Plate heat exchanger, vehicle heat management device, vehicle heat management system and vehicle

Abstract

The utility model discloses a plate heat exchanger, a vehicle heat management device, a vehicle heat management system and a vehicle, the plate heat exchanger is provided with a first refrigerant flow channel and a plurality of first flow channels which are mutually independent, and the plurality of first flow channels comprise a second refrigerant flow channel and a first water cooling flow channel; the first refrigerant flow channel is used for receiving the refrigerant flowing out of the second refrigerant flow channel. According to the technical scheme, the space occupied by the thermal management device for the vehicle is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchangers, and in particular to a plate heat exchanger, a vehicle thermal management device, a vehicle thermal management system and a vehicle. Background Art

[0002] At present, a vehicle includes a vehicle thermal management system, which includes a vehicle thermal management device, which includes a compressor, a condenser, an expansion valve, an evaporator, and a connecting pipe, which is used to conduct the compressor, the condenser, the expansion valve, and the evaporator. However, the length of the connecting pipe is relatively long, which will cause the vehicle thermal management device to occupy a large space. Utility Model Content

[0003] The main purpose of the utility model is to provide a plate heat exchanger, which is intended to help reduce the space occupied by a vehicle thermal management device.

[0004] To achieve the above-mentioned purpose, the plate heat exchanger proposed in the utility model is provided with a mutually independent first refrigerant flow channel and multiple first flow channels, the multiple first flow channels include a second refrigerant flow channel and a first water-cooled flow channel, and the first refrigerant flow channel is used to receive the refrigerant flowing out from the second refrigerant flow channel.

[0005] Optionally, the first refrigerant flow channel extends along a thickness direction of the plate heat exchanger.

[0006] Optionally, the first flow channel includes a first flow area, the plate heat exchanger includes a plurality of stacked first heat exchange plates, a cavity is defined between two adjacent first heat exchange plates, the cavity includes the first flow area, and the first refrigerant flow channel passes through the plurality of first heat exchange plates and is arranged outside the first flow area.

[0007] Optionally, the first heat exchange plate includes a first plate body and a first plate protrusion arranged on the outer periphery of the first plate body, the first plate body is used to limit the first flow area, and the first refrigerant flow channel is penetrated by the first plate protrusion.

[0008] Optionally, in a protruding direction of the first plate protrusion relative to the first plate body, the first plate protrusion is tapered.

[0009] Optionally, the first plate protrusion is provided with a partition rib, and the partition rib is used to separate the cavity into a sealing area and the first flow area, and the first refrigerant flow channel is arranged through the sealing area.

[0010] Optionally, a first guide rib is provided in the first flow area so that the first flow area is bent.

[0011] Optionally, the second refrigerant flow channel is configured as a condensation flow channel.

[0012] Optionally, the plurality of first flow channels further include a supercooling flow channel.

[0013] The utility model also proposes a vehicle thermal management device, which includes a first plate heat exchanger and a second plate heat exchanger. The first plate heat exchanger is configured as the aforementioned plate heat exchanger, and the second plate heat exchanger is provided with a plurality of second flow channels, and the plurality of second flow channels include a third refrigerant flow channel and a second water-cooling flow channel. The first refrigerant flow channel receives the refrigerant flowing out of the second refrigerant flow channel through the third refrigerant flow channel.

[0014] Optionally, the second flow channel includes a second flow area, and the second plate heat exchanger includes a plurality of second heat exchange plates stacked together, and the second flow area is defined between two adjacent second heat exchange plates.

[0015] Optionally, the second heat exchange plate includes a second plate body and a second plate protrusion arranged on the outer periphery of the second plate body, and the second flow area flows through the second plate bodies and the second plate protrusions of two corresponding adjacent second heat exchange plates.

[0016] Optionally, the second flow channel also includes a second confluence section having one end of the second flow channel, and a second diversion section having the other end of the second flow channel, the second flow area connects the second confluence section and the second diversion section, the second flow area is provided with a plurality of the second diversion sections, the second diversion sections are provided through the second plate body, the second confluence section is provided through a plurality of the second plate protrusions, in the thickness direction of the first plate heat exchanger, the second plate heat exchanger is arranged in parallel with the first plate heat exchanger, a port of the second diversion section is provided on a side of the second plate heat exchanger close to the first plate heat exchanger, a port of the second confluence section is provided on a side of the second plate heat exchanger close to the first plate heat exchanger, the second diversion section is communicated with the second refrigerant flow channel, and the second confluence section is communicated with the first refrigerant flow channel.

[0017] Optionally, in a protruding direction of the second plate protrusion relative to the second plate body, the second plate protrusion is tapered.

[0018] Optionally, a second guide rib is provided in the second flow region so that the second flow region is bent.

[0019] Optionally, a liquid flow direction in the second flow region of the third refrigerant flow channel is different from a liquid flow direction in the second flow region of the second water-cooling flow channel.

[0020] The utility model also provides a vehicle thermal management system, which includes the above-mentioned vehicle thermal management device.

[0021] The utility model also provides a vehicle, which comprises the above-mentioned vehicle thermal management system.

[0022] In the technical solution of the utility model, the plate heat exchanger is provided with a first refrigerant flow channel and a plurality of first flow channels which are independent of each other, and the plurality of first flow channels include a second refrigerant flow channel and a first water-cooled flow channel, and the first refrigerant flow channel is used to receive the refrigerant flowing out of the second refrigerant flow channel. In this way, the second refrigerant flow channel is used to receive the refrigerant flowing out of the compressor, and the first refrigerant flow channel is used to deliver the refrigerant to the compressor. Without loss of generality, if the plate heat exchanger is configured as a condenser. In this way, the refrigerant flowing out of the second refrigerant flow channel will pass through the evaporator, and then flow into the first refrigerant flow channel through the evaporator. In addition, the first refrigerant flow channel and the plurality of first flow channels are independent of each other, which enables the floor-type heat exchanger to suppress the mixing of heat between the first refrigerant flow channel and the second refrigerant flow channel, so that the first refrigerant flow channel can be used as a passage for the refrigerant flowing out of the evaporator to the compressor. Since the plate heat exchanger is provided with the first refrigerant flow channel, the volume utilization rate of the plate heat exchanger is improved, which is conducive to reducing the length of the connecting pipe and reducing the space occupied by the vehicle thermal management device. If the plate heat exchanger is configured as an evaporator. In this way, the refrigerant flowing out of the second refrigerant flow path will pass through the condenser, and then flow into the first refrigerant flow path through the condenser. In addition, the first refrigerant flow channel and the multiple first flow channels are independent of each other, which allows the plate heat exchanger to suppress the mixing of heat between the first refrigerant flow channel and the second refrigerant flow channel, so that the second refrigerant flow channel serves as a passage for the refrigerant flowing out of the compressor to the condenser. Since the plate heat exchanger has the second refrigerant flow channel, this improves the volume utilization rate of the plate heat exchanger, which is conducive to reducing the length of the connecting pipe and reducing the space occupied by the vehicle thermal management device. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying creative work.

[0024] Figure 1 It is a partial structural schematic diagram of an embodiment of the vehicle thermal management device of the utility model;

[0025] Figure 2 for Figure 1 Exploded diagram of

[0026] Figure 3 for Figure 2A schematic structural diagram of a first heat exchange plate of a medium plate heat exchanger;

[0027] Figure 4 for Figure 3 A schematic diagram of the structure of the second plate heat exchanger with a portion of the heat exchanger plate hidden, wherein the arrows in the figure indicate the flow direction of the refrigerant in the flow area of ​​the third refrigerant flow channel;

[0028] Figure 5 for Figure 3 A schematic diagram of the structure of the second plate heat exchanger in which part of the heat exchange plate is hidden, wherein the arrows in the figure indicate the flow direction of the liquid in the flow area of ​​the third water-cooling channel.

[0029] Description of Figure Numbers:

[0030] Label name Label name 120 Reservoir 740 Cavity 130 Expansion valve 731 Sealing area 200 Plate Heat Exchanger 800 The first guide rib 310 First entry port 900 Bending part 320 First outlet 910 Second plate heat exchanger 511 Second entry port 920 Second flow channel 512 Second outlet 930 The third refrigerant flow channel 521 The third entrance 940 Second water cooling channel 522 The third outlet 950 Second flow area 530 The first water cooling channel 960 Second diversion section 610 First flow area 970 Second confluence section 700 First heat exchange plate 980 Second guide rib 710 First plate body 990 Second heat exchange plate 720 first plate convex part 991 Second plate body 730 Separator 992 second plate convex part

[0031] The realization of the purpose, functional features and advantages of the utility model will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0032] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0033] It should be noted that all directional indications in the embodiments of the present invention (such as up, down, left, right, front, back, etc.) are only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0034] In the present invention, unless otherwise clearly specified and limited, the terms "connection", "fixation", etc. should be understood in a broad sense. For example, "fixation" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediate medium, or abutment, and it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0035] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the utility model, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In addition, the meaning of "and / or" appearing in the full text includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme that satisfies both A and B. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the utility model.

[0036] At present, a vehicle includes a vehicle thermal management system, which includes a vehicle thermal management device, which includes a compressor, a condenser, an expansion valve, an evaporator, and a connecting pipe, and the connecting pipe is used to conduct the compressor, the condenser, the expansion valve and the evaporator. However, the length of the connecting pipe is long, which will cause the space occupied by the vehicle thermal management device to be large. To this end, the utility model provides a plate heat exchanger, which is intended to help reduce the space occupied by the vehicle thermal management device.

[0037] Reference Figures 1 to 3In one embodiment of the utility model, the plate heat exchanger 200 is provided with a first refrigerant flow channel and a plurality of first flow channels which are independent of each other, the plurality of first flow channels include a second refrigerant flow channel and a first water-cooled flow channel 530, and the first refrigerant flow channel is used to receive the refrigerant flowing out of the second refrigerant flow channel. In this way, the second refrigerant flow path is used to receive the refrigerant flowing out of the compressor, and the first refrigerant flow path is used to deliver the refrigerant to the compressor. Without loss of generality, if the plate heat exchanger 200 is configured as a condenser. In this way, the refrigerant flowing out of the second refrigerant flow path will pass through the evaporator, and then flow into the first refrigerant flow path through the evaporator. In addition, the first refrigerant flow channel and the plurality of first flow channels are independent of each other, which enables the floor-type heat exchanger 200 to suppress the mixing of heat between the first refrigerant flow channel and the second refrigerant flow channel, so that the first refrigerant flow channel can be used as a passage for the refrigerant flowing out of the evaporator to the compressor. Since the plate heat exchanger 200 has the first refrigerant flow channel, the volume utilization rate of the plate heat exchanger 200 is improved, which is conducive to reducing the length of the connecting pipe and reducing the space occupied by the vehicle thermal management device. If the plate heat exchanger 200 is configured as an evaporator. In this way, the refrigerant flowing out of the second refrigerant flow channel will pass through the condenser and then flow into the first refrigerant flow channel through the condenser. In addition, the first refrigerant flow channel and the multiple first flow channels are independent of each other, which allows the plate heat exchanger 200 to suppress heat mixing between the first refrigerant flow channel and the second refrigerant flow channel, so that the second refrigerant flow channel serves as a passage for the refrigerant flowing out of the compressor to the condenser. Since the plate heat exchanger 200 has the second refrigerant flow channel, the volume utilization rate of the plate heat exchanger 200 is improved, which is beneficial to reducing the length of the connecting pipe and reducing the space occupied by the vehicle thermal management device.

[0038] It should be noted that when the plate heat exchanger 200 is used as a condenser, the first water-cooling channel 530 mainly exchanges heat with the second refrigerant channel. When the plate heat exchanger 200 is used as an evaporator, the first water-cooling channel 530 mainly exchanges heat with the first refrigerant channel.

[0039] This article takes the application of the plate heat exchanger 200 in a vehicle thermal management device as an example for introduction. The vehicle thermal management system includes a compressor, an evaporator, an expansion valve 130 and a condenser. Without loss of generality, the plate heat exchanger 200 can be configured as a condenser. In this way, the compressor, the condenser, the expansion valve 130 and the evaporator can be arranged in sequence along the thickness direction of the plate heat exchanger 200, and the refrigerant flowing out of the second refrigerant flow channel can enter the evaporator from the expansion valve 130, and the refrigerant flowing out of the evaporator can flow back to the compressor from the first refrigerant flow channel. The arrangement of the compressor, the evaporator, the expansion valve 130, and the condenser makes the refrigerant flow path between the compressor and the evaporator shorter, which is conducive to reducing the amount of refrigerant added and improving the safety of the vehicle thermal management device. Further, the vehicle thermal management system also includes a liquid reservoir 120 arranged between the evaporator and the condenser, the expansion valve 130 is arranged in the liquid reservoir 120, and the evaporator, the liquid reservoir 120, and the condenser are stacked.

[0040] It can be understood that the plate heat exchanger 200 can also be configured as an evaporator, so that the compressor, evaporator, expansion valve 130, and condenser can be arranged in sequence along the thickness direction of the plate heat exchanger 200. In this way, the refrigerant flowing out of the compressor can enter the condenser through the second refrigerant flow channel, and the refrigerant flowing out of the condenser can enter the first refrigerant flow channel through the expansion valve 130, and flow back to the compressor through the first refrigerant flow channel. The arrangement of the compressor, evaporator, expansion valve 130, and condenser makes the refrigerant flow path between the compressor and the evaporator shorter, which is conducive to reducing the amount of refrigerant added and improving the safety of the vehicle thermal management device.

[0041] Optionally, in one embodiment, the first refrigerant flow channel extends along the thickness direction of the plate heat exchanger 200. In this way, when the plate heat exchanger 200 is configured as a condenser and the layout direction of the vehicle thermal management device is that the compressor, condenser, expansion valve 130 and evaporator are arranged in sequence along the thickness direction of the plate heat exchanger 200, the first refrigerant flow channel is parallel to the thickness direction of the plate heat exchanger 200, so that the length of the first refrigerant flow channel is shorter, and the refrigerant in the first refrigerant flow channel can quickly pass through the plate heat exchanger 200 to reduce the heat exchange between the refrigerant in the first refrigerant flow channel and the first flow channel. However, the present design is not limited to this. In other embodiments, the second refrigerant flow channel extends along the thickness direction of the plate heat exchanger 200. In this way, when the plate heat exchanger 200 is configured as an evaporator and the layout direction of the vehicle thermal management device is that the compressor, evaporator, expansion valve 130, and condenser are arranged in sequence along the thickness direction of the plate heat exchanger 200, the second refrigerant flow channel is parallel to the thickness direction of the plate heat exchanger 200, so that the length of the second refrigerant flow channel is shorter. The refrigerant in the second refrigerant flow channel can pass through the plate heat exchanger 200 quickly to reduce the refrigerant in the second refrigerant flow channel and the first refrigerant flow channel and the first water-cooled flow channel 530 for heat exchange. Alternatively, it can also be set according to actual needs, for example, the first refrigerant flow channel is set in a bent manner or the two ports of the first refrigerant flow channel are set on the same side of the plate heat exchanger 200.

[0042] Optionally, in one embodiment, the first flow channel includes a first flow area 610, the plate heat exchanger 200 includes a plurality of first heat exchange plates 700 stacked, a cavity 740 is limited between two adjacent first heat exchange plates 700, the cavity 740 includes the first flow area 610, and the first refrigerant flow channel is arranged through the plurality of first heat exchange plates 700 and is arranged outside the first flow area 610. In this way, the first flow area 610 increases the heat exchange area of ​​the first flow channel, which is conducive to improving the heat exchange efficiency of the second refrigerant flow channel and the first water-cooled flow channel 530. Since the first refrigerant flow channel is arranged outside the first flow area 610, this can reduce the heat exchange efficiency between the first refrigerant flow channel and the first flow area 610. However, the present design is not limited to this. In other embodiments, the first flow area 610 is arranged around the first refrigerant flow channel.

[0043] Optionally, in one embodiment, the first flow channel further includes a first confluence section having one end of the first flow channel, and a first diversion section having the other end of the first flow channel, the first flow region 610 connects the first confluence section and the first diversion section, a plurality of first flow regions 610 are provided, and the first confluence section and the first diversion section are respectively provided on a plurality of first heat exchange plates 700. It can be understood that the liquid enters from the first diversion section, and the liquid entering from the first diversion section enters the plurality of first flow regions 610 respectively, and the liquid flowing out of the plurality of first flow regions 610 will be gathered in the first confluence section, and finally leave the plate heat exchanger 200. In this way, each first flow region 610 of different first flow channels is fully utilized, so that the liquid in the first flow region 610 maintains a high heat exchange efficiency. However, the present design is not limited thereto. In other embodiments, the first flow channel further includes an input section having one end of the first flow channel and an output section having the other end of the first flow channel. The liquid flowing into the input section will sequentially pass through multiple first flow areas 610 and flow to the output section, and finally flow out of the plate heat exchanger 200 from the output section.

[0044] Optionally, in one embodiment, the first heat exchange plate 700 includes a first plate body 710 and a first plate protrusion 720 disposed on the outer periphery of the first plate body 710, the first plate body 710 is used to limit the first flow area 610, and the first refrigerant flow channel is disposed in the first plate protrusion 720. In this way, the first refrigerant flow channel can be prevented from occupying the area of ​​the first flow area 610, so that the area of ​​the first flow area 610 is larger, and the heat exchange efficiency of the first flow channel is higher.

[0045] Optionally, in one embodiment, the first plate protrusion 720 is gradually contracted in the protruding direction relative to the first plate body 710. In this way, the first plate protrusion 720 has a certain structural strength and the volume of the first plate protrusion 720 is not too large. However, the present design is not limited thereto. In other embodiments, the first plate protrusion 720 is gradually expanded in the protruding direction relative to the first plate body 710.

[0046] Optionally, in one embodiment, the first plate protrusion 720 is provided with a separation rib 730, and the separation rib 730 is used to separate the cavity 740 into a sealing area 731 and a first flow area 610, and the first refrigerant flow channel is arranged in the sealing area 731. In this way, under the separation of the separation rib 730, the refrigerant flowing in the first flow area 610 of the first flow channel will not flow to the sealing area 731, and the first refrigerant flow channel is arranged in the sealing area 731 to reduce the heat exchange between the first refrigerant flow channel and the first flow area 610.

[0047] Optionally, in one embodiment, a first flow guide rib 800 is provided in the first flow region 610, so that the first flow region 610 is bent, thereby extending the length of the first flow channel and making the heat exchange of the first flow channel more sufficient.

[0048] Optionally, in one embodiment, one end of the first guide rib 800 is used to limit the bending portion 900 of the first flow area 610. In the length direction of the first guide rib 800, the first guide rib 800 has a first end and a second end relative to each other, and the second end is used to limit the bending portion 900 of the first flow area 610 as an example. The refrigerant can flow from the first end to the second end, and when flowing to the second end, the refrigerant flows from the second end to the first end. In this way, the flow trajectory of the refrigerant in the first flow area 610 has a bending portion 900, for example, the flow trajectory is V-shaped or U-shaped. This extends the length of the first flow channel, so that the heat exchange of the first flow channel is more sufficient. In addition, for the flow trajectory in the first flow area 610 extending in a certain straight direction and having the same length, this solution can make the length and width values ​​of the plate heat exchanger 200 closer, thereby facilitating the layout of the vehicle thermal management device. However, the present design is not limited thereto, and in other embodiments, the first guide rib 800 may be arranged according to actual needs, as long as the length of the first flow channel can be extended, and no limitation is made here.

[0049] Optionally, in one embodiment, the second refrigerant flow channel is configured as a condensation flow channel. In this way, the plate heat exchanger 200 is configured as a condenser. However, the present design is not limited thereto. In other embodiments, the first refrigerant flow channel is configured as an evaporation flow channel. In this way, the plate heat exchanger 200 is configured as an evaporator.

[0050] Optionally, in one embodiment, the plurality of first flow channels also include a subcooling flow channel. In this way, the plate heat exchanger 200 integrates a subcooler, so that the integration of the vehicle thermal management device is relatively high, which is conducive to reducing the space occupied by the vehicle thermal management device. Further, in one embodiment, the second refrigerant flow channel is configured as a condensing flow channel, the plate heat exchanger 200 has a first side and a second side relative to each other, the first refrigerant flow channel has a first inlet end 310 arranged on the second side and a first outlet end 320 arranged on the first side, the second refrigerant flow channel has a second inlet end 511 arranged on the first side and a second outlet end 512 arranged on the second side, and the subcooling flow channel has a third inlet end 521 and a third outlet end 522 both arranged on the second side.

[0051] Refer to Figure 4 and Figure 5 The utility model also proposes a vehicle thermal management device, which includes a first plate heat exchanger and a second plate heat exchanger 910. The first plate heat exchanger is configured as the aforementioned plate heat exchanger 200. The second plate heat exchanger 910 is provided with a plurality of second flow channels 920. The plurality of second flow channels 920 include a third refrigerant flow channel 930 and a second water-cooled flow channel 940. The first refrigerant flow channel receives the refrigerant flowing out of the second refrigerant flow channel through the third refrigerant flow channel 930. The specific structure of the plate heat exchanger 200 refers to the above embodiment. Since the present vehicle thermal management device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be described one by one here. It can be understood that one of the first plate heat exchanger and the second plate heat exchanger is configured as a condenser, and the other is configured as an evaporator. In one embodiment, the vehicle thermal management device also includes an expansion valve 130, a compressor, and a liquid reservoir 120. The layout of the evaporator, condenser, expansion valve 130, compressor, and liquid reservoir 120 has been mentioned above and will not be elaborated here.

[0052] Optionally, in one embodiment, the second flow channel 920 includes a second flow area 950, and the second plate heat exchanger 910 includes a plurality of second heat exchange plates 990 stacked in layers, and the second flow area 950 is limited between two adjacent second heat exchange plates 990. In this way, the second flow area 950 increases the heat exchange area of ​​the second flow channel 920, which is conducive to improving the heat exchange efficiency of the third refrigerant flow channel 930 and the third water-cooled flow channel, respectively. Further, in one embodiment, the flow area of ​​the third refrigerant flow channel 930 and the flow area of ​​the third water-cooled flow channel are alternately arranged in the thickness direction of the second plate heat exchanger 910 to improve the heat exchange efficiency between the third refrigerant flow channel 930 and the third water-cooled flow channel. However, the present design is not limited to this. In other embodiments, the second flow channel 920 extends along the thickness direction of the second plate heat exchanger 910.

[0053] Optionally, in one embodiment, the second heat exchange plate 990 includes a second plate body 991 and a second plate protrusion 992 provided on the outer periphery of the second plate body 991, and the second flow area 950 flows through the second plate body 991 and the second plate protrusion 992 of the corresponding two adjacent second heat exchange plates 990. In this way, the second plate protrusion 992 extends the length of the second flow channel 920, so that the length of the second flow channel 920 is longer, so that the liquid in the second flow channel 920 can be more fully heat exchanged. It should be pointed out that the two adjacent second heat exchange plates 990 corresponding to the second flow area 950 refer to the two heat exchange plates that limit the second flow area 950. However, the present design is not limited to this. In other embodiments, the second heat exchange plate 990 can also be set in other shapes, which are not limited here.

[0054] Optionally, in one embodiment, the second flow channel 920 also includes a second confluence section 970 having one end of the second flow channel 920, and a second diversion section 960 having the other end of the second flow channel 920, the second flow area 950 connects the second confluence section 970 and the second diversion section 960, the second flow area 950 is provided with multiple second diversion sections 960, the second diversion sections 960 are penetrated through the second plate body 991, the second confluence section 970 is penetrated through multiple second plate protrusions 992, in the thickness direction of the first plate heat exchanger, the second plate heat exchanger 910 is arranged in parallel with the first plate heat exchanger, a port of the second diversion section 960 is arranged on the side of the second plate heat exchanger 910 close to the first plate heat exchanger, a port of the second confluence section 970 is arranged on the side of the second plate heat exchanger 910 close to the first plate heat exchanger, the second diversion section 960 is communicated with the second refrigerant flow channel, and the second confluence section 970 is communicated with the first refrigerant flow channel.

[0055] It can be understood that the refrigerant in the second refrigerant flow channel can flow through the second diverter section 960, multiple second flow areas 950, and the second confluence section 970 of the third refrigerant flow channel 930 in sequence, and finally flow into the first refrigerant flow channel from the second confluence section 970 of the third refrigerant flow channel 930. Since one port of the second diverter section 960 is arranged on the side of the second plate heat exchanger 910 close to the first plate heat exchanger, and one port of the second confluence section 970 is arranged on the side of the second plate heat exchanger 910 close to the first plate heat exchanger, the flow path of the refrigerant is shorter, which is beneficial to reducing the length of the connecting pipe and reducing the space occupied by the vehicle thermal management device.

[0056] In addition, since the multiple second flow areas 950 are respectively connected to the second branch section 960 and the second confluence section 970, each second flow area 950 of different second flow channels 920 is fully utilized, so that the liquid in the second flow area 950 always maintains a high heat exchange efficiency.

[0057] Optionally, in one embodiment, when the first heat exchange plate 700 of the first plate heat exchanger includes a first plate protrusion 720 and a first plate body 710, the first plate protrusion 720 and the second plate protrusion 992 can be arranged opposite to each other in the thickness direction of the first plate heat exchanger, and the first plate body 710 and the second plate body 991 can be arranged opposite to each other.

[0058] Optionally, in the protruding direction of the second plate protrusion 992 relative to the second plate body 991, the second plate protrusion 992 is gradually set. In this way, the second plate protrusion 992 has a certain structural strength and the volume of the second plate protrusion 992 is not too large. However, the present design is not limited to this. In other embodiments, in the protruding direction of the second plate protrusion 992 relative to the second plate body 991, the first plate protrusion is gradually set.

[0059] Optionally, in one embodiment, a second guide rib 980 is provided in the second flow region 950, so that the second flow region 950 is bent, thereby extending the length of the second flow channel 920 and making the heat exchange of the second flow channel 920 more sufficient.

[0060] Optionally, in one embodiment, the liquid flow direction in the second flow area 950 of the third refrigerant flow channel 930 is different from the liquid flow direction in the second flow area 950 of the second water-cooled flow channel 940. It can be understood that the second flow area 950 of the third refrigerant flow channel 930 will be adjacent to the second flow area 950 of the second water-cooled flow channel 940. In this way, the liquid in the second flow area 950 of the third refrigerant flow channel 930 can always exchange heat with the liquid with a lower temperature in the second flow area 950 of the second water-cooled flow channel 940. In this way, the refrigerant in the second flow area 950 of the third refrigerant flow channel 930 can exchange heat more fully. However, the present design is not limited to this. In other embodiments, the liquid flow direction in the second flow area 950 of the third refrigerant flow channel 930 is the same as the liquid flow direction in the second flow area 950 of the second water-cooled flow channel 940.

[0061] The present utility model also proposes a vehicle thermal management system, which includes the aforementioned vehicle thermal management device. The specific structure of the vehicle thermal management device refers to the above-mentioned embodiment. Since the vehicle thermal management system adopts all the technical solutions of all the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, which will not be repeated here one by one.

[0062] The utility model also proposes a vehicle, which includes the aforementioned vehicle thermal management system. The specific structure of the vehicle thermal management system refers to the above-mentioned embodiment. Since the vehicle adopts all the technical solutions of all the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, which will not be repeated here one by one.

[0063] The above description is only an optional embodiment of the present invention, and does not limit the patent scope of the present invention. All equivalent structural changes made by using the contents of the present invention specification and drawings under the inventive concept of the present invention, or directly / indirectly applied in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A plate heat exchanger, characterized in that: The plate heat exchanger is provided with a mutually independent first refrigerant flow channel and a plurality of first flow channels, the plurality of first flow channels include a second refrigerant flow channel and a first water-cooling flow channel, and the first refrigerant flow channel is used to receive the refrigerant flowing out from the second refrigerant flow channel.

2. The plate heat exchanger according to claim 1, characterized in that: The first refrigerant flow channel extends along a thickness direction of the plate heat exchanger.

3. The plate heat exchanger according to claim 2, characterized in that: The first flow channel includes a first flow area, the plate heat exchanger includes a plurality of first heat exchange plates stacked together, a cavity is defined between two adjacent first heat exchange plates, the cavity includes the first flow area, and the first refrigerant flow channel passes through the plurality of first heat exchange plates and is arranged outside the first flow area.

4. The plate heat exchanger according to claim 3, characterized in that: The first heat exchange plate includes a first plate body and a first plate protrusion arranged on the outer periphery of the first plate body, the first plate body is used to limit the first flow area, and the first refrigerant flow channel is penetrated through the first plate protrusion.

5. The plate heat exchanger according to claim 4, characterized in that: In a protruding direction of the first plate protrusion relative to the first plate body, the first plate protrusion is arranged to be tapered.

6. The plate heat exchanger according to claim 4, characterized in that: The first plate protrusion is provided with a partition rib, and the partition rib is used to separate the cavity into a sealing area and the first flow area, and the first refrigerant flow channel is arranged through the sealing area.

7. The plate heat exchanger according to claim 3, characterized in that: A first guide rib is disposed in the first flow region so that the first flow region is bent.

8. The plate heat exchanger according to claim 1, characterized in that: The second refrigerant flow channel is configured as a condensation flow channel; And / or, the plurality of first flow channels further include a supercooling flow channel.

9. A thermal management device for a vehicle, characterized in that: It includes a first plate heat exchanger and a second plate heat exchanger, the first plate heat exchanger is configured as the plate heat exchanger according to any one of claims 1 to 8, the second plate heat exchanger is provided with a plurality of second flow channels, the plurality of second flow channels include a third refrigerant flow channel and a second water-cooled flow channel, the first refrigerant flow channel receives the refrigerant flowing out of the second refrigerant flow channel through the third refrigerant flow channel.

10. The vehicle thermal management device according to claim 9, characterized in that: The second flow channel includes a second flow area, and the second plate heat exchanger includes a plurality of second heat exchange plates stacked together, and the second flow area is defined between two adjacent second heat exchange plates.

11. The vehicle thermal management device according to claim 10, characterized in that: The second heat exchange plate includes a second plate body and a second plate protrusion disposed on the outer periphery of the second plate body, and the second flow region flows through the second plate bodies and the second plate protrusions of two corresponding adjacent second heat exchange plates.

12. The vehicle thermal management device according to claim 11, characterized in that: The second flow channel also includes a second confluence section having one end of the second flow channel, and a second diversion section having the other end of the second flow channel. The second flow area connects the second confluence section and the second diversion section. The second flow area is provided in plurality. The second diversion section is penetrated through the second plate body, and the second confluence section is penetrated through a plurality of second plate protrusions. In the thickness direction of the first plate heat exchanger, the second plate heat exchanger is arranged in parallel with the first plate heat exchanger. A port of the second diversion section is arranged on a side of the second plate heat exchanger close to the first plate heat exchanger, and a port of the second confluence section is arranged on a side of the second plate heat exchanger close to the first plate heat exchanger. The second diversion section is communicated with the second refrigerant flow channel, and the second confluence section is communicated with the first refrigerant flow channel.

13. The vehicle thermal management device according to claim 12, characterized in that: In a protruding direction of the second plate protrusion relative to the second plate body, the second plate protrusion is arranged to be tapered.

14. The vehicle thermal management device according to claim 10, characterized in that: A second guide rib is disposed in the second flow region so that the second flow region is bent.

15. The vehicle thermal management device according to claim 10, characterized in that: A liquid flow direction in the second flow region of the third refrigerant flow channel is different from a liquid flow direction in the second flow region of the second water-cooling flow channel.

16. A thermal management system for a vehicle, characterized in that: It comprises the vehicle thermal management device as described in any one of claims 9 to 15.

17. A vehicle, characterized in that: It includes the vehicle thermal management system as claimed in claim 16.

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