WO2019111621A1

WO2019111621A1 - Heat pump system

Info

Publication number: WO2019111621A1
Application number: PCT/JP2018/041206
Authority: WO
Inventors: 侑樹小中出; 加藤　吉毅; 卓哉布施
Original assignee: 株式会社デンソー
Priority date: 2017-12-08
Filing date: 2018-11-06
Publication date: 2019-06-13
Also published as: CN111448432A; JP2019100688A

Abstract

This heat pump system has: a heat pump cycle (10); recovery parts (25, 35); and a high-temperature side heat reception part (20) and/or a low-temperature side heat reception part (30). The heat pump cycle has a compressor (11) that compresses and discharges a refrigerant, a radiator (12) that radiates heat of a high-pressure refrigerant compressed by the compressor, pressure reduction parts (15a, 15b) that reduce the pressure of the high-pressure refrigerant flowing out from the radiator, and heat sinks (16, 18) that evaporate a low-pressure refrigerant the pressure of which is reduced by the pressure reduction parts and sink heat. The recovery parts recover exhaust heat discharged from the compressor. The high-temperature side heat reception part causes the high-pressure refrigerant to radiate the heat recovered by the recovery parts. The low-temperature side heat reception part causes the low-pressure refrigerant to sink the heat recovered by the recovery parts.

Description

Heat pump system

Cross-reference to related applications

This application is based on Japanese Patent Application No. 2017-235997 filed on Dec. 8, 2017, the contents of which are incorporated herein by reference.

The present disclosure relates to a heat pump system having a heat pump cycle.

BACKGROUND ART Conventionally, a heat pump system has a heat pump cycle (i.e., a vapor compression refrigeration cycle), and controls the operation of the heat pump cycle to adjust the temperature of various heat transfer media.

Such a heat pump cycle is applied to, for example, a vehicle air conditioner, and the comfort of the vehicle interior is improved by adjusting the temperature of the blowing air which is the fluid to be heat-exchanged. Among the air conditioners for vehicles, there is known one configured to absorb heat from the cooling water of a cooling water circuit for cooling on-vehicle equipment etc. to the refrigerant of the refrigeration cycle in addition to heat absorption from the outside air.

For example, Patent Document 1 is known as such a vehicle air conditioner. In the air conditioning apparatus which concerns on patent document 1, it is comprised so that the heat | fever which generate | occur | produced with the compressor may be thermally stored in the thermal storage material arrange | positioned around the time of the thermal storage driving | operation of a refrigerating cycle.

In patent document 1, the heat stored in the heat storage material is used for vaporization of the refrigerant toward the outdoor heat exchanger in the heat storage heat exchanger connected via the heat storage pipe during the defrost operation of the refrigeration cycle. In the said air conditioning apparatus, defrosting of an outdoor heat exchanger is performed by this gaseous-phase refrigerant | coolant being sent to an outdoor heat exchanger.

JP, 2008-241127, A

However, in the case of Patent Document 1, when storing heat generated by the compressor, the operation of the refrigeration cycle is switched to the heat storage operation, and when utilizing the heat stored in the heat storage material, the operation of the refrigeration cycle is defrosted It will be necessary to switch to driving. That is, in utilizing the heat generated by the compressor, the operation of the refrigeration cycle had to be switched sequentially.

Moreover, in the air conditioning apparatus described in Patent Document 1, when switching the operation mode such as the heat storage operation and the defrost operation, the cycle configuration is switched. In order to realize this switching of the cycle configuration, a four-way switching valve, a plurality of solenoid valves, and the like are disposed, and the configuration of the refrigeration cycle has been complicated.

This indication is made in view of these points, and it aims at providing a heat pump system which can effectively utilize exhaust heat of a compressor with simple composition, controlling influence by operation control of a heat pump cycle. .

A heat pump system according to an aspect of the present disclosure includes a heat pump cycle, a recovery unit, and at least one of a high temperature side heat receiving unit and a low temperature side heat receiving unit. The heat pump cycle includes a compressor that compresses and discharges a refrigerant, a radiator that releases the heat of the high-pressure refrigerant compressed by the compressor, a decompression unit that decompresses the high-pressure refrigerant flowing out of the radiator, and a decompression unit. And a heat absorber for evaporating and absorbing the low-pressure refrigerant that has been depressurized. The recovery unit recovers the exhaust heat of the compressor. The high temperature side heat receiving unit dissipates the heat recovered by the recovery unit to the high pressure refrigerant. The low temperature side heat receiving unit absorbs the heat recovered by the recovery unit to the low pressure refrigerant.

According to the heat pump system, the exhaust heat of the compressor in the heat pump cycle can be recovered by the recovery unit regardless of the operation control of the heat pump cycle. Then, the heat pump system effectively uses the exhaust heat of the compressor recovered by the recovery unit on the heat pump cycle side via any one of the high temperature side heat receiving unit and the low temperature side heat receiving unit. be able to. That is, the heat pump system can effectively utilize the exhaust heat of the compressor with a simple configuration regardless of the operation mode of the heat pump cycle.

BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the heat pump system which concerns on at least one embodiment of this indication. It is an explanatory view showing the composition of the high temperature side recovery part in at least one embodiment. It is a block diagram showing a control system of a heat pump system concerning at least one embodiment. It is a block diagram which shows the 1st modification of the heat pump system which concerns on at least one embodiment. It is a block diagram which shows the 2nd modification of the heat pump system which concerns on at least one embodiment. It is a block diagram which shows the 3rd modification of the heat pump system which concerns on at least one embodiment. It is a block diagram of the heat pump system which concerns on at least one embodiment. It is a block diagram which shows the modification of the heat pump system which concerns on at least one embodiment. It is a block diagram of the heat pump system which concerns on at least one embodiment. It is a block diagram of the heat pump system which concerns on at least one embodiment. It is a block diagram which shows the modification of the heat recovery part in this indication. It is a block diagram which shows the modification of the high temperature side heat-medium circuit in this indication. It is a block diagram which shows the modification of the thermal storage part in this indication.

Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. The same referential mark may be attached | subjected to the part corresponding to the matter demonstrated by the form preceded in each form, and the overlapping description may be abbreviate | omitted. When only a part of the configuration is described in each form, the other forms described above can be applied to other parts of the configuration. Not only combinations of parts which clearly indicate that combinations are possible in each embodiment, but also combinations of embodiments even if they are not specified unless there is a problem with the combination. Is also possible.

Hereinafter, embodiments of the present disclosure will be described based on the drawings. In the following embodiments, parts which are the same as or equivalent to each other are given the same reference numerals in the drawings.

First Embodiment
First, a first embodiment of the present disclosure will be described with reference to FIGS. 1 to 3. In 1st Embodiment, the heat pump system 1 which concerns on this indication is applied to the electric vehicle which obtains the driving force for vehicle travel from the electric motor for travel. The heat pump system 1 has a function of performing air conditioning of a vehicle interior which is a space to be air conditioned, and a function of adjusting the temperature of the on-vehicle device 32 including a battery or the like to an appropriate temperature.

And the said heat pump system 1 can switch air conditioning mode, heating mode, and dehumidification heating mode as an operation mode which air-conditions a vehicle interior. The cooling mode is an operation mode in which the blowing air blown into the vehicle compartment is cooled and blown out 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 dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blown air is reheated and blown into the vehicle compartment.

In the heat pump cycle 10, an HFC refrigerant (specifically, R134a) is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. As refrigeration oil, PAG oil (polyalkylene glycol oil) compatible with liquid phase refrigerant is adopted. A portion of the refrigerator oil circulates in the cycle with the refrigerant.

Next, a specific configuration of the heat pump system 1 according to the first embodiment will be described with reference to FIG. The heat pump system 1 includes a heat pump cycle 10, a high temperature side heat medium circuit 20, a low temperature side heat medium circuit 30, an indoor air conditioning unit 50, and a control device 60.

First, each component which comprises the heat pump cycle 10 in the heat pump system 1 is demonstrated. The heat pump cycle 10 is a vapor compression refrigeration cycle device.

The compressor 11 sucks, compresses and discharges the refrigerant in the heat pump cycle 10, and corresponds to the compressor in the present disclosure. The compressor 11 is disposed in a vehicle bonnet.

The compressor 11 is an electric compressor which rotationally drives, by an electric motor, a fixed displacement type compression mechanism whose discharge displacement is fixed. The rotation speed (i.e., the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60 described later. In addition, in order to collect | recover the exhaust heat of the compressor 11 in the outer side of the compressor 11, the structure corresponded to the collection | recovery part in this indication is arrange | positioned. This point will be described in detail later.

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 is a heat exchanger that heats the high temperature side heat medium by exchanging heat between the high pressure refrigerant discharged from the compressor 11 and the high temperature side heat medium circulating the high temperature side heat medium circuit 20. .

The water-refrigerant heat exchanger 12 corresponds to the radiator in the present disclosure. As the high temperature side heat medium, a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted.

The refrigerant inlet side of the refrigerant branch portion 14 a is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12. The refrigerant branch portion 14 a branches the flow of the high pressure refrigerant flowing out of the water-refrigerant heat exchanger 12. The refrigerant branch portion 14a is formed to be a three-way joint structure having three refrigerant inlets and outlets communicating with one another, one of the three inlets and outlets being a refrigerant inlet and the remaining two being refrigerant flows. It is an exit.

The refrigerant inlet side of the indoor evaporator 16 is connected to one of the refrigerant outlets of the refrigerant branch portion 14 a via the cooling expansion valve 15 a. The refrigerant inlet side of the chiller 18 is connected to the other refrigerant outlet of the refrigerant branch portion 14a via the heat absorption expansion valve 15b.

The cooling expansion valve 15a is a cooling decompression unit that decompresses the refrigerant that has flowed out from one refrigerant outlet of the refrigerant branching unit 14a at least in the cooling mode and the dehumidifying and heating mode. The said cooling expansion valve 15a comprises the pressure reduction part in this indication. The cooling expansion valve 15 a also functions as a cooling flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the indoor evaporator 16.

The cooling expansion valve 15a is an electric variable throttle mechanism, and has a valve body and an electric actuator. That is, the cooling expansion valve 15a is configured by a so-called electric expansion valve. The valve body of the cooling expansion valve 15a is configured to be able to change the passage opening degree of the refrigerant passage (in other words, the throttle opening degree). The electric actuator has a stepping motor that changes the throttle opening of the valve body.

The operation of the cooling expansion valve 15 a is controlled by a control signal output from the controller 60. The cooling expansion valve 15a is a variable throttling mechanism having a fully open function of fully opening the refrigerant passage when the throttling degree is fully opened and a fully closing function of closing the refrigerant passage when the throttling degree is fully closed. It is configured.

That is, the cooling expansion valve 15a can prevent the pressure reducing action of the refrigerant from being exhibited by fully opening the refrigerant passage. Further, the cooling expansion valve 15 a can block the flow of the refrigerant into the indoor evaporator 16 by closing the refrigerant passage. That is, the cooling expansion valve 15a has both a function as a pressure reducing unit that reduces the pressure of the refrigerant and a function as a circuit switching unit that switches the refrigerant circuit.

The refrigerant inlet side of the indoor evaporator 16 is connected to the outlet of the cooling expansion valve 15a. The indoor evaporator 16 performs heat exchange between the low pressure refrigerant decompressed by the cooling expansion valve 15a and the blown air at least in the cooling mode and the dehumidifying heating mode to evaporate the low pressure refrigerant and cool the blown air. It is an evaporator.

The indoor evaporator 16 is disposed in the casing 51 of the indoor air conditioning unit 50. That is, the indoor evaporator 16 constitutes a heat sink in the present disclosure, and corresponds to either one of the first heat sink or the second heat sink in the present disclosure.

The inlet side of the evaporation pressure control valve 17 is connected to the refrigerant outlet of the indoor evaporator 16. The evaporation pressure adjustment valve 17 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 17 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.

The evaporation pressure control valve 17 is configured to maintain the refrigerant evaporation temperature in the indoor evaporator 16 at a reference temperature (1 ° C. in the present embodiment) that can suppress the formation of frost on the indoor evaporator 16. ing.

One refrigerant inlet side of the refrigerant merging portion 14 b is connected to the outlet of the evaporation pressure adjusting valve 17. The refrigerant merging portion 14b has a three-way joint structure similar to that of the refrigerant branching portion 14a, with two of the three inflows and outlets being used as a refrigerant inlet and the remaining one being used as a refrigerant outlet. As shown in FIG. 1, the refrigerant merging portion 14 b merges the flow of the refrigerant flowing out of the evaporation pressure adjusting valve 17 and the flow of the refrigerant flowing out of the chiller 18.

Here, the heat absorption expansion valve 15 b is connected to the other refrigerant outlet of the refrigerant branch portion 14 a. The heat absorption expansion valve 15b is a heat absorption decompression unit that decompresses and expands the liquid phase refrigerant that has flowed out from the other refrigerant outlet in the refrigerant branch unit 14a at least in the heating mode and the dehumidifying heating mode. The heat absorption expansion valve 15 b functions as a pressure reduction unit in the present disclosure.

The heat absorption expansion valve 15 b functions as a heat absorption flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the chiller 18. The basic configuration of the heat absorption expansion valve 15b is the same as that of the cooling expansion valve 15a. That is, the heat absorption expansion valve 15b is an electric variable throttle mechanism, and has a valve body and an electric actuator. Then, the heat absorption expansion valve 15b has a full open function and a full close function, as with the cooling expansion valve 15a.

That is, the heat absorption expansion valve 15b can prevent the refrigerant from exerting a pressure reducing action by fully opening the refrigerant passage, and can block the flow of the refrigerant to the chiller 18 by closing the refrigerant passage. . That is, the heat absorption expansion valve 15b has both a function as a pressure reducing unit that reduces the pressure of the refrigerant and a function as a circuit switching unit that switches the refrigerant circuit.

The refrigerant inlet side of the chiller 18 is connected to the outlet of the heat absorption expansion valve 15b. The chiller 18 is a heat exchanger that exchanges heat between the low pressure refrigerant decompressed by the heat absorption expansion valve 15 b and the low temperature side heat medium circulating in the low temperature side heat medium circuit 30. The chiller 18 has a refrigerant passage for circulating the low pressure refrigerant decompressed by the heat absorption expansion valve 15b, and a water passage for circulating the low temperature side heat medium circulating in the low temperature side heat medium circuit 30.

The chiller 18 is an evaporation unit that evaporates the low pressure refrigerant by heat exchange 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 and the dehumidifying heating mode. That is, the chiller 18 is a heat exchanger for heat absorption which evaporates the low pressure refrigerant and absorbs the heat of the low temperature side heat medium to the refrigerant at least in the heating mode and the dehumidifying heating mode.

That is, the chiller 18 constitutes a heat sink in the present disclosure, and corresponds to either the first heat sink or the second heat sink in the present disclosure. The other refrigerant inlet side of the refrigerant merging portion 14 b is connected to the outlet of the refrigerant passage of the chiller 18. And the suction port side of the compressor 11 is connected to the refrigerant | coolant outflow port of the refrigerant | coolant confluence | merging part 14b.

Next, the high temperature side heat medium circuit 20 in the heat pump system 1 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 inlet side of the heater core 22 is connected to another inlet / outlet of the high temperature side flow control valve 24. The inlet side of the high temperature side radiator 23 is connected to still another inlet and outlet of the high temperature side flow control valve 24.

Then, 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, the high temperature side flow rate adjustment valve 24 flows the high temperature side heat medium flowed into the heater core 22 and It has a function of continuously adjusting the flow rate ratio to the flow rate of the high temperature side heat medium to be flowed 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 having passed through the indoor evaporator 16. The heater core 22 corresponds to the heater core in the present disclosure. 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 outlet side of the water passage in 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 outlet side of the high temperature side radiator 23 is connected to the inlet side of the high temperature side heat medium pump 21.

As shown in FIG. 1, in the high temperature side heat medium circuit 20, the heater core 22 and the high temperature side radiator 23 are connected in parallel to the flow of the high temperature side heat medium. 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.

Further, the high temperature side heat medium circuit 20 has a high temperature side recovery unit 25 for recovering and receiving the exhaust heat of the compressor 11 in the heat pump cycle 10. Accordingly, the high temperature side heat medium circuit 20 corresponds to the high temperature side heat receiving portion in the present disclosure and corresponds to the high temperature side heat medium circuit in the present disclosure. The specific configuration of the high temperature side recovery unit 25 will be described in detail later.

Subsequently, the low temperature side heat medium circuit 30 in the heat pump system 1 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 18, the low temperature side heat medium pump 31, the on-vehicle device 32, the low temperature side radiator 33, the low temperature side flow rate adjustment valve 34 and the like are arranged.

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 18. 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.

Then, one outlet / outlet of the low temperature side flow control valve 34 is connected to the outlet side of the water passage in the chiller 18. 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. That is, the low temperature side flow control valve 34 is configured of an electric three-way flow control valve.

The inlet side of the water passage in the on-vehicle device 32 is connected to another inflow / outlet of the low temperature side flow control valve 34. The inlet side of the low temperature side radiator 33 is connected to still another inlet and outlet of the low temperature side flow control valve 34.

The in-vehicle device 32 is mounted on the electric vehicle and is configured of a device that generates heat when activated. The on-vehicle device 32 corresponds to the heat-generating device in the present disclosure. The on-vehicle device 32 includes, for example, a battery, an inverter, a charger, a motor generator, and the like.

The battery supplies power to various electric devices mounted in a vehicle, and is configured of, for example, a chargeable / dischargeable secondary battery (in the present embodiment, a lithium ion battery). The inverter is a power conversion unit that converts direct current into alternating current.

And a charger is a charger which charges electric power to a battery. The motor generator outputs driving power for traveling by being supplied with electric power, and generates regenerative electric power at the time of deceleration or the like.

For this reason, the cooling water passage in the in-vehicle device 32 is formed so as to be able to cool each device by circulating the low temperature side heat medium. The suction port side of the low temperature side heat medium pump 31 is connected to the outlet side of the cooling water passage in the in-vehicle device 32.

The temperature of each component included in the on-vehicle device 32 needs to be adjusted within the range of an appropriate temperature range in which sufficient performance can be exhibited. Therefore, the heat pump system 1 can adjust each device of the in-vehicle device 32 to an appropriate temperature range by adjusting the flow rate of the low-temperature side heat medium to the water passage of the in-vehicle device 32.

The low temperature side radiator 33 is a heat exchanger that exchanges heat between the low temperature side heat medium flowing out from the low temperature side flow rate adjustment valve 34 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, the low temperature side flow control valve 34 functions as a heat exchanger for absorbing heat that absorbs the heat of the outside air to the low temperature side heat medium. The outlet side of the low temperature side radiator 33 is connected to the inlet side of the low temperature side heat medium pump 31. That is, the low temperature side radiator 33 is disposed in parallel with the on-vehicle device 32 with respect to the flow of the low temperature side heat medium in the low temperature side heat medium circuit 30.

The heat pump system 1 can use the low-temperature side heat medium circuit 30 to cool the in-vehicle device 32 and adjust the temperature, and can use heat generated by the in-vehicle device 32 as a heat source. Moreover, the said heat pump system 1 can utilize external air as a heat source, or can thermally radiate external air by utilizing the low temperature side radiator 33 of the low temperature side heat-medium circuit 30. FIG.

Next, the indoor air conditioning unit 50 which comprises the heat pump system 1 is demonstrated. The indoor air conditioning unit 50 is a unit for blowing out the blowing air whose temperature has been adjusted by the heat pump cycle 10 in the heat pump system 1 to an appropriate place in the vehicle compartment. The indoor air conditioning unit 50 is disposed inside the instrument panel (i.e., instrument panel) at the foremost part of the passenger compartment.

The indoor air conditioning unit 50 is configured by housing a blower 52, an indoor evaporator 16, a heater core 22 and the like in an air passage formed inside a casing 51 forming the 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.

As shown in FIG. 1, an internal / external air switching device 53 is disposed on the most upstream side of the flow of the blown air 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 is constituted by an electric blower which drives a centrifugal multi-blade fan by an electric motor, and functions to blow air taken in via the inside / outside air switching device 53 toward the vehicle interior for blowing. 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 arranged in this order with respect to the flow of the blown air on the downstream side of the blown air flow of the blower 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 control device 60.

A mixing space 56 is provided downstream of the air flow of the heater core 22. In the mixing space 56, the blowing air heated by the heater core 22 and the blowing air which has passed the cold air bypass passage 55 and is not heated by the heater core 22 are mixed.

Further, at the most downstream portion of the air flow of the casing 51, an opening for blowing the air (air-conditioned air) mixed in the mixing space 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 passenger 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 is adjusted by adjusting the air volume ratio of the air volume passing the heater core 22 and the air volume passing the cold air bypass passage 55 by the air mix door 54. As a result, the temperature of the air (air-conditioned air) blown out from the outlets into the vehicle compartment is also adjusted.

The face door for adjusting the opening area of the face opening hole, the foot door for adjusting the opening area of the foot opening hole, and the defroster opening on the upstream side of the air flow of the face opening hole, the foot opening hole, and the defroster opening hole, respectively. 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.

Here, in the heat pump system 1 according to the first embodiment, the high temperature side heat medium circuit 20 has a high temperature side recovery unit 25 in order to recover the exhaust heat of the compressor 11 in the heat pump cycle 10. The configuration of the high temperature side recovery unit 25 will be described with reference to FIGS.

The high temperature side recovery unit 25 recovers the exhaust heat of the compressor 11 by absorbing heat from the high temperature side heat medium circulating in the high temperature side heat medium circuit 20, and the exhaust heat of the compressor 11 is recovered by the high temperature side heat medium circuit Accept to 20.

As shown in FIG. 2, the high temperature side recovery unit 25 includes a housing portion 25 a, a high temperature side inflow piping 26, and a high temperature side outflow piping 27. The housing portion 25 a, the high temperature side inflow piping 26, and the high temperature side outflow piping 27 are connected to one another, and constitute a flow path through which the high temperature side heat medium circulating in the high temperature side heat medium circuit 20 flows.

As shown in FIG. 1, the high temperature side inflow pipe 26 is a pipe branched from the high temperature side branch portion 26 a disposed on the outlet side of the water passage in the water-refrigerant heat exchanger 12. The said high temperature side inflow piping 26 is connected to the accommodating part 25a as mentioned above. Accordingly, in the high temperature side heat medium circuit 20, the flow of the high temperature side heat medium branched at the high temperature side branch portion 26a reaches the inside of the accommodation portion 25a.

The high temperature side outflow pipe 27 extends from the housing portion 25 a and is connected to the high temperature side joining portion 27 a disposed in the circulation circuit of the high temperature side heat medium circuit 20. The high temperature side joining portion 27a is located downstream of the high temperature side branch portion 26a in the flow direction downstream of the high temperature side heat medium on the outlet side of the water passage in the water-refrigerant heat exchanger 12.

Accordingly, the high temperature side heat medium flowing out of the storage portion 25a joins the high temperature side heat medium circulating in the heater core 22 and the like in the high temperature side heat medium circuit 20 on the outlet side of the water passage in the water-refrigerant heat exchanger 12. .

Here, as shown in FIG. 2, the housing portion 25 a in the high temperature side recovery portion 25 is formed so as to cover the outer surface of the compressor 11. That is, the housing portion 25 a houses a part of the refrigerant pipe connected to the compressor 11 and the compressor 11 inside.

Therefore, the high temperature side heat medium that has flowed through the high temperature side inflow pipe 26 flows into the inside of the housing 25 a and flows along the outer surface of the compressor 11. At this time, the high temperature side heat medium absorbs and recovers the exhaust heat of the compressor 11.

Thereafter, the high temperature side heat medium flows out from the housing portion 25 a and joins the circulation circuit of the high temperature side heat medium circuit 20 via the high temperature side outflow piping 27. Thus, the high temperature side heat medium circuit 20 can recover and receive the exhaust heat of the compressor 11 through the flow of the high temperature side heat medium in the high temperature side recovery unit 25.

As shown in FIG. 2, a heat storage material 25 b is disposed inside the storage portion 25 a in the high temperature side recovery portion 25. The heat storage material 25 b is a latent heat storage material with a phase change at the time of heat storage. The phase change temperature of the heat storage material 25 b is determined within a range that is higher than the temperature of the high-temperature side heat medium flowing into the housing 25 a and lower than the temperature of the compressor 11.

The heat storage material 25 b stores the exhaust heat of the compressor 11 and dissipates the heat stored in the high temperature side heat medium when the temperature of the high temperature side heat medium is lower than a predetermined temperature. It is configured.

And the said heat storage material 25b is arrange | positioned around the compressor 11 in the accommodating part 25a in the state enclosed with several spherical resin-made or metal-made capsules. The high temperature side heat medium flowing from the high temperature side inflow pipe 26 into the housing portion 25 a flows through the gap of the capsule and flows to the high temperature side outflow pipe 27.

As the heat storage material 25b in the high temperature side recovery unit 25, for example, (water-based heat storage material, paraffin wax-based heat storage material, higher alcohol-based heat storage material, inorganic salt-based heat storage material) can be employed. As a water-based heat storage material, for example, sodium acetate trihydrate and magnesium chloride tetrahydrate can be adopted.

And, as a paraffin wax-based heat storage material, for example, heptacosane, octacosan, nonacosane, stearyl stearate can be adopted. Moreover, as a heat storage material of a higher alcohol type, for example, xylitol can be used. Moreover, these mixed materials can be employ | adopted as the thermal storage material 25b.

Therefore, when the surroundings become higher than the heat storage temperature by the exhaust heat of the compressor 11, the heat storage material 25b absorbs heat from the surroundings and changes in phase. Thus, the exhaust heat of the compressor 11 is stored in the heat storage material 25b. And the thermal storage material 25b which stored heat changes sensible heat so that the temperature of the high temperature side heat carrier may be approached. In addition, when the temperature of the high temperature side heat medium becomes lower than the heat storage temperature, the heat storage material 25b dissipates the exhaust heat of the compressor 11 stored in the high temperature side heat medium to change the phase.

That is, in the first embodiment, the heat storage section 40 can be configured by arranging the heat storage material 25 b in the storage section 25 a of the high temperature side recovery section 25. The heat storage unit 40 stores the exhaust heat of the compressor 11 and dissipates the stored heat to the high temperature side heat medium when the temperature of the high temperature side heat medium becomes lower than a predetermined heat storage temperature. That is, the heat storage unit 40 corresponds to the heat storage unit in the present disclosure.

Next, a control system of the heat pump system 1 according to the first embodiment will be described with reference to FIG. 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, the control device 60 performs various operations and processes based on the control program stored in the ROM, and controls the operation of various control target devices connected to the output side. The control target devices in the first embodiment include the compressor 11, the cooling expansion valve 15a, the heat absorption expansion valve 15b, the high temperature side heat medium pump 21, the high temperature side flow control valve 24, and the low temperature side heat medium The pump 31, the low temperature side flow control valve 34, the blower 52 and the like are included.

As shown in FIG. 3, a sensor group for air conditioning control is connected to the input side of the control device 60. The air conditioning control sensor group includes 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, and an air conditioning air temperature sensor 62f. The control device 60 receives detection signals of these air conditioning control sensors.

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 15 a or the heat absorption expansion valve 15 b.

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.

Furthermore, on the input side of the control device 60, an operation panel 61 disposed in the vicinity of the instrument panel at the front of the vehicle interior is connected. On the operation panel 61, a plurality of operation switches are arranged. Therefore, control signals from the plurality of operation switches are input to the control device 60.

Specifically, as various operation switches in the operation panel 61, an automatic switch for setting or canceling the automatic control operation of the heat pump system 1, a cooling switch for requesting cooling of the vehicle interior, and manually setting an air volume of the blower 52 There are an air volume setting switch, a temperature setting switch for setting a target temperature Tset in the vehicle interior, and the like.

In the control device 60, a control unit for controlling various control target devices connected to the output side is integrally configured, but a 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 that controls the operation of the compressor 11 is the discharge capacity control unit 60a. In the control device 60, a circuit switching control unit 60b controls the operation of the cooling expansion valve 15a and the heat absorption expansion valve 15b as a circuit switching unit.

Subsequently, the operation of the heat pump system 1 in the first embodiment will be described. As described above, in the heat pump system 1 according to the first embodiment, the operation mode can be appropriately switched from the plurality of operation modes. Switching of these operation modes is performed by executing a control program stored in advance in the control device 60.

More specifically, in the control program, based on the detection signal detected by the air conditioning control sensor group and the operation signal output from the operation panel 61, the target blowout temperature TAO of the air blown into the vehicle compartment is calculated. Do. Then, the operation mode is switched based on the target blowout temperature TAO and the detection signal. Hereinafter, among the plurality of operation modes, the operation in the cooling mode, the operation in the heating mode, and the operation in the dehumidifying heating mode will be described.

(A) Cooling Mode The cooling mode is an operation mode in which the air, which is the fluid to be heat-exchanged, is cooled and blown into the vehicle compartment. In the cooling mode, the control device 60 opens the cooling expansion valve 15a at a predetermined throttle opening degree, and brings the heat absorption expansion valve 15b into a fully closed state.

Therefore, in the heat pump cycle 10 in the cooling mode, the compressor 11 → water-refrigerant heat exchanger 12 → refrigerant branch portion 14a → cooling expansion valve 15a → interior evaporator 16 → evaporation pressure control valve 17 → refrigerant merging portion 14b → compression A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the machine 11 is configured.

That is, in the cooling mode, the refrigerant is made to flow into the indoor evaporator 16, and the refrigerant circuit is switched to the refrigerant circuit for cooling the blowing air by heat exchange with the blowing air.

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 controls the operation of 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 operates the high temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the cooling mode determined in advance. Further, the control device 60 controls the operation of 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.

The control device 60 operates the low temperature side heat medium pump 31 so as to exert the water pressure transfer capability in the cooling mode. At this time, the control device 60 controls the operation of the low temperature side flow control valve 34, and the flow balance of the low temperature side heat medium flowing out of the water passage of the chiller 18 is arbitrary between the on-vehicle device 32 side and the low temperature side radiator 33 side. Adjust to achieve a balance of

Then, the control device 60 determines the control voltage (air blowing capacity) of the fan 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 extremely low temperature region (maximum cooling region) and the extremely high temperature region (maximum heating region) of the target blowing temperature TAO, and as the intermediate temperature region is approached. Reduce air flow.

Further, the control device 60 controls the operation of the air mix door 54 so that the cold air bypass passage 55 is fully opened and the air passage on the heater core 22 side is closed. The control device 60 appropriately controls the operation of other various control target devices.

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 operates, 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 15a via the refrigerant branch portion 14a and is decompressed. The throttle opening degree of the cooling expansion valve 15a is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is approximately 3 ° C.

The low pressure refrigerant reduced in pressure by the cooling expansion valve 15 a 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 which is a heat exchange object fluid is cooled. The refrigerant flowing out of the indoor evaporator 16 is sucked into the compressor 11 via the evaporation pressure adjusting valve 17 and the refrigerant merging portion 14 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.

Also in this cooling mode, with the operation of the compressor 11, exhaust heat of the compressor 11 is generated. As described above, in the high temperature side recovery unit 25, the exhaust heat of the compressor 11 can be absorbed by the high temperature side heat medium and recovered, and the exhaust heat of the compressor 11 is stored by the heat storage material 25b. Can be That is, according to the heat pump system 1, the exhaust heat of the compressor 11 is recovered and stored by the high temperature side heat medium of the high temperature side recovery unit 25 and the heat storage material 25b, and dissipated to the high pressure refrigerant side for appropriate use can do.

(B) Heating mode The heating mode is an operation mode in which the chiller 18 absorbs heat from the low-temperature side heat medium of the low-temperature side heat medium circuit 30, and heats the blowing air which is the fluid to be heat exchanged to blow the air into the vehicle compartment . In the heating mode, the control device 60 fully closes the cooling expansion valve 15a and opens the heat absorption expansion valve 15b at a predetermined throttle opening degree.

In the heat pump cycle 10 in the heating mode, steam in which the refrigerant circulates in the following order: compressor 11 → water-refrigerant heat exchanger 12 → refrigerant branch unit 14 a → expansion valve for heat absorption 15 b → chiller 18 → refrigerant merging unit 14 b → compressor 11 A compression type refrigeration cycle is configured.

That is, in the heating mode, the refrigerant is made to flow into the chiller 18, and the heat is absorbed by heat exchange with the low temperature side heat medium to be switched to the refrigerant circuit that heats the blown air.

Here, the low temperature side heat medium in the low temperature side heat medium circuit 30 is heated by the exhaust heat generated in the in-vehicle device 32 when passing through the in-vehicle device 32. Further, when passing through the low temperature side radiator 33, the low temperature side heat medium is heated by heat exchange with the outside air. That is, the heat pump system 1 can use the on-vehicle device 32 or the outside air as a heat source for heating in the heating mode.

For example, the control device 60 controls the operation of 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 heating mode control map 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 operates the high temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the predetermined heating mode. The control device 60 controls the operation of 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.

The control device 60 operates the low temperature side heat medium pump 31 so as to exert the water pressure transfer capability in the heating mode. At this time, the control device 60 controls the operation of the low temperature side flow control valve 34, and the flow balance of the low temperature side heat medium flowing out of the water passage of the chiller 18 is arbitrary between the on-vehicle device 32 side and the low temperature side radiator 33 side. Adjust to achieve a balance of

And the said control apparatus 60 determines the control voltage (blower capability) of the air blower 52 similarly to air conditioning mode. Further, the control device 60 controls the operation of the air mix door 54 so as to close the cold air bypass passage 55 by fully opening the air passage on the heater core 22 side. The control device 60 appropriately controls the operation of various other 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 operates, 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 is a heat exchange object fluid is heated, and the temperature of blowing air approaches the target blowing temperature TAO. The high temperature side heat medium which has flowed 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 flows into the heat absorption expansion valve 15b via the refrigerant branch portion 14a and is reduced in pressure. The throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the refrigerant on the outlet side of the chiller 18 is in a gas-liquid two-phase state.

At this time, in the low temperature side heat medium circuit 30, the low temperature side heat medium circulates in the circulation circuit by the operation of the low temperature side heat medium pump 31. The low temperature side heat medium absorbs heat generated in the in-vehicle device 32 when passing through the water passage of the in-vehicle device 32.

Further, when passing through the low temperature side radiator 33, the low temperature side heat medium absorbs heat from the outside air blown by the outside air fan. The low temperature side heat medium flows into the water passage of the chiller 18 in a state where the heat is absorbed by the on-vehicle device 32 and the low temperature side radiator 33.

In the heat pump cycle 10, the low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15b flows into the chiller 18. The refrigerant flowing into the chiller 18 absorbs heat from the low temperature side heat medium flowing through the water passage of the chiller 18 and evaporates. The refrigerant flowing out of the chiller 18 is sucked into the compressor 11 via the refrigerant merging portion 14b and compressed again.

Therefore, in the heating mode, heating of the vehicle interior can be performed by heating the blown air, which is the fluid to be heat-exchanged, with the heater core 22 and blowing it out into the vehicle interior. That is, in the heating mode, the heat pump system 1 pumps up the heat absorbed from the on-vehicle device 32 or the outside air in the low temperature side heat medium circuit 30 in the heat pump cycle 10, and sends the blown air through the high temperature side heat medium circuit 20. It can be used to heat the

And also in the heating mode concerned, operation of compressor 11 in heat pump cycle 10 is needed. For this reason, the exhaust heat of the compressor 11 is generated also in the heating mode. The heat pump system 1 can recover the exhaust heat of the compressor 11 through the high temperature side heat medium in the high temperature side recovery unit 25 of the high temperature side heat medium circuit 20.

Specifically, a part of the high temperature side heat medium in the high temperature side heat medium circuit 20 branches from the circulation circuit in the high temperature side heat medium circuit 20 and enters the housing portion 25 a via the high temperature side inflow piping 26. To flow. In the housing portion 25 a, the high temperature side heat medium absorbs the exhaust heat of the compressor 11 and joins the circulation circuit of the high temperature side heat medium circuit 20 via the high temperature side outflow pipe 27. In this manner, the high temperature side heat medium circuit 20 can recover the exhaust heat of the compressor 11 and transport the exhaust heat of the compressor 11 to the circulation circuit side of the high temperature side heat medium circuit 20.

According to the heat pump system 1, in addition to the heat of the high pressure refrigerant including the heat pumped up from the low temperature side heat medium circuit 30, the exhaust heat of the compressor 11 is used to heat the high temperature side heat medium of the high temperature side heat medium circuit 20 The heater core 22 can dissipate heat to the blowing air.

Accordingly, the heat pump system 1 can dissipate heat to the high pressure refrigerant side using the exhaust heat of the compressor 11 in addition to the heat of the high pressure refrigerant in the water-refrigerant heat exchanger 12 as a heat source in the heating mode. Therefore, the heating capacity in the heat pump system 1 can be improved.

(C) Dehumidifying heating mode In the dehumidifying heating mode, the blown air cooled by the indoor evaporator 16 is heated by the chiller 18 using heat absorbed from the low temperature side heat medium of the low temperature side heat medium circuit 30 and the like. It is an operation mode for blowing air into the passenger compartment. In the dehumidifying and heating mode, the control device 60 opens the cooling expansion valve 15a and the heat absorption expansion valve 15b at respective predetermined opening degrees.

Accordingly, in the heat pump cycle 10 in the dehumidifying heating mode, the heat flows from the compressor 11 to the water-refrigerant heat exchanger 12 to the refrigerant branch portion 14a, and flows from one side of the refrigerant branch portion 14a to the cooling expansion valve 15a to the indoor evaporator 16. At the same time, it flows from the other side of the refrigerant branch portion 14a to the heat absorption expansion valve 15b to the chiller 18. The refrigerant flowing out of the indoor evaporator 16 and the refrigerant flowing out of the chiller 18 merge at the refrigerant merging portion 14b, and then flow in the order of the compressor 11 and circulate. That is, in the dehumidifying and heating mode, a vapor compression type refrigeration cycle in which the refrigerant flows in parallel to the indoor evaporator 16 and the chiller 18 is configured.

Then, with this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side with reference to the control map for the dehumidifying and heating mode and the like stored in advance in the control device 60.

In the heat pump cycle 10 in the dehumidifying and 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 operates, 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 that has flowed into the heater core 22 exchanges heat with the blowing air cooled by the indoor evaporator 16 and radiates heat since the air mixing door 54 fully opens the air passage on the heater core 22 side.

Thus, the blown air is reheated from the cooled state, and the temperature of the blown air approaches the target blowout temperature TAO. The high temperature side heat medium which has flowed 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 flows into the cooling expansion valve 15a via the refrigerant branch portion 14a and is decompressed. The throttle opening degree of the cooling expansion valve 15a is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is approximately 3 ° C.

The high pressure refrigerant branched at the refrigerant branch portion 14a flows into the heat absorption expansion valve 15b and is decompressed. The throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the refrigerant on the outlet side of the chiller 18 is in a gas-liquid two-phase state.

Also in the dehumidifying and heating mode, in the low temperature side heat medium circuit 30, the low temperature side heat medium circulates in the circulation circuit by the operation of the low temperature side heat medium pump 31. The low temperature side heat medium absorbs heat generated in the in-vehicle device 32 when passing through the water passage of the in-vehicle device 32.

As described above, the heater core 22 is disposed on the downstream side of the air flow of the indoor evaporator 16 inside the casing 51. Therefore, in the dehumidifying and heating mode, the air cooled by the indoor evaporator 16 is on the low temperature side. The heat absorbed by the heat medium circuit 30 can be used to heat the heater core 22. Therefore, in the dehumidifying and heating mode, dehumidifying and heating the passenger compartment can be performed by heating the blown air cooled by the indoor evaporator 16 by the heater core 22 and blowing it out into the passenger compartment.

That is, even in the dehumidifying and heating mode, the heat pump system 1 pumps up the heat absorbed by the low-temperature side heat medium circuit 30 from the on-vehicle device 32 or the outside air in the heat pump cycle 10 and via the high temperature side heat medium circuit 20 It can be used to heat the blast air.

And in the said dehumidification heating mode, operation of compressor 11 in heat pump cycle 10 is needed. For this reason, the exhaust heat of the compressor 11 is generated also in the dehumidifying and heating mode. The heat pump system 1 can recover the exhaust heat of the compressor 11 through the high temperature side heat medium in the high temperature side recovery unit 25 of the high temperature side heat medium circuit 20. The high temperature side heat medium circuit 20 can recover the exhaust heat of the compressor 11 and transport the exhaust heat of the compressor 11 to the circulation circuit side of the high temperature side heat medium circuit 20 as in the heating mode.

According to the heat pump system 1, in addition to the heat of the high pressure refrigerant including the heat pumped up from the low temperature side heat medium circuit 30, the exhaust heat of the compressor 11 is used to heat the high temperature side heat medium of the high temperature side heat medium circuit 20 The air cooled by the indoor evaporator 16 can be heated by the heater core 22.

Accordingly, the heat pump system 1 can dissipate heat to the high pressure refrigerant side using the exhaust heat of the compressor 11 in addition to the heat of the high pressure refrigerant in the water-refrigerant heat exchanger 12 as a heat source in the dehumidifying heating mode. Since it can do, the heating capacity of heat pump system 1 at the time of dehumidification heating mode can be improved.

As described above, according to the heat pump system 1 according to the first embodiment, the cooling mode, the heating mode, and the dehumidifying heating mode are realized among the plurality of operation modes by switching the refrigerant circuit of the heat pump cycle 10. And can perform comfortable air conditioning of the vehicle interior.

And in the said heat pump cycle 10, it does not switch with the refrigerant circuit which makes a high pressure refrigerant flow in the same heat exchanger, and the refrigerant circuit which makes a low pressure refrigerant flow. That is, since it is not necessary to cause the high pressure refrigerant to flow into the indoor evaporator 16 and the chiller 18 regardless of which refrigerant circuit is switched, the refrigerant circuit can be switched with a simple configuration without causing the complication of the cycle configuration.

In any of the operation modes, since the compressor 11 in the heat pump cycle 10 is operated, exhaust heat of the compressor 11 is generated. According to the heat pump system 1, the exhaust heat of the compressor 11 can be recovered via the high temperature side recovery section 25 of the high temperature side heat medium circuit 20 and can be used in the high temperature side heat medium circuit 20.

In the heat pump system 1, the high temperature side heat medium circuit 20 corresponds to the high temperature side heat receiving portion in the present disclosure, and the high temperature side recovery portion 25 corresponds to the recovery portion in the present disclosure.

With this configuration, the heat pump system 1 recovers the exhaust heat of the compressor 11 in the high temperature side recovery unit 25, transports the recovered heat, and uses the recovered heat in the high temperature side heat medium circuit 20, A high temperature side heat medium can be intervened, and the heat generation of the compressor 11 can be handled more efficiently.

Further, the high temperature side heat medium circuit 20 has a heater core 22. Therefore, the heat pump system 1 can use the exhaust heat of the compressor 11 recovered through the high temperature side recovery unit 25 for heating the blowing air, which is the heat exchange object, in the heating mode or the dehumidifying heating mode. The heating capacity for the heat exchange target fluid can be improved.

In the heat pump system 1, the high temperature side heat medium circuit 20 has the high temperature side radiator 23, so the heat of the high temperature side heat medium can be dissipated to the outside air. That is, the heat quantity of the high temperature side heat medium can be adjusted by the high temperature side radiator 23.

Therefore, the heat pump system 1 can adjust the heating capacity (that is, the heating capacity) for the blowing air which is the heat exchange target fluid. The heat pump system 1 can adjust it to a desired heating capacity while heating by effectively using the exhaust heat of the compressor 11.

As shown in FIG. 1, in the heat pump system 1, the heat pump cycle 10 includes an indoor evaporator 16 and a chiller 18. The indoor evaporator 16 evaporates by heat exchange between the refrigerant decompressed by the cooling expansion valve 15a and the blast air, and absorbs heat from the blast air to cool it. The chiller 18 absorbs heat from the low temperature side heat medium by heat exchange between the refrigerant decompressed by the heat absorption expansion valve 15 b and the low temperature side heat medium of the low temperature side heat medium circuit 30.

According to the heat pump system 1, by arranging these two heat sinks in the heat pump cycle 10, for example, heat exchange between the two different heat mediums such as the low temperature side heat medium and the blast air and the refrigerant is enabled. Can be adapted to various applications.

Furthermore, as shown in FIG. 2, in the high temperature side heat medium circuit 20 of the heat pump system 1, the high temperature side recovery unit 25 is configured by arranging a plurality of heat storage materials 25 b in the housing portion 25 a. That is, the high temperature side recovery unit 25 has the function of the heat storage unit according to the present disclosure.

According to the heat pump system 1, the exhaust heat of the compressor 11 can be stored in the heat storage material 25 b in the storage unit 25 a. And each thermal storage material 25b which comprises the thermal storage part 40 thermally radiates the heat stored thermally to the high temperature side heat medium, when the temperature of the high temperature side heat medium falls rather than the temperature defined beforehand.

Therefore, according to the heat pump system 1, the heat stored in the heat storage section 40 can be used in the high temperature side heat medium circuit 20 according to the temperature condition of the high temperature side heat medium. That is, the heat pump system 1 can flexibly utilize the exhaust heat of the compressor 11 according to the condition of the high temperature side heat medium.

(First modification)
In the first embodiment, the high temperature side branch portion 26 a and the high temperature side junction portion 27 a in the high temperature side heat medium circuit 20 are disposed on the outlet side of the water passage in the water-refrigerant heat exchanger 12. As shown, the high temperature side branch portion 26 a and the high temperature side junction portion 27 a may be disposed on the inlet side of the water passage in the water-refrigerant heat exchanger 12. In FIG. 4, the same or equivalent parts as in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

As shown in FIG. 4, on the inlet side of the water passage of the water-refrigerant heat exchanger 12, the high temperature side joining portion 27a is disposed downstream of the high temperature side branch portion 26a with respect to the flow of the high temperature side heat medium. . In the first modification, the arrangement of the high temperature side branch portion 26a and the high temperature side junction portion 27a corresponds to the difference from the first embodiment.

Therefore, the other configuration except this point is the same as that of the first embodiment. And operation of heat pump cycle 10 in the 1st modification, high temperature side heat carrier circuit 20, and low temperature side heat carrier circuit 30 is the same as that of an embodiment mentioned above.

Thus, in the first modification, the heat pump system 1 recovers the exhaust heat of the compressor 11 in the high temperature side recovery unit 25 using the high temperature side heat medium before flowing into the water-refrigerant heat exchanger 12 can do. Then, in the heat pump system 1, the high temperature side heat medium after recovering the exhaust heat of the compressor 11 is heated by the water-refrigerant heat exchanger 12 with the high pressure refrigerant.

According to the heat pump system 1 according to the first modification, the same advantages as those of the first embodiment can be obtained from the same configuration and operation as those of the first embodiment described above. That is, the heat pump system 1 can recover exhaust heat of the compressor 11 and use it effectively by using the high temperature side heat medium circuit 20 and the high temperature side recovery unit 25.

In the first embodiment and the first modification, depending on conditions such as the temperature of the high pressure refrigerant discharged from the compressor 11 and the temperature of the high temperature side heat medium at the time of joining at the high temperature side junction 27a, It can be selected appropriately. By selecting in accordance with these conditions, it is possible to more effectively utilize the exhaust heat of the compressor 11.

(2nd modification)
Further, in the first embodiment, the heat pump system 1 includes the heat pump cycle 10, the high temperature side heat medium circuit 20, and the low temperature side heat medium circuit 30, but the present invention is not limited to this configuration. . That is, as shown in FIG. 5, in the heat pump system 1 according to the first embodiment, the low temperature side heat medium circuit 30 can be eliminated.

In this case, the outdoor heat exchanger 18 a is disposed in place of the chiller 18 in the heat pump cycle 10. The outdoor heat exchanger 18a is an evaporation unit which causes the low pressure refrigerant to evaporate by heat exchange between the low pressure refrigerant flowing through the refrigerant passage and the outside air at least in the heating mode and the dehumidifying and heating mode.

That is, the outdoor heat exchanger 18a is a heat exchanger for absorbing heat that evaporates the low-pressure refrigerant and absorbs the heat of the outside air to the refrigerant at least in the heating mode and the dehumidifying and heating mode. The outdoor heat exchanger 18 a functions as a heat absorber in the present disclosure, and corresponds to any one of the first heat absorber and the second heat absorber.

As shown in FIG. 5, since the heat pump system 1 according to the second modification does not have the low temperature side heat medium circuit 30, the heat pump system 1 does not have the temperature adjustment function of the in-vehicle device 32. Hold The control contents of the heat pump cycle 10 and the high temperature side heat medium circuit 20 in the second modification are the same as those in the first embodiment, and thus the description thereof will be omitted.

Therefore, the heat pump system 1 according to the second modification can obtain the same effects and advantages as those of the first embodiment from the same configuration and operation as those of the first embodiment described above. That is, the heat pump system 1 can recover the exhaust heat of the compressor 11 and use it effectively by using the high temperature side heat medium circuit 20 and the high temperature side recovery unit 25.

(Third modification)
Subsequently, a third modification of the first embodiment will be described. As shown in FIG. 6, in the third modification, the high temperature side branch portion 26a and the high temperature side junction portion 27a are disposed on the inlet side of the water passage in the water-refrigerant heat exchanger 12.

Furthermore, in the third modification, the chiller 18 of the heat pump cycle 10 is replaced with an outdoor heat exchanger 18a, and the low temperature side heat medium circuit 30 is eliminated. That is, the third modification is a modification in which both the difference between the first modification and the difference between the second modification are applied to the first embodiment.

Therefore, the heat pump system 1 according to the third modification is the same as the first modification and the second modification described above in terms of functions and effects exhibited from the configuration and operation common to the first embodiment, the first embodiment. Can be obtained in the same way. That is, the heat pump system 1 can recover the exhaust heat of the compressor 11 and use it effectively by using the high temperature side heat medium circuit 20 and the high temperature side recovery unit 25.

Second Embodiment
Subsequently, a second embodiment different from the above-described first embodiment will be described with reference to FIG.

The heat pump system 1 which concerns on 2nd Embodiment is mounted in the electric vehicle similarly to 1st Embodiment. As shown in FIG. 7, the heat pump system 1 includes a heat pump cycle 10, a high temperature side heat medium circuit 20, and a low temperature side heat medium circuit 30, and further, an indoor air conditioning unit 50 and a control device 60. Etc.

In the second embodiment, the configurations of the high temperature side heat medium circuit 20 and the low temperature side heat medium circuit 30 are different from those of the first embodiment. That is, in 2nd Embodiment, the structure which concerns on the heat pump cycle 10, the indoor air-conditioning unit 50, and the control apparatus 60 is the same as that of 1st Embodiment.

The high temperature side heat medium circuit 20 according to the second embodiment includes the high temperature side heat medium pump 21, the heater core 22, the high temperature side radiator 23, and the high temperature side flow rate adjustment valve 24 as in the first embodiment. The configuration related to the circulation circuit of the high temperature side heat medium circuit 20 is the same. However, unlike the first embodiment, the high temperature side heat medium circuit 20 according to the second embodiment does not have the high temperature side recovery unit 25.

On the other hand, the low temperature side heat medium circuit 30 according to the second embodiment includes the low temperature side heat medium pump 31, the on-vehicle device 32, the low temperature side radiator 33, and the low temperature side flow rate adjustment valve 34 as in the first embodiment. The configuration of the low temperature side heat medium circuit 30 as a circulation circuit is the same.

As shown in FIG. 7, the low temperature side heat medium circuit 30 has a low temperature side recovery unit 35 for recovering and utilizing the exhaust heat of the compressor 11 unlike the first embodiment. The low temperature side recovery unit 35 has a low temperature side inflow piping 36 and a low temperature side outflow piping 37.

The low temperature side recovery unit 35 recovers the exhaust heat of the compressor 11 by absorbing heat from the low temperature side heat medium circulating through the low temperature side heat medium circuit 30, and the exhaust heat of the compressor 11 is recovered by the low temperature side heat medium circuit Accept to 30.

The low temperature side recovery unit 35 includes a storage unit (not shown), a low temperature side inflow piping 36, and a low temperature side outflow piping 37, which are mutually connected. Therefore, the storage portion in the low temperature side recovery unit 35, the low temperature side inflow piping 36, and the low temperature side outflow piping 37 constitute a flow path through which the low temperature side heat medium circulating in the low temperature side heat medium circuit 30 flows.

As shown in FIG. 7, the low temperature side inflow pipe 36 is a pipe branched from the low temperature side branch portion 36 a disposed on the inlet side of the water passage in the chiller 18. The low temperature side inflow piping 36 is connected to the housing portion of the low temperature side heat medium circuit 30. Therefore, in the low temperature side heat medium circuit 30, the flow of the low temperature side heat medium branched at the low temperature side branch portion 36a reaches the inside of the storage portion in the low temperature side recovery portion 35.

The low temperature side outflow piping 37 extends from the housing portion of the low temperature side recovery unit 35 and is connected to the low temperature side joining portion 37 a disposed in the circulation circuit of the low temperature side heat medium circuit 30. The low temperature side merging portion 37 a is located downstream of the low temperature side branch portion 36 a in the flow direction downstream of the low temperature side heat medium on the inlet side of the water passage in the chiller 18.

Therefore, the low temperature side heat medium flowing out from the storage portion of the low temperature side recovery unit 35 merges with the low temperature side heat medium circulating in the on-vehicle equipment 32 in the low temperature side heat medium circuit 30 at the inlet side of the water passage in the chiller 18 Do.

The housing portion of the low temperature side recovery portion 35 is formed to cover the outer surface of the compressor 11 similarly to the housing portion 25a of the high temperature side recovery portion 25 described with reference to FIG. A part of the refrigerant pipe connected to the compressor 11 is accommodated inside.

Therefore, the low temperature side heat medium that has flowed through the low temperature side inflow pipe 36 flows into the inside of the storage portion of the low temperature side recovery unit 35 and flows along the outer surface of the compressor 11. At this time, the low temperature side heat medium absorbs and recovers the exhaust heat of the compressor 11.

Thereafter, the low temperature side heat medium flows out from the housing portion of the low temperature side recovery unit 35 and joins the circulation circuit of the low temperature side heat medium circuit 30 via the low temperature side outflow piping 37. Thus, the low temperature side heat medium circuit 30 can recover and receive the exhaust heat of the compressor 11 through the flow of the low temperature side heat medium in the low temperature side recovery unit 35.

Here, a heat storage material (not shown) is disposed in the storage portion of the low temperature side recovery portion 35. The heat storage material is a latent heat storage material accompanied by a phase change at the time of heat storage, and is enclosed in a plurality of spherical resin or metal capsules.

The phase change temperature of the heat storage material in the low temperature side recovery unit 35 is determined to be higher than the temperature of the low temperature side heat medium flowing into the storage portion of the low temperature side recovery unit 35 with a predetermined temperature difference There is.

Then, the heat storage material in the low temperature side recovery unit 35 stores the exhaust heat of the compressor 11, and when the temperature of the low temperature side heat medium is lower than a predetermined temperature, the heat storage material stores heat in the low temperature side heat medium It is configured to dissipate heat.

In the inside of the storage unit in the low temperature side recovery unit 35, a large number of regenerator materials sealed in a capsule are disposed between the outer shell of the storage unit and the outer surface of the compressor 11. For this reason, the low temperature side heat medium flows through the gap of the capsule and flows to the low temperature side outflow piping 37 inside the storage portion of the low temperature side recovery unit 35.

As the heat storage material in the low temperature side recovery unit 35, for example, (water-based heat storage material, paraffin wax-based heat storage material, high-alcohol-based heat storage material, inorganic salt-based heat storage material) can be adopted. The water-based heat storage material contains water, hydrates and the like. And as a paraffin wax type heat storage material, C12 dodecane, C14 tetradecane, C16 pentadecane can be employ | adopted, for example.

Moreover, as a heat storage material of a higher alcohol type, for example, Diethylene glycol, Triethylene glycol, Tetrahydrofuran can be used. And, as the heat storage material of the inorganic salt type, for example, Tetrahydrofuran clathrate hydrate, KCl (19.5 wt%) + H2O, Dioctyllammonium iodide etc. can be adopted. Moreover, these mixed materials can be employ | adopted as the thermal storage material 25b.

Therefore, when the surroundings become higher than the heat storage temperature due to the exhaust heat of the compressor 11, the heat storage material of the low temperature side recovery unit 35 absorbs heat from the surroundings and changes in phase. Thus, the exhaust heat of the compressor 11 is stored in the heat storage material in the low temperature side recovery unit 35. Then, the heat storage material changes in sensible heat so as to approach the temperature of the low temperature side heat medium. When the temperature of the low temperature side heat medium becomes lower than the heat storage temperature, the heat storage material dissipates the waste heat of the stored compressor 11 to the low temperature side heat medium, and changes its phase.

Therefore, in the second embodiment, the low temperature side recovery unit 35 is configured as the heat storage unit 40 by arranging the heat storage material in the storage unit of the low temperature side recovery unit 35. The heat storage unit 40 in the second embodiment stores the exhaust heat of the compressor 11, and when the temperature of the low temperature side heat medium becomes lower than a predetermined heat storage temperature, the heat stored is stored on the low temperature side Heat is dissipated to the heat medium. That is, the heat storage unit 40 according to the second embodiment also functions as the heat storage unit in the present disclosure.

Subsequently, the operation of the heat pump system 1 according to the second embodiment will be described. Also in the heat pump system 1 according to the second embodiment, as in the first embodiment, the operation mode can be appropriately switched among a plurality of operation modes. Switching of these operation modes is performed by executing a control program stored in advance in the control device 60.

As can be seen from FIGS. 1 and 7, the heat pump cycle 10 according to the second embodiment has a circuit configuration similar to that of the heat pump cycle 10 according to the first embodiment. Further, the high temperature side heat medium circuit 20 according to the second embodiment has the same circuit configuration as that of the first embodiment except that the high temperature side recovery unit 25 is not provided. The low temperature side heat medium circuit 30 according to the second embodiment has the same circuit configuration as that of the first embodiment except that the low temperature side recovery unit 35 is included.

Therefore, the heat pump system 1 according to the second embodiment can realize the cooling mode, the heating mode, and the dehumidifying heating mode by performing the same control as that of the first embodiment. In the heat pump system 1, when operating in the cooling mode, the heating mode, and the dehumidifying heating mode, the compressor 11 is operated.

Thereby, according to the heat pump system 1 according to the second embodiment, in any operation mode, the low temperature side heat medium absorbs the exhaust heat of the compressor 11 by the low temperature side heat medium and recovers it. Thus, the exhaust heat of the compressor 11 can be stored by the heat storage material in the low temperature side recovery unit 35.

That is, according to the heat pump system 1, the exhaust heat of the compressor 11 is recovered and stored by the low temperature side heat medium or the heat storage material of the low temperature side recovery unit 35, and the exhaust heat of the compressor 11 is wasted. Can be effectively utilized through the heat pump cycle 10.

In the low temperature side heat medium circuit 30, the low temperature side branch portion 36 a and the low temperature side joining portion 37 a are disposed on the inlet side of the water passage in the chiller 18. That is, the temperature of the low temperature side heat medium flowing into the chiller 18 can be raised by the exhaust heat of the compressor 11.

As a result, according to the heat pump system 1 according to the second embodiment, it is possible to effectively utilize the exhaust heat of the compressor 11 in the heating mode or the dehumidifying heating mode to increase the heat absorption amount in the chiller 18.

As described above, according to the heat pump system 1 according to the second embodiment, the cooling mode, the heating mode, and the dehumidifying heating mode are realized among the plurality of operation modes by switching the refrigerant circuit of the heat pump cycle 10. And can perform comfortable air conditioning of the vehicle interior.

In any of the operation modes, since the compressor 11 in the heat pump cycle 10 is operated, exhaust heat of the compressor 11 is generated. According to the heat pump system 1, the exhaust heat of the compressor 11 can be recovered via the low temperature side recovery unit 35 of the low temperature side heat medium circuit 30 and can be used in the low temperature side heat medium circuit 30.

In the heat pump system 1, the low temperature side heat medium circuit 30 corresponds to the low temperature side heat receiving portion in the present disclosure, and the low temperature side recovery portion 35 corresponds to the recovery portion in the present disclosure.

With this configuration, the heat pump system 1 recovers the exhaust heat of the compressor 11 in the low temperature side recovery unit 35, transports the recovered heat, and uses the recovered heat in the low temperature side heat medium circuit 30, A low temperature side heat medium can be interposed, and the heat generation of the compressor 11 can be handled more efficiently.

The low temperature side heat medium circuit 30 includes the in-vehicle device 32. The low temperature side heat medium can absorb the heat of the in-vehicle device 32 generated along with the operation to cool the in-vehicle device 32. That is, according to the heat pump system 1, by using the heat pump cycle 10 and the low temperature side heat medium circuit 30, it is possible to effectively utilize the heat generated in the in-vehicle device 32 while adjusting the temperature of the in-vehicle device 32. .

Further, the low temperature side heat medium circuit 30 has the low temperature side radiator 33, and can absorb the heat of the outside air to the low temperature side heat medium. Thereby, the heat pump system 1 can use outside air as a heat source.

And since the low temperature side branch part 36a and the low temperature side junction part 37a are arranged on the inlet side of the water passage in the chiller 18, the low temperature side recovery part 35 is in the water passage in the chiller 18 in the low temperature side heat medium circuit 30. It is located on the entrance side.

As a result, according to the heat pump system 1, the low temperature side heat medium that has recovered the exhaust heat of the compressor 11 flows into the chiller 18, so the heat absorption amount in the chiller 18 can be increased.

As shown in FIG. 7, in the heat pump system 1 according to the second embodiment, the heat pump cycle 10 has an indoor evaporator 16 and a chiller 18. The indoor evaporator 16 evaporates by heat exchange between the refrigerant decompressed by the cooling expansion valve 15a and the blast air, and absorbs heat from the blast air to cool it. The chiller 18 absorbs heat from the low temperature side heat medium by heat exchange between the refrigerant decompressed by the heat absorption expansion valve 15 b and the low temperature side heat medium of the low temperature side heat medium circuit 30.

Furthermore, in the low temperature side heat medium circuit 30 of the heat pump system 1 according to the second embodiment, the low temperature side recovery unit 35 has a plurality of heat storage inside the storage unit, similar to the high temperature side recovery unit 25 according to the first embodiment. The material is arranged. That is, the low temperature side recovery unit 35 according to the second embodiment has the function of the heat storage unit according to the present disclosure.

According to the heat pump system 1, the exhaust heat of the compressor 11 can be stored in the heat storage material disposed in the storage portion of the low temperature side recovery unit 35, and the temperature of the low temperature side heat medium is predetermined. When the temperature is lower than the temperature which has been stored, the heat stored can be dissipated to the low temperature side heat medium.

Therefore, according to the heat pump system 1, the heat stored in the heat storage section 40 can be used in the low temperature side heat medium circuit 30 according to the temperature condition of the low temperature side heat medium. That is, the heat pump system 1 can flexibly utilize the exhaust heat of the compressor 11 according to the condition of the low temperature side heat medium.

(Modification)
The heat pump system 1 according to the second embodiment includes the heat pump cycle 10, the high temperature side heat medium circuit 20, and the low temperature side heat medium circuit 30, but is not limited to this configuration. That is, as shown in FIG. 8, in the heat pump system 1 according to the second embodiment, the high temperature side heat medium circuit 20 can be eliminated.

In this case, in place of the water-refrigerant heat exchanger 12 in the heat pump cycle 10, an indoor condenser 12a is disposed. The indoor condenser 12 a is disposed in the casing 51 of the indoor air conditioning unit 50 at the same position as the heater core 22 in the first embodiment.

The indoor condenser 12a is a heat exchanger that radiates the heat of the high-pressure refrigerant and heats the blowing air with respect to the blowing air blown by the blower 52 at least in the heating mode and the dehumidifying and heating mode.

As shown in FIG. 8, the heat pump system 1 according to the modification has a temperature adjustment function of the in-vehicle device 32 and can realize the heating mode and the dehumidifying heating mode among the air conditioning functions of the vehicle interior. . The control contents of the heat pump cycle 10 and the low temperature side heat medium circuit 30 in the modified example have already been described, and thus the description thereof is omitted.

Therefore, the heat pump system 1 which concerns on a modification can obtain the effect show | played from a structure and operation | movement common to 2nd Embodiment mentioned above similarly to 2nd Embodiment. That is, the heat pump system 1 can recover exhaust heat of the compressor 11 and use it effectively by using the low temperature side heat medium circuit 30 and the low temperature side recovery unit 35.

Third Embodiment
Next, a third embodiment different from the above-described embodiments will be described with reference to FIG.

The heat pump system 1 which concerns on 3rd Embodiment is mounted in an electric vehicle similarly to each embodiment mentioned above. As shown in FIG. 9, the heat pump system 1 includes a heat pump cycle 10, a high temperature side heat medium circuit 20, and a low temperature side heat medium circuit 30, and further, an indoor air conditioning unit 50 and a control device 60. Etc.

In the third embodiment, the configurations of the high temperature side heat medium circuit 20 and the low temperature side heat medium circuit 30 are different. That is, in the third embodiment, the configuration relating to the heat pump cycle 10, the indoor air conditioning unit 50, and the control device 60 is the same as that of the embodiment described above.

The high temperature side heat medium circuit 20 according to the third embodiment includes the high temperature side heat medium pump 21, the heater core 22, the high temperature side radiator 23, and the high temperature side flow rate adjustment valve 24 as in the above-described embodiment. The configuration related to the circulation circuit of the high temperature side heat medium circuit 20 is the same.

The high temperature side heat medium circuit 20 according to the third embodiment has the high temperature side recovery unit 25 as in the first embodiment. The high temperature side recovery unit 25 has a housing portion 25 a, a high temperature side inflow piping 26, and a high temperature side outflow piping 27.

As shown in FIG. 9, the storage portion 25a of the high temperature side recovery portion 25 according to the third embodiment is configured to cover about half of the outer surface of the compressor 11, and a plurality of heat storage materials 25b are provided therein. Is arranged. The heat storage material of the high temperature side recovery unit 25 according to the third embodiment basically has the same configuration as the heat storage material 25 b in the first embodiment.

In the third embodiment, the high temperature side branch portion 26 a and the high temperature side junction portion 27 a are disposed on the high temperature side heat medium circuit 20 on the inlet side of the water passage in the water-refrigerant heat exchanger 12. Therefore, at the inlet side of the water passage in the water-refrigerant heat exchanger 12, the high temperature side heat medium flows into the storage portion of the high temperature side recovery unit 25 via the high temperature side inflow pipe 26 to discharge the exhaust heat of the compressor 11. Heat sink.

Then, the high temperature side heat medium which absorbed the exhaust heat of the compressor 11 flows out through the high temperature side outflow pipe 27, merges at the high temperature side joining portion 27a, and flows into the water-refrigerant heat exchanger 12. Therefore, also in the third embodiment, the high temperature side recovery unit 25 can recover a part of the exhaust heat of the compressor 11 via the high temperature side heat medium and can be received by the high temperature side heat medium circuit 20 .

Further, the low temperature side heat medium circuit 30 according to the third embodiment includes the low temperature side heat medium pump 31, the on-vehicle device 32, the low temperature side radiator 33, and the low temperature side flow rate adjustment valve 34 as in the embodiment described above. The configuration of the low temperature side heat medium circuit 30 as a circulation circuit is the same.

The low temperature side heat medium circuit 30 according to the third embodiment includes the low temperature side recovery unit 35 as in the second embodiment. The low temperature side recovery unit 35 includes a storage unit, a low temperature side inflow piping 36, and a low temperature side outflow piping 37.

The housing portion of the low temperature side recovery portion 35 according to the third embodiment is a portion of the outer surface of the compressor 11 not covered by the housing portion 25 a of the high temperature side recovery portion 25 (ie, the outer surface of the compressor 11 The other half (about half) is covered, and a plurality of heat storage materials are arranged in the inside. The heat storage material of the low temperature side recovery unit 35 according to the third embodiment has basically the same configuration as the heat storage material in the second embodiment.

In the third embodiment, the low temperature side branch portion 36 a and the low temperature side joining portion 37 a are disposed on the inlet side of the water passage in the chiller 18 in the low temperature side heat medium circuit 30. Therefore, on the inlet side of the water passage in the chiller 18, the low temperature side heat medium flows into the storage portion of the low temperature side recovery unit 35 via the low temperature side inflow pipe 36, and absorbs the exhaust heat of the compressor 11.

Then, the low temperature side heat medium which absorbs the exhaust heat of the compressor 11 flows out through the low temperature side outflow pipe 37, joins at the low temperature side joining portion 37a and flows into the chiller 18. Therefore, also in the third embodiment, the low temperature side recovery unit 35 can recover a part of the exhaust heat of the compressor 11 via the low temperature side heat medium and can be received by the low temperature side heat medium circuit 30. .

Subsequently, the operation of the heat pump system 1 according to the third embodiment will be described. Also in the heat pump system 1 according to the third embodiment, the operation mode can be appropriately switched among the plurality of operation modes, as in the above-described embodiment. The switching of these operation modes is performed by executing a control program stored in advance in the control device 60.

As can be seen from FIG. 9, the heat pump cycle 10 according to the third embodiment has the same circuit configuration as the heat pump cycle 10 in the embodiment described above. Further, the high temperature side heat medium circuit 20 according to the third embodiment has the same circuit configuration as that of the first embodiment. The low temperature side heat medium circuit 30 according to the third embodiment has the same circuit configuration as that of the second embodiment.

Therefore, the heat pump system 1 according to the third embodiment can realize the cooling mode, the heating mode, and the dehumidifying heating mode by performing the same control as that of the above-described embodiment. In the heat pump system 1, when operating in the cooling mode, the heating mode, and the dehumidifying heating mode, the compressor 11 is operated.

Thereby, according to the heat pump system 1 according to the third embodiment, the exhaust heat of the compressor 11 is absorbed and recovered by the high temperature side heat medium in the high temperature side recovery unit 25 in any operation mode, and In the low temperature side recovery unit 35, the exhaust heat of the compressor 11 can be absorbed by the low temperature side heat medium and recovered.

Then, according to the heat pump system 1, the exhaust heat of the compressor 11 is stored by the heat storage material in the high temperature side recovery unit 25, and the heat stored in accordance with the temperature condition of the high temperature side heat medium Can be used. At the same time, the heat pump system 1 can store the exhaust heat of the compressor 11 with the heat storage material in the low temperature side recovery unit 35, and the heat stored in accordance with the temperature condition of the low temperature side heat medium It can be used.

That is, according to the heat pump system 1 according to the third embodiment, the exhaust heat of the compressor 11 is not wasted in the high temperature side heat medium circuit 20 and the low temperature side heat medium circuit 30, respectively. Can be used effectively.

On the high temperature side heat medium circuit 20 side, the temperature of the high temperature side heat medium is raised by the exhaust heat of the compressor 11 collected by the high temperature side collection unit 25. That is, according to the heat pump system 1, the exhaust heat of the compressor 11 can be used in addition to the heat of the high-pressure refrigerant in the water-refrigerant heat exchanger 12 as a heat source in the heating mode or the dehumidifying heating mode. The heating capacity of the heat pump system 1 in the heating mode or the dehumidifying heating mode can be improved.

Further, on the low temperature side heat medium circuit 30 side, the temperature of the low temperature side heat medium flowing into the chiller 18 is raised by the exhaust heat of the compressor 11 recovered by the low temperature side recovery unit 35. According to the heat pump system 1, it is possible to effectively utilize the exhaust heat of the compressor 11 in the heating mode or the dehumidifying heating mode to increase the heat absorption amount in the chiller 18.

As described above, according to the heat pump system 1 according to the third embodiment, the effects and advantages exhibited from the configuration and operation common to the first embodiment and the second embodiment described above are described. It can be obtained in the same manner as in the second embodiment.

That is, the heat pump system 1 can recover the exhaust heat of the compressor 11 using the high temperature side heat medium circuit 20 and the high temperature side recovery unit 25, and can effectively utilize the heat in the high temperature side heat medium circuit 20. At the same time, the heat pump system 1 can recover the exhaust heat of the compressor 11 using the low temperature side heat medium circuit 30 and the low temperature side recovery unit 35, and can effectively use the waste heat in the low temperature side heat medium circuit 30.

Further, according to the heat pump system 1, utilization of the exhaust heat of the compressor 11 on the high temperature side heat medium circuit 20 side and utilization of the exhaust heat of the compressor 11 on the low temperature side heat medium circuit 30 side are realized in parallel. Since the exhaust heat of the compressor 11 can be used more effectively.

Fourth Embodiment
Next, a fourth embodiment different from the above-described embodiments will be described with reference to FIG.

The heat pump system 1 which concerns on 4th Embodiment is mounted in the electric vehicle similarly to each embodiment mentioned above. As shown in FIG. 10, the heat pump system 1 includes a heat pump cycle 10, a high temperature side heat medium circuit 20, and a low temperature side heat medium circuit 30, and further, an indoor air conditioning unit 50 and a control device 60. Etc.

In the fourth embodiment, the configuration of the heat pump cycle 10 is different. That is, in the fourth embodiment, configurations relating to the high temperature side heat medium circuit 20, the low temperature side heat medium circuit 30, the indoor air conditioning unit 50, and the control device 60 are the same as those in the first embodiment described above.

As shown in FIG. 10, in the heat pump cycle 10 according to the fourth embodiment, the arrangement of the cooling expansion valve 15a, the heat absorption expansion valve 15b, the indoor evaporator 16, and the chiller 18 is different from that of the first embodiment described above. There is. That is, also in the fourth embodiment, the inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11.

A cooling expansion valve 15 a is connected to the refrigerant outlet side of the water-refrigerant heat exchanger 12. Similar to the first embodiment, the cooling expansion valve 15a is an electric expansion valve, and has a fully open function and a fully closed function. The cooling expansion valve 15a has both a function as a pressure reducing unit that reduces the pressure of the refrigerant and a function as a circuit switching unit that switches the refrigerant circuit.

In the fourth embodiment, the refrigerant inlet side of the indoor evaporator 16 is connected to the outlet of the cooling expansion valve 15a via the three-way valve 16b. The indoor evaporator 16 is a cooling evaporator that exchanges heat between the low pressure refrigerant and the blowing air to evaporate the low pressure refrigerant and cool the blowing air.

As shown in FIG. 10, a heat absorption expansion valve 15 b is connected to the refrigerant outlet of the indoor evaporator 16. As in the first embodiment, the heat absorption expansion valve 15b is an electric expansion valve, and has a fully open function and a fully closed function. The heat absorption expansion valve 15 b has both a function as a pressure reducing unit that reduces the pressure of the refrigerant and a function as a circuit switching unit that switches the refrigerant circuit.

Here, a three-way valve 16 b is disposed between the outlet of the cooling expansion valve 15 a and the refrigerant inlet side of the indoor evaporator 16. A bypass passage 16a is connected to one outlet of the three-way valve 16b. The other end side of the bypass flow passage 16 a is connected between the refrigerant outlet side of the indoor evaporator 16 and the inlet of the heat absorption expansion valve 15 b.

Therefore, by controlling the operation of the three-way valve 16 b, it is possible to switch between the flow path through which the refrigerant passes through the indoor evaporator 16 and the flow path through which the refrigerant bypasses the indoor evaporator 16. The three-way valve 16b is controlled by the circuit switching control unit 60b.

The refrigerant inlet side of the chiller 18 is connected to the outlet of the heat absorption expansion valve 15b. The chiller 18 exchanges heat between the low pressure refrigerant decompressed by the heat absorption expansion valve 15b and the low temperature side heat medium of the low temperature side heat medium circuit 30 in the heating mode, the dehumidifying heating mode, etc. to evaporate the low pressure refrigerant. It is an endothermic evaporator that causes the refrigerant to exhibit an endothermic effect.

The suction port side of the compressor 11 is connected to the refrigerant outlet side of the chiller 18. That is, in the heat pump cycle 10 according to the fourth embodiment, the indoor evaporator 16 and the chiller 18 are connected in series. The control system of the heat pump system 1 according to the fourth embodiment is basically the same as that of the first embodiment, and thus the description thereof is omitted.

Subsequently, the operation of the heat pump system 1 in the fourth embodiment will be described. The heat pump system 1 switches the cooling mode, the heating mode, and the dehumidifying heating mode according to the air conditioning control program stored in advance, as in the above-described embodiment.

The operation in the cooling mode, the operation in the heating mode, and the operation in the dehumidifying heating mode according to the fourth embodiment will be described below.

(A) Cooling Mode In the cooling mode, the control device 60 opens the cooling expansion valve 15a at a predetermined throttle opening degree, and brings the heat absorption expansion valve 15b into a fully open state. Also, the three-way valve 16b is controlled to close the bypass flow passage 16a. As a result, the refrigerant flowing out of the cooling expansion valve 15 a flows into the indoor evaporator 16.

Accordingly, in the heat pump cycle 10 in the cooling mode according to the fourth embodiment, the compressor 11 → water-refrigerant heat exchanger 12 → cooling expansion valve 15a → three-way valve 16b → indoor evaporator 16 → heat absorption expansion valve 15b → chiller A vapor compression refrigeration cycle in which the refrigerant circulates in the order of 18 → 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 based on the target blowout temperature TAO and the detection signal of the sensor group.

For example, the control device 60 controls the operation of the high temperature side heat medium pump 21 and the high temperature side flow rate adjustment valve 24 in the high temperature side heat medium circuit 20 as in the first embodiment. As a result, in the high temperature side heat medium circuit 20, the entire flow rate of the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 enters the high temperature side radiator 23.

Further, the control device 60 also controls the low temperature side heat medium pump 31 and the low temperature side flow rate adjustment valve 34 in the low temperature side heat medium circuit 30 in the same manner as in the first embodiment. The control device 60 appropriately controls the operation of other various control target devices.

Therefore, also in the fourth embodiment, 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 operates, 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.

The high pressure refrigerant cooled in the refrigerant passage of the water-refrigerant heat exchanger 12 flows into the cooling expansion valve 15a and is decompressed. The throttle opening degree of the cooling expansion valve 15a is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is approximately 3 ° C.

The low pressure refrigerant reduced in pressure by the cooling expansion valve 15 a 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 which is a heat exchange object fluid is cooled.

The refrigerant flowing out of the indoor evaporator 16 flows into the chiller 18 without being decompressed by the heat absorption expansion valve 15b. Then, the refrigerant is sucked into the compressor 11 and compressed again, with little heat exchange in the chiller 18.

Therefore, in the cooling mode in the fourth embodiment, cooling of the vehicle interior can be performed by blowing out the blown air cooled by the indoor evaporator 16 into the vehicle interior.

Also in the cooling mode according to the fourth embodiment, with the operation of the compressor 11, the exhaust heat of the compressor 11 is generated. Similar to the above-described embodiment, in the high temperature side recovery unit 25, the exhaust heat of the compressor 11 can be absorbed by the high temperature side heat medium and recovered, and furthermore, the exhaust heat of the compressor 11 is obtained by the heat storage material 25b. It can be stored heat.

That is, according to the heat pump system 1, the exhaust heat of the compressor 11 can be recovered and stored by the high temperature side heat medium of the high temperature side recovery unit 25 and the heat storage material 25b, and can be used appropriately.

(B) Heating mode In the heating mode, the control device 60 fully opens the cooling expansion valve 15a, and opens the heat absorption expansion valve 15b at a predetermined opening degree. At this time, the three-way valve 16b is controlled to fully open the bypass flow passage 16a. As a result, the refrigerant that has passed through the cooling expansion valve 15a flows into the heat absorption expansion valve 15b via the bypass flow path 16a without flowing into the indoor evaporator 16.

Therefore, in the heat pump cycle 10 in the heating mode, the refrigerant circulates in the following order: compressor 11 → water-refrigerant heat exchanger 12 → three-way valve 16 b → bypass flow path 16 a → heat absorption expansion valve 15 b → chiller 18 → compressor 11 A vapor compression refrigeration cycle is configured. That is, in the heating mode, the refrigerant circuit is switched to a refrigerant circuit aiming to heat the blowing air using the heat absorbed by the chiller 18.

Then, in this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side based on the target blowout temperature TAO and the detection signal of the sensor group. For example, the throttle opening degree of the heat absorption expansion valve 15b is determined based on the target blowout temperature TAO or the like with reference to the control map regarding the heating mode.

Further, the control device 60 controls the operation of the high temperature side heat medium pump 21 and the high temperature side flow rate adjustment valve 24 in the high temperature side heat medium circuit 20 as in the first embodiment. As a result, in the high temperature side heat medium circuit 20, the entire 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.

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 operates, 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.

The high pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 flows into the cooling expansion valve 15a. At this time, since the cooling expansion valve 15a is fully open, the high pressure refrigerant flows into the three-way valve 16b and flows through the bypass flow passage 16a without being decompressed. Therefore, in the heating mode, the high pressure refrigerant bypasses the indoor evaporator 16 and flows into the heat absorption expansion valve 15b.

Then, since the high pressure refrigerant flowing into the heat absorption expansion valve 15b is controlled to a predetermined throttle opening degree, the pressure is reduced until it becomes a low pressure refrigerant. The low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15 b flows into the chiller 18.

Here, in the low temperature side heat medium circuit 30, the low temperature side heat medium circulates in the circulation circuit by the operation of the low temperature side heat medium pump 31. The low temperature side heat medium absorbs heat generated in the in-vehicle device 32 when passing through the water passage of the in-vehicle device 32.

Further, when passing through the low temperature side radiator 33, the low temperature side heat medium absorbs heat from the outside air blown by the outside air fan. That is, the low temperature side heat medium flows into the water passage of the chiller 18 in a state where the heat is absorbed by the on-vehicle device 32 and the low temperature side radiator 33.

Therefore, the low pressure refrigerant flowing into the chiller 18 absorbs heat from the low temperature side heat medium having the heat of the on-vehicle device 32 and the heat of the outside air and evaporates. The refrigerant flowing out of the chiller 18 is sucked into the compressor 11 as it is and compressed again.

Therefore, in the heating mode, heating the blown air to the vehicle interior by heating the blown air by the heater core 22 can heat the vehicle interior. That is, in the heating mode, the heat pump system 1 pumps up the heat absorbed from the on-vehicle device 32 or the outside air in the low temperature side heat medium circuit 30 in the heat pump cycle 10, and sends the blown air through the high temperature side heat medium circuit 20. It can be used to heat the

And also in heating mode concerning a 4th embodiment, operation of compressor 11 in heat pump cycle 10 becomes required, and exhaust heat of compressor 11 is generated. The heat pump system 1 can recover the exhaust heat of the compressor 11 through the high temperature side heat medium in the high temperature side recovery unit 25 of the high temperature side heat medium circuit 20.

According to the heat pump system 1 according to the fourth embodiment, the exhaust heat of the compressor 11 is used in addition to the heat of the high-pressure refrigerant including the heat pumped up from the low temperature side heat medium circuit 30 as in the first embodiment. The high temperature side heat medium of the high temperature side heat medium circuit 20 can be heated, and the heat can be released to the blast air by the heater core 22.

Thereby, the heat pump system 1 can utilize the exhaust heat of the compressor 11 in addition to the heat of the high-pressure refrigerant in the water-refrigerant heat exchanger 12 as a heat source in the heating mode. Ability can be improved.

(C) Dehumidifying and heating mode In the dehumidifying and heating mode, the control device 60 opens the cooling expansion valve 15a and the heat absorption expansion valve 15b at a predetermined opening degree. At this time, the three-way valve 16b is controlled to close the bypass flow passage 16a. Thus, the refrigerant that has passed through the cooling expansion valve 15a flows into the indoor evaporator 16 without flowing into the bypass flow passage 16a.

Accordingly, in the heat pump cycle 10 in the dehumidifying and heating mode, the compressor 11 → water-refrigerant heat exchanger 12 → cooling expansion valve 15a → three-way valve 16b → indoor evaporator 16 → heat absorption expansion valve 15b → chiller 18 → compressor 11 In this order, a vapor compression type refrigeration cycle in which the refrigerant circulates is configured.

That is, in the dehumidifying and heating mode, the blown air cooled by the indoor evaporator 16 is switched to a refrigerant circuit that is intended to heat using the heat absorbed by the chiller 18.

Then, in this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side based on the target blowout temperature TAO and the detection signal of the sensor group. For example, the throttle opening degree of the cooling expansion valve 15a and the heat absorption expansion valve 15b is determined based on the target blowing temperature TAO or the like with reference to the control map related to the dehumidifying and heating mode.

Further, the control device 60 controls the operation of the high temperature side heat medium pump 21 and the high temperature side flow rate adjustment valve 24 in the high temperature side heat medium circuit 20 as in the first embodiment. Further, the control device 60 also controls the low temperature side heat medium pump 31 and the low temperature side flow rate adjustment valve 34 in the low temperature side heat medium circuit 30 in the same manner as in the first embodiment. The control device 60 appropriately controls the operation of other various control target devices.

Further, part of the high temperature side heat medium flows into the high temperature side radiator 23 by the operation of the high temperature side flow control 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. The high temperature side heat medium 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 flows into the cooling expansion valve 15a and is decompressed. The low pressure refrigerant decompressed by the cooling expansion valve 15a passes through the three-way valve 16b, flows into the indoor evaporator 16, absorbs heat from the air blown from the blower 52, and evaporates. Thereby, the blowing air which is a heat exchange object fluid is cooled.

Then, the low pressure refrigerant flowing out of the indoor evaporator 16 flows into the heat absorption expansion valve 15b and is further depressurized. The low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15 b flows into the chiller 18.

Here, also in the dehumidifying and heating mode, in the low temperature side heat medium circuit 30, the low temperature side heat medium circulates in the circulation circuit by the operation of the low temperature side heat medium pump 31. The low temperature side heat medium absorbs heat generated in the in-vehicle device 32 when passing through the water passage of the in-vehicle device 32.

Therefore, in the dehumidifying and heating mode, dehumidifying and heating the passenger compartment can be performed by heating the blown air cooled by the indoor evaporator 16 with the heater core 22 and blowing it out into the passenger compartment. That is, even in the dehumidifying and heating mode, the heat pump system 1 pumps up the heat absorbed by the low-temperature side heat medium circuit 30 from the on-vehicle device 32 or the outside air in the heat pump cycle 10 and via the high temperature side heat medium circuit 20 It can be used to heat the blast air.

And also in the said dehumidification heating mode, the action | operation of the compressor 11 in the heat pump cycle 10 is needed, and the exhaust heat of the compressor 11 generate | occur | produces. The heat pump system 1 can recover the exhaust heat of the compressor 11 through the high temperature side heat medium in the high temperature side recovery unit 25 of the high temperature side heat medium circuit 20.

As a result, the heat pump system 1 can utilize the exhaust heat of the compressor 11 in addition to the heat of the high-pressure refrigerant in the water-refrigerant heat exchanger 12 as a heat source in the dehumidifying heating mode. The heating capacity of the heat pump system 1 can be improved.

As described above, according to the heat pump system 1 of the fourth embodiment, the same advantages as those of the first embodiment can be obtained from the configuration and operation common to those of the first embodiment described above. .

That is, the heat pump system 1 according to the fourth embodiment has the high temperature side heat medium circuit 20 and the high temperature side even when the heat pump cycle 10 is configured such that the indoor evaporator 16 and the chiller 18 are connected in series. The exhaust heat of the compressor 11 can be recovered and effectively used by using the recovery unit 25.

In the heat pump cycle 10 in the fourth embodiment, the bypass flow passage 16a and the three-way valve 16b are disposed to suppress heat exchange (that is, cooling of the blown air) in the indoor evaporator 16 in the heating mode or the like. Although the indoor evaporator 16 is bypassed to flow the refrigerant, the present invention is not limited to this aspect.

For example, as long as heat exchange with the blowing air in the indoor evaporator 16 can be prevented, the flow path of the blowing air may be switched so that the blowing air bypasses the indoor evaporator 16. Specifically, a shutter device that can be opened and closed can be disposed between the blower 52 and the indoor evaporator 16, and a bypass flow channel that bypasses the indoor evaporator 16 may be formed in the casing 51.

Moreover, although the heat pump system 1 which concerns on 4th Embodiment was an example which changed the structure of the heat pump cycle 10 in 1st Embodiment, the embodiment etc. which mentioned the structure of the heat pump cycle 10 which concerns on 4th Embodiment were mentioned. It is also possible to apply. That is, the heat pump cycle 10 according to the fourth embodiment may be applied to the heat pump cycle 10 in the first to third modifications of the first embodiment shown in FIGS. 4 to 6.

Further, the heat pump cycle 10 according to the fourth embodiment is applied to the heat pump cycle 10 in the second embodiment shown in FIGS. 7 and 8 and its modification, or the heat pump cycle 10 according to the third embodiment shown in FIG. It is also possible to apply to In any case, the same advantages as those of the above-described embodiment can be obtained from the same configuration and operation as those of the above-described embodiment.

Although the present disclosure has been described above based on the embodiments, the present disclosure is not limited to the above-described embodiments. That is, various improvements and modifications are possible without departing from the scope of the present disclosure. For example, the above-described embodiments may be combined as appropriate, or various modifications of the above-described embodiments may be made.

In the embodiment described above, the high temperature side recovery unit 25 as a heat recovery unit according to the present disclosure includes the high temperature side inflow piping 26 that causes the high temperature side heat medium to branch at the high temperature side branch unit 26a, and the high temperature side junction unit 27a. And a high temperature side outflow pipe 27 for joining the high temperature side heat mediums.

The low temperature side recovery unit 35 further includes a low temperature side inflow pipe 36 for branching the low temperature side heat medium at the low temperature side branch portion 36a, and a low temperature side outflow pipe 37 for joining the low temperature side heat medium at the low temperature side merging portion 37a. have.

That is, in the embodiment described above, the flow of the heat medium for recovering the exhaust heat of the compressor 11 in the heat recovery unit and the flow of the heat medium circulating in the heat medium circuit are arranged in parallel. However, it is not limited to this aspect. For example, the entire amount of the heat medium flowing in the heat medium circuit flows into the storage portion of the heat recovery unit, and after the exhaust heat of the compressor 11 is recovered in the storage portion, flows into the components of the heat medium circuit May be

An example in which this configuration is applied to the second embodiment is shown in FIG. As shown in FIG. 11, a low temperature side inflow pipe 36 is connected to the discharge port side of the low temperature side heat medium pump 31. At this time, since the low temperature side branch portion 36 a is not disposed as in the second embodiment, the entire amount of the low temperature side heat medium flows into the low temperature side inflow pipe 36.

Since the low temperature side inflow piping 36 is connected to the housing portion of the low temperature side recovery unit 35, the low temperature side heat medium that has flowed into the housing portion absorbs the exhaust heat of the compressor 11 and flows out to the low temperature side outflow piping 37 Do. The low temperature side outflow piping 37 is connected to the inlet side of the water passage in the chiller 18.

That is, according to the example shown in FIG. 11, the entire low temperature side heat medium in the low temperature side heat medium circuit 30 is compressed by the low temperature side recovery unit 35 via the low temperature side inflow piping 36 and the low temperature side outflow piping 37 It absorbs the exhaust heat of the machine 11. Even in the case of such a configuration, the same effects as those of the above-described embodiments can be obtained.

In addition, although the case where it applied to 2nd Embodiment shown in FIG. 7 was demonstrated in FIG. 11, applying to each embodiment and each modification which were not limited to this aspect and was mentioned above Is also possible.

Moreover, although the high temperature side heat medium circuit 20 in embodiment mentioned above connected the heater core 22 and the high temperature side radiator 23 in parallel regarding the flow of the high temperature side heat medium, it is not limited to this aspect.

For example, as the high temperature side heat medium circuit 20, it is also possible to adopt the configuration shown in FIG. In the high temperature side heat medium circuit 20 shown in FIG. 12, the outlet side of the high temperature side heat medium pump 21 is connected to the inlet side of the water passage in the water-refrigerant heat exchanger 12. The inlet side of the heater core 22 is connected to the outlet side of the water passage in the water-refrigerant heat exchanger 12.

The outlet side of the heater core 22 is connected to the inlet of the high temperature side flow control valve 24. The inlet side of the high temperature side radiator 23 is connected to one of the outlets of the high temperature side flow control valve 24, and the high temperature side bypass flow path 24 a is connected to the other of the outlet of the high temperature side flow adjustment valve 24. There is.

The other end side of the high temperature side bypass flow passage 24 a is connected to the outlet side of the high temperature side radiator 23. The other end side of the high temperature side bypass flow passage 24 a and the outlet side of the high temperature side radiator 23 are connected to the suction port side of the high temperature side heat medium pump 21.

That is, as shown in FIG. 12, a configuration in which the heater core 22 and the high temperature side radiator 23 are connected in series can be adopted as the high temperature side heat medium circuit 20. Even when the high temperature side heat medium circuit 20 according to each of the above-described embodiments is configured as shown in FIG. 12, each heat pump system 1 provides the same advantages as the above-described embodiments. Can be obtained in the same manner as each embodiment.

And in embodiment mentioned above, thermal storage part 40 is arrange | positioned with respect to the inside of the accommodating part which comprises a heat recovery part like the high temperature side collection part 25 shown, for example in FIG. However, the present invention is not limited to this aspect. The heat storage unit 40 in the present disclosure can adopt various modes as long as the heat exhaust from the compressor 11 can be stored.

For example, as in FIG. 2, the high temperature side recovery unit 25 will be described as an example. As shown in FIG. 13, the heat accumulator 45 may be disposed in the high temperature side outflow pipe 27 in the high temperature side recovery unit 25. The heat storage unit 45 is configured of a container 45a to which the high temperature side outflow piping 27 is connected, and a plurality of heat storage materials 45b disposed in the container 45a. The heat storage material 45 b has the same configuration as the heat storage material 25 b in the first embodiment.

Therefore, according to the configuration shown in FIG. 11, the high temperature side heat medium flowing through the high temperature side inflow pipe 26 absorbs the exhaust heat of the compressor 11 by flowing around the compressor 11 in the housing portion 25a. . Then, the high temperature side heat medium flows out from the housing portion 25 a to the high temperature side outflow pipe 27.

The high temperature side heat medium flowing through the high temperature side outflow piping 27 flows into the inside of the container 45 a of the heat accumulator 45. The high temperature side heat medium flows from the high temperature side outflow piping 27 to the high temperature side heat medium circuit 20 through the gap of the capsule-like heat storage material 45 b in the container 45 a of the heat accumulator 45.

At this time, since the high temperature side heat medium is heated by the exhaust heat of the compressor 11 in the housing portion 25a, each heat storage material 45b in the heat accumulator 45 can be replaced by the heat storage material 45b if the heat storage temperature condition is satisfied. Exhaust heat can be stored. That is, the heat storage unit 45 illustrated in FIG. 11 functions as a heat storage unit in the present disclosure.

Although FIG. 11 describes the case where the heat storage unit 45 is adopted as the heat storage portion in the high temperature side heat medium circuit 20, it is also possible to adopt it as the heat storage portion in the low temperature side heat medium circuit 30. In this case, the container 45 a of the heat accumulator 45 is desirably disposed in the low temperature side outflow pipe 37. Further, as the heat storage material 45b in this case, the heat storage material according to the second embodiment is employed.

In the embodiment described above, the high temperature side heat medium circuit 20 is adopted as the high temperature side heat receiving portion according to the present disclosure, and the low temperature side heat medium circuit 30 is adopted as the low temperature side heat receiving portion according to the present disclosure. However, the present invention is not limited to this aspect.

The high temperature side heat receiving unit and the low temperature side heat receiving unit according to the present disclosure may be capable of receiving the exhaust heat of the compressor 11 recovered by the recovery unit, and is not limited to the heat medium circuit. For example, a metal block or the like can be used as the high temperature side heat receiving portion or the low temperature side heat receiving portion.

And in embodiment mentioned above, as shown to FIG. 2, FIG. 13, at least one part of the compressor 11 is arrange | positioned inside the accommodating part 25a which comprises a collection | recovery part, and the circumference of the said compressor 11 is Although the exhaust heat of the compressor 11 is recovered by the flowing heat medium, it is not limited to this aspect.

For example, as a configuration of the recovery unit according to the present disclosure, the heat medium pipe is disposed in contact with the outer surface of the compressor 11, and the exhaust heat of the compressor 11 is used as the heat medium via the heat medium pipe. It is also possible to make it collect | recover.

At this time, in order to recover more exhaust heat of the compressor 11, it is desirable to increase the contact area between the outer surface of the compressor 11 and the heat medium pipe. For example, the heat medium pipe may be arranged to be wound around the outer surface of the compressor 11 or may be arranged in a serpentine shape with respect to the outer surface of the compressor 11.

Although the present disclosure has been described based on the examples, it is understood that the present disclosure is not limited to the examples and structures. The present disclosure also includes various modifications and variations within the equivalent range. In addition, although various combinations and forms are shown in the present disclosure, other combinations and forms including only one element, more than or less than the above, are also included in the category and the scope of the present disclosure. It is a thing.

Claims

A compressor (11) for compressing and discharging the refrigerant, a radiator (12) for radiating the heat of the high-pressure refrigerant compressed by the compressor, and a pressure reduction unit for reducing the pressure of the high-pressure refrigerant flowing out of the radiator A heat pump cycle (10) comprising: 15a, 15b), and a heat sink (16, 18) which evaporates and absorbs heat from the low pressure refrigerant decompressed in the decompression section;
A recovery unit (25, 35) for recovering the exhaust heat of the compressor;
The high temperature side heat receiving part (20) which radiates the heat collected in the collecting part to the high pressure refrigerant, and the low temperature side heat receiving part (30) absorbing the heat collected in the collecting part to the low pressure refrigerant Heat pump system having at least one.
The high temperature side heat receiving portion is a high temperature side heat medium circuit (20) in which a high temperature side heat medium that exchanges heat with the high pressure refrigerant in the radiator is circulated;
The heat pump system according to claim 1, wherein the recovery unit has a high temperature side recovery unit (25) which recovers the exhaust heat of the compressor by heat exchange with the high temperature side heat medium.
The high temperature side heat medium circuit is
The heat pump system according to claim 2, further comprising: a heater core (22) that heats the heat exchange target fluid by heat exchange between the high temperature side heat medium and the heat exchange target fluid.
The low temperature side heat receiving portion is a low temperature side heat medium circuit (30) in which a low temperature side heat medium which is absorbed by evaporation of the low pressure refrigerant in the heat absorber circulates,
The heat pump system according to any one of claims 1 to 3, wherein the recovery unit has a low temperature side recovery unit (35) which recovers the exhaust heat of the compressor by heat exchange with the low temperature side heat medium.
The heat pump system according to claim 4, wherein the low temperature side heat medium circuit cools the low temperature side heat medium by absorbing heat of a heat generating device (32) which generates heat with operation.
The heat pump system according to claim 4 or 5, wherein the low temperature side heat medium circuit has a low temperature side radiator (33) that exchanges heat between the low temperature side heat medium and the outside air.
The heat pump system according to any one of claims 4 to 6, wherein the low temperature side recovery unit is disposed on the inlet side of the heat absorber in the low temperature side heat medium circuit.
The heat pump cycle is
A first heat absorber (18) that evaporates and absorbs heat from the refrigerant decompressed by the decompression unit;
The heat sink according to any one of claims 1 to 7, further comprising: a second heat sink (16) that evaporates and absorbs heat from the refrigerant decompressed in the pressure reducing unit at a position different from the first heat sink. Heat pump system.
A heat storage section (40) for storing the exhaust heat of the compressor;
The heat pump system according to any one of claims 1 to 8, wherein the recovery unit recovers the heat stored in the heat storage unit.