JP2016138715A - heat pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat pump that enables easy calculation of heat pump output or easy calculation of fuel gas consumption.SOLUTION: A heat pump has a configuration for calculating a mass flow rate of a refrigerant on the basis of suction pressure, a suction temperature, a compressor rotational frequency and a compressor constant and calculating heat pump output at the time of detection on the basis of a ratio of the calculated mass flow rate to a mass flow rate of the refrigerant during rated heat pump output and the rated heat pump output, or a configuration for calculating engine toque on the basis of discharge pressure and the suction pressure, calculating engine output on the basis of the engine torque and engine speed and calculating fuel gas consumption of the engine on the basis of the engine output and engine efficiency.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a heat pump.

As a system for outputting the usage status of energy, Patent Document 1 discloses a system that displays an operating status such as temperature, humidity, CO ₂ concentration and human occupancy information, set temperature, startup status, and operation mode around an air conditioner. Disclosure. Patent Document 2 discloses a system that displays information related to the energy processing status of an energy system having any function of power generation, hot water supply, or air conditioning.

  Patent Documents 3 and 4 are systems in which a medium heated by burning a gas in a heat source machine is circulated between the heat source machine and a plurality of terminal devices. Patent Document 3 discloses heat load related information and each terminal. A configuration for calculating gas consumption related information corresponding to each terminal device using gas consumption related information corresponding to each device and correlation knowledge of heat load related information is disclosed. A configuration is disclosed in which gas consumption related information corresponding to each terminal device is calculated from the gas consumption information and the operation information of each terminal device.

JP 2009-134469 A JP 2012-178701 A Japanese Patent No. 3847196 Japanese Patent No. 3953271

  However, none of these Patent Documents 1 to 4 shows a configuration for calculating the heat pump output and a configuration for calculating the consumption amount of the fuel gas. That is, none of the configurations of Patent Literature 1 to Patent Literature 4 can easily calculate the heat pump output or easily calculate the fuel gas consumption.

  Then, an object of this invention is to provide the heat pump which can calculate a heat pump output easily, or can calculate the consumption of fuel gas easily.

  In order to achieve the above object, the present invention provides heat pumps of the following first and second aspects.

(1) Heat pump of the first aspect A heat pump provided with a compressor, a heat source side heat exchanger, an expansion valve, and a use side heat exchanger, wherein the suction pressure detection detects the refrigerant suction pressure in the suction path of the compressor Means, a suction temperature detection means for detecting a refrigerant suction temperature in the suction path of the compressor, and a compressor rotation speed detection means for detecting a compressor rotation speed that is a rotation speed of the compressor. The suction pressure detected by the pressure detection means, the suction temperature detected by the suction temperature detection means, the compressor rotation speed detected by the compressor rotation speed detection means, and a predetermined constant of the compressor The mass flow rate of the refrigerant is calculated based on the compressor constant, and the ratio of the mass flow rate to the mass flow rate of the refrigerant at the rated heat pump output and the detection based on the rated heat pump output A heat pump characterized by calculating the heat pump output of a point.

(2) Heat pump of the second aspect An engine-driven heat pump provided with an engine, a compressor driven by the engine, a heat source side heat exchanger, an expansion valve and a use side heat exchanger, in the discharge path of the compressor Discharge pressure detection means for detecting the discharge pressure of the refrigerant, suction pressure detection means for detecting the suction pressure of the refrigerant in the suction path of the compressor, and engine speed detection for detecting the engine speed that is the engine speed And calculating an engine torque, which is a torque of the engine, based on the discharge pressure detected by the discharge pressure detecting means and the suction pressure detected by the suction pressure detecting means. And an engine output which is an output of the engine based on the engine speed detected by the engine speed detecting means. An engine-driven heat pump that calculates and calculates a fuel gas consumption amount of the engine based on the engine output and engine efficiency.

  In the heat pump of the first aspect and the second aspect, a fan rotation for detecting a fan rotation speed that is a rotation speed of the heat source side heat exchanger fan for the heat source side heat exchanger and the heat source side heat exchanger fan. And a predetermined set consumption of the fan for the heat source side heat exchanger and the fan rotation number detected by the fan rotation number detection means A mode of calculating the power consumption of the heat source side heat exchanger fan based on the correlation with the power can be exemplified.

  ADVANTAGE OF THE INVENTION According to this invention, the heat pump which can calculate heat pump output easily or can calculate the consumption of fuel gas easily can be provided.

1 is a schematic block diagram of a heat pump according to an embodiment of the present invention. It is a schematic block diagram of the heat pump which shows the heating operation state which is performing heating operation. It is a schematic block diagram of the heat pump which shows the cooling operation state which is performing the cooling operation. It is a flowchart which shows an example of the calculation operation of the heat pump output which concerns on 1st Embodiment by the control apparatus in a heat pump. It is a flowchart which shows an example of the calculation operation | movement of the consumption amount of the fuel gas which concerns on 2nd Embodiment by the control apparatus in a heat pump. It is a chart which shows the conversion table showing the correlation with the setting rotation speed of the heat source side heat exchanger fan, and setting power consumption. It is a flowchart which shows an example of calculation operation | movement of the power consumption of the fan for heat source side heat exchangers concerning 3rd Embodiment by the control apparatus in a heat pump.

  Embodiments according to the present invention will be described below with reference to the drawings.

  FIG. 1 is a schematic block diagram of a heat pump 100 according to an embodiment of the present invention.

  The heat pump 100 shown in FIG. 1 drives the compressor 10 which compresses a refrigerant | coolant, and adjusts temperature with the condensation heat | fever of a refrigerant | coolant or the heat of evaporation. Here, the temperature control is, for example, temperature control of indoor air or air in the refrigerator or freezer when the heat pump 100 functions as an air conditioner, and for chiller when the heat pump 100 functions as a chiller. The temperature of the circulating fluid is adjusted. The circulating fluid may be any fluid as long as it acts as a heat medium, and representatively, water can be exemplified. However, it is not limited thereto, and the circulating fluid may be, for example, water containing an antifreeze.

  The heat pump 100 includes a compressor 10 that sucks and discharges refrigerant, a heat source side heat exchanger 20 that exchanges heat between the refrigerant and air (specifically, outside air), and a heat source for the heat source side heat exchanger 20. Side heat exchanger fan 30, adjustment valve 40 that adjusts the flow rate of the refrigerant, use side heat exchanger 50 that exchanges heat between the temperature adjustment target and the refrigerant, and a drive source that drives the compressor 10 (this example) Then, the engine 60), the receiver 71 which collect | recovers liquid refrigerant | coolants, the refrigerant circuit 110 which distribute | circulates a refrigerant | coolant, and the control apparatus 120 are provided.

  Here, the temperature control target is, for example, indoor air or air in a refrigerator or freezer when the heat pump 100 functions as an air conditioner, and circulating fluid when the heat pump 100 functions as a chiller. The engine 60 may be, for example, an engine using gas fuel as a fuel (so-called gas engine) or an engine using liquid fuel as fuel. In this example, the engine 60 is a gas engine. Therefore, the heat pump 100 is a gas heat pump (GHP: Gas Heat Pump). As a drive source, an electric motor other than the engine 60 may be used. When an electric motor is used as a driving source, the heat pump 100 is an electric heat pump (EHP).

  Then, the heat pump 100 circulates the refrigerant between the heat source side heat exchanger 20 and the use side heat exchanger 50 while repeating the state in which the refrigerant is depressurized to a low temperature and the state in which the refrigerant is pressurized to a high temperature. As described later, in the use side heat exchanging unit 101, a heating operation for heating the temperature adjustment target (for example, indoor air) (for example, heating the room) and the temperature adjustment target (for example, indoor air) are cooled ( For example, a cooling operation for cooling the room is performed.

  The compressor 10 may include a plurality of compressors connected in parallel, and the heat source side heat exchanger 20 may include a plurality of heat source side heat exchangers connected in parallel. The regulating valve 40 functions as an expansion valve, and in this example, includes a first regulating valve 41 that can be closed and a second regulating valve 42 that can be closed. The first regulating valve 41 may be a plurality of regulating valves connected in parallel. The 2nd regulating valve 42 and the use side heat exchanger 50 comprise the use side heat exchange part 101, and the use side heat exchange part 101 is taken as the indoor unit in this example. In addition, the heat source side heat exchanging unit 102 including the constituent members excluding the second regulating valve 42, the use side heat exchanger 50, and the pair of communication pipes 110a and 110b among the constituent members of the heat pump 100 is an outdoor unit in this example. It is said that the machine.

  The heat pump 100 includes a refrigerant auxiliary evaporator 72 (sub-evaporator) that exchanges heat between the refrigerant and exhaust heat of the engine 60 (in this example, heat of engine cooling water), a refrigerant auxiliary evaporator adjustment valve 73 that can be closed, Is further provided.

  The refrigerant circuit 110 is provided with the compressor 10, the heat source side heat exchanger 20, the adjustment valve 40, the use side heat exchanger 50, the receiver 71, the refrigerant auxiliary evaporator 72, and the refrigerant auxiliary evaporator adjustment valve 73.

  The refrigerant circuit 110 includes a four-way valve 111, a bridge circuit 112, a first refrigerant path 113a to a thirteenth refrigerant path 113m, and a pair of connecting pipes 110a and 110b. The eleventh refrigerant path 113k to the thirteenth refrigerant path 113m will be described later.

  The four-way valve 111 is configured to switch between a first connection state (the state shown in FIG. 1) and a second connection state according to an instruction signal from the control device 120. The first connection state is a state in which the inflow port 111a and the one connection port 111c are connected, and the other connection port 111d and the outflow port 111b are connected. The second connection state is a state in which the inflow port 111a and the other connection port 111d are connected, and the one connection port 111c and the outflow port 111b are connected. Thereby, the four-way valve 111 can switch the flow direction of a refrigerant | coolant. In addition, in FIG. 1, the heating operation state which is performing the heating operation is shown.

  The bridge circuit 112 includes four check valves (a first check valve 112a, a second check valve 112b, a third check valve 112c, and a fourth check valve 112d). The bridge circuit 112 includes a first check valve row 1121 including two check valves (a first check valve 112a and a second check valve 112b), and the remaining two check valves (a third check valve 112c). And a second check valve row 1122 including a fourth check valve 112d).

  The first check valve row 1121 is configured such that the first check valve 112a and the second check valve 112b are connected in series so that the refrigerant flows in the same direction. The second check valve row 1122 is configured such that the third check valve 112c and the fourth check valve 112d are connected in series so that the refrigerant flows in the same direction. The first check valve row 1121 and the second check valve row 1122 are connected in parallel so that the refrigerant flows in the same direction.

  In the bridge circuit 112, a connection point between the first check valve 112a and the second check valve 112b is a first intermediate connection point P1, and between the first check valve 112a and the third check valve 112c. Is the outflow connection point P2, the connection point between the third check valve 112c and the fourth check valve 112d is the second intermediate connection point P3, and the second check valve 112b and the fourth check valve A connection point between the stop valve 112d and the stop valve 112d is an inflow connection point P4.

  The first refrigerant path 113 a connects the discharge port 10 a of the compressor 10 and the inflow port 111 a of the four-way valve 111. The second refrigerant path 113b connects the outlet 111b of the four-way valve 111 and the inlet 10b of the compressor 10. The third refrigerant path 113 c connects the other connection port 111 d of the four-way valve 111 and one connection port 20 a of the heat source side heat exchanger 20. The fourth refrigerant path 113d connects the other connection port 20b of the heat source side heat exchanger 20 and the first intermediate connection point P1 of the bridge circuit 112. The fifth refrigerant path 113e connects the outflow connection point P2 of the bridge circuit 112 and the refrigerant inflow port 71a of the receiver 71. The sixth refrigerant path 113f connects the refrigerant outlet 71b of the receiver 71 and the inflow connection point P4 of the bridge circuit 112. The seventh refrigerant path 113g connects the second intermediate connection point P3 of the bridge circuit 112 and one communication pipe 110a connected to one refrigerant connection port 50a of the use side heat exchanger 50. The eighth refrigerant path 113h connects the other connection pipe 110b connected to the other refrigerant connection port 50b of the use side heat exchanger 50 and the one connection port 111c of the four-way valve 111. The ninth refrigerant path 113i connects the inflow connection point P4 of the bridge circuit 112 and the refrigerant inlet 72a of the refrigerant auxiliary evaporator 72. The tenth refrigerant path 113j connects the refrigerant outlet 72b of the refrigerant auxiliary evaporator 72 and the junction P5 in the middle of the second refrigerant path 113b. Here, the downstream side (compressor 10 side) of the second refrigerant path 113b from the junction P5 is a junction path 113b1.

  The receiver 71 temporarily stores the liquid refrigerant from the fifth refrigerant path 113e. The first adjustment valve 41 constituting the adjustment valve 40 is provided in the fourth refrigerant path 113d, and the opening degree is adjusted during the heating operation to control the flow rate of the refrigerant. The second regulating valve 42 constituting the regulating valve 40 is provided in the refrigerant path 51 between one communication pipe 110 a and one refrigerant connection port 50 a of the usage side heat exchanger 50 in the usage side heat exchange unit 101. The opening degree is adjusted during the cooling operation to control the flow rate of the refrigerant. The refrigerant auxiliary evaporator adjusting valve 73 is provided in the ninth refrigerant path 113i, and the opening degree is adjusted during the heating operation or the cooling operation to control the flow rate of the refrigerant.

  In the present embodiment, the heat pump 100 further includes a first switching valve 114 and a check valve 115, and the refrigerant circuit 110 further includes an eleventh refrigerant path 113k.

  The eleventh refrigerant path 113k connects the refrigerant path closer to the heat source side heat exchanger 20 than the first regulating valve 41 of the fourth refrigerant path 113d and the outflow connection point P2 of the bridge circuit 112. The first switching valve 114 and the check valve 115 are provided in the eleventh refrigerant path 113k. The first switching valve 114 switches between a distribution state in which the refrigerant is circulated in the eleventh refrigerant path 113k and an interrupted state in which the circulation of the refrigerant is blocked by an opening / closing operation. The check valve 115 causes the refrigerant to flow from the first switching valve 114 to the outflow connection point P2 of the bridge circuit 112, while blocking the refrigerant flow from the outflow connection point P2 of the bridge circuit 112 to the first switching valve 114.

  In the present embodiment, heat pump 100 further includes an oil separator 81 and an accumulator 82.

  The oil separator 81 is provided in the first refrigerant path 113a, separates the lubricating oil of the compressor 10 contained in the refrigerant, and compresses the separated lubricating oil through a valve 81a (specifically, an electromagnetic valve). Return to machine 10. The accumulator 82 is provided in the merging path 113b1 of the second refrigerant path 113b, and has not completely evaporated in the heat source side heat exchanger 20, the use side heat exchanger 50, and the refrigerant auxiliary evaporator 72 acting as an evaporator. Separate the refrigerant liquid.

  In the present embodiment, the heat pump 100 further includes a second switching valve 116, and the refrigerant circuit 110 further includes a twelfth refrigerant path 113l.

  The twelfth refrigerant path 113l connects the bottom opening 82a of the accumulator 82 and the refrigerant path closer to the compressor 10 than the accumulator 82 of the merging path 113b1. The second switching valve 116 is provided in the twelfth refrigerant path 113l, and switches between a circulation state in which the refrigerant flows in the twelfth refrigerant path 113l and an interruption state in which the refrigerant circulation is blocked by an opening / closing operation.

  In the present embodiment, the heat pump 100 further includes a supercooling heat exchanger 91 and a closeable supercooling heat exchanger regulating valve 92, and the refrigerant circuit 110 further includes a thirteenth refrigerant path 113m. Yes.

  The thirteenth refrigerant path 113m connects the inflow connection point P4 of the bridge circuit 112 and the refrigerant path closer to the compressor 10 than the second switching valve 116 of the twelfth refrigerant path 113l. The subcooling heat exchanger 91 has an inflow port 91a on the receiver 71 side and an outflow port 91b on the inflow connection point P4 side of the bridge circuit 112 in communication with the sixth refrigerant path 113f, and the adjustment valve 92 side for the subcooling heat exchanger The inlet 91c and the outlet 91d on the accumulator 82 side communicate with the thirteenth refrigerant path 113m. The adjustment valve 92 for the supercooling heat exchanger is provided in the refrigerant path closer to the inflow connection point P4 of the bridge circuit 112 than the supercooling heat exchanger 91 of the thirteenth refrigerant path 113m, and the opening degree is adjusted during the cooling operation. To control the flow rate of the refrigerant. The supercooling heat exchanger 91 includes a refrigerant that flows in the sixth refrigerant path 113f during the cooling operation and a refrigerant that flows in the refrigerant path closer to the supercooling heat exchanger 91 than the adjustment valve 92 for the supercooling heat exchanger in the thirteenth refrigerant path 113m. Heat exchange between. Thereby, the cooling efficiency of the refrigerant flowing through the sixth refrigerant path 113f during the cooling operation can be improved.

  The first adjustment valve 41, the second adjustment valve 42, the refrigerant auxiliary evaporator adjustment valve 73, and the subcooling heat exchanger adjustment valve 92 can all be adjusted by an instruction signal from the control device 120. . Thus, the first adjustment valve 41, the second adjustment valve 42, the refrigerant auxiliary evaporator adjustment valve 73, and the subcooling heat exchanger adjustment valve 92 can adjust the flow of the refrigerant in the refrigerant circuit 110.

  In this example, the first regulating valve 41 is configured by connecting a plurality of regulating valves that can be closed in parallel. By doing so, the first adjustment valve 41 can adjust the flow rate of the refrigerant in the refrigerant circuit 110 by combining the adjustment valves whose opening degree is adjusted.

  The compressor 10 is connected to the engine 60 via the clutch 11. The clutch 11 takes a connected state in which driving force is transmitted from the engine 60 to the compressor 10 and a disconnected state in which transmission of driving force from the engine 60 to the compressor 10 is interrupted by an instruction signal from the control device 120. It has become.

  The heat pump 100 includes a discharge pressure sensor 151 (an example of discharge pressure detection means), a suction pressure sensor 152 (an example of suction pressure detection means), a first suction temperature sensor 161, and a second suction temperature sensor 162 (an example of suction temperature detection means). ), And a third intake temperature sensor 163 and an engine speed sensor 170 (an example of an engine speed detecting means).

  The discharge pressure sensor 151 detects the refrigerant discharge pressure in the discharge path of the compressor 10. Specifically, the discharge pressure sensor 151 is provided in the refrigerant path upstream of the oil separator 81 in the first refrigerant path 113a (on the compressor 10 side), and upstream of the oil separator 81 in the first refrigerant path 113a. The pressure of the refrigerant in is detected.

  The suction pressure sensor 152 detects the suction pressure of the refrigerant in the suction path of the compressor 10. Specifically, the suction pressure sensor 152 is provided in the refrigerant path on the upstream side (four-way valve 111 side) from the junction P5 of the second refrigerant path 113b, and upstream of the junction P5 of the second refrigerant path 113b. The pressure of the refrigerant in is detected.

  The first suction temperature sensor 161, the second suction temperature sensor 162, and the third suction temperature sensor 163 all detect the refrigerant suction temperature in the suction path of the compressor 10. Each temperature sensor is a thermistor in this example.

  Specifically, the first suction temperature sensor 161 is provided in the refrigerant path on the upstream side (confluence point P5 side) of the accumulator 82 of the confluence path 113b1 of the second refrigerant path 113b, and is more than the accumulator 82 of the confluence path 113b1. The temperature of the refrigerant on the upstream side is detected.

  The second suction temperature sensor 162 is provided in the refrigerant path on the downstream side (compressor 10 side) from the connection part of the merging path 113b1 of the second refrigerant path 113b with the twelfth refrigerant path 113l. The temperature of the refrigerant | coolant in a downstream is detected rather than the connection part with the 12th refrigerant path | route 113l.

  The third suction temperature sensor 163 is provided in the refrigerant path on the downstream side (compressor 10 side) with respect to the connection portion of the twelfth refrigerant path 113l with the thirteenth refrigerant path 113m, and the thirteenth refrigerant path 113l. The temperature of the refrigerant | coolant in a downstream is detected rather than the connection part with the refrigerant | coolant path | route 113m.

  The engine speed sensor 170 is provided in the engine 60 and detects an engine speed that is the speed of the engine 60 (the number of revolutions per unit time).

  The heat pump 100 includes a compressor rotation speed detecting means (specifically, a compressor rotation speed sensor) that detects a compressor rotation speed that is the rotation speed (rotation speed per unit time) of the compressor 10.

  For example, when the compressor 10 and the engine 60 rotate at the same speed, the compressor rotation speed detection means can also be used as the engine rotation speed detection means (specifically, the engine rotation speed sensor 170). On the other hand, when the compressor 10 and the engine 60 are connected via a transmission drive transmission mechanism such as a transmission pulley or a transmission, the compressor rotational speed by the compressor rotational speed detection means is the engine rotational speed detection means. It can be calculated from the engine speed obtained in step 1 using the gear ratio. In this example, the compressor 10 and the engine 60 rotate at the same speed, and the compressor rotation speed detection means (specifically, the compressor rotation speed sensor) is the engine rotation speed detection means (specifically, Is also used as the engine speed sensor 170). In addition, as a compressor rotation speed detection means, the compressor rotation speed sensor which detects a compressor rotation speed directly may be provided separately, for example.

  The heat pump 100 further includes a fan rotation speed sensor 180 (an example of a fan rotation speed detection unit) for the heat source side heat exchanger 20.

  The fan rotation speed sensor 180 is provided in the heat source side heat exchanger fan 30 and detects the fan rotation speed that is the rotation speed (the rotation speed per unit time) of the heat source side heat exchanger fan 30.

  The control device 120 controls the driving of the refrigerant circuit 110 based on detection signals from various sensors.

  Specifically, the control device 120 compresses the refrigerant sucked from the second refrigerant path 113b by the compressor 10, and discharges the compressed refrigerant to the first refrigerant path 113a. During the heating operation, the control device 120 sets the four-way valve 111 in the first connection state to communicate the first refrigerant path 113a and the eighth refrigerant path 113h and to communicate the third refrigerant path 113c and the second refrigerant path 113b. . Further, during the cooling operation, the control device 120 sets the four-way valve 111 in the second connection state so that the first refrigerant path 113a and the third refrigerant path 113c are communicated, and the eighth refrigerant path 113h and the second refrigerant path 113b are connected. Communicate.

  The heat source side heat exchanger 20 functions as an evaporator that absorbs and vaporizes the refrigerant during the heating operation, and functions as a condenser that radiates and liquefies the refrigerant during the cooling operation. The use-side heat exchanger 50 functions as a heater that heats the temperature adjustment target (for example, indoor air) by the refrigerant radiating heat during the heating operation, and the refrigerant absorbs heat during the cooling operation (for example, indoor air). ) Function as a cooler. The refrigerant auxiliary evaporator 72 and the supercooling heat exchanger 91 function as an evaporator that absorbs heat and vaporizes the refrigerant.

  The control device 120 includes a processing unit 121 including a microcomputer such as a CPU (Central Processing Unit), a nonvolatile memory such as a ROM (Read Only Memory), and a storage unit 122 including a volatile memory such as a RAM (Random Access Memory). And has a timer function.

  The control device 120 controls the operation of various components by causing the processing unit 121 to load and execute a control program stored in advance in the ROM of the storage unit 122 on the RAM of the storage unit 122. .

  The control device 120 transmits an instruction command to the first adjustment valve 41 to adjust the flow rate of the refrigerant from the bridge circuit 112 to the heat source side heat exchanger 20 during the heating operation, and during the cooling operation, the heat source side heat exchange. The flow rate of the refrigerant from the vessel 20 toward the bridge circuit 112 is adjusted. Specifically, during the heating operation, the control device 120 determines the degree of superheat (the detected temperature with respect to the saturated vapor pressure temperature) based on the saturated vapor pressure temperature based on the detected pressure from the intake pressure sensor 152 and the detected temperature from the first intake temperature sensor 161. The first adjustment valve 41 can be made to function as an expansion valve that adjusts the flow rate of the refrigerant according to the temperature difference), and the first adjustment valve 41 can be fully opened during the cooling operation. The saturated vapor pressure temperature can be converted from the suction pressure of the compressor 10 detected by the suction pressure sensor 152 using a predetermined conversion formula or conversion table.

  The control device 120 transmits an instruction command to the second regulating valve 42 to adjust the flow rate of the refrigerant from the use side heat exchanger 50 to the bridge circuit 112 during the heating operation, and from the bridge circuit 112 during the cooling operation. The flow rate of the refrigerant toward the use side heat exchanger 50 is adjusted. Specifically, the control device 120 can fully open the second adjustment valve 42 during the heating operation, and the saturated vapor pressure temperature based on the detected pressure from the suction pressure sensor 152 and the first suction temperature sensor 161 during the cooling operation. The second adjustment valve 42 is caused to function as an expansion valve that adjusts the flow rate of the refrigerant in accordance with the degree of superheat based on the detected temperature from.

  The control device 120 adjusts the flow rate of the refrigerant from the bridge circuit 112 toward the refrigerant auxiliary evaporator 72 during the heating operation or the cooling operation by transmitting an instruction command to the refrigerant auxiliary evaporator adjusting valve 73.

  The control device 120 transmits an instruction command to the first switching valve 114 to block the refrigerant from the heat source side heat exchanger 20 to the receiver 71 by closing the first switching valve 114 during the heating operation. During the cooling operation, the first switching valve 114 is opened to allow the refrigerant to flow from the heat source side heat exchanger 20 toward the receiver 71. Here, the control device 120 can fully close the first adjustment valve 41 when opening the first switching valve 114 during the cooling operation.

  The control device 120 transmits an instruction command to the second switching valve 116 to open the second switching valve 116 during the heating operation or the cooling operation, from the bottom surface opening 82 a of the accumulator 82 toward the compressor 10. While circulating the refrigerant, the second switching valve 116 is closed to block the refrigerant from the bottom opening 82 a of the accumulator 82 to the compressor 10. Specifically, the control device 120 determines in advance the degree of superheat based on the saturated vapor pressure temperature based on the detected pressure from the suction pressure sensor 152 and the detected temperature from the second suction temperature sensor 162 during the heating operation or the cooling operation. When the value is equal to or greater than a predetermined value (first predetermined value), the second switching valve 116 is opened. When the degree of superheat falls below a predetermined value (first predetermined value), the second switching valve 116 is closed. To do.

  Next, the operation of the heating operation and the cooling operation by the heat pump 100 will be described with reference to FIGS.

(Heating operation)
FIG. 2 is a schematic block diagram of the heat pump 100 showing a heating operation state in which a heating operation is performed. In FIG. 2 and FIG. 3 to be described later, the thick line indicates the flow of the refrigerant.

  In the example shown in FIG. 2, in the heating operation, the control device 120 adjusts the opening of the first adjustment valve 41 and the refrigerant auxiliary evaporator adjustment valve 73, fully opens the second adjustment valve 42, and adjusts for the subcooling heat exchanger. The valve 92 is fully closed, the first switching valve 114 is closed, and the second switching valve 116 is opened.

  In the heat pump 100, when performing the heating operation, the control device 120 switches the four-way valve 111 to the first connection state so as to connect the first refrigerant path 113a and the eighth refrigerant path 113h and the third refrigerant path 113c and the second refrigerant path 113h. The refrigerant path 113b is communicated. By doing so, the refrigerant in the high-pressure gas state (hereinafter referred to as high-pressure gas refrigerant) discharged from the compressor 10 flows from the oil separator 81 in the first refrigerant path 113a to the four-way valve 111, the eighth refrigerant path 113h, and the other. It flows to the use side heat exchanger 50 via the communication pipe 110b.

  The temperature of the high-pressure gas refrigerant flowing to the refrigerant circuit 110 side of the use side heat exchanger 50 is higher than the temperature of the temperature adjustment target side (in this example, the indoor air side) of the use side heat exchanger 50. For this reason, heat moves from the high-pressure gas refrigerant to the temperature adjustment target side (in this example, the indoor air side). As a result, the high-pressure gas refrigerant loses heat of condensation and liquefies to become a high-pressure liquid refrigerant (hereinafter referred to as high-pressure liquid refrigerant). On the other hand, the temperature adjustment target side (in this example, the indoor air side) is heated by the heat radiation action of the refrigerant. That is, in the heating operation, the use-side heat exchanger 50 functions as a heater for a temperature adjustment target (in this example, indoor air) radiated by the high-pressure gas refrigerant.

  The high-pressure liquid refrigerant flows from the use side heat exchanger 50 to the second intermediate connection point P3 of the bridge circuit 112 via the second adjustment valve 42, the one connection pipe 110a, and the seventh refrigerant path 113g. Since the second intermediate connection point P3 is located on the inlet side of the third check valve 112c and on the outlet side of the fourth check valve 112d, the high-pressure liquid refrigerant is supplied from the first check valve 112a and the fourth check valve 112a. It does not flow toward the check valve 112d, and passes through the third check valve 112c and the outflow connection point P2 from the second intermediate connection point P3 to the receiver 71 and the sixth refrigerant route 113f from the fifth refrigerant path 113e. It flows to the inflow connection point P4 of the bridge circuit 112 via the cooling heat exchanger 91. The inflow connection point P4 is on the inflow side of the second check valve 112b and the fourth check valve 112d, but the high-pressure liquid refrigerant described above flows to the second intermediate connection point P3 and the outflow connection point P2 side. Therefore, the high-pressure liquid refrigerant does not flow toward the first check valve 112a and the fourth check valve 112d due to a pressure difference from the high-pressure liquid refrigerant flowing to the second intermediate connection point P3 and the outflow connection point P2. From the inflow connection point P4, the first check valve 41 passes through the second check valve 112b and the first intermediate connection point P1.

  In the first regulating valve 41, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant (hereinafter referred to as a low-pressure gas-liquid two-phase refrigerant), and the low-pressure gas-liquid two-phase refrigerant passes through the fourth refrigerant path 113d. To the heat source side heat exchanger 20.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing through the heat source side heat exchanger 20 is lower than the temperature of the air (specifically outside air) flowing through the heat source side heat exchanger 20. For this reason, heat moves from air (specifically, outside air) to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining evaporation heat, and becomes a refrigerant in a low-pressure gas state (hereinafter referred to as a low-pressure gas refrigerant). That is, in the heating operation, the heat source side heat exchanger 20 functions as a refrigerant evaporator that absorbs heat from the low-pressure gas-liquid two-phase refrigerant.

  Thereafter, the low-pressure gas refrigerant flows from the heat source side heat exchanger 20 to the third refrigerant path 113c. At this time, since the control device 120 communicates the third refrigerant path 113c and the second refrigerant path 113b by the four-way valve 111, the low-pressure gas refrigerant is supplied to the accumulator 82 and the second switching on the second refrigerant path 113b. The air is sucked into the compressor 10 via the valve 116.

  The high-pressure liquid refrigerant that has flowed from the sixth refrigerant path 113f to the ninth refrigerant path 113i passes through the refrigerant auxiliary evaporator adjustment valve 73.

  In the refrigerant auxiliary evaporator regulating valve 73, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant, and the low-pressure gas-liquid two-phase refrigerant flows to the refrigerant auxiliary evaporator 72.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing to the refrigerant circuit 110 side of the refrigerant auxiliary evaporator 72 is lower than the temperature of engine cooling water flowing to the engine cooling water circuit side (not shown) of the refrigerant auxiliary evaporator 72. For this reason, heat moves from the engine coolant to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining the evaporation heat, becomes a low-pressure gas refrigerant, and is sent to the tenth refrigerant path 113j. On the other hand, the engine coolant is cooled by the endothermic action of the refrigerant.

  Thereafter, in the heat pump 100, the above-described series of heating operation is repeated in the same manner.

  As described above, in the heat pump 100, by appropriately performing the heating operation, the temperature adjustment target (in this example, indoor air) can be appropriately heated by the use-side heat exchange unit 101 (in this example, the indoor unit).

(Cooling operation)
FIG. 3 is a schematic block diagram of the heat pump 100 showing a cooling operation state in which the cooling operation is performed.

  In the example shown in FIG. 3, in the cooling operation, the control device 120 fully closes the first adjustment valve 41 and opens the second adjustment valve 42, the refrigerant auxiliary evaporator adjustment valve 73, and the subcooling heat exchanger adjustment valve 92. The first switching valve 114 and the second switching valve 116 are opened.

  In the heat pump 100, when performing the cooling operation, the control device 120 switches the four-way valve 111 to the second connection state to communicate the first refrigerant path 113a and the third refrigerant path 113c, and the eighth refrigerant path 113h and the second refrigerant path. The refrigerant path 113b is communicated. By doing so, the high-pressure gas refrigerant discharged from the compressor 10 flows from the oil separator 81 in the first refrigerant path 113a to the heat source side heat exchanger 20 via the four-way valve 111 and the third refrigerant path 113c.

  The temperature of the high-pressure gas refrigerant flowing through the heat source side heat exchanger 20 is higher than the temperature of air (specifically, outside air) flowing through the heat source side heat exchanger 20. For this reason, heat moves from the high-pressure gas refrigerant to the air (specifically, outside air). As a result, the high pressure gas refrigerant loses heat of condensation and liquefies to become a high pressure liquid refrigerant. That is, in the cooling operation, the heat source side heat exchanger 20 functions as a refrigerant condenser that dissipates heat from the high-pressure gas refrigerant.

  The high-pressure liquid refrigerant passes through the fourth refrigerant path 113d from the heat source side heat exchanger 20, the first switching valve 114 in the eleventh refrigerant path 113k, the fifth refrigerant path 113e from the check valve 115, the receiver 71, and the sixth refrigerant path 113f. It flows to the inflow connection point P4 of the bridge circuit 112 via the supercooling heat exchanger 91. The inflow connection point P4 is on the inflow side of the second check valve 112b and the fourth check valve 112d, but the high-pressure liquid refrigerant described above flows to the outflow connection point P2 side. For this reason, the high-pressure liquid refrigerant does not flow toward the second check valve 112b and the third check valve 112c due to the pressure difference from the high-pressure liquid refrigerant flowing to the outflow connection point P2, and the fourth from the inflow connection point P4 to the fourth. It passes through the second regulating valve 42 via the check valve 112d, the second intermediate connection point P3, the seventh refrigerant path 113g, and the one connection pipe 110a.

  In the second adjustment valve 42, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant, and the low-pressure gas-liquid two-phase refrigerant flows to the use side heat exchanger 50.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing to the refrigerant circuit 110 side of the use side heat exchanger 50 is lower than the temperature of the temperature adjustment target side (in this example, the indoor air side) of the use side heat exchanger 50. For this reason, heat moves from the temperature adjustment target side (in this example, the indoor air side) to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining the evaporation heat, and becomes a low-pressure gas refrigerant. On the other hand, the temperature adjustment target side (in this example, the indoor air side) is cooled by the endothermic action of the refrigerant. That is, in the cooling operation, the second adjustment valve 42 functions as an expansion valve that expands the high-pressure liquid refrigerant to form a low-pressure gas-liquid two-phase refrigerant, and the use-side heat exchanger 50 absorbs the low-pressure gas-liquid two-phase refrigerant. It functions as a cooler for the temperature control target (in this example, indoor air).

  Thereafter, the low-pressure gas refrigerant flows from the use side heat exchanger 50 to the other communication pipe 110b and the eighth refrigerant path 113h. At this time, since the control device 120 communicates the eighth refrigerant path 113h and the second refrigerant path 113b by the four-way valve 111, the low-pressure gas refrigerant is supplied to the accumulator 82 and the second switching on the second refrigerant path 113b. The air is sucked into the compressor 10 via the valve 116.

  The high-pressure liquid refrigerant that has flowed from the sixth refrigerant path 113f to the ninth refrigerant path 113i passes through the refrigerant auxiliary evaporator adjustment valve 73.

  In the refrigerant auxiliary evaporator regulating valve 73, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant, and the low-pressure gas-liquid two-phase refrigerant flows to the refrigerant auxiliary evaporator 72.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing to the refrigerant circuit 110 side of the refrigerant auxiliary evaporator 72 is lower than the temperature of engine cooling water flowing to the engine cooling water circuit side (not shown) of the refrigerant auxiliary evaporator 72. For this reason, heat moves from the engine coolant to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining the evaporation heat, becomes a low-pressure gas refrigerant, and is sent to the tenth refrigerant path 113j. On the other hand, the engine coolant is cooled by the endothermic action of the refrigerant.

  The high-pressure liquid refrigerant that has flowed from the sixth refrigerant path 113f to the thirteenth refrigerant path 113m passes through the adjustment valve 92 for the supercooling heat exchanger.

  In the adjustment valve 92 for the supercooling heat exchanger, the high-pressure liquid refrigerant expands to become a low-pressure gas-liquid two-phase refrigerant, and the low-pressure gas-liquid two-phase refrigerant flows to the supercooling heat exchanger 91.

  The temperature of the low-pressure gas-liquid two-phase refrigerant flowing to the thirteenth refrigerant path 113m side of the supercooling heat exchanger 91 is lower than the temperature of the high-pressure liquid refrigerant flowing to the sixth refrigerant path 113f side of the supercooling heat exchanger 91. For this reason, heat moves from the high-pressure liquid refrigerant to the low-pressure gas-liquid two-phase refrigerant. As a result, the low-pressure gas-liquid two-phase refrigerant is vaporized by obtaining evaporation heat, becomes a low-pressure gas refrigerant, and is sent to the refrigerant path closer to the compressor 10 than the second switching valve 116 of the twelfth refrigerant path 113l. On the other hand, the high-pressure liquid refrigerant is cooled by the endothermic action of the refrigerant.

  Thereafter, in the heat pump 100, the above-described series of cooling operation is repeated in the same manner.

  As described above, in the heat pump 100, by appropriately performing the cooling operation, the temperature adjustment target (indoor air in this example) can be appropriately cooled by the use side heat exchange unit 101 (in this example, the indoor unit).

[Calculation configuration of heat pump]
Next, a configuration for calculating the heat pump output in the heat pump 100 will be described as the first embodiment, and a configuration for calculating the fuel gas consumption will be described as the second embodiment. A configuration for calculating the power consumption of an engine-driven heat pump will be described as a third embodiment.

<First Embodiment: Calculation of Heat Pump Output>
The control device 120 includes a first calculation unit and a second calculation unit. The first calculation unit calculates the mass flow rate of the refrigerant based on the suction pressure, the suction temperature, the compressor rotation speed, and the compressor constant. The suction pressure is a value detected by a suction pressure sensor 152 acting as suction pressure detection means. The suction temperature is a value detected by the second suction temperature sensor 162 that functions as suction temperature detection means. The compressor speed is a value detected by an engine speed sensor 170 that acts as a compressor speed detector. The compressor constant is a constant determined in advance for the compressor 10. The second calculation unit calculates the heat pump output (air conditioning output in this example) at the time of detection based on the ratio of the mass flow rate calculated by the first calculation unit to the mass flow rate of the refrigerant at the rated heat pump output and the rated heat pump output. calculate.

  Specifically, the heat pump output at the time of detection is Q, the rated heat pump output (heat pump output at the rated time) is Qr, the mass flow rate of the refrigerant at the rated heat pump output is Gr [kg / s], and the mass flow rate of the refrigerant at the time of detection is G. Assuming [kg / s], the following equation (1-1) is satisfied. Here, “rating” means an output under a predetermined condition.

  The rated heat pump output Qr is the rated output of the heat pump 100 as shown in the following formula (1-2), and its unit is [kW]. In this case, the rated heat pump output Qr means an output under a predetermined condition, and the heat pump output Q at the time of detection is the heat pump output [kW] at the time of detection.

  The refrigerant mass flow rate Gr at the rated heat pump output is a mass flow rate [kg / s] per unit time of the refrigerant at the rated time, and is a mass flow rate under a predetermined condition. For example, the mass flow rate Gr of the refrigerant at the time of rated heat pump output is a predetermined specified mass discharge amount Vr [kg / rotation] of the refrigerant discharged to the refrigerant circuit 110 when the compressor 10 rotates once, and the compressor It can be obtained by the following equation (1-3) obtained by multiplying the compressor rotation speed Nr [rotation speed / s] (rotation speed under a predetermined condition) which is a rated rotation speed of 10. .

The refrigerant mass flow rate G at the time of detection is the mass flow rate [kg / s] per unit time of the refrigerant at the time of detection. For example, the mass flow rate G of the refrigerant at the time of detection includes the density ρ [kg / m ³ ] of the refrigerant in the suction path of the compressor 10 and the volume discharge amount Vd of the refrigerant per rotation of the compressor 10 (of the compressor 10 Volume discharge amount) [m ³ / rotation] can be obtained by the following equation (1-4) obtained by multiplying the compressor rotation speed Ncomp [rotation speed / s], which is the rotation speed of the compressor 10.

  The compressor speed Ncomp can be detected by the engine speed sensor 170.

  Here, assuming that the refrigerant suction pressure in the suction path of the compressor 10 is Ps, the refrigerant gas constant is R, and the refrigerant suction temperature in the suction path of the compressor 10 is Ts, the refrigerant density ρ is the gas equation of state. From (Ps = ρ × R × Ts), it can be expressed by the following equation (1-5). When the pressure sensor detects pressure based on a pressure difference from atmospheric pressure, atmospheric pressure (101.325 kPa) is added to the detection result. The same applies to the discharge pressure Pd described later.

  The refrigerant suction pressure Ps in the suction path of the compressor 10 can be detected by the suction pressure sensor 152, and the refrigerant suction temperature Ts in the suction path of the compressor 10 can be detected by the second suction temperature sensor 162. it can.

  That is, the heat pump output Q at the time of detection can be obtained by only using detection results detected by the suction pressure sensor 152, the second suction temperature sensor 162, and the engine speed sensor 170 as detection information.

  FIG. 4 is a flowchart illustrating an example of a calculation operation of the heat pump output Q according to the first embodiment by the control device 120 in the heat pump 100.

  In the processing operation shown in FIG. 4, first, the control device 120 substitutes the prescribed mass discharge amount Vr of the compressor 10 and the rated compressor rotational speed Nr into the equation (1-3), and outputs the rated heat pump. The refrigerant mass flow rate Gr is calculated in advance (step S11).

  Next, the control device 120 detects the refrigerant suction pressure Ps in the suction path of the compressor 10 based on the detection result of the suction pressure sensor 152, and the refrigerant in the suction path of the compressor 10 based on the detection result of the second suction temperature sensor 162. Is detected, and the compressor speed Ncomp is detected from the detection result of the engine speed sensor 170 (step S12).

  Next, the control device 120 calculates the suction pressure Ps detected by the suction pressure sensor 152, the suction temperature Ts detected by the second suction temperature sensor 162, and the gas constant R of the refrigerant in Expression (1-5). Substituting and calculating the density ρ of the refrigerant (step S13).

  Next, the control device 120 calculates the density ρ of the obtained refrigerant, the volume discharge amount Vd of the compressor 10, and the compressor rotational speed Ncomp detected by the engine rotational speed sensor 170 in the formula (1-4). The refrigerant mass flow rate G at the time of detection is calculated by substitution (step S14).

  Then, the control device 120 obtains the mass flow rate G of the obtained refrigerant, the mass flow rate Gr of the refrigerant at the rated heat pump output calculated in advance, and the rated heat pump output Qr of the equation (1-2) by the equation ( By substituting into 1-1), the heat pump output Q at the time of detection can be obtained (step S15).

  Further, the control device 120 calculates the heat pump output Q at the time of detection by substituting the expression (1-5) into the expression (1-4) and the expressions (1-4) and ( 1-3) and Formula (1-2) may be substituted into Formula (1-1) and calculated using the following Formula (1-6).

  In addition, when the heat pump 100 has the several compressors 10-10, the value corresponding to each compressor 10 can be added.

  As described above, according to the heat pump 100 of the first embodiment, the suction pressure Ps detected by the suction pressure sensor 152, the suction temperature Ts detected by the second suction temperature sensor 162, and the engine speed sensor 170. The refrigerant mass flow rate G is calculated based on the detected compressor rotation speed Ncomp and the compressor constant of the compressor 10 (in this example, the volume discharge amount Vd of the compressor 10), and the rated heat pump output of the mass flow rate G is calculated. Since the heat pump output Q at the time of detection (air conditioning output in this example) is calculated based on the ratio of the refrigerant to the mass flow rate Gr of the hour and the rated heat pump output Qr, the heat pump output Q can be easily calculated. That is, the heat pump output Q (air conditioning output in this example) can be calculated based on information obtained by existing sensors (in this example, the suction pressure sensor 152, the second suction temperature sensor 162, and the engine speed sensor 170). it can.

  The first embodiment is not limited to the engine-driven heat pump 100 but can be applied to other heat pumps (for example, an electric motor-driven heat pump).

<Second Embodiment: Calculation of Fuel Gas Consumption>
The control device 120 includes a third calculation unit, a fourth calculation unit, and a fifth calculation unit. The third calculation unit calculates an engine torque that is a torque of the engine 60 based on the discharge pressure Pd and the suction pressure Ps. The discharge pressure Pd is a value detected by a discharge pressure sensor 151 that acts as a discharge pressure detecting means. The suction pressure Ps is a value detected by a suction pressure sensor 152 acting as suction pressure detection means. The fourth calculation unit calculates an engine output, which is an output of the engine 60, based on the engine torque calculated by the third calculation unit and the engine speed. The engine speed is a value detected by an engine speed sensor 170 acting as an engine speed detecting means. The fifth calculation unit calculates the fuel gas consumption of the engine 60 based on the engine output calculated by the fourth calculation unit and the engine efficiency.

  Specifically, assuming that the engine speed, which is the speed of the engine 60, is Neng [speed / s], the engine output is Peng [kW], and the engine torque is Tq [N · m], the following equation (2-1): It becomes.

  When engine 60 drives the generator, the torque of the generator is added to engine torque Tq.

  The engine speed Neng can be detected by the engine speed sensor 170.

  If the engine efficiency, which is the efficiency of the engine 60, is ηeng, the fuel gas consumption is Geng [kg / s], and the unit calorific value of the fuel gas is Gunit [J / kg], the following equation (2-2) It becomes. Here, the engine efficiency ηeng can be obtained as follows. That is, in an engine efficiency map in which engine efficiency ηeng is associated with the coordinate position of engine speed Neng and engine torque Tq (specifically, in a graph in which the horizontal axis is engine speed Neng and the vertical axis is engine torque Tq). The engine efficiency ηeng distribution) is stored in the storage unit 122 in advance. Thus, the engine efficiency ηeng can be obtained from the engine speed Neng and the engine torque Tq using the engine efficiency map. The engine efficiency map can be set in advance by experiments or the like. Further, the unit calorific value Unit of the fuel gas is a constant value determined based on the gas type.

  The engine torque Tq is a function f (Pd, Ps) [Tq = f (Pd, Ps)] having the discharge pressure Pd detected by the discharge pressure sensor 151 and the suction pressure Ps detected by the suction pressure sensor 152 as variables. Can be calculated.

  That is, the fuel gas consumption Geng at the time of detection can be obtained by using only the detection results detected by the suction pressure sensor 152, the discharge pressure sensor 151, and the engine speed sensor 170 as detection information.

  FIG. 5 is a flowchart illustrating an example of a calculation operation of the fuel gas consumption Geng according to the second embodiment by the control device 120 in the heat pump 100.

  In the processing operation shown in FIG. 5, first, the control device 120 detects the refrigerant suction pressure Ps in the suction path of the compressor 10 based on the detection result of the suction pressure sensor 152, and the compressor 10 based on the detection result of the discharge pressure sensor 151. The discharge pressure Pd of the refrigerant in the discharge path is detected, and the engine speed Neng is detected from the detection result of the engine speed sensor 170 (step S21).

  Next, the control device 120 calculates the engine torque Tq based on the suction pressure Ps detected by the suction pressure sensor 152 and the discharge pressure Pd detected by the discharge pressure sensor 151 (step S22). When engine 60 drives the generator, the torque of the generator is added to engine torque Tq.

  Next, the controller 120 calculates the engine output Peng by substituting the obtained engine torque Tq and the engine speed Neng detected by the engine speed sensor 170 into the equation (2-1) (step S23). ).

  Then, the control device 120 can obtain the fuel gas consumption Geng by substituting the obtained engine output Peng and the engine efficiency ηeng into the equation (2-2) (step S24).

  As described above, according to the heat pump 100 of the second embodiment, the engine torque Tq is calculated based on the discharge pressure Pd detected by the discharge pressure sensor 151 and the suction pressure Ps detected by the suction pressure sensor 152. For example, when the engine 60 drives the generator, the torque of the generator is added to the engine torque Tq and based on the engine torque Tq and the engine speed Neng detected by the engine speed sensor 170. Then, the engine output Peng is calculated, and the fuel gas consumption Geng of the engine 60 is calculated based on the engine output Peng and the engine efficiency ηeng. Therefore, the fuel gas consumption Geng can be easily calculated. That is, the fuel gas consumption Geng can be calculated based on information obtained by existing sensors (in this example, the discharge pressure sensor 151, the suction pressure sensor 152, and the engine speed sensor 170).

<Third Embodiment: Calculation of Power Consumption of Engine Driven Heat Pump>
By the way, in the engine-driven heat pump 100, when the heat source side heat exchanger fan 30 for the heat source side heat exchanger 20 is provided as in the present embodiment, the heat source side heat exchanger fan is usually provided. 30. Most of the power consumption of the heat source side heat exchanger fan 30 in the electrical equipment such as the use side heat exchange unit 101 and a cooling water pump (not shown) accounts for the majority.

  From this point of view, in the engine-driven heat pump 100 according to the third embodiment, the control device 120 includes a sixth calculation unit. The sixth arithmetic unit is configured to calculate the fan speed Nf [rotations / s] and the correlation between the set speed Ns [rotations / s] and the set power consumption Us [kW]. A power consumption Uf [kW] of 30 is calculated. The fan rotation speed Nf is a value detected by a fan rotation speed sensor 180 that functions as a fan rotation speed detection means. The set rotation speed Ns is a preset rotation speed of the heat source side heat exchanger fan 30. The set power consumption Us is a preset set power consumption of the heat source side heat exchanger fan 30. In this example, a conversion table TB representing the correlation between the set rotation speed Ns and the set power consumption Us is stored in the storage unit 122 in advance.

  FIG. 6 is a chart showing a conversion table TB representing the correlation between the set rotational speed Ns of the heat source side heat exchanger fan 30 and the set power consumption Us.

  As shown in FIG. 6, in the conversion table TB, the set power consumption Us (1) to Us (n) correspond to the set rotational speeds Ns (1) to Ns (n) (n is an integer equal to or greater than 1), respectively. It is associated. Note that the set rotational speeds Ns (1) to Ns (n) and the corresponding set power consumption Us (1) to Us (n) can be set in advance by experiments or the like.

  The control device 120 can calculate the power consumption Uf of the heat source side heat exchanger fan 30 by linear interpolation (linear interpolation) from the fan rotation speed Nf using the conversion table TB shown in FIG.

  That is, as shown in FIG. 6, the linear interpolation has two points (Ns (i), Us (i)), (Ns (i + 1), Us (i + 1)) (i is an integer of 1 to n-1). When it is known, a linear function f (Nf) of Nf obtained by connecting an approximate value of the power consumption Uf with respect to the fan speed Nf at an arbitrary point of Ns (i) ≦ Nf ≦ Ns (i + 1) by a straight line of two points. Ask.

  The equation for linear interpolation is the following equation (3-1).

  FIG. 7 is a flowchart illustrating an example of a calculation operation of the power consumption Uf of the heat source side heat exchanger fan 30 according to the third embodiment by the control device 120 in the heat pump 100.

  In the processing operation shown in FIG. 7, first, the control device 120 detects the fan rotation speed Nf based on the detection result of the fan rotation speed sensor 180 (step S31).

  And the control apparatus 120 can obtain the power consumption Uh by substituting the fan rotation speed Nf detected by the fan rotation speed sensor 180 into the equation (3-1) based on the conversion table TB (step S32).

  In this example, the power consumption Uf is calculated from the fan rotation speed Nf using the conversion table TB. However, the power consumption Uf may be calculated from the fan rotation speed Nf using a predetermined conversion formula.

  As described above, according to the heat pump 100 of the third embodiment, the power consumption of the heat source side heat exchanger fan 30 based on the fan rotation speed Nf and the correlation between the set rotation speed Ns and the set power consumption Us. By calculating Uf, the ratio of the power consumption Uf of the heat source side heat exchanger fan 30 to the power consumption of the heat source side heat exchanger 30 is usually the majority of the power consumption in the electrical equipment. The approximate value of the power consumption Uh of the engine-driven heat pump 100 can be easily calculated. For example, the approximate value of the power consumption Uh of the engine-driven heat pump 100 is the power consumption of electrical equipment other than the heat-source-side heat exchanger fan 30 such as the use-side heat exchange unit 101 or a cooling water pump (not shown). It can be obtained by adding to the power consumption Uf of the heat source side heat exchanger fan 30 as a predetermined fixed value.

<Fourth Embodiment: Combination of First to Third Embodiments>
The heat pump 100 of the fourth embodiment may be configured by combining at least two of the first to third embodiments.

  The present invention is not limited to the embodiment described above, and can be implemented in various other forms. Therefore, such an embodiment is merely an example in all respects and should not be interpreted in a limited manner. The scope of the present invention is shown by the scope of claims, and is not restricted by the text of the specification. Further, all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

DESCRIPTION OF SYMBOLS 10 Compressor 11 Clutch 20 Heat source side heat exchanger 30 Heat source side heat exchanger fan 40 Adjustment valve (an example of an expansion valve)
41 First adjustment valve 42 Second adjustment valve 50 Use side heat exchanger 51 Refrigerant path 60 Engine 71 Receiver 71a Refrigerant inlet 71b Refrigerant outlet 72 Refrigerant auxiliary evaporator 73 Refrigerant auxiliary evaporator adjustment valve 81 Oil separator 82 Accumulator 91 Excess Cooling heat exchanger 92 Supercooling heat exchanger regulating valve 100 Heat pump 101 User side heat exchange unit 102 Heat source side heat exchange unit 110 Refrigerant circuit 110a One communication pipe 110b Other communication pipe 111 Four-way valve 112 Bridge circuit 113a First refrigerant path 113b Second refrigerant path 113b1 Merge path 113c Third refrigerant path 113d Fourth refrigerant path 113e Fifth refrigerant path 113f Sixth refrigerant path 113g Seventh refrigerant path 113h Eighth refrigerant path 113i Nth refrigerant path 113j Tenth refrigerant path 113k 11th refrigerant path 113l 12th Medium path 113m thirteenth refrigerant passage 114 first switching valve 115 check valve 116 and the second switching valve 120 control device 121 processor 122 memory 151 discharge pressure sensor (an example of a discharge pressure detection means)
152 Suction pressure sensor (an example of suction pressure detection means)
161 First suction temperature sensor 162 Second suction temperature sensor (an example of suction temperature detection means)
163 Third suction temperature sensor 170 Engine speed sensor (an example of compressor speed detector)
170 Engine speed sensor (an example of engine speed detection means)
180 fan rotation speed sensor (an example of fan rotation speed detection means)
G Refrigerant mass flow rate Geng Fuel gas consumption amount Gr Refrigerant mass flow rate Gunit Unit heat value Ncomp Compressor speed Neng Engine speed Nf Fan speed Nr Rated compressor speed Ns Setting Rotational speed Pd Refrigerant discharge pressure Peng Engine output Ps Refrigerant intake pressure Q Heat pump output Qr Rated heat pump output R Refrigerant gas constant TB Conversion table Tq Engine torque Ts Refrigerant intake temperature Uf Power consumption of heat source side heat exchanger fan Uh Heat pump Power consumption Us Set power consumption Vd Volume discharge amount of compressor Vr Specified mass discharge amount of compressor ηeng Engine efficiency ρ Density of refrigerant

Claims (3)

A heat pump provided with a compressor, a heat source side heat exchanger, an expansion valve and a use side heat exchanger,
A suction pressure detecting means for detecting a suction pressure of the refrigerant in the suction path of the compressor; a suction temperature detecting means for detecting a suction temperature of the refrigerant in the suction path of the compressor; and a compressor which is the rotational speed of the compressor. A compressor rotation number detecting means for detecting the rotation number;
The suction pressure detected by the suction pressure detection means, the suction temperature detected by the suction temperature detection means, the compressor rotation speed detected by the compressor rotation speed detection means, and the compressor in advance Calculate the mass flow rate of the refrigerant based on the compressor constant which is a fixed constant,
A heat pump characterized by calculating a heat pump output at the time of detection based on a ratio of the mass flow rate to the mass flow rate of the refrigerant at the rated heat pump output and the rated heat pump output. An engine-driven heat pump provided with an engine, a compressor driven by the engine, a heat source side heat exchanger, an expansion valve and a use side heat exchanger,
Discharge pressure detection means for detecting the discharge pressure of refrigerant in the discharge path of the compressor, suction pressure detection means for detecting the suction pressure of refrigerant in the suction path of the compressor, and engine speed that is the engine speed An engine speed detecting means for detecting
Based on the discharge pressure detected by the discharge pressure detection means and the suction pressure detected by the suction pressure detection means, an engine torque that is the torque of the engine is calculated,
An engine output that is an output of the engine is calculated based on the engine torque and the engine speed detected by the engine speed detecting means,
An engine-driven heat pump characterized in that a fuel gas consumption amount of the engine is calculated based on the engine output and engine efficiency. The heat pump according to claim 1 or 2,
A heat-source-side heat exchanger fan for the heat-source-side heat exchanger, and fan rotation speed detection means for detecting a fan rotation speed that is the rotation speed of the heat source-side heat exchanger fan,
Based on the fan rotational speed detected by the fan rotational speed detection means, and a correlation between a predetermined set rotational speed of the fan rotational speed fan and a predetermined set power consumption of the heat source side heat exchanger fan. And calculating the power consumption of the heat source side heat exchanger fan.

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