CN111213020B

CN111213020B - Heat exchanger

Info

Publication number: CN111213020B
Application number: CN201880066577.9A
Authority: CN
Inventors: 杉村辽平; 川久保昌章; 加藤大辉; 伊藤哲也; 三枝弘
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2017-10-11
Filing date: 2018-10-03
Publication date: 2021-09-21
Anticipated expiration: 2038-10-03
Also published as: CN111213020A; JP6897478B2; WO2019073880A1; JP2019070504A; US20200232726A1; DE112018004493T5

Abstract

In a heat exchanger, provided are: an inlet (225a) into which the refrigerant flows; a cooling outflow port (227a) through which the refrigerant flows out during cooling operation; and a heating outlet (226a) through which the refrigerant flows out during heating operation, wherein the distance between the inlet (225a) and the heating outlet (226a) is shorter than the distance between the inlet (225a) and the cooling outlet (227 a).

Description

Heat exchanger

Cross reference to related applications

This application is based on japanese patent application No. 2017-197822, filed on 10/11/2017, the priority of which is claimed and the entire contents of which are incorporated by reference into the present specification.

Technical Field

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

Background

As a heat exchanger used in a heat pump system that performs a cooling operation and a heating operation, a heat exchanger described in patent document 1 below is known. In the heat exchanger described in patent document 1, during cooling, a high-temperature and high-pressure gas-phase refrigerant flows into the condensation heat exchange portion, is cooled, and flows into a gas-liquid two-phase refrigerant into the liquid receiving portion. The liquid-phase refrigerant saturated with the two-phase gas-liquid refrigerant flowing into the liquid receiving portion flows into the supercooling heat exchange portion, is supercooled, and then flows into the utilization-side heat exchanger. On the other hand, during heating, the low-pressure gas-liquid two-phase refrigerant flows into the condensation heat exchange portion, exchanges heat and evaporates, turns into a gas-phase refrigerant, and flows into the liquid receiving portion. The gas-phase refrigerant flowing into the liquid receiving portion returns to the compressor without flowing through the supercooling heat exchange portion.

Documents of the prior art

Patent document

Patent document 1: japanese laid-open patent publication No. 2009-236404

In patent document 1, there are technical problems to be solved in heating as follows. As a first technical problem in heating, only the condensing heat exchange unit and not the supercooling heat exchange unit are used in heating operation, and therefore the entire core of the heat exchanger cannot be used, and there is a technical problem of low heating performance compared to the body type. As a second technical problem in heating, there is a problem in that the refrigerant pressure loss increases and the heating performance decreases because the gas-phase refrigerant having a large specific volume bypasses the supercooling heat exchange portion and flows. As a third technical problem in heating, there is a problem in that the distribution of the refrigerant flowing through the condensation heat exchange portion is deteriorated and the heating performance is deteriorated because of the structure in which the gas-liquid two-phase refrigerant is introduced into the core portion of the heat exchanger from above.

In patent document 1, there are technical problems to be solved in cooling as follows. As a first technical problem at the time of cooling, when a refrigerant adjusting portion that is joined integrally to a receiver that stores liquid refrigerant and switches the flow of refrigerant between the time of cooling operation and the time of heating operation is provided, since the refrigerant flows into the refrigerant adjusting portion as a high-temperature high-pressure gas-phase refrigerant, there are the following technical problems: the refrigerant flowing through the heat exchanger is heated and the degree of subcooling is insufficient, and the refrigeration performance is reduced. As a second technical problem in cooling, there is a technical problem that a gaseous refrigerant is mixed into a refrigerant flowing into an expansion valve due to an insufficient degree of supercooling, thereby generating abnormal sound.

Disclosure of Invention

The purpose of the present invention is to provide a heat exchanger that can improve heating performance and cooling performance and can suppress the occurrence of abnormal noise during cooling.

The present invention provides a heat exchanger used in a heat pump system for performing cooling operation and heating operation, the heat exchanger including: a heat exchange unit that exchanges heat between the refrigerant and outside air during a cooling operation and a heating operation; and a refrigerant adjusting portion that is integrally joined to a receiver for storing the liquid refrigerant and switches the flow of the refrigerant during the cooling operation and the heating operation. A heat exchanger is provided with: an inflow port into which a refrigerant flows; a cooling outflow port through which a refrigerant flows out during cooling operation; and a heating outlet through which the refrigerant flows out during heating operation, wherein a distance between the inlet and the heating outlet is shorter than a distance between the inlet and the cooling outlet.

Since the distance between the inlet port and the warm air outlet port is shorter than the distance between the inlet port and the cold air outlet port, heat transfer between the inlet port and the warm air outlet port is promoted. Therefore, at the time of heating, the difference between the enthalpy of the refrigerant before entering the heat exchanger and the enthalpy of the refrigerant after exiting the heat exchanger increases, and therefore, the heating performance improves. Further, the dryness of the gas-liquid two-phase refrigerant introduced from the inlet port is reduced, and therefore the density of the refrigerant is increased, and the pressure loss of the refrigerant is reduced, thereby improving the heating performance. Further, by decreasing the dryness of the gas-liquid two-phase refrigerant introduced from the inlet port, the liquid-phase component of the gas-liquid two-phase refrigerant increases, the refrigerant distribution performance 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 port and the cooling outlet port is promoted, there is a concern that the power of the compressor is deteriorated due to the decrease in the enthalpy difference and the problem is caused by the decrease in the degree of supercooling. By suppressing heat transfer between the inlet port and the cooling outlet port, deterioration of the compressor power due to a decrease in the enthalpy difference can be suppressed. Further, by suppressing the decrease in the degree of supercooling, it is possible to avoid an increase in the refrigerant pressure loss of the evaporator due to an increase in the dryness of the refrigerant flowing into the evaporator and a decrease in the cooling performance due to a deterioration in the distribution. Further, it is possible to suppress the occurrence of abnormal sound caused by the gas-phase refrigerant mixing into the refrigerant flowing into the decompressor.

Drawings

Fig. 1 is a diagram showing a heat exchanger according to an embodiment.

Fig. 2 is a diagram showing an example of a refrigeration cycle using the heat exchanger shown in fig. 1.

Fig. 3 is a diagram showing a heat exchanger according to a modification.

Fig. 4 is a diagram showing a heat exchanger according to a modification.

Fig. 5 is a diagram showing a heat exchanger according to a modification.

Fig. 6 is a diagram for explaining the connector component shown in fig. 1.

Fig. 7 is a diagram for explaining the connector component shown in fig. 1.

Fig. 8 is a diagram for explaining the connector component shown in fig. 3.

Fig. 9 is a diagram for explaining the connector component shown in fig. 3.

Detailed Description

The present embodiment will be described below with reference to the drawings. For the sake of easy understanding of the description, the same components are denoted by the same reference numerals as much as possible in the drawings, and redundant description is omitted.

As shown in fig. 1, the heat exchanger 2 of the present embodiment includes an upstream-side heat exchange unit 20, a downstream-side heat exchange unit 21, and a receiver 22. The upstream-side heat exchange portion 20 has two upstream-

side cores

201, 202 and

header tanks

203, 204, 205. In the present embodiment, the configuration having two

upstream cores

201 and 202 is shown as an example, but one core may be used, or three or more cores may be used. The

upstream cores

201 and 202 exchange heat between the refrigerant flowing inside and the air flowing outside, and the

upstream cores

201 and 202 have tubes through which the refrigerant passes and fins provided between the tubes.

A header tank 203 is attached to an upstream end of the upstream core 201. A header tank 205 is mounted on the downstream side end of the upstream core 202. A header tank 204 is mounted on both the downstream end of the upstream core 201 and the upstream end of the upstream core 202.

The header 203 is connected to a connection channel 221. The header 205 is connected to a connection flow path 222. The refrigerant flowing from the connection channel 221 flows from the header tank 203 into the upstream core 201. The refrigerant flowing through the upstream core 201 flows into the header tank 204. The refrigerant flowing through the header tank 204 flows into the upstream core 202. The refrigerant flowing through the upstream core 202 flows into the header tank 205. The refrigerant flowing into the header 205 flows out to 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 reservoir space 224 of the reservoir 22. The refrigerant flowing out to the connection flow path 222 flows into the inside of the liquid storage space 224.

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

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

The downstream heat exchanger 21 includes a header tank 211, a downstream core 212, and a header tank 213. A cooling outflow passage 227 is connected to the header tank 213. A cooling outflow port 227a is formed at an end of the cooling outflow 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 side end of the downstream side core 212. The header tank 211 is connected to a connection flow path 223.

The liquid-phase refrigerant flows into the header tank 211 from the connecting flow passage 223, and the liquid-phase refrigerant flows into the downstream core 212 from the header tank 211. The downstream core 212 is a portion in which heat exchange is performed between the refrigerant flowing inside and the air flowing outside, and the downstream core 212 includes tubes through which the refrigerant passes and fins provided between the tubes. Therefore, the liquid-phase refrigerant flowing into the downstream core 212 flows to the header tank 213 while being supercooled.

The liquid-phase refrigerant that has flowed into the header tank 213 from the downstream core 212 flows out to the cooling outflow passage 227. The refrigerant outflow channel 227 is connected to a channel to which an expansion valve constituting the refrigeration cycle apparatus is connected at a refrigerant outlet 227a, and an evaporator is connected in front of the expansion valve.

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

The inflow channel 225 and the inflow channel 110 are channels into which the high-pressure refrigerant flowing from the compressor flows. The connection channel 221 and the connection channel 113 are channels through which the refrigerant flowing in flows directly to the upstream side heat exchange unit 20 at a high pressure or a low pressure.

The outflow channel 112 is a channel into which the gas-phase refrigerant flowing out of the receiver space 224 flows. The outflow passage 111 is a passage for sending the refrigerant flowing into the outflow passage 112 to the compressor.

The refrigerant adjusting unit 10 is provided with an expansion unit 101, an opening/closing valve 102, and a flow rate adjusting 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.

Next, 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. 2. As shown in fig. 2, the refrigeration cycle device 71 is applied to the vehicle air conditioner 7. The vehicle air conditioner 7 is a device that adjusts the temperature of the interior of the vehicle by adjusting the temperature of the supply air that is blown into the interior of the vehicle, which is the space to be air-conditioned. The vehicle air conditioner 7 includes a refrigeration cycle device 71, a cooling water circulation circuit 72, and an air conditioning unit 73.

The refrigeration cycle device 71 can selectively switch between a cooling mode for cooling the vehicle interior by cooling the supply air and a heating mode for heating the vehicle interior by heating the supply air. The refrigeration cycle device 71 is a vapor compression refrigeration cycle device including a heat pump circuit for circulating a refrigerant.

The refrigeration cycle device 71 includes the pressure reducer 30, the evaporator 31, the accumulator 32, the compressor 33, the water-cooled condenser 34, and the heat exchanger 2. As the refrigerant circulating through the refrigeration cycle device 71, for example, HFC-based refrigerant or HFO-based refrigerant can be used. Oil for lubricating the compressor 33, i.e., refrigerating machine oil, is mixed into the refrigerant. Therefore, a part of the refrigerating machine oil circulates in the refrigeration cycle device 71 together with the refrigerant.

The compressor 33 sucks and compresses a refrigerant from a suction port in the refrigeration cycle device 71, and discharges the refrigerant that has been brought into a superheated state by compression from a discharge port. The compressor 33 is an electric compressor. The refrigerant discharged from the discharge port flows to the water-cooled condenser 34.

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

The first heat exchange portion 341 is disposed between the discharge port of the compressor 33 and the heat exchanger 2. That is, the refrigerant discharged from the compressor 33 flows to the first heat exchange portion 341.

The second heat exchange portion 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, cooling water is circulated by the cooling pump 37. The cooling water circulates through the second heat exchanger 342, the heater core 35, the cooling pump 37, and the engine 36 in this order.

In the water-cooled condenser 34, heat is exchanged between the refrigerant flowing in the first heat exchange portion 341 and the cooling water flowing in the second heat exchange portion 342, whereby the cooling water is heated by the heat of the refrigerant and the refrigerant is cooled. The refrigerant flowing out of the first heat exchange portion 341 flows into the refrigerant adjusting portion 10 of the heat exchanger 2.

In the cooling water circulation circuit 72, the refrigerant heated by the engine 36 and the second heat exchange portion 342 flows through the heater core 35, and 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 supply air by exchanging heat between the cooling water flowing therein and the supply air flowing in the casing 39. The water-cooled condenser 34 functions as a radiator that indirectly radiates heat of the refrigerant discharged from the compressor 33 and flowing into the first heat exchange portion 341 to the blowing air via the cooling water and the heater core 35.

The throttle part 101 and the on-off valve 102 of the refrigerant adjusting part 10 function as a pressure adjusting part. The throttle unit 101 and the on-off valve 102 correspond to a pressure adjustment unit that adjusts the pressure of the refrigerant flowing into the upstream-side heat exchange unit 20 so as to be able to switch between a heating mode in which the refrigerant absorbs heat from the outside air in the upstream-side heat exchange unit 20 of the heat exchanger 2 and a cooling mode in which the refrigerant radiates heat to the outside air in the upstream-side heat exchange unit 20 of the heat exchanger 2.

The refrigerant flowing out of the first heat exchange portion 341 of the water-cooled condenser 34 flows through the inflow channel 225 to the expansion portion 101. The expansion portion 101 decompresses and discharges the refrigerant flowing out of the first heat exchange portion 341 of the water-cooled condenser 34. As the throttle unit 101, for example, a nozzle, an orifice, or the like having a fixed throttle opening degree can be used, but a configuration in which the throttle opening degree varies may be used. The refrigerant discharged from the expansion unit 101 flows through the connection channel 221 to the upstream side heat exchange unit 20.

The bypass flow path 114 is a refrigerant flow path that guides the refrigerant flowing out of the first heat exchange portion 341 to the upstream side heat exchange portion 20 while bypassing the throttle portion 101. The opening/closing valve 102 is an electromagnetic valve that opens and closes the bypass flow path 114.

In the heating mode, the opening/closing valve 102 is closed. Thus, in the heating mode, the refrigerant flowing out of the first heat exchange portion 341 of the water-cooled condenser 34 is decompressed by passing through the throttle portion 101, and flows toward the upstream-side heat exchange portion 20.

On the other hand, in the cooling mode, opening/closing valve 102 is fully opened. Thus, in the cooling mode, the refrigerant flowing out of the first heat exchange portion 341 of the water-cooled condenser 34 bypasses the throttle portion 101 and flows through the bypass flow path 114. The refrigerant flowing out of the first heat exchange portion 341 flows to the upstream side heat exchange portion 20 without being decompressed.

The heat exchanger 2 is an outdoor heat exchanger disposed on the vehicle front side in the engine compartment. The heat exchanger 2 includes an upstream-side heat exchange portion 20, a receiver 22, a downstream-side heat exchange portion 21, and a refrigerant adjustment portion 10.

The refrigerant flowing out of the throttle portion 101 and the on-off valve 102 as the pressure adjustment portion flows into the upstream side heat exchange portion 20. The upstream side heat exchange portion 20 is a portion that exchanges heat between the refrigerant flowing in and outside air, which is air outside the vehicle interior and blown by a blower fan, not shown. In the heating mode, the upstream-side heat exchange portion 20 functions as an evaporator that evaporates the refrigerant by exchanging heat between the refrigerant flowing in and the outside air. In the cooling mode, the upstream-side heat exchange unit 20 functions as a condenser that cools the refrigerant by exchanging heat between the refrigerant flowing in and the outside air.

The receiver 22 separates the refrigerant flowing out of the upstream side heat exchange portion 20 into a gas-phase refrigerant and a liquid-phase refrigerant, and allows the gas-phase refrigerant and the liquid-phase refrigerant to flow out and to store the liquid-phase refrigerant, respectively. The receiver 22 discharges the separated gas-phase refrigerant to the heating outflow passage 226, and discharges the separated liquid-phase refrigerant to the cooling outflow passage 227.

The heating outflow passage 226 is connected to the heating flow outlet 226a and the refrigerant passage 712. Refrigerant passage 712 is connected to a middle portion of refrigerant passage 711. The refrigerant passage 711 is a passage for guiding the refrigerant flowing out of the decompressor 30 to the suction port of the compressor 33. The heating outflow passage 226 is a passage for guiding the gas-phase refrigerant discharged from the receiver 22 to the compressor 33.

The liquid-phase refrigerant flows from the receiver 22 into the downstream-side heat exchange portion 21. The downstream-side heat exchange portion 21 is a portion that further improves the heat exchange efficiency of the refrigerant in the heat exchanger 2 by exchanging heat between the inflowing liquid-phase refrigerant and the outside air. Specifically, in the heating mode, the downstream-side heat exchange portion 21 exchanges heat between the inflowing liquid-phase refrigerant and the outside air to evaporate the liquid-phase refrigerant. This allows the liquid-phase refrigerant remaining without being completely evaporated in the upstream-side heat exchange portion 20 to be evaporated, and therefore, the function of the heat exchanger 2 as an evaporator is improved. However, since the downstream heat exchange portion 21 has a small number of tubes and a small refrigerant flow path area due to the mounting space, the downstream heat exchange portion may be operated so as not to flow the refrigerant in order to avoid an increase in the refrigerant pressure loss. In the cooling mode, the downstream heat exchange portion 21 functions as a subcooler that further cools the liquid-phase refrigerant by exchanging heat between the inflowing liquid-phase refrigerant and the outside air. Thereby, the function as a condenser in the heat exchanger 2 is improved.

The refrigerant flowing out of the downstream heat exchanger 21 flows into the decompressor 30 through the cooling outflow passage 227 and the refrigerant passage 713 connected to the cooling outflow passage 227. The decompressor 30 decompresses and discharges the refrigerant flowing in. The refrigerant decompressed by the decompressor 30 flows into the evaporator 31. The refrigerant discharged from the evaporator 31 flows into the decompressor 30. The decompressor 30 is a temperature-sensitive mechanical expansion valve that decompresses and expands the 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 set in advance.

The refrigerant discharged from the decompressor 30 flows into the evaporator 31. The evaporator 31 is a heat exchanger that cools the air supply by exchanging heat between the refrigerant flowing inside and the air supply flowing through 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 supply 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 passage 711.

The flow rate adjustment valve 103 is provided in a middle portion from the outflow passage 112 to the heating outflow passage 226. The flow rate adjustment valve 103 is constituted by an electromagnetic valve whose opening degree is adjusted so that the flow path cross-sectional area of the heating outflow path 226 can be changed. By adjusting the opening degree of the flow rate adjustment valve 103, the flow rate of the refrigerant flowing through the heating outflow channel 226 can be adjusted.

The air conditioning unit 73 includes a casing 39 and an air blowing passage switching door 38. The supply air flows through the casing 39. In the casing 39, the evaporator 31 and the heater core 35 are arranged in this order from the upstream side to the downstream side in the flow direction of the blowing air. The evaporator 31 cools the air supply by exchanging heat between the refrigerant flowing therein and the air supply. A warm air passage in which the heater core 35 is disposed and a cool air passage in which the heater core 35 is not disposed are provided on the downstream side of the evaporator 31 in the casing 39.

The air blowing passage switching door 38 is configured to be movable to a first door position indicated by a solid line in the figure, which blocks the cold air passage and opens the warm air passage, and a second door position indicated by a broken line in the figure, which blocks the warm air passage and opens the cold air passage. A plurality of openings, not shown, that open into the vehicle interior are formed on the casing 39 on the downstream side in the air flow direction of the warm air passage and the cool air passage.

In the air conditioning unit 73, in the heating mode, the blowing passage switching door 38 is located at the first door position indicated by the solid line. Thus, since the air passing through the evaporator 31 passes through the warm air passage, the air is heated by the heater core 35 and flows downstream. On the other hand, in the cooling mode, the air blowing passage switching door 38 is located at the second door position indicated by the broken line. Thus, since the air passing through the evaporator 31 passes through the cool air passage, the air cooled by the evaporator 31 flows directly to the downstream side.

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 includes: an upstream-side heat exchange unit 20 and a downstream-side heat exchange unit 21, the upstream-side heat exchange unit 20 and the downstream-side heat exchange unit 21 being heat exchange units that exchange heat between the refrigerant and the outside air during the cooling operation and the heating operation; and a refrigerant adjusting unit 10, wherein the refrigerant adjusting unit 10 is integrally joined to a receiver 22 for storing a liquid refrigerant, and the flow of the refrigerant is switched between the cooling operation and the heating operation. The heat exchanger 2 is provided with an inlet 225a into which refrigerant flows, a cooling outlet 227a from which refrigerant flows out during a cooling operation, and a heating outlet 226a from which refrigerant flows out during a heating operation, and the distance between the inlet 225a and the heating outlet 226a is shorter than the distance between the inlet 225a and the cooling outlet 227 a.

In the present embodiment, 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, and therefore, heat transfer between the inlet 225a and the heating outlet 226a is promoted. Therefore, at the time of heating, the difference between the enthalpy of the refrigerant before entering the heat exchanger 2 and the enthalpy of the refrigerant after exiting the heat exchanger 2 increases, and therefore, the heating performance improves. Further, since the dryness of the gas-liquid two-phase refrigerant introduced from the inlet 225a is reduced, the density of the refrigerant is increased, and the pressure loss of the refrigerant is reduced, thereby improving the heating performance. Further, by decreasing the dryness of the gas-liquid two-phase refrigerant introduced from the inlet 225a, the liquid-phase component of the gas-liquid two-phase refrigerant increases, the refrigerant distribution performance improves, and the heating performance improves.

In the present embodiment, 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, and therefore heat transfer between the inlet 225a and the cooling outlet 227a can be suppressed. When the heat transfer between the inlet 225a and the refrigerant outlet 227a is promoted, there is a concern that the power of the compressor may be deteriorated due to the decrease in the enthalpy difference and the problem may be caused due to the decrease in the degree of supercooling. By suppressing heat transfer between the inflow port 225a and the cooling outflow port 227a, deterioration of the compressor power due to a decrease in the enthalpy difference can be suppressed. Further, by suppressing the decrease in the degree of supercooling, it is possible to avoid an increase in the refrigerant pressure loss of the evaporator 31 due to an increase in the dryness of the refrigerant flowing into the evaporator 31 and a decrease in the cooling performance due to a deterioration in the distribution. Further, it is possible to suppress the occurrence of abnormal sound caused by the gas-phase refrigerant mixing into the refrigerant flowing into the decompressor 30.

In the heat exchanger 2 of the present embodiment, the heat transfer member 27 is provided between the inlet 225a and the heating outlet 226 a. In the present embodiment, a part of the side wall of the reservoir 22 between the inflow channel 225 and the heating outflow channel 226 is used as the heat transfer member 27. By providing the heat transfer member 27 between the inlet 225a and the heating outlet 226a, heat transfer between the inlet 225a and the heating outlet 226a can be further promoted.

As shown in fig. 1, 6, and 7, in the heat exchanger 2 of the present embodiment, the inlet 225a and the heating outlet 226a are formed by a single connector member 25. Fig. 6 is a diagram showing the connector member 25 in fig. 1 in more detail. Fig. 7 is a view showing the connector member 25 in a direction from which the inlet 225a and the hot air outlet 226a are viewed in fig. 6. Further, as in the heat exchanger 2A shown in fig. 3, 8, and 9, the inlet port 225Aa, the heating outlet port 226Aa, and the heat transfer member 27A may be formed by a single connector member 25A. Fig. 8 is a diagram showing the connector member 25A in fig. 3 in more detail. Fig. 9 is a view showing the connector member 25A from the direction in which the inlet port 225Aa and the hot-water outlet port 226Aa are viewed in fig. 8. By configuring the inlet port 225Aa, the heating outlet port 226Aa, and the heat transfer member 27A with a single connector member 25A, a structure for facilitating heat transfer between the inlet port 225Aa and the heating outlet port 226Aa can be realized easily.

Further, the connector member 25A is connected to the inlet port 225Aa and the heating outlet port 226Aa so as to be buried in the heat transfer member 27A. Since the inlet port 225Aa and the heating outlet port 226Aa are connected to each other by the heat transfer member 27A, a heat transfer path can be sufficiently secured, and heat transfer between the inlet port 225Aa and the heating outlet port 226Aa can be further promoted.

In the heat exchanger 2 and the heat exchanger 2A of the present embodiment, the refrigerant outflow port 227a is provided in a member different from the

connector members

25 and 25A. More specifically, the cooling air outlet 227a is provided at an end of the cooling air outlet flow path 227, and the cooling air outlet flow path 227 is connected to the header tank 213 constituting the downstream heat exchanger 21. By providing the cooling outlet 227a in a member different from the

connector members

25, 25A provided with the inlets 225A, 225Aa and the heating outlets 226a, 226Aa, heat transfer between the inlets 225A, 225Aa and the cooling outlet 227a can be suppressed.

Further, as in the heat exchanger 2B shown in fig. 4, the refrigerant outflow port 227Ba may be provided in the receiver 22B. In the heat exchanger 2B, only the upstream-side heat exchange portion 20B is provided, and the heat exchange portion corresponding to the downstream-side heat exchange portion 21 is not provided. The cooling outflow port 227Ba is provided at an end of the cooling outflow channel 227B connected to the receiver 22B.

In the

heat exchangers

2, 2A, and 2B according to the present embodiment, the inlets 225a and 225Aa and the heating outlets 226a and 226Aa are arranged such that the flow direction of the refrigerant in the inlets 225a and 225Aa and the flow direction of the refrigerant in the heating outlets 226a and 226Aa are in convection with each other. The arrangement is such that the refrigerant flow directions of the inlet ports 225a, 225Aa and the heating outlet ports 226a, 226Aa are convection currents, and heat transfer between the inlet ports 225a, 225Aa and the heating outlet ports 226a, 226Aa is further promoted.

In the

heat exchangers

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

reservoirs

22 and 22B, respectively, according to the inlets 225a, 225Aa, the heating outlets 226a and 226Aa, and the

cooling outlets

227a and 227 Ba.

Since the cooling outlet 227a, 227Ba is not disposed between the inlet 225a, 225Aa and the heating outlet 226a, 226Aa, heat transfer between the inlet 225a, 225Aa and the heating outlet 226a, 226Aa can be promoted. Since the heating outlet ports 226a, 226Aa are disposed between the inlet ports 225a, 225Aa and the cooling outlet ports 227a, 227Ba, the heating outlet ports 226a, 226Aa and the channels connected thereto function as heat insulating layers during cooling, and heat transfer between the inlet ports 225a, 225Aa and the cooling outlet ports 227a, 227Ba can be suppressed, thereby avoiding heat damage.

Further, as in the heat exchanger 2C shown in fig. 5, the refrigerant flowing in from the connecting 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 refrigerant adjustment portion 10C from the refrigerant introduction port 115C. As shown in fig. 5, when the flow rate adjustment valve 103C is positioned at the uppermost position, the outflow channel 112C is opened, and the refrigerant flows toward the liquid storage space 224. On the other hand, when the flow rate adjustment valve 103C is positioned at the lowermost position, the outflow channel 112C is closed, and the refrigerant flows toward the hot air outflow port 226 a.

The present embodiment has been described above with reference to specific examples. However, the present invention is not limited to these specific examples. Those skilled in the art can appropriately modify the embodiments of the present invention within the scope of the present invention as long as they have the features of the present invention. The elements, the arrangement, conditions, shapes, and the like of the specific examples are not limited to those illustrated in the drawings, and may be appropriately modified. The combination of the elements included in the specific examples can be changed as appropriate without causing any technical contradiction.

Claims

1. A heat exchanger used in a heat pump system that performs a cooling operation and a heating operation, the heat exchanger comprising:

heat exchange units (20, 21) that exchange heat between the refrigerant and outside air during cooling operation and during heating operation; and

a refrigerant adjusting part (10) which is integrated with a reservoir storing liquid refrigerant and switches the flow of the refrigerant during the cooling operation and the heating operation,

the heat exchanger is provided with: inflow ports (225a, 225Aa) into which the refrigerant flows; a cooling outflow port (227a, 227Ba) through which the refrigerant flows out during cooling operation; and heating outflow ports (226a, 226Aa) through which the refrigerant flows out during heating operation,

a distance between the inlet port and the heating outlet port is configured to be shorter than a distance between the inlet port and the cooling outlet port,

heat transfer members (27, 27A) are provided between the inlet and the heating outlet.

2. The heat exchanger of claim 1,

the inlet (225Aa), the heating outlet (226Aa), and the heat transfer member (27A) are each formed of a single connector member (25A).

3. The heat exchanger of claim 2,

the connector member is connected so that the inlet port and the heating outlet port are embedded in the heat transfer member.

4. The heat exchanger according to claim 2 or 3,

the refrigerant flow outlet is provided in a component different from the connector component.

5. The heat exchanger according to claim 1 or 2,

the inlet port and the heating outlet port are arranged such that a flow direction of the refrigerant in the inlet port and a flow direction of the refrigerant in the heating outlet port are in a counter flow.

6. The heat exchanger according to claim 1 or 2,

the inlet, the heating outlet, and the cooling outlet are arranged in this order in the longitudinal direction of the receiver.