Heat exchanger and fin thereof

Abstract

The present application relates to the technical field of heat exchange, and discloses a heat exchanger and a fin thereof. The fin comprises: two frame edges parallel to each other, wherein the length direction of the frame edges extends in the length direction of the fin, each frame edge is provided with snap-fit segments close to two ends of the frame edge, the snap-fit segments protrude towards one side of the frame edge, and the snap-fit segments of every two adjacent fins abut against each other such that a gap is formed between the adjacent fins to form a flow channel; and a fin plate, which is located between the two frame edges, is fixedly connected to the frame edges, and comprises a plurality of fin segments, wherein a hollowed gap is formed between every two adjacent fin segments, any two adjacent fin segments of a same fin plate are respectively a first segment and a second segment, and the ends, close to each other, of the first segment and the second segment are staggered. When the fin is applied, a flow boundary layer and a temperature boundary layer which are formed in a previous sub-flow channel are damaged when entering a next sub-flow channel, and the flow boundary layer and the temperature boundary layer are re-formed in the next sub-flow channel, thereby improving the convective heat exchange capability, and improving the heat exchange capability.

Description

Heat exchangers and their fins

[0001] This application claims priority of the Chinese patent application number 2024101706612 filed with the China Patent Office on February 6, 2024, with the invention name “Heat exchanger and fin thereof”, 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 dissipation equipment, and in particular to a heat exchanger and fins thereof. Background Art

[0003] Plate heat exchangers are widely used in thermal management for new energy vehicles, supercomputing centers, and energy storage systems. For example, in new energy vehicles, plate heat exchangers are used in battery cooling plates, PTC cooling plates, central control chip cooling plates, and cooling plates for power chips such as IGBT / SiC. Battery temperature control typically utilizes a finless structure due to the relatively low heat flux density. However, central control chips and power chips require a finned cold plate structure due to their small heat dissipation contact surface and high heat flux density, achieving a compact structure and efficient heat exchange to meet the chip's cooling requirements.

[0004] Plate heat exchangers with welded fins typically consist of an upper base plate, fins, a lower base plate, and an outlet flange. The fins are located between the upper and lower base plates, forming flow channels between adjacent fins that carry low-temperature coolant to cool the chips. However, in existing technologies, the fins of plate heat exchangers are typically straight, resulting in a low thermal conductivity and poor heat transfer performance.

[0005] Summary of the Invention

[0006] The purpose of the present application is to provide a heat exchanger and fins thereof to improve the heat transfer coefficient of the heat exchanger, thereby improving the heat exchange performance.

[0007] In order to achieve the above objectives, this application provides the following technical solutions:

[0008] A fin, comprising:

[0009] Two parallel frame edges, the length direction of the frame edges extending along the length direction of the fins, the frame edges are each provided with a buckle section near both ends thereof, the buckle section protruding toward one side of the frame edge, the buckle sections of adjacent fins abut against each other to form a gap between adjacent fins to form a flow channel;

[0010] A fin plate is located between the two frame edges and is fixedly connected to the frame edges. The fin plate includes a plurality of fin segments arranged in sequence along the length direction. There is a hollow gap between two adjacent fin segments along the length direction. Any two adjacent fin segments of the same fin plate are respectively the first segment and the second segment, and the ends of the first segment and the second segment close to each other are staggered.

[0011] When using the fins provided by this application, as shown in Figures 2 and 3, multiple fins are stacked together along the thickness direction, with the buckled sections of two adjacent fins abutting against each other, creating a gap between the fin plates of the two adjacent fins to form a flow channel. Furthermore, a hollow gap is provided along the length between two adjacent fin segments. This hollow gap can form a flow diffusion zone, reducing the flow resistance between the two fin segments while avoiding the problem of excessive drag coefficient caused by sudden expansion and contraction between the two fin segments, thereby reducing the flow resistance of the flow channel between the two fins.

[0012] Furthermore, as shown in Figures 4 and 6, in two adjacent fins, the first segment of the first fin corresponds to the first segment of the second fin, forming a first diversion channel between them. The second segment of the first fin or the second segment of the second fin, located near the end of the first diversion channel, faces the first diversion channel, and the second segment of the first fin corresponds to the second segment of the second fin, forming a second diversion channel between them. With this arrangement, the flow boundary layer and temperature boundary layer formed by the coolant in the first diversion channel are destroyed upon entering the second diversion channel, and the flow boundary layer and temperature boundary layer are re-formed in the second diversion channel, thereby improving the convective heat transfer capacity of the heat exchanger. Furthermore, the coolant in the middle of the first diversion channel is at a lower temperature. After entering the second diversion channel, the coolant in the middle of the first diversion channel directly contacts the second segment of the fin, thereby increasing the temperature difference between the coolant and the fin plate and improving the heat transfer capacity.

[0013] As can be seen above, the multiple fin segments of two adjacent fins form corresponding flow channels arranged sequentially along the length of the fins. The flow boundary layer and temperature boundary layer formed in the previous flow channel are destroyed when entering the next flow channel, and the flow boundary layer and temperature boundary layer are re-formed in the next flow channel, thereby improving convective heat transfer capacity. Furthermore, the coolant in the middle of the previous flow channel enters the next flow channel and directly contacts the fin segment of the next flow channel, increasing the temperature difference between the coolant and the fin plate and improving heat transfer capacity.

[0014] In one implementation, the buckle section includes a first inclined section, a second inclined section, and a transition section connecting the first inclined section and the second inclined section. The first inclined section and the second inclined section are distributed in an eight-shaped pattern. The buckle section protrudes toward the first side of the frame edge. In two adjacent fins, the first side of the buckle section of the first fin abuts against the second side of the buckle section of the second fin.

[0015] The angles between the first inclined section and the second inclined section and the length direction of the fin are 20°-70°; and / or the transition section is a straight section extending along a straight line.

[0016] In one implementation, in two adjacent fins, the first side of the buckle section of the first fin abuts against the second side of the buckle section of the second fin, the first side of the buckle section is provided with a stopper, and the top of the second side of the buckle section of the second fin abuts against the stopper of the buckle section of the first fin;

[0017] The table surface of the retaining table is arranged parallel to the length direction of the fin.

[0018] In one implementation, in two adjacent fins, the first segment of the first fin corresponds to the first segment of the second fin and a first diversion channel is formed between the two, and a center line divides the mouth of the first diversion channel into two parts along the thickness direction of the fin; the second segment of the first fin or the second segment of the second fin is close to the end of the first diversion channel and is opposite to the center line.

[0019] In one implementation, the fin segments are straight plates parallel to the length direction of the fins.

[0020] In one implementation, the fin segments are curved plates, the curved plates protrude toward the first side or the second side of the fin, and the protrusion directions of two adjacent curved plates of the same fin are opposite;

[0021] The curved plate includes a first curved section, a straight section, and a second curved section sequentially connected along the length direction, wherein the first curved section and the second curved section are bent toward the same side of the fin; or, the curved plate is an arc-shaped plate extending along an arc line.

[0022] In one implementation, in the same fin, the hollow gap between two adjacent fin segments extends by a distance of 0.5 mm to 1.5 mm in the length direction; and / or,

[0023] The extension distance of the fin segments along the length direction of the fin is 1.5 mm to 6 mm; and / or,

[0024] The two frame edges of the fin are distributed up and down along the height direction of the fin, and the height of the fin is 1.5mm-7mm; and / or,

[0025] The thickness of the fin segments is 0.15 mm to 0.5 mm.

[0026] In one implementation, the extension distances of the multiple fin segments of the same fin along the length direction of the fin are equal; or, among the multiple fin segments of the same fin, the extension distances of at least some of the fin segments along the length direction of the fin are not equal to the extension distances of the remaining fin segments along the length direction of the fin; or, the extension distances of the multiple hollow gaps of the same fin along the length direction of the fin are equal; or, among the multiple hollow gaps of the same fin, the extension distances of at least some of the hollow gaps along the length direction of the fin are not equal to the extension distances of the remaining hollow gaps along the length direction of the fin.

[0027] In one implementation, the fin segment is further provided with a raised portion, and the top surface of the raised portion is a convex top surface;

[0028] The convex top surface is circular or elliptical; or, the fin segment is provided with two protrusions, the convex top surfaces of the two protrusions are elliptical, and the convex top surfaces of the two protrusions are distributed in an eight-shaped pattern; or, the fin segment is provided with one protrusion and its convex top surface is elliptical, and in the same fin, the convex top surfaces of adjacent fin segments are distributed in an eight-shaped pattern or the long axes of the convex top surfaces of adjacent fin segments are parallel.

[0029] A heat exchanger comprises a first substrate, a second substrate and a plurality of fins as described above, wherein the first substrate and the second substrate are arranged relative to each other and fixedly connected, a cooling liquid flow cavity is formed between the first substrate and the second substrate, a plurality of the fins are stacked in sequence and located in the cooling liquid flow cavity, and a flow channel is formed between two adjacent fins; compared with the prior art, the beneficial effects of the heat exchanger provided in the embodiment of the present application are the same as the beneficial effects of the above-mentioned fins, and will not be repeated here.

[0030] The width of the flow channel formed between two adjacent fins is 0.5mm-2mm. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] The drawings described herein are used to provide a further understanding of the present application and constitute a part of the present application. The illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0032] FIG1 is a schematic structural diagram of a fin provided in one embodiment of the present application;

[0033] FIG2 is a schematic diagram of a plurality of stacked fins provided by an embodiment of the present application;

[0034] FIG3 is a schematic diagram of the coupling of multiple fin buckle sections provided by an embodiment of the present application;

[0035] FIG4 is a top view of a fin plate with multiple fins provided in one embodiment of the present application;

[0036] FIG5 is a schematic diagram of multiple fin ends provided by an embodiment of the present application;

[0037] FIG6 is a top view of a plurality of stacked fin plates provided in one embodiment of the present application;

[0038] FIG7 is a schematic structural diagram of a fin provided in another embodiment of the present application;

[0039] FIG8 is a schematic diagram of a plurality of stacked fins provided in another embodiment of the present application;

[0040] FIG9 a is a partial enlarged view of a fin provided in another embodiment of the present application;

[0041] FIG9 b is a top view of a fin plate with multiple fins provided in another embodiment of the present application;

[0042] FIG10 is a top view of a plurality of stacked fin plates provided in another embodiment of the present application;

[0043] FIG11a is a schematic diagram of a first type of fin with a protrusion in an embodiment of the present application;

[0044] FIG11 b is a schematic diagram of a plurality of first-type fins with protrusions stacked in an embodiment of the present application;

[0045] FIG11c is a top view of a first type of fin with a protrusion in an embodiment of the present application;

[0046] FIG12a is a schematic diagram of a second type of fin with a protrusion in an embodiment of the present application;

[0047] FIG12 b is a schematic diagram of a stack of a plurality of second-type fins with protrusions in an embodiment of the present application;

[0048] FIG12c is a top view of a second type of fin with a raised portion in an embodiment of the present application;

[0049] FIG13a is a schematic diagram of a third type of fin with a protrusion in an embodiment of the present application;

[0050] FIG13 b is a schematic diagram of a third type of stacked fins having protrusions in an embodiment of the present application;

[0051] FIG13c is a top view of a third type of fin with a protrusion in an embodiment of the present application;

[0052] FIG14a is a schematic diagram of a fourth type of fin with a protrusion in an embodiment of the present application;

[0053] FIG14 b is a schematic diagram of a fourth type of stacked fins having a plurality of protrusions in an embodiment of the present application;

[0054] FIG14c is a top view of a fourth type of fin with a protrusion in an embodiment of the present application;

[0055] FIG15 a is a schematic diagram of a fifth type of fin with a protrusion in an embodiment of the present application;

[0056] FIG15 b is a schematic diagram of a fifth type of stacked fins having a plurality of protrusions in an embodiment of the present application;

[0057] FIG15c is a top view of a fifth type of fin having a protrusion in an embodiment of the present application;

[0058] FIG16a is a schematic diagram of fin segments of different lengths in an embodiment of the present application;

[0059] FIG16 b is a top view of an embodiment of the present application showing fin segments of different lengths;

[0060] FIG17 is a comparison diagram of the heat transfer coefficients of the fins in the prior art and the fins of the present application;

[0061] FIG18 is a flow field isometric diagram and a temperature field isothermal diagram of the fin in the prior art and the fin of the present application;

[0062] FIG19 is a diagram showing the relationship between pressure drop and flow rate of the fins in the prior art and the fins of the present application;

[0063] FIG20 is an exploded view of the heat exchanger provided in an embodiment of the present application.

[0064] Figure markings: 1-frame edge, 1a-hook section, 1a1-first inclined section, 1a2-transition section, 1a3-second inclined section, 1a4-stop platform, 2-fin section, 2a-first section, 2b-second section, 2c-first window panel, 2d-flat plate, 2e-second window panel, 2f-raised portion, 3-hollow gap; A-fin, B-first substrate, C-second substrate, C1-coolant inlet, C2-coolant outlet. DETAILED DESCRIPTION

[0065] In order to make the technical problems, technical solutions and beneficial effects to be solved by this application more clearly understood, this application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this application and are not intended to limit this application.

[0066] It should be noted that when an element is referred to as being “fixed on” or “disposed on” another element, it may be directly on the other element or indirectly on the other element. When an element is referred to as being “connected to” another element, it may be directly connected to the other element or indirectly connected to the other element.

[0067] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of this application, "multiple" means two or more, unless otherwise clearly and specifically defined. "Several" means one or more, unless otherwise clearly and specifically defined.

[0068] In the description of this application, it should be understood that the terms "up", "down", "front", "back", "left", "right", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they should not be understood as limitations on this application.

[0069] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "installed," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; they can refer to internal communication between two components or the interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0070] Please refer to Figure 1. The fin provided in the embodiment of the present application includes a fin plate and two frame edges 1. The two frame edges 1 are parallel to each other, and the length direction of the frame edge 1 extends along the length direction of the fin, that is, the length of the frame edge 1 is set along the length direction of the fin. The frame edge 1 is provided with a buckle section 1a near both ends thereof. Specifically, the frame edge 1 is provided with a buckle section 1a near both ends of the fin length direction. If the two sides of the fin are the first side and the second side, respectively, the first side and the second side are located on both sides of the fin thickness direction, and from the first side to the second side along the fin thickness direction. The buckle section 1a protrudes toward one side of the frame edge 1. The buckle section 1a can protrude toward the first side of the frame edge 1 or toward the second side. The buckle sections 1a of adjacent fins are offset against each other so that there is a gap between the adjacent fins to form a flow channel. Taking the buckle section 1a protruding toward the first side of the frame edge 1 as an example, among the two adjacent fins, the buckle section 1a on the first side of one fin is offset against the buckle section 1a on the second side of the other fin, so that there is a gap between the two adjacent fins, and the gap between the two adjacent fins forms a flow channel.

[0071] The fin plate is located between the two frame edges 1. When the fin is placed vertically, the upper side of the fin plate is fixedly connected to one frame edge 1, and the lower side of the fin plate is fixedly connected to the other frame edge 1. The fin plate and the frame edge 1 can be an integral structure for easy processing and manufacturing, or the fin plate and the frame edge 1 can also be fixedly connected by welding, clamping, interference fit, etc. The fin plate and the frame edge 1 can be formed by stamping. The fin plate includes a plurality of fin segments 2 arranged in sequence along the length direction, that is, the plurality of fin segments 2 are arranged in sequence along the length direction of the fin, and there is a hollow gap 3 between two adjacent fin segments 2 along the length direction, that is, the hollow gap 3 between two adjacent fin segments 2 of the same fin extends along the length direction. The distance is greater than zero.

[0072] Any two adjacent fin segments 2 of the same fin plate are respectively the first segment 2a and the second segment 2b, and the ends of the first segment 2a and the second segment 2b that are close to each other are staggered. Specifically, any two adjacent fin segments 2 of the same fin plate are staggered in the thickness direction of the fin. As shown in Figure 4, the ends of the first segment 2a and the second segment 2b that are close to each other are staggered in the thickness direction of the fin, so that the end of the first segment 2a is opposite to the flow channel between the second segments 2b of the adjacent fins, and the end of the second segment 2b is opposite to the flow channel between the first segments 2a of the adjacent fins.

[0073] When using the fins provided by this application, as shown in Figures 2 and 3, multiple fins are stacked together along the thickness direction, with the buckle segments 1a of two adjacent fins abutting against each other, creating a gap between the fin plates of the two adjacent fins to form a flow channel. Furthermore, a hollow gap 3 is provided along the length direction between two adjacent fin segments 2. This hollow gap 3 forms a flow diffusion zone, reducing the flow resistance between the two fin segments while avoiding the problem of excessive drag coefficient caused by sudden expansion and contraction between the two fin segments, thereby reducing the flow resistance of the flow channel between the two fins.

[0074] Furthermore, as shown in Figures 4 and 6, in two adjacent fins, the first segment 2a of the first fin corresponds to the first segment 2a of the second fin, forming a first flow channel between them. The second segment 2b of the first fin or the second segment 2b of the second fin, located near the end of the first flow channel, faces the first flow channel. The second segment 2b of the first fin corresponds to the second segment 2b of the second fin, forming a second flow channel between them. This arrangement disrupts the flow boundary layer and temperature boundary layer formed by the coolant in the first flow channel upon entering the second flow channel, allowing the flow boundary layer and temperature boundary layer to be re-formed in the second flow channel, thereby improving the convective heat transfer capacity of the heat exchanger. Furthermore, the coolant in the middle of the first flow channel is at a lower temperature. Upon entering the second flow channel, the coolant in the middle of the first flow channel directly contacts the second segment 2b of the fin, thereby increasing the temperature difference between the coolant and the fin plate and enhancing heat transfer capacity.

[0075] As can be seen above, the multiple fin segments 2 of two adjacent fins form corresponding flow channels arranged sequentially along the length of the fins. The flow boundary layer and temperature boundary layer formed in the previous flow channel are destroyed when entering the next flow channel, and the flow boundary layer and temperature boundary layer are re-formed in the next flow channel, thereby improving convective heat transfer capacity. Furthermore, the coolant in the middle of the previous flow channel directly contacts the fin segment 2 of the next flow channel after entering the next flow channel, increasing the temperature difference between the coolant and the fin plate and improving heat transfer capacity.

[0076] As shown in Figure 3, the snap-on section 1a includes a first inclined section 1a1, a second inclined section 1a3, and a transition section 1a2, wherein the transition section 1a2 connects the first inclined section 1a1 and the second inclined section 1a3, that is, the first inclined section 1a1, the transition section 1a2, and the second inclined section 1a3 are connected in sequence. The first inclined section 1a1 and the second inclined section 1a3 are arranged in an "eight" shape, that is, the first inclined section 1a1 and the second inclined section 1a3 are inclined toward each other. The two sides of the fin along the thickness direction are respectively a first side and a second side. The snap-on section 1a protrudes toward the first side of the frame edge 1. In two adjacent fins, the first side of the snap-on section 1a of the first fin abuts the second side of the snap-on section 1a of the second fin, so that a flow channel is formed between the fin plates of the two adjacent fins. The first inclined section 1a1 and the second inclined section 1a3 facilitate the positioning of the two adjacent fins in the longitudinal direction, and can prevent the two adjacent fins from being misaligned or offset in the longitudinal direction.

[0077] The angle between the first inclined section 1a1 and the second inclined section 1a3 and the fin length direction is 20°-70°. Specifically, by adjusting the angle between the first inclined section 1a1 and the second inclined section 1a3 and the fin length direction, the width of the flow channel between the two fins can be changed. The angle between the first inclined section 1a1 and the second inclined section 1a3 and the fin length direction can be set according to actual needs. For example, the angle between the first inclined section 1a1 and the second inclined section 1a3 and the fin length direction can be 20°, 25°, 30°, 35°, 40°, 45°, 50°, 55°, 60°, 65°, or 70°.

[0078] In addition, the transition section 1a2 can be a straight section extending along a straight line, which is more convenient for processing and manufacturing. The transition section 1a2 can also be an arc section extending along an arc, which is not limited here.

[0079] Of course, the buckle segment 1a can also be an arc segment extending along the arc as a whole, or the buckle segment 1a can be other shapes as a whole, which is not limited here.

[0080] As shown in Figure 3, in two adjacent fins, the first side of the buckle section 1a of the first fin abuts against the second side of the buckle section 1a of the second fin, and the first side of the buckle section 1a is provided with a stop 1a4, and the top of the second side of the buckle section 1a of the second fin abuts against the stop 1a4 of the buckle section 1a of the first fin. Specifically, the top of the second side of the buckle section 1a of the second fin abuts against the table surface of the stop 1a4 of the first fin to achieve the stacking of the first fin and the second fin, and at the same time, a flow channel is formed between the first fin and the second fin. In this embodiment, the two adjacent fins are in contact and abut against each other through the stop 1a4, thereby making the two adjacent fins more stable. By changing the position of the stop 1a4, the width of the flow channel between the two adjacent fins can be adjusted, thereby improving the accuracy of the heat exchanger.

[0081] In the above embodiment, the surface of the abutment platform 1a4 is arranged parallel to the length direction of the fin. In this way, the surface of the abutment platform 1a4 is flat and arranged along the length direction of the fin, further enhancing the stability between the two adjacent fins. Specifically, the abutment platform 1a4 is provided on the second side of the first inclined section 1a1 and the second inclined section 1a3, so that the top of the buckle section 1a of the second fin abuts the abutment platform 1a4 of the first inclined section 1a1 and the second inclined section 1a3 of the first fin. Of course, solutions in which the surface of the abutment platform 1a4 is a curved surface or the surface of the abutment platform 1a4 is arranged in other directions are all within the scope of protection of this application.

[0082] As shown in Figure 4, in two adjacent fins, the first segment 2a of the first fin corresponds to the first segment 2a of the second fin, and a first diversion channel is formed between them. The center line divides the mouth of the first diversion channel into two parts along the fin thickness direction; the end of the second segment 2b of the first fin or the second segment 2b of the second fin close to the first diversion channel is opposite to the center line. That is, the end of the second segment 2b of the first fin or the second segment 2b of the second fin is opposite to the middle position of the width direction of the outlet of the first diversion channel. The coolant temperature in the middle position of the first diversion channel is the lowest. In this way, after the coolant in the middle position of the first diversion channel enters the next diversion channel, it directly comes into contact with the second segment 2b of the first fin or the second segment 2b of the second fin, maximizing the temperature difference between the coolant and the fin plate in the next diversion channel and further improving the heat exchange capacity. It should be noted that the thickness direction of the fin is the same as the width direction of the diversion channel and the flow channel. In this technical solution, the middle position of the outlet of the upper branch channel is opposite to the side wall of the next branch channel. After the coolant in the middle of the upper branch channel enters the next branch channel, it directly approaches the side wall of the next branch channel, thereby maximizing the temperature difference between the coolant in the next branch channel and the fin plate.

[0083] Of course, the non-middle position of the outlet of the previous branch channel can also be opposite to the side wall of the next branch channel, for example, the one-third position of the outlet of the previous branch channel can be opposite to the side wall of the next branch channel, as long as the first segment 2a and the second segment 2b of the fin are staggered in the thickness direction, and no limitation is made here.

[0084] As shown in Figures 1 and 4, the fin segment 2 is a straight plate parallel to the length direction of the fin, which is easier to process and manufacture. Alternatively, as shown in Figures 7 and 9, the fin segment 2 is a curved plate, which is a non-straight plate, and the first side and second side surfaces of the curved plate are both non-planar. The curved plate protrudes toward the first side or the second side of the fin, and the protruding directions of the two adjacent curved plates of the same fin are opposite. As shown in Figure 9, if the two adjacent fin segments 2 in the same fin are the first segment 2a and the second segment 2b, the first segment 2a protrudes toward the first side and the second segment 2b protrudes toward the second side, or the first segment 2a protrudes toward the second side and the second segment 2b protrudes toward the first side. With such an arrangement, the path of the coolant in the flow channel can be extended, thereby improving the heat exchange effect.

[0085] As shown in Figures 9a and 9b, in one embodiment, the curved plate is a window-type plate, comprising a first window panel 2c, a flat plate 2d, and a second window panel 2e, connected in sequence along the length. The first window panel 2c and the second window panel 2e are tilted toward the same side of the fin. The flat plate 2d is positioned between the first window panel 2c and the second window panel 2e, forming an angle with the length of the fin. The flat plate 2d is parallel to the length of the fin. The first window panel 2c and the second window panel 2e are positioned on the same side of the flat plate. This arrangement facilitates processing and manufacturing, and the first window panel 2c and the second window panel 2e can simply be bent and tilted. Alternatively, the curved plate can be an arc-shaped plate extending along an arc. This curved plate has a smooth surface and reduces flow resistance. Of course, curved plates of other shapes are within the scope of this application.

[0086] In the above embodiment, the angle θ between the first and second bend sections and the lengthwise direction of the fins is used to adjust the flow direction of the coolant. Specifically, the angle θ between the first and second bend sections and the lengthwise direction of the fins can be greater than 0° and less than or equal to 45°. For example, θ can be 45°, 40°, 35°, 30°, etc. The first bend section extends along the lengthwise direction of the fins by a distance Lp1, and the second bend section extends along the lengthwise direction of the fins by a distance Lp2. The values ​​of Lp1 and Lp2 can be set based on actual conditions.

[0087] As shown in Figures 4 and 9 , in the same fin, the lengthwise extension distance Lt of the hollow gap 3 between two adjacent fin segments 2 is 0.5 mm to 1.5 mm. The greater the lengthwise extension distance Lt of the hollow gap 3 between two adjacent fin segments 2, the smaller the flow resistance and the smaller the heat exchange area. Therefore, to reduce flow resistance while ensuring an appropriate heat exchange area, the lengthwise extension distance Lt of the hollow gap 3 between two adjacent fin segments 2 is set within a reasonable range of 0.5 mm to 1.5 mm. Specifically, the lengthwise extension distance Lt of the hollow gap 3 between two adjacent fin segments 2 is 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1.0 mm, 1.1 mm, 1.2 mm, 1.3 mm, 1.4 mm, or 1.5 mm, etc.

[0088] In addition, the extension distance Lp of the fin segment 2 along the length direction of the fin is 1.5mm-6mm. The extension distance Lp of the fin segment 2 along the length direction of the fin can be set according to actual heat exchange needs. For example, the extension distance Lp of the fin segment 2 along the length direction of the fin is 1.5mm, 2mm, 3mm, 4mm, 5mm or 6mm.

[0089] The two frame edges 1 of the fin are distributed up and down along the height direction of the fin, and the height of the fin is 1.5mm-7mm. When the fin is placed vertically, the two frame edges 1 of the fin are distributed up and down, and the fin plate is located between the two frame edges 1. The height Fh of the fin is 1.5mm-7mm. The height of the fin can be set according to the actual heat dissipation situation. For a large amount of heat dissipation, the height of the fin can be increased, and for a small amount of heat dissipation, the height of the fin can be reduced. For example, the height Fh of the fin is 1.5mm, 2mm, 3mm, 4mm, 5mm, 6mm or 7mm.

[0090] The thickness Ft of the fin segment 2 is 0.15 mm to 0.5 mm, so as to save material as much as possible while ensuring the mechanical strength of the fin segment 2. For example, the thickness Ft of the fin segment 2 is 0.15 mm, 0.2 mm, 0.3 mm, 0.4 mm or 0.5 mm.

[0091] Of course, the extension distance Lt of the hollow gap 3 between the two adjacent fin segments 2 along the length direction, the extension distance Lp of the fin segment 2 along the fin length direction, the height Fh of the fin and the thickness Ft of the fin segment 2 can also be other values, which are not limited here.

[0092] In another specific embodiment, the fin segments 2 are further provided with raised portions 2f, each of which has a convex top surface. Each fin segment 2 can be provided with one or more raised portions 2f. The convex top surfaces of the raised portions 2f of two adjacent fins can offset each other, so that the coolant flowing in the flow channel is continuously disturbed by the raised portions 2f and the recessed portions, further improving the heat exchange effect.

[0093] As shown in Figures 11a-11c, the convex top surface of the protrusion 2f can be circular, and the side wall surface of the protrusion 2f is a curved surface. As shown in Figures 12a-12c, the convex top surface of the protrusion 2f can also be elliptical. Of course, the convex top surface can also be polygonal, rounded polygonal, etc. As shown in Figures 12a-12c, when the convex top surface of the protrusion 2f is elliptical, the protrusions 2f on multiple fin segments 2 can be tilted in the same direction; or, as shown in Figures 13a-13c, when the convex top surface of the protrusion 2f is elliptical, the protrusions 2f on multiple fin segments 2 can be tilted in different directions, for example, the protrusions 2f on two adjacent fin segments 2 are distributed in an "eight" shape.

[0094] As shown in Figures 14a-14c, when a fin segment 2 is provided with two raised portions 2f, the convex top surfaces of the two raised portions 2f are elliptical and can be arranged in a figure-eight pattern. This means that the convex top surfaces of the two raised portions 2f of the fin segment 2 are arranged facing each other, causing the coolant to be diverted as it passes through the two raised portions 2f, extending the coolant flow path and improving heat exchange. Alternatively, as shown in Figures 15a-15c, the raised portions 2f on two adjacent fin segments 2 are symmetrically arranged, or in other words, the raised portions 2f on two adjacent fin segments 2 are inclined in opposite directions.

[0095] Alternatively, each fin segment 2 may be provided with a raised portion 2f having an elliptical convex top surface. Furthermore, the convex top surfaces of adjacent fin segments 2 within the same fin may be arranged in an "eight" pattern. This arrangement also allows the coolant to be diverted as it passes through the raised portions 2f of adjacent fin segments 2, extending the coolant flow path and improving heat exchange. Alternatively, the long axes of the convex top surfaces of adjacent fin segments 2 within the same fin may be parallel, although this is not a limitation.

[0096] As shown in Figure 17, a comparison is made between the present invention's fin segments 2, which are flat plates and have a hollow gap 3 extending a distance Lt of 0.7 mm between adjacent fin segments 2, and a prior art fin segment 2, in which the fins are entirely flat plates with no gaps. As can be seen from Figure 17, the prior art fin segment 2 exhibits a higher thermal conductivity of approximately 14,000 W / m²°C at the flow channel inlet. Subsequently, as the flow boundary layer and temperature boundary layer thicken, the thermal conductivity decreases to approximately 2,000 W / m²°C near the flow channel outlet. In contrast, the present invention exhibits a thermal conductivity of approximately 14,000 W / m²°C at the flow channel inlet. Subsequently, upon entering the next branch channel, the flow boundary layer and temperature boundary layer are broken down, re-forming an inlet effect. This ensures that the average thermal conductivity of each branch channel is higher than that of the prior art fin segment 2. Experiments have shown that the average thermal conductivity of the present invention's fins is approximately 25% higher than that of the prior art fin segment 2.

[0097] As shown in Figure 18, the left side of Figure 18 shows the flow field constant velocity diagram and temperature field isotherm diagram for a solution in the prior art where the fins are entirely flat plates without gaps. The right side of Figure 18 shows the flow field constant velocity diagram and temperature field isotherm diagram for a solution in the present application where the fin segments 2 are flat plates and the hollow gaps 3 between adjacent fin segments 2 extend a distance Lt of 0.7 mm in the longitudinal direction. As can be seen from the comparison, with the prior art fins, the flow boundary layer and temperature boundary layer within the flow channel remain essentially unchanged, while with the fins in the present application, the flow boundary layer and temperature boundary layer within the flow channel are destroyed at the hollow gaps 3 and reformed in the next branch channel, greatly improving the heat exchange effect.

[0098] As shown in Figure 19, the left side of Figure 19 shows the relationship between pressure drop and flow rate in the prior art solution where the fins are straight plates without gaps, and the relationship between pressure drop and flow rate in the present application where the fin segments 2 are straight plates and the hollow gaps 3 have different values ​​of the extension distance Lt along the length direction. By comparison, it can be seen that the cooling fluid pressure drop and flow rate when the fins of the present application are used are significantly higher than the cooling fluid pressure drop and flow rate when the fins of the prior art are used, and the flow channel resistance is relatively large. The right side of Figure 19 shows the percentage increase in pressure drop and flow rate when the hollow gaps 3 have different values ​​of the extension distance Lt along the length direction compared with the prior art. It can be seen that the greater the extension distance Lt of the hollow gaps 3 along the length direction, the smaller the flow resistance in the flow channel. Therefore, it can be concluded that the appropriate provision of the hollow gaps 3 can reduce the flow resistance in the flow channel.

[0099] As shown in Figures 16a and 16b, in one specific embodiment, to facilitate manufacturing, the multiple fin segments 2 of the same fin extend the same distance along the fin length. In another embodiment, among the multiple fin segments 2 of the same fin, the extension distance of at least some of the fin segments 2 along the fin length is different from the extension distance of the remaining fin segments 2 along the fin length. The extension distance of a fin segment 2 along the fin length is the length of the fin segment 2. Specifically, the lengths of the multiple fin segments 2 of the same fin can be unequal, so that shorter fin segments 2 are provided in areas with greater heat dissipation to improve heat exchange.

[0100] In addition, the multiple hollow gaps 3 of the same fin extend at equal distances along the fin length direction. The extension distance of the hollow gaps 3 along the fin length direction is the length of the hollow gaps 3, that is, the lengths of the hollow gaps 3 between any two adjacent fin segments 2 of the same fin are equal, which facilitates processing and manufacturing. Alternatively, among the multiple hollow gaps 3 of the same fin, the extension distance of at least some of the hollow gaps 3 along the fin length direction is not equal to the extension distance of the remaining hollow gaps 3 along the fin length direction. That is, among the multiple hollow gaps 3 of the same fin, the length of some of the hollow gaps 3 is not equal to the length of another portion of the hollow gaps 3. Specifically, the lengths of the multiple hollow gaps 3 of the same fin are not completely equal. In areas with greater heat dissipation, the extension distance of the hollow gaps 3 along the fin length direction can be smaller, thereby improving the heat exchange effect.

[0101] By adopting the above technical solution, the lengths of multiple hollow gaps 3 of the same fin and the lengths of multiple fin segments 2 of the same fin can be set according to the heat dissipation requirements, thereby reducing the length of the hollow gaps 3 in areas with larger heat dissipation, increasing the density of the fin segments 2, and improving the heat exchange effect.

[0102] As shown in Figure 20, an embodiment of the present application also provides a heat exchanger, which includes a first substrate B, a second substrate C and a plurality of fins A as provided in any of the above embodiments. The first substrate B and the second substrate C are arranged relative to each other and fixedly connected. The first substrate B and the second substrate C can be fixed by welding, or the first substrate B and the second substrate C can also be fixedly connected by screws. After the first substrate B and the second substrate C are fixedly connected, a coolant flow cavity is formed between the first substrate B and the second substrate C. The plurality of fins A are located in the coolant flow cavity. The plurality of fins A are stacked in sequence, and a flow channel is formed between two adjacent fins A. The second substrate C is provided with a coolant inlet C1 and a coolant outlet C2. The coolant passes through the coolant inlet C1, the flow channel and the coolant outlet C2 in sequence, thereby taking away heat. Compared with the prior art, the beneficial effects of the heat exchanger provided in the embodiment of the present application are the same as the beneficial effects of the above-mentioned fins A, which will not be repeated here.

[0103] Furthermore, the width Ft of the flow channel formed between two adjacent fins A is 0.5 mm to 2 mm to ensure heat exchange effect. Exemplarily, the width Ft of the flow channel formed between two adjacent fins A is 0.5 mm, 0.8 mm, 1 mm, 1.2 mm, 1.5 mm, 1.8 mm or 2 mm.

[0104] 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.

[0105] The above description is merely a specific embodiment of the present application, but the scope of protection of the present application is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in this application should be included in the scope of protection of the present application. Therefore, the scope of protection of the present application should be based on the scope of protection of the claims.

Claims

1. A fin, characterized in that: include: Two parallel frame edges, the length direction of the frame edges extending along the length direction of the fins, the frame edges are each provided with a buckle section near both ends thereof, the buckle section protruding toward one side of the frame edge, the buckle sections of adjacent fins abut against each other to form a gap between adjacent fins to form a flow channel; A fin plate is located between the two frame edges and is fixedly connected to the frame edges. The fin plate includes a plurality of fin segments arranged in sequence along the length direction. There is a hollow gap between two adjacent fin segments along the length direction. Any two adjacent fin segments of the same fin plate are respectively the first segment and the second segment, and the ends of the first segment and the second segment close to each other are staggered.

2. The fin according to claim 1, characterized in that The buckle section includes a first inclined section, a second inclined section, and a transition section connecting the first inclined section and the second inclined section. The first inclined section and the second inclined section are distributed in an eight-shaped pattern. The buckle section protrudes toward the first side of the frame edge. In two adjacent fins, the first side of the buckle section of the first fin abuts against the second side of the buckle section of the second fin. The angles between the first inclined section and the second inclined section and the length direction of the fin are 20°-70°; and / or the transition section is a straight section extending along a straight line.

3. The fin according to claim 1, characterized in that In two adjacent fins, the first side of the buckle section of the first fin abuts against the second side of the buckle section of the second fin, the first side of the buckle section is provided with a stopper, and the top of the second side of the buckle section of the second fin abuts against the stopper of the buckle section of the first fin; The table surface of the retaining table is arranged parallel to the length direction of the fin.

4. The fin according to claim 1, characterized in that In two adjacent fins, the first segment of the first fin corresponds to the first segment of the second fin and a first diversion channel is formed between the two. The center line divides the mouth of the first diversion channel into two parts along the thickness direction of the fin; the second segment of the first fin or the second segment of the second fin is close to the end of the first diversion channel and is opposite to the center line.

5. The fin according to claim 1, characterized in that The fin segments are flat plates parallel to the length direction of the fins.

6. The fin according to claim 1, characterized in that The fin segments are curved plates, the curved plates protrude toward the first side or the second side of the fin, and the protrusion directions of two adjacent curved plates of the same fin are opposite; The curved plate is a window-type plate, which includes a first window plate, a flat plate and a second window plate connected in sequence along the length direction, and the first window plate and the second window plate are tilted toward the same side of the fin; or, the curved plate is an arc-shaped plate extending along an arc line.

7. The fin according to claim 5 or 6, characterized in that: In the same fin, the hollow gap between two adjacent fin segments extends by a distance of 0.5 mm to 1.5 mm in the length direction; and / or, The extension distance of the fin segments along the length direction of the fin is 1.5 mm to 6 mm; and / or, The two frame edges of the fin are distributed up and down along the height direction of the fin, and the height of the fin is 1.5mm-7mm; and / or, The thickness of the fin segments is 0.15 mm to 0.5 mm.

8. The fin according to claim 1, wherein: The extension distances of the multiple fin segments of the same fin along the length direction of the fin are equal; or, among the multiple fin segments of the same fin, the extension distances of at least some of the fin segments along the length direction of the fin are not equal to the extension distances of the remaining fin segments along the length direction of the fin; or, the extension distances of the multiple hollow gaps of the same fin along the length direction of the fin are equal; or, among the multiple hollow gaps of the same fin, the extension distances of at least some of the hollow gaps along the length direction of the fin are not equal to the extension distances of the remaining hollow gaps along the length direction of the fin.

9. The fin according to claim 1, characterized in that The fin segment is further provided with a raised portion, and the top surface of the raised portion is a convex top surface; The convex top surface is circular or elliptical; or, the fin segment is provided with two protrusions, the convex top surfaces of the two protrusions are elliptical, and the convex top surfaces of the two protrusions are distributed in an eight-shaped pattern; or, the fin segment is provided with one protrusion and its convex top surface is elliptical, and in the same fin, the convex top surfaces of adjacent fin segments are distributed in an eight-shaped pattern or the long axes of the convex top surfaces of adjacent fin segments are parallel.

10. A heat exchanger, characterized in that: The invention comprises a first substrate, a second substrate, and a plurality of fins according to any one of claims 1 to 9, wherein the first substrate and the second substrate are arranged opposite to each other and fixedly connected, a cooling liquid flow cavity is formed between the first substrate and the second substrate, the plurality of fins are stacked in sequence and located in the cooling liquid flow cavity, and a flow channel is formed between two adjacent fins; The width of the flow channel formed between two adjacent fins is 0.5mm-2mm.

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