# Experimental Study of the Gas Engine Driven Heat Pump with Engine Heat Recovery

Authors: Wei Zhang; Tao Wang; Sulu Zheng; Xueyuan Peng; Xiaolin Wang
Journal: Mathematical Problems in Engineering
 (2015)

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## Abstract

Gas engine driven heat pumps (GEHPs) represent one of practical solutions to effectively utilize fossil fuel energy and reduce environmental pollution. In this paper, the performance characteristics of the GEHP were investigated experimentally with engine heat recovery. A GEHP test facility was set up for this purpose. The effects of several important factors including engine speed, ambient temperature, condenser water flow rate, and condenser water inlet temperature on the system performance were studied over a wide range of operating conditions. The results showed that the engine waste heat accounted for about 40–50% of the total heat capacity over the studied operating conditions. It also showed that engine speed and ambient temperature had significant effects on the GEHP performance. The coefficient of performance (COP) and the primary energy ratio (PER) decreased by 14% and 12%, respectively, as engine speed increased from 1400 rpm to 2000 rpm. On the other hand, the COP and PER of the system increased by 22% and 16%, respectively, with the ambient temperature increasing from 3 to 12°C. Furthermore, it was demonstrated that the condenser water flow rate and condenser water inlet temperature had little influence on the COP of the heat pump and the PER of the GEHP system.


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## Body

## 1. Introduction

Improving energy utilization efficiency of thermal processes using fossil fuels is one of the important ways to maintain sustainable economic development and protect the environment of the world. Space and process heating is one of the largest energy consuming sectors. Improvements in energy utilization efficiency of systems in this sector provide a basis for integrating an environmental dimension into energy policy. Heat pumps have been proven to have the best prospects for attaining this goal in a wide variety of appropriate heat applications [1]. Among heat pump systems, GEHPs have been paid more attention in recent years due to their distinguished advantages, such as (1) an ability to recover waste heat released from the engine cylinder jacket and exhaust gas, (2) easy modulation of the engine speed to comply with heat load, and (3) high PER in heating processes.Many research works have focused on the performance characteristics of GEHPs using theoretical modeling and experimental approaches. Regarding the chronological development of theoretical models for the GEHP system, Zhang et al. [2] developed a steady-state model for an air to water GEHP in heating mode. The engine and compressor models were based on experimental and manufacturer’s data, while heat exchanger models were built on mass and energy balance equations. A theoretical heat recovery model was incorporated in the simulation. The results showed that the engine speed has a much larger effect on heat pump performance in comparison to environmental temperature. Based on the mass and energy conservation laws, Shin et al. [3] wrote an algorithm to model the GEHP dynamically in cooling mode. Good agreement with the real system was reached for temperatures, pressures, and system COPs. Yang et al. [4] further reported an intelligent control simulation model for the GEHP in heating mode to predict its dynamic performance. The model was demonstrated to be very effective in analyzing the effect of control parameters. The steady-state accuracy of the intelligent control scheme was higher than that of the fuzzy controller which was adopted for the GEHP by Li et al. [5]. Xu and Yang [6] built a theoretical mathematical model in which the waste heat recovered from the engine was used to control year-round room air humidity. The analysis showed that the GEHP could save more energy than the electrical engine heat pump. Sanaye and Chahartaghi [7] developed a theoretical model to predict the performance of the GEHP under different operating conditions. The comparison between simulation results and experimental data showed that the error percentages for suction pressure, discharge pressure, fuel consumption, and system COP were all within 10%, for both cooling and heating modes. Sanaye et al. [8] further combined this model with an economic model in which the economics of the GEHP were analyzed for both residential and commercial buildings in various climate regions of Iran. More recently, Yang et al. [9] developed a thermal model for a GEHP working as a water heater in winter. The model was validated by experimental data. The performance of such a GEHP was analyzed in terms of the COP of the heat pump and PER of the system. The results showed that the water flow rate, hot water temperature, and rotary speed all had an effect on the COP and PER of the system.As for experimental studies of the GEHP system, Patel et al. [10] compared the performance of a GEHP with R22 and R134a as the primary refrigerants. The test was monitored to determine the energy consumption, cooling capacity, and COP, as well as hours and modes of operation. Furthermore, the energy saving using the GEHP was identified in comparison to the electric driven system. Yang et al. [11] investigated the operating characteristics of a GEHP experimentally under different working conditions. It showed that the GEHP clearly saved energy and the system PER is as high as 1.42. Lazzarin and Noro [12] evaluated the performance of S. Nicola plant in Vicenza during three years of operation. Plant heating load was supplied using a GEHP and two condensing boilers. The GEHP system showed good energy efficiencies and low emissions, although it did not show good economics due to the very low local taxation for natural gas in Italy. Recently, Elgendy and Schmidt [13] experimentally investigated the performance of a GEHP, used in water cooling, without engine heat recovery. It was found that the evaporator water inlet temperature and engine speed substantially affected the PER of the system under the studied operating conditions. Soon after this experiment, Elgendy et al. [14] further studied the performance of a GEHP for hot water supply. This study showed that system PER and total heating capacity increased as the condenser water inlet temperature increased and engine speed decreased. Brenn et al. [15] presented annual efficiencies of a GEHP for building heating and compared GEHP performance with electrically driven heat pump and conventional boiler technologies. The comparison showed that the efficiency of the GEHP was much higher than that of the electrically driven heat pump and about twice that of conventional boiler technologies.From the above review, some experimental and theoretical investigations on the GEHP system performance are available. However, there is still a lack of experimental data on the GEHP system with engine heat recovery. In this paper, a GEHP system test facility with R407c as a primary refrigerant is constructed and equipped with the necessary instruments. The proportion of engine waste heat to total heat capacity at various operating conditions is analyzed. Furthermore, the effects of engine speed, ambient temperature, condenser water flow rate, and condenser water inlet temperature on the GEHP performance are studied experimentally. The research work provides useful information for system design and energy efficient control strategy.


## 2. The Experimental Set-Up and System Description

Figure1 shows the experimental set-up of the GEHP system. Schematics with instrumentation points are shown in Figure 2. The system includes a gas engine (Japanese Nissan of nominal heat capacity 39 kW and nominal speed 1800 rpm), a sliding vane compressor, a condenser (plate type heat exchanger), an electronic regulating valve, an evaporator, a four-way valve, a waste heat exchanger, an exhaust heat exchanger, two gas-liquid separators, an engine cylinder heat exchanger, a torque meter, operational and safety control devices, and a set of well-insulated pipes. The measurement points are shown in Figure 2. The environmental nonazeotropic refrigerant R407c was adopted. This apparatus consists of three circuits: a gas supply circuit, heat pump working fluid circuit, and engine coolant circuit.Figure 1
Experimental set-up.Figure 2
Schematic of the experimental apparatus with measuring point locations.Heat Pump Working Fluid Circuit. The refrigerant discharged from the compressor (2) enters the condenser (3) where the hot refrigerant exchanges heat with the condenser water. The refrigerant is then cooled and condensed to a subcooled liquid. The liquid refrigerant flows through the electronic expansion valve (6) via the receiver (5) and expands into the evaporator (7) where it absorbs the heat from the ambient air and vaporizes. Afterwards, the refrigerant is channeled into the waste heat recovery exchanger (11) where it further absorbs heat from the engine coolant used to recover heat from the engine cylinder and exhaust gas. Superheated refrigerant enters the accumulator (12) and is sucked by the compressor (2) for the next cycle. In this circuit, the heating capacity of the heat pump is calculated based on the measured condenser water flow rate and the water temperature difference at the condenser inlet and outlet. The compressor power consumption is calculated based on the refrigerant flow rate and the refrigerant specific enthalpy difference across the compressor.Engine Coolant Circuit. Ethylene glycol-water is used as engine coolant to recover engine waste heat from the exhaust gas heat exchanger (14) and the engine cylinder heat exchanger (15). The coolant flows through the exhaust gas heat exchanger (14) and absorbs heat from the exhaust gas. Afterwards, it is channeled into the engine cylinder where it cools the engine and hence ensures the engine’s stable and efficient operation. After the coolant receives the engine waste heat, it is introduced into the heat pump waste heat recovery exchanger (11) where it exchanges energy with the refrigerant from the evaporator and is cooled down for next cycle. The radiator (8) is an auxiliary heat exchanger for engine cooling to prevent the engine coolant temperature from getting too high and hence affect the engine operation. In the engine coolant circuit, the coolant’s mass flow rate, the coolant temperatures at the inlet and outlet of the waste heat recovery exchanger (11), the exhaust gas heat exchanger (14), and the engine cylinder are all measured. The heat recovered from the engine cylinder and exhaust gas is calculated based on the coolant mass flow rate and temperature differences.Gas Supply Circuit. The natural gas supply system consists of a set of high pressure gas cylinders (19), pressure reducing valve (18), and a mass flow meter which can measure the natural gas flow rate to evaluate energy consumed by the engine.The precalibrated PT100 temperature sensors (±0.1°C) are used to measure operating temperatures, while MPM480 digital pressure sensors (±0.2% of full scale, 0–3.5 MPa) are used to record the operating pressures at the measurement points in the refrigeration circuit of the heat pump, as shown in Figure 2. The mass flow rate of refrigerant is measured using the mass flow meter, LWGYC-10, with an accuracy ±0.5% of full scale (0.2–1.2 m3/h), while the electromagnetic flow meter, ZHLD-25 (with accuracy ±0.5% of full scale, 0.3–12 m3/h), is used to measure the engine coolant. LDBE-40S (with accuracy ±0.5% of full scale, 0.3–12 m3/h) is used to measure the condenser water flow rate. The natural gas flow rate is measured by the mass flow meter DMF-1-1 with an accuracy ±0.2% of full scale (0–15 kg/h). All the measured data are recorded in the computer over time, and the measurement locations are marked as T, p, and M for temperature, pressure, and flow rate, respectively, as shown in Figure 2.


## 3. Data Reduction and Error Analysis

### 3.1. Performance Calculation

Measured data for R407c operating pressures and temperatures, as well as ethylene glycol-water and condenser water temperatures, can be used to determine the specific enthalpy values at the inlet and outlet of each component. Then the energy and mass balance calculations can be carried out for the main components of the gas engine driven heat pump, thus enabling the GEHP system performance to be determined from the measured flow rate data.The heating capacityQ˙h is calculated based on the condenser water flow circuit as follows: (1)Q˙h=m˙w,c·cp,w,c·ΔTw,c,where m˙w,c is condenser water flow rate, cp,w,c is specific heat of condenser water at constant pressure, and ΔTw,c is water temperature difference at the condenser inlet and outlet.The heatQ˙exh recovered from the engine cylinder and exhaust gas is calculated based on the ethylene glycol-water flowing in the waste heat recovery exchanger as follows: (2)Q˙exh=m˙gw,exh·cp,exh·ΔTgw,exh,where m˙gw,exh is ethylene glycol-water flow rate, cp,exh is specific heat of ethylene glycol-water at constant pressure, and ΔTgw,exh is ethylene glycol-water temperature difference at the inlet and outlet of the waste heat recovery exchanger.The fractionηexh of the recovered waste heat Q˙exh to the total heat capacity Q˙h is then calculated by(3)ηexh=Q˙exhQ˙h.The compressor powerWcomp is calculated based on the specific enthalpy of the refrigerant at the compressor inlet and outlet: (4)Wcomp=m˙ref·href,out-href,inηcomp,href,out=fPcomp,out,Tcomp,out,href,in=fPcomp,in,Tcomp,in,where m˙ref refers to refrigerant flow rate and href,in and href,out refer to refrigerant specific enthalpy at the compressor inlet and outlet, respectively. Pcomp,in, Pcomp,outTcomp,in, and Tcomp,out are the pressures and temperatures at the compressor inlet and outlet. The specific enthalpy is obtained from the NIST data base according to the temperature and pressure. ηcomp is compressor mechanical efficiency (0.96).The total energy consumptionE˙ng is calculated based on the natural gas flow rate m˙ng and low heating value, LHV, as follows:(5)E˙ng=m˙ng·LHV.The COP of the heat pump and the PER of the GEHP system are then calculated by(6)COP=Q˙hWcomp,PER=Q˙hE˙ng.


### 3.2. Error Analysis

According to Gaussian law of error propagation, the overall relative error (ex) of a quantity x indirectly evaluated from the measured values of the variable ximeas can be calculated by (7)ex=±∑i=1nei2(ximeas).Using (7), the overall relative errors eQ˙h, eQ˙exh, eWcomp, eCOP, ePER of Q˙h, Q˙exh, Wcomp, COP, and PER are calculated as follows: (8)eQ˙h=±em˙w,c2+eΔTw,c2,eWcomp=±em˙ref2+eΔhref2,eE˙ng=±em˙ng2=±em˙ng,eQ˙exh=±em˙w,exh2+eΔTw,exh2,eCOP=±eQ˙h2+eWcomp2,ePER=±eQ˙h2+eE˙ng2,where em˙w,c is the relative error of condenser water flow rate measurements (±1.8%), eΔTw,c is the relative error of condenser water temperature difference measurements (±2.8%), em˙ref is the relative error of refrigerant flow rate measurements (±1%), eΔhref represents the relative error of refrigerant specific enthalpy difference resulting from error of pressure and temperature measurements and is ±1.8%, em˙ng is the relative error of natural gas flow rate measurements (±1.3%), em˙w,exh is the relative error of ethylene glycol-water flow rate measurements (±7%), and eΔTw,exh is the relative error of ethylene glycol-water temperature difference measurements (2.6%).Therefore, the overall relative errors forQ˙h,  Q˙exh, COP, and PER are ±3.3%, ±7.5%, ±3.5%, and ±3.4%, respectively.


## 3.1. Performance Calculation

Measured data for R407c operating pressures and temperatures, as well as ethylene glycol-water and condenser water temperatures, can be used to determine the specific enthalpy values at the inlet and outlet of each component. Then the energy and mass balance calculations can be carried out for the main components of the gas engine driven heat pump, thus enabling the GEHP system performance to be determined from the measured flow rate data.The heating capacityQ˙h is calculated based on the condenser water flow circuit as follows: (1)Q˙h=m˙w,c·cp,w,c·ΔTw,c,where m˙w,c is condenser water flow rate, cp,w,c is specific heat of condenser water at constant pressure, and ΔTw,c is water temperature difference at the condenser inlet and outlet.The heatQ˙exh recovered from the engine cylinder and exhaust gas is calculated based on the ethylene glycol-water flowing in the waste heat recovery exchanger as follows: (2)Q˙exh=m˙gw,exh·cp,exh·ΔTgw,exh,where m˙gw,exh is ethylene glycol-water flow rate, cp,exh is specific heat of ethylene glycol-water at constant pressure, and ΔTgw,exh is ethylene glycol-water temperature difference at the inlet and outlet of the waste heat recovery exchanger.The fractionηexh of the recovered waste heat Q˙exh to the total heat capacity Q˙h is then calculated by(3)ηexh=Q˙exhQ˙h.The compressor powerWcomp is calculated based on the specific enthalpy of the refrigerant at the compressor inlet and outlet: (4)Wcomp=m˙ref·href,out-href,inηcomp,href,out=fPcomp,out,Tcomp,out,href,in=fPcomp,in,Tcomp,in,where m˙ref refers to refrigerant flow rate and href,in and href,out refer to refrigerant specific enthalpy at the compressor inlet and outlet, respectively. Pcomp,in, Pcomp,outTcomp,in, and Tcomp,out are the pressures and temperatures at the compressor inlet and outlet. The specific enthalpy is obtained from the NIST data base according to the temperature and pressure. ηcomp is compressor mechanical efficiency (0.96).The total energy consumptionE˙ng is calculated based on the natural gas flow rate m˙ng and low heating value, LHV, as follows:(5)E˙ng=m˙ng·LHV.The COP of the heat pump and the PER of the GEHP system are then calculated by(6)COP=Q˙hWcomp,PER=Q˙hE˙ng.


## 3.2. Error Analysis

According to Gaussian law of error propagation, the overall relative error (ex) of a quantity x indirectly evaluated from the measured values of the variable ximeas can be calculated by (7)ex=±∑i=1nei2(ximeas).Using (7), the overall relative errors eQ˙h, eQ˙exh, eWcomp, eCOP, ePER of Q˙h, Q˙exh, Wcomp, COP, and PER are calculated as follows: (8)eQ˙h=±em˙w,c2+eΔTw,c2,eWcomp=±em˙ref2+eΔhref2,eE˙ng=±em˙ng2=±em˙ng,eQ˙exh=±em˙w,exh2+eΔTw,exh2,eCOP=±eQ˙h2+eWcomp2,ePER=±eQ˙h2+eE˙ng2,where em˙w,c is the relative error of condenser water flow rate measurements (±1.8%), eΔTw,c is the relative error of condenser water temperature difference measurements (±2.8%), em˙ref is the relative error of refrigerant flow rate measurements (±1%), eΔhref represents the relative error of refrigerant specific enthalpy difference resulting from error of pressure and temperature measurements and is ±1.8%, em˙ng is the relative error of natural gas flow rate measurements (±1.3%), em˙w,exh is the relative error of ethylene glycol-water flow rate measurements (±7%), and eΔTw,exh is the relative error of ethylene glycol-water temperature difference measurements (2.6%).Therefore, the overall relative errors forQ˙h,  Q˙exh, COP, and PER are ±3.3%, ±7.5%, ±3.5%, and ±3.4%, respectively.


## 4. Results and Discussion

The performance characteristics of the GEHP system were studied under different operating conditions, and the effects of key operating parameters on the system heat capacity, heat pump COP, and system PER were investigated. In order to minimize the measurement error, the experiments were repeated four times at each operating condition. The second order polynomial trend was used to fit the experimental data to analyze the effect of the operating parameters on the GEHP system performance. Table1 listed the GEHP experimental operating conditions in this study.Table 1
GEHP experimental parameters.
Parameter
Value
(1) The effect of engine speed experiment
Engine speed (r/min)
1400, 1600, 1800, and 2000
Ambient temperature (°C)
3
Condenser water flow rate (m3/h)
8.53
Condenser water inlet temperature (°C)
40
(2) The effect of ambient temperature experiment
Engine speed (r/min)
1800
Ambient temperature (°C)
3, 7.2, and 11.8
Condenser water flow rate (m3/h)
8.53
Condenser water inlet temperature (°C)
40
(3) The effect of condenser water flow rate experiment
Engine speed (r/min)
1800
Ambient temperature (°C)
3
Condenser water flow rate (m3/h)
7.58, 8.53, and 9.47
Condenser water inlet temperature (°C)
40
(4) The effect of condenser water inlet temperature experiment
Engine speed (r/min)
1800
Ambient temperature (°C)
3
Condenser water flow rate (m3/h)
8.53
Condenser water inlet temperature (°C)
38, 40, and 42
Evaporation pressure (MPa)
0.36~0.44
Condensation pressure (MPa)
2.04~2.13
Evaporation air inlet temperature (°C)
3
Waste heat exchanger water inlet temperature (°C)
71.7~72.9
Waste heat exchanger R407c inlet temperature (°C)
−1.9~−5.2
Exhaust gas heat exchanger exhaust gas inlet temperature (°C)  Cylinder heat exchanger exhaust gas outlet temperature (°C)
165.8~185.9
Exhaust gas heat exchanger exhaust gas outlet temperature (°C)
49.0~51.3
Exhaust gas heat exchanger water inlet temperature (°C)
65.2~67.5
Exhaust gas heat exchanger exhaust gas outlet temperature (°C)  Cylinder heat exchanger exhaust gas inlet temperature (°C)
67.7~69.1
Cylinder heat exchanger exhaust gas outlet temperature (°C)
72.5~72.8


### 4.1. Effect of Engine Speed

One of the GEHP system advantages is that engine speed can be adjusted easily to comply with the heat load. Hence it is important to understand the effect of engine speed on the system performance.Figures3–5 presented the GEHP system performance at different engine speeds. Figure 3 showed that both the heating capacity and the recovered waste heat increased sharply with increasing the engine speed. With the engine speed increasing from 1400 rpm to 1600 rpm, 1800 rpm and 2000 rpm, the heating capacity increased by 12%, 21%, and 29%, respectively, which was consistent with findings reported for a similar GEHP system in the literature [9]. On the other hand, the recovered waste heat increased by 14%, 34%, and 60%, respectively. This implied that more heat was recovered as the engine speed increased. It could be clearly seen in Figure 4. The fraction of the recovered waste heat with respect to the heating capacity increased from 42% to 53% as the engine speed increased from 1400 rpm to 2000 rpm.Figure 3
Heating capacity and recovered waste heat versus engine speed.Figure 4
Fraction of recovered waste heat to heating capacity versus engine speed.Figure 5
Heat pump COP and system PER versus engine speed.Figure5 showed the variation of the heat pump COP and the system PER as the engine speed increased. Both the heat pump COP and the system PER decreased with the increase of engine speed, which was also consistent with the finding for a similar GEHP system reported in the literature [9]. The heat pump COP and the system PER decreased by 14% and 12%, respectively, as engine speed increased from 1400 rpm to 2000 rpm. This implied that the GEHP system could have perfect part-load performance. The reason is explained by the heat transfer areas of the condenser, evaporator, and exhaust heat exchangers. These heat transfer areas were designed based on the nominal speed of the GEHP system (1800 rpm). These heat transfer areas were larger than those designed for lower speeds, which would reduce the fuel consumption and hence improve the system performance at low speeds. For the high speed, the heat transfer area is relatively smaller in comparison to the standard design and hence the heat transfer rate is not sufficient for the large capacity. Therefore, both the engine and heat pump performance drop at high engine speed.


### 4.2. Effect of Ambient Temperature

The effect of ambient temperature on the GEHP system performance was shown in Figures6–8. As shown in Figure 6, the heating capacity increased by 20% and 25%, respectively, as the ambient temperature increased from 3°C to 7.2°C and 11.8°C. This was consistent with that reported for the standard heat pump system. As the ambient temperature increased, the evaporation temperature went up and hence the refrigerant mass flow rate of the heat pump increased, which would result in the increase of the heating capacity.Figure 6
Heating capacity and recovered waste heat versus ambient temperature.Figure 7
Fraction of recovered waste heat to heating capacity versus ambient temperature.Figure 8
Heat pump COP and system PER versus ambient temperature.However, Figure6 showed that the variation of the recovered waste heat was less than 5% as the ambient temperature increased from 3°C to 11.8°C. This is negligible when taking into consideration the experimental measurement error. As the ambient temperature increased, the evaporation temperature went up and the refrigerant absorbed more energy in the evaporator, while less energy was absorbed by the refrigerant in the waste heat recovery exchanger. Therefore, the recovered waste heat was almost the same although the heating capacity increased. This led to the small decrease in the fraction of the recovered waste heat with respect to the heating capacity, with the increase in ambient temperature, as shown in Figure 7.Figure8 indicated the variation of the heat pump COP and the GEHP system PER at different ambient temperatures. The heat pump COP increased by 7% and 22% as the ambient temperature increased from 3°C to 7.2°C and 11.8°C. This can be easily understood from the standard heat pump system. The increase of the ambient temperature led to the increase of the evaporation temperature and pressure which improved the heat pump COP. On the other hand, the GEHP system PER increased by 13% as the ambient temperature increased from 3°C to 7.2°C, while it only increased by 3% when the ambient temperature increased from 7.2°C to 11.8°C. This was due to the waste heat recovery. With increasing ambient temperature, the fraction of recovered waste heat decreased with respect to heating capacity. However, the compressor power increased with the increase in ambient temperature, due to an increase in the refrigerant flow rate. At the same time, the engine efficiency dropped as the ambient temperature increased. The engine fuel consumption was then increased. Therefore, the influence of the ambient temperature on the system PER became relatively smaller at the high ambient temperature. This was consistent with the theoretical finding for a gas engine driven air to water heat pump reported in the literature [2].


### 4.3. Effect of Condenser Water Flow Rate

Figures9–11 showed the dependency of the GEHP system performance upon the condenser water flow rate, with an engine speed of 1800 rpm, ambient temperature of 3°C, and condenser water inlet temperature of 40°C. Measured heating capacity and recovered waste heat against the condenser water flow rate were presented in Figure 9. The influence of the condenser water flow rate on both heating capacity and recovered waste heat was insignificant at the studied flow rate range when considering the measurement error. The heating capacity and recovered waste heat only increased by 6% and 1.2%, respectively, as the condenser water flow rate increased from 7.58 m3/h to 9.47 m3/h. This was consistent with the finding for a small GEHP system reported in the literature [9]. The increase of condenser water flow rate slightly lowered the heat transfer temperature difference and the heat losses of the condenser. The condenser water outlet temperature went down and the heating capacity of the heat pump increased slightly. However, the recovered waste heat barely changed in the experimental process. This explained the decrease in the fraction of recovered waste heat to total heating capacity, as shown in Figure 10.Figure 9
Heating capacity and recovered waste heat versus condenser water flow rate.Figure 10
Fraction of recovered waste heat to heating capacity versus condenser water flow rate.Figure 11
COP and PER versus condenser water flow rate.Furthermore, when the condenser water flow rate increased, the overall refrigerant condensing temperature and pressure dropped, and hence the compressor power consumption reduced. This led to an increase of the heat pump COP, as shown in Figure11. In the experimental process, it was also found that the fuel consumptions dropped slightly due to drop of the compressor power. Therefore, the system PER increased by 6% upon increasing the condenser water flow rate from 7.58 m3/h to 9.47 m3/h.


### 4.4. Effect of Condenser Water Inlet Temperature

Performance characteristics of the GEHP system as a function of condenser water inlet temperature were presented in Figures12–14, with an ambient temperature of 3°C, condenser water flow rate of 8.5 m3/h, and engine speed of 1800 rpm. Figure 12 illustrated that the heating capacity and recovered waste heat decreased as the condenser water inlet temperature increased from 38 to 42°C, which was consistent with the finding reported in the literature [14]. However, the rate of decrease in the heating capacity and recovered waste heat was very small. The fraction of the recovered engine waste heat to the heating capacity remained unchanged with the increase in condenser water inlet temperature, as shown in Figure 13.Figure 12
Heating capacity and recovered waste heat versus condenser water inlet temperature.Figure 13
Fraction of recovered waste heat to heating capacity versus condenser water inlet temperature.Figure 14
COP and PER versus condenser water inlet temperature.Figure14 showed that the heat pump COP and system PER decreased by 4% and 8.5%, respectively, as the condenser water inlet temperature increased from 38 to 42°C. This trend was consistent with the common practice for heat pumps. As the condenser water inlet temperature increased, the refrigerant condensing temperature and condensing pressure went up. Hence the compressor power consumption increased due to the large compression ratio, which led to an increase in engine fuel consumption. Therefore, both the COP and PER reduced.Furthermore, it was observed that the heat pump COP decreasing rate is smaller than the system PER decreasing rate. This is explained by the heat recovery. When condensing pressure increased, the engine fuel consumption increased, while the recovered waste heat did not increase accordingly. Hence the engine efficiency decreased and then the GEHP system PER dropped faster than the heat pump COP.


## 4.1. Effect of Engine Speed

One of the GEHP system advantages is that engine speed can be adjusted easily to comply with the heat load. Hence it is important to understand the effect of engine speed on the system performance.Figures3–5 presented the GEHP system performance at different engine speeds. Figure 3 showed that both the heating capacity and the recovered waste heat increased sharply with increasing the engine speed. With the engine speed increasing from 1400 rpm to 1600 rpm, 1800 rpm and 2000 rpm, the heating capacity increased by 12%, 21%, and 29%, respectively, which was consistent with findings reported for a similar GEHP system in the literature [9]. On the other hand, the recovered waste heat increased by 14%, 34%, and 60%, respectively. This implied that more heat was recovered as the engine speed increased. It could be clearly seen in Figure 4. The fraction of the recovered waste heat with respect to the heating capacity increased from 42% to 53% as the engine speed increased from 1400 rpm to 2000 rpm.Figure 3
Heating capacity and recovered waste heat versus engine speed.Figure 4
Fraction of recovered waste heat to heating capacity versus engine speed.Figure 5
Heat pump COP and system PER versus engine speed.Figure5 showed the variation of the heat pump COP and the system PER as the engine speed increased. Both the heat pump COP and the system PER decreased with the increase of engine speed, which was also consistent with the finding for a similar GEHP system reported in the literature [9]. The heat pump COP and the system PER decreased by 14% and 12%, respectively, as engine speed increased from 1400 rpm to 2000 rpm. This implied that the GEHP system could have perfect part-load performance. The reason is explained by the heat transfer areas of the condenser, evaporator, and exhaust heat exchangers. These heat transfer areas were designed based on the nominal speed of the GEHP system (1800 rpm). These heat transfer areas were larger than those designed for lower speeds, which would reduce the fuel consumption and hence improve the system performance at low speeds. For the high speed, the heat transfer area is relatively smaller in comparison to the standard design and hence the heat transfer rate is not sufficient for the large capacity. Therefore, both the engine and heat pump performance drop at high engine speed.


## 4.2. Effect of Ambient Temperature

The effect of ambient temperature on the GEHP system performance was shown in Figures6–8. As shown in Figure 6, the heating capacity increased by 20% and 25%, respectively, as the ambient temperature increased from 3°C to 7.2°C and 11.8°C. This was consistent with that reported for the standard heat pump system. As the ambient temperature increased, the evaporation temperature went up and hence the refrigerant mass flow rate of the heat pump increased, which would result in the increase of the heating capacity.Figure 6
Heating capacity and recovered waste heat versus ambient temperature.Figure 7
Fraction of recovered waste heat to heating capacity versus ambient temperature.Figure 8
Heat pump COP and system PER versus ambient temperature.However, Figure6 showed that the variation of the recovered waste heat was less than 5% as the ambient temperature increased from 3°C to 11.8°C. This is negligible when taking into consideration the experimental measurement error. As the ambient temperature increased, the evaporation temperature went up and the refrigerant absorbed more energy in the evaporator, while less energy was absorbed by the refrigerant in the waste heat recovery exchanger. Therefore, the recovered waste heat was almost the same although the heating capacity increased. This led to the small decrease in the fraction of the recovered waste heat with respect to the heating capacity, with the increase in ambient temperature, as shown in Figure 7.Figure8 indicated the variation of the heat pump COP and the GEHP system PER at different ambient temperatures. The heat pump COP increased by 7% and 22% as the ambient temperature increased from 3°C to 7.2°C and 11.8°C. This can be easily understood from the standard heat pump system. The increase of the ambient temperature led to the increase of the evaporation temperature and pressure which improved the heat pump COP. On the other hand, the GEHP system PER increased by 13% as the ambient temperature increased from 3°C to 7.2°C, while it only increased by 3% when the ambient temperature increased from 7.2°C to 11.8°C. This was due to the waste heat recovery. With increasing ambient temperature, the fraction of recovered waste heat decreased with respect to heating capacity. However, the compressor power increased with the increase in ambient temperature, due to an increase in the refrigerant flow rate. At the same time, the engine efficiency dropped as the ambient temperature increased. The engine fuel consumption was then increased. Therefore, the influence of the ambient temperature on the system PER became relatively smaller at the high ambient temperature. This was consistent with the theoretical finding for a gas engine driven air to water heat pump reported in the literature [2].


## 4.3. Effect of Condenser Water Flow Rate

Figures9–11 showed the dependency of the GEHP system performance upon the condenser water flow rate, with an engine speed of 1800 rpm, ambient temperature of 3°C, and condenser water inlet temperature of 40°C. Measured heating capacity and recovered waste heat against the condenser water flow rate were presented in Figure 9. The influence of the condenser water flow rate on both heating capacity and recovered waste heat was insignificant at the studied flow rate range when considering the measurement error. The heating capacity and recovered waste heat only increased by 6% and 1.2%, respectively, as the condenser water flow rate increased from 7.58 m3/h to 9.47 m3/h. This was consistent with the finding for a small GEHP system reported in the literature [9]. The increase of condenser water flow rate slightly lowered the heat transfer temperature difference and the heat losses of the condenser. The condenser water outlet temperature went down and the heating capacity of the heat pump increased slightly. However, the recovered waste heat barely changed in the experimental process. This explained the decrease in the fraction of recovered waste heat to total heating capacity, as shown in Figure 10.Figure 9
Heating capacity and recovered waste heat versus condenser water flow rate.Figure 10
Fraction of recovered waste heat to heating capacity versus condenser water flow rate.Figure 11
COP and PER versus condenser water flow rate.Furthermore, when the condenser water flow rate increased, the overall refrigerant condensing temperature and pressure dropped, and hence the compressor power consumption reduced. This led to an increase of the heat pump COP, as shown in Figure11. In the experimental process, it was also found that the fuel consumptions dropped slightly due to drop of the compressor power. Therefore, the system PER increased by 6% upon increasing the condenser water flow rate from 7.58 m3/h to 9.47 m3/h.


## 4.4. Effect of Condenser Water Inlet Temperature

Performance characteristics of the GEHP system as a function of condenser water inlet temperature were presented in Figures12–14, with an ambient temperature of 3°C, condenser water flow rate of 8.5 m3/h, and engine speed of 1800 rpm. Figure 12 illustrated that the heating capacity and recovered waste heat decreased as the condenser water inlet temperature increased from 38 to 42°C, which was consistent with the finding reported in the literature [14]. However, the rate of decrease in the heating capacity and recovered waste heat was very small. The fraction of the recovered engine waste heat to the heating capacity remained unchanged with the increase in condenser water inlet temperature, as shown in Figure 13.Figure 12
Heating capacity and recovered waste heat versus condenser water inlet temperature.Figure 13
Fraction of recovered waste heat to heating capacity versus condenser water inlet temperature.Figure 14
COP and PER versus condenser water inlet temperature.Figure14 showed that the heat pump COP and system PER decreased by 4% and 8.5%, respectively, as the condenser water inlet temperature increased from 38 to 42°C. This trend was consistent with the common practice for heat pumps. As the condenser water inlet temperature increased, the refrigerant condensing temperature and condensing pressure went up. Hence the compressor power consumption increased due to the large compression ratio, which led to an increase in engine fuel consumption. Therefore, both the COP and PER reduced.Furthermore, it was observed that the heat pump COP decreasing rate is smaller than the system PER decreasing rate. This is explained by the heat recovery. When condensing pressure increased, the engine fuel consumption increased, while the recovered waste heat did not increase accordingly. Hence the engine efficiency decreased and then the GEHP system PER dropped faster than the heat pump COP.


## 5. Conclusions

This paper experimentally investigated the performance characteristics of a GEHP system over a wide range of operating conditions. An experimental test rig was built for this purpose. The effect of the engine speed, ambient temperature, condenser water flow rate, and condenser water inlet temperature on the GEHP system performance was analyzed. According to the trendline obtained from the second order polynomial fit on the experimental data, it was found that the engine speed and ambient temperature had a large influence on the system COP and PER, while the condenser water flow rate and condenser water inlet temperature had only a small effect on the system COP and PER. The experimental results showed that(1)
the recovered engine waste heat was about 40–50% of the total GEHP system heating capacity;(2)
the heat pump COP and system PER decreased by 14% and 12%, respectively, as the engine speed increased from 1400 rpm to 2000 rpm; this also implied that the GEHP system could have a good part-load performance;(3)
the heat pump COP and the GEHP system PER increased by 22% and 16%, respectively, upon the ambient temperature increasing from 3 to 12°C; it was also found that the GEHP system PER would not be affected by the ambient temperature when it increased to a certain level;(4)
the condenser water flow rate and inlet temperature had insignificant influence on the GEHP system performance over the studied range.



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*Source: 417432-2015-08-12.xml*