Plate heat exchanger with subcooling section and liquid reservoir and thermal management system

Abstract

A plate heat exchanger with a supercooling section and a liquid storage section can reduce the types of components, especially heat transfer plates, facilitate daily management and replacement of components, and reduce or even eliminate the introduction of a portion of the bypass components, reduce the pressure loss of refrigerant, and improve the efficiency of supercooling and heat exchange. The plate heat exchanger includes: a heat transfer plate group formed by overlapping a plurality of heat transfer plates, the heat transfer plate group having a condensation section and a supercooling section; a first end plate and a second end plate, the first end plate being provided with a first flow inlet, and the first end plate or the second end plate being provided with a first flow outlet; and a liquid storage section, the heat transfer plate including a condensation section heat transfer plate, a supercooling section heat transfer plate, and a partition heat transfer plate, the condensation section heat transfer plate having a first through hole communicating with the first flow inlet, at least a portion of the condensation section heat transfer plate, the partition heat transfer plate, and the supercooling section heat transfer plate having a flow channel hole, and the flow channel hole of the partition heat transfer plate and the supercooling section heat transfer plate using a double welding structure.

Description

Technical Field

[0001] This utility model relates to a thermal management system capable of indirect cooling, and more specifically, to a plate heat exchanger with a subcooling section and a liquid storage section (i.e., having both subcooling and liquid storage functions) and a thermal management system including the plate heat exchanger. Background Technology

[0002] A thermal management system 10' capable of indirect cooling is known, such as... Figure 11 As shown, the system includes a compressor 11', a first heat exchanger 12' serving as a condenser, a second heat exchanger 13' serving as an evaporator, and a throttling element 14' disposed between the first heat exchanger 12' and the second heat exchanger 13'. Low-temperature, low-pressure liquid refrigerant first absorbs heat from a high-temperature heat source and vaporizes into low-pressure vapor in the second heat exchanger 13', which serves as an evaporator. Then, the refrigerant gas is compressed into high-temperature, high-pressure vapor in the compressor 11'. This high-temperature, high-pressure vapor is cooled and condensed into high-pressure liquid by a low-temperature heat source in the first heat exchanger 12', which serves as a condenser. The liquid is then throttled by the throttling element 14' into low-temperature, low-pressure liquid refrigerant, thus forming a refrigeration cycle. Additionally, a liquid storage tank 15 is disposed between the first heat exchanger 12' and the second heat exchanger 13' to store the condensed high-pressure liquid refrigerant.

[0003] In addition, the cooling capacity of the entire thermal management system mainly depends on the amount of refrigerant charged. To increase the cooling capacity, one would generally think of charging more refrigerant, but this would make the thermal management system larger.

[0004] However, with the development of thermal management systems for electric vehicles, there is a growing demand to minimize the size of these systems while ensuring sufficient cooling capacity. Consequently, the integration requirements for the various components within the thermal management system are becoming increasingly stringent. Furthermore, new challenges have arisen regarding how to increase the cooling capacity of the thermal management system without requiring more refrigerant, thus enabling it to be larger in scale.

[0005] In addition, existing thermal management systems can be designed by dividing the heat transfer plates of a plate heat exchanger into a condensing section, a subcooling section, and a liquid storage section, thus integrating the subcooling and liquid storage sections with the traditional plate heat exchanger. However, to ensure that the liquid refrigerant flowing from the refrigerant inlet and through the condensing section flows directly into the liquid storage section without passing through the subcooling section, and to ensure that the refrigerant stored in the liquid storage section is subcooled through the subcooling section and flows directly out of the refrigerant outlet without merging with the liquid refrigerant flowing in the condensing section, components such as jumpers must be introduced. This not only increases the number of components and the difficulty of component management, but also may cause varying degrees of pressure loss in the refrigerant at multiple points due to the introduction of jumpers and other components. Utility Model Content

[0006] This utility model is made to solve the above-mentioned technical problems. Its purpose is to provide a plate heat exchanger with a subcooling section and a liquid storage section. By integrating the condensing section for condensing gaseous refrigerant, the liquid storage section for storing high-pressure liquid refrigerant, and the subcooling section for subcooling high-pressure liquid refrigerant, the integration of multiple components is improved.

[0007] In addition, another objective of this utility model is to provide a plate heat exchanger with a subcooling section and a liquid storage section, which can not only reduce the types of components, especially heat transfer plates, and facilitate the daily management and replacement of components, but also reduce or even eliminate the introduction of some components such as jumpers, reduce refrigerant pressure loss, and improve the efficiency of subcooling and heat exchange.

[0008] Furthermore, another objective of this utility model is to provide a thermal management system including the aforementioned plate heat exchanger, which can reduce the overall system volume, make the thermal management system more compact, occupy less space, and reduce the weight of refrigerant required in the system.

[0009] To achieve one or more of the above objectives, a first aspect of this utility model provides a plate heat exchanger with a subcooling section and a liquid storage section for heat exchange between a first fluid and a second fluid. The plate heat exchanger includes: a heat transfer plate assembly formed by overlapping multiple heat transfer plates along the length of the plate heat exchanger; the heat transfer plate assembly having a condensation section for condensing the gaseous first fluid into a liquid first fluid and a subcooling section for subcooling the liquid first fluid; a first end plate and a second end plate clamping the heat transfer plate assembly along the length; the first end plate having a first inlet for allowing the first fluid to flow into the heat transfer plate assembly relative to the heat transfer plate assembly, and either the first end plate or the second end plate having a first outlet for allowing the first fluid to flow out relative to the heat transfer plate assembly; and a liquid storage section integrated on one side of the second end plate and storing the liquid first fluid condensed by the condensation section of the heat transfer plate assembly. The multiple heat transfer plates include... The condensing section heat transfer plate, the subcooling section heat transfer plate, and the partition heat transfer plate located between the condensing section and the subcooling section are characterized in that the condensing section heat transfer plate has a first through hole on one side of the plate surface that communicates with the first inlet; at least a portion of the condensing section heat transfer plate, the partition heat transfer plate, and the subcooling section heat transfer plate have flow channel holes on the plate surface that communicate with the liquid storage inlet of the liquid storage section and are located on the same side or opposite side of the first through hole; the flow channel holes of the partition heat transfer plate and the subcooling section heat transfer plate use a double-welded structure; the first fluid flowing into the condensing section from the first inlet through the first through hole does not enter the first fluid flow path of the flow channel in each layer of the partition heat transfer plate and the subcooling section heat transfer plate, but flows into the liquid storage section from the liquid storage inlet through a pipe formed by the flow channel holes using the double-welded structure.

[0010] As described above, due to the use of a double-welded structure at the flow channel holes of the heat transfer plate separating the heat transfer plate and the subcooling section, the liquid refrigerant condensed in the condensing section can be guided to the liquid storage section through a pipe formed by the double-welded structure without entering the subcooling section. This reduces the number of components used in the plate heat exchanger. For example, the connecting pipe (jump pipe) between the condensing section and the liquid storage section in the heat transfer plate assembly of the plate heat exchanger can be omitted, as well as connecting flanges and sealing components such as gaskets or O-rings required for installing this connecting pipe. This facilitates routine management and replacement of components and reduces refrigerant pressure loss. For example, with a flow rate of 200 kg / h and a pressure of 2 MPa for saturated R134a refrigerant, the pressure loss can be reduced by approximately 1 kPa, and the effect is more pronounced at higher flow rates, thereby improving the efficiency of subcooling and heat exchange.

[0011] Preferably, the condensing section has multiple condensing sections that allow the first fluid to flow alternately in opposite directions, and a condensing section separating heat transfer plate is provided between the heat transfer plates constituting two adjacent condensing sections.

[0012] As an example, the condensing section has three condensing sections that allow the first fluid to flow alternately in opposite directions. A first condensing section separating heat transfer plate is provided between the heat transfer plate constituting the first-stage condensing section and the heat transfer plate constituting the second-stage condensing section. A second condensing section separating heat transfer plate is provided between the heat transfer plate constituting the second-stage condensing section and the heat transfer plate constituting the third-stage condensing section.

[0013] According to the configuration described above, compared with the case where the first fluid flows in the same direction in one condensation section, multi-stage condensation is performed by having the first fluid flow alternately in opposite directions in multiple condensation sections. This improves the condensation efficiency of the first fluid in the condensation section, and further enhances the efficiency of subcooling heat exchange by utilizing the high heat exchange characteristics of the plate heat exchanger. As a result, the volume of the entire thermal management system can be reduced, and the amount of refrigerant required can be reduced due to the improved subcooling and heat exchange efficiency.

[0014] In the foregoing examples, which are not limiting, the heat transfer plate for the first condensation section has a first through hole on one side of the plate surface that communicates with the first inlet. The heat transfer plate for the third condensation section has a first flow channel hole on the plate surface opposite to the first through hole that communicates with the liquid storage inlet of the liquid storage section. The first flow channel hole of the separating heat transfer plate and the subcooling section heat transfer plate uses a double-welded structure. The first fluid flowing from the first inlet through the first through hole into the condensation section and into the third-stage condensation section will not enter the first fluid flow path of the flow channel of each layer of the separating heat transfer plate and the subcooling section heat transfer plate. Instead, it flows into the liquid storage section from the liquid storage inlet through a pipe formed by the first flow channel hole with the double-welded structure.

[0015] As described above, similarly, the number of components used in the plate heat exchanger can be reduced. For example, the connecting pipes (jump pipes) between the condenser section and the liquid receiver section in the heat transfer plate assembly of the plate heat exchanger can be omitted, as well as connecting flanges and sealing gaskets or O-rings that must be used to install these connecting pipes. This facilitates routine management and replacement of components and reduces refrigerant pressure loss.

[0016] Preferably, the first inlet and the first outlet are respectively located on one side and the other side of the first end plate. The subcooling section heat transfer plate has a first through hole on one side of the heat transfer plate that communicates with the outlet of the liquid storage section. The condensing section heat transfer plate, the separating heat transfer plate, and the subcooling section heat transfer plate have a second through hole on the other side of the heat transfer plate that communicates with the first outlet and is not at the same vertical position as the flow channel hole. The second through holes of the separating heat transfer plate and the condensing section heat transfer plate use a double-welded structure. The first fluid stored in the liquid storage section and flowing into the subcooling section from the outlet of the liquid storage section through the first through hole will not enter the first fluid flow path of the flow channel of each layer of the separating heat transfer plate and the condensing section heat transfer plate. Instead, it flows out from the first outlet on the first end plate through a pipe formed by the second through hole with the double-welded structure.

[0017] As described above, due to the use of a double-welded structure at the second through-hole of a specific heat transfer plate, the refrigerant flowing out of the liquid reservoir and subcooled through the cold section is guided to the refrigerant piping through a pipe formed by the double-welded structure, without entering the condenser section. This reduces the number of components used in the plate heat exchanger; for example, it eliminates the need for connecting pipes (jump pipes) between the subcooled section and the first outlet, as well as connecting flanges and sealing components such as gaskets or O-rings required for installing these connecting pipes. This facilitates routine management and replacement of components and reduces refrigerant pressure loss.

[0018] In the foregoing examples, which are not limiting, it is preferred that the first inlet and the first outlet are respectively located on one side and the other side of the first end plate. The first condensation section heat transfer plate has a first fluid flow path in each layer that communicates with the first through hole of the first condensation section heat transfer plate, located on the side opposite to the first through hole on the plate surface of the heat transfer plate. The first condensation section separating heat transfer plate and the second condensation section heat transfer plate have the first flow path holes of the first condensation section heat transfer plate that communicate with the first flow path holes of the first condensation section heat transfer plate, located on the same side as the first through hole on the plate surface of the heat transfer plate but not at the same vertical position as the first through hole. The second flow channel hole of the second condensing section heat transfer plate, the second condensing section heat transfer plate having a first fluid flow path in each layer communicating with the second flow channel hole of the second condensing section heat transfer plate, the first flow channel hole located on the plate surface of the heat transfer plate opposite to the first through hole, the second condensing section separating heat transfer plate, the third condensing section heat transfer plate having a second flow channel hole communicating with the first flow channel hole of the second condensing section heat transfer plate, the second flow channel hole located on the plate surface of the heat transfer plate on the same side as the first through hole and not at the same perpendicular position as the first through hole, the first flow channel hole of the third condensing section heat transfer plate having a first fluid flow path in each layer communicating with the second flow channel hole of the third condensing section heat transfer plate. The second flow channel hole of the plate is connected. The subcooling section heat transfer plate has a first through hole on one side of the plate surface of the heat transfer plate, which is connected to the outlet of the liquid storage section. The first condensing section heat transfer plate, the first condensing section separating heat transfer plate, the second condensing section heat transfer plate, the second condensing section separating heat transfer plate, the third condensing section heat transfer plate, the separating heat transfer plate, and the subcooling section heat transfer plate have a second through hole on the other side of the plate surface of the heat transfer plate, which is connected to the first flow outlet and is not at the same vertical position as the first flow channel hole. The separating heat transfer plate, the third condensing section heat transfer plate, the second condensing section separating heat transfer plate, and the second subcooling section heat transfer plate have a second through hole on the other side of the plate surface of the heat transfer plate, which is connected to the first flow outlet and is not at the same vertical position as the first flow channel hole. The heat transfer plate for the condensing section, the heat transfer plate separating the first condensing section, and the heat transfer plate for the first condensing section use a double-welded structure at the second through hole. The first fluid stored in the liquid storage section and flowing into the subcooling section through the first through hole from the outlet of the liquid storage section will not enter the first fluid flow path of the flow channel of each layer of the heat transfer plate separating the first condensing section, the heat transfer plate for the third condensing section, the heat transfer plate separating the second condensing section, the heat transfer plate for the second condensing section, the heat transfer plate separating the first condensing section, and the heat transfer plate for the first condensing section. Instead, it flows out from the first outlet provided on the first end plate through a pipe formed by the second through hole with the double-welded structure.

[0019] According to the configuration described above, it is possible to improve the condensation and subcooling efficiency of the first fluid in the condensation section, while simplifying the daily management and replacement of components, and reducing refrigerant pressure loss.

[0020] The first inlet and first outlet of the plate heat exchanger of this utility model are not limited to being located on the same end plate, i.e., on one side and the other side of the first end plate. They can also be located at the same position on one side of the first end plate and the second end plate, or on one side of the first end plate and the other side of the second end plate. When they are located at the same position on one side of the first end plate and the second end plate, the heat transfer plate for the subcooling section has: a first through hole communicating with the first outlet and located on one side of the heat transfer plate; and a second through hole communicating with the outlet of the liquid storage section, located on the other side of the heat transfer plate and not at the same vertical position as the flow channel hole. When respectively disposed on one side of the first end plate and the other side of the second end plate, the heat transfer plate for the subcooling section has: a first through hole located on one side of the heat transfer plate and communicating with the outlet of the liquid storage section; and a second through hole located on the other side of the heat transfer plate and not at the same vertical position as the flow channel hole and communicating with the first flow outlet.

[0021] Furthermore, when the first flow inlet and the first flow outlet are located on different end plates, the first condensation section heat transfer plate, the first condensation section separating heat transfer plate, and the second condensation section heat transfer plate have a second through hole located on the other side of the plate surface of the heat transfer plate, which communicates with the first through hole of the first condensation section heat transfer plate in the first fluid flow path of the flow channel of each layer. The second condensation section heat transfer plate, the second condensation section separating heat transfer plate, and the third condensation section heat transfer plate have a first through hole located on one side of the plate surface of the heat transfer plate, which communicates with the second through hole of the second condensation section heat transfer plate in the first fluid flow path of the flow channel of each layer. Thus, the flow of the first fluid in the first fluid flow path of the flow channel of each layer can be realized when the condensation section has multiple (three) condensation sections.

[0022] In addition, in this invention, the first fluid is a refrigerant and the second fluid is a heat carrier.

[0023] In addition, a second aspect of this utility model provides a thermal management system, including a compressor, a first heat exchanger as a condenser, a second heat exchanger as an evaporator, and a throttling element disposed between the first heat exchanger and the second heat exchanger, characterized in that the thermal management system does not include a liquid storage section as a separate component, and the first heat exchanger is the plate heat exchanger with a subcooling section and a liquid storage section as described in the first aspect. Attached Figure Description

[0024] Figure 1This is a schematic perspective view of the overall structure (Embodiment 1) of a plate heat exchanger in which the first flow inlet and the first flow outlet are located on the same side end plate, that is, the so-called agent-side inlet and outlet are arranged in a 2-0 configuration.

[0025] Figure 2 and Figure 3 This is a schematic perspective view illustrating the overall structure (Embodiment 2 and Embodiment 3) of a plate heat exchanger 100 with the first flow inlet and first flow outlet located on different side plates, i.e., with the so-called agent-side inlet and outlet arranged in a 1-1 configuration. Figure 2 This is a schematic perspective view of implementation method 2, in which the first flow inlet and the first flow outlet are located at corresponding positions on different side end plates. Figure 3 This is a schematic perspective view of implementation method 3, in which the first flow inlet and the first flow outlet are located at non-corresponding positions on different side end plates.

[0026] Figure 4 This is a schematic side view of the heat transfer plate assembly of the plate heat exchanger of Embodiment 1, omitting the liquid storage section. (a) shows a case where the condensing section is a single condensing section in which the first fluid flows in the same direction, and (b) shows a case where the condensing section is multiple condensing sections (e.g., three condensing sections) in which the first fluid flows alternately in opposite directions.

[0027] Figure 5 This is a plan view showing the schematic structure of a basic configuration heat transfer plate as a basic configuration heat transfer plate used in the heat transfer plate assembly of the plate heat exchanger of various embodiments of the present invention.

[0028] Figure 6 The figure illustrates the flow of refrigerant at the flow channel holes of heat transfer plates using different welding structures at the flow channel holes, wherein (a) shows the flow of refrigerant at the flow channel holes of heat transfer plates using double welding structures, and (b) shows the flow of refrigerant at the flow channel holes of heat transfer plates using single welding structures.

[0029] Figure 7 This is a schematic diagram illustrating the flow of the first fluid (refrigerant) in the plate heat exchanger of Embodiment 1, wherein (a) the flow of the first fluid (refrigerant) in Embodiment 1A is illustrated as a single condensing section of the heat transfer plate assembly in which the first fluid flows in the same direction, and (b) the flow of the first fluid (refrigerant) in Embodiment 1B is illustrated as three condensing sections of the heat transfer plate assembly in which the first fluid flows alternately in opposite directions.

[0030] Figure 8This is a schematic diagram illustrating the flow of the first fluid (refrigerant) in the plate heat exchanger of Embodiment 2, wherein (a) the flow of the first fluid (refrigerant) in Embodiment 2A is illustrated as a single condensing section of the heat transfer plate assembly in which the first fluid flows in the same direction, and (b) the flow of the first fluid (refrigerant) in Embodiment 2B is illustrated as three condensing sections of the heat transfer plate assembly in which the first fluid flows alternately in opposite directions.

[0031] Figure 9 This is a schematic diagram illustrating the flow of the first fluid (refrigerant) in the plate heat exchanger 100 of Embodiment 3, wherein (a) the flow of the first fluid (refrigerant) is illustrated in Embodiment 3A, in which the condensing section of the heat transfer plate assembly is a single condensing section in which the first fluid flows in the same direction, and (b) the flow of the first fluid (refrigerant) is illustrated in Embodiment 3B, in which the condensing section of the heat transfer plate assembly is three condensing sections in which the first fluid flows alternately in opposite directions.

[0032] Figure 10 This is a schematic diagram showing the connection circuit of the thermal management system of this utility model.

[0033] Figure 11 This is a schematic diagram showing the connection loop of a thermal management system in the prior art. Detailed Implementation

[0034] Hereinafter, the plate heat exchanger 100 of various embodiments of the present invention will be described with reference to the accompanying drawings. In addition, in different embodiments, the same or equivalent parts and components are labeled with the same reference numerals, and detailed descriptions of them are omitted as appropriate, while detailed descriptions are given for different parts and components.

[0035] Figure 1 This is a schematic perspective view of the overall structure (Embodiment 1) of a plate heat exchanger 100 in which the first inlet 121 and the first outlet 122 are located on the same side end plate, that is, the so-called agent-side inlet and outlet are arranged in a 2-0 configuration. Figure 2 and Figure 3 This is a schematic perspective view illustrating the overall structure (Embodiment 2 and Embodiment 3) of a plate heat exchanger 100 with the first inlet 121 and the first outlet 122 located on different side plates, i.e., with the so-called agent-side inlet and outlet arranged 1-1. Figure 2 This is a schematic perspective view of Embodiment 2, in which the first flow inlet 121 and the first flow outlet 122 are located at corresponding positions on different side end plates. Figure 3 This is a schematic perspective view of embodiment 3, in which the first flow inlet 121 and the first flow outlet 122 are located at non-corresponding positions on different side end plates.

[0036] like Figures 1 to 3 As shown, the plate heat exchanger 100 of each embodiment of the present invention is similarly used for heat exchange, for example, water (second fluid) and refrigerant (heat carrier, first fluid). It includes a heat transfer plate assembly 110 formed by overlapping multiple heat transfer plates 111 in a predetermined direction (hereinafter referred to as the "plate stacking direction"), a pair of end plates 120A and 120B clamping the heat transfer plate assembly 110 in the plate stacking direction, and a liquid storage section 130 for storing the high-pressure liquid refrigerant condensed from the heat transfer plate assembly 110. In this invention, a refrigerant is used as the first fluid and water as the heat carrier (second fluid) as an example for description; however, the objects of heat exchange (first fluid and second fluid) in this invention are not limited to this, and any other suitable objects can be used.

[0037] (A pair of end plates 120A and 120B)

[0038] In various embodiments of this utility model, such as Figures 1 to 3 As shown, a pair of end plates 120A and 120B form a roughly rectangular plate shape when viewed from the plate stacking direction.

[0039] exist Figure 1In Embodiment 1 shown, the end plate 120A, one of the pair of end plates 120A and 120B located on one side of the plate stacking direction, i.e., the first end plate 120A, is provided with a first inlet 121, a first outlet 122, a second inlet 123, and a second outlet 124. Thus, the plate heat exchanger 100 of Embodiment 1 is a plate heat exchanger 100 with the first inlet 121 and the first outlet 122 located on the same side end plate, i.e., the so-called agent-side inlet and outlet are arranged in a 2-0 configuration. Additionally, although not illustrated, the plate heat exchanger 100 with a 2-0 arrangement of agent-side inlets and outlets can also be a plate heat exchanger 100 with a first inlet 121 and a first outlet 122 provided on one side of the pair of end plates 120A and 120B in the plate stacking direction (more specifically, on the side near the condensing section 110A), and a second inlet 123 and a second outlet 124 provided on the other side of the pair of end plates 120A and 120B in the plate stacking direction (more specifically, on the side near the subcooling section 110B). On the first end plate 120A or the second end plate 120B, the second inlet 123 and the second outlet 124 are respectively located at two adjacent corners of the four corners of the generally rectangular end plate. On the first end plate 120A, the first inlet 121 and the first outlet 122 are respectively located at two other adjacent corners of the four corners of the generally rectangular end plate, which are different from the corners where the second inlet 123 and the second outlet 124 are located. Furthermore, the first inlet 121 and the second inlet 123 are located at two corners of the generally rectangular end plate that are diagonally opposite each other. In addition, since the first inlet 121 and the first outlet 122, especially the first inlet 121, are preferably located near the condensation section 110A in the heat transfer plate assembly 110 ( Figure 4 Therefore, although the first end plate 120A is provided with a second inlet 123 and a second outlet 124 on the side of the plate stacking direction of the pair of end plates 120A and 120B (more specifically, on the side near the condensation section 110A), and on the other side of the pair of end plates 120A and 120B located in the plate stacking direction (more specifically, on the side near the subcooling section 110B), the second inlet 123 and the second outlet 124 are provided on the other side of the pair of end plates 120A and 120B located in the subcooling section 110B (more specifically, on the side near the subcooling section 110B) are provided with a second inlet 123 and a second outlet 124. Figure 4 The plate heat exchanger 100 with a first flow inlet 121 and a first flow outlet 122 on the end plate (i.e., the second end plate 120B) is also a plate heat exchanger 100 with a 2-0 arrangement of the agent-side inlet and outlet, but it is not an ideal arrangement of the agent-side inlet and outlet. Of course, this non-ideal arrangement can also be achieved by adding other complex piping structures, which are still within the protection scope of this utility model, but will not be specifically described in the following detailed description.

[0040] exist Figure 2 and Figure 3In Embodiments 2 and 3 shown, the plate heat exchanger 100 has a first inlet 121, a second inlet 123, and a second outlet 124 on one side of the pair of end plates 120A and 120B in the plate stacking direction (more specifically, on the side near the condensing section 110A), i.e., the first end plate 120A. And the plate heat exchanger 100 has a first outlet 122 on the other side of the pair of end plates 120A and 120B in the plate stacking direction (more specifically, on the side near the subcooling section 110B), i.e., the second end plate 120B. Thus, the plate heat exchanger 100 of Embodiments 2 and 3 is a plate heat exchanger 100 with the first inlet 121 and the first outlet 122 located on different side end plates, i.e., a so-called agent-side inlet and outlet arrangement of 1-1. Additionally, although not illustrated, the plate heat exchanger 100 with a 1-1 arrangement of agent-side inlets and outlets can also be a plate heat exchanger 100 with a first inlet 121 provided on one side of a pair of end plates 120A, 120B in the plate stacking direction (more specifically, on the side near the condensing section 110A) and a first outlet 122, a second inlet 123, and a second outlet 124 provided on the other side of a pair of end plates 120A, 120B in the plate stacking direction (more specifically, on the side near the subcooling section 110B).

[0041] More specifically, in Figure 2 In the illustrated embodiment 2, on the first end plate 120A or the second end plate 120B, the second inlet 123 and the second outlet 124 are respectively located at two adjacent corners of the four corners of the generally rectangular end plate. The first inlet 121 and the first outlet 122 are respectively located at a corresponding corner of the four corners of the generally rectangular first end plate 120A and the second end plate 120B that is different from the corners where the second inlet 123 and the second outlet 124 are located, i.e., at corresponding positions on different side end plates. Furthermore, the first inlet 121 and the second inlet 123 are located at two corners of the generally rectangular end plate that are diagonally opposite each other. Figure 3 In the embodiment 3 shown, the second inlet 123 and the second outlet 124 are respectively located at two adjacent corners of the four corners of the generally rectangular end plate 120A or the second end plate 120B. The first inlet 121 and the first outlet 122 are respectively located at two other adjacent corners of the four corners of the generally rectangular first end plate 120A and the second end plate 120B that are different from the corners where the second inlet 123 and the second outlet 124 are located, that is, at non-corresponding positions on different side end plates. The first inlet 121 and the second inlet 123 are located at two corners of the generally rectangular end plate that are located diagonally.

[0042] Similarly to Embodiment 1, since the first inlet 121 is preferably located on the side of the condensing section 110A in the heat transfer plate assembly 110, although the end plate 120A, which is located on the side of the plate stacking direction (more specifically, on the side of the condensing section 110A) of the pair of end plates 120A, 120B, is provided with a first outlet 122, or is provided with a first outlet 122, a second inlet 123 and a second outlet 124, and the end plate 120B, which is located on the other side of the plate stacking direction (more specifically, on the side of the subcooling section 110B) of the pair of end plates 120A, 120B, is provided with a first inlet 121, a second inlet 123 and a second outlet 124, or the plate heat exchanger 100 provided with the first inlet 121 is also a plate heat exchanger 100 with a 1-1 arrangement of the agent-side inlet and outlet, it is not an ideal arrangement configuration of the agent-side inlet and outlet. Of course, this non-ideal arrangement can also be achieved by adding other complex pipe structures, which are still within the scope of protection of this utility model, but will not be specifically mentioned in the detailed description below.

[0043] (Heat transfer plate assembly 110)

[0044] The following description uses the plate heat exchanger 100 of Embodiment 1 as an example to illustrate the configuration and structure of the heat transfer plate assembly 110 therein. Furthermore, those skilled in the art should understand that the configuration and structure of the heat transfer plate assembly 110 described below are not limited to the heat transfer plate assembly 110 of the plate heat exchanger 100 of Embodiment 1; the same or corresponding configuration and structure may also be present in the heat transfer plate assembly 110 of the plate heat exchanger 100 of Embodiments 2 and 3.

[0045] Figure 4 This is a schematic side view of the heat transfer plate assembly 110 of the plate heat exchanger 100 of Embodiment 1, omitting the liquid storage section 130. In this view, (a) shows a case where the condensing section is a single condensing section in which the first fluid flows in the same direction, and (b) shows a case where the condensing section is a plurality of condensing sections (e.g., three condensing sections) in which the first fluid flows alternately in opposite directions.

[0046] like Figure 4 As shown in (a) and (b), in the plate heat exchanger 100 of Embodiment 1 of this utility model, the heat transfer plate assembly 110 includes one ( Figure 4 (a) or more ( Figure 4(b) Condensing section 110A and subcooling section 110B. That is, the plurality of heat transfer plates 111 constituting the heat transfer plate assembly 110 include: a condensing section heat transfer plate 111A constituting the condensing section 110A; a subcooling section heat transfer plate 111B constituting the subcooling section 110B; and a separating heat transfer plate 111C located between the condensing section 110A and the subcooling section 110B. In a configuration having multiple condensing sections 110A (e.g., Figure 4 In the case of the primary condensing section 110A-1, secondary condensing section 110A-2, and tertiary condensing section 110A-3 shown in (b), an additional heat transfer plate (e.g., a partition plate) located between two adjacent condensing sections 110A is also included. Figure 4 (b) shows the first condensing section partition heat transfer plate 111A-1 and the second condensing section partition heat transfer plate 111A-2. Each heat transfer plate 111 of the heat transfer plate assembly 110 (condensing section heat transfer plate 111A, (other partition heat transfer plates, condensing section heat transfer plate 111A, ... condensing section heat transfer plate 111A, partition heat transfer plate 111C, subcooling section heat transfer plate 111B) and a pair of end plates 120A, 120B overlap with their respective outer peripheral edges and are joined by brazing or the like. Thus, refrigerant flow paths and water flow paths are formed between adjacent heat transfer plates 111. Furthermore, in the heat transfer plate assembly 110, with each heat transfer plate 111 overlapping, each heat transfer plate 111 is configured such that water and refrigerant alternately flow between adjacent heat transfer plates 111, that is, alternating water flow paths and refrigerant flow paths are formed, so that heat exchange occurs between the water in the water flow paths and the refrigerant in the refrigerant flow paths. Additionally, a heat transfer surface for heat exchange is formed on the surface of each heat transfer plate 111. The heat transfer plates 111 are manufactured, for example, by stamping a metal sheet such as stainless steel.

[0047] Figure 5 This is a plan view showing the schematic structure of the basic configuration heat transfer plate 111-1, which is a heat transfer plate assembly 110 used in the plate heat exchanger 100 of various embodiments of the present invention.

[0048] like Figure 5 As shown, in various embodiments of this utility model, each heat transfer plate 111 (heat transfer plate 111A for condensation section, heat transfer plate 111B for subcooling section, and heat transfer plate 111C for separation section) is formed into a generally rectangular plate shape when viewed from the stacking direction.

[0049] As the basic configuration of the heat transfer plate 111, the basic configuration heat transfer plate 111-1 has four through holes at the four corners of its generally rectangular shape, which are flow channels for refrigerant flow. Specifically, the first through hole 112 is connected to the first inlet 121, the second through hole 113 is connected to the first outlet 122, the third through hole 114 is connected to the second inlet 123, and the fourth through hole 115 is connected to the second outlet 124. The first through hole 112 and the second through hole 113 are connected to the refrigerant flow path, and the third through hole 114 and the fourth through hole 115 are connected to the water flow path. Furthermore, in both Embodiment 1 and Embodiments 2 and 3, the first inlet 121 and the second inlet 123 are located at two corners of a generally rectangular end plate located on the same side or on different sides, at the diagonal positions. Therefore, the first through hole 112 and the third through hole 114 are located at two corners of one diagonal position of the generally rectangular heat transfer plate 111, while the second through hole 113 and the fourth through hole 115 are located at two corners of the other diagonal position of the generally rectangular heat transfer plate 111.

[0050] Furthermore, as the basic configuration of the heat transfer plate 111, a first flow channel hole 116 for refrigerant to flow through is provided on the plate surface of the generally rectangular heat transfer plate 111 at a position between the second through hole 113 and the third through hole 114. In addition, a second flow channel hole 117 for refrigerant to flow through is provided on the plate surface of the generally rectangular heat transfer plate 111 at a position between the first through hole 112 and the fourth through hole 115.

[0051] The basic heat transfer plate 111-1 can be formed into heat transfer plates with different configurations by opening different flow channel holes for refrigerant to flow through (first through hole 112, second through hole 113, first flow channel hole 116, second flow channel hole 117), or by closing some of the opened flow channel holes for refrigerant to flow through (first through hole 112, second through hole 113, first flow channel hole 116, second flow channel hole 117).

[0052] Figure 6 The figure illustrates the flow of refrigerant at the flow channel holes of a heat transfer plate 111 with different welding structures at the flow channel holes, wherein (a) shows the flow of refrigerant at the flow channel holes of a heat transfer plate 111 with a double welding structure, and (b) shows the flow of refrigerant at the flow channel holes of a heat transfer plate 111 with a single welding structure.

[0053] Figure 6The single-welded structure shown in (b) can divert the refrigerant flowing through the heat transfer plate 111 of the plate heat exchanger 100, allowing the refrigerant in the refrigerant flow path of each layer to exchange heat with the water flowing through the water flow path formed by the welded part W1. Figure 6 The double-welded structure shown in (a) is compared to Figure 6 As shown in (b), in the single welded structure, since the refrigerant flow path is isolated from the water flow path formed by the welded part W1 through another welded part W2, the refrigerant no longer enters the refrigerant flow path of each layer, nor does it exchange heat with the water flowing in the water flow path. Instead, it forms a pipe to guide the refrigerant to other areas.

[0054] Furthermore, since both single-welded and double-welded stacking of heat transfer plates are well-known technologies, they will not be described in detail here.

[0055] The plate heat exchanger 100 will now be described in detail with reference to different embodiments. Although the different embodiments have been distinguished as Embodiment 1, Embodiment 2, and Embodiment 3 above, since the condensing section 110A can be a single condensing section in which the first fluid flows in the same direction, or multiple condensing sections in which the first fluid flows alternately in opposite directions, the embodiments 1, 2, and 3 will be further subdivided.

[0056] (Implementation Method 1)

[0057] The plate heat exchanger 100 in Embodiment 1 is a plate heat exchanger with a configuration in which the agent-side inlet and outlet are arranged at 2-0, wherein, Figure 7 (a) illustrates the flow of the first fluid (refrigerant) in an embodiment (Embodiment 1A) where the condensation section 110A of the heat transfer plate assembly 110 is a condensation section in which the first fluid flows in the same direction. Figure 7 (b) Lists the flow of the first fluid (refrigerant) in the embodiment (Embodiment 1B) of the condensation section 110A of the heat transfer plate assembly 110, which consists of three condensation sections in which the first fluid flows alternately in opposite directions. Table 1 below summarizes the configuration of each heat transfer plate, i.e., which heat transfer plates have the first through hole 112, the first through hole 113, the third through hole 114, the fourth through hole 115, the first flow channel hole 116, and the second flow channel hole 117. “○” indicates the presence of the hole, and “-” indicates the absence of the hole.

[0058] (Implementation Method 1A)

[0059] In the plate heat exchanger 100 of embodiment 1A, the condensing section 110A is Figure 4The case shown in (a) is a condensation section (i.e., condensation section 110A) in which the first fluid flows in the same direction.

[0060] At this time, the first inlet 121 provided on the first end plate 120A is connected to the first through hole 112 of the condensing section heat transfer plate 111A constituting the condensing section 110A, for introducing refrigerant from the refrigerant piping P1 into the refrigerant flow path of the condensing section 110A. The refrigerant in the condensing section 110A converges at the first flow channel hole 116 before flowing to the partition heat transfer plate 111C, and enters the liquid storage section 130 from the liquid storage section inlet through the first flow channel hole 116 of the partition heat transfer plate 111C and the subcooling section heat transfer plate 111B.

[0061] Thus, the refrigerant is temporarily stored in the liquid storage section 130. When the refrigerant needs to circulate in the thermal management system 10, the refrigerant stored in the liquid storage section 130 flows into the refrigerant flow path of the subcooling section 110B through the first through hole 112 via the liquid storage section outlet. The refrigerant in the subcooling section 110B converges at the second through hole 113 before flowing to the partition heat transfer plate 111C, and flows out to the refrigerant piping P1 through the second through hole 113 of the partition heat transfer plate 111C and the condensing section heat transfer plate 111A via the first outlet 122 provided on the first end plate 120A.

[0062] Thus, in the plate heat exchanger 100 of embodiment 1A, the heat transfer plate 111A for the condensing section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115, and a first flow channel hole 116; the heat transfer plate 111C for the partitioning section is a heat transfer plate with a configuration having a second through hole 113, a third through hole 114, a fourth through hole 115, and a first flow channel hole 116; and the heat transfer plate 111B for the subcooling section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115, and a first flow channel hole 116.

[0063] Furthermore, in Embodiment 1A, the direction in which the refrigerant flows along the heat transfer plate 111A in the condensing section 110A (for example, moving from the left side to the right side of the heat transfer plate 111) is the same as the direction in which the refrigerant flows along the heat transfer plate 111B in the subcooling section 110B (for example, moving from the left side to the right side of the heat transfer plate 111).

[0064] Furthermore, in embodiment 1A, the first flow channel hole 116 at the location separating the heat transfer plate 111C and the subcooling section heat transfer plate 111B is used Figure 6 The double-welded structure shown in (a) further includes a second through hole 113 at which the heat transfer plate 111C and the heat transfer plate 111A separating the heat transfer plate 111C and the condensation section are used. Figure 6The double-welded structure shown in (a) is used for the remaining flow channel holes. Figure 6 The single welded structure shown in (b).

[0065] Because a double-welded structure is used at the first flow channel hole 116 of a specific heat transfer plate, the condensed liquid refrigerant can be guided to the liquid storage section 130 through a pipe formed by the double-welded structure without entering the subcooling section 110B. Similarly, because a double-welded structure is used at the second through hole 113 of a specific heat transfer plate, the refrigerant flowing out of the liquid storage section 130 and subcooled through the cold section 110B is guided to the refrigerant piping P1 through a pipe formed by the double-welded structure without entering the condensation section 110A. This reduces the number of components used in the plate heat exchanger 100. For example, it eliminates the need for connecting pipes (jump pipes) between the condensing section 110A and the liquid storage section 130, the connecting pipes (jump pipes) between the subcooling section 110B and the first outlet 122 in the heat transfer plate assembly 110 of the plate heat exchanger 100, and connecting flanges and sealing gaskets or O-rings that must be used to install these connecting pipes. This facilitates the daily management and replacement of components and reduces refrigerant pressure loss. With saturated R134a refrigerant at a flow rate of 200 kg / h and a pressure of 2 MPa, the pressure loss can be reduced by about 1 kPa, and the effect is more pronounced at higher flow rates, thereby improving the efficiency of subcooling and heat exchange.

[0066] (Implementation Method 1B)

[0067] In the plate heat exchanger 100 of embodiment 1B, the condensing section 110A is as follows: Figure 4 As shown in (b), the three condensation sections (primary condensation section 110A-1, secondary condensation section 110A-2, and tertiary condensation section 110A-3) cause the first fluid to flow alternately in opposite directions. Figure 7 As shown in (b), a first condensing section separating heat transfer plate 111A-4 is provided between the heat transfer plate 111A (the first condensing section heat transfer plate 111A-1) constituting the first-stage condensing section 110A-1 and the heat transfer plate 111A (the second condensing section heat transfer plate 111A-2) constituting the second-stage condensing section 110A-2, and a second condensing section separating heat transfer plate 111A-5 is provided between the heat transfer plate 111A (the second condensing section heat transfer plate 111A-2) constituting the second-stage condensing section 110A-2 and the heat transfer plate 111A (the third condensing section heat transfer plate 111A-3) constituting the third-stage condensing section 110A-3.

[0068] The first inlet 121 on the first end plate 120A is connected to the first through hole 112 of the first condensing section heat transfer plate 111A-1 constituting the first condensing section 110A-1, and is used to introduce refrigerant from the refrigerant piping P1 into the refrigerant flow path of the first condensing section 110A-1. The refrigerant in the first condensing section 110A-1 converges at the first flow channel hole 116 before flowing to the first condensing section separating heat transfer plate 111A-4, and flows into the refrigerant flow path of the second condensing section 110A-2 through the first flow channel hole 116 of the first condensing section separating heat transfer plate 111A-4. The refrigerant in the second condensing section 110A-2 converges at the second flow channel hole 117 before flowing to the second condensing section separating heat transfer plate 111A-5, and flows into the refrigerant flow path of the third condensing section 110A-3 through the second flow channel hole 117 of the second condensing section separating heat transfer plate 111A-5. The refrigerant in the three-stage condensing section 110A-3 converges at the first flow channel hole 116 before flowing to the partition heat transfer plate 111C, and enters the liquid storage section 130 from the liquid storage section inlet through the first flow channel hole 116 of the partition heat transfer plate 111C and the subcooling section heat transfer plate 111B.

[0069] Thus, the refrigerant is temporarily stored in the liquid storage section 130. When the refrigerant needs to circulate in the thermal management system 10, the refrigerant stored in the liquid storage section 130 flows into the refrigerant flow path of the subcooling section 110B through the first through hole 112 via the liquid storage section outlet. The refrigerant in the subcooling section 110B converges at the second through hole 113 before flowing to the partition heat transfer plate 111C, and flows out to the refrigerant piping P1 through the second through holes 113 of the partition heat transfer plate 111C, the third condensing section heat transfer plate 111A-3, the second condensing section partition heat transfer plate 111A-5, the second condensing section heat transfer plate 111A-2, the first condensing section partition heat transfer plate 111A-4, and the first condensing section heat transfer plate 111A-1 via the first outlet 122 provided on the first end plate 120A.

[0070] Thus, in the plate heat exchanger 100 of embodiment 1B, the heat transfer plate 111A-1 for the first condensing section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115, and a first flow channel hole 116; the heat transfer plate 111A-4 for separating the first condensing section is a heat transfer plate with a configuration having a second through hole 113, a third through hole 114, a fourth through hole 115, and a second flow channel hole 117; the heat transfer plate 111A-2 for the second condensing section is a heat transfer plate with a configuration having a second through hole 113, a third through hole 114, a fourth through hole 115, a first flow channel hole 116, and a second flow channel hole 117; and the heat transfer plate 111A-5 for separating the second condensing section is... The heat transfer plate used in the third condensation section 111A-3 has a configuration of a second through hole 113, a third through hole 114, a fourth through hole 115 and a second flow channel hole 117. The heat transfer plate used in the third condensation section 111A-3 has a configuration of a second through hole 113, a third through hole 114, a fourth through hole 115, a first flow channel hole 116 and a second flow channel hole 117. The heat transfer plate used in the partition heat transfer plate 111C has a configuration of a second through hole 113, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116. The heat transfer plate used in the subcooling section 111B has a configuration of a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116.

[0071] Furthermore, in Embodiment 1B, the direction in which the refrigerant flows along the first condensing section heat transfer plate 111A-1 in the first-stage condensing section 110A-1 is the same as the direction in which the refrigerant flows along the third condensing section heat transfer plate 111A-3 in the third-stage condensing section 110A-3 (e.g., both moving from the left side to the right side of the heat transfer plate 111), and opposite to the direction in which the refrigerant flows along the second condensing section heat transfer plate 111A-2 in the second-stage condensing section 110A-2 (e.g., moving from the right side to the left side of the heat transfer plate 111). Moreover, the direction in which the refrigerant flows along the subcooling section heat transfer plate 111B in the subcooling section 110B (e.g., moving from the left side to the right side of the heat transfer plate 111) is opposite to the direction in which the refrigerant flows along the second condensing section heat transfer plate 111A-2 in the second-stage condensing section 110A-2 (e.g., moving from the right side to the left side of the heat transfer plate 111).

[0072] Furthermore, in embodiment 1B, the first flow channel hole 116 of the heat transfer plate 111A-3 for the third condensation section, the heat transfer plate 111C for separating the condensation section, and the heat transfer plate 111B for the subcooling section is used. Figure 6The double-welded structure shown in (a) further includes the use of the second through-hole 113 at the partition heat transfer plate 111C, the third condensing section heat transfer plate 111A-3, the second condensing section partition heat transfer plate 111A-5, the second condensing section heat transfer plate 111A-2, the first condensing section partition heat transfer plate 111A-4, and the first condensing section heat transfer plate 111A-1. Figure 6 The double-welded structure shown in (a) is used for the remaining flow channel holes. Figure 6 The single welded structure shown in (b).

[0073] Similar to Embodiment 1A, since a double-welded structure is used at the first flow channel hole 116 of a specific heat transfer plate, the condensed liquid refrigerant can be guided to the liquid storage section 130 through a pipe formed by the double-welded structure without entering the subcooling section 110B. Similarly, since a double-welded structure is used at the second through hole 113 of a specific heat transfer plate, the refrigerant flowing out of the liquid storage section 130 and subcooled through the cold section 110B is guided to the refrigerant piping P1 through a pipe formed by the double-welded structure without entering the condensation section 110A. Therefore, in Embodiment 1B, the number of components used in the plate heat exchanger 100 can also be reduced. For example, the connecting pipes (jump pipes) between the condensing section 110A and the liquid storage section 130, the connecting pipes (jump pipes) between the subcooling section 110B and the first outlet 122 in the heat transfer plate assembly 110 of the plate heat exchanger 100 can be omitted, as well as the connecting flanges and sealing components such as gaskets or O-rings that must be used to install these connecting pipes. On the one hand, this facilitates the daily management and replacement of components, and on the other hand, it reduces the pressure loss of the refrigerant. In the case of saturated R134a refrigerant with a flow rate of 200 kg / h and a pressure of 2 MPa, the pressure loss can be reduced by about 1 kPa, and the effect is more obvious when the flow rate is higher.

[0074] Furthermore, compared to the case in Embodiment 1A where the first fluid flows in the same direction in one condensation section, Embodiment 1B allows the first fluid to flow alternately in opposite directions in multiple condensation sections for multi-stage condensation. This improves the condensation efficiency of the first fluid in condensation section 110A, and further enhances the efficiency of subcooling heat exchange by utilizing the high heat exchange characteristics of the plate heat exchanger 100. As a result, the volume of the entire thermal management system can be reduced, and the amount of refrigerant required can be reduced due to the improved subcooling and heat exchange efficiency.

[0075] Table 1

[0076] (Implementation Method 2)

[0077] The plate heat exchanger 100 in Embodiment 2 is a plate heat exchanger with a configuration in which the agent-side inlet and outlet are arranged 1-1, wherein, Figure 8 (a) illustrates the flow of the first fluid (refrigerant) in an embodiment (Embodiment 2A) where the condensation section 110A of the heat transfer plate assembly 110 is a condensation section in which the first fluid flows in the same direction. Figure 8 (b) Lists the flow of the first fluid (refrigerant) in the embodiment (Embodiment 2B) of the condensation section 110A of the heat transfer plate assembly 110, which consists of three condensation sections in which the first fluid flows alternately in opposite directions. Table 2 below summarizes the configuration of each heat transfer plate, i.e., which heat transfer plates have the following holes: first through hole 112, first through hole 113, third through hole 114, fourth through hole 115, first flow channel hole 116, and second flow channel hole 117. “○” indicates the presence of the hole, and “-” indicates the absence of the hole.

[0078] (Implementation Method 2A)

[0079] In the plate heat exchanger 100 of embodiment 2A, the condensing section 110A is Figure 4 The case shown in (a) is a condensation section (i.e., condensation section 110A) in which the first fluid flows in the same direction.

[0080] At this time, the first inlet 121 provided on the first end plate 120A is connected to the first through hole 112 of the condensing section heat transfer plate 111A constituting the condensing section 110A, for introducing refrigerant from the refrigerant piping P1 into the refrigerant flow path of the condensing section 110A. The refrigerant in the condensing section 110A converges at the first flow channel hole 116 before flowing to the partition heat transfer plate 111C, and enters the liquid storage section 130 from the liquid storage section inlet through the first flow channel hole 116 of the partition heat transfer plate 111C and the subcooling section heat transfer plate 111B.

[0081] Therefore, the refrigerant is temporarily stored in the liquid storage section 130. When the refrigerant needs to circulate in the thermal management system 10, the refrigerant stored in the liquid storage section 130 flows into the refrigerant flow path of the subcooling section 110B through the second through hole 113 from the liquid storage section outlet. The refrigerant in the subcooling section 110B gathers at the first through hole 112 before flowing to the partition heat transfer plate 111C, and flows out to the refrigerant piping P1 through the first through hole 112 provided on the second end plate 120A via the first through hole 112 of the subcooling section heat transfer plate 111B.

[0082] Thus, in the plate heat exchanger 100 of embodiment 2A, the heat transfer plate 111A for the condensing section is a heat transfer plate with a configuration having a first through hole 112, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116, the heat transfer plate 111C for the partitioning section is a heat transfer plate with a configuration having a third through hole 114, a fourth through hole 115 and a first flow channel hole 116, and the heat transfer plate 111B for the subcooling section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116.

[0083] Furthermore, in Embodiment 2A, the direction in which the refrigerant flows along the heat transfer plate 111A in the condensing section 110A (for example, moving from the left side to the right side of the heat transfer plate 111) is opposite to the direction in which the refrigerant flows along the heat transfer plate 111B in the subcooling section 110B (for example, moving from the right side to the left side of the heat transfer plate 111).

[0084] Furthermore, in embodiment 2A, the first flow channel hole 116 of the heat transfer plate 111C separating the heat transfer plate 111C and the subcooling section is used Figure 6 The double-welded structure shown in (a) is used for the remaining flow channel holes. Figure 6 The single welded structure shown in (b).

[0085] Similar to Embodiment 1A, since a double-welded structure is used at the first flow channel hole 116 of a specific heat transfer plate, the condensed liquid refrigerant can be guided to the liquid storage section 130 through a pipe formed by the double-welded structure without entering the subcooling section 110B. This reduces the number of components used in the plate heat exchanger 100. For example, the connecting pipe (jump pipe) between the condensing section 110A and the liquid storage section 130 in the heat transfer plate assembly 110 of the plate heat exchanger 100, as well as connecting flanges and sealing gaskets or O-rings required for installing this connecting pipe, can be omitted. This facilitates routine management and replacement of components, reduces refrigerant pressure loss, and has a more significant effect at higher flow rates, thereby improving the efficiency of subcooling and heat exchange.

[0086] (Implementation Method 2B)

[0087] In the plate heat exchanger 100 of embodiment 2B, the condensing section 110A is as follows: Figure 4 (b) shows three condensation sections (first-stage condensation section 110A-1, second-stage condensation section 110A-2, and third-stage condensation section 110A-3) in which the first fluid flows alternately in opposite directions, and has the same structure as condensation section 110A in embodiment 1B.

[0088] The first inlet 121 on the first end plate 120A is connected to the first through hole 112 of the first condensing section heat transfer plate 111A-1 constituting the first condensing section 110A-1, and is used to introduce refrigerant from the refrigerant piping P1 into the refrigerant flow path of the first condensing section 110A-1. The refrigerant in the first condensing section 110A-1 converges at the second through hole 113 before flowing to the first condensing section separating heat transfer plate 111A-4, and flows into the refrigerant flow path of the second condensing section 110A-2 through the second through hole 113 of the first condensing section separating heat transfer plate 111A-4. The refrigerant in the second condensing section 110A-2 converges at the first through hole 112 before flowing to the second condensing section separating heat transfer plate 111A-5, and flows into the refrigerant flow path of the third condensing section 110A-3 through the first through hole 112 of the second condensing section separating heat transfer plate 111A-5. The refrigerant in the three-stage condensing section 110A-3 converges at the first flow channel hole 116 before flowing to the partition heat transfer plate 111C, and enters the liquid storage section 130 from the liquid storage section inlet through the first flow channel hole 116 of the partition heat transfer plate 111C and the subcooling section heat transfer plate 111B.

[0089] Therefore, the refrigerant is temporarily stored in the liquid storage section 130. When the refrigerant needs to circulate in the thermal management system 10, the refrigerant stored in the liquid storage section 130 flows into the refrigerant flow path of the subcooling section 110B through the second through hole 113 from the liquid storage section outlet. The refrigerant in the subcooling section 110B gathers at the first through hole 112 before flowing to the partition heat transfer plate 111C, and flows out to the refrigerant piping P1 through the first through hole 112 provided on the second end plate 120A via the first through hole 112 of the subcooling section heat transfer plate 111B.

[0090] Thus, in the plate heat exchanger 100 of embodiment 2B, the heat transfer plate 111A-1 for the first condensing section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, and a fourth through hole 115; the heat transfer plate 111A-4 for separating the first condensing section is a heat transfer plate with a configuration having a second through hole 113, a third through hole 114, and a fourth through hole 115; the heat transfer plate 111A-2 for the second condensing section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, and a fourth through hole 115; and the heat transfer plate 111A-5 for separating the second condensing section is... The heat transfer plate 111A-3 for the third condensing section is a heat transfer plate with a configuration of a first through hole 112, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116. The heat transfer plate 111C for the partitioning section is a heat transfer plate with a configuration of a third through hole 114, a fourth through hole 115 and a first flow channel hole 116. The heat transfer plate 111B for the subcooling section is a heat transfer plate with a configuration of a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116.

[0091] Furthermore, in Embodiment 2B, the direction in which the refrigerant flows along the first condensing section heat transfer plate 111A-1 in the first-stage condensing section 110A-1 is the same as the direction in which the refrigerant flows along the third condensing section heat transfer plate 111A-3 in the third-stage condensing section 110A-3 (e.g., both moving from the left side to the right side of the heat transfer plate 111), and opposite to the direction in which the refrigerant flows along the second condensing section heat transfer plate 111A-2 in the second-stage condensing section 110A-2 (e.g., moving from the right side to the left side of the heat transfer plate 111). Moreover, the direction in which the refrigerant flows along the subcooling section heat transfer plate 111B in the subcooling section 110B (e.g., moving from the right side to the left side of the heat transfer plate 111) is the same as the direction in which the refrigerant flows along the second condensing section heat transfer plate 111A-2 in the second-stage condensing section 110A-2 (e.g., moving from the right side to the left side of the heat transfer plate 111).

[0092] Furthermore, in embodiment 2B, the first flow channel hole 116 of the heat transfer plate 111A-3 for the third condensation section, the heat transfer plate 111C for separating the condensation section, and the heat transfer plate 111B for the subcooling section is used. Figure 6 The double-welded structure shown in (a) is used for the remaining flow channel holes. Figure 6 The single welded structure shown in (b).

[0093] Similar to Embodiment 1B, since a double-welded structure is used at the first flow channel hole 116 of a specific heat transfer plate, the condensed liquid refrigerant can be guided to the liquid storage section 130 through a pipe formed by the double-welded structure without entering the subcooling section 110B. Therefore, in Embodiment 2B, the number of components used in the plate heat exchanger 100 can also be reduced. For example, the connecting pipe (jump pipe) between the condensing section 110A of the heat transfer plate assembly 110 of the plate heat exchanger 100 and the liquid storage section 130, as well as connecting flanges and sealing gaskets or O-rings required for installing this connecting pipe, can be omitted. This facilitates routine management and replacement of components and reduces refrigerant pressure loss, thereby improving the efficiency of subcooling and heat exchange.

[0094] In addition, similar to Embodiment 1B, compared to Embodiment 2A, Embodiment 2B allows the first fluid to flow alternately in opposite directions in multiple condensing sections for multi-stage condensation, which improves the condensation efficiency of the first fluid in condensing section 110A. Furthermore, by utilizing the high heat exchange characteristics of the plate heat exchanger 100, the efficiency of subcooling heat exchange is further improved. As a result, the volume of the entire thermal management system can be reduced, and due to the improvement in subcooling and heat exchange efficiency, the amount of refrigerant required can be reduced.

[0095] Table 2

[0096] (Implementation Method 3)

[0097] The plate heat exchanger 100 in embodiment 3 is another configuration of plate heat exchanger with the agent-side inlet and outlet arranged 1-1, wherein, Figure 9 (a) Lists the flow of the first fluid (refrigerant) in an embodiment (Embodiment 3A) where the condensation section 110A of the heat transfer plate assembly 110 is a condensation section in which the first fluid flows in the same direction. Figure 9 (b) Lists the flow of the first fluid (refrigerant) in the embodiment (Embodiment 3B) of the condensation section 110A of the heat transfer plate assembly 110, in which the first fluid flows alternately in opposite directions. Table 3 below summarizes the configuration of each heat transfer plate, i.e., which heat transfer plates have the first through hole 112, the first through hole 113, the third through hole 114, the fourth through hole 115, the first flow channel hole 116, and the second flow channel hole 117. “○” indicates the presence of the hole, and “-” indicates the absence of the hole.

[0098] (Implementation Method 3A)

[0099] In the plate heat exchanger 100 of embodiment 3A, the condensing section 110A is Figure 4The case shown in (a) is a condensation section (i.e., condensation section 110A) in which the first fluid flows in the same direction.

[0100] At this time, the first inlet 121 provided on the first end plate 120A is connected to the first through hole 112 of the condensing section heat transfer plate 111A constituting the condensing section 110A, for introducing refrigerant from the refrigerant piping P1 into the refrigerant flow path of the condensing section 110A. The refrigerant in the condensing section 110A converges at the first flow channel hole 116 before flowing to the partition heat transfer plate 111C, and enters the liquid storage section 130 from the liquid storage section inlet through the first flow channel hole 116 of the partition heat transfer plate 111C and the subcooling section heat transfer plate 111B.

[0101] Thus, the refrigerant is temporarily stored in the liquid storage section 130. When the refrigerant needs to circulate in the thermal management system 10, the refrigerant stored in the liquid storage section 130 flows into the refrigerant flow path of the subcooling section 110B through the first through hole 112 via the liquid storage section outlet. The refrigerant in the subcooling section 110B converges at the second through hole 113 before flowing to the partition heat transfer plate 111C, and flows out to the refrigerant piping P1 through the second through hole 113 of the subcooling section heat transfer plate 111B via the first outlet 122 provided on the second end plate 120A.

[0102] Thus, in the plate heat exchanger 100 of embodiment 3A, the heat transfer plate 111A for the condensing section is a heat transfer plate with a configuration having a first through hole 112, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116, the heat transfer plate 111C for the partitioning section is a heat transfer plate with a configuration having a third through hole 114, a fourth through hole 115 and a first flow channel hole 116, and the heat transfer plate 111B for the subcooling section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116.

[0103] Furthermore, in Embodiment 3A, the direction in which the refrigerant flows along the heat transfer plate 111A in the condensing section 110A (for example, moving from the left side to the right side of the heat transfer plate 111) is the same as the direction in which the refrigerant flows along the heat transfer plate 111B in the subcooling section 110B (for example, moving from the left side to the right side of the heat transfer plate 111).

[0104] Furthermore, in embodiment 3A, the first flow channel hole 116 of the heat transfer plate 111C separating the heat transfer plate 111C and the subcooling section is used Figure 6 The double-welded structure shown in (a) is used for the remaining flow channel holes. Figure 6 The single welded structure shown in (b).

[0105] Similar to Embodiments 1A and 2A, since a double-welded structure is used at the first flow channel hole 116 of a specific heat transfer plate, the condensed liquid refrigerant can be guided to the liquid storage section 130 through a pipe formed by the double-welded structure without entering the subcooling section 110B. This reduces the number of components used in the plate heat exchanger 100. For example, the connecting pipe (jump pipe) between the condensing section 110A and the liquid storage section 130 in the heat transfer plate assembly 110 of the plate heat exchanger 100, as well as connecting flanges and sealing gaskets or O-rings required for installing this connecting pipe, can be omitted. This facilitates routine management and replacement of components, reduces refrigerant pressure loss, and has a more significant effect at higher flow rates, thereby improving the efficiency of subcooling and heat exchange.

[0106] (Implementation Method 3B)

[0107] In the plate heat exchanger 100 of embodiment 3B, the condensing section 110A is as follows: Figure 4 (b) shows three condensation sections (first-stage condensation section 110A-1, second-stage condensation section 110A-2, and third-stage condensation section 110A-3) in which the first fluid flows alternately in opposite directions, and has the same structure as condensation section 110A in Embodiments 1B and 2B.

[0108] The first inlet 121 on the first end plate 120A is connected to the first through hole 112 of the first condensing section heat transfer plate 111A-1 constituting the first condensing section 110A-1, and is used to introduce refrigerant from the refrigerant piping P1 into the refrigerant flow path of the first condensing section 110A-1. The refrigerant in the first condensing section 110A-1 converges at the second through hole 113 before flowing to the first condensing section separating heat transfer plate 111A-4, and flows into the refrigerant flow path of the second condensing section 110A-2 through the second through hole 113 of the first condensing section separating heat transfer plate 111A-4. The refrigerant in the second condensing section 110A-2 converges at the first through hole 112 before flowing to the second condensing section separating heat transfer plate 111A-5, and flows into the refrigerant flow path of the third condensing section 110A-3 through the first through hole 112 of the second condensing section separating heat transfer plate 111A-5. The refrigerant in the three-stage condensing section 110A-3 converges at the first flow channel hole 116 before flowing to the partition heat transfer plate 111C, and enters the liquid storage section 130 from the liquid storage section inlet through the first flow channel hole 116 of the partition heat transfer plate 111C and the subcooling section heat transfer plate 111B.

[0109] Thus, the refrigerant is temporarily stored in the liquid storage section 130. When the refrigerant needs to circulate in the thermal management system 10, the refrigerant stored in the liquid storage section 130 flows into the refrigerant flow path of the subcooling section 110B through the first through hole 112 via the liquid storage section outlet. The refrigerant in the subcooling section 110B converges at the second through hole 113 before flowing to the partition heat transfer plate 111C, and flows out to the refrigerant piping P1 through the second through hole 113 of the subcooling section heat transfer plate 111B via the first outlet 122 provided on the second end plate 120A.

[0110] Thus, in the plate heat exchanger 100 of embodiment 3B, the heat transfer plate 111A-1 for the first condensing section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, and a fourth through hole 115; the heat transfer plate 111A-4 for separating the first condensing section is a heat transfer plate with a configuration having a second through hole 113, a third through hole 114, and a fourth through hole 115; the heat transfer plate 111A-2 for the second condensing section is a heat transfer plate with a configuration having a first through hole 112, a second through hole 113, a third through hole 114, and a fourth through hole 115; and the heat transfer plate 111A-5 for separating the second condensing section is... The heat transfer plate 111A-3 for the third condensing section is a heat transfer plate with a configuration of a first through hole 112, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116. The heat transfer plate 111C for the partitioning section is a heat transfer plate with a configuration of a third through hole 114, a fourth through hole 115 and a first flow channel hole 116. The heat transfer plate 111B for the subcooling section is a heat transfer plate with a configuration of a first through hole 112, a second through hole 113, a third through hole 114, a fourth through hole 115 and a first flow channel hole 116.

[0111] Furthermore, in Embodiment 3B, the direction in which the refrigerant flows along the first condensing section heat transfer plate 111A-1 in the first-stage condensing section 110A-1 is the same as the direction in which the refrigerant flows along the third condensing section heat transfer plate 111A-3 in the third-stage condensing section 110A-3 (e.g., both moving from the left side to the right side of the heat transfer plate 111), and opposite to the direction in which the refrigerant flows along the second condensing section heat transfer plate 111A-2 in the second-stage condensing section 110A-2 (e.g., moving from the right side to the left side of the heat transfer plate 111). Moreover, the direction in which the refrigerant flows along the subcooling section heat transfer plate 111B in the subcooling section 110B (e.g., moving from the left side to the right side of the heat transfer plate 111) is opposite to the direction in which the refrigerant flows along the second condensing section heat transfer plate 111A-2 in the second-stage condensing section 110A-2 (e.g., moving from the right side to the left side of the heat transfer plate 111).

[0112] Furthermore, in embodiment 3B, the first flow channel hole 116 of the heat transfer plate 111A-3 for the third condensation section, the heat transfer plate 111C for separating the condensation section, and the heat transfer plate 111B for the subcooling section is used. Figure 6 The double-welded structure shown in (a) is used for the remaining flow channel holes. Figure 6 The single welded structure shown in (b).

[0113] Similar to Embodiments 1B and 2B, since a double-welded structure is used at the first flow channel hole 116 of a specific heat transfer plate, the condensed liquid refrigerant can be guided to the liquid storage section 130 through a pipe formed by the double-welded structure without entering the subcooling section 110B. Therefore, in Embodiment 3B, the number of components used in the plate heat exchanger 100 can also be reduced. For example, the connecting pipe (jump pipe) between the condensing section 110A of the heat transfer plate assembly 110 of the plate heat exchanger 100 and the liquid storage section 130, as well as connecting flanges and sealing gaskets or O-rings required for installing this connecting pipe, can be omitted. This facilitates routine management and replacement of components and reduces refrigerant pressure loss, thereby improving the efficiency of subcooling and heat exchange.

[0114] In addition, similar to Embodiments 1B and 2B, compared to Embodiment 3A, Embodiment 3B allows the first fluid to flow alternately in opposite directions in multiple condensing sections for multi-stage condensation, which improves the condensation efficiency of the first fluid in condensing section 110A. Furthermore, by utilizing the high heat exchange characteristics of the plate heat exchanger 100, the efficiency of subcooling heat exchange is further improved. As a result, the volume of the entire thermal management system can be reduced, and due to the improvement in subcooling and heat exchange efficiency, the amount of refrigerant required can be reduced.

[0115] Table 3

[0116] (Thermal Management System 10)

[0117] Below, refer to Figure 10 The connection circuit of the thermal management system 10 of this utility model will be described, wherein... Figure 10 This is a schematic diagram showing the connection circuit of the thermal management system 10 of this utility model.

[0118] The thermal management system 10 of this utility model, such as Figure 10As shown, the system includes a compressor 11, a plate heat exchanger (first heat exchanger) 100 serving as a condenser, a second heat exchanger 13 serving as an evaporator, and a throttling element 14 disposed between the plate heat exchanger 100 and the second heat exchanger 13. Low-temperature, low-pressure liquid refrigerant first absorbs heat from a high-temperature heat source and vaporizes into low-pressure vapor in the second heat exchanger 13, which serves as the evaporator. Then, the refrigerant gas is compressed into high-temperature, high-pressure vapor in the compressor 11. This high-temperature, high-pressure vapor is cooled and condensed into high-pressure liquid by a low-temperature heat source in the plate heat exchanger 100, which serves as the condenser. The liquid is then throttled by the throttling element 14 to become low-temperature, low-pressure liquid refrigerant, thus forming a refrigeration cycle. Furthermore, the high-pressure liquid refrigerant condensed in the condensing section 110A of the heat transfer plate assembly 110 of the plate heat exchanger 100 is stored in a liquid storage section 130 integrated with the plate heat exchanger 100, thereby eliminating the need for... Figure 11 The liquid storage tank 15', which is a separate component located between the first heat exchanger 12' and the second heat exchanger 13' in the existing thermal management system 10' shown, reduces the overall boundary dimensions of the thermal management system 10. At the same time, since the thermal management system 10 of this utility model uses a plate heat exchanger 100 with a subcooling section 110B, the cooling capacity of the thermal management system 10 can be increased without charging more refrigerant.

[0119] Although various embodiments of this application have been shown and described, it will be understood by those skilled in the art that many changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the appended claims and their equivalents.

[0120] Furthermore, in this invention, the case where the condensing section 110A consists of multiple condensing sections in which the first fluid flows alternately in opposite directions is illustrated by taking three condensing sections (first-stage condensing section 110A-1, second-stage condensing section 110A-2, and third-stage condensing section 110A-3) as an example. However, this invention is not limited to this, and the condensing section 110A can also consist of five condensing sections, seven condensing sections, etc. At this point, taking five condensing sections as an example, in the case of a plate heat exchanger 100 with a 2-0 arrangement of the agent-side inlet and outlet, since the first condensing section separating heat transfer plate 111A-4 and the second condensing section heat transfer plate 111A-2, which are grouped together, have the same structure as the second condensing section separating heat transfer plate 111A-5 and the third condensing section heat transfer plate 111A-3, then only two more sets of condensing section separating heat transfer plates and condensing section heat transfer plates need to be added. However, in the case of a plate heat exchanger 100 with a 1-1 arrangement of the agent-side inlet and outlet, since the first condensing section heat transfer plate 111A-1 and the second condensing section heat transfer plate 111A-5 have the same structure as the second condensing section separating heat transfer plate 111A-5 and the third condensing section heat transfer plate 111A-3, then only two more sets of condensing section separating heat transfer plates and condensing section heat transfer plates need to be added. The structure of 2 is exactly the same, that is, it has both a first flow channel hole 116 and a second flow channel hole 117. The first condensing section separating heat transfer plate 111A-4 and the second condensing section separating heat transfer plate 111A-5 have one with a first flow channel hole 116 and the other with a second flow channel hole 117. At this time, it is only necessary to alternately add the "condensing section heat transfer plate with the first flow channel hole 116 and the second flow channel hole 117 and the condensing section separating heat transfer plate with the first flow channel hole 116" as one group and the "condensing section heat transfer plate with the first flow channel hole 116 and the second flow channel hole 117 and the condensing section separating heat transfer plate with the second flow channel hole 117" as another group.

[0121] Furthermore, the number of condensation sections is not limited to an odd number; there can also be two condensation sections, four condensation sections, and so on. In this case, it is sufficient to consider the flow channel hole (i.e., the first flow channel hole 116 in each embodiment) located on the opposite side of the first through hole 112 used when there are three condensation sections, five condensation sections, seven condensation sections, etc., as the second flow channel hole 117, and consider the flow channel hole (i.e., the second flow channel hole 117 in each embodiment) located on the same side of the first through hole 112 used when there are three condensation sections, five condensation sections, seven condensation sections, etc., as the first flow channel hole 116.

Claims

1. A plate heat exchanger with a subcooling section and a liquid storage section for heat exchange between a first fluid and a second fluid, the plate heat exchanger (100) comprising: A heat transfer plate assembly (110) is formed by multiple heat transfer plates (111) overlapping in the length direction of the plate heat exchanger (100). The heat transfer plate assembly (110) has a condensation section (110A) for condensing a gaseous first fluid into a liquid first fluid and a subcooling section (110B) for subcooling the liquid first fluid. A first end plate (120A) and a second end plate (120B) clamp the heat transfer plate assembly (110) along the length direction. The first end plate (120A) is provided with a first inlet (121) for the first fluid to flow into the heat transfer plate assembly (110), and the first end plate (120A) or the second end plate (120B) is provided with a first outlet (122) for the first fluid to flow out of the heat transfer plate assembly (110). A liquid storage section (130) is integrated on one side of the second end plate (120B) and stores the first liquid condensed from the condensation section of the heat transfer plate assembly (110). The plurality of heat transfer plates (111) include a heat transfer plate (111A) for condensing section constituting the condensing section (110A), a heat transfer plate (111B) for subcooling section constituting the subcooling section (110B), and a partition heat transfer plate (111C) located between the condensing section (110A) and the subcooling section (110B). Its features are, The heat transfer plate (111A) for the condensation section has a first through hole (112) located on one side of the plate surface of the heat transfer plate (111) and communicating with the first inlet (121). At least a portion of the heat transfer plate (111A) for the condensation section, the heat transfer plate (111C) for the separation section, and the heat transfer plate (111B) for the subcooling section have flow channel holes on the plate surface of the heat transfer plate (111) that are connected to the inlet of the liquid storage section (130) and located on the same side or opposite side of the first through hole (112). The flow channel holes of the separating heat transfer plate (111C) and the subcooling section heat transfer plate (111B) use a double-welded structure. The first fluid flowing into the condensing section (110A) from the first inlet (121) via the first through hole (112) will not enter the first fluid flow path of the flow channel of each layer of the heat transfer plate (111C) for the separating heat transfer plate (111C) and the heat transfer plate (111B) for the subcooling section, but will instead flow into the liquid storage section (130) from the liquid storage section inlet through a pipe formed by the flow channel hole using a double-welded structure.

2. The plate heat exchanger with subcooling section and liquid storage section as described in claim 1, characterized in that, The condensation section (110A) has multiple condensation sections that allow the first fluid to flow alternately in opposite directions. A heat transfer plate separating the condensing sections is provided between the heat transfer plates that form two adjacent condensing sections.

3. The plate heat exchanger with subcooling section and liquid storage section as described in claim 2, characterized in that, The condensation section (110A) has three condensation sections that allow the first fluid to flow alternately in opposite directions. A first condensing section separating heat transfer plate (111A-4) is provided between the heat transfer plate (111A) constituting the first condensing section (110A-1), i.e., the first condensing section heat transfer plate (111A-1), and the heat transfer plate (111A) constituting the second condensing section (110A-2), i.e., the second condensing section heat transfer plate (111A-2). A second condensing section separating heat transfer plate (111A-5) is provided between the heat transfer plate (111A) constituting the second condensing section (110A-2) and the heat transfer plate (111A) constituting the third condensing section (110A-3).

4. The plate heat exchanger with subcooling section and liquid storage section as described in claim 3, characterized in that, The first condensation section heat transfer plate (111A-1) has a first through hole (112) on one side of the heat transfer plate (111) that communicates with the first inlet (121). The heat transfer plate (111A-3) for the third condensation section has a first flow channel hole (116) on the plate surface of the heat transfer plate (111) opposite to the first through hole (112), which is connected to the inlet of the liquid storage section (130). The first flow channel hole (116) of the separating heat transfer plate (111C) and the subcooling section heat transfer plate (111B) uses a double-welded structure. The first fluid flowing from the first inlet (121) through the first through hole (112) into the condensing section (110A) and into the third-stage condensing section (110A-3) will not enter the first fluid flow path of each layer of the heat transfer channel of the separating heat transfer plate (111C) and the heat transfer plate (111B) of the subcooling section. Instead, it flows into the liquid storage section (130) from the liquid storage section inlet through a pipe formed by the first flow channel hole (116) with a double-welded structure.

5. The plate heat exchanger with subcooling section and liquid storage section as described in claim 1, characterized in that, The first inlet (121) and the first outlet (122) are respectively located on one side and the other side of the first end plate (120A). The subcooling section heat transfer plate (111B) has a first through hole (112) located on one side of the plate surface of the heat transfer plate (111) that communicates with the liquid storage outlet of the liquid storage section (130). The heat transfer plate (111A) for the condensing section, the heat transfer plate (111C) for the separating section, and the heat transfer plate (111B) for the subcooling section have a second through hole (113) that communicates with the first outlet (122), is located on the other side of the surface of the heat transfer plate (111), and is not in the same vertical position as the flow channel hole. The second through hole (113) of the separating heat transfer plate (111C) and the condensation section heat transfer plate (111A) uses a double-welded structure. The first fluid stored in the liquid storage section (130) and flowing into the subcooling section (110B) from the outlet of the liquid storage section via the first through hole (112) will not enter the first fluid flow path of the flow channel of each layer of the heat transfer plate (111C) for separating the heat transfer plate (111A) for the condensing section, but will flow out from the first outlet (122) provided on the first end plate (120A) through a pipe formed by the second through hole (113) using a double welded structure.

6. The plate heat exchanger with subcooling section and liquid storage section as described in claim 4, characterized in that, The first inlet (121) and the first outlet (122) are respectively located on one side and the other side of the first end plate (120A). The first heat transfer plate (111A-1) for the first condensation section has a first fluid flow path in each layer that communicates with the first through hole (112) of the first heat transfer plate (111A-1) for the first condensation section, and a first flow channel hole (116) located on the plate surface of the heat transfer plate (111) on the side opposite to the first through hole (112). The first condensing section separating heat transfer plate (111A-4) and the second condensing section heat transfer plate (111A-2) have a second flow channel hole (117) that communicates with the first flow channel hole (116) of the first condensing section heat transfer plate (111A-1), and is located on the same side of the heat transfer plate (111) as the first through hole (112) and is not in the same vertical position as the first through hole (112). The second condensing section heat transfer plate (111A-2) has a first flow channel hole (116) located on the plate surface of the heat transfer plate (111) opposite to the first through hole (112) that communicates with the first fluid flow path in the flow channel of each layer and the second flow channel hole (117) of the second condensing section heat transfer plate (111A-2). The second condensing section separating heat transfer plate (111A-5) and the third condensing section heat transfer plate (111A-3) have a second flow channel hole (117) that communicates with the first flow channel hole (116) of the second condensing section heat transfer plate (111A-2), and is located on the same side of the heat transfer plate (111) as the first through hole and not at the same vertical position as the first through hole (112). The first flow channel hole (116) of the heat transfer plate (111A-3) for the third condensation section is connected to the first fluid flow path of the flow channel in each layer and the second flow channel hole (117) of the heat transfer plate (111A-3) for the third condensation section. The subcooling section heat transfer plate (111B) has a first through hole (112) located on one side of the plate surface of the heat transfer plate (111) that communicates with the liquid storage outlet of the liquid storage section (130). The first condensing section heat transfer plate (111A-1), the first condensing section partition heat transfer plate (111A-4), the second condensing section heat transfer plate (111A-2), the second condensing section partition heat transfer plate (111A-5), the third condensing section heat transfer plate (111A-3), the partition heat transfer plate (111C), and the subcooling section heat transfer plate (111B) have a second through hole (113) that communicates with the first outlet (122), is located on the other side of the heat transfer plate (111), and is not in the same vertical position as the first flow channel hole (116). The second through hole (113) of the partition heat transfer plate (111C), the third condensing section heat transfer plate (111A-3), the second condensing section partition heat transfer plate (111A-5), the second condensing section heat transfer plate (111A-2), the first condensing section partition heat transfer plate (111A-4), and the first condensing section heat transfer plate (111A-1) uses a double-welded structure. The first fluid stored in the liquid storage section (130) and flowing into the subcooled section (110B) through the first through hole (112) from the outlet of the liquid storage section will not enter the first fluid flow path of the flow channel of each layer of the partition heat transfer plate (111C), the third condensing section heat transfer plate (111A-3), the second condensing section partition heat transfer plate (111A-5), the second condensing section heat transfer plate (111A-2), the first condensing section partition heat transfer plate (111A-4), and the first condensing section heat transfer plate (111A-1), but will flow out from the first outlet (122) provided on the first end plate (120A) through a pipe formed by the second through hole (113) with a double welded structure.

7. The plate heat exchanger with subcooling section and liquid storage section as described in claim 1, characterized in that, The first flow inlet (121) and the first flow outlet (122) are respectively located at the same position on one side of the first end plate (120A) and the second end plate (120B). The subcooling section heat transfer plate (111B) has: a first through hole (112) communicating with the first outlet (122) and located on one side of the plate surface of the heat transfer plate (111); and a second through hole (113) communicating with the outlet of the liquid storage section (130) and located on the other side of the plate surface of the heat transfer plate (111) and not at the same vertical position as the flow channel hole.

8. The plate heat exchanger with subcooling section and liquid storage section as described in claim 1, characterized in that, The first inlet (121) and the first outlet (122) are respectively disposed on one side of the first end plate (120A) and the other side of the second end plate (120B). The subcooling section heat transfer plate (111B) has: a first through hole (112) on one side of the heat transfer plate (111) that communicates with the outlet of the liquid storage section (130); and a second through hole (113) on the other side of the heat transfer plate (111) that communicates with the first outlet (122) and is not at the same vertical position as the flow channel hole.

9. The plate heat exchanger with subcooling section and liquid storage section as described in claim 4, characterized in that, The first inlet (121) and the first outlet (122) are respectively located at the same position on one side of the first end plate (120A) and the second end plate (120B), or the first inlet (121) and the first outlet (122) are respectively located on one side of the first end plate (120A) and the other side of the second end plate (120B). The first condensing section heat transfer plate (111A-1), the first condensing section separating heat transfer plate (111A-4), and the second condensing section heat transfer plate (111A-2) have a second through hole (113) located on the other side of the surface of the heat transfer plate (111) that communicates with the first through hole (112) of the first condensing section heat transfer plate (111A-1) in the first fluid flow path of the flow channel of each layer. The second condensing section heat transfer plate (111A-2), the second condensing section partition heat transfer plate (111A-5), and the third condensing section heat transfer plate (111A-3) have a first through hole (112) located on one side of the heat transfer plate (111) that communicates with the second through hole (113) of the second condensing section heat transfer plate (111A-2) in the first fluid flow path of the flow channel of each layer.

10. The plate heat exchanger with a subcooling section and a liquid storage section as described in any one of claims 1 to 9, characterized in that, The first fluid is a refrigerant. The second fluid is a heat transfer fluid.

11. A thermal management system (10), comprising a compressor (11), a first heat exchanger as a condenser, a second heat exchanger (13) as an evaporator, and a throttling element (14) disposed between the first heat exchanger and the second heat exchanger (13), characterized in that, The thermal management system (10) does not include a liquid storage section as a separate component. The first heat exchanger is a plate heat exchanger with a subcooling section and a liquid storage section as described in any one of claims 1 to 10.

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