Heat exchanger and decompressor

Abstract

To provide a heat exchanger capable of downsizing the physique of a compound-type heat exchanger.SOLUTION: A heat exchanger includes an evaporator body 12, a high pressure refrigerant inlet part 17, a high pressure refrigerant outlet part 18, and a high pressure refrigerant inside flow passage 32. The evaporator body 12 includes a low pressure refrigerant flow passage 20 where a low pressure refrigerant flows, and a heating medium flow passage 25 where a heating medium which exchanges heat with the low pressure refrigerant flows. The high pressure refrigerant inlet part 17 is provided on a predetermined outer wall surface out of the evaporator body 12, and is a portion where the high pressure refrigerant condensed in a condenser 3 flows in. The high pressure refrigerant outlet part 18 is provided on an outer wall surface on the opposite side with respect to the predetermined outer wall surface out of the evaporator body 12, and is a portion where the high pressure refrigerant flows out. The high pressure refrigerant inside flow passage 32 is a flow passage where the high pressure refrigerant flows inside the evaporator body 12 from the high pressure refrigerant inlet part 17 to the high pressure refrigerant outlet part 18.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present disclosure relates to a heat exchanger and a pressure reducer. [Background technology]

[0002] Patent Document 1 discloses a composite heat exchanger that integrates a condenser, a liquid storage section, a supercooling section, an internal heat exchanger, a pressure reducer, and an evaporator that constitute a refrigeration cycle device. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Publication No. 2023-141253 Summary of the Invention [Problem to be solved by the invention]

[0004] In the combined heat exchanger described in Patent Document 1, a pressure reducer is disposed between the evaporator and the internal heat exchanger, which makes it difficult to route the piping connected to the pressure reducer, and there is a risk that the combined heat exchanger will become large in size.

[0005] In view of the above, an object of the present disclosure is to provide a heat exchanger and a pressure reducer that enable the size of a combined heat exchanger to be reduced. [Means for solving the problem]

[0006] According to one aspect of the present disclosure, a heat exchanger used in a refrigeration cycle device (1) performs heat exchange between a high-pressure refrigerant pressurized by a compressor (2) and condensed by a condenser (3) and then decompressed by a pressure reducer (6) and a heat medium, thereby evaporating the low-pressure refrigerant and cooling the heat medium, and includes: an evaporator body (12) having a low-pressure refrigerant flow path (20) through which a low-pressure refrigerant flows, and a heat medium flow path (25) through which a heat medium flows that exchanges heat with the low-pressure refrigerant flowing through the low-pressure refrigerant flow path; a high-pressure refrigerant inlet (17) provided on a predetermined outer wall surface of the evaporator body, into which the high-pressure refrigerant condensed in the condenser flows; a high-pressure refrigerant outlet (18) provided on an outer wall surface of the evaporator body opposite to the predetermined outer wall surface, through which high-pressure refrigerant flows out; and a high-pressure refrigerant internal flow path (32) through which high-pressure refrigerant flows inside the evaporator body from the high-pressure refrigerant inlet port to the high-pressure refrigerant outlet port.

[0007] According to this, when a combined heat exchanger is configured in which a condenser and a pressure reducer are integrated with an evaporator as a heat exchanger, the configuration in which high-pressure refrigerant passes through the interior of the evaporator makes it possible to place the pressure reducer on the opposite side of the evaporator from the condenser. Therefore, compared to a configuration in which the pressure reducer is placed between the evaporator and the condenser, the routing of piping connected to the pressure reducer is easier. Therefore, this heat exchanger configuration allows the combined heat exchanger to be downsized. Furthermore, if the configuration in which high-pressure refrigerant passes through the interior of the evaporator is used, the internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant passing through the evaporator can be expected to improve the cooling performance of the refrigeration cycle device.

[0008] According to another aspect of the present disclosure, a pressure reducer used in a refrigeration cycle apparatus (1) and having a function of reducing the pressure of a high-pressure refrigerant pressurized by a compressor (2) after condensing it in a condenser (3) comprises: a pressure reducer body (62); a pressure reducer-side high-pressure refrigerant inlet (60) provided on an outer wall surface of the pressure reducer body, into which the high-pressure refrigerant condensed in the condenser flows; a pressure reducer-side high-pressure refrigerant outlet (64) provided on an outer wall surface of the pressure reducer body and through which high-pressure refrigerant flows out; a pressure reducer-side high-pressure refrigerant internal flow path (65) through which a high-pressure refrigerant flows inside the pressure reducer body from the pressure reducer-side high-pressure refrigerant inlet port to the pressure reducer-side high-pressure refrigerant outlet port; a branching portion (66) provided midway through the pressure reducer-side high-pressure refrigerant internal flow path, which branches the flow of high-pressure refrigerant; a pressure reducing section (63) that reduces the pressure of one of the high-pressure refrigerant flows branched off at the branch section; and a pressure reducer-side low-pressure refrigerant outlet (61) through which the low-pressure refrigerant reduced in pressure by the pressure reducing section flows out.

[0009] In this case, when a combined heat exchanger is constructed by integrating a condenser, an evaporator, and a pressure reducer, the high-pressure refrigerant flows through the pressure reducer body, which facilitates the routing of the refrigerant piping connected to the pressure reducer. Therefore, this pressure reducer configuration allows the pressure reducer and the evaporator to be easily connected, and further facilitates the construction of a refrigeration cycle device downstream of the pressure reducer-side high-pressure refrigerant outlet.

[0010] The reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and the specific components described in the embodiments described below. [Brief explanation of the drawings]

[0011] [Figure 1] 1 is a circuit diagram of a refrigeration cycle device including an evaporator according to a first embodiment. [Figure 2] FIG. 2 is a schematic diagram of a composite heat exchanger in which a condenser, a liquid storage section, and a pressure reducer are connected to an evaporator according to the first embodiment. [Figure 3] FIG. 2 is a perspective view of the evaporator according to the first embodiment. [Figure 4] FIG. 2 is a perspective view of an evaporator main body included in the evaporator according to the first embodiment. [Figure 5] 3 is a schematic diagram for explaining the flow of low-pressure refrigerant and high-pressure refrigerant in the evaporator according to the first embodiment. FIG. [Figure 6] 3 is a schematic diagram for explaining the flow of a heat medium and a high-pressure refrigerant in the evaporator according to the first embodiment. FIG. [Figure 7] FIG. 2 is a schematic diagram of an evaporator according to the first embodiment. [Figure 8] 1 is a partial cross-sectional view perpendicular to the stacking direction of an evaporator according to a first embodiment. [Figure 9] 1 is a partial cross-sectional view perpendicular to the stacking direction of an evaporator according to a first embodiment. [Figure 10] FIG. 10 is a cross-sectional view taken along line XX of FIG. 9. [Figure 11] FIG. 1 is a Mollier diagram showing an example of the behavior of a refrigerant when heat is exchanged between a high-pressure refrigerant flowing through an internal flow path of the high-pressure refrigerant and a low-pressure refrigerant flowing through an outlet-side tank of the low-pressure refrigerant in a refrigeration cycle device equipped with an evaporator according to the first embodiment. [Figure 12] FIG. 1 is a Mollier diagram showing an example of the behavior of a refrigerant when heat exchange occurs between a high-pressure refrigerant flowing through a high-pressure refrigerant internal flow path and a low-pressure refrigerant flowing through a low-pressure refrigerant inlet tank or a low-pressure refrigerant flow path layer in a refrigeration cycle device equipped with an evaporator according to the first embodiment. [Figure 13] FIG. 2 is a perspective view of a pressure reducer connected to an evaporator according to the first embodiment. [Figure 14] FIG. 2 is a perspective view of a condenser connected to an evaporator according to the first embodiment. [Figure 15] FIG. 6 is a schematic diagram of a refrigeration cycle device including an evaporator according to a second embodiment. [Figure 16] FIG. 10 is a perspective view showing a lubricant oil inflow prevention flow path in an evaporator according to a second embodiment. [Figure 17] FIG. 10 is a perspective view showing a lubricant oil inflow prevention flow path in an evaporator according to a modified example of the second embodiment. [Figure 18] FIG. 10 is a schematic diagram of a refrigeration cycle device including an evaporator according to a third embodiment. [Figure 19] FIG. 10 is a schematic diagram of a refrigeration cycle device including an evaporator according to a fourth embodiment. [Figure 20] FIG. 10 is a schematic diagram of a refrigeration cycle device including an evaporator according to a fifth embodiment. [Figure 21] FIG. 10 is a schematic diagram of a refrigeration cycle device including an evaporator according to a sixth embodiment. [Figure 22] FIG. 10 is a schematic diagram of a refrigeration cycle device including an evaporator according to a seventh embodiment. [Figure 23] FIG. 13 is a schematic diagram of a refrigeration cycle device including an evaporator according to an eighth embodiment. [Figure 24] FIG. 13 is a schematic diagram of a refrigeration cycle device including an evaporator according to a ninth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0012] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, identical or equivalent parts will be denoted by the same reference numerals, and description thereof will be omitted.

[0013] (First embodiment) The evaporator as the heat exchanger according to the first embodiment is used in a refrigeration cycle device mounted on, for example, an electric vehicle.

[0014] <Circuit configuration of refrigeration cycle device> First, the circuit configuration of the refrigeration cycle device will be described with reference to FIG.

[0015] As shown in Fig. 1, the refrigeration cycle apparatus 1 includes a compressor 2, a condenser 3, a liquid storage section 4, a subcooling section 5, a pressure reducer 6, and an evaporator 7. The refrigerant used in the refrigeration cycle apparatus 1 is a refrigerant with a low global warming potential, such as HFO-1234yf. Lubricating oil for lubricating the compressor 2 circulates in the refrigerant circuit of the refrigeration cycle apparatus 1 together with the refrigerant. The lubricating oil used is one that is compatible with the liquid refrigerant, such as PAG oil.

[0016] The compressor 2 is a device that compresses and discharges a refrigerant. The compressor 2 is configured as an electric compressor that is driven by power supplied from a battery (not shown). The drive of the compressor 2 is controlled by a control signal output from an electronic control unit 8 (hereinafter referred to as "ECU 8").

[0017] A condenser 3 is connected to the refrigerant discharge side of the compressor 2. The condenser 3 is a radiator that exchanges heat between the high-temperature, high-pressure refrigerant discharged from the compressor 2 and the high-temperature side heat medium flowing through the high-temperature side heat medium circuit 9. The condenser 3 has the function of condensing the high-pressure refrigerant and heating the high-temperature side heat medium by heat exchange between the high-pressure refrigerant and the high-temperature side heat medium.

[0018] Here, the high-temperature side heat medium is a fluid that flows through the high-temperature side heat medium circuit 9. For example, a liquid containing ethylene glycol or an antifreeze liquid is used as the high-temperature side heat medium. Although not shown, the high-temperature side heat medium circuit 9 is provided with, for example, a high-temperature side pump, an electric heater, a high-temperature side radiator, a heater core, etc.

[0019] A liquid storage section 4 is connected to the refrigerant outlet side of the condenser 3. The liquid storage section 4 is a receiver that stores excess refrigerant in the refrigeration cycle device 1. The liquid storage section 4 separates the high-pressure refrigerant flowing out from the condenser 3 into gas and liquid, temporarily stores the separated high-pressure liquid refrigerant, and then discharges the high-pressure liquid refrigerant.

[0020] A supercooling section 5 is connected to the refrigerant outlet side of the liquid storage section 4. The supercooling section 5 supercools the high-pressure liquid refrigerant by exchanging heat between the high-pressure liquid refrigerant flowing out of the liquid storage section 4 and the high-temperature side heat medium before flowing into the condenser 3. The condenser 3 and the supercooling section 5 may be configured integrally, or the supercooling section 5 may be omitted.

[0021] A pressure reducer 6 is connected to the refrigerant outlet side of the subcooling unit 5. The pressure reducer 6 has the function of reducing the pressure and expanding the high-pressure liquid refrigerant that has passed through the internal heat exchanger, to produce a low-pressure refrigerant in a gas-liquid two-phase state. The pressure reducer 6 is also called an expansion valve. The pressure reducer 6 is configured, for example, by an electric variable throttle whose operation is controlled by a control signal output from the ECU 8.

[0022] An evaporator 7, which serves as a heat exchanger in this embodiment, is connected to the refrigerant outlet side of the pressure reducer 6. The evaporator 7 is a chiller that exchanges heat between the low-pressure refrigerant reduced in pressure by the pressure reducer 6 and the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 10. The evaporator 7 has a function of evaporating the low-pressure refrigerant and cooling the low-temperature side heat medium by heat exchange between the low-pressure refrigerant and the low-temperature side heat medium.

[0023] Here, the low-temperature side heat medium is a fluid that flows through the low-temperature side heat medium circuit 10. For example, a liquid containing ethylene glycol or an antifreeze liquid is used as the low-temperature side heat medium. Although not shown, the low-temperature side heat medium circuit 10 is provided with, for example, a low-temperature side pump, a low-temperature side radiator, a cooler core, etc. In the following description, the low-temperature side heat medium will simply be referred to as the "heat medium."

[0024] The refrigerant outlet side of the evaporator 7 is connected to the refrigerant suction side of the compressor 2. As a result, the low-pressure refrigerant that has passed through the evaporator 7 is sucked into the compressor 2 and then compressed again.

[0025] The ECU 8 is composed of a microcomputer including a processor and memory and its peripheral circuits. The ECU 8 is an abbreviation for Electronic Control Unit. The memory of the ECU 8 is composed of a non-transitory physical storage medium. The ECU 8 performs various arithmetic processing based on control programs stored in the memory, and controls the operation of each component of the refrigeration cycle device 1, such as the compressor 2 and the pressure reducer 6.

[0026] As shown in Fig. 2, in the first embodiment, the condenser 3, liquid storage section 4, supercooling section 5, pressure reducer 6, and evaporator 7 are joined together to form a combined heat exchanger 11. The condenser 3 and supercooling section 5 are integrated. The combined heat exchanger 11 is arranged in the following order from the left side of Fig. 2: liquid storage section 4, condenser 3 and supercooling section 5, evaporator 7, and pressure reducer 6. Arranging the components of the combined heat exchanger 11 in this order facilitates the routing of piping connected to the pressure reducer 6, and the size of the combined heat exchanger 11 can be reduced.

[0027] Next, the evaporator 7, the pressure reducer 6, and the condenser 3 that constitute the combined heat exchanger 11 will be described in detail.

[0028] <About the evaporator 7> First, we will explain the evaporator 7. As shown in Figures 2 to 6, the evaporator 7 has an evaporator body 12, a low-pressure refrigerant inlet 13, a low-pressure refrigerant outlet 14, a heat medium inlet 15, a heat medium outlet 16, a high-pressure refrigerant inlet 17, and a high-pressure refrigerant outlet 18.

[0029] The evaporator body 12 is configured by stacking a plurality of plate-like members 19 and joining them by brazing or the like. In Figure 2 and other figures, the direction in which the plurality of plate-like members 19 that make up the evaporator body 12 are stacked (i.e., the stacking direction) is indicated by an arrow DL. Also in Figure 2 and other figures, the vertical direction when the combined heat exchanger 11 is mounted on a vehicle is indicated by an arrow DG.

[0030] The evaporator body 12 has a low-pressure refrigerant flow path 20 through which a low-pressure refrigerant flows, a heat medium flow path 25 through which a heat medium that exchanges heat with the low-pressure refrigerant flows, and a high-pressure refrigerant internal flow path 32 through which a high-pressure refrigerant flows.

[0031] 2, 4, and 5, the low-pressure refrigerant flow path 20 has a low-pressure refrigerant inlet-side tank 21, a plurality of low-pressure refrigerant flow path layers 22, and a low-pressure refrigerant outlet-side tank 23. The low-pressure refrigerant that flows from the low-pressure refrigerant inlet portion 13 into the low-pressure refrigerant inlet-side tank 21 via a low-pressure refrigerant inlet-side wall flow path 24 (described later) is divided into the plurality of low-pressure refrigerant flow path layers 22, then collects in the low-pressure refrigerant outlet-side tank 23, and flows out from the low-pressure refrigerant outlet portion 14.

[0032] 2, 4, and 6, the heat medium flow path 25 has a heat medium inlet-side tank 26, a plurality of heat medium flow path layers 27, and a heat medium outlet-side tank 28. The low-pressure refrigerant that flows from the heat medium inlet section 15 into the heat medium inlet-side tank 26 via a heat medium inlet-side wall flow path 29 (described later) is divided into the plurality of heat medium flow path layers 27, then collects in the heat medium outlet-side tank 28, and flows out of the heat medium outlet section 16 via a heat medium outlet-side wall flow path 30 (described later).

[0033] As shown in FIGS. 2 to 6 , the evaporator body 12 is a laminated heat exchanger in which a plurality of low-pressure refrigerant channel layers 22 and a plurality of heat medium channel layers 27 are alternately stacked in a predetermined stacking direction. The stacking direction intersects with the vertical direction. A low-pressure refrigerant inlet tank 21 is provided vertically above the evaporator body 12, and a low-pressure refrigerant outlet tank 23 is provided vertically below the evaporator body 12. Therefore, the low-pressure refrigerant flowing through the plurality of low-pressure refrigerant channel layers 22 flows vertically downward from the low-pressure refrigerant inlet tank 21 toward the low-pressure refrigerant outlet tank 23. Meanwhile, a heat medium inlet tank 26 is provided vertically below the evaporator body 12, and a heat medium outlet tank 28 is provided vertically above the evaporator body 12. Therefore, the heat medium flowing through the plurality of heat medium channel layers 27 flows vertically upward from the heat medium inlet tank 26 toward the heat medium outlet tank 28. Therefore, the evaporator body 12 is configured so that the flow of low-pressure refrigerant in the plurality of low-pressure refrigerant channel layers 22 and the flow of heat medium in the plurality of heat medium channel layers 27 are counter-flowing.

[0034] A high-pressure refrigerant inlet 17 and the like are provided on an outer wall surface of the evaporator body 12 on one side in the stacking direction (i.e., the outer wall surface of the evaporator body 12 facing the condenser 3 side). On the other hand, a high-pressure refrigerant outlet 18 and a high-pressure refrigerant outlet-side wall flow path 31 and the like are provided on an outer wall surface of the evaporator body 12 on the other side in the stacking direction (i.e., the outer wall surface of the evaporator body 12 facing the pressure reducer 6 side). The high-pressure refrigerant inlet 17 and the high-pressure refrigerant outlet-side wall flow path 31 are connected by a high-pressure refrigerant internal flow path 32 provided inside the evaporator body 12.

[0035] The high-pressure refrigerant inlet 17 is the portion into which the high-pressure refrigerant flows. The high-pressure refrigerant inlet 17 also functions as a connection portion for connecting to the condenser-side high-pressure refrigerant outlet 45 provided in the condenser body 40. The high-pressure refrigerant inlet 17 and the condenser-side high-pressure refrigerant outlet 45 are directly connected at only one location. In the present disclosure, "direct connection" refers to a connection without any substantial or practical flow path component, and also includes a connection via a washer or the like that is not a substantial or practical flow path component. The high-pressure refrigerant inlet 17 and the condenser-side high-pressure refrigerant outlet 45 may be directly connected at multiple locations.

[0036] On the other hand, the high-pressure refrigerant outlet 18 is a portion from which the high-pressure refrigerant flows out. The high-pressure refrigerant outlet 18 also functions as a connecting portion that directly connects to a pressure reducer-side high-pressure refrigerant inlet 60 provided in the pressure reducer 6. The high-pressure refrigerant outlet-side wall flow path 31 is provided on the outer wall surface of the evaporator body 12 on the side where the high-pressure refrigerant outlet 18 is provided, and is a flow path that connects the high-pressure refrigerant internal flow path 32 and the high-pressure refrigerant outlet 18.

[0037] The high-pressure refrigerant (specifically, high-pressure liquid refrigerant) flowing from the condenser-side high-pressure refrigerant outlet 45 into the high-pressure refrigerant inlet 17 of the evaporator body 12 flows through the high-pressure refrigerant internal flow path 32, and then flows out from the high-pressure refrigerant outlet 18 to the pressure reducer-side high-pressure refrigerant inlet 60 via the high-pressure refrigerant outlet-side wall flow path 31.

[0038] In addition to the high-pressure refrigerant inlet 17, the evaporator body 12 has an outer wall surface on one side in the stacking direction provided with a heat medium inlet 15, a heat medium inlet-side wall flow path 29, a heat medium outlet-side wall flow path 30, and a heat medium outlet 16. The heat medium inlet 15 is the portion into which the heat medium flows. The heat medium inlet-side wall flow path 29 is a flow path that connects the heat medium inlet 15 with a heat medium inlet-side tank 26. The heat medium outlet 16 is the portion from which the heat medium flows out. The heat medium outlet-side wall flow path 30 is a flow path that connects the heat medium outlet-side tank 28 with the heat medium outlet 16.

[0039] On the other hand, the outer wall surface of the evaporator body 12 on the other side in the stacking direction is provided with a low-pressure refrigerant inlet 13, a low-pressure refrigerant inlet-side wall flow path 24, and a low-pressure refrigerant outlet 14, in addition to a high-pressure refrigerant outlet 18 and a high-pressure refrigerant outlet-side wall flow path 31. The low-pressure refrigerant inlet 13 is the portion into which the low-pressure refrigerant flows. The low-pressure refrigerant inlet 13 also functions as a connecting portion that is directly connected to a pressure reducer-side low-pressure refrigerant outlet 61 provided in the pressure reducer 6. The low-pressure refrigerant inlet-side wall flow path 24 is a flow path that connects the low-pressure refrigerant inlet 13 and the low-pressure refrigerant inlet-side tank 21. The low-pressure refrigerant outlet 14 is the portion from which the low-pressure refrigerant flows out.

[0040] The high-pressure refrigerant flowing out from the high-pressure refrigerant outlet 18 of the evaporator body 12 is decompressed through the pressure reducer-side high-pressure refrigerant inlet 60 at the pressure reducer section 63 provided inside the pressure reducer body 62, becomes a gas-liquid two-phase low-pressure refrigerant, and flows out from the pressure reducer-side low-pressure refrigerant outlet 61. The low-pressure refrigerant flows again from the low-pressure refrigerant inlet 13 of the evaporator 7 through the low-pressure refrigerant inlet-side wall flow path 24 and into the low-pressure refrigerant inlet-side tank 21.

[0041] On the outer wall surface of the evaporator body 12, the high-pressure refrigerant outlet 18 and the low-pressure refrigerant inlet 13 connected to the pressure reducer 6 are positioned toward the center of the evaporator body 12 with respect to the low-pressure refrigerant outlet 14. Specifically, on the outer wall surface of the evaporator body 12, the low-pressure refrigerant outlet 14 is positioned vertically downward with respect to the high-pressure refrigerant outlet 18 and the low-pressure refrigerant inlet 13 connected to the pressure reducer 6. This makes it easier to connect the pressure reducer 6 to the high-pressure refrigerant outlet 18 and the low-pressure refrigerant inlet 13 of the evaporator 7, and also makes it possible to position the downstream refrigerant piping connected to the low-pressure refrigerant outlet 14 of the evaporator 7 so as to avoid the pressure reducer 6.

[0042] Here, the evaporator 7 is configured so that heat exchange between the high-pressure refrigerant and the heat medium is suppressed relative to internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant. The configuration will be described in detail below.

[0043] As shown in FIG. 7 , the evaporator body 12 has a low-pressure refrigerant channel layer 22 as the endmost layer on at least one side in the stacking direction. That is, the evaporator body 12 does not have a heat medium channel layer 27 as the endmost layer on at least one side in the stacking direction. As shown by arrow HT1, by using the low-pressure refrigerant channel layer 22 as the endmost layer on one side in the stacking direction, heat from the high-pressure refrigerant inlet 17 is transferred to the low-pressure refrigerant flowing through the low-pressure refrigerant channel layer 22. As shown by arrow HT2, by using the low-pressure refrigerant channel layer 22 as the endmost layer on the other side in the stacking direction, heat from the high-pressure refrigerant outlet 18 and the high-pressure refrigerant outlet-side wall channel 31 is transferred to the low-pressure refrigerant flowing through the low-pressure refrigerant channel layer 22. This suppresses heat transfer from the high-pressure refrigerant inlet 17, the high-pressure refrigerant outlet 18, and the high-pressure refrigerant outlet-side wall channel 31 to the heat medium flowing through the heat medium channel layer 27.

[0044] As a modification of the first embodiment, the evaporator body 12 may have at least one of the endmost layers on one side and the other side in the stacking direction as an insulating space layer instead of the low-pressure refrigerant channel layer 22. By using an insulating space layer as the endmost layer on one side in the stacking direction, it is possible to suppress heat transfer from the high-pressure refrigerant inlet 17 to the heat medium flowing through the heat medium channel layer 27. Furthermore, by using the low-pressure refrigerant channel layer 22 as the endmost layer on the other side in the stacking direction, it is possible to suppress heat transfer from the high-pressure refrigerant outlet 18 and the high-pressure refrigerant outlet-side wall channel 31 to the heat medium flowing through the heat medium channel layer 27.

[0045] 8, inside the evaporator body 12, the high-pressure refrigerant internal flow path 32 is disposed between the low-pressure refrigerant outlet-side tank 23 and the heat medium inlet-side tank 26. The distance D1 between the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant outlet-side tank 23 is shorter than the distance D2 between the high-pressure refrigerant internal flow path 32 and the heat medium inlet-side tank 26. This promotes internal heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through the low-pressure refrigerant outlet-side tank 23. Meanwhile, heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the heat medium flowing through the heat medium inlet-side tank 26 can be suppressed. Note that even if heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the heat medium flowing through the heat medium inlet-side tank 26 is suppressed but slight heat exchange occurs, the heat medium is cooled as it flows through the multiple heat medium flow path layers 27, and therefore a decrease in the cooling capacity of the heat medium by the evaporator 7 is suppressed.

[0046] 9 and 10 , in the evaporator body 12, the high-pressure refrigerant internal flow path 32 is surrounded by a plurality of low-pressure refrigerant flow path layers 22. This allows internal heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through the low-pressure refrigerant flow path layer 22, and suppresses heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the heat medium flowing through the heat medium flow path layer 27 and the heat medium inlet-side tank 26.

[0047] The effects of the above-described configuration in which high-pressure refrigerant and low-pressure refrigerant exchange heat internally in the evaporator 7 will be described.

[0048] 11 and 12 are Mollier diagrams showing an example of the behavior of the refrigerant circulating in the refrigeration cycle apparatus 1. Line SL indicates the saturated liquid line, point CP indicates the critical point, and line SV indicates the saturated vapor line.

[0049] Points A1 to A4 in Fig. 11 show the behavior of the refrigerant circulating in a refrigeration cycle device, which is configured as a comparative example of the first embodiment, in which the high-pressure refrigerant flowing from the subcooling unit 5 to the pressure reducer 6 does not exchange heat at all with the low-pressure refrigerant and heat medium flowing in the evaporator 7. In the following description, the refrigeration cycle device configured in this way is referred to as the "comparative refrigeration cycle device."

[0050] Specifically, in the refrigeration cycle device of the comparative example, point A1 indicates the state of the refrigerant after being discharged from the compressor 2 and before flowing into the condenser 3, point A2 indicates the state of the refrigerant after flowing through the condenser 3, the liquid storage section 4 and the subcooling section 5 and before flowing into the pressure reducer 6, point A3 indicates the state of the refrigerant after flowing out of the pressure reducer 6 and before flowing into the evaporator 7, and point A4 indicates the state of the refrigerant after flowing out of the evaporator 7 and before being sucked into the compressor 2.

[0051] 11 show the behavior of the refrigerant when heat exchange occurs between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through the low-pressure refrigerant outlet tank 23 in the refrigeration cycle apparatus 1 of this embodiment. Hereinafter, the heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through the low-pressure refrigerant outlet tank 23 will be referred to as "internal heat exchange between the high-pressure refrigerant and the outlet-side low-pressure refrigerant." Specifically, in the refrigeration cycle apparatus 1 of this embodiment, point B1 shows the state of the refrigerant after being discharged from the compressor 2 and before flowing into the condenser 3. Point B2 shows the state of the refrigerant after flowing through the condenser 3, the liquid storage section 4, and the subcooling section 5 and before flowing into the pressure reducer 6. Point B3 shows the state of the refrigerant after flowing out of the pressure reducer 6 and before flowing into the evaporator 7. Point B4 shows the state of the refrigerant after flowing out of the evaporator 7 and before being drawn into the compressor 2.

[0052] In this case, as indicated by point A2-B2, the enthalpy of the high-pressure refrigerant (i.e., the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32) after flowing out of the supercooling section 5 and before flowing into the pressure reducer 6 decreases due to internal heat exchange between the high-pressure refrigerant and the outlet-side low-pressure refrigerant. In other words, the degree of subcooling of the high-pressure refrigerant after flowing out of the supercooling section 5 and before flowing into the pressure reducer 6 increases. Therefore, as indicated by point B3-A4 (i.e., arrow ΔH1 in FIG. 11 ), the refrigeration cycle apparatus 1 of this embodiment has an improved cooling capacity of the heat medium by the evaporator 7 compared to the refrigeration cycle apparatus of the comparative example due to internal heat exchange between the high-pressure refrigerant and the outlet-side low-pressure refrigerant.

[0053] Like Fig. 11, points A1 to A4 in Fig. 12 also show the behavior of the refrigerant circulating in the refrigeration cycle apparatus of the comparative example. In contrast, points C1 to C4 in Fig. 12 show the behavior of the refrigerant when heat exchange occurs between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through the low-pressure refrigerant flow path layer 22 or the low-pressure refrigerant inlet-side tank 21 in the refrigeration cycle apparatus 1. However, the refrigeration cycle apparatus 1 of this embodiment employs a configuration in which heat exchange occurs between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through a portion of the low-pressure refrigerant flow path layer 22, but does not employ a configuration in which heat exchange occurs with the low-pressure refrigerant flowing through the low-pressure refrigerant inlet-side tank 21. Hereinafter, the heat exchange between the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant flowing through the low-pressure refrigerant flow path layer 22 or the low-pressure refrigerant inlet-side tank 21 will be referred to as "heat exchange between the high-pressure refrigerant and the inlet-side low-pressure refrigerant." Specifically, in the refrigeration cycle device 1, point C1 indicates the state of the refrigerant after being discharged from the compressor 2 and before flowing into the condenser 3, point C2 indicates the state of the refrigerant after flowing through the condenser 3, the liquid storage section 4 and the subcooling section 5 and before flowing into the pressure reducer 6, point C3 indicates the state of the refrigerant after flowing out of the pressure reducer 6 and before flowing into the evaporator 7, and point C4 indicates the state of the refrigerant after flowing out of the evaporator 7 and before being sucked into the compressor 2.

[0054] In this case, as indicated by point A2-C2, heat exchange between the high-pressure refrigerant and the inlet-side low-pressure refrigerant reduces the enthalpy of the high-pressure refrigerant before flowing into the pressure reducer 6 via the subcooling section 5 (i.e., the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32). However, as indicated by point C3-A3, the enthalpy of the refrigerant flowing through the low-pressure refrigerant inlet-side tank 21 or the low-pressure refrigerant flow path layer 22 increases. Therefore, as indicated by point A3-C4 (i.e., arrow ΔH2 in FIG. 12), in the refrigeration cycle device 1 of this embodiment, even though heat exchange between the high-pressure refrigerant and the inlet-side low-pressure refrigerant occurs, the cooling capacity of the heat medium by the evaporator 7 does not change compared to the refrigeration cycle device of the comparative example.

[0055] <About Pressure Reducer 6> Next, the pressure reducer 6 will be described in detail. As shown in Figures 2 and 13, the pressure reducer 6 has a pressure reducer body 62, a pressure reducer-side high-pressure refrigerant inlet 60, a pressure reducer-side low-pressure refrigerant outlet 61, a pressure reducer-side high-pressure refrigerant outlet 64, a pressure reducer-side high-pressure refrigerant internal flow path 65, a branching section 66, a pressure reduction section 63, an actuator 67, etc.

[0056] The pressure reducer body 62 is formed of, for example, a metal block, and has a flow path formed therein through which the refrigerant flows. The pressure reducer-side high-pressure refrigerant inlet 60 and the pressure reducer-side low-pressure refrigerant outlet 61 are provided on an outer wall surface of the pressure reducer body 62 facing the condenser 3. The pressure reducer-side high-pressure refrigerant outlet 64 is provided on an outer wall surface of the pressure reducer body 62 facing away from the condenser 3.

[0057] A pressure reducer-side high-pressure refrigerant internal flow path 65, a branching portion 66, and a pressure reducing portion 63 are provided inside the pressure reducer body 62. The pressure reducer-side high-pressure refrigerant internal flow path 65 is a flow path that connects the pressure reducer-side high-pressure refrigerant inlet portion 60 and the pressure reducer-side high-pressure refrigerant outlet portion 64. The branching portion 66 is provided midway through the pressure reducer-side high-pressure refrigerant internal flow path 65, and is a portion where the flow of high-pressure refrigerant branches. One flow branched at the branching portion 66 flows toward the pressure reducing portion 63, and the other flow flows toward the pressure reducer-side high-pressure refrigerant outlet portion 64.

[0058] The pressure reducing section 63 has a function of reducing the pressure of the high-pressure refrigerant in one flow branched at the branching section 66 to form a gas-liquid two-phase low-pressure refrigerant by varying the flow path area by driving the actuator 67. The low-pressure refrigerant reduced in pressure reducing section 63 flows out from the pressure reducer-side low-pressure refrigerant outlet section 61.

[0059] The pressure reducer-side high-pressure refrigerant inlet 60 is connected to the high-pressure refrigerant outlet 18 of the evaporator 7, and the pressure reducer-side low-pressure refrigerant outlet 61 is connected to the low-pressure refrigerant inlet 13 of the evaporator 7. Therefore, high-pressure refrigerant (specifically, high-pressure liquid refrigerant condensed in the condenser 3 and passing through the evaporator 7) flows into the pressure reducer-side high-pressure refrigerant inlet 60 from the high-pressure refrigerant outlet 18 of the evaporator 7. The high-pressure refrigerant that flows from the pressure reducer-side high-pressure refrigerant inlet 60 into the pressure reducer-side high-pressure refrigerant internal flow path 65 is branched at the branching portion 66, and one flow is decompressed at the pressure reducer portion 63 to become a gas-liquid two-phase low-pressure refrigerant and flows from the pressure reducer-side low-pressure refrigerant outlet 61 to the low-pressure refrigerant inlet 13 of the evaporator 7. The other flow branched at the branching portion 66 passes through the pressure reducer main body 62 without changing into the high-pressure refrigerant through the pressure reducer-side high-pressure refrigerant internal flow path 65 and flows out from the pressure reducer-side high-pressure refrigerant outlet 64.

[0060] <About Condenser 3> Next, the condenser 3 will be described in detail. As shown in Fig. 2 and Fig. 14, the condenser 3 is also a laminated heat exchanger configured by stacking a plurality of plate-like members 42 and joining them by brazing or the like. The lamination direction of the condenser body 40 is the same as the lamination direction of the evaporator body 12. The condenser body 40 has a condenser-side high-pressure refrigerant flow path 43 through which a high-pressure refrigerant flows, and a high-temperature side heat medium flow path 50 through which a high-temperature side heat medium flows that exchanges heat with the high-pressure refrigerant.

[0061] The condenser body 40 has an outer wall surface facing the evaporator 7 provided with a condenser-side high-pressure refrigerant inlet 44, a condenser-side high-pressure refrigerant outlet 45, a high-temperature side heat medium inlet 51, a high-temperature side heat medium inlet-side wall flow path 52, and a high-temperature side heat medium outlet 53. The condenser body 40 has an outer wall surface facing the liquid storage section 4 provided with a condenser-side second high-pressure refrigerant outlet 46, a condenser-side second high-pressure refrigerant inlet 47, and the like.

[0062] The condenser-side high-pressure refrigerant inlet 44 is a portion into which high-pressure refrigerant (specifically, high-pressure gas refrigerant) discharged from the compressor 2 flows. The high-pressure refrigerant supplied to the condenser-side high-pressure refrigerant inlet 44 flows through a condenser-side high-pressure refrigerant flow path 43 provided inside the condenser body 40, and condenses by releasing heat to the high-temperature side heat medium flowing through the high-temperature side heat medium flow path 50. The high-pressure refrigerant that has flowed through the condenser-side high-pressure refrigerant flow path 43 flows into the liquid storage section 4 from a condenser-side high-pressure refrigerant second outlet 46. The liquid-phase high-pressure refrigerant (i.e., high-pressure liquid refrigerant) that has been separated into gas and liquid in the liquid storage section 4 flows from the liquid storage section 4 into a condenser-side high-pressure refrigerant second inlet 47. The high-pressure refrigerant that has flowed into the condenser-side high-pressure refrigerant second inlet 47 flows through a subcooling section 5 formed integrally with the condenser 3, releasing heat to the high-temperature side heat medium flowing through the high-temperature side heat medium flow path 50, and is then supercooled, and flows out from a condenser-side high-pressure refrigerant outlet 45. As described above, the condenser-side high-pressure refrigerant outlet 45 and the high-pressure refrigerant inlet 17 of the evaporator 7 are directly connected at only one point. Therefore, the high-pressure refrigerant flowing out from the condenser-side high-pressure refrigerant outlet 45 flows into the high-pressure refrigerant inlet 17 of the evaporator 7.

[0063] The high-temperature side heat medium is supplied to the high-temperature side heat medium inlet portion 51. The high-temperature side heat medium supplied to the high-temperature side heat medium inlet portion 51 passes through the high-temperature side heat medium inlet side wall flow path 52 and flows through the high-temperature side heat medium flow path 50 provided inside the condenser body 40, while absorbing heat from the high-pressure refrigerant flowing through the condenser side high-pressure refrigerant flow path 43 and the subcooling portion 5. The high-temperature side heat medium that has flowed through the high-temperature side heat medium flow path 50 flows out from the high-temperature side heat medium outlet portion 53.

[0064] Although not shown in the figures, a high-temperature side heat medium outlet side wall flow path that connects the high-temperature side heat medium flow path 50 and the high-temperature side heat medium outlet portion 53 may be provided on the outer wall surface of the condenser body 40 facing the evaporator 7, as necessary.

[0065] The evaporator 7 as a heat exchanger of the first embodiment described above has the following advantages.

[0066] (1) The evaporator 7 of the first embodiment includes an evaporator body 12, a high-pressure refrigerant inlet 17, a high-pressure refrigerant outlet 18, and a high-pressure refrigerant internal flow path 32. The evaporator body 12 has a low-pressure refrigerant flow path 20 through which a low-pressure refrigerant flows, and a heat medium flow path 25 through which a heat medium that exchanges heat with the low-pressure refrigerant flows. The high-pressure refrigerant inlet 17 is provided on a predetermined outer wall surface of the evaporator body 12 (specifically, the outer wall surface facing the condenser 3), and is a portion into which the high-pressure refrigerant condensed in the condenser 3 flows. The high-pressure refrigerant outlet 18 is provided on an outer wall surface of the evaporator body 12 opposite to the predetermined outer wall surface (specifically, the outer wall surface facing the pressure reducer 6), and is a portion from which the high-pressure refrigerant flows out. The high-pressure refrigerant internal flow path 32 is a flow path through which the high-pressure refrigerant flows inside the evaporator body 12 from the high-pressure refrigerant inlet 17 to the high-pressure refrigerant outlet 18. According to this, when a combined heat exchanger 11 is configured in which the condenser 3 and the pressure reducer 6 are integrated with the evaporator 7, the configuration in which high-pressure refrigerant passes through the inside of the evaporator 7 makes it possible to arrange the pressure reducer 6 on the opposite side of the evaporator 7 from the condenser 3. Therefore, compared to a configuration in which the pressure reducer 6 is arranged between the evaporator 7 and the condenser 3, it is easier to route the piping connected to the pressure reducer 6. Therefore, this configuration of the evaporator 7 allows the size of the combined heat exchanger 11 to be reduced.

[0067] (2) The evaporator 7 of the first embodiment has a low-pressure refrigerant inlet 13. The low-pressure refrigerant inlet 13 is provided on the outer wall surface of the evaporator body 12 on the side where the high-pressure refrigerant outlet 18 is provided, and is a portion where the low-pressure refrigerant flows into the low-pressure refrigerant flow path 20. The low-pressure refrigerant inlet 13 and the high-pressure refrigerant outlet 18 are both connected to the pressure reducer 6. The high-pressure refrigerant flowing out from the high-pressure refrigerant outlet 18 of the evaporator 7 is reduced in pressure by the pressure reducer 6 to become low-pressure refrigerant, and then flows into the low-pressure refrigerant flow path 20 from the low-pressure refrigerant inlet 13 of the evaporator 7. This makes it possible to directly connect the low-pressure refrigerant inlet 13 and the high-pressure refrigerant outlet 18 of the evaporator 7 to the pressure reducer 6. This allows the size of the combined heat exchanger 11, which integrates the evaporator 7, the condenser 3, and the pressure reducer 6, to be reduced. As described above, in this disclosure, direct connection refers to connection without any substantial or practical flow path component, and also includes connection via a washer or the like that is not a substantial or practical flow path component.

[0068] (3) In the first embodiment, the condenser 3 includes a condenser body 40 and a condenser-side high-pressure refrigerant outlet 45. The condenser body 40 has a condenser-side high-pressure refrigerant flow path 43 through which a high-pressure refrigerant flows, and a high-temperature side heat medium flow path 50 through which a high-temperature side heat medium flows that exchanges heat with the high-pressure refrigerant. The condenser-side high-pressure refrigerant outlet 45 is provided on the outer wall surface of the condenser body 40 and is a portion through which the high-pressure refrigerant flows out of the condenser body 40. The condenser-side high-pressure refrigerant outlet 45 provided in the condenser body 40 and the high-pressure refrigerant inlet 17 provided in the evaporator body 12 are directly connected at only one point. Incidentally, strict positioning tolerances are required when circulating high-pressure refrigerant between the evaporator 7 and the condenser 3. In contrast, in this embodiment, the condenser-side high-pressure refrigerant outlet 45 of the condenser body 40 and the high-pressure refrigerant inlet 17 of the evaporator body 12 are directly connected at only one location, which relaxes the tolerance requirements when constructing the combined heat exchanger 11 in which the evaporator 7 and the condenser 3 are integrated.

[0069] (4) The evaporator 7 of the first embodiment has at least one of a high-pressure refrigerant outlet-side wall flow path 31 and a low-pressure refrigerant inlet-side wall flow path 24 on the outer wall surface of the evaporator body 12 on the side where the high-pressure refrigerant outlet 18 is provided. The high-pressure refrigerant outlet-side wall flow path 31 is a flow path that connects the high-pressure refrigerant internal flow path 32 and the high-pressure refrigerant outlet 18. The low-pressure refrigerant inlet-side wall flow path 24 is a flow path that connects the low-pressure refrigerant inlet 13 and the low-pressure refrigerant flow path 20. According to this, by providing at least one of a high-pressure refrigerant outlet side wall surface flow path 31 and a low-pressure refrigerant inlet side wall surface flow path 24 on the outer wall surface of the evaporator body 12 on the side where the high-pressure refrigerant outlet portion 18 is provided, the evaporator 7 and the pressure reducer 6 can be connected compactly.

[0070] (5) The low-pressure refrigerant flow path 20 provided in the evaporator body 12 of the first embodiment has a low-pressure refrigerant inlet-side tank 21, a plurality of low-pressure refrigerant flow path layers 22, and a low-pressure refrigerant outlet-side tank 23. The low-pressure refrigerant inlet-side tank 21 is a flow path into which low-pressure refrigerant flows from the low-pressure refrigerant inlet portion 13. The plurality of low-pressure refrigerant flow path layers 22 are flow paths through which low-pressure refrigerant diverted from the low-pressure refrigerant inlet-side tank 21 flows. The low-pressure refrigerant outlet-side tank 23 is a flow path through which low-pressure refrigerant that has flowed through the plurality of low-pressure refrigerant flow path layers 22 gathers and flows to the low-pressure refrigerant outlet portion 14. The heat medium flow path 25 provided in the evaporator body 12 has a heat medium inlet-side tank 26, a plurality of heat medium flow path layers 27, and a heat medium outlet-side tank 28. The heat medium inlet-side tank 26 is a flow path into which the heat medium flows from the heat medium inlet portion 15. The heat medium channel layers 27 are channels through which the heat medium diverted from the heat medium inlet tank 26 flows. The heat medium outlet tank 28 is a channel through which the heat medium that has flowed through the heat medium channel layers 27 is collected and flows to the heat medium outlet section 16. The evaporator body 12 is a stacked heat exchanger in which the low-pressure refrigerant channel layers 22 and the heat medium channel layers 27 are alternately stacked in a predetermined stacking direction, and is configured so that heat exchange between the high-pressure refrigerant and the heat medium is suppressed compared to internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant. According to this, by performing internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant flowing through the evaporator 7, the degree of supercooling of the high-pressure refrigerant can be increased, and the cooling capacity of the heat medium by the evaporator 7 can be improved.

[0071] (6) The high-pressure refrigerant internal flow path 32 provided in the evaporator body 12 of the first embodiment is disposed between the low-pressure refrigerant outlet-side tank 23 and the heat medium inlet-side tank 26. The distance D1 between the high-pressure refrigerant internal flow path 32 and the low-pressure refrigerant outlet-side tank 23 is shorter than the distance D2 between the high-pressure refrigerant internal flow path 32 and the heat medium inlet-side tank 26. According to this, by bringing the high-pressure refrigerant internal flow path 32 closer to the low-pressure refrigerant outlet side tank 23 than the heat medium inlet side tank 26, internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant flowing through the evaporator 7 can be promoted, and heat exchange between the high-pressure refrigerant and the heat medium can be suppressed. Regarding the relationship D1 < D2 of the above distances, it means that D1 is, for example, 10% or more smaller than D2, and excludes configurations such as when D1 and D2 are substantially the same and D1 is slightly smaller than D2 due to manufacturing tolerances or the like.

[0072] (7) The periphery of the high-pressure refrigerant internal flow path 32 provided in the evaporator body 12 of the first embodiment is surrounded by a plurality of low-pressure refrigerant flow path layers 22. According to this, heat exchange between the high-pressure refrigerant and the low-pressure refrigerant flowing through the evaporator 7 can be performed, and heat exchange between the high-pressure refrigerant flowing through the evaporator 7 and the heat medium can be suppressed. In the present disclosure, the periphery of the high-pressure refrigerant internal flow path 32 being surrounded does not limit to a configuration where all of the periphery of the high-pressure refrigerant internal flow path 32 is surrounded, and also includes a configuration where there is a region not surrounded by the plurality of low-pressure refrigerant flow path layers 22 in a part of the periphery of the high-pressure refrigerant internal flow path 32.

[0073] (8) The evaporator 7 of the first embodiment is a laminated heat exchanger configured such that the flow of the low-pressure refrigerant in the plurality of low-pressure refrigerant flow path layers 22 and the flow of the heat medium in the plurality of heat medium flow path layers 27 are counterflows. According to this, in the evaporator 7, the heat exchange efficiency between the low-pressure refrigerant and the heat medium can be improved. Also, when configuring the composite heat exchanger 11 in which the condenser 3 and the evaporator 7 are integrated, it is possible to arrange the heat medium inlet side tank 26 and the high-pressure refrigerant internal flow path 32 relatively close to each other, and arrange the heat medium outlet side tank 28 and the high-pressure refrigerant internal flow path 32 relatively far from each other. Thus, even when the high-pressure refrigerant flowing through the high-pressure refrigerant internal flow path 32 and the heat medium flowing through the heat medium inlet side tank 26 exchange heat, since the heat medium is cooled when flowing through the plurality of heat medium flow path layers 27, a decrease in the cooling ability of the heat medium by the evaporator 7 can be suppressed.

[0074] (9) The evaporator 7 of the first embodiment includes at least one of a heat medium inlet-side wall flow passage 29 and a heat medium outlet-side wall flow passage 30 on the outer wall surface of the evaporator body 12 on the side where the high-pressure refrigerant inlet 17 is provided. The heat medium inlet-side wall flow passage 29 is a flow passage that connects the heat medium inlet 15 and the heat medium flow passage 25. The heat medium outlet-side wall flow passage 30 is a flow passage that connects the heat medium flow passage 25 and the heat medium outlet 16. The condenser 3 also includes at least one of a high-temperature-side heat medium inlet-side wall flow passage 52 and a high-temperature-side heat medium outlet-side wall flow passage on the outer wall surface of the condenser body 40 on the side where the condenser-side high-pressure refrigerant outlet 45 is provided. The high-temperature-side heat medium inlet-side wall flow passage 52 is a flow passage that connects the high-temperature-side heat medium inlet 51 and the high-temperature-side heat medium flow passage 50. Although not shown, the high-temperature-side heat medium outlet-side wall flow passage is a flow passage that connects the high-temperature-side heat medium flow passage 50 and the high-temperature-side heat medium outlet 53. According to this, by forming wall surface flow paths on the outer wall surface of the condenser body 40 or the outer wall surface of the evaporator body 12, the high-temperature side heat medium inlet 51, the high-temperature side heat medium outlet 53, the heat medium inlet 15, and the heat medium outlet 16 can be arranged to avoid the connection point between the condenser-side high-pressure refrigerant outlet 45 and the high-pressure refrigerant inlet 17. Therefore, the condenser 3 and the evaporator 7 can be integrated into a compact structure.

[0075] (10) In the evaporator 7 of the first embodiment, the evaporator body 12 has a high-pressure refrigerant inlet 17 on one outer wall surface in the stacking direction, and a high-pressure refrigerant outlet 18 on the other outer wall surface in the stacking direction. The evaporator body 12 has a low-pressure refrigerant flow path layer 22 as the outermost layer on at least one of the two outer wall surfaces in the stacking direction. According to this, by making the low-pressure refrigerant flow path layer 22 the endmost layer on at least one side of the stacking direction, where heat exchange occurs between the high-pressure refrigerant inlet portion 17 and the high-pressure refrigerant outlet portion 18 and the evaporator body 12, it is possible to suppress heat exchange between the high-pressure refrigerant and the heat medium.

[0076] (11) As a modification of the first embodiment, at least one of the outermost layers on one side and the other side in the stacking direction of the evaporator body 12 may be a heat insulating space layer. According to this, by making at least one of the endmost layers on one side and the other side in the stacking direction, where heat exchange occurs between the high-pressure refrigerant inlet portion 17 and the high-pressure refrigerant outlet portion 18 and the evaporator body 12, an insulating space layer, heat exchange between the high-pressure refrigerant and the heat medium can be suppressed.

[0077] (12) In the first embodiment, the high-pressure refrigerant outlet 18 of the evaporator 7 is connected to the pressure reducer-side high-pressure refrigerant inlet 60 of the pressure reducer 6. Also, the low-pressure refrigerant inlet 13 of the evaporator 7 is connected to the pressure reducer-side low-pressure refrigerant outlet 61 of the pressure reducer 6. On the outer wall surface of the evaporator body 12, the high-pressure refrigerant outlet 18 and the low-pressure refrigerant inlet 13 are positioned toward the center of the evaporator body 12 relative to the low-pressure refrigerant outlet 14. This makes it easier to connect the pressure reducer-side high-pressure refrigerant inlet 60 and the pressure reducer-side low-pressure refrigerant outlet 61 of the pressure reducer 6 to the high-pressure refrigerant outlet 18 and the low-pressure refrigerant inlet 13 of the evaporator 7. At the same time, it becomes possible to arrange the downstream refrigerant piping connected to the low-pressure refrigerant outlet 14 of the evaporator 7 so as to avoid the pressure reducer 6.

[0078] (13) Furthermore, the pressure reducer 6 described in the first embodiment has the following advantages. The pressure reducer 6 includes a pressure reducer main body 62, a pressure reducer-side high-pressure refrigerant inlet 60, a pressure reducer-side high-pressure refrigerant outlet 64, a pressure reducer-side high-pressure refrigerant internal flow path 65, a branching section 66, a pressure reduction section 63, and a pressure reducer-side low-pressure refrigerant outlet 61. The pressure reducer-side high-pressure refrigerant inlet 60 is provided on the outer wall surface of the pressure reducer main body 62, and is a section into which high-pressure refrigerant that has been condensed in the condenser 3 and passed directly through the evaporator 7 flows. The pressure reducer-side high-pressure refrigerant internal flow path 65 is a flow path through which high-pressure refrigerant flows inside the pressure reducer main body 62 from the pressure reducer-side high-pressure refrigerant inlet 60 to the pressure reducer-side high-pressure refrigerant outlet 64. The pressure reducer-side high-pressure refrigerant outlet 64 is provided on the outer wall surface of the pressure reducer main body 62, and is a section from which the high-pressure refrigerant that has passed directly through the pressure reducer 6 flows out. The branching section 66 is provided midway through the pressure reducer-side high-pressure refrigerant internal flow path 65, and is a section where the flow of high-pressure refrigerant branches. The pressure reducing section 63 is a section that reduces the pressure of the high-pressure refrigerant in one flow branched at the branching section 66. The pressure reducing device side low-pressure refrigerant outlet section 61 is a section from which the low-pressure refrigerant reduced in pressure reducing section 63 flows out. According to this, when a combined heat exchanger 11 is configured in which the condenser 3, the evaporator 7, and the pressure reducer 6 are integrated, the high-pressure refrigerant passes through the inside of the pressure reducer body 62, which facilitates the routing of the refrigerant piping connected to the pressure reducer. Therefore, this configuration of the pressure reducer 6 makes it easy to connect the pressure reducer 6 and the evaporator 7, and further makes it easy to configure a refrigeration cycle apparatus 1 including a second pressure reducer 71, a second evaporator 72, etc., which will be described in a second embodiment later.

[0079] (Second embodiment) The second embodiment will be described. The second embodiment is different from the first embodiment in the configuration of the refrigeration cycle device 1, and is otherwise similar to the first embodiment, so only the parts that are different from the first embodiment will be described.

[0080] In the explanations of the second embodiment and onwards, the "evaporator 7", "pressure reducer 6" and "branch section 66" described in the first embodiment above will be referred to as the "first evaporator 7", "first pressure reducer 6" and "first branch section 66", respectively.

[0081] As shown in FIG. 15, the refrigeration cycle device 1 of the second embodiment has, in addition to the configuration described in the first embodiment, an air-cooled radiator 70, a second pressure reducer 71, a second evaporator 72, a second branch section 73, and an internal heat exchanger 74.

[0082] 15, for convenience of drawing, the internal heat exchanger high-pressure flow path 75 and the internal heat exchanger low-pressure flow path 76 of the internal heat exchanger 74 are depicted at separate positions, but in reality, the internal heat exchanger high-pressure flow path 75 and the internal heat exchanger low-pressure flow path 76 are integrally configured. This is also true for FIGS. 18 to 20 which will be referred to in the description of the third to fifth embodiments described later.

[0083] The first branch section 66 is a flow path component that connects three pipes, with the first pipe being connected to the pressure reducer side high-pressure refrigerant outlet section 64, the second pipe being connected to the internal heat exchanger high-pressure flow path 75, and the third pipe being connected to the air-cooled radiator 70.

[0084] The second branch section 73 is also a flow path component that connects three pipes, with the first pipe being connected to the internal heat exchanger low-pressure flow path 76, the second pipe being connected to the second evaporator 72, and the third pipe being connected to the compressor 2.

[0085] In the refrigeration cycle apparatus 1, an internal heat exchanger high-pressure flow path 75, a pressure reduction section 63 of the first pressure reducer 6, a low-pressure refrigerant flow path 20 of the first evaporator 7, an internal heat exchanger low-pressure flow path 76, and a second branch section 73 are connected in this order to one downstream side of the first branch section 66. In the refrigeration cycle apparatus 1, an air-cooled radiator 70, a second pressure reducer 71, a second evaporator 72, and a second branch section 73 are connected in this order to the other downstream side of the first branch section 66.

[0086] Therefore, a portion of the refrigerant circulating through the refrigeration cycle apparatus 1 flows in the following order: compressor 2 → condenser 3 → liquid storage section 4 → supercooling section 5 → high-pressure refrigerant internal flow path 32 → pressure reducer side high-pressure refrigerant internal flow path 65 → first branch section 66 → internal heat exchanger high-pressure flow path 75 → first pressure reducer 6 → first evaporator 7 → internal heat exchanger low-pressure flow path 76 → second branch section 73 → compressor 2. Another portion of the refrigerant circulating through the refrigeration cycle apparatus 1 flows in the following order: compressor 2 → condenser 3 → liquid storage section 4 → supercooling section 5 → high-pressure refrigerant internal flow path 32 → pressure reducer side high-pressure refrigerant internal flow path 65 → first branch section 66 → air-cooled radiator 70 → second pressure reducer 71 → second evaporator 72 → second branch section 73 → compressor 2. In this refrigerant flow order, the high-pressure refrigerant flowing from the subcooling section 5 to the first branch section 66 passes through the high-pressure refrigerant internal flow path 32 provided in the first evaporator 7 and the pressure reducer-side high-pressure refrigerant internal flow path 65 provided in the first pressure reducer 6, as in the first embodiment.

[0087] The internal heat exchanger 74 is disposed on the opposite side of the evaporator 7 with respect to the first pressure reducer 6. Specifically, the internal heat exchanger high-pressure flow path 75 is provided midway through the piping connecting the first branch portion 66 and the pressure reduction portion 63 of the first pressure reducer 6. The internal heat exchanger low-pressure flow path 76 is provided midway through the piping connecting the low-pressure refrigerant outlet portion 14 of the evaporator 7 and the second branch portion 73. As a result, the internal heat exchanger 74 exchanges heat between the high-pressure refrigerant that has flowed out from the pressure reducer-side high-pressure refrigerant internal flow path 65 and before being reduced in pressure by the pressure reduction portion 63 of the first pressure reducer 6, and the low-pressure refrigerant that has flowed out from the first evaporator 7 and before being drawn into the compressor 2. As a result, the degree of subcooling of the high-pressure refrigerant before being reduced in pressure by the first pressure reducer 6 is increased, and the cooling capacity of the heat medium by the first evaporator 7 can be improved.

[0088] The air-cooled radiator 70 is a subcooler that exchanges heat between a high-pressure refrigerant (specifically, a high-pressure liquid refrigerant) and outside air. The high-pressure refrigerant passing through the air-cooled radiator 70 dissipates heat to the outside air, thereby increasing the degree of subcooling. The high-pressure refrigerant that has passed through the air-cooled radiator 70 is reduced in pressure by the second pressure reducer 71 to become a low-pressure refrigerant in a gas-liquid two-phase state, and flows into the second evaporator 72. The second evaporator 72 is, for example, an air conditioning evaporator that cools the vehicle interior. The low-pressure refrigerant passing through the second evaporator 72 absorbs heat from the air supplied to the vehicle interior and evaporates, cooling the air. Therefore, by disposing the air-cooled radiator 70 between the first branch section 66 and the second pressure reducer 71, the vehicle interior cooling capacity of the second evaporator 72 can be improved.

[0089] 16 , a lubricant oil inflow prevention flow path 33 is provided on the outer wall surface of the evaporator body 12 of the first evaporator 7 on the side where the low-pressure refrigerant outlet 14 is provided. The lubricant oil inflow prevention flow path 33 is a flow path that connects the low-pressure refrigerant flow path 20 inside the evaporator body 12 with the low-pressure refrigerant outlet 14. The lubricant oil inflow prevention flow path 33 has a portion that extends vertically upward on the outer wall surface of the evaporator body 12 with respect to the piping downstream of the low-pressure refrigerant outlet 14. This prevents lubricant oil mixed with the refrigerant from flowing from the piping downstream of the second evaporator 72 to the first evaporator 7 side via the second branch 73 when the refrigeration cycle apparatus 1 operates such that refrigerant is circulated through the second evaporator 72 but not through the first evaporator 7.

[0090] 17, the lubricant oil inflow prevention flow path 33 may be provided inside a block 34 provided on the outer wall surface of the evaporator body 12 of the first evaporator 7. This configuration also makes it possible to prevent lubricant oil from flowing from the piping downstream of the second evaporator 72 through the second branch part 73 into the first evaporator 7.

[0091] The refrigeration cycle device 1 of the second embodiment described above has the following advantages. (1) The refrigeration cycle apparatus 1 of the second embodiment includes an air-cooled radiator 70 in the middle of the pipe connecting the pressure reducer-side high-pressure refrigerant outlet 64 and the second pressure reducer 71 . This allows the second evaporator 72 to improve its cooling capacity for the air supplied to the vehicle interior.

[0092] (2) The refrigeration cycle apparatus 1 of the second embodiment includes an internal heat exchanger 74 that exchanges heat between the high-pressure refrigerant that has passed through the first evaporator 7 and the first pressure reducer 6 and the low-pressure refrigerant that flows downstream of the first evaporator 7. The internal heat exchanger 74 is disposed on the opposite side of the first evaporator 7 with respect to the first pressure reducer 6. According to this, by disposing the internal heat exchanger 74 on the opposite side of the first evaporator 7 with respect to the first pressure reducer 6, the refrigeration cycle apparatus 1 can be configured compactly. In addition, the internal heat exchanger 74 can improve the performance of the refrigeration cycle apparatus 1.

[0093] (3) The first evaporator 7 included in the refrigeration cycle apparatus 1 of the second embodiment has a lubricant oil inflow prevention flow path 33 on the outer wall surface of the evaporator body 12 on the side where the low-pressure refrigerant outlet 14 is provided. The lubricant oil inflow prevention flow path 33 has a portion that extends vertically upward on the outer wall surface of the evaporator body 12 with respect to the piping downstream of the low-pressure refrigerant outlet 14. According to this, when the refrigeration cycle device 1 is operated in such a way that refrigerant is circulated through the second evaporator 72 but not through the first evaporator 7, it is possible to prevent lubricating oil from flowing from the piping downstream of the second evaporator 72 to the first evaporator 7 side via the second branch section 73.

[0094] (Third embodiment) The third embodiment will be described. The third embodiment is similar to the second embodiment except for the position of the first branch portion 66, and therefore only the differences from the second embodiment will be described.

[0095] 18 , in the refrigeration cycle apparatus 1 of the third embodiment, a first branch portion 66 is provided midway through a pipe connecting an air-cooled radiator 70 and a second pressure reducer 71. Specifically, the first branch portion 66 has a first pipe connected to the air-cooled radiator 70, a second pipe connected to the internal heat exchanger high-pressure flow path 75, and a third pipe connected to the second pressure reducer 71. As a result, in the refrigeration cycle apparatus 1 of the third embodiment, the air-cooled radiator 70 can improve the cooling capacity of the heat medium during operation in which the refrigerant is circulated through the first evaporator 7, and further, the air-cooled radiator 70 can improve the vehicle interior cooling capacity during operation in which the refrigerant is circulated through the second evaporator 72.

[0096] (Fourth embodiment) The fourth embodiment will be described. The fourth embodiment is different from the second embodiment in that the position of the internal heat exchanger 74 is changed and the air-cooled radiator 70 is eliminated, but the rest is the same as the second embodiment, so only the differences from the second embodiment will be described.

[0097] 19 , in the fourth embodiment, the internal heat exchanger high-pressure passage 75 is provided in the middle of the piping that connects the pressure reducer-side high-pressure refrigerant outlet 64 and the first branch portion 66. The internal heat exchanger low-pressure passage 76 is provided in the middle of the piping that connects the second branch portion 73 and the compressor 2. The configuration of the fourth embodiment also allows the refrigeration cycle apparatus 1 to be configured compactly, and the performance of the refrigeration cycle apparatus 1 can be improved.

[0098] (Fifth embodiment) The fifth embodiment will be described. The fifth embodiment is the same as the fourth embodiment except that the position of the internal heat exchanger 74 is changed, and therefore only the differences from the second embodiment will be described.

[0099] 20 , in the fifth embodiment, the internal heat exchanger high-pressure passage 75 is provided in the middle of the piping that connects the high-pressure refrigerant outlet 18 of the evaporator 7 and the pressure reducer-side high-pressure refrigerant inlet 60. The internal heat exchanger low-pressure passage 76 is provided in the middle of the piping that connects the second branch portion 73 and the compressor 2. The configuration of the fifth embodiment also allows the refrigeration cycle apparatus 1 to be configured compactly, and the performance of the refrigeration cycle apparatus 1 can be improved.

[0100] (Sixth embodiment) The sixth embodiment will be described. The sixth embodiment is the same as the second embodiment except that the position of the internal heat exchanger 74 is changed. Therefore, only the differences from the second embodiment will be described.

[0101] 21 , in the sixth embodiment, the internal heat exchanger high-pressure passage 75 is provided in the middle of the piping that connects the air-cooled radiator 70 and the second pressure reducer 71. The internal heat exchanger low-pressure passage 76 is provided in the middle of the piping that connects the second evaporator 72 and the second branch portion 73. The configuration of the sixth embodiment also allows the refrigeration cycle apparatus 1 to be configured compactly, and the performance of the refrigeration cycle apparatus 1 can be improved.

[0102] (Seventh embodiment) The seventh embodiment will be described. The seventh embodiment is the same as the sixth embodiment except that the position of the first branch portion 66 is changed, and therefore only the differences from the sixth embodiment will be described.

[0103] 22 , in the seventh embodiment, a first branch portion 66 is provided midway along a pipe connecting the air-cooled radiator 70 and the internal heat exchanger high-pressure passage 75. Specifically, the first branch portion 66 has a first pipe connected to the air-cooled radiator 70, a second pipe connected to the internal heat exchanger high-pressure passage 75, and a third pipe connected to the pressure reducing portion 63 of the first pressure reducing device 6. As a result, the refrigeration cycle device 1 of the seventh embodiment can improve the cooling capacity of the heat medium by the air-cooled radiator 70 in an operation in which the refrigerant is circulated through the first evaporator 7, and further can improve the vehicle interior cooling capacity by the air-cooled radiator 70 in an operation in which the refrigerant is circulated through the second evaporator 72.

[0104] (Eighth embodiment) An eighth embodiment will be described. The refrigeration cycle device 1 of the eighth embodiment is different from the fourth embodiment in that an economizer 77 is installed instead of the internal heat exchanger 74, and other aspects are the same as those of the fourth embodiment, so only the parts that are different from the fourth embodiment will be described.

[0105] 23, for convenience of drawing, the economizer high-pressure passage 78 and the economizer intermediate-pressure passage 79 of the economizer 77 are depicted at separate positions, but in reality, the economizer high-pressure passage 78 and the economizer intermediate-pressure passage 79 are integrally configured. This is also true in FIG. 24, which will be referred to in the description of the ninth embodiment, which will be described later.

[0106] As shown in FIG. 23 , in the eighth embodiment, the economizer 77 is disposed on the opposite side of the evaporator 7 with respect to the first pressure reducer 6. Specifically, the economizer high-pressure passage 78 is provided midway through the piping connecting the pressure reducer-side high-pressure refrigerant outlet 64 and the first branch 66. A third branch 80 is provided midway through the piping connecting the pressure reducer-side high-pressure refrigerant outlet 64 and the economizer high-pressure passage 78. A third pressure reducer 81 and an economizer intermediate-pressure passage 79 are provided in this order in the piping connected to the third branch 80. The third pressure reducer 81 reduces the pressure of the high-pressure refrigerant to a pressure intermediate between the low-pressure refrigerant and the high-pressure refrigerant circulating in the refrigeration cycle apparatus 1. The piping downstream of the economizer intermediate-pressure passage 79 is connected to the intermediate-pressure suction port of the compressor 2. The intermediate pressure suction port of the compressor 2 is a refrigerant suction port for supplying refrigerant to a compression space in the refrigerant compression mechanism of the compressor 2 where the low pressure refrigerant sucked in from the low pressure refrigerant suction port is being pressurized to high pressure refrigerant.

[0107] In the eighth embodiment described above, the refrigeration cycle apparatus 1 can also be configured compactly by arranging the economizer 77 on the opposite side of the first evaporator 7 with respect to the first pressure reducer 6. Furthermore, the economizer 77 can improve the performance of the refrigeration cycle apparatus 1.

[0108] (Ninth embodiment) A ninth embodiment will be described. The refrigeration cycle device 1 of the ninth embodiment is different from the eighth embodiment in that the positions of the economizer 77 and the third branch portion 80 are changed, and the rest is the same as the eighth embodiment, so only the parts that are different from the eighth embodiment will be described.

[0109] 24 , in the ninth embodiment, the economizer high-pressure flow path 78 is provided midway on the piping that connects the high-pressure refrigerant outlet 18 of the evaporator 7 and the pressure reducer-side high-pressure refrigerant inlet 60 of the first pressure reducer 6. A third branch section 80 is provided midway on the piping that connects the high-pressure refrigerant outlet 18 of the evaporator 7 and the economizer high-pressure flow path 78. Specifically, the third branch section 80 has one pipe connected to the high-pressure refrigerant outlet 18 of the evaporator 7, a second pipe connected to the economizer high-pressure flow path 78, and a third pipe connected to the third pressure reducer 81.

[0110] The refrigeration cycle device 1 of the ninth embodiment described above also achieves the same effects as those of the eighth embodiment.

[0111] (Other embodiments) (1) In each of the above embodiments, when the composite heat exchanger 11 is mounted on a vehicle, the stacking direction of the evaporator 7, etc. is set to a direction that intersects with the vertical direction. However, this is not limited to this, and the mounting state of the composite heat exchanger 11 on the vehicle can be set arbitrarily. In other words, the stacking direction of the evaporator 7, etc. can also be set arbitrarily with respect to the vertical direction.

[0112] (2) In the above embodiments, the evaporator 7 and the like are described as stacked heat exchangers, but the evaporator 7 and the like are not limited to this, and various types of heat exchangers can be used.

[0113] (3) In the above embodiments, the refrigeration cycle device 1 has been described as including a receiver as the liquid storage section 4 and a supercooling section 5, but this is not limiting, and the receiver and the supercooling section 5 may be omitted.

[0114] The present disclosure is not limited to the above-described embodiments and can be modified as appropriate within the scope of the claims. Furthermore, the above-described embodiments and portions thereof are not unrelated to each other and can be combined as appropriate unless the combination is clearly impossible. It goes without saying that, in each of the above embodiments, the elements constituting the embodiments are not necessarily essential unless specifically stated as essential or clearly considered essential in principle. Furthermore, in each of the above embodiments, when numerical values ​​such as the number, values, amounts, and ranges of components of the embodiments are mentioned, they are not limited to the specific numbers unless specifically stated as essential or clearly limited to a specific number in principle. Furthermore, in each of the above embodiments, when the shape, positional relationship, etc. of components are mentioned, they are not limited to the shape, positional relationship, etc., unless specifically stated or limited to a specific shape, positional relationship, etc. in principle.

[0115] The control unit and the method described herein may be implemented by a special-purpose computer configured by configuring a processor and memory programmed to perform one or more functions embodied in a computer program. Alternatively, the control unit and the method described herein may be implemented by a special-purpose computer configured by configuring a processor with one or more dedicated hardware logic circuits. Alternatively, the control unit and the method described herein may be implemented by one or more special-purpose computers configured by combining a processor and memory programmed to perform one or more functions with a processor configured with one or more hardware logic circuits. Furthermore, the computer program may be stored as instructions executed by a computer on a computer-readable non-transitory tangible storage medium. The memory is a non-transitory tangible storage medium.

[0116] (Aspects of the present disclosure) The present disclosure described above can be understood from the following viewpoints, for example. [First viewpoint] A heat exchanger used in a refrigeration cycle device (1) performs heat exchange between a high-pressure refrigerant pressurized by a compressor (2), condensed by a condenser (3), and then reduced in pressure by a pressure reducer (6) and a heat medium, thereby evaporating the low-pressure refrigerant and cooling the heat medium, an evaporator body (12) having a low-pressure refrigerant flow path (20) through which a low-pressure refrigerant flows, and a heat medium flow path (25) through which a heat medium flows that exchanges heat with the low-pressure refrigerant flowing through the low-pressure refrigerant flow path; a high-pressure refrigerant inlet (17) provided on a predetermined outer wall surface of the evaporator body, into which the high-pressure refrigerant condensed in the condenser flows; a high-pressure refrigerant outlet (18) provided on an outer wall surface of the evaporator body opposite to the predetermined outer wall surface, through which high-pressure refrigerant flows out; a high-pressure refrigerant internal flow path (32) through which high-pressure refrigerant flows inside the evaporator body from the high-pressure refrigerant inlet port to the high-pressure refrigerant outlet port. [Second viewpoint] a low-pressure refrigerant inlet (13) provided on an outer wall surface of the evaporator body on the side where the high-pressure refrigerant outlet is provided, through which the low-pressure refrigerant flows into the low-pressure refrigerant flow path; the low-pressure refrigerant inlet and the high-pressure refrigerant outlet are both connected to the pressure reducer, The heat exchanger according to a first aspect, wherein the high-pressure refrigerant flowing out from the high-pressure refrigerant outlet port is decompressed by the pressure reducer to become a low-pressure refrigerant, and flows into the low-pressure refrigerant flow path from the low-pressure refrigerant inlet port. [Third Perspective] The condenser is a condenser body (40) having a condenser-side high-pressure refrigerant flow path (43) through which a high-pressure refrigerant flows, and a high-temperature side heat medium flow path (50) through which a high-temperature side heat medium flows, the high-temperature side heat medium exchanging heat with the high-pressure refrigerant flowing through the condenser-side high-pressure refrigerant flow path; a condenser-side high-pressure refrigerant outlet (45) provided on an outer wall surface of the condenser body, through which high-pressure refrigerant flows out from the condenser body, The heat exchanger according to the first or second aspect, wherein the condenser-side high-pressure refrigerant outlet provided in the condenser body and the high-pressure refrigerant inlet provided in the evaporator body are directly connected at only one point. [Fourth viewpoint] a high-pressure refrigerant outlet-side wall surface flow path (31) communicating between the high-pressure refrigerant internal flow path and the high-pressure refrigerant outlet portion, and a low-pressure refrigerant inlet-side wall surface flow path (24) communicating between the low-pressure refrigerant inlet portion and the low-pressure refrigerant flow path, on an outer wall surface of the evaporator body on the side where the high-pressure refrigerant outlet portion is provided. [Fifth viewpoint] the low-pressure refrigerant flow path includes a low-pressure refrigerant inlet-side tank (21) into which low-pressure refrigerant flows from a low-pressure refrigerant inlet portion (13), a plurality of low-pressure refrigerant flow path layers (22) through which low-pressure refrigerant diverted from the low-pressure refrigerant inlet-side tank flows, and a low-pressure refrigerant outlet-side tank (23) through which the low-pressure refrigerant that has flowed through the plurality of low-pressure refrigerant flow path layers is collected and flows to a low-pressure refrigerant outlet portion (14), the heat medium flow path includes a heat medium inlet-side tank (26) into which the heat medium flows from a heat medium inlet portion (15), a plurality of heat medium flow path layers (27) through which the heat medium diverted from the heat medium inlet-side tank flows, and a heat medium outlet-side tank (28) through which the heat medium flowing through the plurality of heat medium flow path layers is collected and flows to a heat medium outlet portion, The heat exchanger according to any one of the first to fourth aspects, wherein the evaporator body is a stacked heat exchanger in which a plurality of the low-pressure refrigerant flow path layers and a plurality of the heat medium flow path layers are alternately stacked in a predetermined stacking direction, and is configured such that heat exchange between the high-pressure refrigerant and the heat medium is suppressed relative to internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant. [Sixth viewpoint] a heat exchanger according to a fifth aspect, wherein the high-pressure refrigerant internal flow path is disposed between the low-pressure refrigerant outlet-side tank and the heat medium inlet-side tank, and a distance (D1) between the high-pressure refrigerant internal flow path and the low-pressure refrigerant outlet-side tank is shorter than a distance (D2) between the high-pressure refrigerant internal flow path and the heat medium inlet-side tank. [Seventh viewpoint] The heat exchanger according to the fifth or sixth aspect, wherein the high-pressure refrigerant internal flow path is surrounded by a plurality of low-pressure refrigerant flow path layers. [Eighth viewpoint] The heat exchanger according to any one of the fifth to seventh aspects, wherein the flow of the low-pressure refrigerant in the plurality of low-pressure refrigerant channel layers and the flow of the heat medium in the plurality of heat medium channel layers are configured to be counter flows. [Ninth viewpoint] The condenser includes a condenser body (40) having a condenser-side high-pressure refrigerant flow path (43) through which a high-pressure refrigerant flows, and a high-temperature side heat medium flow path (50) through which a high-temperature side heat medium flows, the high-temperature side heat medium exchanging heat with the high-pressure refrigerant flowing through the condenser-side high-pressure refrigerant flow path; a condenser-side high-pressure refrigerant outlet (45) provided on an outer wall surface of the condenser body and through which high-pressure refrigerant flows out from the condenser body; a high-temperature side heat medium inlet (51) provided on an outer wall surface of the condenser body on a side where the condenser-side high-pressure refrigerant outlet is provided, and through which the high-temperature side heat medium flows into the high-temperature side heat medium flow path; a high-temperature side heat medium outlet (53) provided on an outer wall surface of the condenser body on a side where the condenser-side high-pressure refrigerant outlet is provided, and through which the high-temperature side heat medium flows out from the high-temperature side heat medium flow path, the condenser further comprises, on an outer wall surface of the condenser body on the side where the condenser-side high-pressure refrigerant outlet portion is provided, at least one of a high-temperature side heat medium inlet-side wall flow path (52) communicating the high-temperature side heat medium inlet portion with the high-temperature side heat medium flow path and a high-temperature side heat medium outlet-side wall flow path communicating the high-temperature side heat medium flow path with the high-temperature side heat medium outlet portion; The heat exchanger includes a heat medium inlet (15) provided on an outer wall surface of the evaporator body on the side where the high-pressure refrigerant inlet is provided, and through which the heat medium flows into the heat medium flow path; a heat medium outlet portion (16) provided on an outer wall surface of the evaporator body on a side where the high-pressure refrigerant inlet portion is provided, and through which the heat medium flows out from the heat medium flow path, The heat exchanger according to any one of the first to eighth aspects, further comprising at least one of a heat medium inlet-side wall surface flow path (29) communicating the heat medium inlet with the heat medium flow path, and a heat medium outlet-side wall surface flow path (30) communicating the heat medium flow path with the heat medium outlet, on an outer wall surface of the evaporator body on a side where the high-pressure refrigerant inlet is provided. [10th viewpoint] A pressure reducer used in a refrigeration cycle device (1) has a function of reducing the pressure of a high-pressure refrigerant pressurized by a compressor (2) after condensing it in a condenser (3), a pressure reducer body (62); a pressure reducer-side high-pressure refrigerant inlet (60) provided on an outer wall surface of the pressure reducer body, into which the high-pressure refrigerant condensed in the condenser flows; a pressure reducer-side high-pressure refrigerant outlet (64) provided on an outer wall surface of the pressure reducer body and through which high-pressure refrigerant flows out; a pressure reducer-side high-pressure refrigerant internal flow path (65) through which a high-pressure refrigerant flows inside the pressure reducer body from the pressure reducer-side high-pressure refrigerant inlet port to the pressure reducer-side high-pressure refrigerant outlet port; a branching portion (66) provided midway through the pressure reducer-side high-pressure refrigerant internal flow path, which branches the flow of high-pressure refrigerant; a pressure reducing section (63) that reduces the pressure of one of the high-pressure refrigerant flows branched off at the branch section; a pressure reducer-side low-pressure refrigerant outlet (61) through which the low-pressure refrigerant reduced in pressure by the pressure reducing section flows out. [Explanation of symbols]

[0117] 1 Refrigeration cycle device 2 Compressor 3. Condenser 6 Pressure Reducer 12 Evaporator body 17 High-pressure refrigerant inlet 18 High-pressure refrigerant outlet 20 Low-pressure refrigerant flow path 25 Heat transfer medium flow path 32 High-pressure refrigerant internal flow path

Claims

1. In a heat exchanger used in a refrigeration cycle device (1), which has the function of exchanging heat with a heat transfer medium and evaporating the low-pressure refrigerant, which is pressurized by a compressor (2), condensed in a condenser (3), and then depressurized in a pressure reducer (6), the low-pressure refrigerant, is used to cool the heat transfer medium, An evaporator body (12) having a low-pressure refrigerant channel (20) through which a low-pressure refrigerant flows, and a heat transfer medium channel (25) through which a heat transfer medium that exchanges heat with the low-pressure refrigerant flowing through the low-pressure refrigerant channel flows, The evaporator body includes a high-pressure refrigerant inlet (17) provided on a predetermined outer wall surface, through which the high-pressure refrigerant condensed in the condenser flows, The evaporator body is provided with a high-pressure refrigerant outlet (18) on the outer wall surface opposite to the predetermined outer wall surface, through which the high-pressure refrigerant flows out, The evaporator body includes a high-pressure refrigerant internal flow path (32) through which the high-pressure refrigerant flows from the high-pressure refrigerant inlet to the high-pressure refrigerant outlet, The aforementioned condenser is, A condenser body (40) having a condenser-side high-pressure refrigerant flow path (43) through which a high-pressure refrigerant flows, and a high-temperature side heat transfer medium flow path (50) through which a high-temperature side heat transfer medium that exchanges heat with the high-pressure refrigerant flowing in the condenser-side high-pressure refrigerant flow path flows, The condenser body is provided with a condenser-side high-pressure refrigerant outlet (45) on the outer wall surface of the condenser body through which high-pressure refrigerant flows out. A heat exchanger in which the condenser and the evaporator body are directly connected at only one location, where the high-pressure refrigerant outlet on the condenser side and the high-pressure refrigerant inlet are directly connected.

2. A heat exchanger used in a refrigeration cycle device (1), which has the function of exchanging heat between a heat medium and a low-pressure refrigerant that has been pressurized by a compressor (2), condensed in a condenser (3), and then depressurized in a pressure reducer (6), thereby evaporating the low-pressure refrigerant and cooling the heat medium, An evaporator body (12) having a low-pressure refrigerant channel (20) through which a low-pressure refrigerant flows, and a heat transfer medium channel (25) through which a heat transfer medium that exchanges heat with the low-pressure refrigerant flowing through the low-pressure refrigerant channel flows, The evaporator body includes a high-pressure refrigerant inlet (17) provided on a predetermined outer wall surface, through which the high-pressure refrigerant condensed in the condenser flows, The evaporator body is provided with a high-pressure refrigerant outlet (18) on the outer wall surface opposite to the predetermined outer wall surface, through which the high-pressure refrigerant flows out, From the high-pressure refrigerant inlet to the high-pressure refrigerant outlet, the high-pressure refrigerant flows through the inside of the evaporator body via an internal high-pressure refrigerant flow path (32), The evaporator body includes a low-pressure refrigerant inlet (13) provided on the outer wall surface on the side where the high-pressure refrigerant outlet is located, through which the low-pressure refrigerant flows into the low-pressure refrigerant flow path, Both the low-pressure refrigerant inlet and the high-pressure refrigerant outlet are connected to the pressure reducer. The high-pressure refrigerant that flows out from the high-pressure refrigerant outlet is reduced in pressure by the pressure reducer to become low-pressure refrigerant, and flows into the low-pressure refrigerant flow path from the low-pressure refrigerant inlet. A heat exchanger further comprising at least one of the following: a high-pressure refrigerant outlet side wall surface flow path (31) provided so as to extend along the outer wall surface of the evaporator body on the side where the high-pressure refrigerant outlet is provided, and communicating the internal high-pressure refrigerant flow path with the high-pressure refrigerant outlet; and a low-pressure refrigerant inlet side wall surface flow path (24) provided so as to extend along the outer wall surface of the evaporator body on the side where the high-pressure refrigerant outlet is provided, and communicating the low-pressure refrigerant inlet with the low-pressure refrigerant flow path.

3. A heat exchanger used in a refrigeration cycle device (1), which has the function of exchanging heat between a heat medium and a low-pressure refrigerant that has been pressurized by a compressor (2), condensed in a condenser (3), and then depressurized in a pressure reducer (6), thereby evaporating the low-pressure refrigerant and cooling the heat medium, An evaporator body (12) having a low-pressure refrigerant channel (20) through which a low-pressure refrigerant flows, and a heat transfer medium channel (25) through which a heat transfer medium that exchanges heat with the low-pressure refrigerant flowing through the low-pressure refrigerant channel flows, The evaporator body includes a high-pressure refrigerant inlet (17) provided on a predetermined outer wall surface, through which the high-pressure refrigerant condensed in the condenser flows, The evaporator body is provided with a high-pressure refrigerant outlet (18) on the outer wall surface opposite to the predetermined outer wall surface, through which the high-pressure refrigerant flows out, The evaporator body includes a high-pressure refrigerant internal flow path (32) through which the high-pressure refrigerant flows from the high-pressure refrigerant inlet to the high-pressure refrigerant outlet, The low-pressure refrigerant flow path includes a low-pressure refrigerant inlet tank (21) into which low-pressure refrigerant flows from a low-pressure refrigerant inlet (13), a plurality of low-pressure refrigerant flow path layers (22) through which low-pressure refrigerant diverted from the low-pressure refrigerant inlet tank flows, and a low-pressure refrigerant outlet tank (23) through which the low-pressure refrigerant that has flowed through the plurality of low-pressure refrigerant flow path layers collects and flows to a low-pressure refrigerant outlet (14). The heat transfer medium flow path includes a heat transfer medium inlet tank (26) into which the heat transfer medium flows from the heat transfer medium inlet (15), a plurality of heat transfer medium flow path layers (27) through which the heat transfer medium diverted from the heat transfer medium inlet tank flows, and a heat transfer medium outlet tank (28) into which the heat transfer medium that has flowed through the plurality of heat transfer medium flow path layers gathers and flows to the heat transfer medium outlet. The evaporator body is a laminated heat exchanger in which a plurality of low-pressure refrigerant flow channel layers and a plurality of heat transfer medium flow channel layers are alternately stacked in a predetermined stacking direction, and is configured such that heat exchange between the high-pressure refrigerant and the heat transfer medium is suppressed while internal heat exchange between the high-pressure refrigerant and the low-pressure refrigerant is performed. A heat exchanger in which the high-pressure refrigerant internal flow path is located between the low-pressure refrigerant outlet tank and the heat transfer medium inlet tank, and the distance (D1) between the high-pressure refrigerant internal flow path and the low-pressure refrigerant outlet tank is shorter than the distance (D2) between the high-pressure refrigerant internal flow path and the heat transfer medium inlet tank.

4. The heat exchanger according to claim 3, wherein the periphery of the high-pressure refrigerant internal flow path is surrounded by a plurality of low-pressure refrigerant flow path layers.

5. The heat exchanger according to claim 3, wherein the flow of low-pressure refrigerant in the plurality of low-pressure refrigerant flow channels and the flow of heat medium in the plurality of heat medium flow channels are configured to be in opposition to each other.

6. A heat exchanger used in a refrigeration cycle device (1), which has the function of exchanging heat between a heat medium and a low-pressure refrigerant that has been pressurized by a compressor (2), condensed in a condenser (3), and then depressurized in a pressure reducer (6), thereby evaporating the low-pressure refrigerant and cooling the heat medium, An evaporator body (12) having a low-pressure refrigerant channel (20) through which a low-pressure refrigerant flows, and a heat transfer medium channel (25) through which a heat transfer medium that exchanges heat with the low-pressure refrigerant flowing through the low-pressure refrigerant channel flows, The evaporator body includes a high-pressure refrigerant inlet (17) provided on a predetermined outer wall surface, through which the high-pressure refrigerant condensed in the condenser flows, The evaporator body is provided with a high-pressure refrigerant outlet (18) on the outer wall surface opposite to the predetermined outer wall surface, through which the high-pressure refrigerant flows out, The evaporator body includes a high-pressure refrigerant internal flow path (32) through which the high-pressure refrigerant flows from the high-pressure refrigerant inlet to the high-pressure refrigerant outlet, The condenser comprises a condenser body (40) having a condenser-side high-pressure refrigerant flow path (43) through which a high-pressure refrigerant flows, and a high-temperature side heat transfer medium flow path (50) through which a high-temperature side heat transfer medium that exchanges heat with the high-pressure refrigerant flowing in the condenser-side high-pressure refrigerant flow path flows. A condenser-side high-pressure refrigerant outlet (45) is provided on the outer wall surface of the condenser body through which high-pressure refrigerant flows out of the condenser body, The condenser body has an outer wall surface on the side where the condenser-side high-pressure refrigerant outlet is provided, and a high-temperature side heat transfer medium inlet (51) into which the high-temperature side heat transfer medium flows into the high-temperature side heat transfer medium flow path, The condenser body includes a high-temperature side heat transfer medium outlet (53) provided on the outer wall surface on the side where the condenser-side high-pressure refrigerant outlet is located, through which the high-temperature side heat transfer medium flows out from the high-temperature side heat transfer medium passage, Furthermore, the condenser includes at least one of the following: a high-temperature side heat transfer medium inlet side wall surface flow path (52) that extends along the outer wall surface of the condenser body on the side where the condenser-side high-pressure refrigerant outlet is provided and connects the high-temperature side heat transfer medium inlet with the high-temperature side heat transfer medium flow path; and a high-temperature side heat transfer medium outlet side wall surface flow path that extends along the outer wall surface of the condenser body on the side where the condenser-side high-pressure refrigerant outlet is provided and connects the high-temperature side heat transfer medium flow path with the high-temperature side heat transfer medium outlet. The heat exchanger is provided on the outer wall surface of the evaporator body on the side where the high-pressure refrigerant inlet is located, and has a heat medium inlet (15) into which the heat medium flows into the heat medium flow path, The evaporator body is provided with an outer wall surface on the side where the high-pressure refrigerant inlet is located, and includes a heat medium outlet (16) through which the heat medium flows out of the heat medium passage, Furthermore, the heat exchanger comprises at least one of the following: a heat medium inlet side wall channel (29) provided so as to extend along the outer wall surface of the evaporator body on the side where the high-pressure refrigerant inlet is provided, and communicating the heat medium inlet and the heat medium channel; and a heat medium outlet side wall channel (30) provided so as to extend along the outer wall surface of the evaporator body on the side where the high-pressure refrigerant inlet is provided, and communicating the heat medium channel and the heat medium outlet.

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