Heat exchange plate and heat exchanger

Abstract

The present invention relates to the technical field of heat exchange devices. Disclosed are a heat exchange plate and a heat exchanger, which aim to avoid the phenomenon of a reduction in the heat exchange temperature difference that is caused by a large pressure drop in a phase-change fluid, thereby improving the heat exchange performance of the heat exchanger. A first zone and a second zone are arranged on the heat exchange plate. A plurality of first heat exchange units are provided in the first zone; and the top surface of each first heat exchange unit has a plurality of first protruding portions, the plurality of first protruding portions enclosing to form a first recessed portion therebetween. A plurality of second heat exchange units are provided in the second zone; and the top surface of each second heat exchange unit has a plurality of second protruding portions, the plurality of second protruding portions enclosing to form a second recessed portion therebetween. On the heat exchange plate, the volume of a heat exchange cavity formed on the top surface of the first zone is greater than that of a heat exchange cavity formed on the top surface of the second zone. The heat exchanger comprises a plurality of stacked heat exchange plates, wherein every two adjacent heat exchange plates are arranged opposite each other to form a heat exchange cavity, and heat exchange cavities on two sides of each heat exchange plate are used for circulation of different media.

Description

Heat exchange plate and heat exchanger

[0001] This application claims priority of the Chinese patent application filed with the China Patent Office on March 25, 2024, with application number 202410345300.7 and application name “A heat exchange plate and heat exchanger”, the entire contents of which are incorporated by reference into this application. Technical Field

[0002] The present application relates to the technical field of heat exchange devices, and in particular to a heat exchange plate and a heat exchanger. Background Art

[0003] A plate heat exchanger consists of front and rear plates and multiple heat exchange plates located between them. Heat exchange cavities are formed between the plates and between the plates and the front and rear plates for fluid flow. During operation, the phase-change fluid and water flow through the heat exchange cavities on either side of the plates, exchanging heat between the two plates.

[0004] The heat exchange plate is provided with a plurality of raised portions protruding toward one side of the heat exchange plate and a plurality of recessed portions recessed toward a side away from the raised portions. The raised portions and recessed portions are staggered on the heat exchange plate so that the phase change fluid and water are continuously disturbed by the raised portions and recessed portions when flowing in the heat exchange cavity, which is beneficial to sufficient heat exchange between the phase change fluid and water.

[0005] However, in the prior art, phase change fluids are prone to large pressure drops, which affects the phase change temperature, reduces the heat exchange temperature difference, and causes a decrease in the overall performance of the heat exchanger.

[0006] Summary of the Invention

[0007] The object of the present invention is to provide a heat exchange plate and a heat exchanger to avoid the phenomenon of large pressure drop and reduced heat exchange temperature difference of phase change fluid, thereby improving the heat exchange performance of the heat exchanger.

[0008] To achieve the above objectives, in a first aspect, the present invention provides a heat exchange plate comprising a fluid inlet and a fluid outlet, the heat exchange plate having opposing top and bottom surfaces, and a first partition and a second partition arranged along a first direction. The first partition comprises a plurality of first heat exchange units arranged in a matrix, the top surfaces of the first heat exchange units comprising a plurality of first protrusions, with first recesses formed between the plurality of first protrusions. The second partition comprises a plurality of second heat exchange units arranged in a matrix, the top surfaces of the second heat exchange units comprising a plurality of second protrusions, with second recesses formed between the plurality of second protrusions. The volume of the phase-change fluid heat exchange cavity formed on the top surface of the first partition of the heat exchange plate is greater than the volume of the phase-change fluid heat exchange cavity formed on the top surface of the second partition.

[0009] When using the above technical solution, a first zone is provided with multiple first heat exchange units arranged in a matrix. The top surface of each first heat exchange unit has multiple first protrusions, with first recesses formed between the multiple first protrusions. A second zone is provided with multiple second heat exchange units arranged in a matrix. The top surface of each second heat exchange unit has multiple second protrusions, with second recesses formed between the multiple second protrusions. In this way, the first protrusions and first recesses on the heat exchange plate are staggered, and the second protrusions and second recesses are staggered. This allows the phase-change fluid and water flowing in the heat exchange cavities on both sides of the heat exchange plate to be continuously disturbed by the protrusions and recesses, causing the flow velocity and direction to continuously change, which is conducive to sufficient heat exchange between the phase-change fluid and water. Furthermore, the volume of the phase-change fluid heat exchange cavity formed on the top surface of the first zone on the heat exchange plate is larger than the volume of the phase-change fluid heat exchange cavity formed on the top surface of the second zone. As a result, the volume of the phase-change fluid heat exchange cavity corresponding to the first zone is larger than the volume of the phase-change fluid heat exchange cavity corresponding to the second zone. When the gaseous phase-change fluid flows through the first partition, the flow resistance of the phase-change fluid is effectively reduced. When the phase-change fluid flows to the second partition, the proportion of liquid phase-change fluid increases. Since the volume of the phase-change fluid heat exchange cavity corresponding to the second partition is smaller, the flow velocity of the liquid phase-change fluid is effectively increased, enhancing the heat exchange between the phase-change fluid and water. Therefore, the heat exchange plate provided by this application can reduce the overall flow resistance of the phase-change fluid, effectively reduce the pressure drop of the phase-change fluid, control the phase change temperature, stabilize the heat exchange temperature difference, and ensure high heat exchange performance.

[0010] In a second aspect, the present invention further provides a heat exchanger comprising a plurality of stacked heat exchange plates as described in the first aspect or any possible implementation of the first aspect, wherein two adjacent heat exchange plates are symmetrically arranged to form a heat exchange cavity, and the heat exchange cavities on both sides of each heat exchange plate are used to circulate different media.

[0011] The beneficial effects of the heat exchanger provided in the second aspect are the same as the beneficial effects of the heat exchange plate described in the first aspect, and will not be described in detail here. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following drawings required for use in the embodiments or the prior art description are described:

[0013] FIG1 is a schematic diagram of a heat exchange plate provided in an embodiment of the present invention;

[0014] FIG2 is a partial schematic diagram of a heat exchange plate provided in an embodiment of the present invention;

[0015] FIG3 is a second schematic diagram of a heat exchange plate provided in an embodiment of the present invention;

[0016] FIG4 is an enlarged schematic diagram of point A in FIG3 ;

[0017] FIG5 is an enlarged schematic diagram of point B in FIG3 ;

[0018] FIG6 is a schematic diagram 1 of a first heat exchange unit or a second heat exchange unit provided by an embodiment of the present invention;

[0019] FIG7 is a second schematic diagram of the first heat exchange unit or the second heat exchange unit provided by an embodiment of the present invention;

[0020] FIG8 is a schematic diagram showing the positional relationship between the first heat exchange unit and the second heat exchange unit according to an embodiment of the present invention;

[0021] FIG9 is a second schematic diagram of the positional relationship between the first heat exchange unit and the second heat exchange unit provided by an embodiment of the present invention.

[0022] Figure numerals: 1-heat exchange plate, 11-fluid inlet, 111-phase change fluid inlet, 112-water inlet, 12-fluid outlet, 121-phase change fluid outlet, 122-water outlet, 13-first heat exchange unit, 131-first protrusion, 132-first recess, 14-second heat exchange unit, 141-second protrusion, 142-second recess, 15-arc-shaped guide groove; a-first partition, b-second partition, c-guide area. DETAILED DESCRIPTION

[0023] As shown in Figures 1 and 2, an embodiment of the present invention provides a heat exchange plate. The heat exchange plate 1 includes a fluid inlet 11 and a fluid outlet 12. The heat exchange plate 1 has opposing top and bottom surfaces. A first subarea a and a second subarea b are arranged along a first direction. The first subarea a includes a plurality of first heat exchange units 13 arranged in a matrix. As shown in Figures 6 and 7, the top surfaces of the first heat exchange units 13 have a plurality of first protrusions 131, with first recesses 132 formed between the plurality of first protrusions 131. The second subarea b includes a plurality of second heat exchange units 14 arranged in a matrix. As shown in Figures 6 and 7, the top surfaces of the second heat exchange units 14 have a plurality of second protrusions 141, with second recesses 142 formed between the plurality of second protrusions 141. The volume of the phase-change fluid heat exchange cavity formed on the top surface of the first subarea a of the heat exchange plate 1 is greater than the volume of the phase-change fluid heat exchange cavity formed on the top surface of the second subarea b.

[0024] When using the above technical solution, the first partition a is provided with a plurality of first heat exchange units 13 arranged in a matrix. The top surface of the first heat exchange units 13 has a plurality of first protrusions 131, and first recesses 132 are formed between the plurality of first protrusions 131. The second partition b is provided with a plurality of second heat exchange units 14 arranged in a matrix. The top surface of the second heat exchange units 14 has a plurality of second protrusions 141, and second recesses 142 are formed between the plurality of second protrusions 141. In this way, the first protrusions 131 and first recesses 132 on the heat exchange plate 1 are staggered, and the second protrusions 141 and second recesses 142 are staggered. This allows the phase change fluid or water flowing within the heat exchange cavities on both sides of the heat exchange plate 1 to be continuously disturbed by the protrusions and recesses, causing the flow velocity and direction to continuously change, which is conducive to sufficient heat exchange between the phase change fluid and water.

[0025] Furthermore, the volume of the phase-change fluid heat exchange cavity formed on the top surface of the first partition a is larger than that of the phase-change fluid heat exchange cavity formed on the top surface of the second partition b. When the phase-change fluid flows within the heat exchange cavity formed on the top surface of the heat exchange plate, the volume of the phase-change fluid heat exchange cavity corresponding to the first partition a is larger than that of the phase-change fluid heat exchange cavity corresponding to the second partition b. It should be noted that the phase-change fluid and water exchange heat through the heat exchange plate 1. Under condensation conditions, part of the gaseous phase-change fluid is liquefied into liquid phase-change fluid, and the ratio of liquid to gaseous phase-change fluid continuously changes. When the gaseous phase-change fluid flows through the first partition a, the larger volume of the phase-change fluid heat exchange cavity corresponding to the first partition a effectively reduces the flow resistance of the phase-change fluid. When the phase-change fluid flows to the second partition b, the proportion of liquid phase-change fluid increases. Since the volume of the phase-change fluid heat exchange cavity corresponding to the second partition b is smaller, the flow velocity of the phase-change fluid is effectively increased, enhancing the heat exchange between the phase-change fluid and water. Under evaporation conditions, part of the liquid phase-change fluid is vaporized into a gaseous phase-change fluid, and the ratio of liquid and gaseous phase-change fluids constantly changes. When the liquid phase-change fluid flows to the second partition b, since the volume of the phase-change fluid heat exchange chamber corresponding to the second partition b is relatively small, the flow velocity of the phase-change fluid can be effectively increased, thereby enhancing the heat exchange between the phase-change fluid and water. When the phase-change fluid flows to the first partition a, the proportion of the gaseous phase-change fluid increases. Since the volume of the phase-change fluid heat exchange chamber corresponding to the first partition a is relatively large, the flow resistance of the phase-change fluid can be effectively reduced. Therefore, the heat exchange plate 1 provided in the present application can reduce the overall flow resistance of the phase-change fluid, effectively reduce the pressure drop of the phase-change fluid, control the phase change temperature, stabilize the heat exchange temperature difference, and ensure high heat exchange performance.

[0026] In a specific implementation, the first direction can be the length of the heat exchange plate 1. This allows for a longer flow path for the phase-change fluid and water, resulting in a better heat exchange effect. Multiple heat exchange plates 1 provided by embodiments of the present invention can be stacked. A heat exchange plate 1 and two heat exchange plates 1 located on either side of the heat exchange plate 1 form a phase-change fluid heat exchange cavity and a water heat exchange cavity. The phase-change fluid and water flow within their respective heat exchange cavities, achieving heat exchange through the heat exchange plates 1.

[0027] Within the first partition a, multiple first heat exchange units 13 are arranged in a matrix, i.e., multiple first heat exchange units 13 are arrayed along the length and width of the heat exchange plate 1, with first protrusions 131 and first recesses 132 arranged in an array along both the length and width of the heat exchange plate 1. Within the second partition b, multiple second heat exchange units 14 are arranged in a matrix, i.e., multiple second heat exchange units 14 are arrayed along the length and width of the heat exchange plate 1, with second protrusions 141 and second recesses 142 arranged in an array along both the length and width of the heat exchange plate 1. As shown in FIG2 , the corners of four adjacent first heat exchange units 13 can form first recesses 132, and the corners of four adjacent second heat exchange units 14 can form second recesses 142. The corners of a first heat exchange unit located at the edge of the first partition a and near the second partition b can form a first recess or a second recess with the corners of a second heat exchange unit located at the edge of the second partition and near the first partition a.

[0028] For example, as shown in Figures 6 to 9 , the number of first protrusions 131 in each first heat exchange unit 13 can be three, four, five, or more. Correspondingly, the number of second protrusions 141 in each second heat exchange unit 14 can be three, four, five, or more. These are not specifically limited here and are subject to actual circumstances. In the same heat exchange plate 1, the number of first protrusions 131 and the number of second protrusions 141 in the first heat exchange unit 13 can be the same or different.

[0029] As shown in Figure 1 , the heat exchange plate provided in an embodiment of the present invention includes a fluid inlet 11 and a fluid outlet 12. Fluid can enter the heat exchange cavity formed between adjacent heat exchange plates 1 through the fluid inlet 11, and the fluid in the heat exchange cavity can flow out of the heat exchange cavity through the fluid outlet 12. The fluid inlet 11 and the fluid outlet 12 can be located anywhere on the heat exchange plate 1. However, to ensure a longer heat exchange path and facilitate pipeline connection, the fluid inlet 11 and the fluid outlet 12 are preferably located near the ends of the heat exchange plate 1.

[0030] Specifically, the fluid inlet 11 includes a phase-change fluid inlet 111 and a water inlet 112, and the fluid outlet 12 includes a phase-change fluid outlet 121 and a water outlet 122. The phase-change fluid inlet 111 and the water inlet 112 can be positioned near one end of the heat exchange plate 1 along the first direction, while the phase-change fluid outlet 121 and the water outlet 122 can be positioned near the other end of the heat exchange plate 1 along the first direction, that is, the phase-change fluid and water flow in the same direction on both sides of the heat exchange plate 1. Alternatively, the phase-change fluid inlet 111 and the water outlet 122 can be positioned near one end of the heat exchange plate 1 along the first direction, while the water inlet 112 and the phase-change fluid outlet 121 can be positioned near the other end of the heat exchange plate 1 along the first direction, that is, the phase-change fluid and water flow in opposite directions on both sides of the heat exchange plate 1, thereby improving the heat exchange effect. Of course, this is not specifically limited here, and the actual situation shall prevail. The phase-change fluid can be antifreeze or cooling water, etc.

[0031] It should be noted that under the condensation conditions described herein, initially, the phase-change fluid is in a gaseous state. The gaseous phase-change fluid flows into the phase-change fluid heat exchange chamber, and after heat exchange with water, the gaseous phase-change fluid gradually liquefies into a liquid state, and ultimately, liquid phase-change fluid flows out of the phase-change fluid heat exchange chamber. Under the evaporation conditions described herein, initially, the phase-change fluid is in a liquid state. The liquid phase-change fluid flows into the phase-change fluid heat exchange chamber, and after heat exchange with water, the liquid phase-change fluid gradually vaporizes into a gaseous state, and ultimately, gaseous phase-change fluid flows out of the phase-change fluid heat exchange chamber. Preferably, in the embodiments provided herein, under the condensation conditions, the phase-change fluid inlet 111 is located at the end of the first partition a away from the second partition b, and the phase-change fluid outlet 121 is located at the end of the second partition b away from the first partition a. In this case, not only is the flow path of the phase-change fluid extended to ensure sufficient heat exchange with water, but also, the gaseous phase-change fluid first flows through the first partition a, which can effectively reduce the flow resistance of the phase-change fluid. Subsequently, when the phase-change fluid flows to the second partition b, the proportion of liquid phase-change fluid increases, effectively increasing the flow velocity of the phase-change fluid and enhancing heat exchange between the phase-change fluid and water. Under evaporation conditions, the phase-change fluid inlet 111 can be located at the end of the second partition b away from the first partition a, and the phase-change fluid outlet 121 can be located at the end of the first partition a away from the second partition b. In this case, not only is the flow path of the phase-change fluid extended, ensuring sufficient heat exchange with the water, but the liquid phase-change fluid first flows through the second partition b, effectively increasing the flow velocity of the phase-change fluid and enhancing heat exchange between the phase-change fluid and water. Subsequently, when the phase-change fluid flows to the first partition a, the proportion of gaseous phase-change fluid increases, effectively reducing the flow resistance of the phase-change fluid.

[0032] For ease of description, a water outlet 122 is provided at one end of the heat exchange plate 1 where the phase change fluid inlet 111 is provided, and a water inlet 112 is provided at one end of the heat exchange plate 1 where the phase change fluid outlet 121 is provided, as shown in FIG1 .

[0033] It should be noted that the first and second partitions a and b are the primary heat exchange zones of the heat exchange plate 1, and the phase-change fluid and water undergo sufficient heat exchange in the locations corresponding to the first and second partitions a and b. As shown in Figure 1, a guide zone c is also provided on one side of the phase-change fluid heat exchange cavity of the heat exchange plate 1. The guide zone c is opposite the gap between the phase-change fluid inlet 111 and the water outlet 122 and is located near the edge of the first partition a facing away from the second partition b. Furthermore, a guide recess is provided between the phase-change fluid inlet 111 and the guide zone c. The guide zone c is used to direct the phase-change fluid to the side of the water outlet 122 facing away from the first partition a. That is, the phase-change fluid entering the phase-change fluid inlet 111 passes through the guide recess and enters the guide zone c. The phase-change fluid in the guide zone c is then directed to the side of the water outlet 122 facing away from the first partition a, thereby causing a portion of the phase-change fluid to flow through the water outlet 122 facing away from the first partition a, thereby avoiding the formation of a heat exchange blind spot there.

[0034] In a specific implementation, a plurality of arcuate guide grooves 15 may be provided in the guide area c. The arcuate guide grooves 15 are concave toward the phase-change fluid inlet 111, i.e., the side of the arcuate guide groove 15 closest to the phase-change fluid inlet 111 is the concave side. The extension direction of the plurality of arcuate guide grooves 15 may be parallel to the circumference of the phase-change fluid inlet 111. The plurality of arcuate guide grooves 15 are arranged sequentially in a direction away from the phase-change fluid inlet 111. Specifically, the plurality of arcuate guide grooves 15 may be provided in parallel with each other, and through grooves may be provided between the plurality of arcuate guide grooves 15, i.e., the phase-change fluid in one arcuate guide groove 15 may flow through the through grooves to another adjacent arcuate guide groove 15. In this embodiment, the phase-change fluid entering the phase-change fluid inlet 111 can enter the guide area c through the guide recess. The phase-change fluid in the guide area c flows through the multiple arcuate guide grooves 15 and the through grooves between the multiple arcuate guide grooves 15. This configuration can make the phase-change fluid more evenly distributed in the guide area c, preventing the formation of heat exchange blind spots in this area. Of course, the guide area c can also be provided with multiple guide grooves extending along a straight line, or guide grooves of any other shape, which are not limited here.

[0035] Correspondingly, a diversion zone is also provided on one side of the corresponding water heat exchange cavity of the heat exchange plate 1. This diversion zone is opposite the gap between the water inlet 112 and the phase-change fluid outlet 121 and is located near the edge of the second partition b that faces away from the first partition a. Similarly, a diversion recess is provided between the water inlet 112 and the diversion zone. The diversion zone is used to direct water to the side of the phase-change fluid outlet 121 facing away from the second partition b. That is, water entering the water inlet 112 passes through the diversion recess and then enters the diversion zone. The water in the diversion zone is then directed to the side of the phase-change fluid outlet 121 facing away from the second partition b, thereby causing a portion of the water to flow through the side of the phase-change fluid outlet 121 facing away from the second partition b, thereby avoiding the formation of a heat exchange blind spot there.

[0036] In one possible implementation, along the first direction, the ratio of the dimension D2 of the second partition b to the sum of the dimensions D of the first and second partitions b is 1:10 to 1:2. This ensures the flow velocity of the phase-change fluid, reduces the overall flow resistance of the phase-change fluid, effectively reduces the pressure drop of the phase-change fluid, and ensures heat exchange performance. For example, the ratio of D2 to D can be 1:10, 1:8, 1:6, 1:5, 1:4, 1:3, 1:2, etc., depending on actual conditions.

[0037] In one example, as shown in Figures 8 and 9 , the top surface shape of the first heat exchange unit 13 and the bottom surface shape of the second heat exchange unit 14 are identical, and the bottom surface shape of the first heat exchange unit 13 and the top surface shape of the second heat exchange unit 14 are identical. In other words, within the same heat exchange plate, the first heat exchange unit 13 and the second heat exchange unit 14 are symmetrically arranged about the surface of the heat exchange plate 1. This results in the symmetrical arrangement of the first partition a and the second partition b about the surface of the heat exchange plate. This allows the phase change fluid and water to flow symmetrically within the phase change fluid heat exchange cavity and the water heat exchange cavity formed on both sides of the heat exchange plate 1, improving the flow stability of the phase change fluid and water. This also facilitates the design and processing of the heat exchange plate 1.

[0038] 3 to 5 , in the heat exchange plate shown in FIG3 , the top surface shape of the first heat exchange unit 13 of the first partition a is the same as the bottom surface shape of the second heat exchange unit 14 , and the bottom surface shape of the first heat exchange unit 13 is the same as the top surface shape of the second heat exchange unit 14 .

[0039] In the embodiment provided by the present invention, to facilitate smoother fluid flow, the first raised portion 131 and the first recessed portion 132 form an arcuate transition, and the second raised portion 141 and the second recessed portion 142 also form an arcuate transition. This allows the fluid to flow along the curved surface, resulting in less overall resistance. Of course, during actual processing, some sharp corners may exist on the transition surface due to operational reasons. The heat exchange plate 1 can be a stamped and formed structure.

[0040] In one possible implementation, the top surface of the first protrusion 131 forms a first welding area, the bottom surface of the first recess 132 forms a second welding area, the top surface of the second protrusion 141 forms a third welding area, and the bottom surface of the second recess 142 forms a fourth welding area. The first, second, third, or fourth welding areas are shaped like an ellipse, a rounded triangle, a rounded rectangle, or a rounded rhombus. Ovals, rounded triangles, rounded rectangles, or rounded rhombuses have fewer corners and generate less overall resistance, ensuring that the fluid flow direction is changed while minimizing the waste of kinetic energy.

[0041] In addition to the above, an embodiment of the present invention further provides a heat exchanger comprising a plurality of stacked heat exchange plates 1, wherein two adjacent heat exchange plates 1 are symmetrically arranged to form a heat exchange cavity, and the heat exchange cavities on both sides of each heat exchange plate 1 are used to circulate different media.

[0042] For ease of description, the three adjacent heat exchange plates 1 are defined as the first, second, and third heat exchange plates, respectively. The second heat exchange plate is located between the first and third heat exchange plates, and is symmetrically arranged with the first and third heat exchange plates. Furthermore, the first, second, and third heat exchange plates are stacked in sequence along a third direction, which is perpendicular to both the first and second directions. The side of the third heat exchange plate facing away from the first heat exchange plate is defined as the top surface of the third heat exchange plate, and the side of the third heat exchange plate facing the first heat exchange plate is defined as the bottom surface of the third heat exchange plate. Similarly, the side of the second heat exchange plate facing away from the first heat exchange plate is defined as the top surface of the second heat exchange plate, and the side of the second heat exchange plate facing the first heat exchange plate is defined as the bottom surface of the second heat exchange plate. The side of the first heat exchange plate facing the second heat exchange plate is defined as the top surface of the first heat exchange plate, and the side of the first heat exchange plate facing away from the second heat exchange plate is defined as the bottom surface of the second heat exchange plate. In this case, during specific implementation, the top surface of the first raised portion 131 of the second heat exchange plate is welded to the bottom surface of the first raised portion 131 of the third heat exchange plate, and the top surface of the second raised portion of the second heat exchange plate is welded to the bottom surface of the second raised portion 141 of the third heat exchange plate. In this way, a heat exchange cavity is formed between the second and third heat exchange plates. At the same time, the bottom surface of the first recessed portion 132 of the second heat exchange plate is welded to the top surface of the first recessed portion 132 of the first heat exchange plate, and the bottom surface of the second recessed portion 142 of the second heat exchange plate is welded to the top surface of the second recessed portion 142 of the third heat exchange plate. In this way, a heat exchange cavity is formed between the second and first heat exchange plates. The phase change fluid and water flow in the heat exchange cavities formed on both sides of the second heat exchange plate, respectively, thereby achieving heat exchange between the phase change fluid and water.

[0043] Compared with the prior art, the beneficial effects of the heat exchanger provided in the present application are the same as those of the above-mentioned heat exchange plate 1, which will not be described in detail here.

[0044] In one possible implementation, the volume ratio of the heat exchange cavities formed on both sides of the first section a of the heat exchange plate 1 is 1:1.1 to 1:1.5. Specifically, the ratio of the phase-change fluid heat exchange cavity to the water heat exchange cavity formed on both sides of the first section a of the heat exchange plate 1 is 1:1.1 to 1:1.5, thereby improving heat exchange performance. For example, the ratio of the phase-change fluid heat exchange cavity to the water heat exchange cavity formed on both sides of the first section a of the heat exchange plate 1 can be 1:1.1, 1:1.2, 1:1.3, 1:1.4, 1:1.5, etc.

[0045] In the description of the above embodiments, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

[0046] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any modifications or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be based on the scope of protection of the claims.

Claims

1. A heat exchange plate, characterized in that: The heat exchange plate comprises a fluid inlet and a fluid outlet, the heat exchange plate has a top surface and a bottom surface opposite to each other, and a first partition and a second partition arranged along a first direction are arranged on the heat exchange plate; A plurality of first heat exchange units arranged in a matrix are provided in the first partition, and a top surface of the first heat exchange unit has a plurality of first protrusions, and a first recessed portion is formed between the plurality of first protrusions; A plurality of second heat exchange units arranged in a matrix are provided in the second partition, and a plurality of second protrusions are provided on the top surface of the second heat exchange units, and second recessed portions are formed between the plurality of second protrusions; The volume of the phase-change fluid heat exchange cavity formed on the top surface of the first partition on the heat exchange plate is greater than the volume of the phase-change fluid heat exchange cavity formed on the top surface of the second partition.

2. The heat exchange plate according to claim 1, characterized in that Along the first direction, a ratio of a size of the second partition to a sum of sizes of the first partition and the second partition is 1:10 to 1:

2.

3. The heat exchange plate according to claim 1, characterized in that The top surface shape of the first heat exchange unit is the same as the bottom surface shape of the second heat exchange unit, and the bottom surface shape of the first heat exchange unit is the same as the top surface shape of the second heat exchange unit.

4. The heat exchange plate according to claim 1, characterized in that The first protrusion and the first recess are in arc-shaped transition; and / or the second protrusion and the second recess are in arc-shaped transition.

5. The heat exchange plate according to claim 1, characterized in that: The top surface of the first protrusion forms a first welding area, and the bottom surface of the first recessed portion forms a second welding area; the top surface of the second protrusion forms a third welding area, and the bottom surface of the second recessed portion forms a fourth welding area; the shape of the first welding area, the second welding area, the third welding area or the fourth welding area is an ellipse, a rounded triangle, a rounded rectangle or a rounded rhombus.

6. The heat exchange plate according to claim 1, characterized in that The fluid inlet comprises a phase-change fluid inlet port, and the fluid outlet comprises a phase-change fluid outlet port; In the condensing condition, the phase-change fluid inlet is located at an end of the first partition away from the second partition, and the phase-change fluid outlet is located at an end of the second partition away from the first partition; In the evaporation state, the phase-change fluid inlet is located at an end of the second partition away from the first partition, and the phase-change fluid outlet is located at an end of the first partition away from the second partition.

7. A heat exchanger, characterized in that: The heat exchange plate comprises a plurality of stacked heat exchange plates according to any one of claims 1 to 8, wherein two adjacent heat exchange plates are symmetrically arranged to form a heat exchange cavity, and the heat exchange cavities on both sides of each heat exchange plate are used to circulate different media.

8. The heat exchanger according to claim 7, characterized in that The ratio of the volumes of the heat exchange cavities formed on both sides of the first partition of the heat exchange plate is 1:1.1 to 1:1.5.

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