Heat exchanger and energy storage equipment

Abstract

The invention provides a heat exchanger and energy storage equipment. The heat exchanger comprises at least one condensation plate heat exchanger, a plurality of evaporation plate heat exchangers and a refrigerant base plate, and each evaporation plate heat exchanger and each condensation plate heat exchanger are arranged on the same side of the refrigerant base plate in the first direction. The side face, facing the refrigerant base plate, of each condensation plate exchanger comprises a condensation refrigerant outlet, and the side face, facing the refrigerant base plate, of each evaporation plate exchanger comprises an evaporation refrigerant inlet. The refrigerant base plate comprises a confluence flow channel and at least one flow dividing structure, each flow dividing structure comprises a plurality of flow dividing flow channels, one end of the confluence flow channel is used for being communicated with a condensation refrigerant outlet of each condensation plate heat exchanger, and the other end of the confluence flow channel is used for being communicated with one end of each flow dividing flow channel. And the other end of each shunting flow channel is used for communicating with an evaporation refrigerant inlet of one evaporation plate heat exchanger. According to the heat exchanger provided by the embodiment of the invention, the shunting structure is arranged on the refrigerant substrate, so that the occupied space of the heat exchanger is reduced, and the assembly of the heat exchanger is simplified.

Description

Technical Field

[0001] The present application relates to the technical field of heat exchange, and particularly to a heat exchanger and an energy storage device. Background Art

[0002] With the vigorous development of new energy technologies, energy storage technologies have also received increasing attention. Generally, it is necessary to set a heat exchanger in an energy storage device to heat or cool the energy storage device to ensure the performance and safety of the energy storage device. However, the existing heat exchangers are large in volume and relatively complex in assembly, which is not conducive to the layout of the internal space of the energy storage device. Summary of the Invention

[0003] The present application provides a heat exchanger and an energy storage device. The heat exchanger is small in volume and simple in assembly, which is conducive to the layout of the internal space of the energy storage device.

[0004] In a first aspect, a heat exchanger is provided. The heat exchanger includes at least one condensation plate heat exchanger, a plurality of evaporation plate heat exchangers, and a refrigerant base plate. Along a first direction, each condensation plate heat exchanger and each evaporation plate heat exchanger are arranged on the same side of the refrigerant base plate. The side of each condensation plate heat exchanger facing the refrigerant base plate includes a condensation refrigerant outlet, and the side of each evaporation plate heat exchanger facing the refrigerant base plate includes an evaporation refrigerant inlet. Wherein, the refrigerant base plate includes a converging flow channel and at least one set of shunt structures. Each set of shunt structures includes a plurality of shunt flow channels. One end of the converging flow channel is used to communicate with the condensation refrigerant outlet of each condensation plate heat exchanger, the other end of the converging flow channel is used to communicate with one end of each shunt flow channel, and the other end of each shunt flow channel is used to communicate with the evaporation refrigerant inlet of an evaporation plate heat exchanger.

[0005] In the heat exchanger provided by the embodiments of the present application, by arranging the shunt structure on the refrigerant base plate, the shunt problem of multiple evaporation plate heat exchangers can be solved. Furthermore, the occupied space of the heat exchanger is reduced, and the assembly of the heat exchanger is simplified.

[0006] In addition, by arranging the shunt structure on the refrigerant base plate, on the one hand, there is no need to consider the sealing problem between the shunt structure and the refrigerant base plate, reducing the production cost of the heat exchanger. On the other hand, when the heat exchanger is in a vibrating environment, it will not affect the shunt structure, ensuring the heat exchange performance of the heat exchanger.

[0007] In one implementation, the refrigerant base plate includes two base plates arranged opposite to each other along the first direction. The side of one base plate facing the other base plate includes a converging groove and at least one set of shunt grooves. Each set of shunt grooves includes a plurality of shunt grooves. The converging groove communicates with each shunt groove. The converging groove and the side of the other base plate facing the one base plate form a converging flow channel, and each shunt groove and the side of the other base plate facing the one base plate form a shunt flow channel.

[0008] By machining a groove on one of the two substrates, the groove on one substrate and the surface of the other substrate can form a corresponding flow channel, thereby simplifying the machining process and assembly process of the flow channel.

[0009] In one implementation, the cross section of each flow-dividing groove is arc-shaped, so that the flow resistance of the refrigerant in each flow-dividing channel is smaller and the pressure drop is also smaller.

[0010] In one implementation, each group of diversion structures also includes a diverter flow channel, which is used to connect the converging flow channel with multiple diverter flow channels. The cross-sectional area of ​​the diverter flow channel first decreases and then increases along the direction in which the diverter flow channel and each diverter flow channel are arranged.

[0011] After the refrigerant enters the flow channel of the diverter, it will first shrink slightly, the speed will increase and the pressure will decrease, and the speed will reach the maximum value when it reaches the narrowest part of the flow channel of the diverter. Then it will slow down and expand the pressure, and the refrigerant will be sprayed into each diverter flow channel like a nozzle. Because the pressure is relatively high, the refrigerant flow rate is relatively fast, so the refrigerant flowing into each diverter flow channel will be more uniform.

[0012] In one implementation, the cross-sectional area of ​​each branch flow channel is smaller than the cross-sectional area of ​​the branch head flow channel. In this way, the refrigerant in the branch head flow channel can be branched into multiple branch flow channels.

[0013] In one implementation, the angle between the axial direction of the flow channel of the splitter and the second direction is θ 1 , 30°≤θ 1 ≤30°, and the second direction is perpendicular to the first direction. In this way, when the heat exchanger is placed along the second direction, the problem of uneven flow distribution caused by gravity can be avoided.

[0014] In one implementation, each group of diversion structures further includes a guide baffle, which is used to be embedded in the converging flow channel. A gap is provided at the connection between the guide baffle and each diversion flow channel. The guide baffle includes a guide flow channel, which is used to connect the converging flow channel with the gap.

[0015] After the refrigerant enters the diversion channel of the diversion baffle, it will first shrink slightly, and the speed will increase while the pressure will decrease. When it reaches the junction of the outlet of the diversion channel and the gap, the speed will reach the maximum value. Then the speed will slow down and expand. Like a nozzle, the refrigerant will be sprayed into each diversion channel. Because the pressure is relatively high, the refrigerant flow rate is relatively fast, so the refrigerant flowing into each diversion channel will be more uniform.

[0016] In one implementation, the cross-sectional area of ​​each diverting flow channel is smaller than the cross-sectional area of ​​the converging flow channel; the distance between the diverting baffle and the end of the converging flow channel away from the diverting baffle is greater than the gap. In this way, the diverting flow channel in the diverting baffle can divert the refrigerant in the converging flow channel into each diverting flow channel.

[0017] In one implementation, the angle between the axial direction of the diversion flow channel and the second direction is θ 2 , 30° ≤ θ 2 ≤ 30°. In this way, when the heat exchanger is placed in the second direction, the problem of uneven flow division caused by gravity can be avoided.

[0018] In one implementation, the lengths of each diversion flow channel are equal, and the cross-sectional areas of each diversion flow channel are the same. Alternatively, the length of one diversion flow channel is less than that of another diversion flow channel, and the cross-sectional area of one diversion flow channel is less than that of another diversion flow channel. In this way, the pressure drops of each diversion flow channel can be ensured to be as identical as possible.

[0019] In one implementation, the angle between the axial direction of the diversion flow channel and the second direction is θ 3 , 30° ≤ θ 3 ≤ 30°. In this way, when the heat exchanger is placed in the second direction, the problem of uneven flow division caused by gravity can be avoided.

[0020] In one implementation, the refrigerant substrate includes two sides arranged opposite to each other in the second direction, and the distance from the connection of each diversion flow channel to the confluence flow channel to one of the two sides is equal.

[0021] When the heat exchanger is placed in the second direction, the connections of each diversion flow channel to the confluence flow channel are arranged in alignment in the third direction. In this way, the refrigerant in the confluence flow channel can almost reach each diversion flow channel simultaneously, making the distribution of the refrigerant in each diversion flow channel relatively uniform.

[0022] In one implementation, the heat exchanger further includes at least one throttling element, and each throttling element is distributed in the confluence flow channel, and each throttling element is used to control the flow rate flowing from the confluence flow channel into a set of diversion structures.

[0023] In one implementation, the throttling element is a throttling flow channel, and the throttling flow channel is used to connect the confluence flow channel and a set of diversion structures. The cross-sectional area of the connection of each throttling flow channel to the confluence flow channel is equal to the cross-sectional area of the connection of each throttling flow channel to a set of diversion structures. By processing the throttling flow channel on the refrigerant substrate, the throttling effect of the refrigerant in the confluence flow channel is realized, reducing the production cost of the heat exchanger.

[0024] In one implementation, the cross-sectional area of the middle part of each throttling flow channel is respectively smaller than the cross-sectional area of the connection of each throttling flow channel to the confluence flow channel and the cross-sectional area of the connection of each throttling flow channel to a set of diversion structures. In this way, after the refrigerant flows into the throttling flow channel, it first slightly contracts, the speed increases, and the pressure decreases. When it reaches the narrowest part in the middle of the throttling flow channel, it reaches the maximum speed, and then decelerates and expands the pressure. Like a nozzle, the refrigerant is sprayed into a set of diversion structures.

[0025] In a second aspect, there is provided an energy storage device, which includes at least one battery cell and a heat exchanger as described in the first aspect and any one of the possible implementation manners of the first aspect. The heat exchanger is used for performing heat exchange with each battery cell.

[0026] Since the energy storage device includes the heat exchanger described in the first aspect, it is beneficial to the layout of the internal space of the energy storage device.

[0027] In a third aspect, there is provided a photovoltaic power generation system, including: a photovoltaic panel, a photovoltaic inverter, and the energy storage device as described in the second aspect. The photovoltaic panel is used for converting solar energy into electrical energy, each battery cell is used for storing the electrical energy from the photovoltaic panel, the photovoltaic inverter is used for converting the direct current from the photovoltaic panel into alternating current, and the heat exchanger is further used for performing heat exchange with the photovoltaic inverter.

[0028] Since the photovoltaic power generation system includes the heat exchanger described in the first aspect, it is beneficial to the layout of the internal space of the photovoltaic power generation system.

[0029] In a fourth aspect, there is provided an electric vehicle, which includes a powertrain and the energy storage device as described in the second aspect. The energy storage device is used for supplying power to the powertrain.

[0030] Since the electric vehicle includes the heat exchanger described in the first aspect, it is beneficial to the layout of the internal space of the electric vehicle. Description of the Drawings

[0031] Figure 1 It is a schematic diagram of a photovoltaic power generation system provided by an embodiment of the present application.

[0032] Figure 2 It is a schematic diagram of an electric vehicle provided by an embodiment of the present application.

[0033] Figure 3 It is a three-dimensional structure schematic diagram of a heat exchanger provided by an embodiment of the present application.

[0034] Figure 4 It is another three-dimensional structure schematic diagram of a heat exchanger provided by an embodiment of the present application.

[0035] Figure 5 It is a three-dimensional structure schematic diagram of a condensing plate heat exchanger provided by an embodiment of the present application.

[0036] Figure 6 It is a three-dimensional structure schematic diagram of an evaporative plate heat exchanger provided by an embodiment of the present application.

[0037] Figure 7 It is a two-dimensional structure schematic diagram of one substrate in a refrigerant substrate provided by an embodiment of the present application.

[0038] Figure 8Schematic diagram of the two-dimensional structure of another substrate in a refrigerant substrate provided by an embodiment of the present application.

[0039] Figure 9 Schematic diagram of the two-dimensional structure of one substrate in another refrigerant substrate provided by an embodiment of the present application.

[0040] Figure 10 Schematic diagram of the two-dimensional structure of another substrate in another refrigerant substrate provided by an embodiment of the present application.

[0041] Figure 11 Schematic diagram of the two-dimensional structure of one substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0042] Figure 12 Schematic diagram of the two-dimensional structure of one substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0043] Figure 13 Schematic diagram of the two-dimensional structure of one substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0044] Figure 14 Schematic diagram of the two-dimensional structure of another substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0045] Figure 15 Schematic diagram of the three-dimensional structure of one substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0046] Figure 16 For Figure 15 Enlarged schematic diagram of part A in the other substrate shown.

[0047] Figure 17 Schematic diagram of the three-dimensional structure of one substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0048] Figure 18 For Figure 17 Enlarged schematic diagram of part B in the other substrate shown.

[0049] Figure 19 Schematic diagram of the two-dimensional structure of one substrate in yet another refrigerant substrate provided by an embodiment of the present application.

[0050] Figure 20 Schematic diagram of the two-dimensional structure of a refrigerant substrate provided by an embodiment of the present application. Detailed implementation manners

[0051] Next, the technical solutions in the embodiments of the present application will be described with reference to the accompanying drawings.

[0052] In the description of the embodiments of the present application, unless otherwise specified, " / " means "or". For example, A / B may mean A or B. The "and / or" herein is merely a description of the association relationship of associated objects, indicating that there can be three relationships. For example, A and / or B may mean: A exists alone, A and B exist simultaneously, and B exists alone.

[0053] In the embodiments of the present application, prefix words such as "first", "second", and "third" are only used to distinguish different described objects, and have no restrictive effect on the position, order, priority, quantity, or content of the described objects, etc. The use of ordinal numbers and other prefix words for distinguishing described objects in the embodiments of the present application does not constitute a limitation on the described objects. The statement of the described objects refers to the description in the context of the claims or embodiments, and should not constitute an unnecessary limitation due to the use of such prefix words. In addition, in the description of this embodiment, unless otherwise specified, "a plurality of" means two or more.

[0054] The orientation or positional relationship indicated by terms such as "upper", "lower", "left", "right", "front", "rear", "top", "bottom", "inner", and "outer" in the embodiments of the present application is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the present application.

[0055] The reference to "some embodiments" and the like described in this specification means that in one or more embodiments of the present application, specific features, structures, or characteristics described in connection with that embodiment are included. Thus, statements such as "in some embodiments" that appear in different places in this specification do not necessarily refer to the same embodiment, but mean "one or more but not all embodiments", unless otherwise specifically emphasized in other ways. The terms "comprising", "including", "having", and their variants all mean "including but not limited to", unless otherwise specifically emphasized in other ways.

[0056] The "vertical" involved in the present application is not strictly vertical, but within the allowable error range. The "parallel" is not strictly parallel, but within the allowable error range.

[0057] In the embodiments of the present application, the same reference numeral represents the same component or the same part. In the embodiments of the present application, for multiple identical parts, only one of the parts may be marked with a reference numeral in the drawings. The reference numeral is also applicable to other identical parts or components. In addition, the dimensions and sizes of the parts shown in the drawings are only exemplary.

[0058] An embodiment of the present application provides a heat exchanger, which includes at least one condensation plate heat exchanger, a plurality of evaporation plate heat exchangers, and a refrigerant substrate. Along a first direction, each evaporation plate heat exchanger and each condensation plate heat exchanger are arranged on the same side of the refrigerant substrate. The side of each condensation plate heat exchanger facing the refrigerant substrate includes a condensation refrigerant outlet, and the side of each evaporation plate heat exchanger facing the refrigerant substrate includes an evaporation refrigerant inlet. Among them, the refrigerant substrate includes a converging flow channel and at least one set of diverging structures, and each set of diverging structures includes a plurality of diverging flow channels. One end of the converging flow channel is used to communicate with the condensation refrigerant outlets of each condensation plate heat exchanger, the other end of the converging flow channel is used to communicate with one end of each diverging flow channel, and the other end of each diverging flow channel is used to communicate with the evaporation refrigerant inlet of an evaporation plate heat exchanger.

[0059] In the heat exchanger provided by the embodiment of the present application, by arranging the diverging structure on the refrigerant substrate, the diverging problem of a plurality of evaporation plate heat exchangers can be solved. Furthermore, the occupied space of the heat exchanger is reduced, and the assembly of the heat exchanger is simplified.

[0060] In addition, by arranging the diverging structure on the refrigerant substrate, on the one hand, there is no need to consider the sealing problem between the diverging structure and the refrigerant substrate, which reduces the production cost of the heat exchanger. On the other hand, when the heat exchanger is in a vibrating environment, it will not affect the diverging structure, ensuring the heat exchange performance of the heat exchanger.

[0061] An embodiment of the present application also provides a photovoltaic power generation system. The following will be combined with Figure 1 to describe in detail the photovoltaic power generation system provided by the embodiment of the present application.

[0062] Figure 1 is a schematic diagram of the photovoltaic power generation system provided by the embodiment of the present application. As Figure 1 shown, the photovoltaic power generation system provided by the embodiment of the present application includes one or more photovoltaic modules 1, a photovoltaic inverter 2, a box-type substation 3, a three-phase AC power grid 4, a first DC cable 5, a first AC cable 6, a second AC cable 7, an energy storage device 8, and a second DC cable 9. Among them, one or more photovoltaic modules 1 are connected to the photovoltaic inverter 2 through the first DC cable 5, and the connection relationship between the photovoltaic modules 1 and the photovoltaic inverter 2 can be a multi-to-one connection. The energy storage device 8 is connected to the photovoltaic inverter 2 through the second DC cable 5. The photovoltaic inverter 2 converts the direct current output by the photovoltaic modules 1 or the energy storage device 8 into alternating current, and the AC side of the photovoltaic inverter 2 is connected to the box-type substation 3 through the first AC cable 6. The box-type substation 3 is connected to the three-phase AC power grid 4 through the second AC cable 7. In this way, the alternating current output by the photovoltaic inverter 2 flows into the three-phase AC power grid 4 after passing through the box-type substation 3.

[0063] This photovoltaic power generation system is a power generation system that utilizes the photovoltaic effect of semiconductor materials to convert solar radiant energy into electrical energy. The photovoltaic power generation system provided by the embodiments of this application can empower electric vehicles. The electric vehicles include pure electric vehicles, hybrid electric vehicles, range extended electric vehicles, plug-in hybrid electric vehicles, or new energy vehicles, etc. Among them, pure electric vehicles are also called pure electric vehicle / battery electric vehicle, or simply pure EV / battery EV for short. Hybrid electric vehicles are also called hybrid electric vehicle, or simply HEV for short. Range extended electric vehicles are also called range extended electric vehicle, or simply REEV for short. Plug-in hybrid electric vehicles are also called plug-in hybrid electric vehicle, or simply PHEV for short. New energy vehicles are also called new energy vehicle, or simply NEV for short.

[0064] The photovoltaic module 1 can also be called a photovoltaic array, which includes multiple photovoltaic strings. Among them, photovoltaic is also called photovoltaic, or simply PV for short. String is also called string. Each photovoltaic string includes multiple serially connected photovoltaic panels. The photovoltaic panels are used to convert light energy into electrical energy. The electrical energy generated by the photovoltaic panels is DC electricity. The voltage at both ends of the photovoltaic string is equal to the sum of the voltages generated by the multiple photovoltaic panels. The output power of the photovoltaic module can represent the electrical energy output by the photovoltaic module per unit time.

[0065] In the photovoltaic power generation system, the area of each photovoltaic module 1 is generally fixed. When the light intensity of the light remains unchanged, the larger the angle between the light irradiating on the photovoltaic module 1 and the plane where the photovoltaic module 1 is located, that is, the smaller the incident angle of the light irradiating on the photovoltaic module 1, the more electrical energy the photovoltaic module 1 outputs. When the light is perpendicularly irradiated on the photovoltaic module 1, that is, the angle between the light and the plane where the photovoltaic module 1 is located is 90°, when reaching the maximum value, the power output by the photovoltaic module 1 reaches the maximum.

[0066] Each photovoltaic inverter 2 is used to convert the input DC into AC, that is, to perform DC-AC conversion. The photovoltaic inverter 2 can also be called a DC-AC converter.

[0067] The box-type substation 3 is simply called box substation 3. It is a compact distribution equipment that arranges high-voltage switchgear, distribution transformers, and low-voltage distribution devices according to a certain wiring scheme. For example, the box substation 3 integrates equipment such as low-voltage cabinets, transformers, ring main units, and auxiliary power supplies into a container to provide a highly integrated power transformation and distribution solution for the medium-voltage grid connection scenario of photovoltaic ground power stations.

[0068] The energy storage device 8 includes a thermal management system 80 and at least one battery cell 81, and the thermal management system 80 is used for heat exchange with each battery cell 81.

[0069] When the photovoltaic power generation system includes a plurality of photovoltaic modules 1, the photovoltaic power generation system further includes a busbar box, which is used for collecting the direct current generated by the plurality of photovoltaic modules 1 and inputting the collected output into the photovoltaic inverter 2.

[0070] The embodiment of the present application also provides an electric vehicle. The following combines Figure 2 to describe in detail the electric vehicle provided by the embodiment of the present application.

[0071] Figure 2 is a schematic diagram of the electric vehicle provided by the embodiment of the present application. As Figure 2 shown, the electric vehicle provided by the embodiment of the present application includes an energy storage device 10, wheels 20, and one or more powertrains 30. Among them, the powertrain 30 is used to receive power supply from the energy storage device 10 and drive the wheels 20, and the powertrain 30 is used to convert electrical energy into mechanical energy.

[0072] The energy storage device 10 includes a thermal management system 11 and at least one battery cell 12, and the thermal management system 80 is used for heat exchange with each battery cell 12. The powertrain 30 includes a motor controller 31, a motor 32, and a reducer 33. The energy storage device 10 is connected to the motor controller 31 of the powertrain 30. The motor controller 31 receives the direct current transmitted by the battery cell 12 through a DC input interface, and the motor controller 31 converts the direct current into alternating current and then transmits it to the terminal of the winding of the motor 32 through an AC output interface to control the start or stop, forward or reverse rotation, increase or decrease of the rotation speed, increase or decrease of the driving torque, increase or decrease of the braking torque, etc. of the motor 32. The output end of the motor shaft transmits power to the wheels 20 of the electric vehicle through the reducer 33 to provide power for the wheels 20.

[0073] As Figure 1 shown, the thermal management system 80 or Figure 2 shown, the thermal management system 11 both include heat exchangers. The following, combines Figures 3 to 20 to describe in detail the specific structure of the heat exchanger provided by the embodiment of the present application.

[0074] As Figure 3 and Figure 4As shown, the heat exchanger 100 includes at least one condensation plate heat exchanger 110, at least one evaporation plate heat exchanger 120, and a refrigerant substrate 130. Each condensation plate heat exchanger 110 and each evaporation plate heat exchanger 120 are arranged on the same side of the refrigerant substrate along the first direction. In embodiments where the heat exchanger 100 includes a plurality of condensation plate heat exchangers 110 and a plurality of evaporation plate heat exchangers 120, the high integration of the heat exchange plate heat exchangers (condensation plate heat exchanger 110 and evaporation plate heat exchanger 120) enables the heat exchanger 100 to achieve a high heat exchange capacity.

[0075] Each condensation plate heat exchanger 110 includes a plurality of condensation substrates, which are spaced apart along the thickness direction of the condensation substrates. As Figure 5 shown, the side surface 111 of each condensation plate heat exchanger 110 includes a condensation refrigerant inlet A 11 and a condensation refrigerant outlet A 12 , and the condensation refrigerant inlet A 11 and the condensation refrigerant outlet A 12 are arranged along the second direction. In some embodiments, for the convenience of connecting the condensation refrigerant inlet A 11 and the condensation refrigerant outlet A 12 of each condensation plate heat exchanger 110 to the condensation refrigerant flow channels on the refrigerant substrate 130, the condensation refrigerant inlet A 11 and the condensation refrigerant outlet A 12 are arranged in alignment along the second direction, that is, the condensation refrigerant inlet A 11 and the condensation refrigerant outlet A 12 are almost on a straight line along the second direction. In some embodiments, to prevent heat leakage between the refrigerant substrate 130 and each condensation plate heat exchanger 110, there is a gap between the side surface 111 of each condensation plate heat exchanger 110 and the side surface of the refrigerant substrate 130 facing the condensation plate heat exchanger 110. For example, this gap can be 1 mm to 10 mm.

[0076] Each evaporation plate heat exchanger 120 includes a plurality of evaporation substrates, which are spaced apart along the thickness direction of the evaporation substrates. As Figure 6 shown, the side surface 121 of each evaporation plate heat exchanger 120 includes an evaporation refrigerant inlet A 21 and an evaporation refrigerant outlet A 22 , and the evaporation refrigerant inlet A 21 and the evaporation refrigerant outlet A 22 are arranged along the second direction. In some embodiments, for the convenience of connecting the evaporation refrigerant inlet A 21 and the evaporation refrigerant outlet A 22 of each evaporation plate heat exchanger 120 to the evaporation refrigerant flow channels on the refrigerant substrate 130, the evaporation refrigerant inlet A 21 and the evaporation refrigerant outlet A 22 are arranged in alignment along the second direction, that is, the evaporation refrigerant inlet A 21 and the evaporation refrigerant outlet A 22Almost in a straight line along the second direction. In some embodiments, in order to prevent heat leakage between the refrigerant substrate 130 and each evaporation heat exchanger 120, there is a gap between the side surface 111 of each condensation heat exchanger 110 and the side surface of the refrigerant substrate 130 facing the condensation heat exchanger 110. For example, this gap can be 1 mm to 10 mm.

[0077] As Figure 7 , Figure 9 , Figures 11 to 13 shown, the side surface of the refrigerant substrate 130 facing the condensation heat exchanger 110 includes two groups of condensation holes E 11 -E 12 and two groups of evaporation holes E 21 -E 22 . The interior of the refrigerant substrate 130 includes two condensation refrigerant flow channels L1-L2, two evaporation refrigerant flow channels L3-L4, and a confluence flow channel H. Among them, along the first direction, each condensation hole E 11 in one group of condensation holes overlaps with the projection of a condensation refrigerant flow channel L1, and each condensation hole E 12 in the other group of condensation holes overlaps with the projection of another condensation refrigerant flow channel L2. Each evaporation hole E 21 in one group of evaporation holes overlaps with the projection of an evaporation refrigerant flow channel L3, and each evaporation hole E 22 in the other group of evaporation holes overlaps with the projection of another evaporation refrigerant flow channel L4.

[0078] Each group of condensation holes includes at least one condensation hole. Each condensation hole E 11 in one group of condensation holes is used to connect a condensation refrigerant flow channel L1 with the condensation refrigerant inlet A 11 of a condensation heat exchanger 110, and each condensation hole E 12 in the other group of condensation holes is used to connect another condensation refrigerant flow channel L2 with the condensation refrigerant outlet A 12 of a condensation heat exchanger 110. In this way, multiple condensation heat exchangers 110 are connected in parallel to each condensation refrigerant flow channel.

[0079] Each group of evaporation holes includes at least one evaporation hole. Each evaporation hole E 21 in one group of evaporation holes is used to connect an evaporation refrigerant flow channel L3 with the evaporation refrigerant inlet A 21 of an evaporation heat exchanger 120, and each evaporation hole E 22 in the other group of evaporation holes is used to connect another evaporation refrigerant flow channel L4 with the evaporation refrigerant outlet A 22 of an evaporation heat exchanger 120. In this way, multiple evaporation heat exchangers 120 are connected in parallel to each evaporation refrigerant flow channel.

[0080] The converging flow channel H is used to connect another condensed refrigerant flow channel L2 and an evaporating refrigerant flow channel L3. In this way, the refrigerant in a condensed refrigerant flow channel L1 can flow along the condensed refrigerant inlet A of each condenser heat exchanger 110 11 and flow into each condenser heat exchanger 110, and flow out along the condensed refrigerant outlet A of each condenser heat exchanger 110 12 and flow into another condensed refrigerant flow channel L2. The refrigerant flows along the converging flow channel H connected to another condensed refrigerant flow channel L2 and into each evaporating refrigerant flow channel L3. The refrigerant in an evaporating refrigerant flow channel L3 can flow along the evaporating refrigerant inlet A of each evaporator heat exchanger 120 21 and flow into each evaporator heat exchanger 120, and flow out along the evaporating refrigerant outlet A of each evaporator heat exchanger 120 22 and flow into another evaporating refrigerant flow channel L4.

[0081] Among them, the number of each group of condensation holes is equal to the number of condenser heat exchangers 110. The number of each group of evaporation holes is equal to the number of evaporator heat exchangers 120. Figures 3 to 18 In the example, the heat exchanger 100 includes three condenser heat exchangers 110 and three evaporator heat exchangers 120, which should not constitute a limitation to this application.

[0082] In some embodiments, as Figure 3 shown, a plurality of condenser heat exchangers 110 and a plurality of evaporator heat exchangers 120 are arranged at intervals along the third direction. In other words, a plurality of condenser heat exchangers 110 are located on the left side, and a plurality of evaporator heat exchangers 120 are located on the right side. Further, a plurality of condenser heat exchangers 110 are arranged at intervals along the second direction, and a plurality of evaporator heat exchangers 120 are arranged at intervals along the second direction. In other embodiments, as Figure 4 shown, a plurality of condenser heat exchangers 110 and a plurality of evaporator heat exchangers 120 are arranged at intervals along the second direction. In other words, a plurality of condenser heat exchangers 110 are located above, and a plurality of evaporator heat exchangers 120 are located below, or a plurality of condenser heat exchangers 110 are located below, and a plurality of evaporator heat exchangers 120 are located above. In this way, according to the deployment method of a plurality of condenser heat exchangers 110 and a plurality of evaporator heat exchangers 120, the condensed refrigerant flow channels connected to each condenser heat exchanger 110 on the refrigerant substrate 130 are arranged on the same side, and the evaporating refrigerant flow channels connected to each evaporator heat exchanger 120 on the refrigerant substrate 130 are arranged on the other side. In this way, it is convenient for the assembly of the condenser heat exchanger 110 and the evaporator heat exchanger 120, as well as the design of the refrigerant flow channels. In addition, in the embodiment where a plurality of condenser heat exchangers 110 are located above and a plurality of evaporator heat exchangers 120 are located below, it is beneficial to reduce the pressure drop caused by gravity of the gas-liquid two-phase refrigerant and improve the performance of the heat exchanger 100.

[0083] It should be noted that the first direction involved in the embodiments of the present application can be understood as: the front-back direction of the heat exchanger 100, the thickness direction of the condensation substrate, the thickness direction of the evaporation substrate, or the thickness direction of the refrigerant substrate 130. The second direction can be understood as the up-down direction of the heat exchanger 100 or the length direction of the refrigerant substrate 130. The third direction can be understood as the left-right direction of the heat exchanger 100 or the width direction of the refrigerant substrate 130.

[0084] In addition, the upgraded refrigerant in the present application can also be called a refrigerant, a refrigerating agent, or a refrigerant, and is a medium substance by which various heat engines complete energy conversion. These substances usually increase power through reversible phase changes (such as gas-liquid phase changes).

[0085] In the present application, the refrigerant is a working fluid used to transfer heat energy and produce a refrigerating effect. Or rather, the refrigerant can transfer heat through evaporation and condensation. The refrigerant can be a substance that is easy to absorb heat and turn into a gas, and is also easy to release heat and turn into a liquid. For example, the refrigerant is an intermediate substance in the refrigeration process. It first receives the cold energy of the refrigerant and cools down, and then cools other substances to be cooled. By way of example and not limitation, in the present application, the refrigerant can include ammonia, air, water, brine, chlorofluorocarbons (or rather, chlorofluorocarbons), etc. In the present application, when the gaseous refrigerant is pressurized, it releases heat and turns into a liquid, and when the high-pressure liquid is depressurized and turns into a gas, it will absorb heat.

[0086] The positional relationship between a condensation refrigerant flow channel L1, another condensation refrigerant flow channel L2, an evaporation refrigerant flow channel L3, and another evaporation refrigerant flow channel L4 is related to the positional relationship between the condensation plate heat exchanger 110 and the evaporation plate heat exchanger 120. In this way, the deployment of the pipelines on the multiple condensation plate heat exchangers 110 that communicate with the two condensation refrigerant flow channels L1-L2 and the pipelines on the multiple evaporation plate heat exchangers 120 that communicate with the two evaporation refrigerant flow channels L3-L4 is relatively regular, simplifying the assembly process between the multiple condensation plate heat exchangers 110 and the two condensation refrigerant flow channels L1-L2 and the assembly process between the multiple evaporation plate heat exchangers 110 and the two evaporation refrigerant flow channels L3-L4.

[0087] In one example, as Figure 3 shown, the multiple condensation plate heat exchangers 110 and the multiple evaporation plate heat exchangers 120 are arranged at intervals in the third direction, as Figure 7 , Figure 9 , Figure 11 , Figure 12 shown, a condensation refrigerant flow channel L1, another condensation refrigerant flow channel L2, an evaporation refrigerant flow channel L3, and another evaporation refrigerant flow channel L4 are arranged in the third direction.

[0088] In another example, as Figure 4 shown, the multiple condensation plate heat exchangers 110 and the multiple evaporation plate heat exchangers 120 are arranged in the second direction, asFigure 13 As shown, a condensing refrigerant flow channel L1, another condensing refrigerant flow channel L2, an evaporating refrigerant flow channel L3, and another evaporating refrigerant flow channel L4 are arranged in the second direction.

[0089] It should be noted that the arrangement of multiple condensing plate heat exchangers 110 and multiple evaporating plate heat exchangers 120 in the second direction can be understood as: all the condensing plate heat exchangers 110 and all the evaporating plate heat exchangers 120 of the heat exchanger 100 are arranged in the second direction. If the number of multiple condensing plate heat exchangers 110 is odd or the number of multiple evaporating plate heat exchangers 120 is odd, such as Figure 4 As shown, there may be a situation where a condensing plate 110 and an evaporating plate heat exchanger 120 are arranged adjacent to each other in the third direction. However, all the condensing plate heat exchangers 110 and all the evaporating plate heat exchangers 120 of the heat exchanger 100 are arranged in the second direction. That is, in this example, multiple condensing plate heat exchangers 110 and multiple evaporating plate heat exchangers 120 can also be understood as being arranged in the second direction.

[0090] The extending direction of a condensing refrigerant flow channel L1, the extending direction of another condensing refrigerant flow channel L2, the arrangement direction of multiple condensing holes E of a group of condensing holes 11 and the arrangement direction of multiple condensing holes E of another group of condensing holes 12 are respectively related to the positional relationship of multiple condensing plate heat exchangers 110. For example, as Figure 3 shown, multiple condensing plate heat exchangers 110 are arranged in the second direction. As Figure 7 , Figure 9 , Figure 11 , Figure 12 shown, the extending direction of a condensing refrigerant flow channel L1, the extending direction of another condensing refrigerant flow channel L2, the arrangement direction of multiple condensing holes E11 of a group of condensing holes, and the arrangement direction of multiple condensing holes E12 of another group of condensing holes are respectively along the second direction.

[0091] The extending direction of an evaporating refrigerant flow channel L3, the extending direction of another evaporating refrigerant flow channel L4, the arrangement direction of multiple evaporating holes E of a group of evaporating holes 21 and the arrangement direction of multiple evaporating holes E of another group of evaporating holes 22 are respectively related to the positional relationship of multiple evaporating plate heat exchangers 120. For example, as Figure 3 shown, multiple evaporating plate heat exchangers 120 are arranged in the second direction. As Figure 7 , Figure 9 , Figure 11 , Figure 12 shown, the extending direction of an evaporating refrigerant flow channel L3, the extending direction of another evaporating refrigerant flow channel L4, the arrangement direction of multiple evaporating holes E of a group of evaporating holes 21 and the arrangement direction of multiple evaporating holes E of another group of evaporating holes 22 are respectively along the second direction.

[0092] It should be noted that, as Figure 7 , Figure 9 , Figures 11 to 13 shown, taking the shortest path where a condensation refrigerant flow channel L1 connects a plurality of condensation holes E of a group of condensation holes as an example, taking the shortest path where another condensation refrigerant flow channel L2 connects a plurality of condensation holes E of another group of condensation holes as an example, taking the shortest path where an evaporation refrigerant flow channel L3 connects a plurality of condensation holes E of a group of evaporation holes as an example, and taking the shortest path where another evaporation refrigerant flow channel L4 connects a plurality of evaporation holes E of another group of evaporation holes as an example, it should not constitute a limitation to this application. 11 For example, taking the shortest path where a condensation refrigerant flow channel L1 connects a plurality of condensation holes E of a group of condensation holes as an example, taking the shortest path where another condensation refrigerant flow channel L2 connects a plurality of condensation holes E of another group of condensation holes as an example, taking the shortest path where an evaporation refrigerant flow channel L3 connects a plurality of condensation holes E of a group of evaporation holes as an example, and taking the shortest path where another evaporation refrigerant flow channel L4 connects a plurality of evaporation holes E of another group of evaporation holes as an example, it should not constitute a limitation to this application. 12 For example, taking the shortest path where a condensation refrigerant flow channel L1 connects a plurality of condensation holes E of a group of condensation holes as an example, taking the shortest path where another condensation refrigerant flow channel L2 connects a plurality of condensation holes E of another group of condensation holes as an example, taking the shortest path where an evaporation refrigerant flow channel L3 connects a plurality of condensation holes E of a group of evaporation holes as an example, and taking the shortest path where another evaporation refrigerant flow channel L4 connects a plurality of evaporation holes E of another group of evaporation holes as an example, it should not constitute a limitation to this application. 21 For example, taking the shortest path where a condensation refrigerant flow channel L1 connects a plurality of condensation holes E of a group of condensation holes as an example, taking the shortest path where another condensation refrigerant flow channel L2 connects a plurality of condensation holes E of another group of condensation holes as an example, taking the shortest path where an evaporation refrigerant flow channel L3 connects a plurality of condensation holes E of a group of evaporation holes as an example, and taking the shortest path where another evaporation refrigerant flow channel L4 connects a plurality of evaporation holes E of another group of evaporation holes as an example, it should not constitute a limitation to this application. 22 For example, taking the shortest path where a condensation refrigerant flow channel L1 connects a plurality of condensation holes E of a group of condensation holes as an example, taking the shortest path where another condensation refrigerant flow channel L2 connects a plurality of condensation holes E of another group of condensation holes as an example, taking the shortest path where an evaporation refrigerant flow channel L3 connects a plurality of condensation holes E of a group of evaporation holes as an example, and taking the shortest path where another evaporation refrigerant flow channel L4 connects a plurality of evaporation holes E of another group of evaporation holes as an example, it should not constitute a limitation to this application.

[0093] In some embodiments, the included angle between the line connecting two adjacent condensation holes in two groups of condensation holes and the second direction is α 1 , 0° ≤ α 1 ≤ 45°. In this way, it can ensure that the flow path of the refrigerant in each condensation refrigerant flow channel in the two condensation refrigerant flow channels L1 - L2 is the shortest and the flow resistance is relatively low.

[0094] For example, as Figures 7 to 12 shown, all the condensation holes E of the two groups of condensation holes 11 -E 12 are almost on a straight line along the second direction, that is, the included angle between the line connecting two adjacent condensation holes in the two groups of condensation holes and the second direction is approximately 0°.

[0095] In some embodiments, the included angle between the line connecting two adjacent condensation holes in two groups of evaporation holes and the second direction is α 2 , 0° ≤ α 2 ≤ 45°. In this way, it can ensure that the flow path of the refrigerant in each evaporation refrigerant flow channel in the two evaporation refrigerant flow channels L3 - L4 is the shortest and the flow resistance is relatively low.

[0096] For example, as Figures 7 to 12 shown, all the evaporation holes E of the two groups of evaporation holes 21 -E 22 are almost on a straight line along the second direction, that is, the included angle between the line connecting two adjacent condensation holes in the two groups of evaporation holes and the second direction is approximately 0°.

[0097] It should be noted that the included angle between the line involved in the embodiments of this application and the second direction can be understood as the included angle between the line and the second direction along the clockwise or counterclockwise direction.

[0098] In some embodiments, another condensing refrigerant flow channel L2 and an evaporating refrigerant flow channel L3 are respectively disposed between a condensing refrigerant flow channel L1 and another evaporating refrigerant flow channel L4. In this way, the condensing refrigerant flow channel L1 for transmitting high-temperature and high-pressure refrigerant and another evaporating refrigerant flow channel L4 are arranged on one side of the edge of the condensing substrate 130, reducing the heat leakage loss with the refrigerant in another condensing refrigerant flow channel L2 and the refrigerant in an evaporating refrigerant flow channel L3.

[0099] In some embodiments, the cross-sectional areas of the two evaporating refrigerant flow channels are respectively larger than those of the two condensing refrigerant flow channels. Since most of the refrigerant flowing in the condensing refrigerant flow channel is in a liquid state and most of the refrigerant flowing in the evaporating refrigerant flow channel is in a gaseous state, and the flow resistance of the liquid refrigerant is smaller than that of the gaseous refrigerant, therefore, compared with the cross-sectional area of the condensing refrigerant flow channel, the cross-sectional area of the evaporating refrigerant flow channel is set larger, and thus the pressure drop of the refrigerant flowing in the evaporating refrigerant flow channel can be increased.

[0100] In some embodiments, the cross-sectional area of a condensing refrigerant flow channel L1 is larger than that of another condensing refrigerant flow channel L2. Since more liquid refrigerant flows in another condensing refrigerant flow channel L2 than in a condensing refrigerant flow channel L1, the flow resistance of the refrigerant flowing in another condensing refrigerant flow channel L2 is smaller than that of the refrigerant flowing in a condensing refrigerant flow channel L1. Therefore, compared with the cross-sectional area of another condensing refrigerant flow channel L2, the cross-sectional area of a condensing refrigerant flow channel L1 is set larger, and thus the pressure drop of the refrigerant flowing in a condensing refrigerant flow channel L1 can be increased.

[0101] In some embodiments, the cross-sectional area of another evaporating refrigerant flow channel L4 is larger than that of an evaporating refrigerant flow channel L3. Since less liquid refrigerant flows in another evaporating refrigerant flow channel L4 than in an evaporating refrigerant flow channel L3, the flow resistance of the refrigerant flowing in another evaporating refrigerant flow channel L4 is greater than that of the refrigerant flowing in an evaporating refrigerant flow channel L3. Therefore, compared with the cross-sectional area of an evaporating refrigerant flow channel L3, the cross-sectional area of another evaporating refrigerant flow channel L4 is set larger, and thus the pressure drop of the refrigerant flowing in another evaporating refrigerant flow channel L4 can be increased.

[0102] It should be noted that the cross-section of the flow channel involved in this application can be understood as a section perpendicular to the extension direction of the flow channel.

[0103] In some embodiments, as Figure 7 、 Figure 9 、 Figures 11 to 13 shown, the heat exchanger 100 further includes at least one throttling element, each throttling element is distributed in the confluence flow channel H, and each throttling element is used to control the flow rate flowing from the confluence flow channel H into an evaporating refrigerant flow channel L3.

[0104] Exemplarily, the projection of the throttling element along the first direction is arranged between the total projection of a plurality of condensation plate exchangers 110 and the total projection of a plurality of evaporation substrates 120.

[0105] In some embodiments, the throttling element realizes the throttling effect through a device. For example, the throttling element can be a device capable of realizing the throttling effect such as an electronic expansion valve (EEV), a thermostatic expansion valve, etc. In this embodiment, as Figure 7 , Figure 9 , Figures 11 to 13 shown, the refrigerant substrate 130 further includes a throttling hole T for embedding the throttling element.

[0106] In some embodiments, the throttling element realizes the throttling effect through a structural design. The throttling element is a throttling flow channel for connecting the confluence flow channel H and an evaporation refrigerant flow channel L3. The cross-sectional area of each throttling flow channel at the connection with the confluence flow channel H is equal to the cross-sectional area of each throttling flow channel at the connection with an evaporation refrigerant flow channel L3.

[0107] In some embodiments, the cross-sectional area of the middle part of each throttling flow channel is respectively smaller than the cross-sectional area of each throttling flow channel at the connection with the confluence flow channel H and the cross-sectional area of each throttling flow channel at the connection with an evaporation refrigerant flow channel L3.

[0108] In some embodiments, along the arrangement direction of the inlet and outlet of the throttling flow channel, the cross-sectional area of the throttling flow channel first decreases and then increases. The connection of the throttling flow channel with the confluence flow channel can be called the inlet of the throttling flow channel, and the connection of the throttling flow channel with an evaporation refrigerant flow channel L3 can be called the outlet of the throttling flow channel.

[0109] In some embodiments, as Figure 7 , Figure 9 , Figures 11 to 13 shown, a notch G can also be provided in at least one of the following: between two condensation refrigerant flow channels, between two evaporation refrigerant flow channels, between another condensation refrigerant flow channel and an evaporation refrigerant flow channel, between the inlet and outlet of the throttling element. In this way, the notch G forms an air isolation, which can reduce the heat leakage of the refrigerant in each refrigerant flow channel through the refrigerant substrate 130, realizes the low heat leakage of the heat exchanger 100, and ensures the high heat exchange performance of the heat exchanger 100. In addition, by providing the notch G only between two condensation refrigerant flow channels and / or between two evaporation refrigerant flow channels, that is, only setting the notch G in the substrate area that contributes the most to the heat leakage effect, not only simplifies the process steps, but also ensures the structural strength of the refrigerant substrate 130.

[0110] Exemplarily, the notch G can be formed by cutting the refrigerant substrate 130, and it can be a straight line or a curve.

[0111] In some embodiments, the length of the incision G is greater than or equal to the length of each refrigerant flow channel, and the length of the incision G is greater than the width of the throttling element T. In this way, the heat insulation effect between the refrigerant flow channels can be increased.

[0112] Exemplarily, the incision G can be a groove, a gap or a scratch.

[0113] In some embodiments, the refrigerant substrate 130 further includes a heat insulation material, and the heat insulation material is distributed in at least one of the following: between two condensing refrigerant flow channels, between two evaporating refrigerant flow channels, between another condensing refrigerant flow channel and an evaporating refrigerant flow channel, and between the inlet and outlet of the throttling element. In this way, the heat insulation material can reduce the heat transfer of the refrigerant in each refrigerant flow channel through the refrigerant substrate 130, realizing low heat leakage of the heat exchanger 100 and ensuring the high heat exchange performance of the heat exchanger 100.

[0114] The embodiment of the present application also provides a flow splitting structure, which is arranged on the refrigerant substrate 130 and is used to split the refrigerant in all the condensing plate exchangers 110 and flow it into each evaporating plate exchanger 120. In this way, since the flow splitting structure is directly arranged on the refrigerant substrate 130, not only the occupied space of the heat exchanger 100 is reduced, the assembly of the heat exchanger 100 is simplified, but also the sealing problem between the flow splitting structure and the refrigerant substrate does not need to be considered. In addition, when the heat exchanger 100 is in a vibrating environment, it will not affect the flow splitting structure.

[0115] It should be noted that in the embodiment where the flow splitting structure is arranged on the refrigerant substrate 130, the above-mentioned one condensing refrigerant flow channel L1, another condensing refrigerant flow channel L2, one evaporating refrigerant flow channel L3, and another evaporating refrigerant flow channel L4 can also be arranged on the refrigerant substrate 130, and the above-mentioned one condensing refrigerant flow channel L1, another condensing refrigerant flow channel L2, one evaporating refrigerant flow channel L3, and another evaporating refrigerant flow channel L4 can also be realized by an external pipeline. The embodiment of the present application does not make any limitation on this.

[0116] The refrigerant substrate 130 includes at least one set of flow splitting structures, and each set of flow splitting structures includes a plurality of flow splitting channels. One end of the converging flow channel H is used to communicate with the condensing refrigerant outlet A of each condensing plate exchanger 110 12 , the other end of the converging flow channel H is used to communicate with one end of each flow splitting channel of each set of flow splitting structures, and the other end of each flow splitting channel is used to communicate with the evaporating refrigerant inlet A of an evaporating plate exchanger 120 21 , that is, the number of flow splitting channels is equal to the number of evaporating plate exchangers 120.

[0117] In one example, the cross-sectional shape of the flow splitting channel is a polygon such as a square. In another example, the cross-sectional shape of the flow splitting channel is circular, arc-shaped or elliptical. In this way, the resistance of the refrigerant in the flow splitting channel will be a little smaller and the pressure drop will also be a little smaller.

[0118] In some embodiments, the flow splitting structure further includes a flow splitting head structure, which can make the refrigerant in each flow splitting channel relatively uniform.

[0119] Such as Figure 15 , Figure 16 and Figure 19 shown, each set of flow splitting structures further includes a flow splitting head channel D1. The flow splitting head channel D1 is used to connect the converging channel H and a plurality of flow splitting channels M. Along the direction of arrangement of the flow splitting head channel D1 and each flow splitting channel M, the cross-sectional area of the flow splitting head channel D1 first decreases and then increases. In this way, after the refrigerant enters the flow splitting head channel D1, it first slightly contracts, the velocity increases and the pressure decreases. When it reaches the narrowest part of the flow splitting head channel D1, it reaches the maximum velocity. After that, it decelerates and expands the pressure. Like a nozzle, the refrigerant sprays into each flow splitting channel D1. Because the pressure is relatively high and the refrigerant flow velocity is relatively fast, the refrigerant flowing into each flow splitting channel will be relatively uniform.

[0120] In some embodiments, the cross-sectional area of each flow splitting channel M is respectively smaller than the cross-sectional area of the flow splitting head channel D1.

[0121] In some embodiments, the included angle between the axial direction of the flow splitting head channel D1 and the second direction is θ 1 , 0° ≤ θ 1 ≤ 30°. In this way, when the heat exchanger 100 is placed along the second direction, uneven flow splitting caused by gravity can be avoided.

[0122] It should be understood that the axial direction of the flow splitting head channel D1 can be understood as the extension direction of the flow splitting head channel.

[0123] It should be noted that the included angle between the axial direction and the second direction involved in the embodiments of the present application can be understood as the included angle between the axial direction and the second direction along the clockwise or counterclockwise direction.

[0124] Such as Figure 17 and Figure 18 shown, each set of flow splitting structures further includes a guiding partition D2. The guiding partition D2 is used to be embedded in the converging channel H. There is a gap B at the connection between the guiding partition D2 and each flow splitting channel. Among them, the guiding partition D2 includes a guiding channel d. The guiding channel d is used to connect the converging channel H and the gap B. In this way, after the refrigerant enters the guiding channel d of the guiding partition D2, it first slightly contracts, the velocity increases, and the pressure decreases. When it reaches the junction of the outlet of the guiding channel d and the gap B, it reaches the maximum velocity. After that, it decelerates and expands the pressure. Like a nozzle, the refrigerant sprays into each flow splitting channel. Because the pressure is relatively high and the refrigerant flow velocity is relatively fast, the refrigerant flowing into each flow splitting channel is relatively uniform.

[0125] Exemplarily, the guide channel d may be a through hole penetrating the guide baffle D2 along the extension direction of the converging channel H. Exemplarily, the cross-sectional area of ​​the through hole may be in any shape such as a circle, an ellipse, or a square.

[0126] In some embodiments, the distance between the guide baffle D2 and the end of the converging flow channel H away from the guide baffle D2 is greater than the gap. That is, the guide baffle D2 is disposed close to each diverting flow channel M.

[0127] In some embodiments, the angle between the axial direction of the flow guide channel d and the second direction is θ 2 , 0°≤θ 2 ≤30°. In this way, when the heat exchanger 100 is placed along the second direction, uneven flow distribution caused by gravity can be avoided.

[0128] In some embodiments, the cross-sectional area of ​​each branch flow channel is smaller than the cross-sectional area of ​​the converging flow channel and the cross-sectional area of ​​each refrigerant flow channel.

[0129] In one example, the length of each branch flow channel is approximately equal, and the cross-sectional area of ​​each branch flow channel is approximately the same. In another example, the length of each branch flow channel and the cross-sectional area of ​​each branch flow channel are approximately positively correlated. For example, the length of one branch flow channel is smaller than the length of another branch flow channel, and the cross-sectional area of ​​one branch flow channel is smaller than the cross-sectional area of ​​another branch flow channel. In this way, the pressure drop of each branch flow channel can be ensured to be as equal as possible.

[0130] In some embodiments, the angle between the axial direction of the flow diversion channel and the second direction is θ 3 , 0°≤θ 3 ≤30°. In this way, when the heat exchanger 100 is placed along the second direction, uneven flow distribution caused by gravity can be avoided.

[0131] In some embodiments, the refrigerant substrate 130 includes two side surfaces arranged opposite to each other along the second direction, and the connection between each branch flow channel and the converging flow channel is equidistant from one of the two side surfaces. That is, the connection between each branch flow channel M and the converging flow channel H is aligned along the third direction, so that the refrigerant of the converging flow channel H can reach each branch flow channel almost at the same time, so that the distribution of the refrigerant in each branch flow channel is relatively uniform.

[0132] In some embodiments, the number of condensing plates 110 included in the heat exchanger 100 is equal to the number of evaporating plates 120 .

[0133] The thermal management system further includes a compressor, which is used to provide heat exchange power for the heat exchanger 100. The compressor is arranged on the side of the refrigerant substrate 130 away from the condensing plate 110. Figure 7 , Figure 9 , Figures 11 to 13 ,Figure 15 , Figure 17 As shown, the refrigerant substrate 130 includes two side surfaces arranged opposite to each other in the second direction. One of the two side surfaces includes a gas inlet C1 and a gas outlet C2. The gas inlet C1 is used to connect a condensing refrigerant flow path L1 to the exhaust port of the compressor, and the gas outlet C2 is used to connect another evaporating refrigerant flow path L4 to the suction port of the compressor.

[0134] As Figure 7 , Figure 9 , Figures 11 to 13 shown, the refrigerant substrate 130 further includes a first gas flow path L5 and a second gas flow path L6. The first gas flow path L5 is used to communicate with the gas outlet C2, and the second gas channel L6 is used to communicate with the gas inlet C1 of the compressor 140 and the first refrigerant flow path L1 respectively. In this way, the compressor can suck the low-temperature and low-pressure gaseous refrigerant in each evaporator 120 from the first gas flow path L5 through the gas outlet C2 of the refrigerant substrate 130, compress the low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant, and discharge the high-temperature and high-pressure gaseous refrigerant into the second gas flow path L6 through the gas inlet C1 of the refrigerant substrate 130, and then flow into the first refrigerant flow path L1.

[0135] In some embodiments, as Figure 6 shown, a pressure-temperature sensor S is further provided on one side of the first gas flow path L5 close to the gas inlet C1 of the refrigerant substrate 130. The pressure-temperature sensor S is used to monitor the pressure and temperature of the high-temperature and high-pressure gaseous refrigerant discharged by the compressor in real time.

[0136] In some embodiments, as Figure 6 shown, a high-pressure switch K is further provided in the first gas flow path L5. The high-pressure switch K is used to block the high-temperature and high-pressure gaseous refrigerant in the first gas flow path L5 from flowing into a condensing refrigerant flow path L1 when the pressure of the high-temperature and high-pressure gaseous refrigerant in the first gas flow path L5 is greater than a threshold value.

[0137] In some embodiments, the thermal management system further includes a gas-liquid separator, and the compressor is arranged on the side of the refrigerant substrate 130 away from the condensing plate heat exchanger 110. As Figure 7 , Figure 9 , Figures 11 to 13 , Figure 15 , Figure 17 shown, the refrigerant substrate 130 includes a gas separation inlet E s1 and a gas separation outlet E s2 , the gas separation inlet E s1 is used to connect another evaporating refrigerant flow path L4 to the liquid separation separator, and the gas separation outlet E s2Used to connect the suction port of the compressor to the liquid separator. In this way, the gas-liquid separator can separate the refrigerant in the gas-liquid two-phase state flowing out of the evaporation plate heat exchanger 120 and send the gaseous refrigerant into the compressor.

[0138] As Figure 6 shown, the third refrigerant flow channel L3 includes a confluence hole H and at least one set of shunt structures. One end of the confluence hole H is used to connect the refrigerant condensation outlet A of each condensation plate heat exchanger 110 12 , and each set of shunt structures includes a diversion hole D and a plurality of shunt holes M. In each set of shunt structures:

[0139] One end of the diversion hole D is used to connect the other end of the confluence hole H, the other end of the diversion hole D is used to connect one end of each shunt hole M, and the other end of each shunt hole M is used to connect the evaporation refrigerant inlet A of an evaporation plate heat exchanger 120 21 .

[0140] In some embodiments, the refrigerant substrate 130 includes two substrates, and one substrate 131 is arranged on the side of the other substrate 132 away from the evaporation plate heat exchanger 110. For example, the refrigerant substrate 130 includes Figure 7 a substrate 131 as shown in Figure 8 and Figure 9 another substrate 132 as shown in Figure 10 . Another example is that the refrigerant substrate 130 includes Figure 13 a substrate 131 as shown in Figure 4 and

[0141] Another substrate 132 as shown in 11 -E 12 , two sets of evaporation holes E 21 -E 22 , two condensation refrigerant flow channels L1-L2, two evaporation refrigerant flow channels L3-L4, and the formation method of the confluence flow channel H will be described below.

[0142] ① The refrigerant flow channels are distributed on one of the two substrates, i.e., substrate 131. In this way, only the refrigerant flow channels need to be processed on one substrate 131, and the two substrates are welded and assembled into the refrigerant substrate, which simplifies the processing technology of the refrigerant substrate.

[0143] For example, on the side surface of one substrate 131 facing another substrate 132, grooves corresponding to a condensation refrigerant flow path L1, another groove corresponding to a condensation refrigerant flow path L2, another groove corresponding to an evaporation refrigerant flow path L4, a groove corresponding to a first gas flow path L5, a groove corresponding to a second gas flow path L6, and a groove corresponding to a confluence flow path H are respectively machined. In this way, after the two substrates are welded and assembled into a refrigerant substrate, the groove corresponding to a condensation refrigerant flow path L1 on one substrate 131 and the side surface of another substrate 132 facing the one substrate 131 form a condensation refrigerant flow path L1, the groove corresponding to another condensation refrigerant flow path L2 and the side surface of another substrate 132 facing the one substrate 131 form another condensation refrigerant flow path L2, the groove corresponding to another evaporation refrigerant flow path L4 and the side surface of another substrate 132 facing the one substrate 131 form another evaporation refrigerant flow path L4, the groove corresponding to the first gas flow path L5 and the side surface of another substrate 132 facing the one substrate 131 form a first gas flow path L5, the groove corresponding to the second gas flow path L6 and the side surface of another substrate 132 facing the one substrate 131 form a second gas flow path L6, and the groove corresponding to the confluence flow path H and the side surface of another substrate 132 facing the one substrate 131 form a confluence flow path H.

[0144] In addition, each condensation hole penetrating along the thickness direction of another substrate 132 is machined on another substrate 132, and each condensation hole corresponding to each condensation hole on another substrate 132 is machined on one substrate 131.

[0145] In an embodiment where the refrigerant substrate includes at least one set of shunt structures, a plurality of shunt holes are machined on the groove wall of the confluence groove as shunt flow paths.

[0146] ② The refrigerant flow paths are distributed on the two substrates. In this way, a part of the refrigerant flow paths are machined on the two substrates simultaneously, and the two substrates are welded and assembled into a refrigerant substrate, shortening the processing time of the refrigerant substrate.

[0147] For example, on the side of one substrate 131 facing another substrate 132, grooves corresponding to a part of a condensing refrigerant flow path L1, grooves corresponding to a part of another condensing refrigerant flow path L2, grooves corresponding to a part of another evaporating refrigerant flow path L4, grooves corresponding to a part of a first gas flow path L5, grooves corresponding to a part of a second gas flow path L6, and grooves corresponding to a part of a confluence flow path H are respectively machined. Also, on the side of another substrate 132 facing one substrate 131, grooves corresponding to the remaining part of a condensing refrigerant flow path L1, grooves corresponding to the remaining part of another condensing refrigerant flow path L2, grooves corresponding to the remaining part of another evaporating refrigerant flow path L4, grooves corresponding to the remaining part of a first gas flow path L5, grooves corresponding to the remaining part of a second gas flow path L6, and grooves corresponding to the remaining part of a confluence flow path H are respectively machined. Further, along the arrangement direction of the two substrates, the projection of the grooves corresponding to a part of a condensing refrigerant flow path L1 on one substrate 131 overlaps with the projection of the grooves corresponding to the remaining part of the condensing refrigerant flow path L1 on another substrate 132, the projection of the grooves corresponding to a part of another condensing refrigerant flow path L2 on one substrate 131 overlaps with the projection of the grooves corresponding to the remaining part of another condensing refrigerant flow path L2 on another substrate 132, the projection of the grooves corresponding to a part of another evaporating refrigerant flow path L4 on one substrate 131 overlaps with the projection of the grooves corresponding to the remaining part of another evaporating refrigerant flow path L4 on another substrate 132, the projection of the grooves corresponding to a part of a first gas flow path L5 on one substrate 131 overlaps with the projection of the grooves corresponding to the remaining part of the first gas flow path L5 on another substrate 132, the projection of the grooves corresponding to a part of a second gas flow path L6 on one substrate 131 overlaps with the projection of the grooves corresponding to the remaining part of the second gas flow path L6 on another substrate 132, and the projection of the grooves corresponding to a part of a confluence flow path H on one substrate 131 overlaps with the projection of the grooves corresponding to the remaining part of the confluence flow path H on another substrate 132.

[0148] In this way, after the two substrates are welded and assembled into the refrigerant substrate, the grooves corresponding to a part of a condensation refrigerant flow channel L1 on one substrate 131 are buckled with the grooves corresponding to the remaining part of a condensation refrigerant flow channel L1 on the other substrate 132 to form a condensation refrigerant flow channel L1. The grooves corresponding to a part of another condensation refrigerant flow channel L2 on one substrate 131 are buckled with the grooves corresponding to the remaining part of another condensation refrigerant flow channel L2 on the other substrate 132 to form another condensation refrigerant flow channel L2. The grooves corresponding to a part of another evaporation refrigerant flow channel L4 on one substrate 131 are buckled with the grooves corresponding to the remaining part of another evaporation refrigerant flow channel L4 on the other substrate 132 to form another evaporation refrigerant flow channel L4. The grooves corresponding to a part of the first gas flow channel L5 on one substrate 131 are buckled with the grooves corresponding to the remaining part of the first gas flow channel L5 on the other substrate 132 to form the first gas flow channel L5. The grooves corresponding to a part of the second gas flow channel L6 on one substrate 131 are buckled with the grooves corresponding to the remaining part of the second gas flow channel L6 on the other substrate 132 to form the second gas flow channel L6. The grooves corresponding to a part of the confluence flow channel H on one substrate 131 are buckled with the grooves corresponding to the remaining part of the confluence flow channel H on the other substrate 132 to form the confluence flow channel H.

[0149] In addition, each condensation hole penetrating along the thickness direction of the other substrate 132 is machined on the other substrate 132, and each condensation hole corresponding to each condensation hole on the other substrate 132 is machined on one substrate 131.

[0150] In an embodiment where the refrigerant substrate includes at least one set of shunt structures, a plurality of shunt holes are machined on the groove wall of the confluence groove as shunt channels.

[0151] In some embodiments, in an embodiment where the cross-sectional shape of each flow channel is circular, arc-shaped or elliptical, and each flow channel is distributed in the form of a groove on one substrate 131, as Figure 20 shown, the dimension Δh of each flow channel in the first direction is less than or equal to the maximum dimension H of each refrigerant flow channel. In this way, it is ensured that each shunt flow channel formed after the two substrates are covered is closed.

[0152] The compressor compresses the low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant, and discharges the high-temperature and high-pressure gaseous refrigerant into the second gas flow channel L6 through the gas inlet C1 of the refrigerant substrate 130, and then flows into a condensation refrigerant flow channel L1. The high-temperature and high-pressure gaseous refrigerant entering the condensation refrigerant flow channel L1 respectively passes through the condensation refrigerant inlet A of each condensation plate exchanger 110 11Upon entering each condenser heat exchanger 110, the high-temperature and high-pressure gaseous refrigerant releases part of its heat after flowing into each condenser heat exchanger 110 and is converted into subcooled liquid refrigerant. At the same time, the condenser refrigerant outlet A of each condenser heat exchanger 110 21 The outflowing subcooled liquid flows into another condenser refrigerant flow channel L2. Furthermore, the subcooled liquid refrigerant in another condenser refrigerant flow channel L2 flows along the confluence channel H into an evaporation refrigerant flow channel L3, and the subcooled liquid refrigerant entering an evaporation refrigerant flow channel L3 enters each evaporation heat exchanger 120 through the evaporation refrigerant inlet A of each evaporation heat exchanger 120 21 enters each evaporation heat exchanger 120; or the subcooled liquid refrigerant in another condenser refrigerant flow channel L2 is shunted through a shunt structure in the confluence channel H into respective shunt flow channels and flows into each evaporation heat exchanger 120 through each shunt flow channel. After flowing into each evaporation heat exchanger 120, the subcooled liquid absorbs part of its heat and is converted into a low-temperature and low-pressure gas-liquid mixed refrigerant. At the same time, the evaporation refrigerant outlet A of each evaporation heat exchanger 120 22 The outflowing low-temperature and low-pressure gas-liquid mixed refrigerant flows into another evaporation refrigerant flow channel L4. In an embodiment without a gas-liquid separator, the gas-liquid mixed refrigerant flowing into another evaporation refrigerant flow channel L4 flows back into the compressor through the gas outlet C2 of the refrigerant substrate 130, thus completing the heat exchange cycle. In an embodiment with a gas-liquid separator, the gas-liquid mixed refrigerant flowing into another evaporation refrigerant flow channel L4 flows into the gas-liquid separator through the gas separation inlet E of the refrigerant substrate 130 s1 flows into the gas-liquid separator, and the gas-liquid separator separates the gaseous refrigerant and flows it through the gas separation outlet E of the refrigerant substrate 130 s2 flows into the first gas flow channel L5, and then flows back into the compressor through the gas inlet C1 communicated with the first gas flow channel L5, thus completing the heat exchange cycle.

[0153] As described above, the above is only the specific embodiment of the present application, but the protection scope of the present application is not limited thereto. Any person skilled in the art within the technical scope disclosed in the present application can easily think of changes or substitutions, which should all be covered by the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claimed rights.

Claims

1. A heat exchanger, It is characterized in that The heat exchanger includes at least one condensing plate heat exchanger, a plurality of evaporating plate heat exchangers and a refrigerant substrate, each of the condensing plate heat exchangers and each of the evaporating plate heat exchangers are arranged on the same side of the refrigerant substrate along a first direction, each of the condensing plate heat exchangers includes a condensed refrigerant outlet on the side facing the refrigerant substrate, and each of the evaporating plate heat exchangers includes an evaporative refrigerant inlet on the side facing the refrigerant substrate, wherein: The refrigerant substrate includes a converging flow channel and at least one group of branching structures, each group of branching structures includes a plurality of branching flow channels, one end of the converging flow channel is used to connect to the condensing refrigerant outlet of each of the condensing plate exchangers, the other end of the converging flow channel is used to connect to one end of each of the branching flow channels, and the other end of each of the branching flow channels is used to connect to the evaporating refrigerant inlet of an evaporating plate exchanger.

2. The heat exchanger according to claim 1, It is characterized in that The refrigerant substrate includes two substrates arranged relatively to each other along the first direction, and the side of one substrate facing the other substrate includes a converging groove and at least one group of diverter grooves, each group of diverter grooves includes a plurality of diverter grooves, the converging groove is connected to each of the diverter grooves, the converging groove and the side of the other substrate facing the one substrate form the converging flow channel, and each of the diverter grooves and the side of the other substrate facing the one substrate form the diverter flow channel.

3. The heat exchanger according to claim 1 or 2, It is characterized in that The cross section of each diversion groove is arc-shaped.

4. The heat exchanger according to any one of claims 1 to 3, It is characterized in that Each group of the diversion structures also includes a diversion head flow channel, which is used to connect the converging flow channel with the multiple diversion flow channels. The cross-sectional area of ​​the diversion head flow channel first decreases and then increases along the direction in which the diversion head flow channel and each of the diversion flow channels are arranged.

5. The heat exchanger according to claim 4, It is characterized in that The cross-sectional area of ​​each of the flow-dividing channels is smaller than the cross-sectional area of ​​the flow-dividing head channel.

6. The heat exchanger according to claim 4 or 5, It is characterized in that The included angle between the axis of the flow channel of the flow splitter head and the second direction is θ 1 , 0° ≤ θ 1 ≤ 30°, and the second direction is perpendicular to the first direction.

7. The heat exchanger according to any one of claims 1 to 3, It is characterized in that Each group of the flow diversion structures further includes a flow guide baffle, which is used to be embedded in the converging flow channel, and a gap is formed at the connection between the flow guide baffle and each of the flow diversion channels, wherein: The guide baffle includes a guide channel, and the guide channel is used to connect the converging channel and the gap.

8. The heat exchanger according to claim 7, It is characterized in that The cross-sectional area of ​​each of the branch flow channels is smaller than the cross-sectional area of ​​the converging flow channel; The distance between the guide baffle and an end of the converging flow channel away from the guide baffle is greater than the gap.

9. The heat exchanger according to claim 7 or 8, It is characterized in that The included angle between the axial direction of the diversion flow channel and the second direction is θ 2 , 0° ≤ θ 2 ≤ 30°.

10. The heat exchanger according to any one of claims 1 to 9, It is characterized in that The lengths of the branch flow channels are equal, and the cross-sectional areas of the branch flow channels are the same, or, The length of one of the shunt channels is less than that of the other shunt channel, and the cross-sectional area of the one shunt channel is less than that of the other shunt channel.

11. The heat exchanger according to any one of claims 1 to 10, characterized in that The included angle between the axis of the shunt flow channel and the second direction is θ 3 , 30° ≤ θ 3 ≤ 30°; the refrigerant substrate includes two sides arranged opposite to each other in the second direction, and the distance from the connection of each shunt channel to the confluence channel to one of the two sides is equal.

12. The heat exchanger according to any one of claims 1 to 11, characterized in that the heat exchanger further includes at least one throttling element, each throttling element is distributed in the confluence channel, and each throttling element is used to control the flow rate flowing from the confluence channel into a group of the shunt structures.

13. The heat exchanger according to claim 12, characterized in that the throttling element is a throttling channel, the throttling channel is used to connect the confluence channel and a group of the shunt structures, and the cross-sectional area of the connection of each throttling channel to the confluence channel is equal to the cross-sectional area of the connection of each throttling channel to the group of shunt structures.

14. The heat exchanger according to claim 13, characterized in that the cross-sectional area of the middle part of each throttling channel is respectively less than the cross-sectional area of the connection of each throttling channel to the confluence channel and the cross-sectional area of the connection of each throttling channel to the group of shunt structures.

15. An energy storage device, characterized in that the energy storage device includes at least one battery cell and the heat exchanger according to any one of claims 1 to 14, and the heat exchanger is used to perform heat exchange with each battery cell.

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