WO2019073880A1

WO2019073880A1 - Heat exchanger

Info

Publication number: WO2019073880A1
Application number: PCT/JP2018/037044
Authority: WO
Inventors: 遼平杉村; 川久保　昌章; 加藤　大輝; 伊藤　哲也; 三枝　弘
Original assignee: 株式会社デンソー
Priority date: 2017-10-11
Filing date: 2018-10-03
Publication date: 2019-04-18
Also published as: JP2019070504A; CN111213020A; DE112018004493T5; CN111213020B; US20200232726A1; JP6897478B2

Abstract

This heat exchanger is provided with: an inflow port (225a), through which a refrigerant flows in; a cooling flow outlet port (227a), through which the refrigerant flows out when cooling operations are performed; and a warming flow outlet port (226a), through which the refrigerant flows out when warming operations are performed. The ports are disposed such that the distance between the inflow port (225a) and the warming flow outlet port (226a) is shorter than the distance between the inflow port (225a) and the cooling flow outlet port (227a).

Description

Heat exchanger

Cross-reference to related applications

This application is based on Japanese Patent Application No. 2017-197822 filed on October 11, 2017, and claims the benefit of its priority, and the entire contents of the patent application are as follows: Incorporated herein by reference.

The present disclosure relates to a heat exchanger used in a heat pump system that performs cooling operation and heating operation.

As a heat exchanger used for a heat pump system which performs cooling operation and heating operation, a thing given in the following patent documents 1 is known. In the heat exchanger described in Patent Document 1 below, during cooling, a high-temperature high-pressure gas-phase refrigerant flows into the condensation heat exchange unit, is cooled, and flows into the liquid-receiving unit as a gas-liquid two-phase refrigerant. The liquid-phase refrigerant in which the gas-liquid two-phase refrigerant that has flowed into the liquid receiving portion is saturated flows into the subcooling heat exchange portion, is subcooled, and flows to the use side heat exchanger. On the other hand, at the time of heating, a low pressure gas-liquid two-phase refrigerant flows into the heat exchange part for condensation, performs heat exchange and evaporates, and becomes a gas phase refrigerant and flows into the liquid receiving part. The gas-phase refrigerant that has flowed into the liquid receiving portion returns to the compressor without flowing through the supercooling heat exchange portion.

JP, 2009-236404, A

Patent Document 1 has the following problems to be solved at the time of heating. As the first problem in heating, only the heat exchange unit for condensation is used during heating operation, and the heat exchange unit for supercooling is not used, so the entire core unit of the heat exchanger can not be utilized, and heating is performed compared to physique There is a problem that the performance is lowered. As a second problem at the time of heating, a gas phase refrigerant having a large specific volume flows around the heat exchange portion for supercooling and flows, so there is a problem that the refrigerant pressure loss increases and the heating performance decreases. As the third problem at the time of heating, since the gas-liquid two-phase refrigerant is introduced from above to the core portion of the heat exchanger, the distribution of the refrigerant flowing through the condensing heat exchange portion is deteriorated, and the heating There is a problem that the performance is reduced.

Patent Document 1 has the following problem to be solved at the time of cooling. As a first problem at the time of cooling, when a refrigerant adjustment unit is provided that is joined integrally with a liquid storage unit that stores liquid refrigerant and switches the flow of the refrigerant during cooling operation and heating operation, the refrigerant flows into the refrigerant adjustment unit However, since the refrigerant flowing in the heat exchanger is heated, the degree of subcooling is insufficient, and the cooling performance is lowered. As a second problem at the time of cooling, there is a problem that a gas phase refrigerant is mixed in the refrigerant flowing into the expansion valve and a noise is generated due to the insufficient degree of supercooling.

An object of the present disclosure is to provide a heat exchanger capable of suppressing the generation of noise during cooling while improving the heating performance and the cooling performance.

The present disclosure is a heat exchanger used in a heat pump system for performing a cooling operation and a heating operation, the heat exchange unit performing heat exchange between the refrigerant and the outside air during the cooling operation and the heating operation; And a refrigerant adjustment unit that is joined integrally with the liquid storage container and switches the flow of the refrigerant during the cooling operation and the heating operation. The heat exchanger is provided with an inlet through which the refrigerant flows, a cooling outlet through which the refrigerant flows out during the cooling operation, and a heating outlet through which the refrigerant flows out during the heating operation, and the inlet and the heating outlet Are arranged to be shorter than the distance between the inlet and the cooling outlet.

The heat transfer between the inlet and the heating outlet is facilitated because the distance between the inlet and the heating outlet is reduced compared to the distance between the inlet and the cooling outlet. Therefore, at the time of heating, since the difference between the enthalpy of the refrigerant before entering the heat exchanger and the enthalpy of the refrigerant after leaving the heat exchanger is increased, the heating performance is improved. In addition, since the dryness of the gas-liquid two-phase refrigerant introduced from the inlet decreases, the density of the refrigerant increases and the pressure loss of the refrigerant decreases, so the heating performance is improved. Furthermore, by lowering the dryness of the gas-liquid two-phase refrigerant introduced from the inflow port, the liquid phase component of the gas-liquid two-phase refrigerant increases, the distribution of the refrigerant improves, and the heating performance improves.

Since the distance between the inlet and the cooling outlet is longer than the distance between the inlet and the heating outlet, heat transfer between the inlet and the cooling outlet can be suppressed. . When the heat transfer between the inlet and the cooling outlet is promoted, there is a concern that the compressor power may be deteriorated due to the reduction of the enthalpy difference, or the failure due to the reduction of the degree of supercooling. By suppressing the heat transfer between the inlet and the cooling outlet, it is possible to suppress the deterioration of the compressor power due to the reduction of the enthalpy difference. Further, by suppressing the decrease in the degree of supercooling, it is possible to avoid the decrease in cooling performance due to the increase in refrigerant pressure loss in the evaporator and the deterioration in distribution due to the increase in dryness of the refrigerant flowing into the evaporator. Furthermore, it is possible to suppress the generation of abnormal noise caused by the mixture of the gas phase refrigerant into the refrigerant flowing into the pressure reducer.

FIG. 1 is a view showing a heat exchanger as an embodiment. FIG. 2 is a view showing an example of a refrigeration cycle using the heat exchanger shown in FIG. FIG. 3 is a view showing a heat exchanger as a modification. FIG. 4 is a view showing a heat exchanger as a modification. FIG. 5 is a view showing a heat exchanger as a modification. FIG. 6 is a view for explaining the connector component shown in FIG. FIG. 7 is a view for explaining the connector part shown in FIG. FIG. 8 is a view for explaining the connector part shown in FIG. FIG. 9 is a view for explaining the connector part shown in FIG.

Hereinafter, the present embodiment will be described with reference to the attached drawings. In order to facilitate understanding of the description, the same constituent elements in the drawings are denoted by the same reference numerals as much as possible, and redundant description will be omitted.

As shown in FIG. 1, the heat exchanger 2 according to the present embodiment includes an upstream heat exchange unit 20, a downstream heat exchange unit 21, and a reservoir 22. The upstream heat exchange unit 20 includes two

upstream cores

201 and 202 and

header tanks

203, 204 and 205. In the present embodiment, one having two

upstream cores

201 and 202 is shown as an example, but the number of cores may be one or three or more. The

upstream cores

201 and 202 are portions that exchange heat between the refrigerant flowing inside and the air flowing outside, and have tubes through which the refrigerant passes and fins provided between the tubes.

A header tank 203 is attached to the upstream end of the upstream core 201. A header tank 205 is attached to the downstream end of the upstream core 202. At the downstream end of the upstream core 201 and the upstream end of the upstream core 202, a header tank 204 disposed so as to straddle both is attached.

A connection channel 221 is connected to the header tank 203. A connection channel 222 is connected to the header tank 205. The refrigerant flowing from the connection flow channel 221 flows from the header tank 203 into the upstream core 201. The refrigerant having flowed through the upstream core 201 flows into the header tank 204. The refrigerant flowing in the header tank 204 flows into the upstream core 202. The refrigerant having flowed through the upstream core 202 flows into the header tank 205. The refrigerant flowing into the header tank 205 flows out into the connection flow path 222.

The connection flow path 222 is a flow path provided in the reservoir 22. The connection flow path 222 is connected to the liquid storage space 224 of the liquid reservoir 22. The refrigerant flowing out to the connection flow path 222 flows into the liquid storage space 224.

The reservoir 22 is a substantially cylindrical one in which a reservoir space 224 is formed. The liquid storage space 224 is a portion that separates the gas-liquid two-phase refrigerant flowing from the connection flow path 222 into a liquid-phase refrigerant and a gas-phase refrigerant, and stores the liquid-phase refrigerant. The liquid storage device 22 is provided with an inflow passage 225, a connection passage 221, a connection passage 222, a heating and outflow passage 226, and a connection passage 223. At the end of the inflow channel 225, an inflow port 225a is formed. A heating outlet 226 a is formed at an end of the heating outlet channel 226.

The connection flow path 222, the connection flow path 223, and the outflow flow path 112 are connected to the liquid storage space 224. The connection flow path 222 is a flow path connecting the upstream side heat exchange unit 20 and the liquid storage device 22. The connection flow path 223 is a flow path connecting the reservoir 22 and the downstream side heat exchange unit 21. The liquid-phase refrigerant that has flowed out of the connection flow path 223 flows into the downstream heat exchange unit 21. The outflow channel 112 is a channel through which the gas phase refrigerant flows out of the reservoir 22.

The downstream heat exchange unit 21 includes a header tank 211, a downstream core 212, and a header tank 213. A cooling outlet channel 227 is connected to the header tank 213. A cooling outlet 227 a is formed at an end of the cooling outlet channel 227. The header tank 213 is provided at the downstream end of the downstream core 212. A header tank 211 is provided at the upstream end of the downstream core 212. A connection channel 223 is connected to the header tank 211.

The liquid phase refrigerant flows from the connection flow path 223 into the header tank 211, and the liquid phase refrigerant flows from the header tank 211 into the downstream core 212. The downstream core 212 is a portion that exchanges heat between the refrigerant flowing inside and the air flowing outside, and has a tube through which the refrigerant passes, and a fin provided between the tubes. Therefore, the liquid phase refrigerant flowing into the downstream core 212 travels to the header tank 213 while being subcooled.

The liquid-phase refrigerant flowing from the downstream core 212 into the header tank 213 flows out to the cooling outflow channel 227. The cooling outlet channel 227 is connected to a channel connected to an expansion valve constituting the refrigeration cycle apparatus at the cooling outlet 227a, and an evaporator is connected earlier than the expansion valve.

The refrigerant adjustment unit 10 is provided above the liquid storage device 22. The refrigerant adjustment unit 10 is provided with an inflow passage 110, an outflow passage 111, an outflow passage 112, and a connection passage 113. The inflow passage 110 is disposed to be connected to the inflow passage 225. The outflow passage 111 is disposed to be connected to the heating outflow passage 226. The connection flow channel 113 is provided to face the liquid storage space 224, and is connected to the outflow flow channel 111 inside the refrigerant adjustment unit 10. The connection flow channel 113 is disposed to be connected to the connection flow channel 221.

The inflow path 225 and the inflow path 110 are flow paths into which the high pressure refrigerant flowing from the compressor flows. The connection flow channel 221 and the connection flow channel 113 are flow channels that allow the inflowing refrigerant to flow at the high pressure or low pressure as it is to flow toward the upstream heat exchange unit 20.

The outflow flow channel 112 is a flow channel into which the gas phase refrigerant flowing out of the liquid storage space 224 flows. The outflow flow passage 111 is a flow passage for delivering the refrigerant flowing into the outflow flow passage 112 to the compressor.

The refrigerant adjustment unit 10 is provided with a throttle 101, an on-off valve 102, and a flow rate adjustment valve 103. The throttle 101, the on-off valve 102, and the flow rate adjustment valve 103 will be described later together with an example of a refrigeration cycle to which the heat exchanger 2 is applied.

Subsequently, an example of a refrigeration cycle to which the heat exchanger 2 of the present embodiment is applied will be described with reference to FIG. As shown in FIG. 2, the refrigeration cycle apparatus 71 is applied to a vehicle air conditioner 7. The vehicle air conditioner 7 is a device that adjusts the temperature of the vehicle interior by adjusting the temperature of the blowing air that is blown into the vehicle interior that is the air conditioning target space. The vehicle air conditioner 7 includes a refrigeration cycle apparatus 71, a cooling water circulation circuit 72, and an air conditioning unit 73.

The refrigeration cycle apparatus 71 can be selectively switched between a cooling mode for cooling the passenger compartment by cooling the blowing air and a heating mode for heating the passenger compartment by heating the blowing air. The refrigeration cycle apparatus 71 is a vapor compression type refrigeration cycle apparatus including a heat pump circuit in which a refrigerant circulates.

The refrigeration cycle apparatus 71 includes a pressure reducer 30, an evaporator 31, an accumulator 32, a compressor 33, a water-cooled condenser 34, and a heat exchanger 2. For example, an HFC refrigerant or an HFO refrigerant can be used as the refrigerant circulating through the refrigeration cycle apparatus 71. The refrigerant is mixed with oil for lubricating the compressor 33, that is, refrigerator oil. Therefore, a part of the refrigeration oil circulates through the refrigeration cycle apparatus 71 together with the refrigerant.

The compressor 33 sucks and compresses the refrigerant from the suction port in the refrigeration cycle apparatus 71, and discharges the refrigerant, which has been superheated by being compressed, from the discharge port. The compressor 33 is an electric compressor. The refrigerant discharged from the discharge port flows to the water cooling condenser 34.

The water cooled condenser 34 is a known water refrigerant heat exchanger. The water-cooled condenser 34 has a first heat exchange unit 341 and a second heat exchange unit 342.

The first heat exchange unit 341 is provided between the discharge port of the compressor 33 and the heat exchanger 2. That is, the refrigerant discharged from the compressor 33 is flowing in the first heat exchange unit 341.

The second heat exchange unit 342 is provided in the middle of the cooling water circulation circuit 72 through which the engine cooling water flows. In the cooling water circulation circuit 72, the cooling water is circulated by the cooling pump 37. The cooling water circulates in the order of the second heat exchange unit 342, the heater core 35, the cooling pump 37, and the engine 36.

In the water-cooled condenser 34, heat exchange is performed between the refrigerant flowing in the first heat exchange unit 341 and the cooling water flowing in the second heat exchange unit 342, thereby heating the cooling water with the heat of the refrigerant and Cool down. The refrigerant flowing out of the first heat exchange unit 341 flows to the refrigerant adjustment unit 10 of the heat exchanger 2.

In the cooling water circulation circuit 72, the refrigerant heated in the engine 36 and the second heat exchange unit 342 flows through the heater core 35, whereby the heater core 35 is heated. The heater core 35 is disposed in the casing 39 of the air conditioning unit 73. The heater core 35 heats the blowing air by performing heat exchange between the cooling water flowing inside and the blowing air flowing inside the casing 39. The water-cooled condenser 34 functions as a radiator that indirectly radiates the heat of the refrigerant discharged from the compressor 33 and flowing into the first heat exchange unit 341 to the blast air through the cooling water and the heater core 35.

The throttle 101 and the on-off valve 102 of the refrigerant adjustment unit 10 function as a pressure adjustment unit. The throttling 101 and the on-off valve 102 are configured to be able to switch between the heating mode in which the refrigerant absorbs heat from the outside air in the upstream heat exchange unit 20 of the heat exchanger 2 and the cooling mode in which the refrigerant dissipates heat to the outside air. It corresponds to a pressure adjustment unit that adjusts the pressure of the refrigerant flowing into the exchange unit 20.

The refrigerant that has flowed out of the first heat exchange portion 341 of the water-cooled condenser 34 flows to the throttle 101 through the inflow passage 225. The throttle 101 depressurizes and discharges the refrigerant flowing out of the first heat exchange unit 341 of the water-cooled condenser 34. For example, a nozzle or an orifice having a fixed opening degree can be used as the throttle 101, but a nozzle having a fluctuation in the opening degree can also be used. The refrigerant discharged from the throttle 101 flows to the upstream heat exchange unit 20 through the connection channel 221.

The bypass flow passage 114 is a refrigerant flow passage that guides the refrigerant flowing out of the first heat exchange unit 341 to the upstream heat exchange unit 20 by bypassing the throttle 601. The on-off valve 102 is an electromagnetic valve that opens and closes the bypass channel 114.

In the heating mode, the on-off valve 102 is closed. Thus, in the heating mode, the refrigerant flowing out of the first heat exchange unit 341 of the water-cooled condenser 34 is decompressed by flowing through the throttle 101 and flows to the upstream heat exchange unit 20.

On the other hand, in the cooling mode, the on-off valve 102 is fully open. Thus, in the cooling mode, the refrigerant flowing out of the first heat exchange portion 341 of the water cooling condenser 34 bypasses the throttle 101 and flows in the bypass flow path 114. The refrigerant flowing out of the first heat exchange unit 341 flows to the upstream heat exchange unit 20 without being decompressed.

The heat exchanger 2 is an outdoor heat exchanger disposed on the front side of the vehicle in the engine room. The heat exchanger 2 has an upstream side heat exchange unit 20, a liquid storage unit 22, a downstream side heat exchange unit 21, and a refrigerant adjustment unit 10.

The refrigerant that has flowed out from the throttle 101 and the on-off valve 102 as a pressure adjustment unit flows into the upstream side heat exchange unit 20. The upstream heat exchange unit 20 is a portion that performs heat exchange between the inflowing refrigerant and the outside air that is the air outside the vehicle that is blown by a blowing fan (not shown). The upstream heat exchange unit 20 functions as an evaporator that evaporates the refrigerant by performing heat exchange between the inflowing refrigerant and the outside air in the heating mode. Further, in the cooling mode, the upstream heat exchange unit 20 functions as a condenser that cools the refrigerant by performing heat exchange between the inflowing refrigerant and the outside air.

The liquid storage device 22 separates the refrigerant flowing out from the upstream side heat exchange unit 20 into a gas phase refrigerant and a liquid phase refrigerant, and causes the gas phase refrigerant and the liquid phase refrigerant to flow separately, and stores the liquid phase refrigerant. It is possible. The liquid storage device 22 discharges the separated gas phase refrigerant toward the heating outflow channel 226, and discharges the separated liquid phase refrigerant toward the cooling outflow channel 227.

The heating outlet channel 226 is connected to the refrigerant channel 712 at the heating outlet 226a. The refrigerant flow passage 712 is connected to an intermediate portion of the refrigerant flow passage 711. The refrigerant channel 711 is a channel that leads the refrigerant flowing out of the pressure reducer 30 to the suction port of the compressor 33. The heating outflow channel 226 is a channel that leads the gas phase refrigerant discharged from the liquid storage 22 to the compressor 33.

The liquid-phase refrigerant flows from the liquid storage device 22 into the downstream side heat exchange unit 21. The downstream side heat exchange unit 21 is a part that further enhances the heat exchange efficiency of the refrigerant in the heat exchanger 2 by performing heat exchange between the inflowing liquid phase refrigerant and the outside air. Specifically, in the heating mode, the downstream side heat exchange unit 21 exchanges heat between the inflowing liquid phase refrigerant and the outside air to evaporate the liquid phase refrigerant. As a result, since the liquid phase refrigerant remaining without being completely evaporated in the upstream side heat exchange unit 20 can be evaporated, the function as the evaporator in the heat exchanger 2 is enhanced. However, since the downstream heat exchange section 21 has a small number of tubes and a small refrigerant flow area due to the mounting space, the refrigerant may not be allowed to flow in order to avoid an increase in refrigerant pressure loss. Further, in the cooling mode, the downstream side heat exchange unit 21 functions as a subcooler that further cools the liquid phase refrigerant by performing heat exchange between the inflowing liquid phase refrigerant and the outside air. Thus, the function of the heat exchanger 2 as a condenser is enhanced.

The refrigerant that has flowed out of the downstream side heat exchange unit 21 flows into the pressure reducing device 30 via the refrigerant flow path 713 connected to the cooling outflow flow path 227 and the cooling outflow flow path 227. The pressure reducer 30 decompresses and discharges the inflowing refrigerant. The refrigerant reduced in pressure by the pressure reducer 30 flows into the evaporator 31. Further, the refrigerant discharged from the evaporator 31 flows into the decompressor 30. The pressure reducing device 30 is a temperature sensitive mechanical expansion that reduces the pressure of refrigerant flowing into the evaporator 31 by a mechanical mechanism so that the degree of superheat of the refrigerant discharged from the evaporator 31 falls within a predetermined range. It is a valve.

The refrigerant discharged from the pressure reducing device 30 flows into the evaporator 31. The evaporator 31 is a heat exchanger that cools the blowing air by performing heat exchange between the refrigerant flowing inside and the blowing air flowing inside the casing 39 of the air conditioning unit 73 in the cooling mode. In the evaporator 31, the refrigerant is evaporated by heat exchange between the blown air and the refrigerant. The evaporated refrigerant is discharged from the evaporator 31 and flows into the suction port of the compressor 33 via the pressure reducer 30 and the refrigerant channel 711.

The flow rate adjustment valve 103 is provided on the way from the outflow passage 112 to the heating outflow passage 226. The flow rate adjustment valve 103 is composed of a solenoid valve that can change the flow passage cross-sectional area of the heating outflow passage 226 by adjusting the opening degree thereof. By adjusting the opening degree of the flow rate adjustment valve 103, the flow rate of the refrigerant flowing through the heating outflow passage 226 can be adjusted.

The air conditioning unit 73 includes a casing 39 and an air passage switching door 38. In the casing 39, blowing air is flowing. In the casing 39, the evaporator 31 and the heater core 35 are disposed in order from the upstream side to the downstream side in the flow direction of the blown air. The evaporator 31 cools the blowing air by performing heat exchange between the refrigerant flowing inside and the blowing air. On the downstream side of the evaporator 31 in the casing 39, a hot air passage in which the heater core 35 is disposed and a cold air passage in which the heater core 35 is not disposed are provided.

The air passage switching door 38 closes the cold air passage and opens the hot air passage. The first door position shown by a solid line in the figure and the hot air passage closes and opens the cold air passage. The second door position is configured to be displaceable. On the downstream side in the air flow direction of the hot air passage and the cold air passage in the casing 39, a plurality of openings (not shown) opening into the vehicle interior are formed.

In the air conditioning unit 73, in the heating mode, the air passage switching door 38 is positioned at the first door position indicated by the solid line. As a result, since the blown air having passed through the evaporator 31 passes through the hot air passage, the blown air is heated by the heater core 35 and flows to the downstream side. On the other hand, in the cooling mode, the air passage switching door 38 is located at the second door position indicated by the broken line. Thereby, since the blast air which has passed the evaporator 31 passes through the cold air passage, the blast air cooled by the evaporator 31 flows downstream as it is.

The heat exchanger 2 of the present embodiment is a heat exchanger used in a heat pump system that performs a cooling operation and a heating operation, and performs heat exchange between the refrigerant and the outside air during the cooling operation and the heating operation. Control unit that is integrally joined with the upstream heat exchange unit 20 and the downstream heat exchange unit 21 that are the unit and the liquid storage device 22 that stores liquid refrigerant, and switches the flow of refrigerant during cooling operation and heating operation And a unit 10. The heat exchanger 2 is provided with an inlet 225a through which the refrigerant flows, a cooling outlet 227a through which the refrigerant flows out during the cooling operation, and a heating outlet 226a through which the refrigerant flows out during the heating operation. The distance between 225a and the heating outlet 226a is shorter than the distance between the inlet 225a and the cooling outlet 227a.

In this embodiment, since the distance between the inlet 225a and the heating outlet 226a is shorter than the distance between the inlet 225a and the cooling outlet 227a, the inlet 225a and the heating outlet 226a Heat transfer is promoted. Therefore, at the time of heating, since the difference between the enthalpy of the refrigerant before entering the heat exchanger 2 and the enthalpy of the refrigerant after leaving the heat exchanger 2 increases, the heating performance is improved. In addition, since the dryness of the gas-liquid two-phase refrigerant introduced from the inflow port 225a decreases, the density of the refrigerant increases and the pressure loss of the refrigerant decreases, so the heating performance is improved. Furthermore, by lowering the dryness of the gas-liquid two-phase refrigerant introduced from the inflow port 225a, the liquid phase component of the gas-liquid two-phase refrigerant is increased, the distribution of the refrigerant is improved, and the heating performance is improved.

In this embodiment, since the distance between the inlet 225a and the cooling outlet 227a is longer than the distance between the inlet 225a and the heating outlet 226a, the inlet 225a and the cooling outlet 227a Heat transfer can be suppressed. When the heat transfer between the inflow port 225a and the cooling outflow port 227a is promoted, there is a concern that the compressor power deterioration due to the reduction of the enthalpy difference or the failure due to the reduction of the degree of supercooling. By suppressing the heat transfer between the inflow port 225a and the cooling outflow port 227a, it is possible to suppress the deterioration of the compressor power due to the reduction of the enthalpy difference. Further, by suppressing the decrease in the degree of supercooling, it is possible to avoid the decrease in cooling performance due to the increase in refrigerant pressure loss in the evaporator 31 and the deterioration in distribution due to the increase in dryness of the refrigerant flowing into the evaporator 31. Furthermore, it is possible to suppress the generation of abnormal noise caused by the mixture of the gas phase refrigerant into the refrigerant flowing into the pressure reducer 30.

Moreover, in the heat exchanger 2 of this embodiment, the heat transfer member 27 is provided between the inlet 225a and the heating outlet 226a. In the present embodiment, the heat transfer member 27 is a partial side wall of the liquid storage device 22 between the inflow passage 225 and the heating and outflow passage 226. By providing the heat transfer member 27 between the inlet 225a and the heating outlet 226a, the heat transfer between the inlet 225a and the heating outlet 226a can be further promoted.

Further, in the heat exchanger 2 of the present embodiment, as shown in FIGS. 1, 6 and 7, the inlet 225a and the heating outlet 226a are constituted by a single connector part 25. FIG. 6 is a view more specifically showing the connector part 25 in FIG. FIG. 7 is a view showing the connector part 25 from the direction of looking through the inlet 225a and the heating outlet 226a in FIG. Furthermore, as in the heat exchanger 2A shown in FIGS. 3, 8 and 9, the inlet 225Aa, the heating outlet 226Aa, and the heat transfer member 27A can be configured by a single connector part 25A. FIG. 8 is a view more specifically showing the connector part 25A in FIG. FIG. 9 is a view showing the connector part 25A from the direction of looking through the inlet 225Aa and the heating outlet 226Aa in FIG. By configuring the inlet 225Aa, the heating outlet 226Aa, and the heat transfer member 27A with a single connector part 25A, the configuration for facilitating the heat transfer between the inlet 225Aa and the heating outlet 226Aa can be easily realized. be able to.

Further, the connector part 25A is connected such that the heat transfer member 27A fills the space between the inlet 225Aa and the heating outlet 226Aa. Since the heat transfer member 27A is connected between the inlet 225Aa and the heating outlet 226Aa, a sufficient heat transfer path can be secured, which further promotes the heat transfer between the inlet 225Aa and the heating outlet 226Aa. can do.

Moreover, in the heat exchanger 2 and the heat exchanger 2A of the present embodiment, the cooling outlet 227a is provided in a component different from the

connector components

25 and 25A. More specifically, the cooling outlet 227 a is provided at the end of the cooling outlet channel 227 connected to the header tank 213 that constitutes the downstream side heat exchange unit 21. By providing the cooling outlet 227a in a component different from the inlet port 225a, 225Aa and the

connector component

25, 25A provided with the heating outlet 226a, 226Aa, the space between the inlet 225a, 225Aa and the cooling outlet 227a Heat transfer can be suppressed.

Furthermore, as in the heat exchanger 2B shown in FIG. 4, the cooling outlet 227Ba can be provided in the reservoir 22B. In the heat exchanger 2B, only the upstream side heat exchange unit 20B is provided, and no heat exchange unit corresponding to the downstream side heat exchange unit 21 is provided. The cooling outlet 227Ba is provided at an end of the cooling outlet channel 227B connected to the liquid storage 22B.

Further, in the

heat exchangers

2, 2A, 2B of the present embodiment, the inflow ports 225a, 225Aa so that the flow direction of the refrigerant at the inflow ports 225a, 225Aa and the flow direction of the refrigerant at the heating outflow ports 226a, 226Aa are counterflows. , 225Aa and heating outlets 226a, 226Aa. The heat transfer between the inflow ports 225a and 225Aa and the heating outflow ports 226a and 226Aa can be further enhanced by arranging the refrigerants in the inflow ports 225a and 225Aa and the heating outflow ports 226a and 226Aa to have opposite flow directions. Promoted.

In the

heat exchangers

2, 2A, 2B of the present embodiment, the inlets 225a, 225Aa, the heating outlets 226a, 226Aa, and the cooling outlets 227a, 227Ba are arranged in the longitudinal direction of the

reservoirs

22, 22B. ing.

Since the cooling outlets 227a and 227Ba are not disposed between the inlets 225a and 225Aa and the heating outlets 226a and 226Aa, heat transfer between the inlets 225a and 225Aa and the heating outlets 226a and 226Aa is promoted. be able to. Since the heating outlets 226a and 226Aa are disposed between the inlets 225a and 225Aa and the cooling outlets 227a and 227Ba, the heating outlets 226a and 226Aa and the flow path connected thereto function as a heat insulating layer during cooling. The heat transfer between the inflow ports 225a and 225Aa and the cooling outflow ports 227a and 227Ba can be suppressed, and heat damage can be avoided.

Furthermore, as in the heat exchanger 2C shown in FIG. 5, the refrigerant flowing from the connection flow path 222 may be directly introduced into the refrigerant adjustment unit 10C. The refrigerant flowing in from the connection flow path 222 flows into the inside of the refrigerant adjustment unit 10C from the refrigerant inlet 115C. As shown in FIG. 5, when the flow rate adjustment valve 103C is located at the uppermost position, the outflow passage 112C is opened, and the refrigerant flows in the liquid storage space 224. On the other hand, when the flow rate adjustment valve 103C is located at the lowermost position, the outflow passage 112C is closed, and the refrigerant flows toward the heating outlet 226a.

The present embodiment has been described above with reference to the specific example. However, the present disclosure is not limited to these specific examples. Those appropriately modified in design by those skilled in the art are also included in the scope of the present disclosure as long as the features of the present disclosure are included. The elements included in the above-described specific examples, and the arrangement, conditions, and shapes thereof are not limited to those illustrated, but can be appropriately modified. The elements included in the above-described specific examples can be appropriately changed in combination as long as no technical contradiction arises.

Claims

A heat exchanger used in a heat pump system for performing a cooling operation and a heating operation, comprising:
A heat exchange unit (20, 21) that exchanges heat between the refrigerant and the outside air at the time of cooling operation and heating operation;
And a refrigerant adjustment unit (10) joined integrally with a liquid storage unit for storing liquid refrigerant and switching the flow of the refrigerant during the cooling operation and the heating operation,
An inlet (225a, 225Aa) through which the refrigerant flows in, a cooling outlet (227a, 227Ba) through which the refrigerant flows out during the cooling operation, and a heating outlet (226a, 226Aa) through which the refrigerant flows out during the heating operation are provided. Yes,
Heat exchanger, wherein the distance between the inlet and the heating outlet is arranged to be shorter than the distance between the inlet and the cooling outlet.
The heat exchanger according to claim 1, wherein
A heat exchanger, wherein a heat transfer member (27, 27A) is provided between the inlet and the heating outlet.
The heat exchanger according to claim 2, wherein
A heat exchanger, wherein the inlet (225Aa), the heating outlet (226Aa) and the heat transfer member (27A) are constituted by a single connector part (25A).
The heat exchanger according to claim 3, wherein
The heat exchanger according to claim 1, wherein the connector component is connected between the inlet and the heating outlet by the heat transfer member.
The heat exchanger according to claim 3 or 4, wherein
The heat exchanger according to claim 1, wherein the cooling outlet is provided in a component different from the connector component.
The heat exchanger according to any one of claims 1 to 5, wherein
The heat exchanger according to claim 1, wherein the inlet and the heating outlet are disposed such that the flow direction of the refrigerant at the inlet and the flow direction of the refrigerant at the heating outlet are opposite to each other.
The heat exchanger according to any one of claims 1 to 6, wherein
A heat exchanger, which is disposed in the order of the inlet, the heating outlet, and the cooling outlet in the longitudinal direction of the reservoir.