotorRPM Windings MCA

Motor InformationSize

Mark: MUA-1

Weight

MSX-120-H32 7.55 hp 460/60/3 ODP12,550 CFM

1.376 in wg

813 RPM1 1725 1 18.710 hp1,697 lb

Required Flow**Dry

Filters Cooling Control

Cooling

NA93 F 2in. Aluminum Mesh

Automatic Drain Flush Valve-By Factory65 F

Cooling MediaCooling Type

CELdekEvaporative

**Required flow and inlet pressure are for supply line sizing only. They do not represent water usage during normal operation. Consult factory for actual water usage.

Summer Bulb

Wet

125 4000250 1000 200062.5

Outlet Sound Power By Octave Band

8000

89.2 79.286.8 83.4 82.999.8 74.2

dBA

78.5

LwA

89.5

500

85.7

Sones

33.2· LwA - A weighted sound power level based on ANSI S1.4· dBA - A weighted sound pressure level base on 11.f dB attenuation per octabe band at 5.0 ft.· Noise Criteria (NC) based on an average attenuation of 11.5 dB per octabe band at 5.0 ft.

OPTIONS AND ACCESSORIES

Spare Set of Belts - Quantity 1

Unit Insulation - DoubleWall - Entire UnitAir Flow Arrangement - Outdoor Air Only - 100% OSAHorizontal Unit - No Weatherhood Provided Discharge Position - Downblast - No DiffuserInlet DamperInlet Air Sensor - CoolingControl CenterFactory Finish - GalvanizedService ReceptacleBlower Isolation - NeopreneRoof Curb - GPI 50 in (W) x 64 in (L) x 16 in (H) - Galvanized - 1 in Insulated





APPENDIX G

GREENHECK MAU SELECTION

MECHANICAL COOLING SOLUTION

SUBMITTAL






Date: 05/22/12



DENVER , CO 80223

US



DESCRIPTION

Model Elevation(ft) Qty Approximate

Weight (lb)

RV-35 5,500 1 2,038

--Weight does NOT include skid/crating and may vary by 15%based on options selected.

ARRANGEMENT

OA IntakePosition

SA DischargePosition

Return AirIntake Position

Exhaust AirDischargePosition

End Side N/A

MOTOR SPECS

V/C/P Enclosure RPM SupplyEfficiency

ExhaustEfficiency

460/60/3 ODP 3500 PE N/A

ELECTRICAL

Minimum CircuitAmps (A)

Max. OverCurrent

Protection (A)

40 50

COOLING

Cooling Type CondensingUnit By

Cond. UnitCap. (MBH)

CompressorQty.

CompressorType

Packaged DX Greenheck 162.9 2 StandardScroll

SUPPLY FAN PERFORMANCE

Volume(CFM)

OutdoorVolume(CFM)

Supply SP(in wg)

Total SP(in wg) FRPM

OperatingPower(hp)

Motor Size(hp)

5,000 5,000 0.8 1.698 3248 2.12 5

RV Rooftop Ventilator

STANDARD CONSTRUCTION FEATURES

Exterior housing constructed of galvanized steel • Direct-drive airfoilplenum blowers with factory mounted VFDs • Ball bearing motors • Fanshafts in permanently lubricated bearings • Corrosion resistant fasteners •Internally lined with galvanized steel metal creating a double wall •Insulated with 2 inch, 3# density insulation • Internally mounted controlcenter with motor starters, 24 VAC control transformers, control circuitfusing

SELECTED ACCESSORIESUL\cUL1995Weatherhood: Downturned HoodFinal Filters - 2" Pleated MERV 8Roof Curbs - GKD 14"Supply Dampers - Motorized Low LeakageMicroprocessor ControlsSupply Fan Controls - Constant Volume (on/off)Dirty Filter Sensor: FinalPhase and Brown Out Protection120v NEMA 3R Outlet (ships loose-power by others)Unit Disconnect - Mounted By FactorySpare Filter Final, Quantity of 1

Note: Unit is proved with factory mounted and wired disconnect switch.


Energy RecoveryProduct Type: MUA-1 DXMark:


RVRooftop Ventilator

Coil / Condensing Unit PerformanceCondensing Unit DetailsThe RV will come equipped with the following components:• Hermetic scroll type compressors• Compressors mounted in an isolated compartment to be serviceablewithout affecting airflow and on neoprene vibration isolation to minimizevibration transmission and noise• Crankcase heater on compressor• Thermal expansion valve for refrigerant flow control• Hot gas bypass• Multiple condensing fans to allow fan cycling for head pressure control• Liquid-Line filter drier• High pressure manual reset cutout• Low-pressure auto-reset cutout• Time delay relays for compressor protection• Service/charging valves• Moisture-indicating sight glass• Direct drive, statically and dynamically balanced, AMCA Licensed for AirPerformance• Condensing coils with 3/8" copper tubes mechanically bonded toaluminum fins

COMPRESSORNominal Tonnage /

CompressorCompressor

QuantityCompressor

Type

7.5 2 Standard Scroll

CONDENSING COILFace Area

(ft2) Rows FPI CondensingTemp. (F)

AmbientTemp. (F)

21.1 3 16 129.0 103.0

CONDENSING FAN

Quantity DiameterMotor

Motor Size (Watts)(each) RPM

2 20 1119 1100

Cooling Coil

Cooling Type Direct Exp (DX)Face Area (ft2): 9.7Rows Deep (Evap Coil): 3Fins Per Inch: 10Face Velocity (ft/min): 420Entering Dry Bulb (F): 103.0Entering Wet Bulb (F): 67.0Leaving Dry Bulb (F): 66.6Leaving Wet Bulb (F): 54.3Cool Coil SP (in wg): 0.134Refrigerant Velocity (ft/min): 20Suction Temp. (F): 43.4Refrigerant: 410aCond. Unit Cap. (MBH): 162.9Unit EER: 9.76




OUTDOOR AIR INLET

OUTDOOR AIRWEATHERHOOD

DX COIL

SUPPLY AIR DISCHARGE

OUTDOOR AIR DAMPER SUPPLY BLOWER

COMPRESSORS

CONDENSING COIL

DRAIN LOCATION

SUPPLY FINAL FILTERS

CONTROL CENTER

Plan

Left End Elevation Right End

52.5 28.8

22.4

4.0

18.227.0

95.6

58.2

7.2 38.1

7.4

22.0

21.5





APPENDIX H

GREENHECK FAN SELECTIONS

MECHANICAL COOLING SOLUTION

SUBMITTAL






Date: 04/27/12



DENVER , CO 80223

US



SUPPLY FANS CAN CARRY RAIN OR SNOW INTO THE BUILDING

AIR FLOWSee the Assembly Drawing For

Selected Accessories

32

1.25

20

24.625

Model: SBS-2H24-5Sidewall Belt Drive Supply FanTags: SFS-1 SFS-2

Standard Construction Features:- Galvanized steel fan panel - Die formed, galvanized steel drive frame assembly- Fabricated steel propeller for Levels 1 and 2, welded and painted steel for Level3 - Adjustable motor pulley - Ball bearing motors - Fan shaft mounted in ballbearing pillow blocks - Static resistant belts - Corrosion resistant fastenersOptions & Accessories:Motor with Thermal OverloadSpare Belt(s) - 1 Set (Attached)UL/cUL 705 Listed - "Power Ventilators"Damper, VCD-23-PB-26X26, End Switch (Mounted)Damper Actuator, 24 VAC ActuatedLong Wall Hsg, Flush Ext, (1B-Sup), w/ OSHA Grd.Switch, NEMA-1, Toggle, Junction Box Mounted & WiredClosure AnglesOne Point wiring

Dimensional

QtyWeight w/oAccessories

(lb)

Weight withAccessories

(lb)

WallOpening

(in)

OptionalDamper

(in)2 76 245 33.75 x 33.75 26 x 26

PerformanceRequested

Volume(CFM)

ActualVolume(CFM)

RequestedSP

(in wg)

ActualSP

(in wg)

FanRPM

OperatingPower(hp)

Elevation(ft)

AirstreamTemperature

(F)

DriveLoss(%)

TipSpeed(ft/min)

SE(%)

3,775 3,775 0.25 0.25 1,001 0.36 5,500 70 10.0 6288 45.8

Sound Power by Octave BandSoundData 62.5 125 250 500 1000 2000 4000 8000 LwA dBA Sones

Inlet 78 83 85 81 77 74 68 63 83 72 19.4

MotorMotor

MountedSize(hp) V/C/P Encl. Motor

RPM WindingsNECFLA*

(Amps)Yes 1/2 208/60/1 ODP 1725 1 5.4

Notes:All dimensions shown are in units of in.*FLA - based on tables 150 or 148 of National ElectricalCode 2002. Actual motor FLA may vary, for sizing thermaloverload, consult factory.LwA - A weighted sound power level, based on ANSI S1.4dBA - A weighed sound pressure level, based on 11.5 dBattenuation per Octave band at 5.0 ft - dBA levels are notlicensed by AMCA InternationalSones - calculated using AMCA 301 at 5.0 ft


FanProduct Type: SFS-1, 2 REV3Mark:


Assembly DrawingType: Sidewall Belt Drive Supply Fan

HOUSINGMOUNTING

FLANGE

OSHAAPPROVED

GUARD

AIR FLOWWALL OPENING 33.75 SQ.

LONG WALLHOUSING

WA

LL

-INTE

RIO

R-

-EX

TER

IOR

-

WA

LL

CLOSURE ANGLES

supply fans can carry rain or snow into the building

DAMPER WITHACTUATOR

32.25

38.25

43

Notes: All dimensions shown are in units of in.




DAMPER

TYP. SECTION VIEW

2626

5.010.0Min.

1.3max. 1.3

max.

Standard Construction Features:- Model VCD-23 is a well built low leakage control damper for automatic control or manual balancing applications - Galvanized16 ga channel frame - Galvanized blades with reinforcements - Side mounted steel linkage is concealed in the frame to preventadditional pressure drop - Axles are steel and 0.5 in dia.- Synthetic axle bearings - Width and height furnished approximately0.25 in undersized - Field wiring is required to individual components

Accessory ConfigurationActuator Type: 24 VACEnd Switch: Yes

Notes: All dimensions shown are in units of inWidth And height furnished approximately 0.125 in undersize

Control DamperModel: VCD-23





APPENDIX I

INGERSOLL RAND

COMPRESSOR SELECTIONS

ENGINEERING DATARef: L100A Page 1Date: 11/25/03Cancels: All Previous

Davidson, NC

Capacity FAD (at stated pressure) (1)150 psig N/A CFM N/A m3/min140 psig N/A CFM N/A m3/min125 psig N/A CFM N/A m3/min115 psig N/A CFM N/A m3/min100 psig 419 CFM 11.9 m3/min85 psig 419 CFM 11.9 m3/min

Compressor Shaft Power (at stated pressure)150 psig N/A BHP N/A kW140 psig N/A BHP N/A kW125 psig N/A BHP N/A kW115 psig N/A BHP N/A kW100 psig 102 BHP 76 kW85 psig 95 BHP 71 kW

Specific Power (at stated pressure)150 psig N/A BHP/100 CFM N/A kW/m3/min140 psig N/A BHP/100 CFM N/A kW/m3/min125 psig N/A BHP/100 CFM N/A kW/m3/min115 psig N/A BHP/100 CFM N/A kW/m3/min100 psig 24.4 BHP/100 CFM 6.4 kW/m3/min85 psig 22.7 BHP/100 CFM 6.0 kW/m3/min

Unloaded Compressor Shaft PowerUnloaded 26.8 BHP 20 kW

Full Load Operating Pressure 100 psig 6.9 bargMaximum Off Line Pressure 103 psig 7.1 bargMinimum Operating Pressure 72 psig 5.0 barg

Compression ModuleNumber of compressor stages 2

1st StageRotor Diameter 108 mmMale Rotor Speed 17519 RPMTip Speed 99 m/s

2nd StageRotor Diameter 72.9 mmMale Rotor Speed 24527 RPMTip Speed 94 m/s

Lubrication DataOil Pressure -Normal Operation 45 psig 3.1 bargOil Temperature -Normal Operation 135 oF 57 oCOil Pump Type positive displacement, gear type Sump Capacity 9 US Gal 34 LiterTotal System Capacity 10.5 US Gal 40 Liter

Cooling Data (115oF/46oC maximum ambient temperature)Heat Removal at 68oF(20oC) (2)

Intercooler 98 1000 BTU/hr 103 1000 kJ/hrAftercooler 138 1000 BTU/hr 145 1000 kJ/hrOilcooler 42 1000 BTU/hr 44 1000 kJ/hrTotal 278 1000 BTU/hr 293 1000 kJ/hr

Aftercooler Inlet Temperature (@ full load) 380 oF 193 oCAftercooler CTD (3) 25 oF 13.9 oCCooling Air Fan Power 5 HP 3.7 kWCooling Air Flow 8000 CFM 227 m3/minMaximum Added Static Pressure 0.25 Inches H2O 62 Pa

Cooling Air ∆T Approx. 32 oF 18 oC

Sound Level (4)Sound Pressure 76 dB(A)

Sierra ®Two-Stage Oil-free Air Compressor

L100A

ENGINEERING DATARef: L100A Page 2Date: 11/25/03

Davidson, NC

Electrical DataMain Drive Motor (5) (7)Nominal Shaft Power 100 HP 75 kWNumber of Poles 2Motor Speed 3575 rpmMotor Frame Size ODP 404T

TEFC 405TSDEfficiency at Full Load ODP 94.8 %

TEFC 94.7 %Power Factor at Full Load ODP 0.842

TEFC 0.816Compressor Full Load Current at 200 V 271 AMPS

230 V 236 AMPS460 V 118 AMPS575 V 94 AMPS

Locked Rotor Current at 200 V 2604 AMPS230 V 2264 AMPS460 V 1132 AMPS575 V 906 AMPS

IEC Starter Size (8) 200 V B250230 V B180460 V C85575 V C72

Fan MotorNominal Shaft Power 5 HP 3.7 kWNumber of Poles 4Fan Motor Speed 1745 rpmFan Motor Frame Size TEFC 184TEfficiency at Full Load TEFC 87.5 %Power Factor at Full Load TEFC 0.82Full Load Current at 200 V 14 AMPS


Total Package (5)Total Installed Package Shaft Power 107 BHP 80 kWFull Load Package Current at 200 V 286 AMPS


Construction - General Data (6)Package Dimension - Length 88.5 Inches 2246 mmPackage Dimension - Width 54.0 Inches 1371 mmPackage Dimension - Height 75.4 Inches 1913 mmShipping Weight - Total Package, Std. Scope 5500 lb 2495 kgCompression Module Only 1235 lb 560 kgDrive Motor Only - ODP 700 lb 318 kgAir Discharge Pipe Connection 1.5 Inch NPTIntercooler Condensate Drain 0.5 Inch NPTAftercooler Condensate Drain 0.5 Inch NPTElectrical Power Inlet Cable Diameter 3.0 Inches 76 mm

Notes (1) FAD (Free Air Delivery) is actual flow rate at the compressor inlet measured atthe discharge terminal point of the package in accordance with ISO1217 Annex C.

(2) Heat removal including latent heat(3) CTD (Cold Temperature Difference) based on 100oF/38oC inlet air at 40% relative humidity.(4) Sound levels are "free field conditions" per CAGI/Pneurop, ±3 dB(A)(5) Electrical data based on Reliance ODP motors (unless otherwise stated)(6) For details on dimensions and piping conditions see General Arrangement Drawing.(7) Motor rating is maintained up to an altitude of 3,000 ft. above sea level.(8) Starter data is for the 1M/2M drive motor contactor in a Star Delta starter.

L100A


ENGINEERING DATARef: H100A Page 1Date: 11/25/03Cancels: All Previous

Davidson, NC

Capacity FAD (at stated pressure) (1)150 psig N/A CFM N/A m3/min140 psig N/A CFM N/A m3/min125 psig 407 CFM 11.5 m3/min115 psig 407 CFM 11.5 m3/min100 psig 408 CFM 11.5 m3/min85 psig 408 CFM 11.5 m3/min

Compressor Shaft Power (at stated pressure)150 psig N/A BHP N/A kW140 psig N/A BHP N/A kW125 psig 108 BHP 80 kW115 psig 105 BHP 78 kW100 psig 98 BHP 73 kW85 psig 93 BHP 69 kW

Specific Power (at stated pressure)150 psig N/A BHP/100 CFM N/A kW/m3/min140 psig N/A BHP/100 CFM N/A kW/m3/min125 psig 26.5 BHP/100 CFM 7.0 kW/m3/min115 psig 25.7 BHP/100 CFM 6.8 kW/m3/min100 psig 24.1 BHP/100 CFM 6.4 kW/m3/min85 psig 22.8 BHP/100 CFM 6.0 kW/m3/min





2nd StageRotor Diameter 72.9 mmMale Rotor Speed 21645 RPMTip Speed 83 m/s

Lubrication DataOil Pressure -Normal Operation 45 psig 3.1 bargOil Temperature -Normal Operation 135 oF 57 oCOil Pump Type positive displacement, gear type Sump Capacity 9 US Gal 34 LiterTotal System Capacity 10.5 US Gal 40 Liter



Aftercooler Inlet Temperature (@ full load) 404 oF 207 oCAftercooler CTD (3) 25 oF 13.9 oCCooling Air Fan Power 5 HP 3.7 kWCooling Air Flow 8000 CFM 227 m3/minMaximum Added Static Pressure 0.25 Inches H2O 62 Pa




H100A

ENGINEERING DATARef: H100A Page 2Date: 11/25/03

Davidson, NC


TEFC 405TSDEfficiency at Full Load ODP 94.8 %


TEFC 0.816Compressor Full Load Current at 200 V 286 AMPS


Locked Rotor Current at 200 V 2604 AMPS230 V 2264 AMPS460 V 1132 AMPS575 V 906 AMPS

IEC Starter Size (8) 200 V B250230 V B180460 V C85575 V C72

Fan MotorNominal Shaft Power 5 HP 3.7 kWNumber of Poles 4Fan Motor Speed 1745 rpmFan Motor Frame Size TEFC 184TEfficiency at Full Load TEFC 87.5 %Power Factor at Full Load TEFC 0.82Full Load Current at 200 V 14 AMPS


Total Package (5)Total Installed Package Shaft Power 113 BHP 84 kWFull Load Package Current at 200 V 301 AMPS





H100A


ENGINEERING DATARef: L125A Page 1Date: 11/25/03Cancels: All Previous

Davidson, NC

Capacity FAD (at stated pressure) (1)150 psig N/A CFM N/A m3/min140 psig N/A CFM N/A m3/min125 psig N/A CFM N/A m3/min115 psig N/A CFM N/A m3/min100 psig 585 CFM 16.6 m3/min85 psig 585 CFM 16.6 m3/min

Compressor Shaft Power (at stated pressure)150 psig N/A BHP N/A kW140 psig N/A BHP N/A kW125 psig N/A BHP N/A kW115 psig N/A BHP N/A kW100 psig 133 BHP 99 kW85 psig 124 BHP 93 kW

Specific Power (at stated pressure)150 psig N/A BHP/100 CFM N/A kW/m3/min140 psig N/A BHP/100 CFM N/A kW/m3/min125 psig N/A BHP/100 CFM N/A kW/m3/min115 psig N/A BHP/100 CFM N/A kW/m3/min100 psig 22.8 BHP/100 CFM 6.0 kW/m3/min85 psig 21.2 BHP/100 CFM 5.6 kW/m3/min





2nd StageRotor Diameter 87 mmMale Rotor Speed 12757 RPMTip Speed 58 m/s

Lubrication DataOil Pressure -Normal Operation 45 psig 3.1 bargOil Temperature -Normal Operation 135 oF 57 oCOil Pump Type positive displacement, gear type Sump Capacity 11 US Gal 42 LiterTotal System Capacity 13 US Gal 49 Liter



Aftercooler Inlet Temperature (@ full load) 372 oF 189 oCAftercooler CTD (3) 19 oF 10.6 oCCooling Air Fan Power 7.5 HP 5.6 kWCooling Air Flow 15000 CFM 425 m3/minMaximum Added Static Pressure 0.25 Inches H2O 62 Pa




L125A

ENGINEERING DATARef: L125A Page 2Date: 11/25/03

Davidson, NC


TEFC 444TEfficiency at Full Load ODP 94.7 %


TEFC 0.839Compressor Full Load Current at 200 V N/A AMPS


Locked Rotor Current at 200 V N/A AMPS230 V 1544 AMPS460 V 772 AMPS575 V 618 AMPS

IEC Starter Size (8) 200 V N/A230 V B250460 V B110575 V C85

Fan MotorNominal Shaft Power 10 HP 7.5 kWNumber of Poles 4Fan Motor Speed 1765 rpmFan Motor Frame Size TEFC 215TEfficiency at Full Load TEFC 91 %Power Factor at Full Load TEFC 0.81Full Load Current at 200 V N/A AMPS


Total Package (5)Total Installed Package Shaft Power 143 BHP 107 kWFull Load Package Current at 200 V N/A AMPS





L125A


ENGINEERING DATARef: H125A Page 1Date: 11/25/03Cancels: All Previous

Davidson, NC

Capacity FAD (at stated pressure) (1)150 psig N/A CFM N/A m3/min140 psig N/A CFM N/A m3/min125 psig 523 CFM 14.8 m3/min115 psig 523 CFM 14.8 m3/min100 psig 524 CFM 14.8 m3/min85 psig 524 CFM 14.8 m3/min

Compressor Shaft Power (at stated pressure)150 psig N/A BHP N/A kW140 psig N/A BHP N/A kW125 psig 133 BHP 99 kW115 psig 129 BHP 96 kW100 psig 122 BHP 91 kW85 psig 115 BHP 86 kW

Specific Power (at stated pressure)150 psig N/A BHP/100 CFM N/A kW/m3/min140 psig N/A BHP/100 CFM N/A kW/m3/min125 psig 25.4 BHP/100 CFM 6.7 kW/m3/min115 psig 24.7 BHP/100 CFM 6.5 kW/m3/min100 psig 23.2 BHP/100 CFM 6.1 kW/m3/min85 psig 21.9 BHP/100 CFM 5.8 kW/m3/min





2nd StageRotor Diameter 87 mmMale Rotor Speed 13402 RPMTip Speed 61 m/s

Lubrication DataOil Pressure -Normal Operation 45 psig 3.1 bargOil Temperature -Normal Operation 135 oF 57 oCOil Pump Type positive displacement, gear type Sump Capacity 11 US Gal 42 LiterTotal System Capacity 13 US Gal 49 Liter



Aftercooler Inlet Temperature (@ full load) 477 oF 247 oCAftercooler CTD (3) 19 oF 10.6 oCCooling Air Fan Power 7.5 HP 5.6 kWCooling Air Flow 15000 CFM 425 m3/minMaximum Added Static Pressure 0.25 Inches H2O 62 Pa




H125A

ENGINEERING DATARef: H125A Page 2Date: 11/25/03

Davidson, NC


TEFC 444TEfficiency at Full Load ODP 94.7 %


TEFC 0.839Compressor Full Load Current at 200 V N/A AMPS


Locked Rotor Current at 200 V N/A AMPS230 V 1544 AMPS460 V 772 AMPS575 V 618 AMPS

IEC Starter Size (8) 200 V N/A230 V B250460 V B110575 V C85

Fan MotorNominal Shaft Power 10 HP 7.5 kWNumber of Poles 4Fan Motor Speed 1765 rpmFan Motor Frame Size TEFC 215TEfficiency at Full Load TEFC 91 %Power Factor at Full Load TEFC 0.81Full Load Current at 200 V N/A AMPS


Total Package (5)Total Installed Package Shaft Power 143 BHP 107 kWFull Load Package Current at 200 V N/A AMPS





H125A



APPENDIX J

ACOUSTICAL ANALYSIS

NEW YORK HONG KONG WASHINGTON, DC CHICAGO SAN FRANCISCO PRINCETON HOUSTON DENVER LONDON LAS VEGAS

DUBAI

Cherry Creek Reservoir Compressor Station Cherry Creek, CO Acoustical Noise Study February 27th, 2012 Prepared for: Scott McQuoid Eaton Energy Solutions, Inc 143 Union Blvd. Suite 350 Lakewood, CO 80228

TECHNOLOGY CONSULTANTS IN TELECOMMUNICATIONS, AUDIOVISUAL & ACOUSTICS 1822 Blake Street Suite 2A Denver, CO 80202 Tel: 720-482-0770 Fax: 720-482-0450

www.smwinc.com

Shen Milsom & Wilke, Inc.

INTRODUCTION This report summarizes Shen Milsom Wilke’s findings pertaining to the sound generated from the Cherry Creek Reservoir compressor station. Acoustical testing was performed on the afternoon of February 8th, 2012. The purpose of the acoustical study was to document the noise levels generated by the compressor and identify possible noise mitigation measures to reduce the overall background noise levels in the marina and other adjacent park areas. The findings of this acoustical testing and study are detailed below. MEASUREMENT OVERVIEW Noise level measurements were conducted in following locations:

1. East side of compressor building (Louvers) 2. North side of compressor building 3. West side of compressor building (Louvered doors) 4. South side of compressor building 5. Road to South side of compressor building 6. Marina Parking lot to South East side of compressor building

MEASUREMENT CONDITIONS Temp: 45 to 50 degrees Wind: 10 to 15 mph MEASUREMENT EQUIPMENT The sound level meter used for this testing was an ANSI Type 1, IEC 60804 integrating sound level meter manufactured by 01dB, serial number 60202, with a model MCE 212, ½-inch microphone, serial number 67236. The system was calibrated at the beginning and end of the measurements with no shift greater than 0.1 dB in the calibration level. A wind screen rated for 20 mph was in place during the measurements. MEASUREMENT RESULTS

Location Description Measured Noise Level dBA

East side of building 76.6 North side of building 83.8 West side of building 70.1 South side of building 67.0 Road at South side of building

59.0

Marina Parking Lot 53.8 Please see attached graph G-1 for spectral content of noise level measurements. MEASUREMENT RESULTS DISCUSSION The noise levels generated by the compressor were primarily transmitted through two paths from the compressor building. The first sound transmission path is through the ductwork on the North side of the building. The noise generated at this location has a significant tonal peak at 250 Hz of 86.6 dB. People typically find tonal noise sources more annoying and disruptive than broadband noise sources. However, the location of this ductwork, directed away from the marina and public areas, provides a noise barrier effect to the marina and park areas south of the compressor building.


PHOTO P-1: Ductwork to North Exterior The second path is through the louvers on the East side of the building. The noise generated at this location is more broadband in nature with less significant tonal peaks at 1000 and 2000 Hz of 76.5 dB and 73.3 dB, respectively. However, the location of the louvers is in the direct line of sight of the marina and is the primary noise source audible within the marina parking lot.

PHOTO P-2: LOUVER ON EAST SIDE OF BUILDING RECOMMENDATIONS We understand that the current configuration will accept very little increase in static pressure. Therefore, we have provided recommendations in an effort maximize the mitigation of the compressor noise while minimizing the addition of static pressure. We have not provided


recommendations such as acoustical louvers or attenuators because of the potential change in static pressure however these mitigation measures are available. Based on the measurement results and the conditions noted during our acoustical study, we have the following recommendations to mitigate the noise levels generated by the compressor to the marina and other park areas located to the South of the building:

1. Incorporate a barrier wall on the east and south side of the louvers as needed to block the line of sight from the marina and public areas. The barrier should be solid and continuous construction with enough length and height to block the line of sight as described above. We recommend incorporating 2 inch thick absorptive material with a minimum NRC rating of 0.70 such as the Acoustical Surfaces P.E.P.P Panel to the inside of the barrier wall facing the compressor building. Please see attached product information.

a. Adding a barrier wall may affect the required air circulation and should be reviewed by a mechanical engineer.

It is projected that the addition of the barrier wall will decrease the audible noise levels in the marina parking lot by 5 to 8 dB.

2. It is apparent from the noise level measurements that the 250 Hz peak from ductwork on

the North side of the building is still audible on the South and East sides of the building. Therefore, we recommend internally lining the circular ductwork, shown in photo P-1 above, with 1 inch thick ductliner or incorporating an engine grade muffler, if required for heat.

a. Adding internal ductliner may affect the required air flow which may require an increase in ductwork size and should be reviewed by a mechanical engineer.

It is projected that the addition of the internally lined ductwork will decrease the audible noise levels in the marina parking lot by 2 to 5 dB.

This concludes our comments at this time. The information described in the report above is based on information currently available. If additional information or conditions are made available, Shen Milsom & Wilke, Inc. reserves the right to revise or amend this report accordingly. Please contact us with any questions. Respectfully submitted: Kelly Stumpf Associate

Acoustical Surfaces, Inc.Soundproofing, Acoustics, Noise & Vibration Control Specialists

123 Columbia Court North = Suite 201 = Chaska, MN 55318(952) 448-5300 = Fax (952) 448-2613 = (800) 448-0121

Email: [email protected] our Website: www.acousticalsurfaces.com

We Identify and S.T.O.P. Your Noise Problems

SOUND SILENCERSOUND SILENCERTMTM

ARPROª Porous Expanded Polypropylene (P.E.P.P.)Acoustical Wall Panels

a Class A Fire Retardenta No Fiberglass - Non-Fibrousa Moisture Resistant-Indoor-Outdoora Impact Resistant

Semi Rigid Porous Expanded Polypropylene Acoustical Bead Foam (P.E.P.P.). Non Abrasive, Slightly Textured, PorousLightweight, Impact Resistant, Moisture, Bacteria & Fungi Resistant, Tackable Surface, UVStableGymnasiums, Auditoriums, Classrooms, Swimming Pools, Ice Arenas, Clean Rooms, FoodProcessing Plants, Food Prep Areas, Cafeterias & Resturaunts, Manufacturing Plants, CarWashes, Rooftop and Machine Enclosures, Gun Ranges, Dog Kennels, Locker Rooms.1Ó & 2Ó SIZES: Nominal 2Õx2Õ, 2Õx4Õ; Custom Sizes AvailableWhite, CharcoalASTM E84, Class A. 1Ó: Flame Spread: 3, Smoke Developed: 84. 2Ó: Flame Spread: 5,Smoke Developed: 113ASI S.T.O.P. Noise Acoustical Adhesive, Mechanical Fasteners

MATERIAL:PATTERN:

FEATURES:

APPLICATIONS:

THICKNESS:COLOR:

FLAMMABILITY:

INSTALLATION:

Mount 125Hz 250Hz 500Hz 1KHz 2KHz 4KHz NRC

1Ó Wall Amtg 0.05 0.06 0.21 0.80 0.65 0.75 0.45

1Ó Wall w/ 3/4Ó Airspace 0.06 0.13 0.51 0.79 0.62 0.79 0.50

1Ó Wall w/ 1Ó B.A.P. 0.11 0.58 1.07 0.71 0.74 0.72 0.86

2Ó Wall Amtg 0.07 0.21 0.81 0.85 0.93 0.88 0.70

2Ó Wall w/ 3/4Ó Airspace 0.10 0.29 0.99 0.74 0.90 0.93 0.75

2Ó Wall w/ 1Ó B.A.P. 0.17 0.81 0.97 0.85 0.89 0.92 0.90

1Ó Ceiling E400 0.46 0.59 0.42 0.49 0.76 0.86 0.55

2Ó Ceiling E400 0.51 0.52 0.52 0.72 0.77 0.89 0.70

SOUND SILENCERª: Sound Absorption / Noise Reduction

125Hz 250Hz 500Hz 1KHz 2.5KHz 5KHz STC1Ó 6 5 7 8 10 15 92Ó 9 8 10 10 17 22 131Ó 27 27 29 31 32 45 32w/ 5/8Ó Gypsum both Sides

SOUND SILENCERTM: Sound Transmission Loss (STC)

¥ Soundproofing Products ¥ SonexTM Ceiling & Wall Panels ¥ Sound Control Curtains ¥ Equipment Enclosures ¥ Acoustical Baffles & Banners ¥ Solid Wood & VeneerAcoustical Ceiling & Wall Systems ¥ Professional Audio Acoustics ¥ Vibration & Damping Control ¥ Fire Retardant Acoustics ¥ Hearing Protection ¥ Moisture & Impact

Resistant Products ¥ Floor Impact Noise Reduction ¥ Sound Absorbers ¥ Noise Barriers ¥ Fabric Wrapped Wall Panels ¥ Acoustical Foam (Egg Crate) ¥ Acoustical Sealants &Adhesives ¥ Outdoor Noise Control ¥ Assistive Listening Devices ¥ OSHA, FDA, ADA Compliance ¥ On-Site Acoustical Analysis ¥ Acoustical Design & Consulting ¥ Large

Inventory ¥ Fast Shipment ¥ No Project too Large or Small ¥ Major Credit Cards Accepted


APPENDIX K

ESTIMATES OF PROBABLE COST

PROJECT: SCOPE:

LOCATION: SALESMAN:

ARCHITECT: CUSTOMER:

ENGINEER: EST NO:

EST. BY:

EST DATE: ALTERNATE:

MAN DAYS

COSTS OH % OVERHEAD General 36,000 P.F.

729 S/M 63,905 TOTAL 9

10,634 ======> 10,6342045 ======> 2,045

======> 12,6795% 634

1.5% 190251

13,754

10% 1,375

15,130

30% 4,539

19,668

505

20,17354.24

YES NO 23.08%1.30

Version 2.06Revised Date 6/08

Date Run: 5/29/2012

Time Run: 17:37

ADDENDA ACKNOWLEDGEMENT:

Gross MarginMark-Up

DATE:

EST. REVIEWED BY:

JOB SUMMARY REVIEWED:

TAXES

SELLING PRICE

Gross Profit/Manhour

MARKUP

TOTAL COST BEFORE MARKUP

PRICE BEFORE TAXES

WARRANTYPERMITS

BONDS

ENGINEERING

CONTINGENCY

SUBTOTAL (TOTAL COST)

LEARNING CENTER

SUBCONTRACTORS

TOTAL LABOR, EQUIPMENT, SUBS & OTHER COSTS

MATERIAL

LABOR MISC. COSTS

TOTAL DIRECT COSTS

EQUIPMENT

PROJECT MANAGEMENT

ESTIMATE SUMMARY

VENTILATION SOLUTION

BASE SCOPE

Scott McQuoid5/29/2012

Cherry Creek CompressorLittleton, CO

Eaton's EMC Engineers

PROJECT: SCOPE:

LOCATION: SALESMAN:


ENGINEER: EST NO:

EST. BY:


MAN DAYS

COSTS OH % OVERHEAD General 311,700 P.F. 15

1,894 S/M 710,780 TOTAL 25

24,374 ======> 24,37415251 ======> 15,251

======> 39,6255% 1,981

1.5% 594665

42,866

10% 4,287

47,152

30% 14,146

61,298

1,020

62,31760.03

YES NO 23.08%1.30


Date Run: 5/24/2012

Time Run: 10:46

ESTIMATE SUMMARY

EVAPORATIVE COOLING SOLUTION

BASE SCOPE




EQUIPMENT

PROJECT MANAGEMENT

LEARNING CENTER

SUBCONTRACTORS


MATERIAL

LABOR MISC. COSTS

TOTAL DIRECT COSTS

WARRANTYPERMITS

BONDS

ENGINEERING

CONTINGENCY


MARKUP


PRICE BEFORE TAXES

TAXES

SELLING PRICE



Gross MarginMark-Up

DATE:

EST. REVIEWED BY:


PROJECT: SCOPE:

LOCATION: SALESMAN:


ENGINEER: EST NO:

EST. BY:


MAN DAYS


1,106 S/M 84,950 TOTAL 12

31,256 ======> 31,25619871 ======> 19,871

======> 51,1275% 2,556

1.5% 767830

55,280

10% 5,528

60,808

30% 18,242

79,050

1,973

81,023129.26

YES NO 23.08%1.30


Date Run: 5/24/2012

Time Run: 10:46


Gross MarginMark-Up

DATE:

EST. REVIEWED BY:


TAXES

SELLING PRICE


MARKUP


PRICE BEFORE TAXES

WARRANTYPERMITS

BONDS

ENGINEERING

CONTINGENCY


LEARNING CENTER

SUBCONTRACTORS


MATERIAL

LABOR MISC. COSTS

TOTAL DIRECT COSTS

EQUIPMENT

PROJECT MANAGEMENT

ESTIMATE SUMMARY

MECHANICAL COOLING & FAN SOLUTION

BASE SCOPE




PROJECT: SCOPE:

LOCATION: SALESMAN:


ENGINEER: EST NO:

EST. BY:


MAN DAYS


1,267 S/M 128,690 TOTAL 20

94,273 ======> 94,2733210 ======> 3,210

======> 97,4835% 4,874

1.5% 1,4621,573

105,392

10% 10,539

115,932

30% 34,779

150,711

6,419

157,130136.13

YES NO 23.08%1.30


Date Run: 5/24/2012

Time Run: 10:47

ESTIMATE SUMMARY

INSTALL NEW AIR COMPRESSOR

BASE SCOPE




EQUIPMENT

PROJECT MANAGEMENT

LEARNING CENTER

SUBCONTRACTORS


MATERIAL

LABOR MISC. COSTS

TOTAL DIRECT COSTS

WARRANTYPERMITS

BONDS

ENGINEERING

CONTINGENCY


MARKUP


PRICE BEFORE TAXES

TAXES

SELLING PRICE



Gross MarginMark-Up

DATE:

EST. REVIEWED BY:


PROJECT: SCOPE:

LOCATION: SALESMAN:


ENGINEER: EST NO:

EST. BY:


MAN DAYS


1,351 S/M 76,050 TOTAL 14

28,401 ======> 28,40126300 ======> 26,300

======> 54,7014% 2,1881% 547

1.5% 821880

59,137

59,137

40% 23,655

82,791

1,676

84,467153.84

YES NO 28.57%1.40


Date Run: 6/28/2012

Time Run: 16:54

Install 2800 gallon receiver tank

Cherry Creek Water Board

SKM6/28/2012

Chery Creek AerationLittleton, CO

Eaton Energy Solutions

EQUIPMENT

ESTIMATE SUMMARY

SUBCONTRACTORS


MATERIAL

LABOR MISC. COSTS

TOTAL DIRECT COSTS

PROJECT MANAGEMENT

LEARNING CENTER

WARRANTYPERMITS

ENGINEERING

CONTINGENCYBONDS



MARKUP

PRICE BEFORE TAXES

TAXES

SELLING PRICE



Gross MarginMark-Up

DATE:

EST. REVIEWED BY:


Compressor Evaluation CHERRY CREEK RESERVOIR AERATION ...

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