JP2019105409A - Heat pump cycle - Google Patents

Abstract

To provide a heat pump cycle that can sufficiently recover and use exhaust heat of a compressor.SOLUTION: An exhaust heat recovery part 41 is provided for recovering exhaust heat of a compressor 11 of a heat pump cycle 10 by the refrigerant piping wound around the outer periphery of the compressor 11. Further, in a heating mode of performing heating while using a high-temperature and high-pressure refrigerant discharged from the compressor 11 as a heat source, a low-pressure refrigerant, which is reduced in pressure by an expansion valve 15 for heat absorption and becomes a gas-liquid two-phase state, is caused to flow into the exhaust heat recovery part 41, and the refrigerant flowing out from the exhaust heat recovery part 41 is sucked into the compressor 11. With this, the heat transfer coefficient in the exhaust heat recovery part 41 is improved, a temperature difference between the refrigerant and the compressor 11 is increased, and exhaust heat of the compressor 11 is sufficiently recovered and used as a heat source for heating.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a heat pump cycle.

  BACKGROUND ART Conventionally, Patent Document 1 discloses a heat pump cycle applied to a vehicle air conditioner. In the heat pump cycle of Patent Document 1, when frost is generated on the outdoor heat exchanger which causes the refrigerant to evaporate by heat exchange between the refrigerant and the outside air, the frost is melted using the exhaust heat of the compressor as a heat source to perform outdoor heat Defrosting of the exchanger is performed.

  More specifically, the heat pump cycle of Patent Document 1 includes an exhaust heat recovery unit configured by winding a refrigerant pipe around a housing of a compressor. Then, when frost formation occurs on the outdoor heat exchanger, the liquid-phase refrigerant condensed in the indoor condenser is made to flow into the exhaust heat recovery unit and reheated by the exhaust heat of the compressor. Furthermore, the outdoor heat exchanger is defrosted by causing the reheated refrigerant to flow into the outdoor heat exchanger.

JP 2008-241127 A

  However, in the configuration in which the liquid-phase refrigerant condensed by the indoor condenser flows into the exhaust heat recovery unit as in the heat pump cycle of Patent Document 1, the refrigerant can not sufficiently absorb the exhaust heat of the compressor. In other words, in the heat pump cycle of Patent Document 1, the exhaust heat of the compressor can not be sufficiently recovered and used.

  The reason is that the heat transfer coefficient of the liquid-phase refrigerant is lower than that of the gas-liquid two-phase refrigerant, so the amount of heat absorption of the refrigerant decreases until the liquid-phase refrigerant flowing into the exhaust heat recovery portion starts to boil It is from. Furthermore, since the temperature difference between the liquid phase refrigerant condensed by the indoor condenser and the housing of the compressor is relatively small, the heat absorption amount of the refrigerant is reduced.

  An object of the present invention is to provide a heat pump cycle which can be used by sufficiently recovering the exhaust heat of a compressor.

  In order to achieve the above object, the invention according to claim 1 comprises a compressor (11) which compresses and discharges a refrigerant, and an exhaust heat recovery part (41) which absorbs the exhaust heat of the compressor by the refrigerant. It is a heat pump cycle which is equipped with the refrigerant | coolant which flows in into an exhaust heat recovery part in the gas-liquid two phase state.

  According to this, since the refrigerant flowing into the exhaust heat recovery unit (41) is in a gas-liquid two-phase state, the refrigerant has a high heat transfer coefficient immediately after flowing into the exhaust heat recovery unit (41). The exhaust heat of the compressor can be absorbed. Therefore, the exhaust heat of the compressor (11) can be sufficiently recovered and used.

  Furthermore, a decompression unit (15) for decompressing the high-pressure refrigerant boosted by the compressor may be provided, and the refrigerant flowing into the exhaust heat recovery unit may be the refrigerant decompressed by the decompression unit.

  According to this, since the refrigerant decompressed by the pressure reducing section (15) is made to flow into the exhaust heat recovery section (41), the temperature of the refrigerant and the compressor (11) which has flowed into the exhaust heat recovery section (41) The difference can be magnified. Therefore, the heat absorption amount of the refrigerant can be increased, and the exhaust heat of the compressor (11) can be recovered more sufficiently.

  In addition, the code | symbol in the parenthesis of each means described by this column and the claim is an example which shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole block diagram of the heat pump cycle of 1st Embodiment. It is an explanatory view for explaining a compressor and exhaust heat recovery part of a 1st embodiment. It is a typical axial direction perpendicular | vertical cross section of the compressor and exhaust heat recovery part of 1st Embodiment. It is a block diagram which shows the electric control part of the heat pump cycle of 1st Embodiment. It is a flowchart which shows a part of control flow of the heat pump cycle of 1st Embodiment. It is a whole block diagram of the heat pump cycle of 2nd Embodiment. It is a flowchart which shows a part of control flow of the heat pump cycle of 2nd Embodiment. It is an explanatory view for explaining a compressor and a waste heat recovery part of a 3rd embodiment. It is an explanatory view for explaining a compressor and an exhaust heat recovery part of a 4th embodiment.

First Embodiment
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the heat pump cycle 10 according to the present invention is applied to an electric vehicle which obtains driving power for traveling from an electric motor. The heat pump cycle 10 performs the function of air conditioning the passenger compartment in the electric vehicle.

  The heat pump cycle 10 is a vapor compression refrigeration cycle device. The heat pump cycle 10 can switch the refrigerant circuit in accordance with the operation mode for air conditioning. The operation mode for air conditioning includes a cooling mode, a dehumidifying heating mode, and a heating mode.

  The cooling mode is an operation mode in which the blowing air blown into the vehicle compartment, which is a space to be air-conditioned, is cooled and blown out into the vehicle compartment. The dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blown air is reheated and blown into the vehicle compartment. The heating mode is an operation mode in which the blown air is heated and blown into the vehicle compartment.

  The heat pump cycle 10 constitutes a subcritical refrigeration cycle in which the high pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. In the heat pump cycle 10, an HFC refrigerant (specifically, R134a) is employed as the refrigerant. Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. A portion of the refrigeration oil circulates in the cycle with the refrigerant.

  The compressor 11 sucks, compresses and discharges the refrigerant in the heat pump cycle 10. The compressor 11 is disposed in a vehicle bonnet. The compressor 11 is an electric compressor configured by housing a fixed displacement type compression mechanism whose discharge displacement is fixed, an electric motor for driving the compression mechanism, and the like in a housing 11a forming the outer shell thereof. is there.

  As this compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be adopted. Further, as the electric motor, any form of an alternating current motor and a direct current motor may be adopted. The rotation speed of the electric motor is controlled by a control signal output from a control device 60 described later. And the refrigerant | coolant discharge capability of the compressor 11 is controlled by this rotation speed control.

  The housing 11a is formed of an iron-based metal. As shown in FIG. 2, the housing 11 a is formed in a bottomed cylindrical shape extending in the rotation axis direction of the electric motor. Here, when the compressor 11 is operated, the temperature of the entire compressor 11 rises due to the temperature rise of the refrigerant due to the compression work of the compression mechanism and the temperature rise of the electric motor due to Joule heat. Furthermore, part of the heat of the compressor 11 whose temperature has been raised is dissipated from the housing 11a to the outside as exhaust heat.

  So, in this embodiment, the exhaust heat recovery part 41 which absorbs the exhaust heat of the compressor 11 to a refrigerant | coolant is arrange | positioned on the outer periphery of the housing 11a. The exhaust heat recovery unit 41 has a refrigerant pipe wound so as to be in thermal contact with the outer periphery of the housing 11a. In other words, the exhaust heat recovery unit 41 has a refrigerant pipe as a heat exchange unit for exhaust heat recovery that exchanges heat between the refrigerant flowing inside and the compressor.

  Therefore, when the refrigerant is caused to flow through the exhaust heat recovery part 41 at the time of operation of the compressor 11, the refrigerant can absorb the exhaust heat of the compressor 11.

  Further, the compressor 11 is attached with a heat storage unit 42 for storing exhaust heat of the compressor 11. As shown in FIG. 3, the heat storage unit 42 is arranged to cover the outer peripheral side of the housing 11 a and the exhaust heat recovery unit 41. The heat storage portion 42 is formed of a resin into which the heat storage material 42 a is kneaded.

  More specifically, the heat storage material 42a is kneaded in the deformable resin in a state of being enclosed in a plurality of spherical resin or metal capsules. Therefore, the heat storage portion 42 can be freely deformed so as to conform to the outer peripheral shape of the housing 11 a and the outer peripheral shape of the exhaust heat recovery portion 41.

  The heat storage material 42a is a latent heat storage material accompanied by a phase change at the time of heat storage. In the present embodiment, the heat storage temperature at which the heat storage material 42 a changes phase and stores heat is set to 35 ° C. or more and 60 ° C. or less.

  As such a heat storage material 42a, a paraffin wax-based heat storage material (specifically, C22 docosan, C24 tetracosan, C26 hexacosan), a higher alcohol heat storage material (specifically, Caprylone, Camphene), an inorganic salt A heat storage material of a system (specifically, sodium phosphate dibasic dodecahydrate, sodium thiosulfate pentahydrate) or the like, or a mixed material thereof can be adopted.

  The outlet side of the compressor 11 is connected to the inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12. The water-refrigerant heat exchanger 12 has a refrigerant passage for circulating the high pressure refrigerant discharged from the compressor 11 and a water passage for circulating the high temperature side heat medium circulating in the high temperature side heat medium circuit 20. The water-refrigerant heat exchanger 12 is a heat exchanger for heating which heats the high temperature side heat medium by heat exchange between the high pressure refrigerant flowing in the refrigerant passage and the high temperature side heat medium flowing in the water passage. is there. Details of the high temperature side heat medium circuit 20 will be described later.

  The refrigerant inlet side of the branch portion 13 a is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12. The branch part 13a branches the flow of the high pressure refrigerant which flowed out of the refrigerant passage of the water-refrigerant heat exchanger 12. The branch portion 13a is a three-way joint structure having three refrigerant inlets and outlets communicating with each other, one of the three inlets and outlets being a refrigerant inlet and the remaining two being a refrigerant outlet.

  The refrigerant | coolant inlet side of the indoor evaporator 16 is connected to one refrigerant | coolant outflow port of the branch part 13a via the expansion valve 14 for cooling. The inlet side of the refrigerant passage of the chiller 17 is connected to the other refrigerant outlet of the branch portion 13 a via the heat absorption expansion valve 15.

  The cooling expansion valve 14 is a cooling decompression portion that decompresses the refrigerant that has flowed out from one refrigerant outlet of the branching portion 13a at least in the cooling mode. Furthermore, the cooling expansion valve 14 is a cooling flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the indoor evaporator 16 connected downstream.

  The cooling expansion valve 14 is configured by including a valve body configured to be able to change the throttle opening degree, and an electric actuator (specifically, a stepping motor) that changes the opening degree of the valve body. Is a variable stop mechanism of the formula. The operation of the cooling expansion valve 14 is controlled by a control signal (specifically, control pulse) output from the control device 60.

  Further, the cooling expansion valve 14 has a fully closing function of closing the refrigerant passage by fully closing the valve opening degree. With this fully closed function, the cooling expansion valve 14 can switch between the refrigerant circuit that causes the refrigerant to flow into the indoor evaporator 16 and the refrigerant circuit that does not cause the refrigerant to flow into the indoor evaporator 16. That is, the cooling expansion valve 14 also has a function as a circuit switching unit that switches the refrigerant circuit.

  The indoor evaporator 16 is a heat exchanger that exchanges heat between the low pressure refrigerant decompressed by the cooling expansion valve 14 and the blowing air. The indoor evaporator 16 is a heat exchanger for cooling which evaporates the low-pressure refrigerant and cools the blowing air at least in the cooling mode. The indoor evaporator 16 is disposed in the casing 51 of the indoor air conditioning unit 50. Details of the indoor air conditioning unit 50 will be described later.

  The inlet side of the evaporation pressure control valve 18 is connected to the refrigerant outlet of the indoor evaporator 16. The evaporation pressure adjustment valve 18 is an evaporation pressure adjustment unit that maintains the refrigerant evaporation pressure in the indoor evaporator 16 at or above a predetermined reference pressure. The evaporation pressure control valve 18 is configured by a mechanical variable throttle mechanism that increases the valve opening degree as the refrigerant pressure on the outlet side of the indoor evaporator 16 increases.

  In the present embodiment, as the evaporation pressure adjusting valve 18, the refrigerant evaporation temperature in the indoor evaporator 16 is maintained at or above the frost formation suppression reference temperature (1.degree. C. in the present embodiment) that can suppress frost formation in the indoor evaporator 16. We adopt what we do.

  One refrigerant inlet side of the merging portion 13 b is connected to the outlet of the evaporation pressure adjusting valve 18. The merging portion 13 b merges the flow of the refrigerant flowing out of the evaporation pressure adjusting valve 18 and the flow of the refrigerant flowing out of the chiller 17. The merging portion 13b has a three-way joint structure similar to that of the branching portion 13a, in which two of the three inlets and outlets are used as a refrigerant inlet and the remaining one is used as a refrigerant outlet. The suction port side of the compressor 11 is connected to the refrigerant outlet of the merging portion 13b.

  The heat absorption expansion valve 15 is a heat absorption decompression unit that decompresses the refrigerant that has flowed out from the other refrigerant outlet of the branch unit 13a at least in the heating mode. That is, it is a pressure reducing unit that reduces the pressure of the high pressure refrigerant pressurized by the compressor 11. Furthermore, the heat absorption expansion valve 15 is a heat absorption flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the refrigerant passage of the chiller 17 connected downstream.

  The basic configuration of the heat absorption expansion valve 15 is the same as that of the cooling expansion valve 14. Therefore, the heat absorption expansion valve 15 is an electric variable throttle mechanism having a fully closed function. Furthermore, the heat absorption expansion valve 15 can switch between the refrigerant circuit that causes the refrigerant to flow into the refrigerant passage of the chiller 17 and the refrigerant circuit that prevents the refrigerant from flowing into the refrigerant passage of the chiller 17. That is, the heat absorption expansion valve 15 also has a function as a circuit switching unit, similarly to the cooling expansion valve 14.

  The chiller 17 has a refrigerant passage for circulating the low pressure refrigerant decompressed by the heat absorption expansion valve 15 and a water passage for circulating the low temperature side heat medium circulating in the low temperature side heat medium circuit 30. The chiller 17 exchanges heat between the low-pressure refrigerant flowing in the refrigerant passage and the low-temperature side heat medium flowing in the water passage at least in the heating mode to evaporate the low-pressure refrigerant to exhibit heat absorption. It is a heat exchanger. The other refrigerant inlet side of the merging portion 13 b is connected to the outlet of the refrigerant passage of the chiller 17. Details of the low temperature side heat medium circuit 30 will be described later.

  Further, in the heat pump cycle 10, at least a part of the refrigerant flowing out of the heat absorption expansion valve 15 is caused to flow into the exhaust heat recovery unit 41, and the refrigerant flowing out of the exhaust heat recovery unit 41 is made from the refrigerant outlet of the heat absorption expansion valve 15. An exhaust heat recovery passage 45 leading to a refrigerant flow path leading to the suction port of the compressor 11 is connected.

  More specifically, the inlet of the exhaust heat recovery passage 45 is connected between the outlet of the heat absorption expansion valve 15 and the refrigerant inlet of the chiller 17. The outlet portion of the exhaust heat recovery passage 45 is connected between the refrigerant outlet of the merging portion 13 b and the suction port of the compressor 11. In other words, the exhaust heat recovery passage 45 diverts the low pressure refrigerant decompressed by the heat absorption expansion valve 15 around the chiller 17 and causes it to flow into the exhaust heat recovery unit 41 and the refrigerant flowing out of the exhaust heat recovery unit 41 Are introduced to the suction port side of the compressor 11.

  Further, an open / close valve 45 a for opening and closing the exhaust heat recovery passage 45 is disposed in the exhaust heat recovery passage 45. The on-off valve 45 a is an electromagnetic valve that opens and closes by the control voltage output from the control device 60. The on-off valve 45a is a so-called normally closed electromagnetic valve that opens the exhaust heat recovery passage 45 when it is energized. The on-off valve 45 a is a flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing through the exhaust heat recovery passage 45.

  Next, the high temperature side heat medium circuit 20 will be described. The high temperature side heat medium circuit 20 is a circuit for circulating the high temperature side heat medium. As the high temperature side heat medium, a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted. In the high temperature side heat medium circuit 20, the water passage of the water-refrigerant heat exchanger 12, the high temperature side heat medium pump 21, the heater core 22, the high temperature side radiator 23, the high temperature side flow rate adjustment valve 24 and the like are arranged.

  The high temperature side heat medium pump 21 is a water pump that pumps the high temperature side heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12. The high temperature side heat medium pump 21 is an electric pump whose rotational speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.

  One inlet / outlet of the high temperature side flow control valve 24 is connected to the outlet of the water passage of the water-refrigerant heat exchanger 12. The high temperature side flow control valve 24 is an electrical three-way flow control valve having three inlets and outlets, of which the passage area ratio of the two inlets and outlets can be continuously adjusted. The operation of the high temperature side flow control valve 24 is controlled by a control signal output from the controller 60.

  The heat medium inlet side of the heater core 22 is connected to another inflow / outlet of the high temperature side flow control valve 24. The heat medium inlet side of the high temperature side radiator 23 is connected to still another inflow / outlet of the high temperature side flow control valve 24.

  The high-stage flow rate adjustment valve 24 controls the flow rate of the high-temperature side heat medium to be flowed into the heater core 22 among the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 in the high-temperature side heat medium circuit 20. And the function of continuously adjusting the flow ratio of the high temperature side heat medium flowing into the high temperature side radiator 23.

  The heater core 22 is a heat exchanger that heats the blown air by heat exchange between the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 16. The heater core 22 is disposed in the casing 51 of the indoor air conditioning unit 50. The inlet side of the high temperature side heat medium pump 21 is connected to the heat medium outlet of the heater core 22.

  The high temperature side radiator 23 exchanges heat between the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the outside air blown from the outside air fan (not shown) to radiate the heat of the high temperature side heat medium to the outside air Heat exchanger.

  The high temperature side radiator 23 is disposed on the front side in the vehicle bonnet. For this reason, when the vehicle is traveling, the traveling wind can be applied to the high temperature side radiator 23. The high temperature side radiator 23 may be integrally formed with the water-refrigerant heat exchanger 12 and the like. The inlet side of the high temperature side heat medium pump 21 is connected to the heat medium outlet of the high temperature side radiator 23.

  Therefore, in the high temperature side heat medium circuit 20, the high temperature side flow rate adjustment valve 24 adjusts the flow rate of the high temperature side heat medium flowing into the heater core 22, so that the heat radiation amount of the high temperature side heat medium in the heater core 22 to the blast air. That is, the heating amount of the blowing air in the heater core 22 can be adjusted.

  That is, in the present embodiment, the components constituting the water-refrigerant heat exchanger 12 and the high temperature side heat medium circuit 20 constitute a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. .

  Next, the low temperature side heat medium circuit 30 will be described. The low temperature side heat medium circuit 30 is a heat medium circulation circuit that circulates the low temperature side heat medium. As the low temperature side heat medium, the same fluid as the high temperature side heat medium can be adopted. In the low temperature side heat medium circuit 30, the water passage of the chiller 17, the low temperature side heat medium pump 31, the low temperature side radiator 33, the low temperature side flow rate adjustment valve 34 and the like are arranged.

  Furthermore, a cooling water passage of the battery 32 is connected to the low temperature side heat medium circuit 30. The battery 32 supplies power to various electric devices mounted on the vehicle. The battery 32 is a chargeable / dischargeable secondary battery (in the embodiment, a lithium ion battery). This type of battery 32 involves heat generation during charging and discharging. Therefore, the cooling water passage of the battery 32 is formed so as to be able to cool the entire battery 32 by circulating the low temperature side heat medium.

  In addition, when the battery 32 is at a low temperature, the chemical reaction does not proceed easily, and the battery 32 can not exhibit sufficient performance in charge and discharge. On the other hand, when the temperature becomes high, the deterioration tends to progress. Therefore, the temperature of the battery 32 needs to be adjusted within the range of a proper temperature range (for example, 10 ° C. or more and 40 ° C. or less) that can exhibit sufficient performance.

  The low temperature side heat medium pump 31 is a water pump that pumps the low temperature side heat medium to the inlet side of the water passage of the chiller 17. The basic configuration of the low temperature side heat medium pump 31 is similar to that of the high temperature side heat medium pump 21. The heat medium inlet side of the low temperature side radiator 33 is connected to the outlet side of the water passage of the chiller 17. The low temperature side radiator 33 is a heat exchanger that exchanges heat between the low temperature side heat medium flowing out of the heat accumulator 32 and the outside air blown from an outside air fan (not shown).

  The low temperature side radiator 33 functions as a heat exchanger for radiating the heat of the low temperature side heat medium to the outside air when the temperature of the low temperature side heat medium is higher than the outside air. Further, when the temperature of the low temperature side heat medium is lower than the outside air, it functions as a heat exchanger for heat absorption which absorbs the heat of the outside air to the low temperature side heat medium.

  Further, a bypass passage 35 is provided in the low temperature side heat medium circuit 30. The bypass passage 35 is a passage for guiding the low temperature side heat medium flowing out of the water passage of the chiller 17 to the suction port side of the low temperature side heat medium pump 31 by bypassing the low temperature side radiator 33. The coolant passage of the battery 32 is connected to the bypass passage 35.

  The low temperature side flow control valve 34 is disposed at the outlet of the bypass passage 35. The basic configuration of the low temperature side flow control valve 34 is similar to that of the high temperature side flow control valve 24. The low temperature side flow control valve 34 is a flow control valve that adjusts the flow rate of the low temperature side heat medium flowing in the bypass passage 35 in the low temperature side heat medium circuit 30.

  Therefore, in the low temperature side heat medium circuit 30, the low temperature side flow rate adjustment valve 34 adjusts the flow rate of the low temperature side heat medium flowing through the bypass passage 35 (that is, the cooling water passage of the battery 32). Can be adjusted.

  Next, the indoor air conditioning unit 50 will be described. The indoor air conditioning unit 50 forms an air passage for blowing out the blowing air whose temperature has been adjusted by the heat pump cycle 10 to an appropriate place in the vehicle compartment in the heat pump cycle 10. The indoor air conditioning unit 50 is disposed in the passenger compartment and inside the instrument panel (i.e., instrument panel) at the front of the passenger compartment.

  The indoor air conditioning unit 50 accommodates the blower 52, the indoor evaporator 16, the heater core 22 and the like in an air passage formed inside a casing 51 forming an outer shell thereof.

  The casing 51 forms an air passage for blowing air blown into the vehicle compartment, and is molded of a resin (specifically, polypropylene) which has a certain degree of elasticity and is excellent in strength. An internal / external air switching device 53 is disposed on the most upstream side of the blowing air flow of the casing 51. The inside / outside air switching device 53 switches and introduces inside air (air in the vehicle interior) and outside air (air outside the vehicle) into the casing 51.

  The inside / outside air switching device 53 continuously adjusts the opening area of the inside air introduction port for introducing inside air into the casing 51 and the outside air introduction port for introducing outside air by means of the inside / outside air switching door. The introduction rate with the introduction air volume can be changed. The inside and outside air switching door is driven by an electric actuator for the inside and outside air switching door. The operation of the electric actuator is controlled by a control signal output from the controller 60.

  A blower 52 is disposed downstream of the inside / outside air switching device 53 in the flow of the blown air. The blower 52 has a function of blowing the air taken in via the inside / outside air switching device 53 toward the vehicle interior and blowing it. The blower 52 is an electric blower that drives a centrifugal multiblade fan by an electric motor. The rotation speed (i.e., the blowing capacity) of the blower 52 is controlled by the control voltage output from the control device 60.

  The indoor evaporator 16 and the heater core 22 are disposed in this order with respect to the flow of the air, on the downstream side of the air flow of the fan 52. That is, the indoor evaporator 16 is disposed upstream of the heater core 22 in the flow of the blown air. Further, in the casing 51, a cold air bypass passage 55 is formed, in which the blown air having passed through the indoor evaporator 16 is allowed to bypass the heater core 22 and flow downstream.

  An air mix door 54 is disposed on the downstream side of the air flow of the indoor evaporator 16 and on the upstream side of the air flow of the heater core 22. The air mix door 54 adjusts the air volume ratio of the air volume passing through the heater core 22 and the air volume passing through the cold air bypass passage 55 in the blown air after passing through the indoor evaporator 16.

  The air mix door 54 is driven by an electric actuator for driving the air mix door. The operation of the electric actuator is controlled by a control signal output from the controller 60.

  On the downstream side of the air flow of the heater core 22, there is provided a mixing space 56 for mixing the air heated by the heater core 22 and the air not passing through the cold air bypass passage 55 and not heated by the heater core 22. There is. Further, at the most downstream portion of the air flow of the casing 51, an opening for blowing out the air (air-conditioned air) mixed in the mixing space 56 into the vehicle compartment is disposed.

  As this opening hole, a face opening hole, a foot opening hole, and a defroster opening hole (all not shown) are provided. The face opening hole is an opening hole for blowing the conditioned air toward the upper body of the occupant in the vehicle compartment. The foot opening hole is an opening hole for blowing the conditioned air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing the conditioned air toward the inner side surface of the vehicle front windshield.

  These face opening holes, foot opening holes, and defroster opening holes are respectively provided in the vehicle compartment via a duct that forms an air passage, face outlet, foot outlet, and defroster outlet (all not shown) )It is connected to the.

  Therefore, the temperature of the conditioned air mixed in the mixing space 56 is adjusted by adjusting the air volume ratio between the air volume that allows the air mix door 54 to pass the heater core 22 and the air volume that causes the cold air bypass passage 55 to pass. As a result, the temperature of the air (air-conditioned air) blown out from the outlets into the vehicle compartment is also adjusted.

  In addition, a face door for adjusting the opening area of the face opening hole, a foot door for adjusting the opening area of the foot opening hole, and a defroster opening on the upstream side of the air flow of the face opening hole, the foot opening hole and the defroster opening hole. A defroster door (not shown) is arranged to adjust the opening area of the hole.

  These face door, foot door, and defroster door constitute an air outlet mode switching device that switches the air outlet from which the conditioned air is blown out. The face door, the foot door, and the defroster door are connected to an electric actuator for driving the air outlet mode door via a link mechanism and the like, and are operated to rotate in conjunction with each other. The operation of the electric actuator is controlled by a control signal output from the controller 60.

  Next, an outline of the electric control unit of the present embodiment will be described using the block diagram of FIG. 4. The control device 60 is composed of a known microcomputer including a CPU, a ROM, a RAM and the like, and peripheral circuits thereof. Then, various calculations and processing are performed based on the air conditioning control program stored in the ROM, and various control target devices 11, 14, 15, 21, 24, 31, 34, 45a, 52 connected to the output side Control the operation of

  Further, as shown in FIG. 4, on the input side of the control device 60, an inside air temperature sensor 62a, an outside air temperature sensor 62b, a solar radiation sensor 62c, a high pressure sensor 62d, an evaporator temperature sensor 62e, an air conditioning air temperature sensor 62f, a battery temperature A sensor group for control such as the sensor 62g is connected. The control device 60 receives detection signals of these sensor groups.

  The inside air temperature sensor 62a is an inside air temperature detection unit that detects a vehicle room temperature (inside air temperature) Tr. The outside air temperature sensor 62b is an outside air temperature detection unit that detects the temperature outside the vehicle (outside air temperature) Tam. The solar radiation sensor 62c is a solar radiation amount detection unit that detects the solar radiation amount As emitted to the vehicle interior. The high pressure sensor 62 d is a refrigerant pressure detection unit that detects the high pressure refrigerant pressure Pd of the refrigerant flow path from the discharge port side of the compressor 11 to the inlet side of the cooling expansion valve 14 or the heat absorption expansion valve 15.

  The evaporator temperature sensor 62 e is an evaporator temperature detection unit that detects a refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 16. The air conditioning air temperature sensor 62f is an air conditioning air temperature detection unit that detects the temperature of the air that is blown into the vehicle compartment from the mixing space 56.

  The battery temperature sensor 62 g is a battery temperature detection unit that detects the temperature Tb of the battery 32. The battery temperature sensor 62 g has a plurality of temperature sensors, and detects the temperatures of a plurality of locations of the battery 32. Therefore, in the control device 60, an average value of detection values of a plurality of temperature sensors is adopted as the temperature Tb of the battery 32.

  Furthermore, as shown in FIG. 5, an operation panel 61 disposed near the instrument panel in the front of the vehicle compartment is connected to the input side of the control device 60, and various operation switches provided on the operation panel 61 are connected. An operation signal is input.

  Specifically, the various operation switches provided on the operation panel 61 include an air conditioning operation switch, an air volume setting switch, a temperature setting switch, and the like. The air conditioning operation switch is an air conditioning operation request unit for requesting the occupant to perform air conditioning in the vehicle compartment. The air volume setting switch is an air volume setting unit for the passenger to manually set the air volume of the blower 52. The temperature setting switch is a temperature setting unit for setting a set temperature of the vehicle interior.

  Note that the control device 60 of the present embodiment is integrally configured with a control unit that controls various control target devices connected to the output side, but the configuration for controlling the operation of each control target device ( Hardware and software) constitute a control unit that controls the operation of each control target device.

  For example, in the control device 60, the configuration for controlling the operation of the compressor 11 constitutes a compressor control unit 60a. Moreover, the structure which controls the action | operation of the on-off valve 45a comprises the on-off valve control part 60b. Of course, each control unit such as the compressor control unit 60a and the on-off valve control unit 60b may be configured separately.

  Next, the operation of the heat pump cycle 10 of the present embodiment having the above configuration will be described. As described above, the heat pump cycle 10 of the present embodiment can switch the refrigerant circuit in accordance with the operation mode for air conditioning. The operation mode for air conditioning is determined by executing an air conditioning control program stored in advance in the control device 60.

  The air conditioning control program is executed when the air conditioning operation switch of the operation panel 61 is turned on (ON) while the vehicle system is activated. In the air conditioning control program, the target blowout temperature TAO of the air blown into the vehicle compartment is calculated based on the detection signal detected by the control sensor group and the operation signal output from the operation panel 61.

The target blowing temperature TAO is calculated by the following formula F1.
TAO = Kset × Tset−Kr × Tr × Kam × Tam−Ks × As + C (F1)
Tset is a set temperature set by the temperature setting switch. Tr is the inside air temperature detected by the inside air temperature sensor 62a. Tam is the outside air temperature detected by the outside air temperature sensor 62b. As is the amount of solar radiation detected by the solar radiation sensor 62c. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

  Then, in the air conditioning control program, the operation mode is switched based on the target blowout temperature TAO, the detection signal, and the operation signal. Furthermore, in the control device 60 of the present embodiment, the operation of the on-off valve 45a is controlled by executing the control routine shown in FIG. The control routine shown in FIG. 5 is executed at predetermined intervals as a subroutine of the main routine of the air conditioning control program.

  In the control routine shown in FIG. 5, when the operation mode is switched to the heating mode in the main routine in step S51, the process proceeds to step S52, the on-off valve 45a is opened, and the process returns to the main routine. On the other hand, when the operation mode is not switched to the heating mode in step S51, the process proceeds to step S53, the on-off valve 45a is closed, and the process returns to the main routine. The operation of each operation mode will be described below.

(A) Cooling Mode In the cooling mode, the control device 60 brings the cooling expansion valve 14 into the throttling state to exert the refrigerant pressure reducing action, and brings the heat absorption expansion valve 15 into the fully closed state. Furthermore, in the cooling mode, as shown in step S53 of FIG. 5, the control device 60 closes the on-off valve 45a.

  Thereby, in the heat pump cycle 10 in the cooling mode, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → cooling expansion valve 14 → indoor evaporator 16 → evaporation pressure adjusting valve 18 → merging portion 13b A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the suction port of the compressor 11 is configured. Then, in this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side.

  For example, the control device 60 determines the control signal output to the compressor 11 such that the refrigerant evaporation temperature Tefin detected by the evaporator temperature sensor 62e becomes the target evaporation temperature TEO. The target evaporation temperature TEO is determined based on the target blowing temperature TAO with reference to the control map for cooling mode stored in advance in the control device 60.

  Specifically, in this control map, the target evaporation temperature TEO is raised along with the rise of the target blowout temperature TAO so that the blown air temperature TAV detected by the air conditioning air temperature sensor 62f approaches the target blowout temperature TAO. Furthermore, the target evaporation temperature TEO is determined to be a value in a range (specifically, 1 ° C. or more) in which frost formation of the indoor evaporator 16 can be suppressed.

  Further, the control device 60 controls the output to the cooling expansion valve 14 so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 approaches a predetermined reference degree of superheat (3 ° C. in this embodiment). Determine the signal.

  Further, the control device 60 operates the high temperature side heat medium pump 21 so as to exert the pressure feeding capability in the predetermined cooling mode. Furthermore, the control device 60 outputs a control signal to the high temperature side flow control valve 24 so that the total flow rate of the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23 Decide.

  Further, the control device 60 determines the control voltage to be output to the blower 52 with reference to the control map stored in advance in the control device 60 based on the target blowing temperature TAO. Specifically, in this control map, the air flow of the blower 52 is maximized in the cryogenic temperature range (maximum cooling area) and the extremely high temperature area (maximum heating area) of the target blowout temperature TAO, and as the intermediate temperature range is approached. Reduce air flow.

  Further, the control device 60 determines a control signal to be output to the electric actuator for driving the air mix door so that the cold air bypass passage 55 is fully opened and the air passage on the heater core 22 side is closed. Further, the control device 60 appropriately determines control signals and the like to be output to the other various control target devices.

  Then, the control device 60 outputs the control signal or the like determined as described above to various control target devices. Thereafter, reading of the detection signal and the operation signal described above → calculation of the target blowout temperature TAO → control signals to be output to various control target devices and the like every predetermined control cycle until a stop of air conditioning in the vehicle compartment is requested. A control routine such as determination → output of control signal etc. is repeated. The repetition of such a control routine is similarly performed in other operation modes.

  Therefore, in the heat pump cycle 10 in the cooling mode, the high pressure refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12. In the water-refrigerant heat exchanger 12, since the high temperature side heat medium pump 21 is operating, the high pressure refrigerant and the high temperature side heat medium exchange heat, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated. Be done.

  In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23 through the high temperature side flow rate adjustment valve 24. The high temperature side heat medium flowing into the high temperature side radiator 23 exchanges heat with the outside air and radiates heat. Thereby, the high temperature side heat medium is cooled. The high temperature side heat medium cooled by the high temperature side radiator 23 is drawn into the high temperature side heat medium pump 21 and is pressure-fed again to the water passage of the water-refrigerant heat exchanger 12.

  The high pressure refrigerant cooled in the refrigerant passage of the water-refrigerant heat exchanger 12 flows into the cooling expansion valve 14 via the branch portion 13a and is decompressed. At this time, the throttle opening degree of the cooling expansion valve 14 is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 approaches the reference degree of superheat.

  The low pressure refrigerant that has been reduced in pressure by the cooling expansion valve 14 to be in a gas-liquid two-phase state flows into the indoor evaporator 16. The refrigerant flowing into the indoor evaporator 16 absorbs heat from the air blown from the fan 52 and evaporates. Thereby, the blowing air is cooled, and the blowing air temperature TAV approaches the target blowing temperature TAO. The refrigerant that has flowed out of the indoor evaporator 16 is sucked into the compressor 11 via the evaporation pressure adjusting valve 18 and the merging portion 13 b and compressed again.

  Therefore, in the cooling mode, the blowing air cooled by the indoor evaporator 16 can be blown into the vehicle compartment to perform cooling of the vehicle compartment.

  Here, the cooling mode is an operation mode that is executed when the outside air temperature Tam is relatively high (for example, when the outside air temperature is 25 ° C. or higher). For this reason, there is a possibility that the temperature of the battery 32 may rise more than a proper temperature zone by self-heating.

  Therefore, when the temperature Tb of the battery 32 detected by the battery temperature sensor 62g is equal to or higher than a predetermined reference battery temperature, the control device 60 exerts the predetermined pressure feeding capability so that the low temperature side thermal conductivity is obtained. The medium pump 31 is operated. Furthermore, the controller 60 controls the operation of the low temperature side flow control valve 34 so that the temperature Tb of the battery 32 is maintained in a proper temperature range.

  Such temperature control of the electric device by the control device 60 is not limited to the cooling mode, and is also performed as needed in the dehumidifying and heating mode and the heating mode. Furthermore, as long as the entire vehicle system is activated, it is executed as needed, regardless of whether air conditioning in the passenger compartment is being performed (that is, regardless of whether the air conditioning control program is being executed). Ru.

(B) Dehumidifying and heating mode In the dehumidifying and heating mode, the control device 60 sets the cooling expansion valve 14 in the throttling state, and sets the heat absorption expansion valve 15 in the throttling state. Furthermore, in the dehumidifying and heating mode, as shown in step S53 of FIG. 5, the control device 60 closes the on-off valve 45a.

  Thereby, in the heat pump cycle 10 in the dehumidifying heating mode, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → cooling expansion valve 14 → interior evaporator 16 → evaporation pressure adjusting valve 18 → merging portion The refrigerant circulates in the order of 13b → the suction port of the compressor 11, and the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the branch portion 13a → the heat absorption expansion valve 15 → the chiller 17 → the merging portion 13b → compression A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the suction port of the machine 11 is configured.

  That is, in the dehumidifying and heating mode, the indoor evaporator 16 and the chiller 17 are switched to the refrigerant circuits connected in parallel. Then, in this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side.

  For example, the control device 60 determines a control signal to be output to the compressor 11 such that the high pressure refrigerant pressure Pd detected by the high pressure sensor 62d becomes the target high pressure PCO. The target high pressure PCO is determined based on the target blowout temperature TAO with reference to the control map for the dehumidifying and heating mode stored in advance in the control device 60.

  Specifically, in this control map, the target high pressure PCO is raised with the rise of the target blowing temperature TAO so that the blowing air temperature TAV approaches the target blowing temperature TAO.

  Further, the control device 60 refers to the control map for the dehumidifying and heating mode stored in advance in the control device 60 based on the target blowout temperature TAO and the outside air temperature Tam, and outputs a control signal to the cooling expansion valve 14 And a control signal to be output to the heat absorption expansion valve 15.

  Specifically, in this control map, the throttle opening degree of the heat absorption expansion valve 15 is determined such that the refrigerant evaporation temperature in the chiller 17 is at least a temperature lower than the outside air temperature Tam. Further, the throttle opening degree of the cooling expansion valve 14 is determined in a range which is larger than the throttle opening degree of the heat absorption expansion valve 15.

  Further, the control device 60 operates the high temperature side heat medium pump 21 so as to exert the pressure feeding capability in the predetermined dehumidifying and heating mode. Further, the controller 60 determines the control signal output to the high temperature side flow control valve 24 so that the total flow rate of the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 flows into the heater core 22. Do.

  Further, the control device 60 operates the low temperature side heat medium pump 31 so as to exert the pressure feeding capability in the predetermined dehumidifying and heating mode.

  Further, the control device 60 determines the control voltage to be output to the blower 52, as in the cooling mode. Further, the control device 60 determines a control signal to be output to the electric actuator for driving the air mix door so as to completely open the air passage on the heater core 22 side and close the cold air bypass passage 55. Further, the control device 60 appropriately determines control signals and the like to be output to the other various control target devices.

  Accordingly, in the heat pump cycle 10 in the dehumidifying and heating mode, the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12. In the water-refrigerant heat exchanger 12, since the high temperature side heat medium pump 21 is operating, the high pressure refrigerant and the high temperature side heat medium exchange heat, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated. Be done.

  In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 22 via the high temperature side flow rate adjustment valve 24. The high temperature side heat medium having flowed into the heater core 22 exchanges heat with the air that has passed through the indoor evaporator 16 and radiates heat since the air mix door 54 fully opens the air passage on the heater core 22 side. Thereby, the blowing air which passed indoor evaporator 16 is heated, and the temperature of blowing air approaches target blowing temperature TAO.

  The high temperature side heat medium flowing out of the heater core 22 is drawn into the high temperature side heat medium pump 21 and is pressure-fed again to the water passage of the water-refrigerant heat exchanger 12.

  The high pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is branched at the branch portion 13a. One of the refrigerants branched by the branch portion 13a flows into the cooling expansion valve 14 and is decompressed. The low pressure refrigerant that has been reduced in pressure by the cooling expansion valve 14 to be in a gas-liquid two-phase state flows into the indoor evaporator 16. The refrigerant flowing into the indoor evaporator 16 absorbs heat from the air blown from the fan 52 and evaporates. Thereby, the blast air is cooled and dehumidified.

  Under the present circumstances, the refrigerant | coolant evaporation temperature in the indoor evaporator 16 is maintained by 1 degreeC or more by the effect | action of the evaporation pressure control valve 18, irrespective of the refrigerant | coolant discharge capacity of the compressor 11. FIG. Therefore, frosting does not occur in the indoor evaporator 16. The refrigerant | coolant which flowed out out of the indoor evaporator 16 flows in into one refrigerant | coolant flow inlet of the confluence | merging part 13b via the evaporation pressure control valve 18. As shown in FIG.

  The other refrigerant branched at the branch portion 13a flows into the heat absorption expansion valve 15 and is decompressed. At this time, the throttle opening degree of the heat absorption expansion valve 15 is adjusted so that the refrigerant evaporation temperature in the chiller 17 is at least a temperature lower than the outside temperature Tam. The low pressure refrigerant that has been reduced in pressure by the heat absorption expansion valve 15 to be in a gas-liquid two-phase state flows into the chiller 17. The refrigerant flowing into the chiller 17 absorbs heat from the low temperature side heat medium and evaporates.

  In the low temperature side heat medium circuit 30, the low temperature side heat medium cooled by the chiller 17 flows into the low temperature side radiator 33. In the low temperature side radiator 33, the low temperature side heat medium absorbs heat from the outside air. Thereby, the temperature of the low temperature side heat medium approaches the outside air temperature Tam. The low temperature side heat medium flowing out of the low temperature side radiator 33 is drawn into the low temperature side heat medium pump 31 and is pressure-fed again to the water passage side of the chiller 17.

  The refrigerant flowing out of the chiller 17 flows into the other refrigerant inlet of the merging portion 13b, and merges with the refrigerant flowing out of the evaporation pressure adjusting valve 18. The refrigerant flowing out of the junction 13b is sucked into the compressor and compressed again.

  Therefore, in the dehumidifying and heating mode, the dehumidified heating of the vehicle interior can be performed by reheating the blown air cooled and dehumidified by the indoor evaporator 16 by the heater core 22 and blowing it out into the vehicle interior.

(C) Heating Mode In the heating mode, the control device 60 brings the cooling expansion valve 14 into a fully closed state, and brings the heat absorption expansion valve 15 into a throttling state. Furthermore, in the heating mode, as shown in step S52 of FIG. 5, the control device 60 opens the on-off valve 45a.

  Thereby, in the heat pump cycle 10 in the heating mode, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → expansion valve for heat absorption → chiller 17 → joining portion 13b → intake port of the compressor 11 While the refrigerant circulates in order, a vapor compression type refrigeration cycle in which the refrigerant circulates in the order of the heat absorption expansion valve 15 → the exhaust heat recovery unit 41 → the suction port of the compressor 11 is configured.

  Here, the flow ratio of the flow rate of the refrigerant flowing from the heat absorption expansion valve 15 into the chiller 17 to the flow rate of the refrigerant flowing from the heat absorption expansion valve 15 into the exhaust heat recovery unit 41 It is determined by the flow characteristics of the recovery passage 45 and the exhaust heat recovery unit 41.

  In the present embodiment, the sum of the heat absorption amount that the low pressure refrigerant absorbs heat from the low temperature side heat medium in the chiller 17 and the heat absorption amount that the low pressure refrigerant absorbs the exhaust heat of the compressor 11 in the exhaust heat recovery unit 41 is maximum. The flow characteristics of the refrigerant passage of the chiller 17, the exhaust heat recovery passage 45, the refrigerant piping of the exhaust heat recovery unit 41, and the like are set so as to approach values.

  More specifically, even if the entire flow rate of the fluid flowing out of the heat absorption expansion valve 15 is made to flow into the exhaust heat recovery unit 41, the refrigerant is discharged from the exhaust heat recovery unit 41 due to restrictions such as the size of the exhaust heat recovery unit 41. There is a limit to the amount of exhaust heat recovered from the compressor 11.

  Therefore, in the present embodiment, the refrigerant passage of the chiller 17, the exhaust heat recovery passage 45, and the refrigerant piping of the exhaust heat recovery unit 41 so that the refrigerant can efficiently absorb heat in both the chiller 17 and the exhaust heat recovery unit 41. The flow characteristics such as are set. Specifically, the flow rate of the refrigerant flowing from the heat absorption expansion valve 15 into the chiller 17 is set to be larger than the flow rate of the refrigerant flowing from the heat absorption expansion valve 15 into the exhaust heat recovery unit 41.

  Then, in this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side.

  For example, the control device 60 determines a control signal to be output to the compressor 11 as in the dehumidifying and heating mode. Further, the control device 60 refers to the control map for the heating mode stored in advance in the control device 60 based on the target blowout temperature TAO and the outside air temperature Tam, and outputs the control signal output to the heat absorption expansion valve 15 decide. Specifically, in this control map, the refrigerant evaporation temperature in the chiller 17 is determined to be at least equal to or lower than the outside air temperature Tam.

  Further, the control device 60 operates the high temperature side heat medium pump 21 so as to exert the pressure feeding capability in the predetermined heating mode. Furthermore, the controller 60 sends the high temperature side flow control valve 24 to the high temperature side flow control valve 24 so that the total flow rate of the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 flows into the heater core 22 as in the dehumidifying and heating mode. Determine the control signal to be output.

  Further, the control device 60 operates the low temperature side heat medium pump 31 so as to exert a pressure feeding capability in the predetermined heating mode.

  Further, the control device 60 determines the control voltage to be output to the blower 52, as in the cooling mode and the dehumidifying and heating mode. Further, similarly to the dehumidifying and heating mode, the control device 60 determines a control signal to be output to the electric actuator for driving the air mix door so as to fully open the air passage on the heater core 22 side and close the cold air bypass passage 55. . Further, the control device 60 appropriately determines control signals and the like to be output to the other various control target devices.

  Therefore, in the heat pump cycle 10 in the heating mode, the high pressure refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12. In the water-refrigerant heat exchanger 12, since the high temperature side heat medium pump 21 is operating, the high pressure refrigerant and the high temperature side heat medium exchange heat, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated. Be done.

  In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 22 via the high temperature side flow rate adjustment valve 24. The high temperature side heat medium having flowed into the heater core 22 exchanges heat with the air that has passed through the indoor evaporator 16 and radiates heat since the air mix door 54 fully opens the air passage on the heater core 22 side. As a result, the blowing air is heated, and the blowing air temperature TAV approaches the target blowing temperature TAO.

  The high temperature side heat medium flowing out of the heater core 22 is drawn into the high temperature side heat medium pump 21 and is pressure-fed again to the water passage of the water-refrigerant heat exchanger 12.

  The high pressure refrigerant that has flowed out of the refrigerant passage of the water-refrigerant heat exchanger 12 flows into the heat absorption expansion valve 15 via the branch portion 13a and is decompressed. At this time, the throttle opening degree of the heat absorption expansion valve 15 is adjusted so that the refrigerant evaporation temperature in the chiller 17 becomes lower than the outside temperature Tam.

  Part of the low pressure refrigerant that has been reduced in pressure by the heat absorption expansion valve 15 to be in a gas-liquid two-phase state flows into the exhaust heat recovery unit 41 via the exhaust heat recovery passage 45. Then, when flowing through the exhaust heat recovery section 41, the low pressure refrigerant in the gas-liquid two-phase state absorbs the exhaust heat of the compressor 11 and evaporates. At this time, the low-pressure refrigerant not only absorbs the exhaust heat directly from the compressor 11, but also absorbs the exhaust heat stored in the heat storage section 42.

  Further, the remaining low-pressure refrigerant that has been reduced in pressure by the heat absorption expansion valve 15 to be in a gas-liquid two-phase state flows into the chiller 17. The refrigerant flowing into the chiller 17 absorbs heat from the low temperature side heat medium and evaporates, as in the dehumidifying and heating mode.

  In the low temperature side heat medium circuit 30, the low temperature side heat medium cooled by the chiller 17 flows into the low temperature side radiator 33 as in the dehumidifying and heating mode. In the low temperature side radiator 33, the low temperature side heat medium absorbs heat from the outside air. Thereby, the temperature of the low temperature side heat medium approaches the outside air temperature Tam. The low temperature side heat medium flowing out of the low temperature side radiator 33 is drawn into the low temperature side heat medium pump 31 and is pressure-fed again to the water passage side of the chiller 17.

  The refrigerant flowing out of the chiller 17 merges with the refrigerant flowing out of the exhaust heat recovery unit 41. As a result, the temperature of the refrigerant flowing out of the chiller 17 rises. The joined refrigerants whose temperature has risen are drawn into the compressor 11 and compressed again.

  Therefore, in the heating mode, the blowing air heated by the heater core 22 can be blown into the passenger compartment to heat the passenger compartment.

  As described above, according to the heat pump cycle 10 of the present embodiment, by switching the refrigerant circuit, the heat pump cycle 10 can switch the cooling mode, the dehumidifying heating mode, and the heating mode, and realize comfortable air conditioning of the vehicle interior. be able to.

  Here, as in the present embodiment, in the heat pump cycle 10 in which the refrigerant circuit is switched according to the operation mode, the cycle configuration tends to be complicated.

  On the other hand, in the heat pump cycle 10 of the present embodiment, there is no switching between the refrigerant circuit that causes the high pressure refrigerant to flow into the same heat exchanger and the refrigerant circuit that causes the low pressure refrigerant to flow. That is, since it is not necessary to flow the high-pressure refrigerant into the indoor evaporator 16 and the outdoor heat exchanger 19 even if switching to any refrigerant circuit, switching the refrigerant circuit with a simple configuration without causing complication of the cycle configuration it can.

  Further, in the heat pump cycle 10 of the present embodiment, the control device 60 controls the low temperature side heat medium pump 31 and the low temperature side flow rate adjustment valve 34 regardless of the operation mode for air conditioning as long as the entire vehicle system is activated. The operation can be controlled. Thereby, the temperature of the battery 32 can be maintained in the appropriate temperature range.

Furthermore, in the heat pump cycle 10 of the present embodiment, the exhaust heat recovery section 41 can sufficiently recover the exhaust heat of the compressor 11 in the heating mode. Explaining this in detail, the heat absorption amount Q in the exhaust heat recovery part 41 can be expressed by the following formula F2.
Q = h × Ar × ΔT (F2)
Here, h is a heat transfer coefficient, Ar is a heat transfer area, and ΔT is a temperature difference between the temperature of the refrigerant flowing through the exhaust heat recovery unit 41 and the temperature of the compressor 11.

  Here, as the heat transfer coefficient h of the equation F2, the convective heat transfer coefficient is used when the refrigerant is in the liquid phase, and the boiling heat transfer is performed when the refrigerant is in the gas-liquid two phase state. The rate is used. The boiling heat transfer coefficient is larger than the convective heat transfer coefficient.

  On the other hand, in the heat pump cycle 10 of the present embodiment, since the refrigerant flowing into the exhaust heat recovery unit 41 in the heating mode is in the gas-liquid two-phase state, immediately after the refrigerant flows into the exhaust heat recovery unit 41 The refrigerant can absorb the exhaust heat of the compressor at a high heat transfer rate h. Therefore, the exhaust heat of the compressor 11 can be recovered efficiently.

  Furthermore, in the heat pump cycle 10 of the present embodiment, since the refrigerant decompressed by the heat absorption expansion valve 15 is made to flow into the exhaust heat recovery unit 41 in the heating mode, for example, high pressure refrigerant on the upstream side of the heat absorption expansion valve 15 The temperature difference ΔT can be expanded relative to the case of flowing into the exhaust heat recovery unit 41. Therefore, the heat absorption amount Q of the refrigerant can be increased.

  Therefore, according to the heat pump cycle 10 of the present embodiment, the exhaust heat of the compressor 11 can be sufficiently recovered in the exhaust heat recovery unit 41.

  Further, according to the heat pump cycle 10 of the present embodiment, the exhaust heat recovery passage 45 is connected so as to lead the refrigerant flowing out from the exhaust heat recovery unit 41 to the suction port side of the compressor 11. The temperature of the refrigerant drawn into the chamber 11 can be raised to surely raise the temperature of the refrigerant discharged from the compressor 11. Therefore, the exhaust heat of the compressor 11 recovered by the exhaust heat recovery unit 41 can be effectively used as a heating heat source.

  Furthermore, since the on-off valve 45a as the flow rate adjustment unit is disposed in the exhaust heat recovery passage 45, the exhaust heat of the compressor 11 recovered by the exhaust heat recovery unit 41 is effectively used as necessary. be able to.

  In addition to this, in the heat pump cycle 10 of the present embodiment, since the refrigerant reduced in pressure by the heat absorption expansion valve 15 is made to flow in the exhaust heat recovery passage 45, the refrigerant pressure on the inlet side of the exhaust heat recovery passage 45 There is almost no pressure difference with the refrigerant pressure on the outlet side. Therefore, there is no need to provide a check valve or the like for inhibiting the refrigerant from flowing backward in the exhaust heat recovery passage 45. That is, it is hard to cause complication of a cycle.

  Further, according to the heat pump cycle 10 of the present embodiment, since the heat storage unit 42 is provided, even if the temperature of the compressor 11 is increased as in the initial stage of startup of the compressor 11, the heat is stored in the heat storage unit 42. The exhaust heat of the compressor 11 can be recovered by the refrigerant. Furthermore, since the heat insulating material is disposed on the outer peripheral side of the heat storage portion 42, the exhaust heat of the compressor 11 stored in the heat storage portion 42 can be stored for a long time.

Second Embodiment
In the present embodiment, as shown in FIG. 6, an example in which a part of the configuration of the heat pump cycle 10 is modified with respect to the first embodiment will be described. In FIG. 6, the same or equivalent parts as in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  Specifically, in the present embodiment, the low temperature side heat medium circuit 30 is eliminated. For this reason, in the heat pump cycle 10, the chiller 17 is eliminated. The refrigerant inlet side of the outdoor heat exchanger 19 is connected to the other refrigerant outlet of the branch portion 13 a of the heat pump cycle 10 via the heat absorption expansion valve 15.

  The outdoor heat exchanger 19 exchanges heat between the refrigerant depressurized by the heat absorption expansion valve 15 and the outside air blown from an outside air fan (not shown) at least in the heating mode, and is depressurized by the heat absorption expansion valve 15 It is an evaporation unit that evaporates the refrigerant. The outdoor heat exchanger 19 is disposed on the front side in the vehicle bonnet. Therefore, when the vehicle is traveling, the outdoor heat exchanger 19 can be subjected to traveling air. The outdoor heat exchanger 19 may be integrally formed with the high temperature side radiator 23 or the like.

  Further, the exhaust heat recovery passage 45 of the present embodiment causes at least a part of the refrigerant flowing out of the heat absorption expansion valve 15 to flow into the exhaust heat recovery unit 41 and the refrigerant flowing out of the exhaust heat recovery unit 41 in the pressure reduction unit. It is connected so as to lead to a refrigerant flow path from a refrigerant outlet of a certain heat absorption expansion valve 15 to a refrigerant inlet of the outdoor heat exchanger 19. The other configuration of the heat pump cycle 10 is the same as that of the first embodiment.

  Next, the operation of the heat pump cycle 10 of the present embodiment having the above configuration will be described. The basic operation of the heat pump cycle 10 of the present embodiment is the same as that of the first embodiment. Therefore, the heat pump cycle 10 of the present embodiment also switches the refrigerant circuit in accordance with the operation mode for air conditioning, as in the first embodiment.

  Furthermore, in the control device 60 of the present embodiment, the operation of the on-off valve 45a is controlled by executing the control routine shown in FIG. The control routine shown in FIG. 7 is executed at predetermined intervals as a subroutine of the main routine of the air conditioning control program.

  In the control routine shown in FIG. 7, when it is determined in step S71 that the predetermined frost forming condition is satisfied, the process proceeds to step S72. In step S72, the mode is switched to the defrosting mode in which the on-off valve 45a is opened, and the process returns to the main routine. On the other hand, when it is not determined in step S71 that the frost forming condition is satisfied, the process proceeds to step S73. In step S73, the mode is switched to the normal operation mode in which the on-off valve 45a is closed, and the process returns to the main routine.

  Therefore, the control step S71 of the present embodiment is a frost formation determination unit that determines that frost formation has occurred on the outdoor heat exchanger 19 when a predetermined frost formation condition is satisfied. Furthermore, in the present embodiment, as the frost formation condition, the fact that the heat release amount Qr in the heater core 22 is equal to or less than a predetermined reference heat release amount KQr is adopted.

  The amount of heat released from the heater core 22 is a value obtained by subtracting the temperature of the blown air flowing into the heater core 22 from the temperature of the blown air flowing out of the heater core 22 (for example, TAV-Tam or Tam-Tr). The amount of air (for example, a value estimated from a control voltage applied to the blower 52) can be determined from an integrated value. The operation of each operation mode will be described below.

(A) Cooling Mode In the cooling mode, the control device 60 brings the cooling expansion valve 14 into the throttling state to exert the refrigerant pressure reducing action, and brings the heat absorption expansion valve 15 into the fully closed state. Furthermore, since the cooling mode is one of the normal operation modes executed when the frost formation condition is not established, as shown in step S73 of FIG. 7, the control device 60 closes the on-off valve 45a.

  Thus, in the heat pump cycle 10 in the cooling mode, as in the first embodiment, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → cooling expansion valve 14 → indoor evaporator 16 → evaporation A vapor compression type refrigeration cycle in which the refrigerant circulates in the order of the pressure control valve 18 → the junction 13b → the suction port of the compressor 11 is configured. Then, in this cycle configuration, the control device 60 appropriately controls the operation of various control target devices as in the first embodiment.

  Therefore, in the cooling mode, as in the case of the cooling mode of the first embodiment, the blowing air cooled by the indoor evaporator 16 can be blown into the passenger compartment to perform cooling of the passenger compartment.

(B) Dehumidifying and heating mode In the dehumidifying and heating mode, the control device 60 sets the cooling expansion valve 14 in the throttling state, and sets the heat absorption expansion valve 15 in the throttling state. Furthermore, since the dehumidifying and heating mode is one of the normal operation modes executed when the frost formation condition is not established, the control device 60 closes the open / close valve 45a as shown in step S73 of FIG.

  Thereby, in the heat pump cycle 10 in the dehumidifying heating mode, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → cooling expansion valve 14 → interior evaporator 16 → evaporation pressure adjusting valve 18 → merging portion The refrigerant circulates in the order of 13b → the suction port of the compressor 11, and the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the branch portion 13a → the heat absorption expansion valve 15 → the outdoor heat exchanger 19 → the junction portion A vapor compression type refrigeration cycle in which the refrigerant circulates in the order of 13 b → the suction port of the compressor 11 is configured.

  That is, in the dehumidifying and heating mode, the indoor evaporator 16 and the outdoor heat exchanger 19 are switched to the refrigerant circuits connected in parallel. Then, with this cycle configuration, the control device 60 appropriately controls the operation of various control target devices as in the dehumidifying and heating mode of the first embodiment.

  For example, the control device 60 refers to the control map for the dehumidifying and heating mode stored in advance in the control device 60 based on the target blowout temperature TAO and the outside air temperature Tam, and outputs the control signal to the cooling expansion valve 14 And a control signal to be output to the heat absorption expansion valve 15.

  In the control map of the present embodiment, the throttle opening degree of the heat absorption expansion valve 15 is determined so that the refrigerant evaporation temperature in the outdoor heat exchanger 19 is at least a temperature lower than the outside air temperature Tam. Further, the throttle opening degree of the cooling expansion valve 14 is determined in a range which is larger than the throttle opening degree of the heat absorption expansion valve 15.

  Therefore, in the dehumidifying and heating mode, as in the dehumidifying and heating mode of the first embodiment, the blown air which has been cooled and dehumidified by the indoor evaporator 16 is reheated by the heater core 22 and blown out to the vehicle interior. The room can be dehumidified and heated.

(C) Heating Mode In the heating mode, the control device 60 brings the cooling expansion valve 14 into a fully closed state, and brings the heat absorption expansion valve 15 into a throttling state. Furthermore, since the heating mode is one of the normal operation modes executed when the frost formation condition is not established, as shown in step S73 of FIG. 7, the control device 60 closes the on-off valve 45a.

  Thereby, in the heat pump cycle 10 in the heating mode, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → heat absorption expansion valve 15 → outdoor heat exchanger 19 → conjoining portion 13b → compressor 11 A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the suction port is configured. Then, in this cycle configuration, the control device 60 appropriately controls the operation of various control target devices as in the heating mode of the first embodiment.

  For example, the control device 60 refers to the control map for heating mode stored in advance in the control device 60 based on the target blowout temperature TAO and the outside air temperature Tam, and outputs the control signal output to the heat absorption expansion valve 15 decide. In the control map of the present embodiment, the throttle opening degree of the heat absorption expansion valve 15 is determined so that the refrigerant evaporation temperature in the outdoor heat exchanger 19 is at least a temperature lower than the outside air temperature Tam.

  Accordingly, in the heating mode, as in the heating mode of the first embodiment, the blowing air heated by the heater core 22 can be blown into the vehicle compartment to heat the vehicle compartment.

  In the dehumidifying and heating mode and the heating mode, the refrigerant evaporation temperature in the outdoor heat exchanger 19 is lower than the outside temperature Tam. Furthermore, when the outside temperature Tam becomes extremely low temperature (for example, 0 ° C. or less), frost formation may occur on the outdoor heat exchanger 19.

  When such frost formation occurs, the outdoor air passage of the outdoor heat exchanger 19 is blocked by the frost, so that the heat exchange performance of the outdoor heat exchanger 19 is lowered. Therefore, the heat absorption amount that the refrigerant absorbs heat from the outside air in the outdoor heat exchanger 19 is significantly reduced, and the heat pump cycle 10 can not sufficiently heat the high temperature side heat medium. As a result, the passenger's feeling of heating is deteriorated.

  On the other hand, in the heat pump cycle 10 of the present embodiment, when it is determined in step S71 of the subroutine shown in FIG. 7 that the frost forming condition is satisfied, the process proceeds to step S72 and the defrost mode is switched. Be

(D) Defrosting Mode In the defrosting mode, the controller 60 opens the on-off valve 45a. The other operations are similar to the heating mode.

  Thereby, in the heat pump cycle 10 in the defrosting mode, the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → branching portion 13a → heat absorption expansion valve 15 → outdoor heat exchanger 19 → joining portion 13b → compressor 11 The refrigerant is circulated in the order of the suction port, and a vapor compression type refrigeration cycle in which the refrigerant circulates in the order of the heat absorption expansion valve 15 → the exhaust heat recovery unit 41 → the refrigerant inlet of the outdoor heat exchanger 19 is configured.

  Therefore, in the defrosting mode, part of the low-pressure refrigerant that has been reduced in pressure by the heat absorption expansion valve 15 to be in a gas-liquid two-phase state flows into the exhaust heat recovery unit 41 via the exhaust heat recovery passage 45 . Then, as in the heating mode of the first embodiment, the low pressure refrigerant in the gas-liquid two-phase state absorbs heat of the exhaust heat of the compressor 11 and evaporates when flowing through the exhaust heat recovery unit 41.

  The remaining low pressure refrigerant that has been reduced in pressure by the heat absorption expansion valve 15 to be in a gas-liquid two-phase state merges with the refrigerant flowing out of the exhaust heat recovery unit 41. This raises the temperature of the remaining low pressure refrigerant. The refrigerant which has joined and is elevated in temperature flows into the outdoor heat exchanger 19. Thereby, the frost which reached the outdoor heat exchanger 19 is fuse | melted, and defrost of the outdoor heat exchanger 19 is made. The refrigerant flowing out of the outdoor heat exchanger 19 is sucked into the compressor 11 via the junction 13b and compressed again.

  As described above, according to the heat pump cycle 10 of the present embodiment, the same effect as that of the first embodiment can be obtained. That is, the refrigerant circuit can be switched with a simple configuration without causing the complication of the cycle configuration, and comfortable air conditioning of the vehicle interior can be realized. In addition, the temperature of the battery 32 can be maintained in an appropriate temperature range. Further, the exhaust heat of the compressor 11 can be recovered sufficiently in the exhaust heat recovery unit 41.

  Furthermore, according to the heat pump cycle 10 of the present embodiment, the exhaust heat recovery passage 45 is connected so as to lead the refrigerant flowing out of the exhaust heat recovery unit 41 to the refrigerant flow path leading to the refrigerant inlet of the outdoor heat exchanger 19. ing. Therefore, the exhaust heat of the compressor 11 recovered by the exhaust heat recovery unit 41 can be effectively used as a heat source for defrosting the outdoor heat exchanger 19.

  Further, since the heat pump cycle 10 of the present embodiment includes the frosting determination unit configured by the control step S71, when the outdoor heat exchanger 19 needs to be defrosted, the exhaust heat recovery unit 41 is used. The outdoor heat exchanger 19 can be defrosted by heat (that is, heat recovered from the refrigerant by the exhaust heat recovery unit 41) of the refrigerant that has flowed out.

Third Embodiment
In the present embodiment, an example in which the configuration of the exhaust heat recovery unit 41 is changed with respect to the first embodiment will be described. As shown in FIG. 8, the exhaust heat recovery unit 41 of the present embodiment has a refrigerant pipe bent in a serpentine shape (so-called serpentine shape). And this refrigerant | coolant piping is arrange | positioned so that the outer periphery of the housing 11a may be thermally contacted. FIG. 8 is a drawing corresponding to FIG. 2 described in the first embodiment.

  The other configuration and operation of the heat pump cycle 10 are the same as those of the first embodiment. Therefore, also in this embodiment, the same effect as that of the first embodiment can be obtained.

Fourth Embodiment
In the present embodiment, an example in which the configuration of the exhaust heat recovery unit 41 is changed with respect to the first embodiment will be described. The exhaust heat recovery part 41 of this embodiment arrange | positions the case 11b in the outer peripheral side of the housing 11a, as shown in FIG. Then, the refrigerant is made to flow in the space formed between the outer peripheral side of the housing 11a and the inner peripheral side of the case 11b.

  Further, a plurality of heat storage materials 42a enclosed in a plurality of spherical resin or metal capsules are disposed in an annular space in cross section formed between the outer peripheral side of the housing 11a and the inner peripheral side of the case 11b. doing. Therefore, in the space formed between the outer peripheral side of the housing 11a and the inner peripheral side of the case 11b, the gap of the capsule in which the heat storage material 42a is enclosed flows. FIG. 9 is a drawing corresponding to FIG. 3 described in the first embodiment.

  The other configuration and operation of the heat pump cycle 10 are the same as those of the first embodiment. Therefore, also in this embodiment, the same effect as that of the first embodiment can be obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) Although the above-mentioned embodiment explained the example which applied thermal management system 1 concerning the present invention to an electric vehicle, application of thermal management system 1 is not limited to this. For example, the present invention may be applied to a normal engine vehicle that obtains a driving force for traveling a vehicle from an internal combustion engine or a hybrid vehicle that obtains a driving force for traveling a vehicle from both an internal combustion engine and an electric motor. Furthermore, the present invention is not limited to a vehicle, and may be applied to a stationary temperature control device or the like.

  (2) Although the above-mentioned embodiment demonstrated heat pump cycle 10 constituted so that switching of the operation mode for air conditioning was possible, switching of the operation mode for air conditioning is not indispensable. In the first embodiment, if at least the heating mode can be performed, the exhaust heat of the compressor 11 can be sufficiently recovered and effectively used. Similarly, in the second embodiment, in addition to any one of the dehumidifying and heating mode and the heating mode, it may be possible to execute the defrosting mode.

  (3) In the above embodiment, an example was described in which the low-pressure refrigerant that has been reduced in pressure by the heat absorption expansion valve 15 to be in a gas-liquid two-phase state flows into the exhaust heat recovery unit 41. The refrigerant to be flowed into is not limited to this. For example, as long as it is a gas-liquid two-phase refrigerant, it may be a high pressure refrigerant immediately after flowing out from the refrigerant passage of the water-refrigerant heat exchanger 12 or high temperature in the refrigerant passage of the water-refrigerant heat exchanger 12 It may be a side heat medium and a high pressure refrigerant in a heat exchange process.

  (4) Although the above-mentioned embodiment explained the example which adopted the latent heat storage material with a phase change at the time of heat storage as heat storage material 42a, the heat storage material is not limited to this. For example, the heat storage material may be formed of a metal member or the like. Furthermore, the heat storage material may be a chemical heat storage material accompanied by a chemical change at the time of heat storage. As such a chemical heat storage material, a heat storage material which chemically reacts alkali metal chloride and ammonia, a heat storage material which chemically reacts alkaline earth metal chloride and ammonia, a chemical reaction of transition metal element chloride and ammonia A heat storage material can be adopted.

  (5) The frost formation determination unit configured by the control step S71 described in the second embodiment described above is not limited to the determination unit that determines whether or not frost formation has actually occurred on the outdoor heat exchanger 19 . For example, the determination unit may be a determination unit that determines whether the operation condition may cause frost formation on the outdoor heat exchanger 19. It may be a determination unit that determines whether or not frost formation may occur in the outdoor heat exchanger 19.

  Moreover, frost formation conditions are not limited to what was demonstrated in the above-mentioned 2nd Embodiment. For example, the amount of heat release Qr in the heater core 22 is the flow rate of the refrigerant discharged from the compressor 11 (for example, the compressor 11) according to the temperature difference between the temperature of the inlet-side refrigerant and the temperature of the outlet-side refrigerant of the water-refrigerant heat exchanger 12 It may be determined from an integrated value obtained by integrating the value (estimated from the control signal output to the circuit). The temperature difference between the temperature of the inlet side refrigerant of the outdoor heat exchanger 19 and the temperature of the outlet side refrigerant may be calculated from an integrated value obtained by integrating the flow rate of the refrigerant discharged from the compressor 11.

  Furthermore, as the frost formation condition, it may be adopted that a value obtained by subtracting the refrigerant evaporation temperature in the outdoor heat exchanger 19 from the outside air temperature Tam is equal to or more than a predetermined reference temperature difference.

  (6) In the first embodiment described above, the on-off valve 45a is opened in the heating mode and the exhaust heat of the compressor 11 is recovered. However, the heating mode is executed with the on-off valve 45a closed. A normal heating mode and a strong heating mode which is executed with the open / close valve 45a open may be provided.

  In the second embodiment described above, the outlet portion of the exhaust heat recovery passage 45 is connected to both the suction port side of the compressor 11 and the refrigerant inlet side of the outdoor heat exchanger 19, and in the heating mode, the exhaust heat is exhausted. As in the second embodiment, in the defrosting mode, the refrigerant from which exhaust heat has been recovered is introduced to the refrigerant inlet side of the outdoor heat exchanger 19 in the defrosting mode. May be

  (7) Each composition of heat pump cycle 10 is not limited to what was indicated by the above-mentioned embodiment.

  For example, although heat pump cycle 10 explained by the above-mentioned embodiment explained to the example which adopted an electric compressor as compressor 11, it is not limited to this. For example, an engine driven compressor may be employed. As the engine-driven compressor, a variable displacement compressor may be employed in which the refrigerant discharge capacity can be adjusted by changing the discharge capacity.

  In addition, a gas-liquid separation unit may be added to the heat pump cycle 10 described in the above-described embodiment to separate the gas and liquid of the refrigerant that has flowed into the inside and store excess liquid phase refrigerant of the cycle. For example, an accumulator as a gas-liquid separation unit may be disposed in the refrigerant flow path extending from the refrigerant outlet of the merging portion 13b to the suction port of the compressor 11.

  Furthermore, with respect to the heat pump cycle 10 of the first embodiment, a receiver as a gas-liquid separation unit is disposed in the refrigerant passage extending from the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12 to the refrigerant inlet of the branch unit 13a. May be

  In the heat pump cycle 10 described in the above embodiment, an example in which the electric variable throttle mechanism with the fully closed function is adopted as the cooling expansion valve 14 and the heat absorption expansion valve 15 has been described. I will not. For example, instead of at least one of the cooling expansion valve 14 and the heat absorption expansion valve 15, a thermal expansion valve and an electric on-off valve that adjust the valve opening degree with a mechanical mechanism may be employed.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted the on-off valve 45a as a flow volume adjustment part which adjusts the flow volume of the refrigerant | coolant which distribute | circulates the waste heat recovery passage 45, a flow volume adjustment part is not limited to this. For example, as the flow rate adjusting unit, a variable throttle mechanism similar to the cooling expansion valve 14 or the heat absorption expansion valve 15 may be employed. Alternatively, a three-way flow control valve similar to the high temperature flow control valve 24 or the low temperature flow control valve 34 may be employed and disposed at the inlet or outlet of the exhaust heat recovery passage 45.

  Furthermore, when a variable throttling mechanism or a three-way flow control valve is employed as the flow control unit, the amount of exhaust heat of the compressor 11 to be recovered may be appropriately adjusted.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted R134a as a refrigerant | coolant of the heat pump cycle 10, a refrigerant | coolant is not limited to this. For example, R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Or you may employ | adopt the mixed refrigerant etc. which mixed multiple types among these refrigerant | coolants.

  Moreover, although the above-mentioned embodiment demonstrated the example which comprised the heating part which heats blowing air by the water-refrigerant heat exchanger 12 and the high temperature side heat-medium circuit 20, a heating part is not limited to this. For example, as the heating unit, an indoor condenser that directly exchanges heat between the refrigerant discharged from the compressor 11 and the blown air may be employed.

  Moreover, although the above-mentioned embodiment demonstrated the low temperature side heat-medium circuit 30 which can adjust the temperature of the battery 32, the temperature control target object of the low-temperature side heat-medium circuit 30 is not limited to this. For example, the temperature adjustment target may be an inverter, a charger, a motor generator, or the like. Furthermore, a plurality of temperature control objects may be provided.

  Further, the high temperature side radiator 23 and the low temperature side radiator 33 described in the first embodiment are not limited to configurations independent of each other. For example, in the high temperature side radiator 23 and the low temperature side radiator 33 described in the first embodiment, the heat of the high temperature side heat medium and the heat of the low temperature side heat medium may be integrated so as to be able to mutually transfer heat.

  Specifically, the heat mediums may be integrated so as to be capable of transferring heat by sharing a part of components (for example, heat exchange fins) of the high temperature side radiator 23 and the low temperature side radiator 33.

10 heat pump cycle 11 compressor 15 expansion valve for heat absorption (pressure reduction section)
19 Outdoor heat exchanger (evaporation unit)
41 exhaust heat recovery unit 42 heat storage unit 43 heat insulation unit 45 exhaust heat recovery passage 45 a on-off valve (flow rate adjustment unit)

Claims (7)

A compressor (11) that compresses and discharges a refrigerant;
And an exhaust heat recovery unit (41) for absorbing the exhaust heat of the compressor to the refrigerant.
A heat pump cycle in which a refrigerant flowing into the exhaust heat recovery unit is in a gas-liquid two-phase state. A pressure reducing unit (15) for reducing the pressure of the high pressure refrigerant pressurized by the compressor;
The heat pump cycle according to claim 1, wherein the refrigerant flowing into the exhaust heat recovery unit is a refrigerant decompressed by the decompression unit. An exhaust heat recovery passage (45) for leading the refrigerant flowing out of the exhaust heat recovery unit to a refrigerant flow path extending from the refrigerant outlet of the pressure reducing unit to the suction port of the compressor;
The heat pump cycle according to claim 2, further comprising: a flow rate adjusting unit (45a) configured to adjust a flow rate of the refrigerant flowing through the exhaust heat recovery passage.   The heat pump cycle according to claim 3, further comprising a heat storage section (42) for storing exhaust heat of the compressor.   The heat pump cycle according to claim 4, further comprising: a heat insulating portion (43) that suppresses heat released from the heat stored in the heat storage portion from the outside air. An evaporation unit (19) for evaporating the refrigerant decompressed by the decompression unit;
And a frost formation determination unit (S71) that determines that frost formation has occurred in the evaporation unit when a predetermined frost formation condition is satisfied.
6. The defrosting unit according to claim 5, wherein the defrosting unit is defrosted by the heat of the refrigerant flowing out from the exhaust heat recovery unit when it is determined by the frosting determination unit that frost formation has occurred in the evaporation unit. The heat pump cycle according to any one of the preceding claims. It is a heat pump cycle used for temperature control of air conditioning object space, and
The heat pump cycle according to any one of claims 1 to 6, wherein heating of the space to be air-conditioned is performed by the heat of the refrigerant flowing out of the exhaust heat recovery unit.

Images