NREL is a national laboratory of the U.S. Department of Energy

Office of Energy Efficiency & Renewable Energy

Operated by the Alliance for Sustainable Energy, LLC

This report is available at no cost from the National Renewable Energy

Laboratory (NREL) at www.nrel.gov/publications.

Contract No. DE-AC36-08GO28308

RM12-2798 High-Efficiency 

Rooftop Unit Replacement

Hawaii and Guam Energy 

Improvement Technology 

Demonstration Project

Ian Doebber and Gene Holland

National Renewable Energy Laboratory

NREL Technical Monitor: Steve Gorin

Produced under direction of the Naval Facilities Engineering Command 

(NAVFAC) by the National Renewable Energy Laboratory (NREL) under 

Interagency Agreement 11-01829.

Strategic Partnership Project Report

NREL/TP-7A40-71508

July 2018
NREL is a national laboratory of the U.S. Department of Energy

Office of Energy Efficiency & Renewable Energy

Operated by the Alliance for Sustainable Energy, LLC

This report is available at no cost from the National Renewable Energy

Laboratory (NREL) at www.nrel.gov/publications.

Contract No. DE-AC36-08GO28308

National Renewable Energy Laboratory

15013 Denver West Parkway

Golden, CO 80401

303-275-3000 • www.nrel.gov

Strategic Partnership Project Report

NREL/TP-7A40-71508

July 2018

RM12-2798 High-Efficiency 

Rooftop Unit Replacement

Hawaii and Guam Energy 

Improvement Technology 

Demonstration Project

Ian Doebber and Gene Holland

National Renewable Energy Laboratory

NREL Technical Monitor: Steve Gorin

Suggested Citation

Doebber, Ian, Gene Holland. 2018. RM12-2798 High-Efficiency Rooftop Unit 

Replacement: Hawaii and Guam Energy Improvement Technology 

Demonstration Project. Golden, CO: National Renewable Energy Laboratory. 

NREL/TP-7A40-71508. https://www.nrel.gov/docs/fy18osti/71508.pdf.
NOTICE

This work was supported by the U.S. Department of Energy under Contract No. DE-AC36-08GO28308 with 

Alliance for Sustainable Energy, LLC, the Operator of the National Renewable Energy Laboratory, and the Naval 

Facilities Engineering Command (NAVFAC) under Interagency Agreement 11-01829. The views expressed in the 

article do not necessarily represent the views of the DOE or the U.S. Government.

This report is available at no cost from the National Renewable 

Energy Laboratory (NREL) at www.nrel.gov/publications.

U.S. Department of Energy (DOE) reports produced after 1991 

and a growing number of pre-1991 documents are available 

free via www.OSTI.gov.

NREL prints on paper that contains recycled content.
iv

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Acknowledgments 

The authors wish to acknowledge Joint Base Pearl Harbor-Hickam (JBPHH) personnel for 

hosting this demonstration and providing key support from initial design to project completion. 

We thank Robert Cabreros and David Stiner from Naval Facilities Engineering Command 

(NAVFAC) Pacific; Peter Yuen and Chelsea Goto of the NAVFAC Hawaii energy team;

Captain Jeffrey W. James, joint base commander; and Colonel David Kirkendall, deputy base 

commander.

The project could not have met success without the coordination and oversight from Florence 

Ching, Wah-Cheong Sze, James Low, April Teekell, and Susan Kim with NAVFAC Pacific and 

Hawaii.

We also thank Kevin Hurley of NAVFAC Headquarters for his guidance and administration of 

the demonstration program.

Numerous contributors at the U.S. Department of Energy’s National Renewable Energy 

Laboratory (NREL), Transformative Wave (TW), ClimaCheck, Emerging Energy Solutions, and 

Daikin Applied should be acknowledged. At NREL, contributors include Jeff Dominick, John 

Nangle, Mike Heaney, Michael Deru, Eric Kozubal, and Melissa Butheau. At TW, who managed 

the construction, Web-based building management system, and remote monitoring, we wish to 

thank Justin Sipe, Danny Miller, Jerry Scott, and Ken Hellewell. At ClimaCheck and Emerging 

Energy Solutions, who provided the detailed submetering on each refrigeration circuit, we wish 

to thank Klas Berglof, Sean McCaffery and Joel Klobas. At Daikin Applied who provided Rebel 

technical support, we wish to thank Brett Gist, Gregory Durant, and Brad Hassing.
v

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List of Abbreviations and Acronyms

AFDD automated fault detection and diagnostics

AHJ authority having jurisdiction

AHRI Air-Conditioning, Heating, & Refrigeration Institute

ANSI American National Standards Institute

ASHRAE American Society of Heating, Refrigerating and Air-Conditioning Engineers

Btuh British thermal units per hour

cfm cubic feet per minute

CO2 carbon dioxide

COP coefficient of performance

CVRMSE coefficient of variation of the root mean squared error

DAT discharge air temperature

DCV demand-controlled ventilation

DOD U.S. Department of Defense

DOE U.S. Department of Energy

DX direct expansion

ECM electronically commutated motor

EER energy efficiency ratio

FEMP Federal Energy Management Program

ft2 square feet

fpm flow per minute

HVAC heating, ventilation, and air conditioning

IEER integrated energy efficiency ratio

JBPHH Joint Base Pearl Harbor-Hickam

kW kilowatt
vi

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kWh kilowatt-hour

MWh megawatt-hours

NAVFAC Naval Facilities Engineering Command

NEMA National Electrical Manufacturers Association

NREL National Renewable Energy Laboratory

OA outdoor air

O&M operation and maintenance

PAC Pacific (NAVFAC PAC)

PI proportional-integral

RH relative humidity

ROI return on investment

RTU packaged air conditioning rooftop unit

SEER seasonal energy efficiency ratio

SHGC solar heat gain coefficient

SZVAV single-zone variable-air volume

TAB (HVAC) testing, adjusting, and balancing

TMY3 typical meteorological year 3

TWT Transformative Wave Technologies

UFC Unified Facilities Criteria

UFGS Unified Facilities Guide Specifications

W Watt

WC water column
vii

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Executive Summary

As part of its overall strategy to meet its energy goals, NAVFAC partnered with NREL to 

rapidly demonstrate and deploy cost-effective renewable energy and energy efficiency 

technologies. This was one of several demonstrations of new and underutilized commercial 

energy efficiency technologies. The common goals were to demonstrate and measure the 

performance and economic benefits of the system and to monitor any ancillary impacts related to 

standards of service and operation and maintenance (O&M) practices. In short, these

demonstrations simultaneously evaluated the benefits and compatibility of the technologies with 

the U.S. Department of Defense (DOD) mission, and with NAVFAC’s design, construction, and 

O&M practices.

A wide variety of DOD buildings, such as offices, warehouses, gymnasiums, commissaries, 

exchange stores, and hangars, are ventilated, cooled, and heated with packaged rooftop air 

conditioning units (RTUs). The term RTU refers to a pre-engineered unitary system that houses 

all the components of a heating, ventilation, and air conditioning (HVAC). Most RTUs are 

located on a roof but can also be located on concrete pads next to the building they serve. In 

Hawaii, RTUs provide only space cooling and outdoor air (OA) for ventilation, as no heating is 

needed. RTUs are popular for three reasons: (1) minimal engineering design and specifications; 

(2) low first costs compared to built-up systems (e.g., chillers with air handling units); and (3) 

quick installation. Unfortunately, RTUs have historically been one of the lowest efficiency 

HVAC systems on the market. 

DOE issued the High-Performance Rooftop Unit Challenge in January 2011 to:1

catalyze the market introduction of cost-effective, energy-saving RTUs that would 

significantly outperform any models that were currently available. RTUs built 

according to this specification are expected to reduce energy use by as much as 

50% compared to the current ASHRAE 90.1 Standard, depending on location and 

facility type. 

In May 2012,

2 the Daikin Applied Rebel3 was the first commercially available RTU to meet the 

DOE RTU challenge specification. The Rebel met the comprehensive RTU challenge 

requirements with: an integrated energy efficiency ratio (IEER) exceeding18.0, a variable-speed 

supply fan, direct digital controls, and automated fault detection and diagnostics (AFDD). This 

field demonstration evaluated the energy savings and thermal comfort benefits of the Rebel 

compared to a code-minimum RTU. The baseline RTU met the ASHRAE 90.1-2010 minimum 

performance requirements per the United Facilities Guide Specification (UFGS) 23 81 00 00 20. 

Both the Rebel and baseline RTUs served a small office located on JBPHH.

The field demonstration was designed to provide a true apples-to-apples comparison between the 

Rebel RTU and baseline RTU. Based on an extensive investigation of existing RTUs at JBPHH, 

NAVFAC and NREL chose to replace two 10-ton, 15-year-old RTUs serving a 5,000-ft2 office. 

 1 “DOE Facilitates Market-Driven Solutions to Develop and Deploy New High-Efficiency Commercial Air 

Conditioners.” U.S. Department of Energy, Office of Energy Efficiency & Renewable Energy, February 3, 2011. 2 “Energy Department Announces First Product to Meet the Commercial Rooftop Air Conditioner Challenge.” U.S. 

Department of Energy, Office of Energy Efficiency & Renewable Energy, May 24, 2012. 3 “Rebel Overview.” Daikin Applied, 2014. http://www.daikinapplied.com/rooftop-rebel.php. 
viii

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The RTU serving the southern half of the space was replaced with a Rebel; the RTU serving the 

northern half of the space with the baseline. Table ES-1 compares their rated performances and 

highlights the high-efficiency components of the Rebel.

Table ES-1. Daikin Applied Rebel and Baseline RTU Rated Performance

Baseline RTU1 Daikin Applied Rebel 

Model DPS010A

Energy 

Efficiency Ratio 

(EER)

2/IEER3

11.3/11.8 12.5/19.4

Net Rated 

Cooling 10 tons 10 tons

Supply Fan

Constant-speed/belt-driven/

National Electrical Manufacturers 

Association (NEMA) standard 

efficiency motor

Variable-speed/direct drive/electronically 

commutated motor (ECM)

Compressors 

2 constant speed scrolls on 2 

separate direct expansion (DX) 

circuits

1 variable-speed scroll and 1 constant-speed 

scroll on a single DX circuit

OA Damper Fixed parallel blade;

No edge/jamb seals

Actuator/linkage-driven opposing blade damper;

Low-leakage damper with edge/jamb seals

Cabinet Casing Single-wall with no insulation Double-wall with foam insulation

Notes: (1) Per UFGS-23 81 00.00 20, the baseline is a code-minimum RTU meeting ASHRAE Standard 90.1-2010 

prescriptive performance requirements of 11.2 EER and 11.4 IEER based on Table 6.8.1A for air conditioners 

≥65,000 British thermal units per hour (Btuh) (5.4 tons) and <135,000 Btuh (11.3 tons). The baseline RTU has basic 

thermostatic control – fan (G), cooling stage 1 (Y1), cooling stage 2 (Y2). (2) EER rated conditions are at an 

ambient dry-bulb of 95°F and a mixed-air dry-bulb of 80°F and wet-bulb of 67°F per the Air-Conditioning, Heating, 

& Refrigeration Institute (AHRI) Standard 340/360-2007. (3) IEER rating incorporates the part load performance of 

an RTU per AHRI Standard 340/360-2007.

NREL stipulated a true apples-to-apples RTU comparison must meet two requirements: (1) both 

RTUs provide the same amount of cooling to achieve the same duty cycle and (2) both RTUs

maintain their respective temperature sensors to ±1°F of a 76°F set point. While operating the 

RTUs simultaneously during the first month of the demonstration period (October 2013), the 

monitored data clearly showed that the first parameter was not achievable. Even though the 

RTUs were conditioning different sides of an open office space, the Rebel RTU was providing 

more than 70% of the cooling and, consequently, was consuming more energy. 

The Rebel provided more cooling because of its single-zone variable-air volume (SZVAV) 

control logic. The Rebel ramps the supply fan from 40%–100% based on the space temperature 

versus set point error. The Rebel then modulates the compressors to maintain a user-specified 

discharge air temperature (DAT). The Rebel would essentially stay on for most of the occupied

hours, nimbly adjusting its compressor capacity to maintain more gradual temperature changes 

within its ±1°F deadband. In contrast, the baseline maintained a constant supply airflow and 

could only control its cooling to either 50% (first stage) or 100% (second stage) capacity. 
ix

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Therefore, NREL shifted tactics. For the remainder of the demonstration period, from November 

2013 through January 2014, NREL alternated baseline and Rebel operation weekly. The 

demonstration data were then used to develop calibrated models of both RTUs. The baseline 

model was calibrated against 36 days of baseline-only operation. The Rebel model was 

calibrated against 35 days of Rebel-only operation. Oahu’s weather year-round is consistent such 

that this limited dataset was sufficient to capture the performance of both RTUs across the year.

Each calibrated model was then simulated across an entire year using Honolulu typical 

meteorological year (TMY3) weather data. The baseline model was simulated as if two baseline 

RTUs were conditioning the entire office space. Similarly, the Rebel model was simulated with 

the entire office space being conditioned by two Rebel RTUs. Both baseline and Rebel models 

incorporated identical building envelope, infiltration, and internal loads. 

The Rebel RTU model provided ventilation that met ASHRAE 62.1-2010 requirements

according to its testing, adjusting, and balancing (TAB) report. The demand-controlled 

ventilation (DCV) capability of the Rebel was not modeled because it is not common on 

NAVFAC facilities. The Unified Field Criteria (UFC) 3-410-01stipulates DCV must receive 

approval from the authority having jurisdiction (AHJ) because of NAVFAC’s concern about the 

carbon dioxide sensors maintaining calibration over time. 

The baseline RTU was found to have an extremely leaky OA damper based on its TAB report. 

Even a fixed 5% OA damper position resulted in a ventilation rate over three times the ASHRAE 

62.1-2010 minimum requirement. NREL found typical RTU OA dampers ranging from 5%–20% 

fixed positions based on site visits to more than 30 RTUs throughout JBPHH. Therefore, NREL 

compared the Rebel model versus the baseline model with (1) a fixed 5% OA damper, (2) a fixed 

20% OA damper, and (3) a ventilation rate exactly meeting the ASHRAE 62.1-2010 minimum

requirements. 

Table ES-2 compares a single 10-ton Rebel RTU to a single 10-ton baseline RTU with a fixed 

5% OA damper configuration. Accounting for the power measurement and model uncertainties, 

the annual energy savings of 3,862 kilowatt-hours (kWh) has a ±27% uncertainty (±1,042 kWh)

based on a 95% confidence interval. Compared to a 10-ton baseline RTU with a fixed 20% OA 

damper, the Rebel saved 4,552 kWh (37%). Compared to a 10-ton baseline RTU exactly 

providing ASHRAE 62.1 ventilation rates, the Rebel saved 3,034 kWh (29%).

In summary, a 10-ton Rebel RTU serving a small office at JBPHH will save 34%–37% 

compared to a code-minimum, baseline RTU with a typical OA damper set to a 5%–20% 

position. If the baseline RTU is specified with a low leakage damper at least meeting leakage 

class 2 per Air Movement and Control Association Standard 511, the Rebel saves 29% for a 

small office at JBPHH. These savings are based on operating the RTUs only during NAVFAC 

Pacific approved HVAC times (see footnote a in Table ES-2).
x

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Table ES-2. Model Energy Usage of One 10-Ton Rebel Versus

One 10-Ton Baseline Serving an Office Space in JBPHH

Baseline RTU 10-Ton 

Fixed 5% OA Dampera

Rebel RTU

10-Tona,b Savings

Supply Fan 2,607 kWh 1,268 kWh 1,339 kWh 

(51%)

Compressors &

Condenser Fan(s) 8,855 kWh 6,332 kWh 2,523 kWh (28%)

Total RTU 11,462 kWh 7,600 kWh 3,862 kWhc

(34%) a Models controlled the baseline and Rebel RTUs to operate only during NAVFAC Pacific approved hours of 0600–

1530 for summer weekdays (May 1-October 31) and 0800–1530 for winter weekdays (November 1-April 30). This 

yields 1,950 operational hours annually. RTUs are turned-off outside these hours. b Rebel provided the minimum ventilation rate per ASHRAE 62.1-2010; DCV capability was not enabled. c ±27% total uncertainty (±1,042 kWh) based on a 95% confidence interval

In 2018, the Rebel model was rerun with a lower fan pressure drop. When the demonstration was 

completed in 2014, Daikin Applied only provided a downward discharge configuration. To 

integrate with the existing ductwork, the installation at the small office used a roof curb to 

transition the airflow from downward to horizontal, resulting in an additional inch of static 

pressure. The Rebel now has a horizontal discharge option. Table ES-3 shows the fan savings 

increased to 71% over the baseline. Across the three baseline damper configurations, the energy 

savings ranged from 33-42%. 

Table ES-3. Updated Model Energy Usage Account for the Rebel Having a Lower Pressure Drop

Baseline RTU 10-Ton 

Fixed 5% OA Dampera

Rebel RTU

10-Tona,b Savings

Supply Fan 2,607 kWh 767 kWh 1,840 kWh 

(71%)

Compressors &

Condenser Fan(s) 8,855 kWh 6,332 kWh 2,523 kWh (28%)

Total RTU 11,462 kWh 7,099 kWh 4,363 kWhc

(38%) 

In addition to energy savings, the Rebel improves thermal comfort compared to the baseline 

RTU. The variable speed fan and variable capacity cooling maintain a smoother, more constant

space temperature throughout the day. The Rebel also maintains a drier space—lower relative 

humidity (RH) and dew point. By controlling to a constant DAT, the Rebel achieves a 

consistently lower discharge air dew point. The modeling results showed that during operational 

hours, the Rebel maintained a 53% annual average space RH compared to the 61% annual 

average space RH for the baseline RTU with a 5% fixed OA damper.

Based on the energy savings from Table ES-2 and the additional cost of the Rebel, NREL 

estimates a total discounted operational savings of $18,000 over a 15-year operational life, with a 

simple payback occurring in the ninth year of operation. Just using the RTU-only cost difference 

between the Rebel versus the baseline – excluding the Rebel’s larger incremental costs for the 

cabinet coating, condenser coil coating, extended 5-year parts and compressor warranties, and 

roof curb – the same energy savings yields a simple payback in the fifth year of operation. No 

utility incentives are included in these paybacks.
xi

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During site inspections, NREL found most office buildings not abiding by the NAVFAC Pacific 

mandated operating hours. Building occupants are over-riding thermostats, enabling cooling 

from typically 0600 to 1800. Therefore, NREL re-calculated the 10-ton Rebel’s annual energy 

savings to be 7,426 kWh based on weekday operation of 0600 to 1800. The baseline had a fixed 

5% damper position. This yielded a simple payback in the fifth year including all incremental 

costs. When excluding these incremental costs, the simple payback was in the third year. 

For next steps, NREL recommends NAVFAC expand the sample size of measured energy 

savings for high-efficiency RTUs, leveraging the DOE-sponsored field demonstrations that will 

be completed in spring 2015. If NAVFAC begins to invest in high-efficiency RTUs, NAVFAC 

service technicians should receive formal training to provide the same level of service they 

currently provide for typical RTUs. Local distributors of high-efficiency RTUs can provide onsite training. Some manufacturers of high-efficiency RTUs provide multiday, formalized training 

at their facilities. These trainings will be crucial for NAVFAC to ensure proper control of the 

advanced features of these high-efficiency RTUs, as well as utilizing the enhanced 

troubleshooting capabilities of the AFDD features.
xii

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Table of Contents

1 Introduction........................................................................................................................................... 1

2 Demonstration Objectives................................................................................................................... 3

2.1 Rooftop Unit and Rated Performance Definition.......................................................................... 3

2.2 High-Efficiency Rooftop Unit Technology Description ............................................................... 4

2.3 Summary of Performance Objectives............................................................................................ 6

3 Demonstration Design ......................................................................................................................... 7

3.1 Demonstration Site Description .................................................................................................... 7

3.2 Baseline Rooftop Unit Description ............................................................................................... 9

3.2.1 ENERGY STAR/Federal Energy Management Program Rooftop Unit Performance 

Requirements.................................................................................................................... 9

3.2.2 ASHRAE 90.1-2010 Rooftop Unit Performance Requirements...................................... 9

3.3 Monitoring Plan........................................................................................................................... 11

3.4 Maintaining Internal Sensible and Latent Loads......................................................................... 13

4 Technical Performance Analysis and Assessment ........................................................................ 14

4.1 Monitored Performance Data for Model Calibration .................................................................. 16

4.1.1 Rebel Rooftop Unit Modeling Process........................................................................... 21

4.1.2 Baseline Rooftop Unit Modeling Process...................................................................... 25

4.1.3 Supply Fan Models......................................................................................................... 27

4.2 Model Results.............................................................................................................................. 28

4.3 Interior Thermal Comfort............................................................................................................ 32

4.4 Ventilation Rates......................................................................................................................... 35

5 Economic Performance Analysis and Assessment........................................................................ 38

6 Project Management Considerations ............................................................................................... 41

6.1 Site Approval, National Environmental Policy Act, and DD1391.............................................. 41

6.2 Contracts and Procurement ......................................................................................................... 41

6.3 Design ......................................................................................................................................... 42

6.4 Installation and Construction (includes permitting, interconnect agreements, factory acceptance 

testing, commissioning)............................................................................................................... 43

6.5 Operation and Maintenance......................................................................................................... 43

6.6 Training ....................................................................................................................................... 44

7 Commercial Readiness Qualitative Assessment ............................................................................ 45

8 Recommended Next Steps ................................................................................................................ 46

Appendix A: ClimaCheck Methodology.................................................................................................. 48

Appendix B: Model Geometry, Envelope, and Internal Loads ............................................................. 50

Appendix C: Rebel Model Summary ....................................................................................................... 52

Supply Fan Model ................................................................................................................................ 53

Outdoor Air Flow Rates ....................................................................................................................... 56

Calibration Results............................................................................................................................... 57

Appendix D: Baseline Model Summary .................................................................................................. 58

Direct Expansion System ..................................................................................................................... 58

Calibration Results............................................................................................................................... 59

Appendix E: Artificial Internal Sensible and Latent Loads................................................................... 60

Appendix F: Baseline and Rebel Monitoring Points ............................................................................. 63

Appendix G: Economic Analysis Details................................................................................................ 70

Economic Analysis Information........................................................................................................... 70

eROI Analyses............................................................................................................................. 70

BLCC Analysis ........................................................................................................................... 71

Appendix H: Uncertainty Analysis .......................................................................................................... 72

Rooftop Unit Power Measurement Uncertainty ................................................................................... 72

Sampling Uncertainty........................................................................................................................... 72
xiii

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EnergyPlus Model Uncertainty ............................................................................................................ 73

Appendix I: Naval Facilities Engineering Command Routine Rooftop Unit Maintenance Procedures

.............................................................................................................................................................. 75
xiv

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List of Figures

Figure 1. RTU schematic showing basic component operation.................................................................... 3

Figure 2. Technologies incorporated into the Daikin Applied Rebel RTU .................................................. 4

Figure 3. (a) Location of building 550 in NAVFAC PAC (Rebel = RTU #1; Baseline = RTU #2) (b) 

Google map satellite image of building 550 ............................................................................ 7

Figure 4. Roof of building 550 showing the existing two Trane TCH120 RTUs......................................... 8

Figure 5. Roof of building 550, which shows the Daikin Applied Rebel and baseline RTU ....................... 8

Figure 6. Unitary air-conditioning equipment (RTUs) efficiency requirements per UFGS 23 81 00.00 20, 

last edited November 2009....................................................................................................... 9

Figure 7. Airside monitoring....................................................................................................................... 11

Figure 8. ClimaCheck methodology to measure temperatures, pressure, and power of the DX circuit to 

calculate real-time cooling capacity and COP ....................................................................... 12

Figure 9. Rebel and baseline RTU simultaneous operation on October 28, 2013: (a) space temperature 

measured by each RTU’s temperature sensor (b) total DX cooling by each RTU ................ 14

Figure 10. Histogram of monitored baseline and Rebel operational cooling capacities............................. 18

Figure 11. Rebel DX power regression modeled versus measured, including uncertainty based on 

CVRMSE ............................................................................................................................... 22

Figure 12. Using DX power regression model to calculate DX cycle performance (EER) for a range of 

DAT, OAT, and capacity fractions........................................................................................ 23

Figure 13. Rebel RTU model versus measured daily RTU energy usage................................................... 24

Figure 14. Baseline RTU DX power regression (including compressors and condenser fans).................. 26

Figure 15. Baseline RTU model versus measured daily DX energy usage ................................................ 27

Figure 16. Baseline and Rebel annual operating hours at different capacity bins...................................... 30

Figure 17. Baseline and Rebel daily energy usage versus daily average dry-bulb temperature ................. 30

Figure 18. Office space dry-bulb temperature histogram comparing the Rebel model versus the baseline 

model with a fixed 5% OA damper position.......................................................................... 33

Figure 19. Measured (not modeled) space temperature fluctuation across the day between the Rebel RTU 

at a 76°F set point and baseline RTU at a 68°F set point....................................................... 34

Figure 20. Office space RH histogram comparing the Rebel model versus the baseline model with a 5% 

OA damper position............................................................................................................... 35

Figure 21. Sensitivity analysis on electricity pricing.................................................................................. 40

Figure A-1. Rebel refrigerant-side monitoring (instance December 10, 2013 6:40).................................. 48

Figure A-2. Baseline refrigerant-side monitoring (instance December 4, 2013 13:00).............................. 49

Figure B-1. Southeast view of building 550 model .................................................................................... 50

Figure C-1. Correlation between supply fan controller speed setting and supply air flow rate based on 

TAB........................................................................................................................................ 53

Figure C-2. (a) Regression model of supply fan pressure and efficiency as a function of flow fraction (b) 

EnergyPlus model of supply fan power based on flow fraction............................................. 54

Figure C-3. Projected error timeline from MicroTech III unit controller operation manual ...................... 56

Figure C-4. OA flow rates based on the supply air flow rate (a) shows flow rates in cfm and (b) shows 

regression equations relating OA mass flow rates to supply air mass flow rates used in the 

EnergyPlus model of the Rebel RTU..................................................................................... 56

Figure C-5. Rebel RTU model versus measured daily RTU energy usage................................................. 57

Figure C-6. Rebel RTU model versus measured space dry-bulb and dew point ........................................ 57

Figure D-1. Baseline RTU model versus measured daily DX energy usage .............................................. 59

Figure D-2. Baseline RTU model versus measured space dry-bulb and dew point.................................... 59

Figure H-1. NAVFAC quarterly RTU maintenance procedure .................................................................. 75
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List of Tables

Table ES-1. Daikin Applied Rebel and Baseline RTU Rated Performance ..............................................viii

Table ES-2. Model Energy Usage of One 10-Ton Rebel Versus One 10-Ton Baseline Serving an Office 

Space in JBPHH....................................................................................................................... x

Table ES-3. Updated Model Energy Usage Account for the Rebel Having a Lower Pressure Drop ........... x

Table 1. Performance Objectives Defining How the Daikin Applied Rebel RTU Was Compared Against 

the Code-Minimum, Baseline RTU ......................................................................................... 6

Table 2. Performance and Component Comparison Between the Baseline RTU and the Daikin Applied 

Rebel ...................................................................................................................................... 10

Table 3. Artificial Internal Sensible and Latent Loads Established to Represent a Typical Office Space . 13

Table 4. Performance Comparison Between Baseline and Rebel RTUs on October 28, 2013................... 15

Table 5. Summary of Performance Data Used to Develop and Calibrate the Baseline and Rebel Energy 

Models Across Dates November 10, 2013, through January 26, 2014.................................. 15

Table 6. Performance Objective Results..................................................................................................... 16

Table 7. Rebel and Baseline Control Parameters During Demonstration Period ....................................... 17

Table 8. Monitored Daily Rebel RTU Performancea

.................................................................................. 20

Table 9. Monitoring Daily Baseline RTU Performancea ............................................................................ 20

Table 10. Rebel RTU DX Power Regression Model Parameters ............................................................... 23

Table 11. Baseline RTU DX Power Regression Parameters (including Compressors and Condenser Fans)

................................................................................................................................................ 26

Table 12. Supply Fan Comparison.............................................................................................................. 27

Table 13. Rebel and Baseline Control Parameters...................................................................................... 28

Table 14. Modeled Annual Energy Consumption and Savings Between One 10-Ton Rebel RTU Versus 

One 10-Ton Baseline RTU Serving the Building 550 Small Office Space ........................... 29

Table 15. Modeled Rebel Savings Over the Baseline RTU Maintaining Different Ventilation Flow Rates

................................................................................................................................................ 31

Table 16. Office Minimum Ventilation Rates per ASHRAE Standard 62.1-2010 ..................................... 36

Table 17. Baseline RTU Ventilation Flow Rates........................................................................................ 36

Table 18. Rebel Ventilation Flow Rates..................................................................................................... 37

Table 19. Overall Economic Analysis of Rebel RTU Demonstration ........................................................ 39

Table 20. Summary of Programmatic Elements......................................................................................... 41

Table 21. Applicable Division 01, General Requirements ......................................................................... 42

Table 22. UFGS Facility Construction/Technical Design Specifications Used in the Construction Activity

................................................................................................................................................ 43

Table 23. Commercially Available DOE RTU Challenge RTUs............................................................... 45

Table B-1. Summary of Building Envelope and Internal Load Parameters................................................ 51

Table C-1. Rebel RTU Supply Fan Performance Based on TAB Report................................................... 53

Table C-2. Fan Operational Sequence Based on Startup ............................................................................ 55

Table D-1. Baseline RTU Cooling Capacity Regression Parameters......................................................... 58

Table E-1. Overhead Lighting Power and Schedule Maintained During the Demonstration Period ......... 60

Table E-2. NREL Installed Heat Lamps to Represent the Sensible Loads from Occupants and Plug Loads

................................................................................................................................................ 61

Table E-3. Total Internal Sensible Heat Gain from Overheat Lighting and NREL’s Installed Heat Lamps 

on Timers ............................................................................................................................... 61

Table E-4. NREL Set Up Humidifiers on Timers to Represent the Total Internal Latent Heat Gain from 

Occupantse

.............................................................................................................................. 62

Table F-1. Baseline RTU Monitoring Points.............................................................................................. 63

Table F-2. Rebel Monitoring Points ........................................................................................................... 64

Table G-1. Summary of Key Information Regarding the eROI Analyses Developed for This Project...... 70
xvi

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Table G-2. Summary of Key Information Regarding the Building Life-Cycle Cost Analyses Developed 

for This Project....................................................................................................................... 71
1

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1 Introduction

To meet its energy goals, the Naval Facilities Engineering Command (NAVFAC) partnered with 

the U.S. Department of Energy’s (DOE) National Renewable Energy Laboratory (NREL) to 

rapidly demonstrate and deploy cost-effective renewable energy and energy efficiency 

technologies. This is one of several demonstrations of new or underutilized energy technologies. 

The common goal is to demonstrate and measure the energy savings and return on investment 

(ROI) of the system while monitoring any ancillary impacts to related standards of service and 

operation and maintenance (O&M) practices. 

The standards of service may include acceptable temperature and relative humidity (RH) ranges, 

power quality, allowable setbacks, noise criteria, air quality parameters, light levels, and other 

related factors. In short, demonstrations at U.S. Department of Defense (DOD) facilities 

simultaneously evaluate the benefits and compatibility of the technology with the DOD mission, 

and with its design, construction, and O&M practices.

The consistent year-round demand for cooling and dehumidification in Hawaii and Guam 

provide ideal locations for realizing significant energy savings from high-efficiency heating, 

ventilation, and air conditioning (HVAC) systems. Many of NAVFAC’s small- to medium-size 

facilities are conditioned by packaged roof top units (RTUs). These facilities include offices, 

warehouses, gymnasiums, commissaries, exchange stores, and hangars. 

The term packaged RTU refers to a pre-engineered unitary system that houses all the components 

of an HVAC system. For Hawaii and Guam, RTUs need to provide cooling and ventilation only.

Therefore, the DOD has a significant amount of conditioned square footage that can leverage 

high-efficiency RTUs to reduce energy usage while improving thermal comfort. 

The performance range from code-minimum to the highest efficiency RTUs was not that 

significant until the past couple years. To help incentivize manufacturers to build higher 

performance RTUs, DOE issued the High-Performance Rooftop Unit Challenge in January 2011

to:4

catalyze the market introduction of cost-effective, energy-saving RTUs that would 

significantly outperform any models that were currently available. RTUs built 

according to the specification are expected to reduce energy use by as much as 

50% compared to the current ASHRAE 90.1 Standard, depending on location and 

facility type. 

To achieve the DOE RTU Challenge status, RTUs that range from 10 to 20 tons must meet a 

comprehensive specification codeveloped by DOE national labs, including NREL, and private 

sector building owners with large building portfolios (i.e., Target, Walmart).

5 The primary 

specification requirements include a minimum integrated energy efficiency ratio (IEER) of 18.0, 

 4 “DOE Facilitates Market-Driven Solutions to Develop and Deploy New High-Efficiency Commercial Air 

Conditioners.” U.S. Department of Energy, Office of Energy Efficiency & Renewable Energy, February 3, 2011. 

http://apps1.eere.energy.gov/news/news_detail.cfm/news_id=16696. 5 “Install units produced by the High-Performance Rooftop Unit Challenge that meet the high-performance rooftop 

unit specification.” U.S. Department of Energy, Office of Renewable Energy & Energy Efficiency, undated. 
2

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a variable- or multispeed supply fan, direct digital controls, and automated fault detection and 

diagnostics (AFDD).

In May 2012,

6 the Daikin Applied Rebel7 was the first commercially available RTU to meet the 

DOE High Performance Rooftop Unit Challenge. The following field demonstration compared 

the performance of the Daikin Applied Rebel against a code-minimum, baseline RTU serving a 

small office building on NAVFAC Pacific (PAC). 

 6 “Energy Department Announces First Product to Meet the Commercial Rooftop Air Conditioner Challenge.” U.S. 

Department of Energy, Office of Renewable Energy & Energy Efficiency, May 24, 2012. 

http://apps1.eere.energy.gov/news/progress_alerts.cfm/news_id=20367. 7 “Rebel Overview.” Daikin Applied, 2014. www.go.Rebel.com/rebel. 
3

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2 Demonstration Objectives

The demonstration objectives were to evaluate the energy savings, ROI, and thermal comfort 

impact of the Daikin Applied Rebel against a code-minimum, baseline RTU.

2.1 Rooftop Unit and Rated Performance Definition

To better understand the basic function of an RTU, Figure 1 shows the components and 

airstreams. An RTU uses a supply fan to draw in return air from the conditioned space along 

with a controlled amount of outdoor air (OA) needed to ventilate the space. The mixed air is then 

cooled as it passes through a direct expansion (DX) evaporator coil. For the humid Hawaiian

climate, the DX coil also dehumidifies by condensing moisture out of the mixed air stream. For 

maintaining space comfort in Hawaii and Guam, dehumidifying the air (latent cooling) is as 

important as sensible cooling. Sometimes, RTUs include exhaust fans that push some of the 

return air outside, although neither of the RTUs in this demonstration included exhaust fans. 

Figure 1. RTU schematic showing basic component operation

(Credit: Eric Kozubal, NREL)

The refrigerant in the evaporator coil is pumped by the compressor to the condenser coil. Here, 

the DX cycle rejects the heat by blowing OA across the condenser coil. RTUs with 10 tons of 

cooling operate with two compressors that can be “staged”, operating one or two at a time.

RTU-rated performance is based on the applicable American National Standards Institute 

(ANSI)/Air-Conditioning, Heating, & Refrigeration Institute (AHRI) standards. For RTUs lower 

than 65,000 British thermal units per hour (Btuh) (5.4 tons), ANSI/AHRI 210/240-2008 defines 

an energy efficiency ratio (EER) to characterize peak operational performance and a seasonal 

energy efficiency ratio (SEER) to represent cooling season average performance. Larger RTUs 

adhere to ANSI/AHRI 340/360-2007, which also uses EER to define peak performance but 

defines a separate IEER to represent cooling season average performance. Compared to EER, the 

seasonal performance ratings, SEER and IEER, provide a better indication of annual energy 

usage. Consequently, the DOE RTU challenge mandated a minimum 18.0 IEER rating, rather 

than stipulating an EER rating because annual energy savings was the goal.
4

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2.2 High-Efficiency Rooftop Unit Technology Description

The Daikin Applied Rebel exceeds the 18.0 IEER by packaging multiple advanced technologies 

and control capabilities. These include a variable-speed direct-drive supply fan, variable-speed 

condenser fans, and a variable-speed first-stage compressor (second-stage compressor is constant 

speed). A sophisticated programmable logic controller (PLC) controls all the components and 

includes AFDD along with open protocol communication (BACnet IP, BACnet MSTP, and 

LonMark). 

As Hawaii does not need heating, the Rebel unit demonstrated did not have gas heating. Yet,

because of an ordering mix-up, the Rebel delivered was a heat pump RTU. The heat pump

operational mode was never utilized during the demonstration. The marketing schematic 

developed by Daikin Applied, shown in Figure 2, highlights these advanced components and 

control features of the Rebel.

Figure 2. Technologies incorporated into the Daikin Applied Rebel RTU 

Source: Daikin Applied
5

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The Daikin Applied Rebel achieves improved energy and thermal comfort performance over a 

code-minimum, baseline RTU by incorporating the following technologies:

Direct-drive, variable-speed supply fan. RTUs are typically configured with a constantspeed supply fan that moves more air than necessary for most of the year. These constant 

flow rates are sized to meet the worst-case design condition. These worst-case design 

conditions typically represent fewer than 100 hours of the year. The Rebel uses a variablespeed electronically commutated motor (ECM) to directly drive the supply fan, eliminating 

the need for a fan belt. The Rebel supply fan can be controlled in three ways:

o Duct static pressure control for standard variable air volume (VAV) applications,

o Constant air volume (CAV) and

o Single-zone variable-air volume (SZVAV).

NREL configured the Rebel for SZVAV control, which changes the fan speed based on the 

space temperature relative to the temperature set point. See Appendix C for a detailed 

summary of the supply fan proportional-integral [PI] control sequence. Consequently, the 

supply fan will move only enough air as necessary, based on the space demands. 

Variable refrigerant flow. Daikin Applied packaged its variable-refrigerant flow technology 

into the Rebel’s DX system. The lead compressor is an inverter-driven scroll. Rebels larger 

than 5 tons have a second-stage, constant-speed compressor. Both variable- and fixed-speed 

compressors are part of the same DX circuit. By ramping the variable-speed lead compressor, 

the Rebel provides the proper amount of cooling to meet the space’s needs whether at part 

load or extreme design conditions. Comparatively, code minimum RTUs achieve cooling

load control based on the number of separate compressor stages. The Rebel also leverages 

electronic expansion valves to achieve improved refrigerant flow control (i.e., tight 

superheat) compared to standard thermostatic expansion valves.

In addition to greater control of space temperature and RH, the variable-refrigerant flow 

technology improves the refrigeration cycle efficiency because the full-load heat transfer 

surface area on the evaporator and condenser coils is available for low-load conditions. The

improved part-load efficiency is reflected in the 10-ton Rebel’s 19.4 Btuh/W8 IEER. For 

context, a 10-ton code-minimum RTU is 11.4 IEER, according to ASHRAE 90.1-2010.

Variable-speed condenser fans. The Rebel’s two condenser fans are variable speed, which 

are controlled to maintain the refrigerant saturated condensing temperature (discharge 

pressure) a specified delta-T above ambient dry-bulb. For this demonstration, the condenser 

fan speeds were controlled to maintain a 10°F delta-T. Compared to constant-speed 

condenser fans, the Rebel can achieve improved refrigerant discharge pressure and 

subcooling control to enhance performance at part-load conditions.

Low-leakage OA damper. Standard RTU OA dampers are notoriously leaky and typically 

not certified under Air Movement and Control Association Standard 511. The Rebel has 

vinyl gasket, motorized blade dampers that maintain low leakage.

 8 Based on AHRI Certified Reference Number 5056846. 
6

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Demand-controlled ventilation (DCV). RTUs are typically configured with an OA flow 

rate based on the expected maximum number of occupants. Yet most spaces typically 

experience occupancy rates well below this number throughout most of the year. The Rebel

has DCV capability in which, based on the return air carbon dioxide (CO2) concentration, the 

OA damper will open beyond a set minimum OA flow rate to meet the ventilation needs of 

the space. However, Unified Facilities Criteria (UFC) 3-410-01 Section 401.1 (dated July 1, 

2013) states “Use of CO2 sensors for ventilation control is prohibited unless approved by 

AHJ” Based on this requirement, NREL did not demonstrate the Rebel enabled with DCV. 

Dual enthalpy economizing. In many U.S. climates, during cooling demands, the OA

temperature and RH may be low enough to use in lieu of—or in conjunction with—

compressor-based cooling. The Rebel’s advanced controller has the ability to leverage 

multiple economizer control sequences, including fixed dry-bulb, dual dry-bulb, and dual 

enthalpy. However, Hawaii has such a humid climate that none of the economizing features 

of the Rebel were initiated for the demonstration.

2.3 Summary of Performance Objectives

NREL developed a list of performance objectives to evaluate the Daikin Applied against the 

baseline RTU. Table 1 defines each performance objective, the data required, and how success 

was defined.

Table 1. Performance Objectives Defining How the Daikin Applied Rebel RTU

Was Compared Against the Code-Minimum, Baseline RTU

Performance 

Objective Metric Data Requirements Success Criteria

1. Annual 

energy 

savings

Annual kilowatt-hour 

savings 

Calibrated energy models of 

the baseline and Rebel RTUs,

based on measured 

performance data

Rebel reduces energy 

usage by at least 30% 

compared to the Baseline 

RTU

2. Interior 

thermal 

comfort

improvement

Space temperature 

and RH during 

occupied hours 

Measurements of space 

temperature and RH;

calibrated energy models of 

the baseline and Rebel RTUs,

based on measured 

performance data

Rebel maintains a narrower 

temperature band and 

lower annual average RH

by at least 5%

3. Proper 

ventilation 

rates and 

reduced OA 

damper 

leakage

Leakage flow rates 

while OA damper is 

closed; Proper 

ventilation flow rates 

maintained during 

occupied hours per 

ASHRAE Standard 

62.1-2010

Testing, adjusting, and

balancing (TAB) OA flow rates 

measured at different OA 

damper positions and fan 

speeds

Rebel reduces OA damper 

leakage by 30% compared 

to the baseline RTU; Rebel 

maintains proper ventilation 

rates during occupied hours
7

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3 Demonstration Design

The performance benefits of the Daikin Applied Rebel were compared against a code-minimum 

baseline RTU that the Navy would typically purchase adhering to Unified Facilities Guide 

Specifications (UFGS) and UFC requirements. After evaluating potential demonstration sites 

across Joint Base Pearl Harbor-Hickam (JBPHH) and NAVFAC PAC, NAVFAC and NREL 

determined building 550 NAVFAC PAC Public Works was an ideal configuration with two 

identically sized RTUs serving a typical small office space. The following section summarizes 

building 550 characteristics and thermal loads, the baseline RTU, thermostat set point schedules, 

and the calibrated energy models.

3.1 Demonstration Site Description

Building 550, NAVFAC PAC Public Works, is a two-story building built in 1946, which is 

broken up into four separate facilities. Figure 3 shows how the Rebel and baseline RTUs serve 

one of these facilities, a 4,976-ft2 office space on the second floor. Figure 3 shows the location of 

building 550 inside NAVFAC PAC and details the location of the second-floor office space on 

the northern side of the building. Based on NAVFAC’s property record (iNFAD) report, building 

550 has a total of 26,313 ft2. Therefore, the second-floor office space comprises 19% of the total 

floor area. Figure 4 shows the roof of building 550 with the two 17-year-old (built in 1996) 10-

ton Trane RTUs that were replaced. Figure 5 shows the Daikin Applied Rebel and baseline RTU

on the roof of building 550.

(a) (b)

Figure 3. (a) Location of building 550 in NAVFAC PAC (Rebel = RTU #1;

Baseline = RTU #2) (b) Google map satellite image of building 550

Source: (a) JBPHH Building Site Map provide by NAVFAC (b) Google Earth

North North

Second Floor 

Office Location

Daikin 

Applied

Rebel

Baseline RTU
8

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Figure 4. Roof of building 550 showing the existing two Trane TCH120 RTUs

Figure 5. Roof of building 550, which shows the Daikin Applied Rebel and baseline RTU

RTU #1 replaced by 

Daikin Applied Rebel

RTU #2 replaced 

by Baseline RTU

Daikin Applied Rebel

Baseline RTU
9

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3.2 Baseline Rooftop Unit Description

The Daikin Applied Rebel was compared against a baseline code-minimum RTU meeting UFC 

3-410-019 Heating, Ventilating, and Air Conditioning Systems (dated July 1, 2013) and UFGS23 81 00.00 2010 Unitary Air Conditioning Equipment. Per Part 2 of UFGS 23 81 00.00 20 

(shown in Figure 6), RTUs must exceed the minimum performance requirements of ASHRAE 

Standard 90.1-2010, ENERGY STAR®, and the Federal Energy Management Program (FEMP). 

Therefore, these three references were evaluated to confirm the baseline RTU met the most 

stringent requirements. 

Figure 6. Unitary air-conditioning equipment (RTUs) efficiency requirements

per UFGS 23 81 00.00 20, last edited November 2009

3.2.1 ENERGY STAR/Federal Energy Management Program Rooftop Unit

Performance Requirements

FEMP requirements11 state “Federal purchases of light commercial heating and cooling 

equipment must be ENERGY STAR qualified.” The ENERGY STAR website reveals RTUs 

lower than 65,000 Btuh (approximately 5 tons) must meet a minimum 11.0 EER and 14.5 

SEER.

12 Because this demonstration was for a 10-ton RTU, the FEMP/ENERGY STAR 

requirements did not apply.

3.2.2 ASHRAE 90.1-2010 Rooftop Unit Performance Requirements

Based on ASHRAE Standard 90.1-2010, Table 6.8.1A stipulates for nominal tonnages ≥ 65,000 

Btuh and < 135,000 Btuh, RTUs must exceed 11.2 EER and 11.4 IEER. Consequently, NREL 

specified a baseline RTU that just exceeds the ASHRAE Standard 90.1-2010 requirements to 

represent the baseline, code-minimum RTU (Table 2). Beyond the EER and IEER performance 

requirements, the baseline represents a typical RTU installed today at JBPHH with a constant-

 9 National Institute of Building Sciences, Whole Building Design Guide, Unified Facilities Criteria 3-410-01: 

www.wbdg.org/ccb/browse_cat.php?c=4. 10 National Institute of Building Sciences, Whole Building Design Guide, Unified Facilities Guide Specifications 23 

81 00.00 20: www.wbdg.org/ccb/browse_cat.php?c=3. 11 “Covered Product Category: Light Commercial Heating and Cooling.” U.S. Department of Energy, Office of 

Energy Efficiency & Renewable Energy, April 24, 2014. http://energy.gov/eere/femp/covered-product-categorylight-commercial-heating-and-cooling. 12 “Air-Source Heat Pumps and Central Air Conditioners Key Product Criteria.” ENERGY STAR, April 24, 2014. 

www.energystar.gov/index.cfm?c=airsrc_heat.pr_crit_as_heat_pumps.
10

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speed fan and standard thermostatic control. Although the OA damper can modulate, for this 

demonstration it was controlled to be fixed at a specified position.

Table 2. Performance and Component Comparison Between the

Baseline RTU and the Daikin Applied Rebel

Baseline RTU 1 Daikin Applied Rebel 

Model DPS010A

EER 2

(note ASHRAE 90.1-2010 = 

11.2 EER)

11.3 12.5

IEER 3

(note ASHRAE 90.1-2010 = 

11.4 IEER)

11.8 19.4

Gross Cooling Capacity at 

EER-rated conditions [Btuh] 124,700 Btuh 122,000 Btuh

Gross Cooling Capacity at 

EER-rated conditions (tons) 10.4 tons 10.2 tons

Supply Fan

Constant speed/belt 

driven/National Electrical 

Manufacturers Association 

(NEMA) standard efficiency motor

Variable-speed/direct-drive/ECM

Refrigeration Circuit(s)

Two DX circuits with thermostatic 

expansion valves/constant speed 

scroll compressors

Single DX circuit served by one

variable-speed scroll compressor 

and one constant speed scroll 

compressor with electronic 

expansion valves

Condenser Fan(s) Two fans at constant speed with 

NEMA standard efficiency motors

Two fans at variable speed

OA Damper

Gear-driven parallel blade damper 

with direct coupled actuator

No edge or jamb seals: ASHRAE 

90.1-2010 code-min leakage

Not certified to Air Movement and 

Control Association Standard 511

Actuator/linkage-driven opposing

blade damper

Low-leakage damper with edge and 

jamb seals

Humidity Control Hot gas reheat coil Modulating hot gas reheat coil

Cabinet Casing Single-wall with no insulation Double-wall with foam insulation

Notes: (1) Per UFGS-23 81 00.00 20, the baseline is a code-minimum RTU meeting ASHRAE Standard 90.1-2010 

prescriptive performance requirements of 11.2 EER and 11.4 IEER, based on Table 6.8.1A for air conditioners ≥

65,000 Btuh (5.4 tons) and < 135,000 Btuh (11.3 tons). RTU has a constant-speed supply fan, fixed outdoor-air 

damper, and basic thermostatic control. (2) EER-rated conditions are at an ambient dry-bulb of 95°F and a mixed air 

dry-bulb of 80°F/wet-bulb of 67°F per AHRI Standard 340/360-2007. (3) IEER rating represents the part-load 

performance of an RTU per AHRI Standard 340/360-2007.
11

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3.3 Monitoring Plan

A Web-based building management system called the eIQ13 was installed on site and enabled 

cellular control and monitoring of both RTUs. The baseline RTU was fitted with an advanced 

RTU control system called the CATALYST.

14 The CATALYST changes the supply fan to 

variable speed, controls the OA damper, and sequences the compressors. Through the eIQ, the 

CATALYST system was controlled remotely based on the defined baseline operation. The 

CATALYST also provided RTU operation and airside and power monitoring points, which are 

summarized in Table F-1 in Appendix F. Through BACnet, the eIQ also controlled the Rebel and 

monitored its internal points, which are summarized in Table F-2 in Appendix F. Figure 7

provides the power and airside measurements for both RTUs.

Figure 7. Airside monitoring

Credit: Al Hicks, NREL

Beyond the airside and total power monitoring, NREL monitored the refrigerant side in detail to 

implement a methodology that would calculate total DX cooling capacity and coefficient of 

performance (COP) in real time. Figure 8 and equations 1–3 provide a summary of the 

methodology for a simple DX circuit. By measuring the refrigerant temperature and pressure at 

points 1, 2, and 3 on the DX circuit and assuming the compressor jacket heat loss, the DX COP

can be calculated in real time. Then, by measuring the compressor power, the real time cooling 

capacity can be calculated. When the DX circuit has achieved steady state, typically 2 minutes

after the compressor starts, the ClimaCheck methodology provides performance accuracy to ±5% 

 13 “eIQ Platform.” Transformative Wave Technologies, undated. https://transformativewave.com/technologysolutions/eiq-platform. 14 “Catalyst.” Transformative Wave Technologies, 2013. https://transformativewave.com/technologysolutions/catalyst. 
12

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and capacity accuracy to ±7%.

15 Appendix A summarizes the ClimaCheck methodology in more 

detail.

(a) (b)

Figure 8. ClimaCheck methodology to measure temperatures, pressure, and power of the

DX circuit to calculate real-time cooling capacity and COP

CCCCCCCCCCCCCC = hh11−hh33

hh22−hh11

∗ (11 − cccc_hhhhhhhh_ llll) (1)

RR RRRRRRRR rr MM MM = cccc_ ∗(11− cccc_hhhhhhhh_ llll)

hh −hh (2)

RR TT CCCCCCCC CC CC CC = CCCCCCCCCCCCCC ∗ cccc_ (3)

where

h1 is the superheated refrigerant enthalpy entering the compressor

h2 is the superheated refrigerant enthalpy leaving the compressor

h3 is the subcooled refrigerant enthalpy entering the thermostatic expansion valve

comp_power is the power of the DX compressor

comp_heat_loss is the percentage of the compressor power loss to the ambient 

environment (power not delivered to the refrigerant).

 15 Berglof, K. Performance Inspections with Innovative Analyzing Equipment Results in Significant Energy Savings 

in Air-Conditioning and Refrigeration Systems. Accessed January 10, 2013: www.eeswest.com/wpcontent/themes/xero/pdf/pr-berglof-performance-inspections-iir-prag-2011(v2).pdf.
13

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3.4 Maintaining Internal Sensible and Latent Loads

Soon after both RTUs were installed, building 550’s occupants in the second-floor office space 

were moved to another office location. Fortunately, NREL had monitored the space temperature, 

space RH, and power consumption of the original Trane TCH120 RTUs from December 2012 

through May 2013 prior to installing the new RTUs. Based on these monitored data and on 

interviews with the original occupants of the second-floor space, NREL installed heat lamps and 

humidifiers on timers to represent typical office space sensible and latent internal loads. 

NAVFAC personnel were also scheduled to turn on/off the overhead lights. Table 3 provides a 

summary of the artificial loads. Appendix E reviews the sensible and latent loads maintained in 

the space during the demonstration period in more detail.

Table 3. Artificial Internal Sensible and Latent Loads Established

to Represent a Typical Office Space

Load and Schedule Schedule/Notes

Overhead Lights 1 W/ft2 NAVFAC personnel would turn lights 

on at 0700 and off at 1700

Occupancy

34 occ [146 ft2/occ]

Sensible = 8,500 Btuh (250 Btuh/occ)

Latent = 4.2 gal/day (200 Btuh/occ)

Timers would control to 0700–1700

Sensible represented by heat lamps

Latent represented by humidifiers

Plug Loads 0.4 W/ft2

Timers would control to 0700–1700

Sensible represented by heat lamps

Office plug loads are not a latent load
14

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4 Technical Performance Analysis and Assessment 

The demonstration was initiated as planned, with simultaneous operation of the baseline and 

Rebel RTUs cooling to the same 76°F set point. However, the monitored data clearly showed the 

Rebel and baseline RTUs interact with the space very differently. The Rebel’s set point

deadbands and control logic differ from the baseline in a way that caused the Rebel to provide 

more than 70% of the cooling and, consequently, use more energy. 

The Rebel has a 2°F (±1°F) control deadband about the set point. The baseline’s control 

deadband was +0.5° to +1°F above the set point for first stage and +1° to +1.5°F above the set

point for second stage. Therefore, given the same temperature set point of 76°F, the Rebel would 

maintain a slightly cooler temperature range of 75°–77°F compared to the baseline range of 

76.5°–77.5°F.

In the hope of balancing out the loading, NREL compensated for the deadband control difference 

by setting the baseline RTU set point to 74.5°F, while the Rebel continued to control to a 76°F

set point. Figure 9(a) shows how offsetting the baseline set point resulted in both RTUs 

maintaining their respective sections of the office space within ±1°F. These set points are

recommended for use after the demonstration period.

However, the Rebel RTU still provided most of the cooling because its control logic maintains 

the compressor on for almost the entire cooling period shown in Figure 9(b). Comparatively, the 

baseline cycles its compressors. Table 4 provides a daily summary between the RTUs. While the 

Rebel maintained a higher daily average EER, it provided more than twice the cooling and 

consumed significantly more energy than the baseline unit. This is fine for long-term 

conditioning of the space, but it did not meet the needs of the demonstration, as NREL needed 

the RTUs evenly loaded to provide a true comparison. 

(a) (b)

Figure 9. Rebel and baseline RTU simultaneous operation on October 28, 2013: (a) space 

temperature measured by each RTU’s temperature sensor (b) total DX cooling by each RTU

74

75

76

77

78

79

80

81

82

83

84

5:00 6:00 7:00 8:00 9:00 10:00 11:00 12:00 13:00 14:00 15:00 16:00

Respective Space Temperature Sensor [°F]

Time of Day

Baseline Space Temperature Sensor 10-28-13

McQuay Space Temperature Sensor 10-28-13

0.0

2.0

4.0

6.0

8.0

10.0

12.0

14.0

16.0

5.00 6.00 7.00 8.00 9.00 10.00 11.00 12.00 13.00 14.00 15.00 16.00

Total DX Cooling (tons)

Time of Day

Baseline Total Cooling 10-28-13

McQuay Total Cooling 10-28-13
15

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Table 4. Performance Comparison Between Baseline and Rebel RTUs on October 28, 2013

Baseline RTU Rebel RTU

Total Cooling Delivereda 34 ton-h 69 ton-h

DX Energyb 30 kWh 52 kWh

Supply Fan Energy 18 kWh 6 kWh

Daily Average EERc 8.6 14.1d

a Calculated based on the ClimaCheck methodology. b Includes compressors, condenser fans, and controller. c Includes supply fan energy. d Discharge air temperature (DAT) set point to 55°F (daily average EER equals 

17–19 with a 60°F DAT set point). 

Therefore, NREL modified its demonstration plan to run the units independently, alternating 

weeks between the Rebel and the baseline RTU operations, starting in November 2013. Because 

the space was unoccupied during the demonstration period, NREL was not concerned about 

leaving half the space unconditioned. The focus of the demonstration period was collecting 

calibration data for baseline and Rebel energy models. The performance data collected are 

described in Section 4.1. 

Table 5 provides a summary of the demonstration data utilized for both model calibrations. The 

total number of days shown in Table 5 does not include the demonstration period days in 

October 2013 when both RTUs were being run simultaneously. Although NREL could not use 

days of simultaneous day operation for calibrating the models (could only use alternating 

operational days), the performance data were still useful in developing DX performance models 

of the baseline and Rebel RTUs, which are summarized in Section 4.1.

Table 5. Summary of Performance Data Used to Develop and Calibrate the Baseline and

Rebel Energy Models Across Dates November 10, 2013, through January 26, 2014

Rebel Measured 

Performance Data

Used for Calibration

Baseline Measured 

Performance Data

Used for Calibration

Days of Operation 35 days 36 days 

DX Operation Time 262 h 241 h

Supply Fan Operation Time 332 h 342 h

To achieve a true RTU comparison, NREL used the calibrated models of the baseline and Rebel

RTUs to simulate each conditioning building 550. The methodology used to calibrate each model 

is summarized in Section 4.1, Appendix C, and Appendix D. The baseline model was simulated 

as if two Baseline RTUs were conditioning the entire space. Similarly, the Rebel model was 

simulated with the entire space being conditioned by two Rebel RTUs. Both models incorporated 

identical building envelope, infiltration, and internal loads (Appendix E). The internal space 

loads mirrored the artificial sensible and latent heat gains maintained during the actual 

demonstration period (Section 3.4). The results from the calibrated models addressed the 

demonstration objectives of energy savings and thermal comfort described in Sections 4.2 and
16

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4.3, respectively. The TAB results addressed the ventilation demonstration objectives in Section 

4.4. Table 6 summarizes the performance objective results.

Table 6. Performance Objective Results

Performance 

Objective Success Criteria Results

1 Annual Energy 

Savings

The Rebel reduces 

energy usage by at least 

30% compared to the 

baseline RTU

The Rebel met the energy savings 

demonstration objective. The calibrated 

energy models showed the Rebel saving 

34%–37% annual energy compared to a 

baseline RTU with a typical leaky OA 

damper fixed at a 5%–20% position.

2

Interior 

Thermal 

Comfort

The Rebel maintains a 

narrower temperature 

band and lower annual 

average RH by at least 

5%

The temperature band for both RTUs 

depends on their respective deadbands. 

Based on its default setting, the Rebel

maintains a ±1°F temperature band while 

the baseline maintains a ±0.5°F 

temperature band. Yet despite a larger 

temperature band, the Rebel provides 

improved thermal comfort because it 

maintains a more stable space temperature. 

The modeling results show the Rebel

maintains a drier space with the annual 

average space RH (during operational 

hours) being 8% lower than that of the 

baseline RTU model.

3 Ventilation 

Quality

The Rebel reduces OA 

damper leakage by 30% 

compared to the baseline 

RTU; Rebel and baseline

maintain proper 

ventilation rates during 

occupied hours

The Rebel and Baseline met the minimum 

ventilation rates according to ASHRAE 

62.1-2010. Compared to the leaky baseline 

OA damper, the Rebel maintained ~60% 

reduction in ventilation flow rate while still 

meeting ASHRAE 62.1 minimum ventilation 

rates.

4.1 Monitored Performance Data for Model Calibration

The models were calibrated using performance data from November 10, 2013, through January 

25, 2014. To achieve a larger cross section of operation, the control parameters were modified 

during the demonstration period (see Table 7). The Rebel RTU supply fan speed was controlled 

to modulate at 34%–100%. The Rebel compressors throttled to maintain a DAT set point from 

55°–65°F. NREL changed the DAT set point during the demonstration period to capture the 

impact of different suction pressures on performance. 
17

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Table 7. Rebel and Baseline Control Parameters During Demonstration Period

Rebel Baseline

Temperature Set Point 

Schedule

Ranged from 70°–76°F

0600–1530

Ranged from 68°–76°F

0600–1530

Temperature Control 

Deadband ±1.0°F 1st stage: +0.5 to +1.02nd stage: +1.0 to +1.5

Temperature Set Back 100°F 100°F

Humidity Control None None

DAT Set Point Ranged from 55°–65Fa N/A

Supply Fan Control SZVAVb Constant

Supply Flow Rate 1,601–4,069 cfmc

(controller range 34%–100% fan speed) 3,558 cfm

OA Damper Position Range = 5%–15%d

Ventilation Range = 219–342 cfm

Position Range = 0%–20%

Ventilation = 574–1,413 cfme

a For SZVAV control, the Rebel RTU controls the compressors to maintain a constant DAT regardless of the fan 

speed. b For SZVAV control, the Rebel RTU controls the supply fan using a PI logic based on the current and previous 

minute’s space temperature compared to set point (see Appendix C). c The Rebel supply fan was allowed to ramp from 34%–100% based on the controller’s settings. The TAB report 

provided the supply flow rates associated with these settings. d Prior to the TAB, the Rebel OA damper was fixed at 15% open; after the TAB, the Rebel OA damper was 

controlled to open linearly from 5% at 100% fan speed to 15% at 40% fan speed. e The baseline OA damper was measured to have significant leakage. After the TAB report, NREL and its

subcontractor, Transformative Wave Technologies (TWT), separately measured the ventilation flow rate at a 0% 

damper position and verified the baseline RTU was still bringing in almost 600 cfm of OA.

For both RTUs, the temperature set points were lowered below 76°F for some days to ensure 

sufficient operation in second stage. Figure 10 shows that despite these lower set points, both 

RTUs operated most of the time near 50% of capacity. Although the baseline does not have a 

variable-speed compressor, the cooling capacity at both of its stages change slightly based on the 

mixed-air conditions (entering the evaporator coil) and ambient dry-bulb conditions (entering the 

condenser coil). 
18

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Figure 10. Histogram of monitored baseline and Rebel operational cooling capacities

After gathering a sufficient range of calibration data under various control configurations (most 

of November 2013), NREL configured the Rebel to achieve its maximum efficiency while 

meeting NAVFAC’s standards of comfort and ventilation. Two Rebel control settings that had a 

dramatic impact on performance were DAT set point and OA damper position. These maximum 

efficiency control settings were maintained for the remainder of the demonstration period from 

November 24, 2013, through January 25, 2014.

DAT set point. The warmer the DAT set point, the more efficient the DX operation. 

However, the supply fan would then have to work harder (move more air) to meet the space 

conditioning load. At first, NREL was considering a 65°F DAT set point. Yet, the warmer 

the supply air, the higher the resulting space moisture conditions, causing discomfort and 

greater potential for mold growth. To balance DX efficiency with space moisture, NREL 

specified a constant 60°F DAT set point. 

At a 60°F DAT set point, the saturated supply air would have a dew point ranging from 56°–

58°F. NREL determined this supply air dew point range was sufficient to maintain a space 

dew point < 63°F (< 65% RH at a 76°F dry-bulb set point). The only moisture-based 

requirement in UFC or UFGS is UFC 3-410-01 Section 3-4.3.1 (dated July 1, 2013), which 

states “78°F (26°C) dry bulb and a maximum of 55°F (12.8°C) dew point.” However, this is 

a design-based requirement, namely for sizing HVAC equipment. There are no operational

moisture (RH or dew point) requirements throughout the UFC, UFGS, Commander Navy 

Installations Command Common Output Level Standards, or NAVFAC Hawaii energy 

mandates. NREL proposed—and NAVFAC agreed—to use 65% RH (maximum 63°F dew

point at a 76°F dry-bulb set point) as the moisture threshold during occupied hours. A 

maximum RH of 65% is based on ASHRAE Standard 55-2010 for maintaining thermal 

comfort and mitigating mold issues.

0%

10%

20%

30%

40%

50%

60%

70%

80%

90%

100%

< 2 tons 2 - 4 tons 4 - 6 tons 6 - 8 tons 8 - 10 tons 10 - 12 tons 12 - 14 tons

Percentage of Total Compressor On Time

McQuay Demonstration Period Operation

Baseline Demonstration Period Operation
19

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OA damper position. Based on the TAB report, the Rebel OA damper was configured to 

maintain the minimum ventilation per ASHRAE 62.1-2010 (the DCV features were not 

exercised in this demonstration according to UFC 3-410-01 Section 401.1 [dated July 1, 

2013]; see Section 2.2). The OA damper position was controlled based on the supply fan 

speed; 5% open at 100% fan speed to 15% open at 40% fan speed. Section 4.4 reviews the 

ventilation rates maintained compared to the ASHRAE 62.1-2010 minimum requirement.

Table 8 presents representative Rebel RTU daily performance for five weekdays of the 

demonstration period. The “Total DX Cooling” is the daily sum of refrigeration-based cooling 

calculated using the ClimaCheck methodology summarized in Appendix A. Dividing this daily 

total DX cooling (converted to Btuh) by the daily total electric energy usage (converted to Watthour) provides a daily average EER that includes the supply fan energy. Note these daily average 

EERs should not to be compared against rated EER or IEER conditions because these field 

measurements were not at proper AHRI rating conditions.

To fully characterize performance, the baseline was operated at a 68°F set point for many hours 

of the demonstration to realize more second-stage operation. NREL found that the greater 

percentage of time the baseline RTU operated in first stage cooling, the lower the overall daily 

EER. The baseline under first-stage operation realizes a lower performance because both fixedspeed condenser fans are operating with only one compressor providing cooling. These 

additional parasitic power draws drive down the real-time EER. During the demonstration period 

days with a 76°F set point, the baseline RTU would operate more often under first-stage 

operation, which would further drive down the daily average EER. Table 9 presents the baseline 

RTU daily performance for five weekdays of the demonstration period when the set point was 

68°F.

The baseline RTU also experiences performance degradation caused by compressor cycling the 

ClimaCheck methodology does not capture. The ClimaCheck methodology is accurate only 

when the DX circuit has reached steady-state operation, which is typically 2 minutes after the 

compressors turns on. When the baseline RTU turned on a compressor, the ClimaCheck method 

was calculating a cooling rate well beyond the capacity of that DX circuit. For example, when 

the second-stage compressor turned on, the first minute of operation would report 10 tons of 

additional cooling, the second minute 7 tons of additional cooling, and from the third minute on,

the additional cooling would settle to a realistic 5 tons. When calculating the daily total DX 

cooling, NREL set the first and second minute cooling rates to that measured in the third minute 

each time a compressor started. Yet this adjustment of the monitored data does not fully address 

the performance degradation caused by significant compressor cycling. Therefore, the daily 

average EER provided in Table 9 may overstate the baseline RTU performance. The true daily 

average EER may be up to 8% below that shown, based on the uncertainty in the measurement. 

The daily average EERs and energy usage from Table 8 and Table 9 should not be used for the 

true RTU comparison, nor should they be compared to the unit’s rated IEER. They are field test 

measurements, not lab test results at proper AHRI rating conditions. Instead, the monitored data 

from the demonstration period were used to calibrate a Rebel RTU model and baseline RTU 

model. NREL used calibrated whole-building energy models to establish a true RTU 

performance comparison. 
20

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Table 8. Monitored Daily Rebel RTU Performancea

Date

Avg.

OAT

(°F)

Total DX 

Coolingb

(ton-h)

Compressor + 

Cond. Fan

Energyc

(kWh)

Supply Fan

Energyd

(kWh)

Total 

Energye

(kWh)

Daily 

Average

EERf

12/9/13 81.2 54 30.6 3.6 36.0 17.9

12/10/13 80.1 52 31.6 4.0 37.0 16.7

12/11/13 78.4 47 25.7 3.4 30.9 18.1

12/12/13 78.5 38 23.2 3.2 27.1 17.0

12/13/13 77.5 40 20.9 3.1 25.5 19.0

a For December 2013, the Rebel RTU was controlled to a 76°F set point, 60°F DAT set point, modulating OA 

damper to maintain ASHRAE 62.1 minimum ventilation based on fan speed, and variable-supply flow rate of 

1,601–4,069 cfm. b Daily DX cooling capacity calculated using the ClimaCheck methodology with ±7% uncertainty. c Compressor and condenser fan energy measured at a ±3% accuracy (separately submetered). d Supply fan energy with uncertainty of 5%; based on subtraction of compressor, condenser fan, and controller 

energy from total RTU energy (supply fan power was not separately submetered). e Total RTU energy (including controller) with ±3% uncertainty (separately submetered). f Daily averaged performance based on total daily cooling provided (ton-hours) and total RTU energy (including 

supply fan energy) with ±5% uncertainty; not to be compared against rated EER or IEER conditions as these field 

measurements were not at proper AHRI rating conditions.

Table 9. Monitoring Daily Baseline RTU Performancea

Date

Avg.

OAT

(°F)

Total DX 

Coolingb

(ton-h)

Compressor + 

Cond. Fan 

Energyc

(kWh)

Supply Fan

Energyd

(kWh)

Total 

Energy

(kWh)

Daily Average

EERf,g

12/2/13 75.0 70 56.0 10.5 66.7 12.5

12/3/13 75.7 69 55.9 10.5 66.7 12.4

12/4/13 76.5 67 54.9 10.5 66.2 12.2

12/5/13 75.6 65 53.9 10.5 64.9 12.0

12/6/13 76.8 66 54.2 10.5 64.7 12.2

a For December 2013, the baseline RTU was controlled to a 68°F set point, 20% fixed OA damper, and 3,558 cfm 

supply flow rate.

b Daily cooling capacity calculated using the ClimaCheck method with ±7% uncertainty. c Compressor and condenser fan energy measured at a ±3% accuracy (separately submetered). d Supply fan energy with uncertainty of 5%; based on subtraction of compressor, condenser fan, and controller from 

total RTU energy (supply fan power was not separately submetered). e Total RTU energy (including controller) with ±3% uncertainty (separately submetered). f Daily averaged performance based on daily cooling provided (ton-hours) and total RTU energy (including supply 

fan energy) with ±5% uncertainty; not to be compared against rated EER or IEER conditions as these field 

measurements were not at proper AHRI rating conditions. g Baseline daily average EER ranged from 8.5–10.5 with more typical compressor staging where 80% of DX 

operation time was under first stage and 20% operation time under second stage. When the set point was reduced to 

68°F, the greater percentage of second-stage operation improved daily average EER to 10.5–12.5.
21

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The following two subsections describe how the RTUs were modeled using the EnergyPlus16

whole-building energy simulation program. Two models were constructed with identical 

building characteristics (geometry, envelope, and internal loads). These building parameters 

were based on measurements taken on site; structural drawings; and the artificial occupant, plug, 

and lighting loads (Section 3.4). Because the space was unoccupied for the demonstration period 

and the internal loads were artificial, the randomness induced by human behavior was nearly 

eliminated. The RTUs conditioning the space constituted the only difference between the two 

models.

4.1.1 Rebel Rooftop Unit Modeling Process

The Rebel RTU modeling was a three-part process:

1. The monitored demonstration data were used to develop mathematical models to 

characterize the Rebel supply fan and DX system. 

2. The Rebel RTU model was integrated into a whole-building simulation of building 550. 

Two unknown envelope parameters— infiltration rate and window properties (solar heat 

gain coefficient [SHGC] and U-value)—were adjusted within appropriate bounds to 

calibrate the whole-building simulation against the measured data. NREL conducted a 

rigorous uncertainty analysis comparing the measured versus modeled daily energy to 

quantify the 95% confidence bounds of the model (Appendix H). There were 35 days in 

the Rebel calibration period. NREL also stipulated the model must maintain the occupied 

average space temperature to ±1°F and dew point to ±3°F of the measured space 

conditions. Based on these specifications, NREL was assured the model represented the 

measured Rebel RTU energy usage and resultant space conditions (sensible and latent). 

3. The calibrated model was simulated for an entire year using typical meteorological year 3

(TMY3) weather data. The resultant annual energy usage was compared to the calibrated 

baseline model also simulated using TMY3 weather. 

Steps 1 and 2 are described below. Step 3’s annual energy results are summarized in Section 4.2.

Step 1. Rebel Supply Fan and DX System Models

The Rebel RTU’s PI supply fan control logic was integrated into the model. For each minute, the 

Rebel RTU calculates a projected error (difference between space temperature and set point) 

based on the current and previous minute’s error. The supply fan speed changes based on the 

projected error and a gain term. Appendix C explains the supply fan control logic in detail. 

Appendix C also summarizes the relationship between fan speed, supply air flow rate, total static 

pressure drop, and supply fan power. The Rebel DX system was controlled to maintain a 

constant 60°F DAT.

Once the compressor and supply fan control logic was integrated into the EnergyPlus model, 

NREL used the monitored data to develop a regression model of DX (compressors and 

condenser fans) power. Equation 4 shows this regression model. At each time step (1 minute) in 

the EnergyPlus model, these predictors are known. The calculated DX power for each time step 

is then used to calculate energy usage. 

 16 https://energyplus.net/
22

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DDXXPPPPPPPPPP = −0.752 + (−0.051 ∙ TTDDDD) + (0.077 ∙ TTOO ) +

(6.067 ∙ CCCCppFF FFFF) + (−0.772 ∙ CCCCCC 1 oo2) (4)

where

DDXXPPPPPPPPPP is the combined power draw of the compressors and condenser fan (kW)

TTDDDD is the DAT (°C)

TTOO is the ambient dry-bulb temperature (°C)

CCCC _FF FF is the capacity fraction based on the ClimaCheck calculated real-time cooling 

normalized to the RTU’s AHRI nominal capacity (117,907 Btuh; 9.8 tons)

CCCCCC 1 oo2 signifies whether operating in first or second stage (+1 = stg 1; -1 = stg 2).

NREL included the predictor Comp1or2 because the monitored data showed a step-wise change 

in performance when the second-stage compressor initiated. For example, the ClimaCheck 

methodology would show the real-time DX efficiency operating around 18 EER (not including 

the supply fan energy) with only the first-stage compressor operating. When the second-stage 

compressor turned on, the real-time DX efficiency would immediately drop to around 15 EER

(not including the supply fan energy). Including the Comp1or2 predictor in equation 4 captures 

this step-wise change. 

Based on the monitored data, NREL found the second-stage compressor would initiate when the 

capacity fraction exceeded 0.6. Therefore, during the modeling process, only the first stage was 

operating until the capacity fraction exceeded 0.6. Figure 11 shows the Rebel DX power 

regression equation provides a ±10% uncertainty at a 68% confidence based on the coefficient of 

variation of the root mean squared error (CVRMSE).

Figure 11. Rebel DX power regression modeled versus measured,

including uncertainty based on CVRMSE

Table 10 summarizes the parameters of this regression model. Appendix C summarizes this 

regression model in greater detail. Figure 12 uses equation 4 to compare the Rebel’s DX 

performance, not including the supply fan power, across a range of predictor values. The step0

1

2

3

4

5

6

7

8

9

10

0 1 2 3 4 5 6 7 8 9 10

Modeled McQuay DX Power [kW]

Measured McQuay DX Power [kW]

Modeled vs

Measured

Correlation

+10% uncertainty

based on CVRMSE

-10% uncertainty

based on CVRMSE
23

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wise change in performance is apparent when the second stage compressors turn on at capacity 

fractions that exceed 0.6. 

Table 10. Rebel RTU DX Power Regression Model Parameters

Adjusted R-squared 0.96

Standard error/CVRMSE 0.28 kW/10%

Total RTU operational hours 262 h (245 h first stage; 17 h second stage)

Regressed DX power range

(includes condenser fan)

First-stage operation: 0.7–5.2 kW

Second-stage operation: 3.7–8.7 kW

Regressed TTDDDD range 55°–68°F

Regressed TTOO 61°–87°F

Regressed CCCC _FF FF 0.1–1.3

Figure 12. Using DX power regression model to calculate DX cycle performance (EER)

for a range of DAT, OAT, and capacity fractions

Step 2. Rebel Rooftop Unit and Building 550 Model Calibration

With the supply fan logic, compressor logic, and DX power regression model implemented, the 

EnergyPlus model was calibrated against 35 days of monitored data between November 24, 2013 

and January 25, 2014. These were days when only the Rebel RTU was operating, and the control 

parameters were adjusted to maximize efficiency while meeting thermal comfort requirements. 

These control parameters included a 76°F set point, 60°F DAT set point, and OA damper

10

15

20

25

30

35

0 0.2 0.4 0.6 0.8 1 1.2

Performance of DX Cycle (no supply fan) [EER]

McQuay RTU Capacity Fraction of Nominal [117,907 Btuh; 9.8 tons]

DAT=65°F; OAT=75°F

DAT=55°F; OAT=75°F

DAT=65°F; OAT=85°F

DAT=55°F; OAT=85°F
24

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modulating from 15% open at 40% fan speed to 5% open at 100% fan speed. The ventilation 

flow rate at this supply fan and OA damper control met the ASHRAE 62.1 minimum ventilation

requirements. The model was simulated using a 1-minute time step and the measured National 

Oceanic and Atmospheric Administration Honolulu International Airport weather data. 

For calibration, NREL adjusted two “knobs” to ensure the model aligned with the monitored 

data. These were two model inputs that characterized building 550’s envelope; infiltration rate

and double-pane window properties (SHGC and U-value). Appropriate upper and lower bands

were established for both inputs. NREL found an infiltration of 0.10 cfm/ft2 of wall area at 0.05

in. water column (WC) pressure (equivalent to 0.34 air changes per hour), glazing SHGC of 

0.50, and glazing U-value of 0.5 resulted in the best fit to the measured daily energy usage. 

Figure 13b shows the comparison for the daily RTU energy calibration (including supply fan, 

compressors, and condenser fans). Using the uncertainty analysis in Appendix H, the uncertainty 

of the Rebel EnergyPlus model was based on the CVRMSE. The CVRMSE was calculated to be 

±17% at a 68% confidence. These confidence bands are plotted in Figure 13b. Appendix H goes 

into further detail regarding the propagation of modeling error in the final annual energy savings 

prediction. Figure 13a shows the daily RTU energy usage versus the daily average ambient drybulb temperature. The plots trend well together and provide confidence that the Rebel RTU 

model captured the impact of weather on energy usage. Appendix C summarizes all the Rebel

calibration results. 

(a) (b)

Figure 13. Rebel RTU model versus measured daily RTU energy usage

5

10

15

20

25

30

35

68 70 72 74 76 78 80 82 84

Daily Total RTU Energy [kWh]

Daily Average Ambient Dry-Bulb Temperature [°F]

Measured Daily Energy

Modeled Daily Energy

5

10

15

20

25

30

35

5 10 15 20 25 30 35

Modeled Daily RTU Energy [kWh]

Measured Daily RTU Energy [kWh]

Model vs Measured

Correlation

+17% uncertainty based on CVRMSE

-17% uncertainty based on CVRMSE
25

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4.1.2 Baseline Rooftop Unit Modeling Process

The baseline RTU modeling was a three-part process:

1. The monitored data were used to develop mathematical models characterizing the 

baseline’s supply fan and DX system. 

2. The baseline RTU model was integrated into a whole-building simulation of building 

550. The infiltration and window properties established during the Rebel RTU model 

calibration were maintained for the baseline RTU model. The baseline RTU model was 

calibrated based on the same set of specifications:

a. Measured versus modeled daily energy usage

b. Model must maintain the occupied average space temperature to ±1°F and dew

point to ±3°F of the measured space conditions. 

3. The calibrated model simulated two baseline RTUs that served the entire office space in 

building 550 using TMY3 normalized weather data. 

The following subsection summarizes step 1 and step 2. Section 4.2 reviews the annual energy 

results from step 3.

The baseline RTU was modeled by determining for each time step whether first- or second-stage 

compressors were operating based on the space temperature versus set point error. Depending on 

the stage of operation, the mixed-air wet-bulb temperature, ambient dry-bulb temperature, and 

two sets of regression equations were used to calculate the cooling capacity and associated DX 

(compressor(s) and condenser fans) power. Based on the baseline RTU sequence, both condenser 

fans operated whether in stage 1 or 2 cooling operation. The baseline RTU OA damper was 

modeled at 20% open based on how it was configured during the days used in the calibration 

period. The supply fan was modeled with a constant 3,558 cfm based on the TAB report. 

Step 1. Regression Models

The baseline RTU was characterized with two sets of regression equations. Equations 5 and 6 

capture the variations in the first- and second-stage DX system power draw, respectively, based 

on the mixed-air wet-bulb and ambient dry-bulb temperatures. NREL found the ambient drybulb temperature had the most significant impact on compressor power because it directly 

impacts discharge pressure (saturated condensing temperature) and refrigerant subcooling. To a 

lesser extent, the mixed-air wet-bulb impacted the compressor power because it influences the 

suction pressure (saturated suction temperature). 

SSSS SSSS 1 DD PP PP 15,058 + (−919 ∙ TTWWWW) + �16 ∙ TTWWWW

2� + (5)

(−283 ∙ TTOO ) + �1.4 ∙ TTOO

2� + (16 ∙ TTWWWW ∙ TTOO )

SSSS SSSS 2 DD PP PP 17,559 + (−487 ∙ TTWWWW) + �−6 ∙ TTWWWW

2� + (6)

(−634 ∙ TTOO ) + �3.1 ∙ TTOO

2� + (34 ∙ TTWWWW ∙ TTOO )

where

DX Power includes the compressors and condenser fans power (W),

TWB is the mixed-air wet-bulb temperature entering the evaporator coil (°C), and

TOA is the ambient dry-bulb temperature (°C).
26

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The DX system power includes the compressors and condenser fans power draw. Although the 

mixed-air wet-bulb was not measured directly during the demonstration period, NREL used the 

return air temperature/RH conditions, ambient temperature/RH conditions, and OA fraction 

based on the TAB report to calculate the mixed-air wet-bulb temperature. Figure 14 shows the 

regression model for both stages of cooling with both having a 2% uncertainty at a 68% 

confidence interval based on the models’ CVRMSE. 

Figure 14. Baseline RTU DX power regression (including compressors and condenser fans)

Table 11 shows some additional regression parameters. A second set of regressions was 

conducted that related the cooling capacity under first- and second-stage operation to the mixedair wet-bulb temperature and ambient dry-bulb temperature (see Appendix D).

Table 11. Baseline RTU DX Power Regression Parameters

(including Compressors and Condenser Fans)

First-Stage DX Second-Stage DX

Adjusted R-squared 0.86 0.83

Standard error / CVRMSE 0.08 kW / 2% 0.16 kW / 2%

Regressed DX power range

(includes cond. fans)

4.2–5.0 kW 7.1–8.7 kW

Regressed operational hours 173 h 68 h

Regressed TTWWWW range 62°–68°F 62°–69°F

Regressed TTOO range 62°–86°F 63°–87°F

Step 2. Baseline Rooftop Unit and Building 550 Model Calibration

Figure 15 shows the calibration of the model versus monitored daily DX energy usage. 

Compared to the Rebel model, the baseline model showed a better calibration with respect to the 

measured daily energy usage with a ±7% uncertainty at a 68% confidence interval based on the 

CVRMSE. Additional calibration results are presented in Appendix D.

4,000

4,200

4,400

4,600

4,800

5,000

4,000 4,200 4,400 4,600 4,800 5,000

Modeled Baseline 1st Stage DX Power [W]

Measured Baseline 1st Stage DX Power [W]

Model vs

Measured

Correlation

Line

+2%

uncertainty

based on

CVRMSE

-2%

uncertainty

based on

CVRMSE

7,000

7,500

8,000

8,500

9,000

7,000 7,500 8,000 8,500 9,000

Modeled Baseline 2nd Stage DX Power [W]

Measured Baseline 2nd Stage DX Power [W]

Model vs

Measured

Correlation

Line

+2%

uncertainty

based on

CVRMSE

-2%

uncertainty

based on

CVRMSE
27

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Figure 15. Baseline RTU model versus measured daily DX energy usage

4.1.3 Supply Fan Models

Table 12 provides a performance comparison between the Rebel and baseline RTU supply fans. 

The Rebel’s ECM direct drive supply fan achieves a much higher static efficiency compared to 

the baseline. NREL found the baseline static efficiency was lower than the expected range of 

40%–50%. Regardless, the power draw was consistent with expectations and used as the baseline 

fan power for the model. 

Table 12. Supply Fan Comparison

Rebel Baseline

Fan Type Variable-speed

Direct-drive ECM

Belt driven

Constant-speed

NEMA std eff

Flow Rate During Demonstration 1,600–3,575 cfm 3,558 cfm

Pressure Drop at Peak Flow Rate 1.96 in. WC 0.91 in. WC

Power Draw at Peak Flow Rate 1.3 kW 1.1 kW

The Rebel total static pressure drop was significant because the Rebel had to be transitioned 

from vertical discharge to horizontal discharge. Most standard RTUs can be provided in either 

configuration. The Rebel was designed for vertical discharge only, but is adaptable to horizontal 

discharge through a custom roof curb. The supply air duct leaving the roof curb under the Rebel

was a small, cross-sectional area of 1.9 ft2 compared to 4.5 ft2 horizontal discharge ductwork on 

the baseline. The Rebel air speeds at 1,880 feet per minute (fpm), compared to 870 fpm for the 

baseline, resulted in a significant supply fan static pressure drop. The 1.3-kW Rebel supply fan 

power was implemented in the model at the TAB measured 3,575 cfm. To capture the fan power 

changes at variable supply fan speeds, the fan power was correlated to variable supply air flow 

rates established from the TAB report. See Appendix C and Appendix D for more detailed 

summaries of the supply parameters for the Rebel and baseline supply fans, respectively.

0

10

20

30

40

50

60

70

80

68 70 72 74 76 78 80 82 84

Daily Total RTU Energy [kWh]

Daily Average Ambient Dry-Bulb Temperature [°F]

Measured Daily Energy

Modeled Daily Energy

40

45

50

55

60

65

70

75

80

40 45 50 55 60 65 70 75 80

Modeled Total RTU Energy [kWh]

Measured Total RTU Energy [kWh]

Model vs Measured

Correlation

+7% uncertainty

based on CVRMSE

-7% uncertainty

based on CVRMSE
28

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4.2 Model Results

The two calibrated models were then simulated for a year’s operation using Honolulu TMY3 

weather data. TMY3 weather data eliminate weather abnormalities and provide an annual RTU 

energy use that would be expected averaged over 30 years of operation. Table 13 provides the 

control parameters for each RTU model. For the most part, the models mirrored the controls

implemented during the December 2013 through January 2014 timeframe of the demonstration 

period. 

Table 13. Rebel and Baseline Control Parameters

Rebel Baseline

Temperature Set Point

Schedule

76°F

0600–1530 weekdays (Summer May 1-

October 31)

0800–1530 Weekdays (Winter November

1-April 30)

74.5°F

0600–1530 Weekdays

(Summer May 1-October 31)

0800–1530 Weekdays (Winter 

November 1–April 30)

Temperature Control

Deadband ±1.0°F First stage: +0.5 to +1Second stage: +1 to +1.5

Temperature Setback 100°F 100°F

Humidity Control None None

DAT Set Point 60°Fa N/A

Supply Fan Control SZVAVb Constant speed

Min–Max Flow Rate 1,601–3,575 cfm 3,558 cfm

OA Damper

Minimum position (Closed all other times)

0800–1530 weekdays (Summer May 1-

October 31) 1000–1530 weekdays (Winter 

November 1-April 30) Ventilation range = 

219-342 cfm Meets ASHRAE 62.1c

Fixed 5% open Ventilationd = 

672 cfm Meets ASHRAE 62.1

a Rebel controls the compressors to maintain a constant DAT at any fan speed. b Rebel controls the supply fan based on its SZVAV logic, which ramps the fan using a PI control based on the 

current and previous minute’s space temperature compared to set point (see Appendix C). c Rebel model simulated OA flow rates based on correlation between OA flow rate and supply air flow rate 

established using the TAB report. OA flow rates meets minimum ventilation rate according to ASHRAE Standard 

62.1 non-DCV requirements. d Baseline model simulated constant OA flow rate of 672 cfm, based on the TAB report.

The major control change to the baseline RTU model was maintaining the OA damper fixed at 

5% compared to the 20% position during the demonstration. As summarized in Section 4.4, the 

excessive leakage of the OA damper even at a 5% damper position resulted in approximately 

three times the ventilation required per ASHRAE 62.1-2010. The baseline temperature set point 

was maintained lower than the Rebel because of their respective deadbands. This offset ensured 

both models maintained the average office space temperature within ±1°F of each other; to be 

considered a true RTU comparison, both models needed to maintain nearly the same bulk space 

temperature during occupied hours.

The calculated energy consumptions of the two Rebel RTUs were averaged together. Similarly, 

the two baseline RTU’s energy consumptions were averaged together. Table 14 then compares 
29

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these averages to show the energy savings of one 10-ton Rebel RTU versus one 10-ton baseline 

RTU serving a small office space. The Rebel provides 34% energy savings compared to the 

baseline RTU at a fixed 5% OA damper position. Despite a much larger total static pressure 

drop, the Rebel supply fan still provided a 51% energy savings compared to the baseline supply 

fan. 

The annualized EER was calculated based on the annual cooling provided by each RTU (in 

British thermal units) divided by the annual energy usage (in Watt-hour). As mentioned 

previously, the EER numbers below should not be compared to the unit’s rated IEER because

they are modeled results averaged across a year’s operation (not lab test results at proper AHRIrating conditions). The Rebel 15.6 annualized EER is slightly below the daily EER range 

measured during the demonstration period as shown in Table 8. The daily range shown in Table 

8 represents cooler days in the winter while the slightly hotter summer months drive down the 

annualized EER. The baseline 10.1 annualized EER was lower than the EER range measured 

during the demonstration period because the annualized EER is influenced by summer operation 

and the fact the baseline RTU operated significantly more in first-stage operation where its realtime EER is lower because two condenser fans were operating. 

Appendix H summarizes the uncertainty analysis of the predicted annual energy savings. Based 

on the measured power, sampling, and model uncertainties, NREL calculates the 3,682 kWh 

annual energy savings presented in Table 14 has a ±27% uncertainty at a 95% confidence 

interval. This energy savings was then used in Section 5 to conduct the ROI analysis.

Table 14. Modeled Annual Energy Consumption and Savings Between One 10-Ton Rebel RTU

Versus One 10-Ton Baseline RTU Serving the Building 550 Small Office Space

1 Baseline RTU

5% OA Damper 1 Rebel RTU Savings

Supply Fan 2,607 kWh 1,268 kWh 1,339 kWh (51%)

Compressors + Condenser Fans 8,855 kWh 6,332 kWh 2,523 kWh (28%)

Total RTU 11,462 kWh 7,600 kWh 3,862 kWha (34%)

Total Cooling 9,616 ton-h 9,879 ton-h

Annualized EERb (do not use as rated 

IEER) 10.1 EER 15.6 EER

a Propagation of uncertainty yields ±27% of the annual energy savings, based on a 95% confidence interval (see 

Appendix H)

b Not to be compared against rated EER or IEER conditions as these model results are annualized and not at proper 

AHRI rating conditions.

Figure 16 shows a histogram of the annual capacity operation for the Rebel and baseline RTUs. 

The baseline RTU spent more than 90% of its DX operational hours in first stage. Because the 

Rebel was able to vary its capacity, it spent most of its time lower than 4 tons. The reason both 

the baseline and Rebel RTUs operate at a lower capacity is most likely because they are

oversized. Based on site visits of different RTU installations at JBPHH, the typical range is 250–

400 ft2/ton. Building 550 at 20 tons serving 5,000 ft2 is on the small side of 250 ft2/ton. These 

RTUs serving spaces in the 300–400 ft2/ton range would operate more hours at a larger capacity. 
30

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Figure 17 compares the daily energy usage versus the daily average ambient dry-bulb for both 

RTUs.

Figure 16. Baseline and Rebel annual operating hours at different capacity bins

Figure 17. Baseline and Rebel daily energy usage versus daily average dry-bulb temperature

0

250

500

750

1,000

1,250

1,500

1,750

2,000

2,250

2,500

Off 0 - 4 tons 4 - 6 tons 6 - 8 tons 8 - 10 tons 10 - 12 tons

Annual Hours of Operation

McQuay Rebel

Baseline

0

10

20

30

40

50

60

70

80

65 70 75 80 85 90

Daily Energy Usage [kWh]

Daily Average Ambient Dry-Bulb Temperature [°F]

Baseline 10 ton RTU

McQuay 10 ton RTU
31

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Based on JBPHH site visits, NREL found that typical RTU OA dampers were fixed at some 

arbitrary 5%–20% opening. These OA dampers were also of typical construction—not low 

leakage. To provide a better cross-section of savings beyond the 5% damper position shown in 

Table 14, NREL compared the Rebel energy usage versus two additional OA damper 

configurations. One configuration represented a low leakage damper installed on a baseline unit,

which provides just the correct amount of ventilation to meet ASHRAE 62.1-2010. This 

configuration isolates the energy savings of the Rebel from its variable-speed supply fan and 

variable refrigerant flow technologies—eliminating the energy savings of the Rebel’s lowleakage OA damper. Based on correspondence with the local HVAC distributors on Oahu, codeminimum RTUs can be specified with low-leakage dampers. The second configuration 

represented OA dampers set to a larger 20% opening. Table 15 shows the energy savings ranges 

from 29%–37%, depending on the OA damper configuration of the baseline RTU. Considering 

that the typical OA damper at JBPHH is not low leakage and the fixed positions fluctuate from 

5%–20%, the annual energy savings should be within the 34%–37% range.

In 2018, the Rebel model was rerun with a lower fan pressure drop. When the demonstration was 

completed in 2014, Daikin Applied only provided a downward discharge configuration. To 

integrate with the existing ductwork, the installation at the small office used a roof curb to 

transition the airflow from downward to horizontal, resulting in an additional inch of static 

pressure. The Rebel now has a horizontal discharge option. In Table 15 below, the number in 

brackets shows the Rebel energy savings with the lower fan pressure drop. Across the three 

baseline damper configurations, the energy savings ranged from 33-42%. 

Table 15. Modeled Rebel Savings Over the Baseline RTU Maintaining

Different Ventilation Flow Rates

1 Baseline RTU 1 Rebel RTU Savings

Baseline with low-leakage OA 

damper meeting ASHRAE 62.1 

minimum ventilation rate

10,634 kWh 7,600 kWh

[7,099 kWhb]

3,034 kWha (29%)

[3,535 kWhb] (33%)

Baseline with standard OA damper 

fixed at 5% open 11,462 kWh 7,600 kWh

[7,099 kWh]

3,862 kWha (34%)

[4,363 kWhb] (38%)

Baseline with standard OA damper 

fixed at 20% open 12,151 kWh 7,600 kWh

[7,099 kWh]

4,552 kWha (37%)

[5,052 kWhb] (42%)

a Propagation of uncertainty yields ±27% of the annual energy savings based on a 95% confidence interval (see 

Appendix H).

During the site inspections of 30 RTUs throughout JBPHH, NREL found that most office 

buildings were not abiding by the NAVFAC Pacific operating hours limits for HVAC 

equipment. Table 13 above shows these allowed hours. Outside these hours, the RTUs were 

supposed to be completely off, not even maintaining a set-back temperature set point. While 

NREL found a large range in the times the thermostats were set to enable cooling, the general 

trend was from 0600 to 1800, or 12 hours a day. Since most of these thermostats had 7-day 

programmable capability, these operating hours were just during the weekdays – the thermostats 

were correctly set to prevent weekend operation.
32

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To account for the longer hours of operation, NREL ran the Rebel and baseline energy models 

from 0600 to 1800 on weekdays. NREL chose the baseline with a standard OA damper fixed at 

5% open. The annual energy savings was 7,426 kWh, nearly double that shown in Table 15. 

NREL found that the percentage energy savings increased to 48% because of the larger number 

of hours in the early morning and late afternoon that the Rebel was able to operate in its 

improved part load operation of the supply fan and DX circuit. Essentially, the longer the 

operating hours of the facility, the larger the percentage energy savings for high-efficiency RTUs 

that enable improved part-load performance.

4.3 Interior Thermal Comfort

The modeling results also show the Rebel will provide slightly more cooling over a year 

compared to a baseline RTU because it will provide more latent cooling. The Rebel maintains a 

lower space dew point because it can maintain a constant DAT. At a 60°F DAT set point, the 

Rebel is providing supply air at a 57°F dew point or lower. The baseline RTU supply air dew

point changes based on the cooling stage and the cycle rate. Under consistent first-stage cooling 

(over 10 consecutive minutes), the baseline RTU is typically maintaining a 65°–68°F supply air 

temperature, which results in a supply dew point of 60°–63°F. Only under consistent secondstage cooling can the baseline supply air at 55°–60°F yielding a supply dew point of 53°–58°F. 

Yet, when the second stage frequently cycles, as was seen during the demonstration period and 

in the model, the second stage provides negligible latent cooling. While the second-stage 

compressor is on for 5 minutes, moisture is condensing on the coil and fin surfaces. When the 

compressor turns off, that moisture re-evaporates into the supply air. Because the baseline RTU 

typically operates in first-stage cooling and cycles the second stage on for brief periods only, the 

supply air dew point will be consistently 60°–63°F. As a result, the Rebel’s supply of lower dew

point air will maintain a drier space, but the additional latent cooling will require more work 

from the DX system. Therefore, the Rebel provides both energy savings and improved thermal 

comfort by maintaining a drier space. Section 4.3 further summarizes the difference in thermal 

comfort between the Rebel and the baseline RTUs.

For the same reasons energy modeling was used to predict annual energy savings, the models 

were also used to predict interior space conditions throughout the year. The Rebel and baseline 

RTUs were modeled according to what NREL defined as the typical JBPHH interpretation of the

NAVFAC Hawaii Region Energy Instruction. This mandate states that thermostats should not be 

set lower than 78°F. Based on discussions with NAVFAC building energy managers, most 

JBPHH small office buildings were being set to a 76°F set point. The NAVFAC building energy 

managers justified this lower set point by stating a thermostat set point at 76°F would ensure the 

hottest location within the conditioned space would not exceed 78°F. NREL also took into 

consideration the Common Output Level Standards established by the Commander Navy 

Installations Command. Although Common Output Level Standards 3 and 4 push the minimum 

thermostat requirement warmer than 78°F, these levels are not typical. Therefore, NREL 

established 76°F as the average space temperature to maintain for both RTU models (Table 13).

Regarding set point schedules, NAVFAC Hawaii Region Energy Instruction stipulates air 

conditioning is allowed only from 1000–1500 for winter hours (November 1–April 30) and 

0800–1600 for summer hours (May 1–October 31). During the demonstration period, NREL 

defined a thermostat schedule based on what was determined to be typical from discussions with 
33

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NAVFAC building energy managers. This schedule was 1000–1530 for winter hours and 0800–

1530 for summer hours. NREL was concerned about the RH within the space when these 

schedules were implemented while the office space was still occupied by NAVFAC personnel 

(June to July 2013). The RH was exceeding 65%, which NREL established with NAVFAC as 

the maximum allowable. NREL found that by starting the RTUs 2 hours prior to the NAVFAC 

Hawaii Region Energy Instruction schedule, the space was sufficiently dehumidified and 

maintained space RH lower than 65% for the remainder of the day. Therefore, the RTU

operation was modeled to occur from 0800–1530 for winter hours (November 1–April 30) and 

0600–1530 for summer hours (May 1–October 31), as shown in Table 13Table 13.

Figure 18 plots a histogram of the hourly average space temperature maintained during occupied 

hours for both models. Despite a few fringe hours during the morning cooldown (temperature 

bins higher than 77°F), the temperature bins emphasize each respective RTU’s deadband control. 

The baseline RTU shows a tighter temperature range of 75°–76F as the two DX stages are cycled 

to maintain the space at 0.5°–1.5°F higher than the 74.5°F set point. The Rebel 2°F deadband is 

shown with most of the hourly averages at 75°–77°F. This histogram of binned hourly averages 

appears to show that the baseline RTU maintains improved thermal comfort. However, dialing 

down to 1-minute monitored, not model, data show the Rebel maintaining a more stable space 

temperature. 

Figure 18. Office space dry-bulb temperature histogram comparing the Rebel model

versus the baseline model with a fixed 5% OA damper position 

Figure 19 plots the measured space temperature under Rebel-only operation on December 10, 

2013 (76°F set point), compared to baseline-only operation on December 4, 2013 (68°F set

point). Just focusing on the shape of the temperature profiles (ignoring the set point differences), 

the Rebel leverages its variable capacity to maintain a smooth temperature profile compared to 

0

250

500

750

1,000

1,250

1,500

1,750

2,000

74≤ x <75 75≤ x <76 76≤ x <77 77≤ x <78 78≤ x <79 79≤ x <80 80≤ x <81 81≤ x <82

Annual Hours of Operation

Bulk Office Space Dry-Bulb Temperature Bins [°F]

McQuay RTU at 76°F set-point

Baseline RTU at 74.5°F set-point
34

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the baseline, which experiences more dramatic temperature swings because the compressor 

cycles—at a warmer set point of 74.5°F, the baseline unit experienced a lower cycling frequency 

but the general trend was the same. Consequently, the smoother temperature control of the Rebel

enables it to provide improved thermal comfort despite a larger deadband of 2°F (compared to 

1°F deadband for the baseline). Note the Rebel enables users to reduce the deadband control 

from 2°F to 1°F. NREL recommends the control is kept to a 2°F deadband because it achieves 

greater energy savings while still providing improved comfort compared to a baseline RTU.

Figure 19. Measured (not modeled) space temperature fluctuation across the day

between the Rebel RTU at a 76°F set point and baseline RTU at a 68°F set point

Figure 20 plots the modeling results of the Rebel versus baseline hourly average space RH 

(operational hours only). This histogram clearly shows the Rebel maintaining a drier space. The 

annual average space RH during occupied hours was 53% for the Rebel compared to 61% for the 

baseline. Therefore, the models indicate that by maintaining a constant 60°F DAT, the Rebel was 

able to maintain a more comfortable space with a lower annual average RH of at least 5% 

compared to a baseline RTU (see Figure 20).
35

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Figure 20. Office space RH histogram comparing the Rebel model versus the baseline model

with a 5% OA damper position

For future applications of the Rebel, if a lower moisture condition is desired, the control can be 

changed to maintain a lower DAT and maintain the same space temperature set point. For 

example, setting the DAT to 55°F will maintain the supply air dew point lower than 53°F, and 

the space set point can be left at 76°F. This flexibility enables users to control the Rebel to 

provide more latent cooling and maintain a drier space—lower RH—if so desired. Note the

lower the DAT set point, the lower the overall efficiency of the Rebel, resulting in increased

energy usage. To balance space moisture conditions with energy usage, users want to determine 

the maximum DAT set point that maintains the space under some specified moisture threshold

which was 65% RH for this demonstration.

4.4 Ventilation Rates

UFGS 23 05 93 “Testing, Adjusting, and Balancing for HVAC” mandates that ventilation rates 

must meet ASHRAE standard 62.1-2010 requirements. According to UFC 3-410-01 Section 

401.1 (dated July 1, 2013), “Use of CO2 sensors for ventilation control is prohibited unless 

approved by AHJ.” To provide the most flexibility for applying these demonstration results for 

future installations (where the AHJ may not grant approval for DCV), NREL operated the Rebel

model without DCV capability. Therefore, the annual energy savings provided in Section 4.2 is 

based on the Rebel meeting ASRHAE 62.1-2010 minimum ventilation requirements.

The building 550 minimum ventilation rates are presented in Table 16. The DCV-based 

minimum ventilation is provided for reference only, as the Rebel was evaluated without DCV 

enabled. Compared to other building types, the ASHRAE 62.1 Ventilation Rate Procedure has 

0

250

500

750

1,000

< 50 50≤ x <55 55≤ x <60 60≤ x <65 65≤ x <70 70≤ x <75 75≤ x <80

Annual Hours of Operation

Bulk Office Space Relative Humidity [%]

McQuay RTU at 76°F set-point

Baseline RTU at 74.5°F set-point
36

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lower requirements for offices. Table 16 shows the difference between the non-DCV and DCV 

requirements is approximately 30%. 

Table 16. Office Minimum Ventilation Rates per ASHRAE Standard 62.1-2010

Building Area

Served 

Occupancy 

Ventilation 

Rate

Default 

Occupant 

Density

Area 

Ventilation 

Rate

Combined 

Ventilation 

Rate Inc.

Occ. and

Area

Min. 

Required

(no DCV)

Min. 

Required 

(with DCV)

Delta 

Between 

Min.

Required

Baseline 2,400 ft2 5.0 cfm/occ 5 occ/

1,000 ft2 0.06 cfm/ft2 0.09 cfm/ft2 204 cfm 144 cfm 60 cfm(29%)

Rebel 2,576 ft2 5.0 cfm/occ 5 occ/

1,000 ft2 0.06 cfm/ft2 0.09 cfm/ft2 219 cfm 155 cfm

64 cfm

(29%)

The ventilation rates of both RTUs were measured during the TAB, and these measurements 

were input into the energy models. Table 17 shows the baseline RTU far exceeded the ASHRAE 

62.1 minimum ventilation rates. NREL was surprised by the significant leakage through the OA 

damper, even at 0% and 5% positions. To validate these measurements, NREL then directly 

measured the ventilation flow rate into the damper using a pitot tube grid. At a 5% damper 

position, NREL measured 487 cfm. At a 0% damper position, NREL again measured 487 cfm. 

Repeatability in the measurements leads NREL to believe the baseline OA damper was leaking 

around 500 cfm, even at a 0% OA damper position (approximately 185 fpm face velocity across 

the OA damper). Consequently, NREL was confident in the TAB results, and therefore, used the

Table 17 OA flow rates in baseline models.

Table 17. Baseline RTU Ventilation Flow Rates

OA Damper 

Position

Ventilation

Flow Ratea

Meets

ASHRAE 62.1

0% 574 cfm Yes

5% 672 cfm Yes

20% 1,413 cfm Yes

a Based on TAB measurements.

Table 18 shows the ventilation flow rates calculated at different OA damper and supply fan 

speed configurations. For the demonstration period and the model, the Rebel was operated from 

5% position at 100% fan speed to 15% position at 40% fan speed. 
37

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Table 18. Rebel Ventilation Flow Rates

OA Damper 

Position

Fan 

Speed

Ventilation 

Flow Ratea

Meets ASHRAE 

62.1 Minimum

0% 88% 3 cfm No

5% 100% 318 cfm Yes

7% 88% 350 cfm Yes

11% 63% 288 cfm Yes

15% 40% 233 cfm Yes

a Based on TAB measurements

The Rebel met the ventilation-based demonstration objectives. At all OA damper and supply fan 

speed configurations (except for the 0% damper position), the Rebel provided ventilation that 

exceeded the ASHRAE 62.1 minimum requirement. Additionally, the Rebel maintained an OA 

flow rate range of 233–318 cfm, which is an approximately 60% reduction from the OA flow 

rate for the baseline RTU, even at a 0% damper position. Section 4.2 summarizes the annual 

energy savings impacts of the Rebel maintaining a lower ventilation flow rate while still 

maintaining the minimum ASHRAE 62.1 requirements (Table 15).
38

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5 Economic Performance Analysis and Assessment

Economic results of the demonstration indicate application of high-efficiency RTUs can yield a 

positive economic return in Hawaii. In demonstration of the Rebel, the aggregate annual energy 

savings is estimated at 3.8 MWh/yr for a 10-ton RTU serving a small office building. In 

comparison to a baseline RTU, minimally compliant with ASHRAE Standard 90.1-2010, NREL 

estimates a total discounted operational savings of $18,000 over a 15-year operational life, with a 

simple payback occurring within the ninth year of operation. The economic analysis conducted 

(results shown in Table 19) was based on a cost different between the Rebel versus the baseline 

which included the Rebel’s larger incremental costs for the cabinet coating, condenser coil 

coating, extended 5 year parts and compressor warranties, and roof curb. NREL thought it 

important to add that just comparing the RTUs themselves, excluding these incremental costs, 

the same energy savings yields a simple payback in the fifth year of operation.

Regional factors, including Hawaii’s relatively high electricity pricing and year-round demand 

for cooling, were key contributors to the cited economic return. Results indicate the Navy would

achieve a positive ROI in deployment of this technology in Hawaii assuming a minimum of 15 

year economic life. These energy savings and ROI are not directly transferable to other 

geographic regions (see note b for Table 19). Section 8 states that additional field demonstrations 

are recommended to quantify savings in other climates that most likely have much lower utility 

rates. 

Table 19 provides a full summary of economic results, in addition to key analysis inputs. 

Estimates for total discounted operational savings, savings to investment ratio, and simple 

payback were calculated using the latest version of the National Institute of Standards and 

Technology-developed Building Life-Cycle Cost (BLCC) Program. eROI values were provided 

using the latest available version of the Neptune eROI calculator, as provided by NAVFAC.17

 17 eROI is a Navy-specific metric for evaluating benefits of investment in energy technologies. The benefit figure 

reflects the present value of the project’s anticipated contributions to energy, as well as its contribution, in dollarequivalent terms, to other Navy objectives, such as improving energy reliability for critical infrastructure, reducing 

greenhouse gas emissions, meeting regulatory mandates, and so on. An eROI greater than 1 indicates the project’s 

benefits are anticipated to exceed its costs. The higher the eROI value, the more attractive the project.
39

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Table 19. Overall Economic Analysis of Rebel RTU Demonstration

Economic Analysis Results Key Analysis Inputs

eROI Value 12.4 Annual energy savings 3.8 MWh/yr

Total Discounted 

Operational Savings $18,000 Electricity pricea $0.425/kWh

Savings to Investment Ratio 1.4 Investment cost deltab $14,519

Simple Payback <9 years Units installed 1

Adjusted Internal Rate of 

Return 5% Economic life 15 years

a Electricity pricing reflects the average price of FY 2013 and FY 2014 rates at JBPHH. b Investment delta reflects the calculated difference in the purchase price between a code-minimum, baseline 

RTU versus the high-efficiency RTU including the Rebel’s larger incremental cost adds for the cabinet coating, 

condenser coil coating, extended 5 year parts and compressor warranties, and roof curb. Excluding these 

incremental costs, the investment cost delta is $9,679. 

Based on the uncertainty analysis (Appendix H), the annual energy savings of 3.8 MWh/yr is 

±27% based on a 95% confidence interval. Consequently, the economic analysis metrics 

provided in Table 19 also realize the same uncertainty band.

Beyond the uncertainty bands in the predicted annual energy savings, economic results were 

reviewed to evaluate performance sensitivities and potential sources of error in the estimates

provided. Three key factors are identified and described below:

• Utility electricity rate volatility. Significant volatility in JBPHH utility rates from FY 2013 

to FY 2014 indicate analysis results may be susceptible to uncertainty in projecting future 

year utility rate pricing. More specifically, electricity rates jumped from $0.24/kWh in FY

2013 to $0.58/kWh in FY 2014. The expectation, based on discussion with NAVFAC Hawaii

personnel, is for utility rates to decline in FY 2015, but an exact value remains uncertain. 

This volatility in pricing must be considered in evaluating economic results of this 

demonstration, as applied to JBPHH.

A preliminary sensitivity analysis was performed to evaluate the effect of electricity 

pricing uncertainty on economic yield. Figure 21 shows savings to investment ratio

estimates for a 15-year economic life across an electricity pricing range of $0.325–

$0.525/kWh. This range encompasses a ±$0.10/kWh sensitivity band around the nominal 

rate applied to the economic analysis. As indicated by the figure, electricity pricing has a 

significant impact on estimated economic return. 
40

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Figure 21. Sensitivity analysis on electricity pricing

• Results are region-specific. Electricity pricing, weather patterns, and climate are key input 

parameters in estimating energy and cost savings. Hawaiian values for these parameters, 

although reasonably attributable to other areas of the Pacific, deviate considerably relative to 

other applicable regions, such as the continental United States. Energy and cost saving 

estimates as presented, although promising, are not directly translatable to other geographic 

regions.

• Results based on a single sample. The annual energy savings was calculated by comparing 

a single high-efficiency RTU to a single, code-minimum, baseline RTU serving one type of 

building, a small office. Applying the annual energy savings from this field demonstration to 

a larger population for potential future high-efficiency RTU installations is susceptible to 

significant sampling uncertainty. In Section 8, NREL recommends additional monitoring of 

other high-efficiency RTU installations to achieve a larger sample size with which to provide 

greater confidence in the annual energy saving expectations.

0

0.2

0.4

0.6

0.8

1

1.2

1.4

1.6

1.8

2

$0.305 $0.355 $0.405 $0.455 $0.505

Savings to Investment Ratio (SIR)

Electricity Price ($/kWh)
41

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6 Project Management Considerations

Execution of this technology demonstration was programmatically straightforward. Challenges 

experienced were unique to the constraints of the demonstration. Section 6.2 summarizes how 

the acquisition using a minor construction contract mechanism resulted in lack of response from 

several design-build firms b burdensome administrative requirements associated with the 

demonstration. Further deployment of this technology should not present significant challenges 

beyond those typical to the installation of RTUs. There are negligible cost differences in the 

design (Section 6.3) and installation (Section 6.4) activities between high-efficiency and baseline 

RTUs. Table 20 provides a summary of programmatic elements of this project and a high-level 

timeline of events.

Table 20. Summary of Programmatic Elements 

Programmatic Summary 

Implementation Method Design-build contractor, minor construction

Key Contractors TWT

Critchfield Pacific Inc.

Period of Performance 20 months

Project Timeline

March 2012–September 2012 Site selection and approval

October 2012–February 2013 Design build solicitation and award

March 2013–June 2013 Design

June 2013–July 2013 Site construction

August 2013–October 2013 Commissioning and TAB

October 2013–January 2014 Demonstration

6.1 Site Approval, National Environmental Policy Act, and DD1391 

Site selection was based on identification of facilities needing RTU replacement and evaluation 

of these facilities in providing an effective environment for comparison of the high-efficiency

RTU to a baseline RTU. Site approval, the National Environmental Policy Act, and DD1391 

activities were required for this demonstration. All of these activities presented minimal 

administrative burden and were performed over a period of a few months. For the National 

Environmental Policy Act evaluation, a categorical exclusion was determined.

6.2 Contracts and Procurement 

The implementation strategy for this project used a competitively selected design-build contract. 

As a technology demonstration of a set of two RTUs, acquisition using a minor construction, the 

design-build contract presented a solicitation challenge. Applicable Division 01, General 

Requirements, utilized by this project are presented in Table 21.
42

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Table 21. Applicable Division 01, General Requirements

Unified Facilities Guide Specifications

Division 01—General Requirements

01 11 00 Summary of Work

01 14 00 Work Restrictions

01 30 00 Administrative Requirements

01 33 00 Submittal Procedures

01 35 26 Governmental Safety Requirements

01 45 00.10 20 Quality Control for Minor Construction

01 57 19.00 20 Temporary Environmental Controls

01 74 19 Construction and Demolition Waste Management

01 78 00 Closeout Submittals

For future acquisitions, we recommend the following:

1. Facility owners should consider defining equipment conditions that determine an RTU’s 

useful lifetime, accounting for economic considerations and applicable climate zones.

2. Facility owners should perform an evaluation of their RTUs, using defined conditions of 

a useful lifetime, which will enable them to determine whether a funded action 

constitutes an activity of “repair” or “construction.” This is especially important for 

government agencies to ensure the correct funding mechanism is applied.

3. Projects should be considered for individual facilities (that result in a complete and 

usable facility) within funding source restrictions. Economy-of-scale benefits are,

however, realizable in a large number of multifacility deployments of this technology.

4. Extended warranties should be considered, but economic payback should be considered 

in evaluation of the net benefits. 

6.3 Design 

Design requirements of the Rebel RTU were limited and consistent with installations of 

commercially available RTUs. A roof curb was required for transitioning the Rebel RTU from a 

vertical discharge to a horizontal discharge unit. This is not a typical requirement in RTU 

installations. UFGS facility construction and technical design specifications were developed, and 

are presented in Table 22.
43

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Table 22. UFGS Facility Construction/Technical Design Specifications

Used in the Construction Activity

Unified Facilities Guide Specifications

Division 23—Heating, Ventilating, and Air Conditioning

23 00 00 Air Supply, Distribution, Ventilation, and Exhaust Systems

23 05 93 Testing, Adjusting, and Balancing for HVAC

23 08 00.00 10 Commissioning of HVAC Systems

23 09 53.00 20 Space Temperature Control Systems

23 82 02.00 10 Unitary Heating and Cooling Equipment

Division 26—Electrical

26 00 00.00 20 Basic Electrical Materials and Methods

26 20 00 Interior Distribution System

6.4 Installation and Construction (includes permitting, interconnect 

agreements, factory acceptance testing, commissioning)

RTU installation was straightforward and easily executed for the baseline and Rebel RTUs.

Except for some additional commissioning work to set up the Rebel’s more advanced controller, 

there was no difference in the construction activity or construction cost between the baseline and 

Rebel. The additional Rebel controls configuration is no more than 2 hours during the 

commissioning activity. The additional 2 hours of a commissioning agent were not factored into 

the economic analysis in Section 5, as this additional cost was minimal relative to the cost of the 

entire installation; an additional 2 hours of commissioning costs approximately $300, based on 

$150 per hour.

Both RTUs were installed over the course of a few weeks. Utilization of a crane for removing 

existing RTUs and installing the new RTUs presented the greatest degree of permitting and site 

coordination but remained consistent with this type of construction activity.

TAB of the RTUs did present some scheduling challenges. Initial TAB report results were not 

consistent with ASHRAE 62.1, and a second TAB activity was required. Unfortunately, 

coordination with the independent TAB provider to execute the second TAB activity took 

significantly longer than expected; commissioning activities were not completed until October 

2013 (3 months postcompletion of RTU installation). These delays, although unfortunate, were 

related to facility conditions and contractual issues, and were not caused by the technical 

performance of the installed RTUs.

6.5 Operation and Maintenance 

The maintenance activities for the Rebel RTU will be similar to those for a baseline RTU, such 

as filter changes and blowing drains. Yet, some of the routine maintenance inspections will 

require interfacing with the advanced controller on the Rebel. The controller settings are 

numerous and can be overwhelming to an untrained technician. Although Rebel provides 

significant control, installation, and O&M literature on its website (www.go.Rebel.com/rebel), if 

NAVFAC begins to adopt high-efficiency RTUs, NREL recommends the NAVFAC HVAC 
44

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technicians receive formal training to work on them. As a part of the DOE challenge 

specification, these high-efficiency RTUs incorporate more sophisticated AFDD. The advanced 

controller on the Rebel can be leveraged for enhanced troubleshooting and deep dive assessment 

of system components. 

6.6 Training 

At the completion of the construction activity, NREL, subcontractor TWT, and the local Rebel

distributor, Norman S. Wright, held a 3-hour training for NAVFAC HVAC technicians. One 

hour was spent in the classroom reviewing the capabilities of the Rebel and reviewing the control 

and O&M literature for the unit. Two hours were spent at the Rebel RTU, reviewing the system 

layout and interfacing with the controller. In Section 8, NREL recommends NAVFAC HVAC 

technicians receive formal Rebel training to enable them to provide the same level of 

maintenance they currently provide on baseline RTUs. NAVFAC HVAC shop’s standard routine 

maintenance procedure is summarized in Appendix I.
45

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7 Commercial Readiness Qualitative Assessment 

High-efficiency RTUs that meet the DOE Challenge specification are at technology readiness 

level 9. In addition to the Rebel, Carrier has a high-efficiency RTU called the WeatherExpert. 

Table 23 provides a summary. Both Rebel and Carrier distributors in Hawaii have been trained 

on these two new units. These high-efficiency RTUs currently are higher priced and have a 6-

week longer lead time than their standard RTU equivalents.

Table 23. Commercially Available DOE RTU Challenge RTUs

Daikin Applied Rebel (DPS)

(www.go.rebel.com/rebel)

Carrier WeatherExpert (48LC / 50LC)

(www.carrierweatherexpert.com)

3–15 ton capacity 3–23 ton capacity

18.5–20.6 IEER range (>5 ton)

16.9-17.0 SEER range (≤5 ton)

17.8–20.8 IEER range (>5 ton)

17.1–17.5 SEER range (≤5 ton)

Variable-speed lead compressor

Fixed-compressor added above 5 tons

Fixed-speed compressors

2 stages ≤5 ton; 3 stages >5 ton

Variable ECM direct-drive supply fan 

Variable-speed belt-driven supply fan

ECM direct-drive option for ≤5 ton

Variable-speed direct-drive condenser fans Direct-drive ECM condenser fans

Low-leakage OA damper with dry-bulb or 

enthalpy economizing and DCV capability

Low-leakage OA damper with dry-bulb or 

enthalpy economizing and DCV capability

Heat pump, electric heat, gas heating Electric heat, gas heat

Heat pump COP @ 47°F 3.33–9.2

Heat pump COP @ 17°F 2.5–2.75 N/A

HVAC technicians will require additional training to maintain, repair, and fully benefit from the 

more sophisticated controls and advanced technology features. The Rebel is a much more 

sophisticated RTU, particularly with its variable refrigerant flow system. Compared to standard 

one or two stage thermostatic control, the Rebel controller has many more configuration options. 

NAVFAC HVAC technicians will need to have training specific on the Rebel, particularly on 

interfacing with the controller to change control and troubleshoot by leveraging the Rebel’s 

extensive AFDD capabilities. The Rebel supplier in Hawaii, Norman S. Wright, has a field 

technician who has received the advanced training on the Rebel. At first, NAVFAC will need to 

rely heavily on external HVAC technicians, who have been specifically trained on these highefficiency RTUs to resolve advanced maintenance issues. Eventually, NAVFAC HVAC 

technicians will achieve the skills and confidence necessary to perform the same level of 

maintenance they currently perform on code minimum RTUs.

To leverage the full performance of the WeatherExpert, the unit should be controlled using 

Carrier’s ComfortLink interface or by a building management system to enable the supply fan’s 

variable speed capability and separately control each cooling stage. The WeatherExpert’s 

incorporation of belt-driven supply fans and standard fixed-speed compressors may be less of a 

technology jump for NAVFAC HVAC technicians compared to the Rebel. As the Navy 

continues to demonstrate these types of high-efficiency RTUs, the performance impacts should 

be analyzed and captured for incorporation into revisions of the UFGSs and UFCs.
46

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8 Recommended Next Steps

The Rebel RTU showed significant (34%–37%) energy savings compared to the code-minimum, 

baseline RTU meeting UFGS 23 81 00 00 20. For the Hawaii climate, the year-round demand for 

cooling and dehumidification translates these large percentage savings into larger kilowatt-hour

savings compared to RTUs in less cooling dominated climates. Because high-efficiency RTUs 

are new to the industry (2 years for the Rebel and 1 year for the WeatherExpert), they have a 

significant cost premium, which reduces their cost effectiveness. 

Yet, NAVFAC new construction or retrofit projects should find that high-efficiency RTUs 

meeting the DOE RTU challenge specification will meet the DOD’s ROI criteria based on life 

cycle cost analysis, not just using the simple payback metric. Life cycle cost analysis is required 

according to UFC 1-200-02 for either new construction or replacement activities.

Based on NAVFAC’s adoption of high-efficiency RTUs, NREL has three recommendations:

1. Conduct field demonstrations of other high-efficiency RTUs that meet the DOE RTU 

Challenge (such as the Carrier WeatherExpert) in Hawaii and leverage the results of other 

ongoing demonstrations. More specifically, DOD is partnering with the DOE on additional 

field demonstrations of DOE Challenge RTUs. These demonstrations should be completed 

by spring 2015. NAVFAC is participating in three of these demonstrations within the 

continental United States. NREL recommends comparing the energy savings discussed in 

this report with these other demonstrations in different climates. 

2. In a coordinated manner, train NAVFAC HVAC technicians on these high-efficiency RTUs. 

To be successful over the long term, the NAVFAC HVAC technicians will need specific 

training to provide the same level of maintenance they provide on code-minimum RTUs. 

Appendix I provides a summary of typical maintenance procedures NAVFAC technicians 

provide quarterly on RTUs. The nature of HVAC, particularly in Hawaii and Guam where 

cooling is continuous, is that maintenance issues will always arise. Daikin Applied offers 2.5-

day training classes on the Rebel at its facility in Plymouth, Minnesota.18 At the time of 

writing this report, NREL was not aware of specific WeatherExpert training by Carrier. 

NREL recommends NAVFAC contact its local HVAC distributors to learn about local, onsite training. NREL contacted Rebel and Carrier distributors for Hawaii and was told that 

custom training can be provided to NAVFAC HVAC technicians.

3. Incorporate 2 to 4 hours of additional commissioning time for each high-efficiency RTU 

installation. The greater control complexity of these RTUs needs additional attention from a 

commissioning agent to maximize comfort and energy savings. In addition, Carrier and 

Daikin Applied stated that they can pre-program their controllers in the factory based on 

NAVFAC’s specific control requirements, thereby reducing installation time and maintaining 

consistent high performance in the field. Moreover, Daikin Applied has started to offer 

remote on-going commissioning by connecting to their controller over a cellular modem. 

NAVFAC should investigate these on-going services from manufacturers or third parties, 

incorporating the potential deferred O&M costs and improved energy savings within their 

life cycle cost analysis.

 18 “Rebel Rooftop Training Course.” Daikin Applied, 2014. http://www.daikinapplied.com/training.php.
47

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Bibliography

ASHRAE. (2002). ASHRAE Guideline 14-2002. Measurement of Energy and Demand Savings. 

American Society of Heating, Refrigerating and Air-Conditioning Engineers, Atlanta, GA.

Berglof, K. (2011). Performance Inspections with Innovative Analyzing Equipment Results in 

Significant Energy Savings in Air-Conditioning and Refrigeration Systems, Accessed Jan. 10, 

2013: www.eeswest.com/wp-content/themes/xero/pdf/pr-berglof-performance-inspections-iirprag-2011(v2).pdf.

Wang, W.; Katipamula, S. (September 2013). Part-Load Performance Characterization and 

Energy Savings Potential of the RTU Challenge Unit: Daikin Rebel, PNNL-22720. Accessed 

Oct. 5, 2013: www.pnl.gov/main/publications/external/technical_reports/PNNL-22720.pdf.

Daikin. (March 2013). MicroTech III Unit Controller for Rebel Commercial Package Rooftop 

Systems. Accessed April 3, 2013:

http://lit.daikinapplied.com/bizlit/DocumentStorage/RooftopSystems/InstallationandOperationM

anuals/OM_1141-2_Rebel_DPS-MT3_Controller.pdf.

Unified Facilities Criteria UFC-1-200-02. (March 2013). High Performance and Sustainable 

Building Requirements. Accessed June 6, 2013: www.wbdg.org/ccb/browse_cat.php?c=4.

Unified Facilities Criteria UFC-3-410-01. (July 2013). Heating, Ventilating, and Air 

Conditioning Systems. Accessed July 15, 2013: www.wbdg.org/ccb/browse_cat.php?c=4.

Unified Facilities Guide Specifications UFGS-23 81 00.00 20. (November 2009). Division 23 –

Heating, Ventilating, and Air Conditioning. Accessed Nov. 10, 2012: 

www.wbdg.org/ccb/browse_cat.php?c=3.
48

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Appendix A: ClimaCheck Methodology

Figure A-1 and Figure A-2 show the schematics of the Rebel and baseline RTUs through the 

ClimaCheck website. For each minute of DX operation, the ClimaCheck methodology utilizes 

refrigerant pressure, refrigerant temperature, and compressor power measurements to calculate 

real-time EER and cooling capacity.

19

Figure A-1. Rebel refrigerant-side monitoring (instance December 10, 2013 6:40)

Source: ClimaCheck

 19 Berglof, K. Performance Inspections with Innovative Analyzing Equipment Results in Significant Energy Savings 

in Air-Conditioning and Refrigeration Systems. Accessed January 10, 2013: www.eeswest.com/wpcontent/themes/xero/pdf/pr-berglof-performance-inspections-iir-prag-2011(v2).pdf.
49

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Figure A-2. Baseline refrigerant-side monitoring (instance December 4, 2013 13:00)

Source: ClimaCheck
50

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Appendix B: Model Geometry, Envelope, and Internal 

Loads

NREL dimensioned the entire space and developed a three-dimensional model of building 550, 

as shown in Figure B-1. Based on the actual air distribution layout, the space was split into two 

separate thermal zones. The southern zone (dimensioned 60 feet × 43 feet) was served by the 

Rebel. The northern zone (dimensioned 60 feet × 40 feet) was served by the baseline RTU. The 

two zones were simulated to exchange air based on a 1 flow per minute air cross-flow through 

the imaginary wall that split the space. The southernmost wall was simulated as adiabatic (no 

heat transfer) as the actual wall abutted a separately conditioned space on the other side of the 

building. 

Figure B-1. Southeast view of building 550 model

Source: Google Maps and NREL SketchUp Model

Table B-1 summarizes the model parameters that significantly influence building sensible and 

latent heat loads. The model included the 4.5-foot overhang around the entire building’s 

perimeter to capture the shading impacts (purple in Figure B-1). The internal sensible and latent 

loads were based on the artificial loads actually set up in the space during the demonstration 

period using heat lamps and humidifiers on timers (see Section 3.4). Two of the model inputs, 

infiltration rate, and window properties (SHGC and U-value), were not known or measured. 

Therefore, NREL adjusted these parameters within appropriate bounds for calibrating the 

models. All the assumptions are specified in Table B-1.

Rebel Area

Baseline Area

Southeast View
51

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Table B-1. Summary of Building Envelope and Internal Load Parameters

Parameter Comments

Total Area = 4,976 ft2 Total model dimensions 60 ft × 83 ft; Rebel side 2,576 ft2; Baseline side 

2,400 ft2

Floor = Carpeting over 

8-in. Concretea Slab

Based on structural drawings; underside of slab set to adiabatic (no heat 

transfer) as first-floor space was separately conditioned to 76°F

Wall = 10-in. Concretea Based on structural drawings; no wall insulation 

Roof = Black Asphalt 

over 8-in. Polystyrene 

above 6-in. Concretea

Slab

Based on structural drawings and measured roof insulation during RTU 

installation; total construction R-value = 42 h-ft2-F/Btu

Window Area = 668 ft2 Window wall ratio = 0.23; SHGC = 0.5 (double pane with some low-e 

coating); U-value = 0.50; SHGC and U-value assumed, no data available 

regarding window construction type other than being double paned

Nominal Infiltration Set 

to 0.10 cfm/ft2 of

Exterior Wall Area; 

Equates to 0.34 Air 

Changes per Hour for 

Building 550

Based on typical building envelope pressure of 0.02 in. WC with typical 

leakage valuesb for commercial buildings equal to 0.10 cfm/ft2 of exterior 

wall area; nominal infiltration rate is modified; each model time step based 

on the DOD BLAST program’s (predecessor to EnergyPlus) 

recommended equation: 0.606 + 0.03636 (Tzone-TOAT) + 0.1177 

(WindSpeed)

Overhead Lighting = 

1 W/ft2

Based on count of 151 T-8 fluorescent lights throughout the office space; 

manually operated by NAVFAC personnel during business weekdays from 

0700 to 1500

Occupancy Sensible + 

Plug Loads = 0.9 W/ft2

Occupancy sensible and plug loads were based on 4,625 W of heat lamps 

distributed throughout the space (32 × 125 W and 5 × 75 W); all lights on 

timers from 0700 to 1700 daily

Occupancy Latent Installed six humidifiers throughout the space that deliver 1.5 gallons of 

moisture each per day—therefore, total latent load of 9 gallons delivered 

each day; total moisture load based on 34 occupants (146 ft2/occ) at 200 

Btuh latent load per occupant; humidifiers are started at 0700 by NAVFAC 

personnel when the overhead lights are turned on; moisture load in the 

model is spread across 24 hours as NAVFAC personnel notified NREL 

that humidifiers were not empty by 1500 when they came to turn the lights 

off but were empty the following morning

a Concrete thermal properties based on 2,300 kg/m3 density. b Tamura, G.T.; Shaw, C.Y. (1976). “Studies on Exterior Wall Airtightness and Air Infiltration of Tall Buildings.”

ASHRAE Transactions 82(1):122.
52

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Appendix C: Rebel Model Summary

Based on the monitored data, NREL leveraged the Rebel’s capability to maintain a constant 

DAT set point to develop a simple modeling procedure. By always knowing the leaving air drybulb temperature, the Rebel RTU model would calculate the total cooling based on the mixed-air 

conditions (entering the evaporator), ambient dry-bulb (entering the condenser), and supply air 

flow rate. The Rebel RTU model’s supply air moisture content was maintained at 85%–95% RH

based on DOE’s lab test results of a 10-ton Rebel (Wang et al 2013). The supply air humidity 

was not monitored in this demonstration because of the significant uncertainty caused by the 

insufficient accuracy of field RH sensors and difficulty of ensuring the supply air was 

sufficiently mixed at a single RH sensor location. 

The Rebel was modeled exactly as it was controlled during the demonstration period. The supply 

fan modulated between minimum and maximum flow rates according to a PI control that is 

summarized below. The Rebel ventilation rate was modeled as if the OA damper opened from 

5%–15% as the supply air flow changed from 100% to 40%, respectively. The ventilation rate 

maintained at all supply fan and OA damper configurations met the minimum ventilation 

requirements per ASHRAE Standard 62.1 without DCV operation. The Rebel was not modeled 

with DCV operation per UFC 3-410-01 (dated July 1, 2013). The compressors were controlled to 

maintain the constant DAT at 60°F (post-supply fan), regardless of the supply air flow rate. If the 

Rebel compressors at 100% capacity could not achieve a 60°F DAT at a given set of mixed-air 

conditions and supply air flow rate, the discharge air condition was calculated based on the

maximum cooling rate the Rebel could provide.

The Rebel cooling capacity was limited in the model based on the maximum cooling capacity 

measured during the demonstration period. NREL found the Rebel would peak at 13 tons when 

the variable-speed compressor was at 100% capacity and the second-stage compressor was 

operating. These measured maximum cooling capacities occurred for the first 5–10 minutes of 

the initial morning cooldown period and the first 1–3 minutes that both compressors would turn 

on after both were off. Therefore, the Rebel’s model was limited to 13 tons. Although the Rebel

RTU installed had a nominal 10-ton capacity, it could overdrive the variable-speed compressor 

to achieve 12 tons capacity under nominal conditions. Then, based on the mixed-air conditions 

(entering the evaporator coil) and ambient dry-bulb (entering the condenser coil), the Rebel RTU 

can achieve an additional 10% capacity above 12 tons.

The following subsections summarize the Rebel RTU modeling and then summarize the 

calibration procedure and results. The DX model summary is provided in Section 4.1.
53

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Supply Fan Model

NREL used the TAB report to correlate the fan speed setting at the MicroTech controller to the 

supply flow rate. Table C-1 summarizes the Rebel model’s supply fan performance at different 

controller fan speed settings. NREL developed a correlation between the controller fan speed 

setting and supply air flow rate (equation C-1 and Figure C-1).

Table C-1. Rebel RTU Supply Fan Performance Based on TAB Report

Fan Speed Setting 

on MicroTech 

Controller

Total Static

Pressure

Supply

Air Flowa

Fan 

Powerb

Total Fan+ 

Motor Static 

Efficiency

100% 2.54 in. WC 4,069 cfm 2,144 W 63%

88% 1.96 in. WC 3,575 cfm 1,578 W 59%

63% 1.24 in. WC 2,547 cfm 693 W 50%

34% 0.37 in. WC 1,601 cfm 214 W 42%

VV̇

SS = �4,114 ∙ ff nnss ssssssssss� − 45 (C-1)

where

VV̇

SS iiii h ss ssss ff ( )

ff nnss ssssssssss is the control fan speed setting.

Figure C-1. Correlation between supply fan controller speed setting and

supply air flow rate based on TAB

0

500

1,000

1,500

2,000

2,500

3,000

3,500

4,000

4,500

0% 10% 20% 30% 40% 50% 60% 70% 80% 90% 100%

Air Flow Rate [cfm]

Supply Fan Controller Setting
54

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At each fan speed, the model needs the associated total static pressure and total static efficiency 

to calculate fan power. Equation C-2 and Equation C-3 provide regression models of total static 

pressure and fan efficiency versus flow fraction, respectively (Figure C-2a). At each time step, 

the EnergyPlus Rebel RTU model will calculate the supply fan power based on the supply air 

flow fraction, static pressure, and fan efficiency (Figure C-2b).

PP FF FF = 1.0518 ∙ ffff2.0269 (C-2)

where 

Pressure Fraction is the fraction of the peak 2.57 in. WC (639 Pa) pressure at 100% fan 

speed

ff is the flow fraction of the 4,069 cfm (1.92 m3/s) supply air flow at 100% fan speed.

FF EE FF FF = (0.5076 ∙ ffff) + 0.5081 (C-3)

where

Fan Efficiency Fraction is the fraction of the peak 63% efficiency at 100% fan speed

ff is the flow fraction of the 4,069 cfm (1.92 m3

/s) supply air flow at 100% fan speed.

Figure C-2. (a) Regression model of supply fan pressure and efficiency as a function of flow 

fraction (b) EnergyPlus model of supply fan power based on flow fraction

The Rebel supply fan was controlled based on the single-zone variable-air zone control logic 

built into the MicroTech III controller. The supply fan modulates its speed between a specified 

minimum and maximum using a PI control based on space temperatures relative to set point. 

Rebel defines three PI control parameters including gain, sample time period, and projected 

ahead time. Due to unstable operation of the supply fan speed identified from the monitored data, 

on November 1, 2013, these control parameters were changed to the following:

• Gain = 0.8 (originally set to 1.5)

• Sample time = 60 seconds (originally set to 30 seconds) 

• Projected ahead time = 400 seconds (originally set to 100 seconds).

y = 1.0518x2.0269

R2 = 0.9792

y = 0.5076x + 0.5081

R2 = 0.9042

0.0

0.2

0.4

0.6

0.8

1.0

1.2

0.00 0.20 0.40 0.60 0.80 1.00 1.20

Pressure Fraction / Efficiency Fraction

Flow Fraction

Pressure Fraction

Fan Efficiency Fraction

Power (Pressure Fraction)

0 W

500 W

1,000 W

1,500 W

2,000 W

2,500 W

0.00 0.20 0.40 0.60 0.80 1.00 1.20

Supply Fan Power [kW]

Flow Fraction
55

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Upon startup, the supply fan sequence follows that shown in Table C-2. For the first few 

minutes, the supply fan goes from off (0), start (1), recirculation (2) to fan only (3). During off 

and start, the supply fan speed remains at 0%. During recirculation, the supply air flow speed is 

controlled to the keypad adjustable maximum heating speed (default 100%). When in cooling, 

the supply fan varies between minimum cooling speed (default 40%) and maximum cooling

speed (default 100%) as space temperature changes. During heating, the supply fan speed varies 

between minimum heating speed (default 40%) and maximum heating speed (default 100%) as 

space temperature changes. During fan only and minimum DAT, the supply fan is controlled to 

the minimum cooling speed (default 40%) or minimum heating speed (default 40%), depending 

on which operation (cooling or heating) the RTU is moving toward.

Table C-2. Fan Operational Sequence Based on Startup

Unit State (BACnet enumeration) Supply Fan Operation

Off (1) Set to 0%

Start (2) Set to 0%

Recirculation (3) Controlled to keypad-adjusted maximum heating speed 

defaulted to 100%

Fan Only (4)

The Rebel implements the PI loop as follows: 

• The current space temperature is set at T1. The current error is calculated using equation C-4:

cc = TT1 − SSSSSS PP (C-4)

• The previous space temperature, sample time minutes prior, is set at T2. The previous error is 

calculated using equation C-5:

pp pp = TT2 − SSSSSS PP (C-5)

• Rebel then calculates the projected error based on the rate the error is changing a function of 

the previous error and current error shown in equation C-6. Projected error equals:

PP PP PP_EE = CC _EE + � cccccccccccccc− pp pppppp pp

SSSS ∗ PPPP � (C-6)

• The change in fan speed (Do) after each sample time period is calculated using equation C-7:

∆SS SSSS = GG ∙ (PP PP PP_EE ) (C-7)

Figure C-3 shows a schematic of the PI logic from the Rebel operations manual.
56

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Figure C-3. Projected error timeline from MicroTech III unit controller operation manual

Outdoor Air Flow Rates

During the demonstration period, the OA damper position varied linearly from 5% open at 100% 

fan speed to 15% open at 40% fan speed. The 40%–100% fan speeds were based on settings on 

the MicroTech controller. Based on the TAB report, NREL developed a correlation between OA 

flow rate and supply air flow rate based on this OA damper control (equation C-8 and Figure C4). The OA flow rates at all fan speeds meet the 219 cfm minimum ventilation requirement (nonDCV) per ASHRAE 62.1. For each time step in the Rebel RTU EnergyPlus model, the OA mass 

flow rate was calculated based on the supply air mass flow rate.

̇OO = �−0.0502 ∙ ̇ ss ssss

2

� + �0.2069 ∙ ̇ ss ssss� − 0.0243 (C-8)

(a) (b)

Figure C-4. OA flow rates based on the supply air flow rate (a) shows flow rates in cfm and

(b) shows regression equations relating OA mass flow rates to supply air mass flow rates

used in the EnergyPlus model of the Rebel RTU

0

50

100

150

200

250

300

350

400

0 1,000 2,000 3,000 4,000

OA Flow Rate [cfm]

Supply Air Flow Rate [cfm]

y = -0.0502x2 + 0.2069x - 0.0243

R2 = 0.944

0.00

0.05

0.10

0.15

0.20

0.25

0.0 0.5 1.0 1.5 2.0 2.5

OA Mass Flow Rate [kg/s]

Supply Air Mass Flow Rate [kg/s]

OA Flow Rate during Final Model

Poly. (OA Flow Rate during Final Model)
57

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Calibration Results

Figure C-5b shows the whole-building energy model of the Rebel RTU calibrated against the 35

days of the calibration period. The modeled data compare well against the measured daily total 

energy versus daily average ambient dry-bulb (Figure C-5a). The 17% CVRMSE is the 

uncertainty of the model. This overlap reinforces the model is properly accounting for the impact 

of ambient conditions on RTU behavior. Finally, Figure C-6a and C-6b show the model meets 

the calibration specification of average space conditions within ±1°F dry-bulb and ±3°F dew

point, respectively.

(a) (b)

Figure C-5. Rebel RTU model versus measured daily RTU energy usage

(a) (b)

Figure C-6. Rebel RTU model versus measured space dry-bulb and dew point

5

10

15

20

25

30

35

68 70 72 74 76 78 80 82 84

Daily Total RTU Energy [kWh]

Daily Average Ambient Dry-Bulb Temperature [°F]

Measured Daily Energy

Modeled Daily Energy

5

10

15

20

25

30

35

5 10 15 20 25 30 35

Modeled Daily RTU Energy [kWh]

Measured Daily RTU Energy [kWh]

Model vs Measured

Correlation

+17% uncertainty based on CVRMSE

-17% uncertainty based on CVRMSE

75.0

75.5

76.0

76.5

77.0

75.0 75.5 76.0 76.5 77.0

Modeled Space Average Dry-Bulb [°F]

Measured Space Average Dry-Bulb [°F]

50

55

60

65

70

50 55 60 65 70

Modeled Space Dew-Point [°F]

Measured Space Dew-Point [°F]

Modeled vs

Measured

Correlation

+3°F DP

-3°F DP
58

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Appendix D: Baseline Model Summary

The baseline RTU was modeled conservatively without penalizing the cooling capability of the 

DX circuit for significant compressor cycling. Therefore, the first and second minute after a 

compressor would turn on, the cooling delivered to the air was modeled as if the compressor had 

already been operating for at least 3 minutes and had achieved steady state operation. NREL was 

not able to quantify the compressor cycling degradation, and therefore, did not want to 

incorporate any degradation in the model that was not supported by monitored performance data. 

Thus, the baseline RTU model annualized energy usage and performance may be slightly 

overstated in the final model. 

The following subsection reviews the DX regression models that capture power and capacity. 

The calibrated results are presented next.

Direct Expansion System

The first set of regression equations that correlate DX cooling power were summarized in 

Section 4.1. The second set of regression equations correlate DX cooling capacity fraction to 

mixed-air wet-bulb and ambient dry-bulb temperatures (equations D-1 and D-2). Table D-1

summarizes these regression models’ parameters. Although the R-squared for these two 

regressions are low for both stages, the absolute change in capacity is not significant; under first 

stage the range is 0.4–0.6 and under second stage the range is 0.9–1.2. Compared to compressor 

power, which was measured using a power transducer with a 3% accuracy specification, the 

cooling capacity was calculated using the ClimaCheck methodology which has a ±7% 

uncertainty. The low R-squared was due to a combination of the small variation in capacity at 

each stage and larger uncertainty of a calculated parameter rather than a measured one.

SSSS SSSS 1 CCCC CC FF FF 0.0077 + (0.0096 ∙ TTWWWW) + (D-1)

(0.0334 ∙ TTOO ) + �−0.0008 ∙ TTOO

2�

SSSS SSSS 2 CCCC CC FF FF − 2.269 + (0.313 ∙ TTWWWW) + (D-2)

�−0.008 ∙ TTWWWW

2� + (0.022 ∙ TTOO ) + �−0.001 ∙ TTOO2�

where

Capacity Fraction is the fraction of the nominal cooling capacity,

TWB is the mixed-air wet-bulb temperature entering the evaporator coil (°C), and

TOA is the ambient dry-bulb temperature (°C).

Table D-1. Baseline RTU Cooling Capacity Regression Parameters

First-Stage DX Second-Stage DX

Adjusted R-Squared 0.56 0.11

Capacity Fraction Range 0.4–0.6 0.9–1.2

Total RTU Operational Hours for Regressions 173 h 68 h

TTWWWW 62°–68°F 62°–69°F

TTOO 62°–86°F 63°–87°F
59

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Calibration Results

Figure D-1b shows the baseline RTU model compares well against the measured data with 

respect to total energy usage per day. Based on the CVRSME, the baseline RTU daily energy 

usage realized a 75 uncertainty based on a 68% confidence interval. Figure D-1a shows the 

model captured the impact of dry-bulb temperature on daily energy usage. Figure D-2a and 

Figure D-2b show the baseline model met the space temperature and dew point specifications for 

calibration.

(a) (b)

Figure D-1. Baseline RTU model versus measured daily DX energy usage

(a) (b)

Figure D-2. Baseline RTU model versus measured space dry-bulb and dew point

0

10

20

30

40

50

60

70

80

68 70 72 74 76 78 80 82 84

Daily Total RTU Energy [kWh]

Daily Average Ambient Dry-Bulb Temperature [°F]

Measured Daily Energy

Modeled Daily Energy

40

45

50

55

60

65

70

75

80

40 45 50 55 60 65 70 75 80

Modeled Total RTU Energy [kWh]

Measured Total RTU Energy [kWh]

Model vs Measured

Correlation

+7% uncertainty

based on CVRMSE

-7% uncertainty

based on CVRMSE

68.0

68.5

69.0

69.5

70.0

70.5

71.0

71.5

72.0

68.0 68.5 69.0 69.5 70.0 70.5 71.0 71.5 72.0

Modeled Space Average Dry-Bulb [°F]

Measured Space Average Dry-Bulb [°F]

Model vs Measured

Correlation

+1°F

-1°F

50

55

60

65

70

50 55 60 65 70

Modeled Space Dew-Point [°F]

Measured Space Dew-Point [°F]

Modeled vs

Measured

Correlation

+3°F DP

-3°F DP
60

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Appendix E: Artificial Internal Sensible and Latent 

Loads

The heat lamps and humidifiers were configured to maintain a uniform distribution across the 

second-floor office space such that both RTUs would be exposed to nearly the same internal 

loads. Although the space is somewhat divided in two because of two separate air distribution 

systems, there is significant air mixing because there is no wall separating these spaces. As the 

Rebel conditions 176 ft2 more than the baseline, the additional internal sensible gain was 

considered negligible. Table E-1 summarizes the number of air diffusers and the internal sensible 

load due to overhead lights, which NREL coordinated with NAVFAC to turn on and off during 

the demonstration period. Table E-2 summarizes how heat lamps were installed throughout the 

space to represent occupant and plug load heat gains. Table E-3 summarizes the combined 

overhead lights, occupant, and plug load sensible internal gains. 

Table E-1. Overhead Lighting Power and Schedule Maintained During the Demonstration Period

Area 4-Way Air Diffusers Overhead Lightsa

Baseline RTU’s Side of the 

Office Space 2,400 ft2 12 200 ft2/diff 73 T-8s 2,336 W 1 W/ft2

Daikin Applied Rebel’s 

Side of the Office Space 2,576 ft2 9 286 ft2/diff 78 T-8s 2,496 W 1 W/ft2

Combined Second-Floor 

Office Space 4,976 ft2 21 237 ft2/diff 151 T-8s 4,832 W 1 W/ft2

a NREL coordinated with NAVFAC to have the overhead lights turned on throughout the second-floor office space 

in the morning between 0630–0730 until the end of the day between 1600–1700. Each T-8 bulb consumes 32 W.
61

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Table E-2. NREL Installed Heat Lamps to Represent the Sensible Loads from

Occupants and Plug Loads

Expected Full Occupancya

Plug Load Power 

Draw Based on Full 

Load Occupancyc

Installed Heat Lampsb

Baseline RTU’s 

Side of the Office 

Space

17 occ 141 ft2/occ 4,250 

Btuh 1,245 W 1,105 W 0.5 W/ft2

17 × 125 W 

heat lamps

3 × 75 W 

heat lamps

2,350 W 1 W/ft2

Daikin Applied

Rebel’s Side of 

the Office Space

17 occ 152 ft2/occ 4,250 

Btuh 1,245 W 1,030 W 0.4 W/ft2

15 × 125 W 

heat lamps

2 × 75 W 

heat lamps

2,275 W 0.9 W/ft2

Combined 

Second-Floor 

Office Space

34 occ 146 ft2/occ 8,500 

Btuh 2,490 W 2,135 W 0.4 W/ft2

32 × 125 W 

heat lamps

5 × 75 W 

heat lamps

4,625 W 0.9 W/ft2

a Based on the office layout and interviewing the original occupants, NREL determined the full load occupancy of the space, 

which resulted in a typical office space occupancy density of ~150 ft2/occupant. Note that per standard office activity metabolic 

rates and average occupant size, each occupant emits 250 Btuh. b Based on the full load occupancy, NREL determined the typical plug load density throughout the space, which resulted in 0.4 

W/ft2. c Beyond the sensible heat gains from the overhead lights, the internal heat gains come from occupants and plug loads. NREL 

installed heat lamps on timers to represent these sensible loads. The timers were set to operate from 0700–1700 daily.

Table E-3. Total Internal Sensible Heat Gain from Overheat Lighting and 

NREL’s Installed Heat Lamps on Timers

Area Total Office Space Internal Sensible Heat Load including 

Overheat Lights, Occupant Heat Gain, and Plug Loads

Baseline RTU’s Side 

of the Office Space 2,400 ft2 4,686 W 15,993 Btuh 1.3 tons 2.0 W/ft2 6.7 Btuh/ft2

Daikin Applied

Rebel’s Side of the 

Office Space

2,576 ft2 4,771 W 16,283 Btuh 1.4 tons 1.9 W/ft2 6.3 Btuh/ft2

Combined SecondFloor Office Space 4,976 ft2 9,457 W 32,277 Btuh 2.7 tons 1.9 W/ft2 6.5 Btuh/ft2

Similar to the sensible internal loads, NREL calculated the latent load based on a fully occupied 

office space. Table E-4 shows how six 1.5-gal humidifiers were distributed throughout the space 

to represent the moisture load of 34 occupants. After the NAVFAC representative turned on all 

the overhead lights each morning between 0630–0730 they filled each humidifier and ensure 

they were plugged in. Each humidifier was on a timer and staggered across the day to ensure a 

consistent vaporization, rather than having all the humidifiers on at once in the morning.
62

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Table E-4. NREL Set Up Humidifiers on Timers to Represent the Total

Internal Latent Heat Gain from Occupantse

Full Occupancya Latent Loadb,d

Daily 

Moisture 

Volumec

Installed Humidifiers

Baseline RTU’s 

Side of the Office 

Space

17 occ 141 ft2/occ 3,400 

Btuh 996 W 4.2 gal/day

3 ×

1.5-gal 

humidifier

~4.5 

gal/day

Daikin Applied

Rebel’s Side of 

the Office Space

17 occ 152 ft2/occ 3,400 

Btuh 996 W 4.2 gal/day

3 × 

1.5-gal 

humidifier

~4.5 

gal/day

Combined 

Second-Floor 

Office Space

34 occ 146 ft2/occ 6,800 

Btuh 1,992 W 8.4 gal/day

6 ×

1.5-gal 

humidifier

~9.0 

gal/day

a Based on the office layout and interviewing the original occupants, NREL determined the full load occupancy of 

the space, which resulted in a typical office space occupancy density of 150 ft2

/occupant. b Latent load based on 200 Btuh/occupant. c Based on the number of occupants and 200 Btuh latent load per occupant, calculated the daily total gallons of 

water that should be vaporized to represent occupant latent loads for the office space.

d To represent the internal occupant latent load, NREL set up humidifiers staggered on timers that would vaporize 

sufficient gallons across the day starting at 0700. Note that floor fans were trained on the humidifiers to speed the 

diffusion of moisture throughout the office space. e Regarding infiltration, NREL coordinated with NAVFAC to leave the entrance doors open while they were at 

building 550 in the mornings and afternoons to turn on/off the overhead lights and the humidifiers. One of the 

windows was left propped open to capture some additional infiltration from occupants entering/leaving the building 

during the workday. 
63

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Appendix F: Baseline and Rebel Monitoring Points

Table F-1 summarizes all the monitoring points maintained on the baseline RTU other than the 

baseline ClimaCheck monitoring points. Similarly, Table F-2 summarizes the Rebel RTU 

monitoring points in addition to the ClimaCheck monitoring points.

Table F-1. Baseline RTU Monitoring Points

Digital or 

Analog 

Signal

Monitoring 

Point

Catalyst Standard 

Sensor or 

Demonstration Add

Sensor 

Manufactu

rer/Model

Sensor 

Accuracy Sensor Notes

Digital-1 Occupied 

Status Standard N/A N/A

Controller-calculated,

based on programmed 

schedule

Digital-2 First-Stage 

Cooling Standard N/A N/A Signal from controller

Digital-3

SecondStage 

Cooling

Standard N/A N/A Signal from controller

Digital-4 Supply Fan 

Power Standard

Yaskawa 

variable 

frequency 

drive Output

unknown

Value is monitored via a 

communication output 

on the drive; power is 

measured internally on 

the drive

Digital-5 Total RTU 

Power Add

Continental 

watt-node 

WNC-3D 

with ACT 

current

transducers

±3%

at leading 

power 

factor of 

0.866

100 Hz resolution WattNode; accuracy 

combines Watt-Node 

and current transducers 

(www.ccontrolsys.com/

w/Metering_System_Ac

curacy)

Analog-1 OA Temp 

Sensor Standard Senva HD3B

±2°C 

(3.6°F) full 

range; 

0.5°C

(0.9°F) typ 

@ 25°C 

(77.0 ̊F)

RTD; positioned inside 

the OA hood, always in 

the shade

Analog-2 RA Temp 

Sensor Standard Senva HD3B

±2 ̊C 

(3.6 ̊F) full 

range; 

0.5 ̊C 

(0.9 ̊F) typ 

@ 25 ̊C 

(77.0 ̊F)

RTD; positioned at the 

RA inlet into the RTU

Analog-3 SA Temp 

Sensor Standard ACI-AN Series ±0.36°F RTD in supply air ductwork

Analog-4 MA Temp 

Sensor Add ACI-AN Series ±0.36°F

Single RTD 

measurement located at 

the filter inlet

Analog-5 OA RH 

Sensor Standard Senva HD3B

±3%, 20%–

80% Range

Capacitance sensor; 

positioned inside the 

OA hood, always in the 

shade
64

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Digital or 

Analog 

Signal

Monitoring 

Point

Catalyst Standard 

Sensor or 

Demonstration Add

Sensor 

Manufactu

rer/Model

Sensor 

Accuracy Sensor Notes

Analog-6 RA RH 

Sensor Standard Senva HD3B

±3%, 20%–

80% Range

Capacitance sensor; 

positioned at the RA 

inlet into the RTU

Analog-7 RA CO2

Sensor Standard AirTest TR9291

±30 PPM;

±3% 

reading

CO2 sensor positioned 

in return air ductwork

Analog-8 Space 

Temperature Add ACI A/1K2W

±1.1°C 

(1.9°F)

Wall-mount temperature 

sensor located at the 

existing thermostat 

location

Analog-9 OA Damper 

Controller Standard CAT-371

0–10 VDC 

signal at 8-

bit 

resolution

Control signal 

generated by controller 

CAT-371

Analog-10 Fan Speed Standard

Communicat

ing Modbus 

signal

N/A

Control signal 

generated by controller 

CAT-371

Table F-2. Rebel Monitoring Points20

BACnet Variable 

Name Description

Eq_ID

Timestamp

FanSpeedRebel

Remapped from "Supply Fan Capacity (SupFanCap)." This read-only 

attribute indicates the current supply fan capacity. The BACnet property reads 

only the subject attribute; however, the LONWORKS variable is only a part of 

the LONWORKS Unit Status network variable. See Unit State for details. This 

variable will read 0% whenever the fan is off. If the unit is configured as 

constant volume, this variable reads 100% when the fan is on. Otherwise, it 

will read the feedback from the variable-frequency drive.

OATempRebel

Remapped from "Outdoor Air Temperature (OutdoorTemp)." This read-only 

attribute indicates the current value of a unit-mounted outdoor air temperature 

sensor. This variable only applies if the unit is configured for an outdoor air 

temperature sensor.

 20 Daikin. March 2013. “MicroTech III Unit Controller for Rebel Commercial Package Rooftop Systems.” Accessed 

April 3, 2013:

http://lit.daikinapplied.com/bizlit/DocumentStorage/RooftopSystems/InstallationandOperationManuals/OM_1141-

2_Rebel_DPS-MT3_Controller.pdf.
65

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BACnet Variable 

Name Description

RATempRebel

Remapped from "Return Air Temperature (RATemp)." This read-only attribute 

that indicates the current reading from the unit return air temperature sensor. 

This variable only applies if the unit is configured for a return air sensor.

DATempRebel

Remapped from "Discharge Air Temperature (DischAirTemp)." This read-only 

property indicates the current reading of the unit discharge air temperature 

sensor.

SpaceTempRebel

Remapped from "Space Temperature Input (SpaceTempInput)." This 

read/write attribute indicates the current space or zone temperature that is 

written from the network. If this network value becomes unreliable, the 

temperature reverts to the value provided by the attached space temperature 

sensor. This variable only applies if the unit is configured for a space 

temperature sensor.

UnitPower This is not a BACnet point. This is monitored power from a separate meter.

AlarmValue

This object allows individual notification of the highest priority active alarm. 

The value in the table below is the largest number in its enumeration that 

corresponds to an active alarm. This object is set to zero if no alarms are 

active.

ActiveFault

ActiveProblem

ActiveWarning

ClgCapacity

This read-only property indicates the current percentage of unit maximum 

cooling capacity. The BACnet property reads only the subject attribute; 

however, the LONWORKS variable is only a part of the LONWORKS Unit 

Status network variable. See Page 90 for details of LONWORKS network 

variable. The BACnet property only applies to the subject data point. The 

LONWORKS variable covers six other data points: Unit State, Heating 

Capacity, Reheat Capacity, Supply Fan Capacity, Economizer Capacity, and 

In Alarm. This variable only applies if the unit is configured for cooling.

ClgStatus

This read-only attribute indicates whether or not cooling is currently enabled. 

If cooling is disabled, the reason is indicated. 1=Enabled; 2=None; 3=Off 

Amb; 4=Off Alarm; 5=Off Net; 6=Off Man.

CmpClgHrs
66

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BACnet Variable 

Name Description

Comp2Hrs

ControlTemp This read-only property indicates the current control temperature. As shown 

in the graph to the right, this parameter is set to "SpaceTempNet."

CurrentState

DewpointSp This read/write property sets the dew point set point via the network.

DischLn1Temp This read-only property indicates the current reading of the unit inverter 

compressor (Comp. 1) discharge line refrigerant temperature sensor.

DischLn3Temp Swap out with DischLn2Temp.

EconCapacity

This read-only attribute indicates the current economizer capacity or outdoor 

air damper position. The BACnet property reads only the subject attribute; 

however, the LONWORKS variable is only a part of the LONWORKS Unit 

Status network variable. See Unit State for details. The BACnet property only 

applies to the subject data point. The LONWORKS variable covers six other 

data points: Unit State, Cooling Capacity, Heating Capacity, Reheat Capacity, 

Supply Fan Capacity, and In Alarm.

EconoHrs This read/write property indicates the economizer accumulated run hours. It 

can be reset via the network.

EconoStatus

This read-only attribute indicates whether or not the economizer is currently 

enabled. If the economizer is disabled, the reason is indicated. 1=Enabled; 

2=None; 3=Off Amb; 4=Off Alarm (Not Used); 5=Off Net; 6=Off Man; 7=Off 

Dehum.

Eft_Lct

This read-only attribute indicates the current value of the unit entering 

fan/leaving coil air temperature sensor. This variable only applies to units 

configured for an entering fan temperature sensor.

EffectOccup

This read-only property indicates if the unit is currently in an occupied, 

unoccupied, or tenant override mode of operation. 1 = Occ; 2 = Unocc; 3 = 

TntOvrd.

EmergOverride

This read/write property shuts off the unit controller. If this property is set to 

Off, the unit controller cannot start based on a time clock or any other means. 

The only way to start the unit controller is to change the value to Normal. If a 

value other than Off or EMERG_SHUTDOWN, is written, this variable reverts 

back to Normal. 1 = Normal; 2 = Off.
67

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BACnet Variable 

Name Description

HumiditySp This is a read/write property that the network can use to set the relative 

humidity set point from the network.

INVCMPHRS This read/write property indicates the inverter compressor accumulated run 

hours. It can be reset via the network.

INVCOMPPRB This read-only BACnet object indicates whether the Inverter Compressor 

Problem alarm is active (1) or not active (0).

RebelStatus

This output network variable indicates the operating status of the unit 

controller. 1 = Enabled; 2 = Off Man; 3 = Off ManCtrl; 4 = Off Net; 5 = Off 

Alarm; 6 = Off Fan Retry.

MINOAPOSNETIN

This read/write configuration property sets the Outdoor Air Damper Minimum 

Position set point for MicroTech III Unit Controller. The Minimum Outdoor Air 

Damper Position Input set point uses this value when it is not being set by

any other function and when Min OA Type is set to Network. The controller 

internally limits the present value that is written between the DCV Limit and 

the Vent Limit (see the Min OA Damper menu on the keypad/display). This 

variable only applies to units configured with an airside economizer.

OccManCmd

This read/write property sets the unit into a different occupancy mode. The 

request is typically sent by a wall-mounted occupant-interface module or a 

supervisory node, typically used to manually control occupancy modes or to 

override the scheduled occupancy. This input is used with nviOccSchedule to 

determine the effective occupancy mode. Refer to Occupancy 

(nvoEffectOccup) section for more information. 1 = Occ; 2 = Unocc; 3 = 

TntOvrd; 4 = Standby (Same as Occ); 5 = Auto.

OccupiedCool

Remapped from "Occupied Cooling Set Point (OccCoolSP)." This read/write 

configuration property sets the Occupied Cooling Set Point is set to this value 

when it is not being set by another function. This attribute uses maximum and 

minimum limits. If the present value is set beyond these limits from the 

network, the value is ignored and the controller continues to control to the last 

valid value. The BACnet property only applies to the subject data point, but 

the LONWORKS variable is a structure that covers three other data points: 

Unoccupied Cooling Set Point, Occupied Heating Set Point, and Unoccupied 

Heating Set Point.

RefDischP This read-only property indicates the current reading of the unit discharge line 

refrigerant pressure sensor.

RefSuctionP This read-only property indicates the current reading of the unit suction line 

refrigerant temperature sensor.

ReheatCapacity

This read-only attribute indicates the current percentage of unit reheat 

capacity. The BACnet property reads only the subject attribute and only 

applies to the subject data point. The LONWORKS variable is only a part of 

the LONWORKS Unit Status network variable. See Unit State for details. The 

LONWORKS variable covers six other data points: Unit State, Supply Fan 
68

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BACnet Variable 

Name Description

Capacity, Cooling Capacity, Heating Capacity, Economizer Capacity, and In 

Alarm.

SpaceRHNETIN

This is a read/write property the network can use to set the relative humidity 

from the network. If the network value becomes unreliable, the humidity 

reverts to the value provided by the attached relative humidity sensor.

SucnRefTemp This read-only property indicates the current reading of the unit suction line 

refrigerant temperature sensor.

TenantOrHrs This read/write property indicates the tenant override operation accumulated 

run hours. It can be reset via the network.

UnitState

This read-only property indicates the current unit operating state. This is a 

LONWORKS only variable that covers six other data points: Supply Fan 

Capacity, Cooling Capacity, Heating Capacity, Reheat Capacity, Economizer, 

and In Alarm. 1 = Off; 2 = Start; 3 = Recirc; 4 = FanOnly; 5 = MinDAT; 6 = 

Htg; 7 = Econo; 8 = Clg.

UnoccupiedCool

This read/write configuration property sets the temperature above which the 

unit starts and provides cooling (night setup) during unoccupied periods. An 

optional space temperature sensor is required for unoccupied cooling 

operation. This attribute uses maximum and minimum limits. If the present 

value is set beyond these limits from the network, the value is ignored and the 

controller continues to control to the last valid value. The BACnet property 

only applies to the subject data point, but the LONWORKS variable is a 

structure that covers three other data points: Occupied Cooling Set Point, 

Occupied Heating Set Point, and Unoccupied Heating Set Point.

ChargeLossPrb This read-only BACnet object indicates whether the refrigerant system charge 

has been completely lost (1) or not (0).

DirtyFilterSw This read-only BACnet object indicates whether the Dirty Filter Warning alarm 

is active (1) or not active (0).

DuctHiLmtSw

This read-only BACnet object indicates whether the Duct High Limit Fault 

alarm is active (1) or not active (0). This variable only applies to units 

configured for supply fan VFDs. 0 – Normal; 1 – Alarm.

EmergencyOffSw This read-only BACnet object indicates whether the Emergency Off Fault 

alarm is active (1) or not active (0).

ExpValveProb This read-only BACnet object indicates whether the Expansion Valve 

Problem alarm is active (1) or not active (0).
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This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

BACnet Variable 

Name Description

HiDlTempPrb This read-only BACnet object indicates whether the High Discharge 

Temperature Problem alarm is active (1) or not active (0).

HiPress1Prb

This read-only BACnet object indicates whether the High Pressure Circuit 1 

Problem alarm is active (1) or not active (0). This variable applies only to units 

configured for two or more mechanical cooling circuits.

HiPress1Sw

This read-only BACnet object indicates the condition of the High Pressure 

Circuit 1 Switch (Closed (1) or Open (0)). The ‘OffNormal’ state of this object 

indicates a High Pressure Circuit 1 Problem.

IFBCommPrb This read-only BACnet object indicates whether the Interface Board 

Communication Problem alarm is active (1) or not active (0).

LoChargePrb This read-only BACnet object indicates whether the Low Refrigerant Charge 

Problem alarm is active (1) or not active (0).

LoPress1Prb This read-only BACnet object indicates whether the Low Pressure Problem 

alarm is active (1) or not active (0).

LoPressDiffPrb This read-only BACnet object indicates whether the Low Pressure Differential 

Problem alarm is active (1) or not active (0).

OaFanPrb This read-only BACnet object indicates whether the Outdoor Fan Problem 

alarm is active (1) or not active (0).

SupFanCtrl

This read/write property selects the supply fan airflow control used on a 

variable air volume unit. If this parameter is set to Duct Static Pressure 

(DSP), the supply fan airflow maintains the duct static pressure at the duct 

static pressure set point. If this parameter is set to Speed, the supply fan 

airflow is controlled to a variable frequency drive speed set via the Supply 

Fan Capacity Input. If this is set to 1ZnVAV, the supply fan airflow is 

controlled to maintain the Control Temperature at the Occupied Cooling Set

Point or the Occupied Heating Set Point depending on the Unit State.

SpaceDewPt This read-only attribute indicates the current dew point calculated from the 

current reading of the optional relative humidity sensor.
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This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Appendix G: Economic Analysis Details

Economic Analysis Information

eROI Analyses

Table G-1. Summary of Key Information Regarding the eROI Analyses Developed for This Project

Input Type Demo Actuals

Date of Analysis Feb. 11, 2014

eROI Version v2.9.16B

Project Overview Tab

Project Category

Fac. Energy 

Improv.

Regional Priority Project No

Max. Financial Benefits Tab

Salvage Value $0

Provide Reliable Energy Tab

MDI Critical Facilities 0

Regulatory & SH Expect. Tab

Regulatory Compliance 2

Public Perception 1

Quality of Service, Goals 0

Quality of Service, # People 1

Develop. Enabling Infrast. Tab

Question 1, Data Improvement 0

Question 2, Flex. Energy Inf. 0

Question 3a, Energy Indep. 2

Question 3b, % of Installations 75%

Project Risk Tab

1. Timeline and Cost ±10%

2. Energy Reduction ±10%

3. a Facility Energy Reliance ±10%

3.b Facility Outages ±10%

3.c Backup Power ±10%

4. Regulatory & Stakeholders ±10%

5. Enabling Infrastructure ±10%

6. Aggregate Benefits ±10%

Impact of Deferring Tab

Impact of Deferring 1 Year No Change
71

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

BLCC Analysis

Table G-2. Summary of Key Information Regarding the Building Life-Cycle Cost Analyses 

Developed for This Project

BLCC Analyses: Key Information

Input Type Value

Report Type MILCON/ECIP

BLCC Version BLC 5.3-12

Location Hawaii

Discounting Convention Mid-Year Discounting

Analysis Type Constant Dollar Analysis

Base Date October 2013

Beneficial Occupancy October 2013

Length of Study 15 Years

Energy Usage Indice 100% through Economic Life

Initial Investment Costa $13,419

Non-Annual Recurring Costb $1,100

User Rates Electricity Escalationc 0%

Real Discount Rate 3.0%

a Initial investment cost equal to the difference between the HE RTU and 

ASHRAE 90.1 code compliant RTU

b Additional training expense, occurring at time of beneficial occupancy. c DOE, State specific escalation rates were not used due to recent, high 

variability in pricing
72

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Appendix H: Uncertainty Analysis 

All RTU field demonstration measurements and models based thereupon have inherent 

uncertainties that should be accounted for when discussing the predicted annual energy usage. 

The uncertainties in the measurements and models in this paper are discussed in this Appendix. 

All of these uncertainties contribute to the variations in the model predictions, expressed in 

confidence intervals.

The final uncertainty in the respective Rebel and baseline EnergyPlus models’ annual energy 

prediction (annual kilowatt-hours) is shown in equation H-1. This uncertainty equation accounts 

for the power meter uncertainty, sample uncertainty (extrapolating several months of measured 

data to a yearly savings prediction) and modeling uncertainty. The following subsections discuss 

the calculation of each uncertainty term. The t-statistic was set to 2.04 based on an n-p of 70 and 

95% confidence interval (2 standard deviations). NREL calculated the total uncertainty to be 

±27% of the annual energy savings based on a 95% confidence interval.

UU = �RR ii 2 + UUss

2 + UU2 (H-1)

where

UT is the total uncertainty of the EnergyPlus model’s annual energy prediction,

REinstrument is the total uncertainty of the RTU power measurement based on the power 

meter manufacturer’s stated accuracy,

Us is the sampling uncertainty,

Um is the uncertainty in the EnergyPlus model, and

t is the t-statistic.

Rooftop Unit Power Measurement Uncertainty

The baseline and Rebel RTUs total power were monitored using 100 hertz resolution WNC-3D 

watt-nodes with ACT current transducers on each phase. The manufacturer, Continental 

Controls, provides the calculation procedure for combining the accuracy of their watt-node and 

current transducers based on power factor. For the RTU power measurements, which are

predominantly inductive motor loads, the lagging power factor will range from 0.8 to 0.9

(www.ccontrolsys.com/w/Metering_System_Accuracy). Based on the on-site power factor 

measurement being above 0.85 for the power entering both RTUs, NREL stipulated the 

uncertainty of the power measurement was 3% based on the calculated combined watt-node and 

current transducer measurement accuracy.

Sampling Uncertainty

There are two types of sampling uncertainties. The first is the sampling uncertainty based on 

measuring across a large cross-section of RTU characteristics found at NAVFAC facilities,

including make, model, size, and building type served. The sample size of this field 

demonstration is 1. Because the scope of the study was to quantify the energy savings of one 10-

ton Rebel against one 10-ton baseline, this sampling uncertainty was not considered. While the 

savings numbers presented in this report can be indicative of energy savings realized on a larger 

sample set, these energy savings are by no means representative of a random sample set 

representing the entire RTU sample set at NAVFAC facilities.
73

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

The second type of sample uncertainty deals with the fact the annual energy savings is based on 

a model that was calibrated against several months of field demonstration data (November 2013 

through January 2014). The data samples are compared in “days” as NREL used daily total 

energy usage (kilowatt-hours) when calibrating the models. The baseline EnergyPlus model was 

calibrated against 36 days measured during the demonstration period. The Rebel EnergyPlus 

model was calibrated against 35 days measured during the demonstration period. The 

EnergyPlus calculation of annual energy usage is based on 260 days (5 days per week multiplied 

by 52 weeks).

21

Equation H-2 shows the calculation of this sampling uncertainty for the baseline and Rebel 

annual energy usage. This methodology is based on Equation 5.1 in ASHRAE Guideline 14.

22

Because the energy savings is the difference between the baseline and Rebel model energy 

outputs, the sampling uncertainty was calculated by combining both together. Therefore, the total 

number of data samples (Q) was 520 days (1 year at 260 days for the Rebel Model plus 1 year at 

260 days for the baseline model). The number of measured samples (q) was 71 days (36 days for 

baseline plus 35 days for Rebel). The combined sampling uncertainty was 8%.

UUss = 100

� × �(1 − qq/QQ) �∑ � − ��

2

/(qq − 1) =1 � /qq (H-2)

where

Us is sampling uncertainty (%),

� is mean of the measured data (kWh/day),

q is number of samples in the measured data,

Q is total number of data samples for both annual models (520 days), and

is measured data sample (kWh/day).

EnergyPlus Model Uncertainty

During the calibration process, NREL compared the daily modeled energy usage (kilowatthours) versus the daily measured energy usage (kilowatt-hours). Equation H-3 shows the 

calculation procedure for the coefficient of variation of the root mean squared error CVRMSE,

based on the measured versus modeled daily energy usage. Similar to the sampling uncertainty 

calculation above, the CVRMSE was calculated combining the measured versus model with both

baseline and Rebel RTU calibration data sets. The CVRMSE for the combined baseline and 

Rebel calibration periods was 10%. When calculated separately, the CVRMSE of the Rebel 

model was 17% and 7% for the baseline model.

 21 NREL did not include holidays when running the annual models because typical thermostat controls can only 

handle a 7-day schedule, not incorporating holidays. Therefore, even though the buildings are empty on holidays, 

the RTUs will continue to run. However, the energy models did account for reduced building loads on 10 holidays 

across the year. 

22 ASHRAE. ASHRAE Guideline 14-2002. Measurement of Energy and Demand Savings. Atlanta, GA: American 

Society of Heating, Refrigerating and Air-Conditioning Engineers, 2012. 
74

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Um = CVRMSE = �∑ � −⏞�

2

=1 /( −pp)

� (H-3)

where

is the measured daily energy usage during the calibration period,

⏞ is the model daily energy usage during the calibration period,

n is the total days in the Baseline and Rebel calibration periods, and 

p is equal to 1,

� is the average measured daily energy usage during the calibration period.
75

This report is available at no cost from the National Renewable Energy Laboratory (NREL) at www.nrel.gov/publications.

Appendix I: Naval Facilities Engineering Command

Routine Rooftop Unit Maintenance Procedures

The NAVFAC PAC HVAC shop provided its quarterly Job Plan and Task Report, which is 

shown in Figure H-1.

Figure H-1. NAVFAC quarterly RTU maintenance procedure