WO2019031221A1

WO2019031221A1 - Refrigeration cycle device

Info

Publication number: WO2019031221A1
Application number: PCT/JP2018/027593
Authority: WO
Inventors: 康介白鳥; 加藤　吉毅; 徹岡村
Original assignee: 株式会社デンソー
Priority date: 2017-08-10
Filing date: 2018-07-24
Publication date: 2019-02-14

Abstract

This refrigeration cycle device is to be applied to air conditioning devices. The refrigeration cycle device is provided with a compressor (11), first heating units (12, 22, 12a), and second heating units (14, 14a, 42). The compressor compresses and discharges a refrigerant. Using the refrigerant discharged from the compressor as a heat source, the first heating units heat blowing air to be blown to a space that is to be air-conditioned. Using the refrigerant flowed out from the first heating units as a heat source, the second heating units heat the blowing air. The second heating units are disposed so as to heat the blowing air and flow the blowing air to the first heating unit side. In heating mode in which the blowing air is to be heated, the blowing air is heated by means of both the first heating units and the second heating units. Consequently, the present invention makes it possible to provide a refrigeration cycle device capable of suppressing, with a simple configuration, deterioration of heating performance of heating units even if operation mode is switched.

Description

Refrigeration cycle device

Cross-reference to related applications

This application is based on Japanese Patent Application No. 2017-155680 filed on Aug. 10, 2017 and Japanese Patent Application No. 2018-124604 filed on June 29, 2018, which are incorporated herein by reference. The contents of the description are incorporated.

The present disclosure relates to a refrigeration cycle apparatus and is effective when applied to an air conditioner.

BACKGROUND ART Conventionally, Patent Document 1 discloses a vapor compression refrigeration cycle apparatus applied to a vehicle air conditioner. The refrigeration cycle apparatus of Patent Document 1 includes a refrigerant circuit in a cooling mode that cools air blown into a vehicle compartment that is a space to be air-conditioned, a refrigerant circuit in a heating mode that heats blast air, and air that has been cooled and dehumidified. It is comprised so that switching of the refrigerant circuit of the dehumidification heating mode which reheats air is possible.

More specifically, the refrigeration cycle apparatus of Patent Document 1 includes a first outdoor heat exchanger that exchanges heat between the refrigerant and the heat medium, a second outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the refrigerant and the air. The indoor heat exchanger which exchanges heat with air is provided.

Then, in the cooling mode and the dehumidifying and heating mode executed under predetermined conditions, the high pressure refrigerant is made to flow in the order of the first outdoor heat exchanger → the second outdoor heat exchanger, and the first outdoor heat exchanger and the second outdoor While making a heat exchanger function as a radiator, low pressure refrigerant is made to flow into an indoor heat exchanger, and it switches to a refrigerant circuit which makes an indoor heat exchanger function as an evaporator. Furthermore, in the dehumidifying and heating mode, the first outdoor heat exchanger functions as a heating unit that heats the blowing air.

On the other hand, in the heating mode, the high pressure refrigerant is made to flow in the order of the first outdoor heat exchanger → the indoor heat exchanger, and the first outdoor heat exchanger and the indoor heat exchanger function as a radiator and the second outdoor heat exchange The low pressure refrigerant is caused to flow into the unit, and the second outdoor heat exchanger is switched to a refrigerant circuit that functions as an evaporator. Furthermore, in the heating mode, both the first outdoor heat exchanger and the indoor heat exchanger function as a heating unit that heats the blown air.

Patent No. 4232463

By the way, like the refrigeration cycle apparatus of Patent Document 1, the refrigerant circuit and the low pressure refrigerant that cause the high pressure refrigerant to flow into the heat exchanger (specifically, the indoor heat exchanger) that functions as the heating unit according to the operation mode. In the configuration in which the refrigerant circuit to be introduced is switched, the cycle configuration may be easily complicated.

Furthermore, when switching from the refrigerant circuit that causes the low pressure refrigerant to flow into the heat exchanger that functions as the heating unit to the refrigerant circuit that flows the high pressure refrigerant, the heat of the refrigerant is used to heat the heat exchanger itself that functions as the heating unit. There is also a possibility that the heating capacity of the blowing air in the heating unit may be reduced.

That is, in the refrigeration cycle apparatus applied to the air conditioner, it is desirable that the decrease in the heating capacity of the heating unit can be suppressed even if the operation mode is switched with a simple configuration.

An object of this indication is to provide a refrigerating cycle device which can control a fall of heating capability of blowing air in view of the above-mentioned point.

A refrigeration cycle apparatus according to an aspect of the present disclosure is applied to an air conditioner. The refrigeration cycle apparatus includes a compressor, a first heating unit, and a second heating unit. The compressor compresses and discharges the refrigerant. The first heating unit uses the refrigerant discharged from the compressor as a heat source to heat the air that is blown to the space to be air-conditioned. The second heating unit heats the blowing air using the refrigerant flowing out of the first heating unit as a heat source. The second heating unit is disposed so as to heat the blown air and cause it to flow out to the first heating unit side. In the heating mode for heating the blowing air, the blowing air is heated in both of the first heating unit and the second heating unit.

According to this, in the heating mode, the refrigerant discharged from the compressor is made to flow in the order of the first heating unit → the second heating unit, and the second heating unit → even if the air is relatively low temperature → The heating can be performed stepwise and efficiently in the order of the first heating unit.

Further, in the heating mode, the enthalpy of the refrigerant flowing out of the second heating unit can be sufficiently reduced by the air which is relatively low in temperature. Therefore, the heat absorption amount of the refrigerant in the heat exchanger that functions as an evaporator can be increased, and a decrease in the heating capacity of the blowing air in the first heating unit and the second heating unit can be suppressed.

That is, it is possible to provide a refrigeration cycle apparatus capable of suppressing a decrease in the heating capacity of the blowing air in the heating mode.

Further, the apparatus includes a pressure reducing unit that reduces the pressure of the refrigerant flowing out of the second heating unit, and a cooling evaporation unit that causes the refrigerant reduced in the pressure reducing unit to heat exchange with the blowing air and evaporates the refrigerant.
The second heating unit is disposed so as to heat the blown air cooled by the cooling evaporation unit to flow out toward the first heating unit side, and the blown air cooled and dehumidified by the cooling evaporation unit In the dehumidifying and heating mode of reheating, the blowing air may be heated by at least the second heating unit.

According to this, at the time of the dehumidifying and heating mode, the high pressure refrigerant can be made to flow at least into the second heating unit, and the blowing air cooled and dehumidified by the cooling evaporation unit can be reheated by the second heating unit. . Therefore, the operation mode can be switched with a simple configuration in which the low pressure refrigerant does not flow into the first heating unit and the second heating unit.

Furthermore, in the dehumidifying and heating mode, the enthalpy of the refrigerant flowing out of the second heating unit can be sufficiently reduced by the blowing air cooled by the cooling evaporation unit. Therefore, the amount of heat absorption of the refrigerant in the cooling evaporation portion can be increased, and a decrease in the heating capacity of the blowing air in the second heating portion can be suppressed.

That is, it is possible to provide a refrigeration cycle apparatus capable of suppressing a decrease in heating capacity in the heating unit even when the operation mode is switched with a simple configuration.

BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of this indication. FIG. 7 is a partial cross-sectional view of an indoor air conditioning unit of at least one embodiment of the present disclosure. It is a block diagram showing an electric control part of a vehicular air-conditioning system of at least one embodiment of the present disclosure. It is an explanatory view for explaining a control mode of dehumidification heating mode. BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of this indication. FIG. 7 is a partial cross-sectional view of an indoor air conditioning unit of at least one embodiment of the present disclosure. It is a block diagram showing an electric control part of a vehicular air-conditioning system of at least one embodiment of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of this indication. BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of this indication. BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of this indication. BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of this indication. BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the vehicle air conditioner of at least one embodiment of 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.

First Embodiment
A first embodiment of the present disclosure will be described using FIGS. 1 to 4. The refrigeration cycle apparatus 10 of the present embodiment is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains driving power for traveling a vehicle from a traveling electric motor. The refrigeration cycle apparatus 10 has a function of adjusting the temperature of the blowing air blown into the vehicle compartment, which is a space to be air conditioned, in the vehicle air conditioner 1.

In the vehicle air conditioner 1 of the present embodiment, the operation in the cooling mode, the operation in the heating mode, and the operation in the first and second dehumidifying and heating modes can be switched. The cooling mode is an operation mode for cooling the inside of the vehicle by cooling the blown air. The heating mode is an operation mode in which the blowing air is heated to heat the vehicle interior. The first and second dehumidifying and heating modes are operation modes for reheating the cooled and dehumidified air to dehumidify and heat the passenger compartment.

In the refrigeration cycle apparatus 10, an HFC refrigerant (specifically, R134a) is adopted as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. In this refrigerant, refrigerator oil for lubricating the compressor 11 is mixed, and a part of the refrigerator oil circulates in the cycle together with the refrigerant.

First, each component which comprises the refrigerating-cycle apparatus 10 is demonstrated using the whole block diagram of FIG.

The compressor 11 sucks, compresses and discharges the refrigerant in the refrigeration cycle apparatus 10. 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 (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from an air conditioning control device 60 described later.

The outlet side of the compressor 11 is connected to the inlet side of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. The high temperature side water-refrigerant heat exchanger 12 performs heat exchange between the high pressure refrigerant discharged from the compressor 11 and the high temperature side heat medium circulating in the high temperature side heat medium circuit 20 to heat the high temperature side heat medium. It is As the high temperature side heat medium, a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted.

Here, the high temperature side heat medium circuit 20 is a high temperature side water circuit that circulates the high temperature side heat medium. In the high temperature side heat medium circuit 20, the water passage of the high temperature side water-refrigerant heat exchanger 12, the high temperature side heat medium pump 21, the high temperature side heater core 22, the high temperature side radiator 23, the high temperature side flow control valve 24 etc. There is.

The high temperature side heat medium pump 21 is a high temperature side water pump that pumps the high temperature side heat medium to the inlet side of the water passage of the high temperature side water-refrigerant heat exchanger 12 in the high temperature side heat medium circuit 20. The high temperature side heat medium pump 21 is an electric pump whose rotational speed (that is, water pressure transfer capacity) is controlled by a control voltage output from the air conditioning controller 60.

The high temperature side heater core 22 is disposed in a casing 51 of an indoor air conditioning unit 50 described later. The high temperature side heater core 22 exchanges heat between the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 and the air which has passed through the subcooling side indoor condenser 14 or the indoor evaporator 17 described later. , Is a heat exchanger for heating the blowing air.

The high temperature side radiator 23 is disposed on the front side in the vehicle bonnet. The high temperature side radiator 23 may be integrally formed with the high temperature side water-refrigerant heat exchanger 12 or the like. The high temperature side radiator 23 performs heat exchange between the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 and the outside air blown from the outside air fan (not shown) to obtain the heat of the high temperature side heat medium as the outside air. Is a heat exchanger that dissipates heat.

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

The high temperature side flow control valve 24 includes a high temperature side heater core flow rate Qa1 which is a flow rate of the high temperature side heat medium flowing into the high temperature side heater core 22, and a high temperature side radiator flow rate Qb1 which is a flow rate of the high temperature side heat medium flowing into the high temperature side radiator 23. It is a high temperature side flow ratio adjustment part which adjusts the high temperature side flow ratio (Qb1 / Qa1).

The high temperature side flow control valve 24 is a three-system flow control valve capable of continuously adjusting the high temperature flow rate ratio (Qb1 / Qa1). The operation of the high temperature side flow control valve 24 is controlled by a control signal output from the air conditioning controller 60.

The high temperature side flow control valve 24 is disposed at the connection between the heat medium inlet side of the high temperature side heater core 22 and the heat medium inlet side of the high temperature side radiator 23.

Specifically, the inlet side of the high temperature side flow control valve 24 is connected to the outlet of the water passage of the high temperature side water-refrigerant heat exchanger 12. The heat medium inlet side of the high temperature side heater core 22 is connected to one outlet of the high temperature side flow control valve 24. The heat medium inlet side of the high temperature side radiator 23 is connected to the other outlet of the high temperature side flow control valve 24.

Therefore, in the high temperature side heat medium circuit 20, when the high temperature side flow control valve 24 adjusts the high temperature side flow ratio (Qb1 / Qa1), the flow rate of the high temperature side heat medium flowing into the high temperature side heater core 22 changes. Thereby, the amount of heat radiation to the blast air of the high temperature side heat medium in high temperature type heater core 22, ie, the amount of heating of blast air, is adjusted.

Therefore, in the present embodiment, the compressor is constituted by the high temperature side heat medium pump 21 disposed in the high temperature side heat medium circuit 20, the high temperature side water-refrigerant heat exchanger 12, the high temperature side heater core 22, the high temperature side flow control valve 24 etc. A first heating unit is configured to heat the blown air by using the refrigerant discharged from 11 as a heat source.

Next, the inlet side of the receiver (receiver) is connected to the outlet of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. The receiver 13 separates the gas phase of the high pressure refrigerant flowing out from the high temperature side water-refrigerant heat exchanger 12 and allows the separated liquid phase refrigerant to flow out to the downstream side, and stores the excess refrigerant of the cycle as the liquid phase refrigerant. It is a liquid separation part. The receiver 13 is a cylindrical container with a bottom, and may be integrally formed with the high temperature side water-refrigerant heat exchanger 12 or the like.

The refrigerant inlet side of the subcooling side indoor condenser 14 is connected to the liquid phase refrigerant outlet of the receiver 13. The supercooling side indoor condenser 14 is disposed in the casing 51 of the indoor air conditioning unit 50 together with the high temperature side heater core 22. More specifically, the supercooling side indoor condenser 14 is disposed upstream of the high temperature side heater core 22 in the flow of the blast air.

The supercooling side indoor condenser 14 exchanges heat between the high pressure refrigerant flowing out of the receiver 13 and the air blowing through the indoor evaporator 17 described later to heat the air blowing, and the high pressure refrigerant flowing out of the receiver 13 It is a heat exchanger that overcools. Therefore, in the present embodiment, the subcooling side indoor condenser 14 configures a second heating unit that heats the blown air by using the refrigerant flowing out of the first heating unit as a heat source.

The outlet side of the supercooling side indoor condenser 14 is connected to the inlet side of the branch portion 15a. The branch portion 15 a branches the flow of the refrigerant flowing out of the supercooling side indoor condenser 14. The branch portion 15a is a three-way joint structure having three inlets and outlets communicating with each other, one of the three inlets and outlets being a refrigerant inlet and the remaining two being a refrigerant outlet.

The inlet side of the cooling expansion valve 16a is connected to one outlet of the branch portion 15a. The inlet side of the heat absorption expansion valve 16b is connected to the other outlet of the branch portion 15a.

The cooling expansion valve 16a is a pressure reducing unit that reduces the pressure of the refrigerant flowing out of the supercooling side indoor condenser 14 at least in the cooling mode and the dehumidifying heating mode, and adjusts the flow rate of the refrigerant flowing into the indoor evaporator 17. It is a flow control unit for cooling.

The cooling expansion valve 16a includes a valve body configured to be able to change the throttle opening degree, and an electric actuator (specifically, a stepping motor) that changes the opening degree of the valve body. Is a variable stop mechanism of the formula. The operation of the cooling expansion valve 16 a is controlled by a control signal (control pulse) output from the air conditioning control device 60. The cooling expansion valve 16a has a fully closing function of closing the refrigerant passage by fully closing the valve opening degree.

The refrigerant inlet side of the indoor evaporator 17 is connected to the outlet of the cooling expansion valve 16a. The indoor evaporator 17 is disposed in the casing 51 of the indoor air conditioning unit 50. More specifically, the indoor evaporator 17 is disposed upstream of the supercooled side indoor condenser 14 and the high temperature side heater core 22 in the flow of the blast air.

The indoor evaporator 17 performs a heat exchange between the low pressure refrigerant decompressed by the cooling expansion valve 16a and the blast air at least in the cooling mode and the dehumidifying heating mode to evaporate the low pressure refrigerant and cool the blast air. It is an evaporation part.

The inlet side of the evaporation pressure control valve 19 is connected to the refrigerant outlet of the indoor evaporator 17. The evaporation pressure adjustment valve 19 is an evaporation pressure adjustment unit that maintains the refrigerant evaporation pressure in the indoor evaporator 17 at or above a predetermined reference pressure. The evaporation pressure control valve 19 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 17 increases.

In the present embodiment, as the evaporation pressure adjusting valve 19, one that maintains the refrigerant evaporation temperature in the indoor evaporator 17 at a reference temperature (1.degree. C. in the present embodiment) or more that can suppress the formation of frost on the indoor evaporator 17. It is adopted.

One outlet side of the merging portion 15 b is connected to the outlet of the evaporating pressure regulating valve 19. The merging portion 15 b merges the flow of the refrigerant flowing out of the evaporation pressure adjusting valve 19 and the flow of the refrigerant flowing out of the chiller 18. The basic configuration of the merging portion 15b is the same as that of the branching portion 15a. That is, the junction portion is of a three-way joint structure, in which two of the three inflow / outlet ports are used as the refrigerant inlet and the remaining one is used as the refrigerant outlet.

The heat absorption expansion valve 16 b is a pressure reduction unit that reduces the pressure of the refrigerant flowing out of the supercooling side indoor condenser 14 at least in the heating mode, and is 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 16b is the same as that of the cooling expansion valve 16a.

The inlet side of the refrigerant passage of the chiller 18 is connected to the outlet of the heat absorption expansion valve 16b. The chiller 18 exchanges heat between the low pressure refrigerant decompressed by the heat absorption expansion valve 16b and the low temperature side heat medium circulating in the low temperature side heat medium circuit 30 at least in the heating mode, evaporates the low pressure refrigerant, and absorbs heat to the refrigerant. It is a heat absorption evaporator that exerts an action. As the low temperature side heat medium, a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted.

Here, the low temperature side heat medium circuit 30 is a low temperature side water circuit for circulating the low temperature side heat medium. In the low temperature side heat medium circuit 30, a low temperature side heat medium pump 31, a cooling unit of the on-vehicle device 32, a low temperature side radiator 33, a low temperature side flow rate adjustment valve 34 and the like are arranged.

The low temperature side heat medium pump 31 and the low temperature side heat medium circuit 30 are low temperature side water pumps for pumping 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.

The in-vehicle device 32 is a heat generating device that generates heat when it is activated, and the in-vehicle device of the present embodiment is a battery that supplies an electric quantity to the traveling electric motor. Further, the cooling unit of the on-vehicle device 32 means a heat medium passage formed in the battery in order to absorb the heat generated by the battery at the time of operation such as charging and discharging to the low-pressure side heat medium. .

The low temperature side radiator 33 is integrally formed with the chiller 18 and the like, and is disposed on the front side in the vehicle bonnet. The low temperature side radiator 33 is a heat exchanger which causes the low temperature side heat medium to absorb heat from the outside air by heat exchange between the low temperature side heat medium cooled by the chiller 18 and the outside air blown from the outside air fan.

The cooling unit of the on-vehicle device 32 and the low temperature side radiator 33 are connected in parallel to the flow of the low temperature side heat medium in the low temperature side heat medium circuit 30, as shown in FIG.

The low temperature side flow control valve 34 is a device side flow Qa2 which is a flow of the low temperature side heat medium flowing into the cooling unit of the in-vehicle device 32 and a low temperature side radiator side flow which is a flow of the low temperature side heat medium flowing into the low temperature side radiator 33 It is a low temperature side flow ratio adjustment part which adjusts the low temperature side flow ratio (Qb2 / Qa2) with Qb2. The basic configuration of the low temperature side flow control valve 34 is similar to that of the high temperature side flow control valve 24.

The low temperature side flow control valve 34 is disposed at a connection portion between the heat medium inlet side of the cooling unit of the on-vehicle device 32 and the heat medium inlet side of the low temperature side radiator 33. That is, the inlet side of the low temperature side flow control valve 34 is connected to the outlet of the water passage of the chiller 18. The heat medium inlet side of the cooling unit of the on-vehicle device 32 is connected to one outlet of the low temperature side flow rate adjustment valve 34. The heat medium inlet side of the low temperature side radiator 33 is connected to the other outlet of the low temperature side flow rate adjustment valve 34.

In the low temperature side heat medium circuit 30, the low temperature side flow rate adjustment valve 34 adjusts the low temperature side flow ratio (Qb2 / Qa2) to obtain the heat absorption amount from the in-vehicle device 32 of the low temperature side heat medium in the cooling unit of the in-vehicle device 32; The heat absorption amount from the outside air of the low temperature side heat medium in the low temperature side radiator 33 can be adjusted.

The other inlet side of the merging portion 15 b is connected to the outlet of the refrigerant passage of the chiller 18. The suction port side of the compressor 11 is connected to the outlet of the merging portion 15b.

Next, the indoor air conditioning unit 50 will be described using FIGS. 1 and 2. FIG. 2 is a cross-sectional view of a portion of the indoor air conditioning unit 50 that is positioned downstream of the air flow from the fan 52 described later. Arrows in the upper, lower, front, and back directions in FIG. 2 indicate directions when the indoor air conditioning unit 50 is mounted on a vehicle. The indoor air conditioning unit 50 is disposed inside the instrument panel (i.e., the instrument panel) at the front of the vehicle interior.

The indoor air conditioning unit 50 forms an air passage for blowing out the temperature-controlled blowing air to an appropriate place in the vehicle compartment. The indoor air conditioning unit 50 is one in which the blower 52, the indoor evaporator 17, the overcooling side indoor condenser 14, the high temperature side heater core 22 and the like are housed in an air passage formed inside the casing 51 forming the outer shell thereof. is there.

The casing 51 forms an air passage for blowing air blown into the vehicle compartment, and is formed of a resin (specifically, polypropylene) which has a certain degree of elasticity and is excellent in strength. In the casing 51, a partitioning member 51a is disposed. Thus, the air passage in the casing 51 is divided into a first air passage 50a formed on the upper side in the vertical direction and a second air passage 50b formed on the lower side in the vertical direction.

An internal / external air switching device 53 is disposed on the most upstream side of the blowing air flow of the casing 51. The inside / outside air switching device 53 changes the introduction ratio of inside air (air in the vehicle compartment) and outside air (air outside the vehicle) introduced into the casing 51.

More specifically, the inside / outside air switching device 53 has an inside / outside air switching door formed of a plate door. The inside / outside air switching device 53 displaces the inside / outside air switching door to continuously change the opening area ratio between the opening area of the inside air inlet and the opening area of the outside air inlet, thereby introducing the inside air to the outside air. Change

The inside and outside air switching door is driven by an electric actuator 61a for the inside and outside air switching door. The operation of the electric actuator 61a is controlled by a control signal output from the air conditioning controller 60.

As an inside / outside air introduction mode switched by the inside / outside air switching door, there are a inside air mode, an outside air mode, and an inside / outside air double layer mode.

The inside air mode is an introduction mode in which inside air is introduced into both the first air passage 50a and the second air passage 50b. The outside air mode is an introduction mode in which the outside air is introduced into both the first air passage 50a and the second air passage 50b. The inside / outside air double-layer mode is an introduction mode in which outside air is introduced into the first air passage 50a and inside air is introduced into the second air passage 50b.

A blower 52 is disposed downstream of the inside / outside air switching device 53 in the flow of the blown air. The blower 52 drives the first centrifugal multi-blade fan for blowing the blown air toward the first air passage 50a and the second centrifugal multi-blade fan for blowing the blown air toward the second air passage 50b with a common electric motor. It is a two-stage electric blower. The rotation speed (that is, the blowing capacity) of the blower 52 is controlled by the control voltage output from the air conditioning control device 60.

An indoor evaporator 17, an overcooling side indoor condenser 14, and a high temperature side heater core 22 are arranged in this order with respect to the flow of the blowing air, on the downstream side of the blowing air flow of the blower 52. Therefore, the supercooling side indoor condenser 14 is arranged so as to heat the blown air cooled by the indoor evaporator 17 and to discharge it to the high temperature side heater core 22 side.

The indoor evaporator 17 and the high temperature side heater core 22 are disposed across the first air passage 50a and the second air passage 50b through the attachment holes formed in the dividing member 51a.

That is, the refrigerant flowing through the indoor evaporator 17 is disposed so as to be able to exchange heat with both the blown air flowing through the first air passage 50a and the blown air flowing through the second air passage 50b. Further, the high temperature side heat medium flowing through the high temperature side heater core 22 is disposed so as to be able to exchange heat with both the blown air flowing through the first air passage 50 a and the blown air flowing through the second air passage 50 b.

The supercooling side indoor condenser 14 is disposed on the first air passage 50a side. That is, the refrigerant flowing through the supercooling side indoor condenser 14 is disposed so as to be able to exchange heat with the blowing air flowing through the first air passage 50a.

In the first air passage 50a, there is provided a first cold air bypass passage 55a for flowing the blown air which has passed through the indoor evaporator 17 to the downstream side by bypassing the overcooling side indoor condenser 14 and the high temperature side heater core 22. There is. Further, in the second air passage 50b, a second cold air bypass passage 55b is provided which allows the blown air that has passed through the indoor evaporator 17 to bypass the high temperature side heater core 22 and flow downstream.

The first air mix door 54a is on the downstream side of the blown air flow of the indoor evaporator 17 of the first air passage 50a and on the upstream side of the blown air flow of the supercooling side indoor condenser 14 and the high temperature side heater core 22. It is arranged. The first air mix door 54a is configured such that the volume of air passing through the supercooling side indoor condenser 14 and the high temperature side heater core 22 and the first cold air bypass of the blown air after passing through the indoor evaporator 17 flowing through the first air passage 50a. The ratio of the air volume to the air volume passing through the passage 55a is adjusted.

A second air mix door 54b is disposed on the downstream side of the flow of the blown air of the indoor evaporator 17 of the second air passage 50b and on the upstream side of the flow of the blown air of the high temperature side heater core 22. The second air mix door 54b includes, among the blown air after passing through the indoor evaporator 17 flowing through the second air passage 50b, an air volume for passing the high temperature side heater core 22 and an air volume for passing the second cold air bypass passage 55b. It adjusts the air volume ratio.

Each of the first air mix door 54 a and the second air mix door 54 b is a slide door that slides in a direction substantially parallel to the heat exchange surface of the high temperature side heater core 22 to adjust the air volume ratio.

The first air mix door 54a and the second air mix door 54b are operated in conjunction with each other by a common electric mix door electric actuator 61b via a link mechanism or the like. Therefore, the opening degree at which the first air mix door 54a opens the first cold air bypass passage 55a and the opening degree at which the second air mix door 54b opens the second cold air bypass passage 55b are substantially equal. The operation of the electric actuator 61 b for the air mix door is controlled by a control signal output from the air conditioning controller 60.

On the downstream side of the blown air flow of the high temperature side heater core 22 of the first air passage 50a, the blown air heated by the supercooling side indoor condenser 14 and the high temperature side heater core 22 passes through the first cold air bypass passage 55a A first mixing space 56a is provided to mix with the air not being supplied. On the downstream side of the flow of the blown air of the high temperature side heater core 22 of the second air passage 50b, the blown air heated by the high temperature side heater core 22 and the blown air not passing through the second cold air bypass passage 55b are mixed. A second mixing space 56b is provided.

The partition member 51a positioned on the downstream side of the air flow of the high temperature side heater core 22 is provided with a communication port 57d for communicating the air flowing into the first mixing space 56a with the air flowing into the second mixing space 56b. ing.

Further, inside the casing 51, a communication port opening / closing door 58d for opening and closing the communication port 57d is disposed. The communication opening and closing door 58d is driven by an electric actuator 61c for the communication opening and closing door. The operation of the electric actuator 61 c is controlled by a control signal output from the air conditioning controller 60.

A defroster opening hole 57c and a face opening hole 57a for blowing the blowing air (air conditioned air) mixed in the first mixing space 56a into the vehicle compartment at the most downstream portion of the blowing air flow on the side of the first air passage 50a of the casing 51. Is provided. A foot opening hole 57b is provided at the most downstream portion of the air flow on the second air passage 50b side of the casing 51 for blowing air (air-conditioned air) mixed in the second mixing space 56b into the vehicle compartment. .

The face opening hole 57a is an opening hole for blowing the conditioned air toward the upper body of the occupant in the vehicle compartment. The foot opening hole 57b is an opening hole for blowing the conditioned air toward the feet of the occupant. The defroster opening hole 57c is an opening hole for blowing the conditioned air toward the inner side surface of the vehicle front windshield.

The face opening hole 57a, the foot opening hole 57b, and the defroster opening hole 57c are respectively provided with a face outlet, a foot outlet, and a defroster outlet provided in the vehicle compartment via a duct that forms an air passage (all shown) Not connected).

Therefore, by adjusting the air volume ratio of the air volume of the blown air which the first air mix door 54a passes the supercooling side indoor condenser 14 and the high temperature side heater core 22 and the air volume which passes the first cold air bypass passage 55a, The temperature of the conditioned air mixed in the first mixing space 56a is adjusted. As a result, the temperature of the air (air-conditioned air) blown out from the defroster outlet and the face outlet into the vehicle compartment is also adjusted.

Similarly, in the second mixing space 56b, the second air mixing door 54b adjusts the air volume ratio between the air volume of the blown air passing through the high temperature side heater core 22 and the air volume passing through the second cold air bypass passage 55b. The temperature of the conditioned air to be mixed is adjusted. As a result, the temperature of the air (air-conditioned air) blown out from the foot outlet into the vehicle compartment is also adjusted.

Here, the first air mix door 54a adjusts the amount of air blown through the supercooled side indoor condenser 14 to adjust the amount of heat released to the blown air in the supercooled side indoor condenser 14. be able to. Therefore, the first air mix door 54a of the present embodiment constitutes a heat release amount adjustment unit.

Further, on the upstream side of the blast air flow of the defroster opening hole 57c and the face opening hole 57a, a face defroster door for adjusting the opening area of the defroster opening hole 57c and the face opening hole 57a is disposed. The face defroster door 58a is a slide door which increases the opening area of one of the defroster opening hole 57c and the face opening hole 57a and at the same time reduces the other opening area.

A foot door 58b for adjusting the opening area of the foot opening hole 57b is disposed on the upstream side of the air flow of the foot opening hole 57b. The foot door 58b is a plate door that changes the opening area of the foot opening hole 57b.

The face defroster door 58a and the foot door 58b constitute an air outlet mode switching device for switching the air outlet from which the conditioned air is blown out. The face defroster door 58a and the foot door 58b are connected to an electric actuator 61d for driving the air outlet mode door via a link mechanism or the like, and are rotationally operated in conjunction with each other. The operation of the electric actuator 61 d is controlled by a control signal output from the air conditioning controller 60.

Next, the outline of the electric control unit according to the present embodiment will be described with reference to FIG. The air conditioning control device 60 is configured of a known microcomputer including a CPU, a ROM, a RAM, and the like, and peripheral circuits thereof. Then, various calculations and processing are performed based on the air conditioning control program stored in the ROM, and various

control target devices

11, 16a, 16b, 21, 24, 31, 34, 52, 61a connected to the output side Control the operation of.

Further, as shown in the block diagram of FIG. 3, on the input side of the air conditioning control device 60, an inside air temperature sensor 62a, an outside air temperature sensor 62b, a solar radiation sensor 62c, a high pressure sensor 62d, a supercooling sensor 62e, and an evaporator temperature sensor A group of sensors for air conditioning control such as 62 f, superheat degree sensor 62 g, air conditioning air temperature sensor 62 h and the like are connected. The air conditioning 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 62d 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 16a or the heat absorption expansion valve 16b.

The subcooling degree sensor 62 e is a subcooling degree detection unit that detects the subcooling degree SC of the refrigerant based on the temperature and the pressure of the refrigerant flowing out of the subcooling side indoor condenser 14. The evaporator temperature sensor 62 f is an evaporator temperature detection unit that detects a refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 17.

The superheat degree sensor 62g is a superheat degree detection unit that detects the superheat degree SH of the refrigerant based on the temperature and pressure of the refrigerant on the suction port side of the compressor 11. The air conditioning air temperature sensor 62 h is an air conditioning air temperature detection unit that detects the temperature of the air supplied from the first mixing space 56 a and the second mixing space 56 b into the vehicle compartment.

Further, as shown in FIG. 3, an operation panel 63 disposed near the instrument panel at the front of the vehicle compartment is connected to the input side of the air conditioning control device 60, and various operation switches provided on the operation panel 63 The operation signal of is input.

Specifically, the various operation switches provided on the operation panel 63 include an auto switch for setting or canceling the automatic control operation of the air conditioning system for a vehicle, a cooling switch for requesting cooling of the vehicle interior, and an air volume of the blower 52 There are an air volume setting switch for manually setting the temperature setting switch and a temperature setting switch for setting the target temperature Tset in the vehicle compartment.

In addition, although the control part which controls the various control object apparatus connected to the output side was integrally comprised, the air-conditioning control apparatus 60 of this embodiment controls the operation | movement of each control object apparatus (Hardware and software) constitute a control unit that controls the operation of each control target device.

For example, in the air conditioning control device 60, the configuration that controls the operation of the compressor 11 is the discharge capacity control unit 60a. The configuration for controlling the operation of the high temperature side heat medium pump 21 is a high temperature side pressure feeding capacity control unit 60b. The configuration for controlling the operation of the high temperature side flow control valve 24 is the high temperature side flow ratio control unit 60c. The configuration for controlling the operation of the low temperature side heat medium pump 31 is the low temperature side pressure feeding capacity control unit 60d. The configuration for controlling the operation of the low temperature side flow control valve 34 is the low temperature side flow ratio control unit 60 e.

Further, the configuration for controlling the operation of the first and second

air mix doors

54a and 54b (specifically, the electric actuator 61b for the air mix door) is an air mix control unit 60f. The first air mix door 54a of the present embodiment constitutes a heat release amount adjustment unit, so the air mix control unit 60f is a heat release amount control unit.

Next, the operation of the vehicle air conditioner 1 of the present embodiment in the above configuration will be described. As described above, in the vehicle air conditioner 1 of the present embodiment, the operation mode can be switched. The switching of these operation modes is performed by executing the air conditioning control program stored in advance in the air conditioning control device 60.

More specifically, in the air conditioning control program, based on the detection signal detected by the air conditioning control sensor group and the operation signal output from the operation panel 63, the target blowout temperature TAO of the air to be blown into the vehicle compartment is calculated. calculate. Then, the operation mode is switched based on the target blowout temperature TAO and the detection signal. Then, according to the operation mode, the operation of various control target devices connected to the output side is controlled. The operation of each operation mode will be described below.

(A) Cooling Mode In the cooling mode, the air-conditioning control device 60 controls the operation of the compressor 11 such that the refrigerant evaporation temperature Tefin detected by the evaporator temperature sensor 62f becomes the target evaporation temperature TEO. The target evaporation temperature TEO is determined based on the target blowout temperature TAO with reference to a control map stored in advance in the air conditioning control device 60.

Specifically, in the control map of the cooling mode, the target evaporation temperature TEO is increased along with the increase of the target outlet temperature TAO so that the blown air temperature TAV detected by the air conditioning air temperature sensor 62h approaches the target outlet temperature TAO. Let

Further, the air conditioning control device 60 brings the cooling expansion valve 16a into a throttling state for exerting the refrigerant pressure reducing action, and brings the heat absorption expansion valve 16b into a fully closed state. Therefore, the refrigeration cycle apparatus 10 in the cooling mode is a refrigerant circuit that causes the refrigerant decompressed by the cooling expansion valve 16 a to flow into the indoor evaporator 17. Furthermore, the air conditioning control device 60 sets the throttle opening degree of the cooling expansion valve 16a so that the degree of superheat SH detected by the degree of superheat sensor 62g approaches a predetermined reference degree of superheat KSH (3.degree. C. in the present embodiment). adjust.

In addition, the air conditioning 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 set in advance. Furthermore, the air conditioning control device 60 operates the high temperature side flow control valve 24 so that the full flow rate of the high temperature side heat medium flowing out of the water passage of the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23 Control.

In addition, the air conditioning control device 60 displaces the first air mix door 54a so that the total volume of the cold air flowing through the first air passage 50a flows into the first cold air bypass passage 55a. Further, the second air mix door 54b is displaced so that the total amount of cold air flowing through the second air passage 50b flows into the second cold air bypass passage 55b.

Further, the air conditioning control device 60 displaces the inside / outside air switching device door of the inside / outside air switching device 53 so that the inside / outside air introduction mode becomes the outside air mode. Furthermore, the communication port opening / closing door 58d is displaced so as to fully open the communication port 57d. However, in the cooling mode, the inside / outside air switching device door is displaced so as to be in the inside air mode at the maximum cooling time when the target blowing temperature TAO is in the cryogenic temperature range.

Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12. In the high temperature side 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.

In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the high temperature side 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 high temperature side water-refrigerant heat exchanger 12.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid. The liquid-phase refrigerant separated by the receiver 13 flows into the subcooling side indoor condenser 14. In the cooling mode, since the first air mix door 54a closes the air passage on the side of the overcooling side indoor condenser 14, the refrigerant flowing into the overcooling side indoor condenser 14 hardly dissipates heat, so It flows out of the condenser 14.

The refrigerant flowing out of the supercooling side indoor condenser 14 flows into the cooling expansion valve 16a and is decompressed because the heat absorption expansion valve 16b is fully closed. At this time, the degree of opening of the cooling expansion valve 16a is controlled so that the degree of superheat SH approaches the reference degree of heating KSH.

The low pressure refrigerant reduced in pressure by the cooling expansion valve 16 a flows into the indoor evaporator 17. The refrigerant flowing into the indoor evaporator 17 absorbs heat from the air blown from the fan 52 and evaporates. This cools the blowing air. The refrigerant that has flowed out of the indoor evaporator 17 is sucked into the compressor 11 via the evaporation pressure adjusting valve 19 and the merging portion 15 b and compressed again.

As described above, in the cooling mode, cooling of the vehicle interior can be performed by blowing the blowing air cooled by the indoor evaporator 17 into the vehicle interior.

(B) Heating Mode In the heating mode, the air conditioning 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 a control map stored in advance in the air conditioning control device 60.

Specifically, in the control map of the heating mode, 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 air conditioning control device 60 brings the cooling expansion valve 16a into a fully closed state, and brings the heat absorption expansion valve 16b into a throttling state. Therefore, the refrigeration cycle apparatus 10 in the heating mode is a refrigerant circuit that causes the refrigerant decompressed by the heat absorption expansion valve 16 b to flow into the chiller 18. Further, the air conditioning control device 60 adjusts the throttle opening degree of the heat absorption expansion valve 16b such that the degree of superheat SH approaches the predetermined reference degree of superheat KSH.

Further, the air conditioning 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. Furthermore, the air conditioning controller 60 operates 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 high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side heater core 22. Control.

Further, the air conditioning control device 60 operates the low temperature side heat medium pump 31 so as to exert the water pressure transfer capability in the predetermined heating mode. Furthermore, the air conditioning control device 60 controls the operation of the low temperature side flow control valve 34 so that the battery which is the in-vehicle device 32 can be maintained at a temperature at which the battery can exhibit appropriate charge and discharge performance.

Further, the air conditioning control device 60 closes the air passage on the side of the first cold air bypass passage 55a, so that the total volume of the cold air flowing through the first air passage 50a flows into the overcooling side indoor condenser 14 The mix door 54a is displaced. Furthermore, the air passage on the second cold air bypass passage 55 b side is closed, and the second air mix door 54 b is displaced so that the total amount of cold air flowing through the second air passage 50 b flows into the high temperature side heater core 22.

For this reason, in the heating mode, the air volume of the blowing air flowing into the subcooling side indoor condenser 14 increases more than in the cooling mode. In other words, in the cooling mode, the air volume of the blowing air flowing into the subcooling side indoor condenser 14 is smaller than in the heating mode.

Further, the air conditioning control device 60 displaces the inside / outside air switching device door of the inside / outside air switching device 53 so that the inside / outside air introduction mode becomes the outside air mode. Furthermore, the communication port opening / closing door 58d is displaced so as to fully open the communication port 57d. However, in the heating mode, the inside / outside air switching device door is displaced so as to be in the inside / outside air double layer mode at the maximum heating where the target blowout temperature TAO is in the extremely high temperature region, and the communication port is opened and closed. The door 58d is displaced.

Accordingly, in the heating mode refrigeration cycle apparatus 10, the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12. In the high temperature side 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.

In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side heater core 22 through the high temperature side flow rate adjustment valve 24. The high temperature side heat medium that has flowed into the high temperature side heater core 22 exchanges heat with the air that has passed through the supercooling side indoor condenser 14 and radiates heat. As a result, the blowing air is heated, and the temperature of the blowing air approaches the target blowing temperature TAO. The high temperature side heat medium flowing out of the high temperature side 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 high temperature side water-refrigerant heat exchanger 12.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid. The liquid-phase refrigerant separated by the receiver 13 flows into the subcooling side indoor condenser 14. The refrigerant flowing into the supercooling side indoor condenser 14 exchanges heat with the air that has passed through the indoor evaporator 17 and radiates heat. Thereby, the blowing air which flows in into the high temperature side heater core 22 arrange | positioned at the 1st air path 50a side is heated.

Here, the refrigerant flowing into the supercooling side indoor condenser 14 is the liquid phase refrigerant separated by the receiver 13. For this reason, in the subcooling side indoor condenser 14, this liquid phase refrigerant is subcooled. Therefore, the temperature of the blown air heated by the supercooling side indoor condenser 14 does not become higher than the temperature of the high temperature side heat medium flowing into the high temperature side heater core 22.

The refrigerant flowing out of the supercooling side indoor condenser 14 flows into the heat absorption expansion valve 16b and is reduced in pressure because the cooling expansion valve 16a is fully closed. At this time, the throttle opening degree of the heat absorption expansion valve 16b is controlled such that the degree of superheat SH approaches the reference degree of heating KSH.

The low pressure refrigerant decompressed by the cooling expansion valve 16 a flows into the refrigerant passage of the chiller 18. In the chiller 18, since the low temperature side heat medium pump 31 is operating, the low pressure refrigerant and the low temperature side heat medium exchange heat, and the low pressure refrigerant absorbs heat from the low temperature side heat medium and evaporates. Thereby, the low temperature side heat medium is cooled.

In the low temperature side heat medium circuit 30, part of the low temperature side heat medium cooled by the chiller 18 flows into the low temperature side radiator 33 via the low temperature side flow rate adjustment valve 34. The low temperature side heat medium flowing into the low temperature side radiator 33 exchanges heat with the outside air and is heated. The remaining low-temperature side heat medium cooled by the chiller 18 flows into the cooling unit of the battery, which is the on-vehicle device 32, via the low-temperature side flow rate adjustment valve 34 and is heated.

At this time, the low temperature side flow rate adjustment valve 34 adjusts the low temperature side flow ratio (Qb2 / Qa2) so that the battery which is the on-vehicle device 32 can be maintained at a temperature at which the battery can exhibit appropriate charge / discharge performance. The low temperature side heat medium flowing out of the low temperature side radiator 33 and the low temperature side heat medium flowing out of the cooling portion of the in-vehicle apparatus 32 are drawn into the high temperature side heat medium pump 21 and pumped again to the water passage of the chiller 18.

The refrigerant that has flowed out of the refrigerant passage of the chiller 18 is sucked into the compressor 11 via the junction portion 15b and compressed again.

As described above, in the heating mode, it is possible to heat the vehicle interior by blowing the blown air heated by the high temperature side heater core 22 into the vehicle interior. Furthermore, in the first air passage 50a, heating the vehicle interior can be performed by blowing out the heated air in the order of the supercooled side indoor condenser 14 and the high temperature side heater core 22 into the vehicle interior.

(C) First Dehumidifying / Heating Mode The first dehumidifying / heating mode is a dehumidifying / heating mode that is executed when the outside temperature Tam is in a relatively high temperature zone (for example, a temperature zone of 15 ° C. or more and 25 ° C. or less) It is.

In the first dehumidifying and heating mode, the air conditioning control device 60 controls the operation of the compressor 11 such that the refrigerant evaporation temperature Tefin becomes the target evaporation temperature TEO. The target evaporation temperature TEO is determined based on the target blowout temperature TAO with reference to a control map stored in advance in the air conditioning control device 60.

Specifically, in the control map of the first dehumidifying and heating mode, the target evaporation temperature TEO is raised as the target blow-out temperature TAO rises. Furthermore, the target evaporation temperature TEO is determined to a value that is equal to or higher than a reference temperature (specifically, 1 ° C.) at which frost formation of the indoor evaporator 17 can be suppressed.

Further, the air conditioning control device 60 sets the cooling expansion valve 16a in the squeezed state and sets the heat absorption expansion valve 16b in the fully closed state, as in the cooling mode.

Further, the air-conditioning control device 60 operates the high-temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the first dehumidifying and heating mode determined in advance. Furthermore, the air conditioning control device 60 controls the operation of the high temperature side flow control valve 24 so that the blowing air temperature TAV approaches the target blowing temperature TAO.

Further, the air conditioning control device 60 displaces the first air mix door 54a and the second air mix door 54b such that the degree of subcooling SC detected by the degree of subcooling sensor 62e approaches the target degree of subcooling KSC. The target degree of subcooling KSC is determined based on the target blowout temperature TAO with reference to a control map stored in advance in the air conditioning control device 60.

Here, in a general refrigeration cycle apparatus, the coefficient of performance (COP) of the cycle can be improved by increasing the degree of subcooling of the refrigerant flowing out of the refrigerant functioning as the condenser. Therefore, it is preferable to increase the target degree of supercooling KSC as much as possible.

However, in the supercooling side indoor condenser 14 of the present embodiment, the refrigerant can not be cooled more than the temperature of the blown air cooled by the indoor evaporator 17. Furthermore, as shown in FIG. 4, a slope exists in the saturated liquid line of the Mollier diagram. Therefore, in the control map of the present embodiment, the target degree of subcooling KSC is decreased as the target blowout temperature TAO decreases.

Further, the air conditioning control device 60 displaces the inside / outside air switching device door of the inside / outside air switching device 53 so that the inside / outside air introduction mode becomes the outside air mode. Furthermore, the communication port opening / closing door 58d is displaced so as to fully open the communication port 57d.

Therefore, in the refrigeration cycle apparatus 10 in the first dehumidifying and heating mode, the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12. In the high temperature side 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.

In the high temperature side heat medium circuit 20, a part of the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side heater core 22 via the high temperature side flow rate adjustment valve 24. The high temperature side heat medium that has flowed into the high temperature side heater core 22 exchanges heat with the air that has passed through the supercooling side indoor condenser 14 and radiates heat. In the first dehumidifying and heating mode, since the first air mix door 54a and the second air mix door 54b respectively open the air passage on the high temperature side heater core 22 side, the blowing air is heated and the temperature of the blowing air is a target It approaches the blowing temperature TAO.

The remaining high temperature side heat medium heated by the high temperature side 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 flowing out of the high temperature side heater core 22 and the high temperature side heat medium flowing out of the high temperature side radiator 23 are drawn into the high temperature side heat medium pump 21 and pumped again to the water passage of the high temperature side water-refrigerant heat exchanger 12 Be done.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid. The liquid-phase refrigerant separated by the receiver 13 flows into the subcooling side indoor condenser 14. Since the first air mix door 54a opens the ventilation path on the side of the supercooling side indoor condenser 14, the refrigerant having flowed into the supercooling side indoor condenser 14 exchanges heat with the air that has passed through the indoor evaporator 17. Dissipate heat. Thereby, the blowing air which flows in into high temperature side heater core 22 is heated.

The refrigerant flowing out of the supercooling side indoor condenser 14 flows into the cooling expansion valve 16a and is decompressed because the heat absorption expansion valve 16b is fully closed. The low pressure refrigerant reduced in pressure by the cooling expansion valve 16 a flows into the indoor evaporator 17. The refrigerant flowing into the indoor evaporator 17 absorbs heat from the air blown from the fan 52 and evaporates. As a result, the blowing air is cooled and dehumidified. The subsequent operation is the same as in the cooling mode.

As described above, in the first dehumidifying and heating mode, the blown air cooled and dehumidified by the indoor evaporator 17 is reheated by at least the supercooling side indoor condenser 14 and blown out into the vehicle compartment, thereby Dehumidifying and heating can be performed.

Here, in the first dehumidifying and heating mode, when the temperature of the blown air heated by the supercooling side indoor condenser 14 has reached the target blowing temperature TAO, the high temperature side water-refrigerant heat exchanger 12 is used. There is no need to further heat the blowing air. Therefore, in this case, the air conditioning control device 60 may control the operation of the high temperature side flow rate adjustment valve 24 so that the full flow rate of the high temperature side heat medium flows into the high temperature side radiator 23 as in the cooling mode. .

Therefore, the first dehumidifying and heating mode is a dehumidifying and heating mode in which the blown air is heated by at least the subcooling side indoor condenser 14.

(D) Second Dehumidifying / Heating Mode The second dehumidifying / heating mode is a dehumidifying / heating mode that is executed in a temperature range where the outside temperature Tam is relatively low (for example, a temperature range of 0 ° C. or more and 20 ° C. or less). That is, the second dehumidifying and heating mode is performed when the heating capacity of the blowing air required for the refrigeration cycle apparatus 10 is higher than that of the first dehumidifying and heating mode.

In the second dehumidifying and heating mode, the air conditioning control device 60 controls the operation of the compressor 11 so that the blown air temperature TAV approaches the target blowing temperature TAO regardless of the refrigerant evaporation temperature Tefin.

Further, the air conditioning control device 60 sets both the cooling expansion valve 16a and the heat absorption expansion valve 16b in a throttling state. Specifically, the throttle opening degree of the cooling expansion valve 16a and the throttle opening degree of the heat absorption expansion valve 16b are each set as the throttle opening degree for the second dehumidifying and heating mode, which is predetermined.

In addition, the air conditioning control device 60 operates the high temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the second dehumidifying and heating mode determined in advance. Furthermore, in the same manner as in the heating mode, the air conditioning control device 60 causes the high temperature side flow so that the total flow rate of the high temperature side heat medium flowing out of the water passage of the high temperature side water-refrigerant heat exchanger 12 The operation of the control valve 24 is controlled.

Further, the air conditioning control device 60 operates the low temperature side heat medium pump 31 so as to exert the pressure feeding capability in the second dehumidifying and heating mode determined in advance. Furthermore, the air conditioning control device 60 controls the operation of the low temperature side flow control valve 34 so that the battery which is the in-vehicle device 32 can be maintained at a temperature at which appropriate charge / discharge performance can be exhibited.

Further, the air conditioning control device 60 displaces the first air mix door 54a and the second air mix door 54b so that the degree of subcooling SC approaches the target degree of subcooling KSC, as in the first dehumidifying and heating mode.

Therefore, in the refrigeration cycle apparatus 10 in the second dehumidifying and heating mode, the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12. In the high temperature side 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.

In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side heater core 22 through the high temperature side flow rate adjustment valve 24 as in the heating mode. Do. The high temperature side heat medium that has flowed into the high temperature side heater core 22 exchanges heat with the air that has passed through the supercooling side indoor condenser 14 and radiates heat. As a result, the blowing air is heated, and the temperature of the blowing air approaches the target blowing temperature TAO.

The high temperature side heat medium flowing out of the high temperature side 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 high temperature side water-refrigerant heat exchanger 12.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid. The liquid-phase refrigerant separated by the receiver 13 flows into the subcooling side indoor condenser 14. The refrigerant that has flowed into the supercooling side indoor condenser 14 exchanges heat with the air that has passed through the indoor evaporator 17 and radiates heat, as in the heating mode. Thereby, the blowing air before flowing into the high temperature side heater core 22 is heated.

The flow of the refrigerant flowing out of the supercooling side indoor condenser 14 is branched at the branch portion 15a. One of the refrigerants branched by the branch portion 15a flows into the cooling expansion valve 16a and is decompressed. The low pressure refrigerant reduced in pressure by the cooling expansion valve 16 a flows into the indoor evaporator 17. The refrigerant flowing into the indoor evaporator 17 absorbs heat from the air blown from the fan 52 and evaporates. This cools the blowing air.

Under the present circumstances, the refrigerant | coolant evaporation temperature in the indoor evaporator 17 is maintained by 1 degreeC or more by the effect | action of the evaporation pressure control valve 19, irrespective of the refrigerant | coolant discharge capacity of the compressor 11. FIG.

On the other hand, the other refrigerant branched at the branch portion 15a flows into the heat absorption expansion valve 16b and is decompressed. The low pressure refrigerant decompressed by the cooling expansion valve 16 a flows into the refrigerant passage of the chiller 18. In the chiller 18, as in the heating mode, since the low temperature side heat medium pump 31 is operating, the low pressure refrigerant and the low temperature side heat medium exchange heat, and the low pressure refrigerant absorbs heat from the low temperature side heat medium and evaporates.

In the low temperature side heat medium circuit 30, as in the heating mode, the low temperature side heat medium absorbs heat from the outside air and the battery as the on-vehicle device 32. The refrigerant flowing out of the refrigerant passage of the chiller 18 merges with the refrigerant flowing out of the evaporation pressure adjusting valve 19 at the merging portion 15b, and is drawn into the compressor 11 and compressed again.

As described above, in the second dehumidifying and heating mode, dehumidifying and heating the passenger compartment is performed by reheating the blown air cooled and dehumidified by the indoor evaporator 17 with the high temperature side heater core 22 and blowing it out into the passenger compartment. Can. Furthermore, in the first air passage 50a, the blown air cooled and dehumidified by the indoor evaporator 17 is reheated in the order of the supercooled side indoor condenser 14 → the high temperature side heater core 22 and blown out into the vehicle compartment, It is possible to perform dehumidifying and heating of the vehicle interior.

Here, in the second dehumidifying and heating mode, since both the cooling expansion valve 16a and the heat absorption expansion valve 16b are in the squeezed state, the indoor evaporator 17 and the chiller 18 are connected in parallel to the refrigerant flow. Then, the refrigerant can be evaporated by both the indoor evaporator 17 and the chiller 18, and the heat of the blown air and the heat of the low temperature side heat medium can be absorbed by the refrigerant.

Furthermore, the refrigerant evaporation pressure in the chiller 18 can be made lower than the refrigerant evaporation pressure in the indoor evaporator 17 by the action of the evaporation pressure adjusting valve 19 disposed on the refrigerant flow downstream side of the indoor evaporator 17. Therefore, in the second dehumidifying and heating mode, the heat absorption amount of the refrigerant can be increased more than in the first evaporation and heating mode, and the heating capacity of the blowing air can be improved.

Hereinafter, the excellent effects of the refrigeration cycle apparatus 10 of the present embodiment will be described. In the refrigeration cycle apparatus 10 of the present embodiment, in the heating mode, the high pressure refrigerant discharged from the compressor 11 is made to flow in the order of the high temperature side water-refrigerant heat exchanger 12 → the overcooling side indoor condenser 14 to obtain the first air. In the passage 50a, the blowing air (generally, the outside air) which is relatively low temperature can be heated stepwise and efficiently in the order of the overcooling side indoor condenser 14 → the high temperature side heater core 22.

Furthermore, in the first air passage 50a in the first dehumidifying and heating mode, high pressure refrigerant is caused to flow at least into the overcooling side indoor condenser 14, and the cooled air dehumidified by the indoor evaporator 17 is on the overcooling side. It can be reheated by the indoor condenser 14. Therefore, the operation mode can be switched with a simple configuration in which the low pressure refrigerant does not need to flow into the high temperature side water-refrigerant heat exchanger 12 or the supercooling side indoor condenser 14.

Further, in the heating mode, the refrigerant is supercooled by heat exchange with the relatively low temperature blowing air (generally the outside air) in the supercooling side indoor condenser 14, and the supercooling side indoor condenser 14 Can sufficiently reduce the enthalpy of the refrigerant flowing out of the Therefore, it is possible to suppress the decrease in the heating capacity of the blowing air in the high temperature side heater core 22 and the overcooling side indoor condenser 14 by increasing the heat absorption amount of the refrigerant in the chiller 18.

Further, in the first dehumidifying and heating mode, the refrigerant is supercooled by heat exchange with the blown air cooled by the indoor evaporator 17 in the supercooling side indoor condenser 14, and the supercooling side indoor condenser 14 It is possible to sufficiently reduce the enthalpy of the refrigerant flowing out. Therefore, the heat absorption amount of the refrigerant in the indoor evaporator 17 can be increased, and the decrease in the heating capacity of the blown air in the supercooling side indoor condenser 14 can be suppressed.

That is, according to the refrigeration cycle apparatus 10 of the present embodiment, even if the operation mode is switched with a simple configuration, it is possible to suppress the decrease in the heating capacity of the blowing air in the high temperature side heater core 22 and the subcooling side indoor condenser 14 .

Further, the refrigeration cycle apparatus 10 of the present embodiment includes the chiller 18, and the low temperature side heat medium circuit 30 is provided with the battery cooling unit as the on-vehicle device 32 and the low temperature side radiator 33. Then, in the heating mode, the low pressure refrigerant decompressed by the heat absorption expansion valve 16b flows into the chiller 18, and in the first dehumidifying heating mode, the low pressure refrigerant decompressed by the cooling expansion valve 16a to the indoor evaporator 17 It is flowing.

According to this, in the heating mode, the blown air can be reliably heated by using the waste heat of the on-vehicle device 32 or the heat absorbed from the outside air as a heat source.

Further, in the refrigeration cycle apparatus 10 of the present embodiment, the high temperature side water-refrigerant heat exchanger 12, the high temperature side heater core 22 and the like constitute a first heating unit, and the high temperature side radiator 23 is disposed in the high temperature side heat medium circuit 20. doing.

Then, in the heating mode, the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 is made to flow into the high temperature side heater core 22, and the heat of the high temperature side heat medium is radiated to the blast air. On the other hand, in the cooling mode, the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 is made to flow into the high temperature side radiator 23, and the heat of the high temperature side heat medium is radiated to the outside air.

According to this, not only can the heated air be heated by the high temperature side heater core 22 in the heating mode, but also the heat generated by the refrigerant from the air in the indoor evaporator 17 in the cooling mode, the high temperature side heat medium Can be dissipated to the outside air at the high temperature side radiator 23 via the Therefore, it is possible to switch to the cooling mode with a simple configuration that does not require the low pressure refrigerant to flow into the high temperature side water-refrigerant heat exchanger 12 or the overcooling side indoor condenser 14.

Moreover, in the refrigerating cycle device 10 of the present embodiment, the receiver 13 is provided. According to this, it becomes easy to supply the liquid phase refrigerant to the supercooling side indoor condenser 14, and the supercooling side indoor condenser 14 functions as a supercooling heat exchanger (so-called subcooler) for supercooling the refrigerant. Cheap. Therefore, it is possible to suppress the decrease in the heating capacity of the blowing air in the high temperature side heater core 22 and the supercooling side indoor condenser 14 more effectively.

Moreover, in the refrigeration cycle apparatus 10 of the present embodiment, the supercooling side indoor condenser 14 that directly exchanges heat between the refrigerant and the blown air is adopted as the second heating unit. Therefore, the heating efficiency of the blowing air can be improved as compared with the case of indirectly performing heat exchange via a heat medium such as antifreeze liquid.

Furthermore, since the first air mix door 54a as the heat release amount adjustment unit is disposed in the indoor air conditioning unit 50, the heat release amount from the refrigerant to the blast air in the subcooling side indoor condenser 14 can be easily adjusted. .

Then, in the cooling mode, the first air mix door 54a reduces the air volume of the blowing air flowing into the overcooling side indoor condenser 14 more than the heating mode. Therefore, in the cooling mode, it is possible to perform the efficient cooling of the vehicle interior by suppressing the reheating of the blown air in the supercooling side indoor condenser 14.

Further, in the first dehumidifying and heating mode of the refrigeration cycle apparatus 10 of the present embodiment, the refrigerant evaporation temperature Tefin in the indoor evaporator 17 is a reference temperature (specifically, 1 ° C.) at which frost formation on the indoor evaporator 17 can be suppressed. As described above, since the operation of the compressor 11 is controlled, frost formation of the indoor evaporator 17 can be suppressed.

Furthermore, in the first dehumidifying and heating mode, the operation of the first air mix door 54a is controlled so that the degree SC of subcooling of the refrigerant flowing out from the subcooling side indoor condenser 14 approaches the target degree of subcooling KSC. It can be reliably suppressed that the heating capacity of the blowing air in the cooling side indoor condenser 14 is reduced.

Further, in the second dehumidifying and heating mode of the refrigeration cycle apparatus 10 of the present embodiment, the operation of the compressor 11 is controlled so that the blown air temperature TAV approaches the target blowing temperature TAO, so that comfortable heating of the vehicle compartment is realized. can do. At this time, the refrigeration cycle apparatus 10 according to the present embodiment includes the evaporation pressure control valve 19, so that frost formation of the indoor evaporator 17 can be suppressed regardless of the refrigerant discharge capacity of the compressor 11.

Furthermore, in the second dehumidifying and heating mode, since the operation of the first air mix door 54a is controlled so that the degree of subcooling SC of the refrigerant flowing out from the subcooling side indoor condenser 14 approaches the target degree of subcooling KSC, It can be reliably suppressed that the heating capacity of the blowing air in the side indoor condenser 14 is reduced.

Second Embodiment
In the present embodiment, an example in which the configuration of the refrigeration cycle apparatus 10 is changed as shown in the overall configuration diagram of FIG. 5 with respect to the first embodiment will be described. In FIG. 5, the same or equivalent parts as in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings. Specifically, in the present embodiment, the supercooling side water-refrigerant heat exchanger 14a is employed in place of the supercooling side indoor condenser 14 described in the first embodiment.

The supercooling side water-refrigerant heat exchanger 14a exchanges heat between the liquid phase refrigerant flowing out of the receiver 13 and the supercooling side heat medium circulating in the supercooling side heat medium circuit 40 to supercool the liquid phase refrigerant. And a heat exchanger for heating the subcooling side heat medium. As the supercooling side heat medium, a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted.

Here, the overcooling side heat medium circuit 40 is a water circuit that circulates the overcooling side heat medium. In the subcooling side heat medium circuit 40, the water passage of the subcooling side water-refrigerant heat exchanger 14a, the subcooling side heat medium pump 41, and the subcooling side heater core 42 are disposed. In other words, the overcooling side heat medium circuit 40 is a water circuit that circulates the overcooling side heat medium between the overcooling side water-refrigerant heat exchanger 14 a and the overcooling side heater core 42.

The supercooling side heat medium pump 41 is a supercooling side water pump that pumps the supercooling side heat medium to the inlet side of the water path of the supercooling side water-refrigerant heat exchanger 14a in the supercooling side heat medium circuit 40. . The supercooling-side heat medium pump 41 is an electric pump whose rotational speed (that is, hydraulic feed capacity) is controlled by a control voltage output from the air conditioning controller 60.

The supercooling side heater core 42 is disposed in the casing 51 of the indoor air conditioning unit 50. The supercooling side heater core 42 thermally exchanges the heat of the supercooling side heat medium heated by the supercooling side water-refrigerant heat exchanger 14a with the blast air having passed through the indoor evaporator 17 to heat the blast air. It is an exchanger.

Therefore, in the present embodiment, the second heating unit is disposed by the supercooling side heat medium pump 41, the supercooling side water-refrigerant heat exchanger 14a, the supercooling side heater core 42, and the like disposed in the subcooling side heat medium circuit 40. Is configured.

Furthermore, as shown in the cross-sectional view of FIG. 6, the supercooling side heater core 42 is disposed across the first air passage 50a and the second air passage 50b through the mounting holes formed in the dividing member 51a. It is done. The supercooling side heater core 42 is disposed downstream of the indoor evaporator 17 in the flow of the blown air and upstream of the first air mix door 54a and the second air mix door 54b in the flow of the blown air.

For this reason, in the present embodiment, by adjusting the flow rate of the overcooling side heat medium that the overcooling side heat medium pump 41 causes the overcooling side heater core 42 to flow, the overcooling side heater core 42 dissipates heat into the blown air. The amount of heat is adjusted. Therefore, the subcooling side heat medium pump 41 of the present embodiment constitutes a heat release amount adjustment unit. The inlet side of the branch portion 15a is connected to the outlet of the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a.

Further, in the air conditioning control device 60 of the present embodiment, the configuration for controlling the operation of the overcooling side heat medium pump 41 is the overcooling side pumping capacity control unit 60g shown in FIG. Since the supercooling side heat medium pump 41 of the present embodiment is a heat release amount adjustment unit, the supercooling side pressure feeding capacity control unit 60g is a heat release amount control unit. The other configuration is the same as that of the first embodiment.

Next, the operation of the present embodiment in the above configuration will be described.

(A) Cooling Mode In the cooling mode, the air conditioning controller 60 stops the overcooling side heat medium pump 41. The other operations are the same as in the first embodiment. Therefore, the refrigeration cycle apparatus 10 in the cooling mode can operate substantially in the same manner as the cooling mode of the first embodiment, and can perform cooling of the vehicle interior as in the first embodiment.

(B) Heating Mode In the heating mode, the air conditioning control device 60 operates the supercooling side heat medium pump 41 so as to exert the water pressure transfer capability in the predetermined heating mode. The other operations are the same as in the first embodiment.

Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, when the liquid phase refrigerant separated by the receiver 13 flows into the refrigerant passage of the supercooling side water-refrigerant heat exchanger 14a, the liquid phase refrigerant and the supercooling side heat medium are heat Exchange. Thereby, the liquid phase refrigerant is subcooled and the subcooling side heat medium is heated.

In the subcooling-side heat medium circuit 40, the subcooling-side heat medium heated in the subcooling-side water-refrigerant heat exchanger 14 a flows into the subcooling-side heater core 42. The supercooling side heat medium that has flowed into the supercooling side heater core 42 exchanges heat with the blowing air that has passed through the indoor evaporator 17 and radiates heat. Thereby, the blowing air which flows in into high temperature side heater core 22 is heated.

The other operations are the same as in the heating mode of the first embodiment. Accordingly, in the heating mode refrigeration cycle apparatus 10, heating of the passenger compartment can be performed as in the first embodiment.

(C) First and second dehumidifying and heating modes In the first and second dehumidifying and heating modes, the air conditioning control device 60 causes the subcooling degree SC detected by the subcooling degree sensor 62e to approach the target subcooling degree KSC. The supercooling side heat medium pump 41 is operated. As a result, the amount of heat released to the air by the supercooling side heater core 42 is adjusted.

The other operations are the same as in the first embodiment. Therefore, in the refrigeration cycle apparatus 10 in the first and second dehumidifying and heating modes, dehumidifying and heating of the passenger compartment can be performed as in the first embodiment.

The refrigeration cycle apparatus 10 of the present embodiment operates as described above, so that the same effect as that of the first embodiment can be obtained.

That is, various operation modes can be switched with a simple configuration in which the low pressure refrigerant does not need to flow into the high temperature side water-refrigerant heat exchanger 12 or the supercooling side water / refrigerant heat exchanger 14a. Furthermore, similarly to the first embodiment, even if the operation mode is switched, it is possible to suppress the decrease in the heating capacity of the blown air in the high temperature side heater core 22 and the subcooling side heater core 42.

Further, in the refrigeration cycle apparatus 10 of the present embodiment, the second cooling unit is configured by the supercooling side water-refrigerant heat exchanger 14a, the supercooling side heater core 42, and the like. Furthermore, since the overcooling side heat medium pump 41 as the heat release amount adjustment unit is disposed in the overcooling side heat medium circuit 40, the heat release amount from the overcooling side heat medium in the overcooling side heater core 42 to the blowing air is It can be easily adjusted.

Then, in the cooling mode, the overcooling side heat medium pump 41 stops the overcooling side heat medium pump 41. That is, the flow rate of the overcooling side heat medium which causes the overcooling side heat medium pump 41 to flow into the overcooling side heater core 42 in the heating mode is decreased. Therefore, in the cooling mode, it is possible to suppress the reheating of the blown air by the supercooling side heater core 42, and perform the efficient cooling of the vehicle interior.

In addition to this, according to the second heating unit of the present embodiment, the supercooling side heater core 42 can be disposed upstream of the first air mix door 54a and the second air mix door 54b in the flow of the blowing air. According to this, the degree of freedom of the arrangement (layout) of the second heating unit (specifically, the supercooling side heater core 42) can be improved, and the indoor air conditioning unit 50 can be miniaturized.

Third Embodiment
In the present embodiment, an example in which the configuration of the first heating unit is changed as shown in FIG. 8 with respect to the first embodiment will be described. Specifically, in the present embodiment, the indoor condenser 12a is employed as the first heating unit. Furthermore, in the high temperature side heat medium circuit 20 of the present embodiment, the high temperature side heater core 22 and the high temperature side flow rate adjustment valve 24 are eliminated.

The indoor condenser 12 a is disposed in the casing 51 of the indoor air conditioning unit 50 in the same manner as the high temperature side heater core 22 of the first embodiment. The indoor condenser 12a is a heat exchanger that heats the blown air by heat exchange between the refrigerant discharged from the compressor 11 and the blown air that has passed through the overcooling side indoor condenser 14 or the indoor evaporator 17. Further, in the high temperature side water-refrigerant heat exchanger 12 of the present embodiment, the refrigerant flowing out of the indoor condenser 12a exchanges heat with the high temperature side heat medium circulating in the high temperature side heat medium circuit 20.

Further, in the high temperature side heat medium circuit 20 of the present embodiment, the high temperature side heat medium is circulated between the high temperature side water-refrigerant heat exchanger 12 and the high temperature side radiator 23. For this reason, in the high temperature side heat medium circuit 20 of the present embodiment, when the high temperature side heat medium pump 21 is operated, when the high temperature side heat medium passes through the water passage of the high temperature side water-refrigerant heat exchanger 12, The heat absorbed can be dissipated to the outside air by the high temperature side radiator 23. The other configuration is the same as that of the first embodiment.

Next, the operation of the present embodiment in the above configuration will be described. In the present embodiment, the air conditioning control device 60 operates the high temperature side heat medium pump 21 so as to exert a pressure feeding capability for the cooling mode, which is determined in advance, in the cooling mode. In the heating mode and in the first and second dehumidifying and heating modes, the high temperature side heat medium pump 21 is stopped. The other operations are the same as in the first embodiment. Hereinafter, the operation of each operation mode will be described.

(A) Cooling Mode In the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a. In the cooling mode, the first air mixing door 54a and the second air mixing door 54b completely close the air passage on the indoor condenser 12a side. Therefore, the refrigerant flowing into the indoor condenser 12a does not exchange heat with the blown air, and the high pressure refrigerant flowing into the indoor condenser 12a flows out from the indoor condenser 12a with almost no heat dissipation.

The refrigerant flowing out of the indoor condenser 12 a flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. In the cooling mode, since the high temperature side heat medium pump 21 is operating, the high temperature side water-refrigerant heat exchanger 12 exchanges heat between the high pressure refrigerant and the high temperature side heat medium. Thereby, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated. The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid.

In the high temperature side heat medium circuit 20, the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23. The high temperature side heat medium flowing into the high temperature side radiator 23 exchanges heat with the outside air and radiates heat. That is, in the high temperature side radiator 23, the heat of the high temperature side heat medium is radiated to the outside air. 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 high temperature side water-refrigerant heat exchanger 12.

The other operations are the same as in the cooling mode of the first embodiment. Accordingly, in the cooling mode, the blowing air cooled by the indoor evaporator 17 can be blown into the vehicle compartment to perform cooling of the vehicle compartment.

(B) Heating mode and first and second dehumidifying heating modes In the heating mode and the first and second dehumidifying and heating modes, the air-conditioning control device 60 controls the first air mix door 54a and the first air mixing door as in the first embodiment. 2 Move the air mix door 54b. Therefore, in the indoor condenser 12a, the high pressure refrigerant discharged from the compressor 11 and the air blown from the blower 52 exchange heat, and the air is heated. That is, in the indoor condenser 12a, the heat of the high pressure refrigerant discharged from the compressor 11 is radiated to the blowing air.

The refrigerant flowing out of the indoor condenser 12 a flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. In the heating mode, the high temperature side heat medium pump 21 is stopped. Therefore, the refrigerant flowing into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 hardly exchanges heat with the high temperature side heat medium when the temperature of the high temperature side heat medium rises to the same temperature as the refrigerant. leak. The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid.

The other operations are the same as in the first embodiment. Therefore, at the time of the heating mode, it is possible to heat the vehicle interior by blowing the blown air heated by the supercooling side indoor condenser 14 and the indoor condenser 12a into the vehicle interior. Furthermore, in the first and second dehumidifying and heating modes, the blown air which has been cooled and dehumidified by the indoor evaporator 17 is reheated by the supercooling side indoor condenser 14 and the indoor condenser 12a and blown out into the vehicle compartment. Thus, dehumidifying and heating of the passenger compartment can be performed.

Furthermore, in the present embodiment, the high temperature side heat medium circuit 20 is configured to circulate the high temperature side heat medium between the high temperature side water-refrigerant heat exchanger 12 and the high temperature side radiator, and as the first heating unit The indoor condenser 12a is adopted.

And in heating mode, the heat which the high pressure refrigerant | coolant discharged from the compressor 11 by the indoor condenser 12a has is released to blowing air. On the other hand, in the cooling mode, the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 is made to flow into the high temperature side radiator 23, and the heat of the high temperature side heat medium is radiated to the outside air.

According to this, in the heating mode or the like, the indoor condenser 12a can directly exchange heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air, so indirectly through the heat medium In contrast to the case of heat exchange, the heating efficiency of the blown air can be improved. Therefore, the heating capacity of the blowing air in the first heating unit can be improved.

Further, in the cooling mode, the heat absorbed by the refrigerant from the blown air by the indoor evaporator 17 can be dissipated to the outside air by the high temperature side radiator 23 through the high temperature side heat medium. Therefore, the operation mode can be switched with a simple configuration in which the low pressure refrigerant does not have to flow into the indoor condenser 12a or the supercooling side indoor condenser 14.

Fourth Embodiment
In the present embodiment, as shown in FIG. 9, an example in which the configuration of the first heating unit is changed as in the third embodiment will be described with respect to the second embodiment. That is, in the refrigeration cycle apparatus 10 of the present embodiment, the indoor condenser 12a is employed as the first heating unit. Furthermore, the high temperature side heater core 22 and the high temperature side flow control valve 24 of the high temperature side heat medium circuit 20 are eliminated. The other configuration is the same as that of the second embodiment.

Next, the operation of the present embodiment in the above configuration will be described. In the present embodiment, the air conditioning control device 60 stops the overcooling side heat medium pump 41 in the cooling mode as in the second embodiment. In the heating mode and in the first and second dehumidifying and heating modes, the supercooling side heat medium pump 41 is operated.

Furthermore, the air conditioning controller 60 operates the high temperature side heat medium pump 21 in the cooling mode as in the third embodiment. In the heating mode, the first dehumidifying heating mode, and the second dehumidifying heating mode, the high temperature side heat medium pump 21 is stopped. The other operations are similar to those of the second embodiment. Hereinafter, the operation of each operation mode will be described.

(A) Cooling Mode In the cooling mode, since the overcooling side heat medium pump 41 is stopped, the blowing air is not heated by the overcooling side heater core 42 using the overcooling side heat medium as a heat source. Furthermore, since the high temperature side heat medium pump 21 is operating, it can operate substantially in the same manner as the third embodiment to cool the vehicle interior.

(B) Heating mode and first and second dehumidifying and heating modes In the heating mode and first and second dehumidifying and heating modes, high-pressure refrigerant discharged from the compressor 11 is condensed in the room as in the third embodiment. The heat is exchanged with the blown air that has passed through the subcooling side heater core 42 in the vessel 12a. As a result, the air that has passed through the supercooling side heater core 42 is heated.

The refrigerant flowing out of the indoor condenser 12 a flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. In the heating mode and the first and second dehumidifying heating modes, since the high temperature side heat medium pump 21 is stopped, the refrigerant flowing into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 is the same as the third embodiment. In addition, it flows out with almost no heat exchange with the high temperature side heat medium. The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid.

The liquid phase refrigerant flowing out of the receiver 13 flows into the refrigerant passage of the supercooling side water-refrigerant heat exchanger 14a. In the heating mode and the first and second dehumidifying heating modes, since the supercooling side heat medium pump 41 is operating, the liquid phase refrigerant flowing into the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a is excessive. Heat exchange with the cooling side heat medium. Thereby, the liquid phase refrigerant is subcooled and the subcooling side heat medium is heated.

The supercooling side heat medium heated in the subcooling side water-refrigerant heat exchanger 14a exchanges heat with the air which has passed through the indoor evaporator 17 in the supercooling side heater core 42, as in the second embodiment. Do. Thereby, the blowing air which passes the indoor evaporator 17 and flows in into the indoor condenser 12a is heated.

The other operations are similar to those of the second embodiment. Therefore, in the heating mode, heating the vehicle interior can be performed by blowing out the blown air heated by the supercooling side heater core 42 and the indoor condenser 12a into the vehicle interior. Furthermore, in the first and second dehumidifying and heating modes, the blown air which has been cooled and dehumidified by the indoor evaporator 17 is reheated by the supercooling side heater core 42 and the indoor condenser 12a and blown out into the vehicle compartment. , Dehumidifying and heating of the passenger compartment can be performed.

The refrigeration cycle apparatus 10 of this embodiment can operate as described above to obtain the same effect as that of the second embodiment.

Furthermore, in the present embodiment, the high temperature side heat medium circuit 20 is configured to circulate the high temperature side heat medium between the high temperature side water-refrigerant heat exchanger 12 and the high temperature side radiator, and as the first heating unit The indoor condenser 12a is adopted. Therefore, as in the third embodiment, the heating capacity of the blown air in the first heating unit can be improved in the heating mode or the like. In addition, the operation mode can be switched with a simple configuration in which the low-pressure refrigerant does not have to flow into the indoor condenser 12 a or the overcooling side indoor condenser 14.

Fifth Embodiment
In this embodiment, an example in which the configuration of the high temperature side heat medium circuit 20 is changed as shown in FIG. 10 with respect to the third embodiment will be described. Specifically, in the high temperature side heat medium circuit 20 of the present embodiment, a supercooling side water-refrigerant heat exchanger 14a is added to the third embodiment. Furthermore, in the refrigeration cycle apparatus 10 of the present embodiment, a high-pressure side three-way valve 71 and a supercooling side three-way valve 72 are added to the third embodiment.

The supercooling side water-refrigerant heat exchanger 14a of the present embodiment exchanges heat between the refrigerant flowing out of the supercooling side indoor condenser 14 and the high temperature side heat medium circulating in the high temperature side heat medium circuit 20 in the cooling mode. Thus, the function of radiating the heat of the refrigerant to the high temperature side heat medium (that is, the function of supercooling the refrigerant) is performed.

In the high temperature side heat medium circuit 20 of the present embodiment, when the air conditioning controller 60 operates the high temperature side heat medium pump 21, the high temperature side heat medium is the discharge port of the high temperature side heat medium pump 21 → high temperature side water-refrigerant heat The high temperature side heat medium circulates in the order of the water passage of the exchanger 12 → the supercooling side water-water passage of the refrigerant heat exchanger 14a → the high temperature side radiator 23 → the suction port of the high temperature side heat medium pump 21.

In addition, the high-pressure side three-way valve 71 switches the refrigerant circuit leading the high-pressure refrigerant discharged from the compressor 11 to the indoor condenser 12a and the refrigerant circuit leading to the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 It is a switching valve. The operation of the high-pressure side three-way valve 71 is controlled by the control voltage output from the air conditioning controller 60.

The supercooling side three-way valve 72 switches between the refrigerant circuit leading the refrigerant flowing out of the receiver 13 to the subcooling side indoor condenser 14 and the refrigerant circuit leading the refrigerant side of the subcooling side water-refrigerant heat exchanger 14a. It is a switching valve. The basic configuration of the overcooling side three-way valve 72 is similar to that of the high pressure side three-way valve 71. The other configuration is the same as that of the first embodiment.

Next, the operation of the present embodiment in the above configuration will be described. In the present embodiment, the air conditioning control device 60 operates the high temperature side heat medium pump 21 in the cooling mode as in the third embodiment. In the heating mode and in the first and second dehumidifying and heating modes, the high temperature side heat medium pump 21 is stopped.

Further, in the cooling mode, the air conditioning control device 60 controls the operation of the high pressure side three-way valve 71 so as to lead the high pressure refrigerant discharged from the compressor 11 to the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12, The operation of the subcooling side three-way valve 72 is controlled so as to lead the refrigerant flowing out of the fuel cell 13 to the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a.

Furthermore, in the heating mode and in the first and second dehumidifying and heating modes, the operation of the high-pressure side three-way valve 71 is controlled to lead the high-pressure refrigerant discharged from the compressor 11 to the indoor condenser 12a, and it flows out from the receiver 13. The operation of the subcooling side three-way valve 72 is controlled so as to lead the refrigerant to the subcooling side indoor condenser 14. The other operations are the same as in the first embodiment. Hereinafter, the operation of each operation mode will be described.

(A) Cooling Mode In the cooling mode, the high pressure refrigerant discharged from the compressor 11 flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 via the high pressure side three-way valve 71. In the high temperature side 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. Thereby, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated. The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid.

The liquid phase refrigerant flowing out of the receiver 13 flows into the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a via the subcooling side three-way valve 72. In the subcooling side water-refrigerant heat exchanger 14a, since the high temperature side heat medium pump 21 is operating, the liquid phase refrigerant and the high temperature side heat medium exchange heat. Thereby, the liquid phase refrigerant is subcooled and the high temperature side heat medium is heated.

In the high temperature side heat medium circuit 20, the high temperature side heat medium heated in the order of the high temperature side water-refrigerant heat exchanger 12 → the supercooling side water / refrigerant heat exchanger 14a flows into the high temperature side radiator 23. 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 high temperature side water-refrigerant heat exchanger 12.

(B) Heating mode and first and second dehumidifying heating modes In the heating mode and the first and second dehumidifying and heating modes, the high pressure refrigerant discharged from the compressor 11 is indoors through the high pressure side three-way valve 71. It flows into the condenser 12a. In the indoor condenser 12a, the blown air is heated as in the third embodiment.

The refrigerant flowing out of the indoor condenser 12 a flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. In the heating mode and the first and second dehumidifying heating modes, since the high temperature side heat medium pump 21 is stopped, the refrigerant flowing into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 is the third embodiment and Similarly, it flows out with almost no heat exchange with the high temperature side heat medium. The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid.

The liquid-phase refrigerant flowing out of the receiver 13 flows into the subcooling side indoor condenser 14 via the subcooling side three-way valve 72. In the supercooling side indoor condenser 14, as in the first embodiment, the liquid phase refrigerant is subcooled and the blowing air is heated.

The refrigerant flowing out of the subcooling side indoor condenser 14 flows into the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a. In the heating mode and the first and second dehumidifying and heating modes, the high temperature side heat medium pump 21 is stopped. Therefore, the refrigerant flowing into the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a exchanges heat with the high temperature side heat medium almost when the temperature of the high temperature side heat medium rises to the same temperature as the refrigerant. Spill out.

The refrigeration cycle apparatus 10 of this embodiment can operate as described above to obtain the same effect as that of the first embodiment.

Further, in the present embodiment, the supercooling side water-refrigerant heat exchanger 14a which exchanges heat between the refrigerant flowing out from the supercooling side indoor condenser 14 and the high temperature side heat medium flowing out from the high temperature side water-refrigerant heat exchanger 12. Is equipped. Therefore, in the cooling mode, the refrigerant flowing out of the subcooling side indoor condenser 14 can be further subcooled, and the cooling capacity of the blown air in the indoor evaporator 17 can be further improved.

Further, in the present embodiment, since the high-pressure side three-way valve 71 and the overcooling side three-way valve 72 are provided, the high-pressure refrigerant discharged from the compressor 11 during the cooling mode is the indoor condenser 12a and the overcooling side indoor condenser 14 will never be distributed. According to this, it is possible to improve the COP by suppressing the occurrence of unnecessary pressure loss in the refrigerant circulating in the refrigeration cycle apparatus 10.

Sixth Embodiment
In this embodiment, an example in which the configuration of the high-temperature side heat medium circuit 20 is changed as shown in FIG. 11 with respect to the third embodiment will be described. Specifically, in the high temperature side heat medium circuit 20 of the present embodiment, a supercooling side water-refrigerant heat exchanger 14a is added as in the fifth embodiment. Furthermore, the arrangement of the high temperature side heat medium pump 21 is changed.

In the high temperature side heat medium circuit 20 of the present embodiment, when the air conditioning controller 60 operates the high temperature side heat medium pump 21, the high temperature side heat medium is discharged from the discharge port of the high temperature side heat medium pump 21 → high temperature side radiator 23 → excess The water is circulated in the order of the water passage of the cooling side water-refrigerant heat exchanger 14a → the water passage of the high temperature side water−refrigerant heat exchanger 12 → the suction port of the high temperature side heat medium pump 21. The other configuration is the same as that of the first embodiment.

Next, the operation of the present embodiment in the above configuration will be described. In the present embodiment, the air conditioning control device 60 operates the high temperature side heat medium pump 21 in the cooling mode. In the heating mode and in the first and second dehumidifying and heating modes, the high temperature side heat medium pump 21 is stopped. The other operations are the same as in the first embodiment. Hereinafter, the operation of each operation mode will be described.

(A) Cooling Mode In the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a. The high-pressure refrigerant flowing into the indoor condenser 12a flows out with almost no heat release in the indoor condenser 12a, as in the third embodiment.

The refrigerant flowing out of the indoor condenser 12 a flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. In the cooling mode, since the high temperature side heat medium pump 21 is operating, in the high temperature side water-refrigerant heat exchanger 12, the high temperature side flowing out from the water passage of the high pressure refrigerant and the supercooling side water-refrigerant heat exchanger 14a. The heat medium exchanges heat. Thereby, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid. The liquid-phase refrigerant flowing out of the receiver 13 flows into the supercooling side indoor condenser 14. As in the third embodiment, the liquid-phase refrigerant flowing into the supercooling side indoor condenser 14 flows out with almost no heat release in the supercooling side indoor condenser 14.

The refrigerant flowing out of the subcooling side indoor condenser 14 flows into the refrigerant passage of the subcooling side water-refrigerant heat exchanger 14a. In the cooling mode, since the high temperature side heat medium pump 21 operates, the liquid refrigerant and the high temperature side heat medium flowing out from the high temperature side radiator 23 exchange heat in the supercooling side water-refrigerant heat exchanger 14a. Thereby, the liquid phase refrigerant is subcooled and the high temperature side heat medium is heated.

(B) Heating mode and first and second dehumidifying heating modes In the heating mode and the first and second dehumidifying and heating modes, the high-temperature side heat medium pump 21 is stopped, so substantially the fifth embodiment And the first and second dehumidifying heating modes.

Therefore, at the time of the heating mode, it is possible to heat the vehicle interior by blowing the blown air heated by the supercooling side indoor condenser 14 and the indoor condenser 12a into the vehicle interior. Furthermore, in the first and second dehumidifying and heating modes, the blown air which has been cooled and dehumidified by the indoor evaporator 17 is reheated by the supercooling side indoor condenser 14 and the indoor condenser 12a and blown out into the vehicle compartment. Thus, dehumidifying and heating of the passenger compartment can be performed.

Further, in the present embodiment, the supercooling side water-refrigerant heat exchanger (heat exchange between the refrigerant flowing out from the subcooling side indoor condenser 14 and the high temperature side heat medium flowing out from the high temperature side water-refrigerant heat exchanger 12 14a) is provided. Therefore, as in the fifth embodiment, the cooling capacity of the blowing air in the indoor evaporator 17 can be further improved in the cooling mode.

At this time, in the refrigeration cycle apparatus 10 of the present embodiment, the refrigerant flows in the order of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 → the receiver 13 → the refrigerant passage of the supercooling side water / refrigerant heat exchanger 14a, In the heat medium circuit 20, the high temperature side heat medium flows in the order of the water passage of the supercooling side water-refrigerant heat exchanger 14a to the water passage of the high temperature side water-refrigerant heat exchanger 12.

According to this, the temperature difference between the refrigerant and the high temperature side heat medium in the high temperature side water-refrigerant heat exchanger 12 and the subcooling side water-refrigerant heat exchanger 14a as in the so-called counterflow heat exchanger The heat exchange efficiency can be improved by securing it.

Seventh Embodiment
In the present embodiment, an example in which the configuration of the high-temperature side heat medium circuit 20 is changed as shown in FIG. 12 with respect to the fourth embodiment will be described. Specifically, the subcooling side water-refrigerant heat exchanger 14a is disposed in the high temperature side heat medium circuit 20 of the present embodiment, and the heat medium three-way valve 25, the heat medium bypass passage 26, and the subcooling side heater core 42 are provided. Has been added. Furthermore, the arrangement of the high temperature side heat medium pump 21 is changed.

The heat medium three-way valve 25 is a heat medium circuit that causes the refrigerant flowing out of the high temperature side radiator 23 to be drawn to the high temperature side heat medium pump 21 and a heat medium made to draw the refrigerant flowing out of the supercooling side heater core 42 to the high temperature side heat medium pump 21 It is a three-way switching valve that switches to the medium circuit. The operation of the heat medium three-way valve 25 is controlled by the control voltage output from the air conditioning controller 60.

The heat medium bypass passage 26 is a heat medium passage that guides the high temperature side heat medium flowing out of the water passage of the high temperature side water-refrigerant heat exchanger 12 to the supercooling side heater core 42 without flowing into the high temperature side radiator 23. .

Therefore, in the high temperature side heat medium circuit 20 of the present embodiment, the high temperature side is switched to the heat medium circuit in which the air conditioning control device 60 causes the refrigerant flowing out of the high temperature side radiator 23 to be sucked into the high temperature side heat medium pump 21. When the heat medium pump 21 is operated, the discharge port of the high temperature side heat medium pump 21 → water passage of the supercooling side water—refrigerant heat exchanger 14a → water passage of the high temperature side water—refrigerant heat exchanger 12 → high temperature side radiator 23 The high temperature side heat medium circulates in the order of the heat medium three-way valve 25 and the suction port of the high temperature side heat medium pump 21.

Further, when the high temperature side heat medium pump 21 is operated while the air conditioning control device 60 is switching to a heat medium circuit that causes the refrigerant flowing out of the supercooling side heater core 42 to be drawn to the high temperature side heat medium pump 21, Discharge port of medium pump 21 → supercooling side water-water passage of refrigerant heat exchanger 14 a → high temperature side water-water passage of refrigerant heat exchanger 12 → heat medium bypass passage 26 → supercooling side heater core 42 → heat medium three-way valve The high temperature side heat medium circulates in the order of 25 → the suction port of the high temperature side heat medium pump 21.

Therefore, in the present embodiment, the high temperature side heat medium pump 21 disposed in the high temperature side heat medium circuit 20, the high temperature side water-refrigerant heat exchanger 12, the supercooling side water-refrigerant heat exchanger 14a, and the supercooling side heater core The second heating unit is configured by 42 and the like. The other configuration is the same as that of the fourth embodiment.

Next, the operation of the present embodiment in the above configuration will be described. In the present embodiment, the high-temperature side heat medium pump 21 is operated so that the air conditioning control device 60 exerts a pumping capability predetermined for each operation mode in any operation mode.

Further, the air conditioning control device 60 controls the operation of the heat medium three-way valve 25 so as to switch to the heat medium circuit that causes the high temperature side heat medium pump 21 to suck the high temperature side heat medium flowing out of the high temperature side radiator 23 in the cooling mode. . Further, in the heating mode and in the first and second dehumidifying heating modes, the heat medium three-way valve is switched so that the high temperature side heat medium flowing out from the supercooling side heater core 42 is switched to the heat medium circuit which sucks the high temperature side heat medium pump 21. Control the operation of 25.

The other operations are the same as in the first embodiment. Hereinafter, the operation of each operation mode will be described.

(A) Cooling Mode In the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a. The high-pressure refrigerant flowing into the indoor condenser 12a flows out with almost no heat release in the indoor condenser 12a, as in the fourth embodiment.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid.

The liquid phase refrigerant flowing out of the receiver 13 flows into the refrigerant passage of the supercooling side water-refrigerant heat exchanger 14a. In the cooling mode, since the high temperature side heat medium pump 21 operates, the liquid refrigerant and the high temperature side heat medium flowing out from the high temperature side radiator 23 exchange heat in the supercooling side water-refrigerant heat exchanger 14a. Thereby, the liquid phase refrigerant is subcooled and the high temperature side heat medium is heated.

In the high temperature side heat medium circuit 20, the high temperature side heat medium heated in the order of the subcooling side water-refrigerant heat exchanger 14 a → the high temperature side water / refrigerant heat exchanger 12 flows into the high temperature side radiator 23. 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 through the heat medium three-way valve 25 and is pressure-fed again to the water passage of the high temperature side water-refrigerant heat exchanger 12 .

The other operations are the same as in the cooling mode of the fourth embodiment. Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, cooling the vehicle interior can be performed by blowing the blown air cooled by the indoor evaporator 17 into the vehicle interior.

(B) Heating mode and first and second dehumidifying heating modes In the heating mode and the first and second dehumidifying and heating modes, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a. In the indoor condenser 12a, the blown air is heated as in the third embodiment.

The refrigerant flowing out of the indoor condenser 12 a flows into the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12. In the heating mode and the first and second dehumidifying heating modes, the high temperature side heat medium pump 21 is operating, so the high temperature side water-refrigerant heat exchanger 12 exchanges high pressure refrigerant and supercooling side water-refrigerant heat The high temperature side heat medium which flowed out of the water passage of vessel 14a exchanges heat. Thereby, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium is heated.

The refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the receiver 13 and is separated into gas and liquid. The liquid phase refrigerant flowing out of the receiver 13 flows into the refrigerant passage of the supercooling side water-refrigerant heat exchanger 14a. In the heating mode and the first and second dehumidifying heating modes, since the high temperature side heat medium pump 21 is operating, in the supercooling side water-refrigerant heat exchanger 14 a, the liquid phase refrigerant and the supercooling side heater core 42 are The high temperature side heat medium which has flowed out exchanges heat. Thereby, the liquid phase refrigerant is subcooled and the high temperature side heat medium is heated.

In the high temperature side heat medium circuit 20, the high temperature side heat medium whose temperature is increased by absorbing heat from the refrigerant in the order of the subcooling side water-refrigerant heat exchanger 14a → the high temperature side water / refrigerant heat exchanger 12 is the heat medium bypass passage 26 Flows into the subcooling side heater core 42 via the The high temperature side heat medium that has flowed into the supercooling side heater core 42 exchanges heat with the blowing air that has passed through the indoor evaporator 17. Thereby, the blowing air which passes the indoor evaporator 17 and flows in into the indoor condenser 12a is heated.

The other operations are similar to those of the fourth embodiment. Therefore, in the heating mode, heating the vehicle interior can be performed by blowing out the blown air heated by the supercooling side heater core 42 and the indoor condenser 12a into the vehicle interior. Furthermore, in the first and second dehumidifying and heating modes, the blown air which has been cooled and dehumidified by the indoor evaporator 17 is reheated by the supercooling side heater core 42 and the indoor condenser 12a and blown out into the vehicle compartment. , Dehumidifying and heating of the passenger compartment can be performed.

Further, in the present embodiment, the supercooling side water-refrigerant heat exchanger 14a for exchanging heat between the liquid phase refrigerant flowing out of the receiver 13 and the high temperature side heat medium pressure fed from the high temperature side heat medium pump 21 is provided. Therefore, in the cooling mode, the high pressure refrigerant flowing out of the receiver 13 can be further subcooled, and the cooling capacity of the blowing air in the indoor evaporator 17 can be further improved.

At this time, in the refrigeration cycle apparatus 10 of the present embodiment, the refrigerant flows in the order of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 → the receiver 13 → the refrigerant passage of the supercooling side water / refrigerant heat exchanger 14a, In the heat medium circuit 20, the high temperature side heat medium flowing out of the high temperature side radiator 23 flows in the order of the water passage of the supercooling side water-refrigerant heat exchanger 14a to the water passage of the high temperature side water-refrigerant heat exchanger 12.

Therefore, as in the sixth embodiment, the temperature difference between the refrigerant and the high temperature side heat medium in the high temperature side water-refrigerant heat exchanger 12 and the subcooling side water-refrigerant heat exchanger 14a is secured to achieve heat exchange efficiency. Can be improved.

The present disclosure is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present disclosure. In addition, the means disclosed in each of the above embodiments may be combined as appropriate in the feasible range.

Although the above-mentioned embodiment explained the example which applied refrigeration cycle device 10 concerning this indication to an air-conditioner for electric vehicles, application of refrigeration cycle device 10 is not limited to this. For example, the present invention may be applied to an air conditioner for a hybrid vehicle that obtains driving force for traveling the vehicle from both an internal combustion engine and an electric motor. Furthermore, the present invention is not limited to vehicles, and may be applied to stationary heating devices, cooling devices, and the like.

Although the above-mentioned embodiment explained refrigeration cycle device 10 which can be switched to various operation modes, an operation mode is not limited to this. If at least the heating mode and the first dehumidifying and heating mode can be performed, it is possible to obtain the effect of suppressing the decrease in heating capacity. Therefore, the refrigeration cycle apparatus 10 may be applied to an air conditioner that does not operate in the cooling mode. In this case, the high temperature side radiator 23 of the high temperature side heat medium circuit 20 may be eliminated.

Furthermore, in addition to the various operation modes described in the above-described embodiment, it may be possible to switch to the cooling only operation mode. In the cooling only operation mode, the heat absorbed by the low temperature side heat medium from the on-vehicle device 32 is absorbed by the refrigerant, and the high temperature side radiator 23 dissipates the outside air through the high temperature side heat medium. According to this, it is possible to cool the in-vehicle device 32 without air conditioning the vehicle interior.

Further, when the low pressure refrigerant is made to flow into both the indoor evaporator 17 and the chiller 18 in the cooling operation mode or the first dehumidifying heating mode as in the second dehumidifying heating mode, the air conditioning of the vehicle interior is performed. Simultaneously, the on-vehicle device 32 can be cooled.

Each composition of refrigerating cycle device 10 is not limited to what was indicated by the above-mentioned embodiment.

For example, although the example which employ | adopted the electric compressor as the compressor 11 was demonstrated in the above-mentioned embodiment, when applying to the vehicle which has an internal combustion engine, you may employ | adopt an engine drive type compressor. . Furthermore, as the engine-driven compressor, a variable displacement compressor may be employed in which the refrigerant discharge capacity can be adjusted by changing the discharge capacity.

In the above embodiment, an example in which the branch portion 15a has a three-way joint structure is described. However, as the branch portion 15a, the flow rate of the refrigerant flowing from the second heating portion to the cooling expansion valve 16a and the second flow portion A three-system flow control valve may be employed to adjust the refrigerant flow ratio with respect to the flow rate of the refrigerant flowing into the heat absorption expansion valve 16b from the heating unit.

Moreover, in the above-mentioned embodiment, although what can be switched to inside-and-outside air 2 layer mode is employ | adopted as inside-and-outside air introduction mode as indoor air-conditioning unit 50, the indoor air-conditioning unit 50 is not limited to this. It may not have the partitioning member of the casing 51 and can not be switched to the inside / outside air two-layer mode.

In the embodiment described above, the low temperature side radiator 33 and the battery as the in-vehicle device 32 are disposed in the low temperature side heat medium circuit 30, but the low temperature side radiator 33 and the in-vehicle device At least one of 32 may be disposed.

Furthermore, the on-vehicle device 32 is not limited to the battery, and may be any heat-generating device that generates heat during operation. For example, as the in-vehicle device 32, an electric motor that outputs a driving force for traveling, an inverter that converts the frequency of electric power supplied to the electric motor, a charger for charging the battery with electric power, or the like may be adopted. A plurality of heat generating devices may be adopted as the on-vehicle device 32 and connected in parallel or in series to the flow of the low temperature side heat medium.

Moreover, in the above-mentioned embodiment, although the relationship between the high temperature side radiator 23 and the low temperature side radiator 33 is not mentioned, the high temperature side radiator 23 and the low temperature side radiator 33 are not limited to the mutually independent structure.

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

In the second embodiment described above, the supercooling side heater core 42 is located downstream of the indoor evaporator 17 with respect to the flow of the air, and the air flow is more than the first air mix door 54a and the second air mix door 54b. Although the example arrange | positioned at the upstream side was demonstrated, it is not limited to this.

For example, the subcooling side heater core 42 may be disposed in the same manner as the subcooling side indoor condenser 14 of the first embodiment. In this case, the hydraulic transport capacity of the supercooling side heat medium pump 41 is constant during the first and second dehumidifying heating modes, and the opening degree of the first air mix door 54a causes the supercooling side heater core 42 to radiate heat to the blown air. The amount of heat dissipation may be adjusted.

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

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 refrigeration cycle apparatus applied to an air conditioner, comprising:
A compressor (11) that compresses and discharges a refrigerant;
A first heating unit (12, 22, 12a) that heats the blown air blown into the air-conditioned space using the refrigerant discharged from the compressor as a heat source;
And a second heating unit (14, 14a, 42) configured to heat the blown air using the refrigerant flowing out of the first heating unit as a heat source,
The second heating unit is disposed so as to heat the blown air and cause it to flow out to the first heating unit side.
In the heating mode for heating the blowing air, a refrigeration cycle apparatus for heating the blowing air in both of the first heating unit and the second heating unit.
Furthermore, a pressure reducing unit (16a, 16b) for reducing the pressure of the refrigerant flowing out of the second heating unit;
And a cooling evaporation unit (17) for heat exchange of the refrigerant decompressed by the decompression unit (16a) with the blown air to evaporate the refrigerant.
The second heating unit is disposed so as to heat the blown air cooled by the cooling evaporation unit and cause the blown air to flow out to the first heating unit side.
The refrigeration cycle apparatus according to claim 1, wherein in the dehumidifying and heating mode of reheating the blown air cooled and dehumidified by the cooling evaporation unit, the blown air is heated at least by the second heating unit.
Furthermore, the heat absorption evaporator (18) is provided, which causes the refrigerant decompressed by the decompression unit (16b) to heat exchange with the low temperature side heat medium and evaporate the refrigerant.
The low temperature side heat medium circuit (30) for circulating the low temperature side heat medium includes at least at least a low temperature side radiator (33) for heat exchange between the low temperature side heat medium and the heat generating device (32) One is placed,
In the heating mode, switching is performed to a refrigerant circuit that causes the refrigerant reduced in pressure by the pressure reduction unit to flow into the heat absorption evaporation unit;
The refrigeration cycle apparatus according to claim 2, wherein in the dehumidifying and heating mode, the refrigerant cycle reduced in pressure by the pressure reducing unit is switched to a refrigerant circuit that causes the refrigerant to flow into the cooling evaporation unit.
The first heating unit heats the high temperature side water-refrigerant heat exchanger (12) which exchanges heat between the refrigerant discharged from the compressor and the high temperature side heat medium, and heats the high temperature side heat medium and the blowing air. Has a high temperature side heater core (22) to be replaced,
In the high temperature side heat medium circuit (20) for circulating the high temperature side heat medium, a high temperature side radiator (23) for heat exchange between the high temperature side heat medium and the outside air is disposed;
In the heating mode, the heat of the high temperature side heat medium is released to the blowing air by the high temperature side heater core,
The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein in the cooling mode for cooling the blown air, the heat of the high temperature side heat medium is radiated to the outside air by the high temperature side radiator.
Furthermore, a high temperature side water-refrigerant heat exchanger (12) for heat exchange between the refrigerant discharged from the compressor and the high temperature side heat medium, and a high temperature side radiator (23 for heat exchange between the high temperature side heat medium and the outside air A high temperature side heat medium circuit (20) having
The first heating unit includes an indoor condenser (12a) that exchanges heat between the refrigerant discharged from the compressor and the blowing air.
In the heating mode, the heat generated by the refrigerant discharged from the compressor is released to the blowing air by the indoor condenser.
The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein in the cooling mode for cooling the blowing air, the heat of the high temperature side heat medium is radiated to the outside air by the high temperature side radiator.
The gas-liquid separation unit (13) according to any one of claims 1 to 5, further comprising: a gas-liquid separation unit (13) for separating the gas-liquid of the refrigerant flowing out from the first heating unit and flowing the separated liquid-phase refrigerant to the second heating unit side. Refrigerating cycle device according to one.
The second heating unit according to any one of claims 1 to 6, wherein the second heating unit includes a supercooling side indoor condenser (14) that performs heat exchange between the refrigerant flowing out of the first heating unit and the blown air. Refrigeration cycle device as described.
The second heating unit has a supercooling side indoor condenser (14) that exchanges heat between the refrigerant flowing out of the indoor condenser and the air.
The refrigeration cycle apparatus according to claim 5, further comprising: a supercooling side water-refrigerant heat exchanger (14a) for exchanging heat between the refrigerant flowing out of the subcooling side indoor condenser (14) and the high temperature side heat medium.
Furthermore, a heat release amount adjustment unit (54a, 41) that adjusts the amount of heat released to the blast air by the second heating unit;
A heat release control unit (60f) for controlling the operation of the heat release adjustment unit;
The refrigeration cycle apparatus according to claim 7 or 8, wherein the heat release amount adjustment unit is an air mix door (54a) that adjusts an air volume of the blown air flowing into the supercooling side indoor condenser (14).
The refrigeration according to claim 9, wherein in the cooling mode for cooling the blowing air, the heat release amount control unit reduces an air volume of the blowing air flowing into the overcooling side indoor condenser (14) more than the heating mode. Cycle equipment.
The second heating unit is a supercooling side water-refrigerant heat exchanger (14a) that exchanges heat between the refrigerant flowing out of the first heating unit and the supercooling side heat medium, and the supercooling side heat medium and the air blowing The refrigeration cycle apparatus according to any one of claims 1 to 6, further comprising a supercooling side heater core (42) which exchanges heat with air.
Furthermore, a heat release amount adjustment unit (54a, 41) that adjusts the amount of heat released to the blast air by the second heating unit;
A heat release amount control unit (60 g) for controlling the operation of the heat release amount adjustment unit;
The refrigeration cycle apparatus according to claim 11, wherein the heat release amount control unit is a supercooling side heat medium pump (41) that pumps the supercooling side heat medium to the supercooling side heater core.
The refrigeration cycle apparatus according to claim 12, wherein in the cooling mode for cooling the blown air, the heat release amount control unit reduces the flow rate of the supercooling side heat medium to be flowed into the second heating unit more than the heating mode. .
The second heating unit is a supercooling side water-refrigerant heat exchanger (14a) that exchanges heat between the refrigerant flowing out of the indoor condenser and the high temperature side heat medium, the high temperature side heat medium, and the blowing air. The refrigeration cycle apparatus according to claim 5, further comprising a supercooling side heater core (42) for exchanging heat.
In the high temperature side heat medium circuit (20) for circulating the high temperature side heat medium, the high temperature side heater core flow rate (Qa1) of the high temperature side heat medium flowing into the high temperature side heater core and the high temperature side heat flow into the high temperature side radiator A high temperature side flow ratio adjustment unit (24) is arranged to adjust the flow ratio (Qb1 / Qa1) of the medium to the radiator side flow (Qb1),
And a discharge capacity control unit (60a) for controlling the operation of the compressor.
A high temperature side flow ratio control unit (60c) for controlling the operation of the high temperature side flow ratio adjustment unit;
At least in the dehumidifying heating mode,
The discharge capacity control unit controls the operation of the compressor such that the refrigerant evaporation temperature (Tefin) in the cooling evaporation unit becomes a target evaporation temperature (TEO),
The heat release amount control unit controls the operation of the heat release amount adjustment unit such that the degree of subcooling (SC) of the refrigerant flowing out of the second heating portion approaches a target degree of subcooling (KSC);
The high temperature side flow ratio control unit controls the operation of the high temperature side flow ratio adjustment unit such that the temperature (TAV) of the blown air heated by the first heating unit approaches a target temperature (TAO) The refrigeration cycle apparatus according to any one of Items 9, 10, 12, and 13.
And a discharge capacity control unit (60a) for controlling the operation of the compressor.
An evaporation pressure adjusting unit (19) for adjusting the refrigerant evaporation temperature in the cooling evaporation unit to be equal to or higher than a predetermined reference temperature;
At least in the dehumidifying heating mode,
The discharge capacity control unit controls the operation of the compressor such that the temperature (TAV) of the blowing air heated by the first heating unit approaches a target temperature (TAO),
The heat release amount control unit controls the operation of the heat release amount adjustment unit such that the degree of subcooling (SC) of the refrigerant flowing out of the second heating portion approaches a predetermined target degree of supercooling (KSC). The refrigeration cycle apparatus according to any one of 9, 10, 12, and 13.