CN114383445A - Heat exchanger - Google Patents

Abstract

The application discloses a heat exchanger, including first fluid passage and the second fluid passage that adjacent setting, first fluid passage is enclosed by first slab and second slab and forms, second fluid passage is enclosed by second slab, fin board and third slab and forms, the second slab includes second base plate and a plurality of second arch, form the second slot between the adjacent second arch, second pit and second flat portion are formed respectively to second arch and second slot in the side towards the fin board, the second pit includes the pit bottom, the fin board contacts with at least partial second flat portion, along the length direction of heat exchanger, the distance between the pit bottom of adjacent second pit is a1, the minimum size of second flat portion between the adjacent second pit along the length direction of heat exchanger is a2, wherein, a2 is no more than 0.3a 1. The heat exchanger of this application reduces second fluid passage's pressure drop to thereby promote the fluidic mixture of second pit department and fin board department and promote the heat transfer effect.

Description

Heat exchanger

Technical Field

The invention relates to the technical field of heat exchange, in particular to a heat exchanger.

Background

The heat exchanger is used as an efficient and compact heat exchanger and widely applied to industries such as refrigeration air conditioners and new energy vehicles, and with the continuous improvement of requirements on energy efficiency, weight, installation and the like, the technical characteristics of high efficiency and compactness of the heat exchanger need to be further improved.

The heat exchanger is including overlapping a plurality of slab of setting usually, form fluid passage between the adjacent slab, the medium in the adjacent fluid passage carries out the heat transfer through the slab, in order to promote heat transfer performance, set up a plurality of discrete salient points in the first fluid passage side of part slab and increase first fluid passage's heat transfer area, the mode that sets up the fin at the second fluid passage side of slab increases second fluid passage's heat transfer area, in order to further promote second fluid passage's heat transfer effect, it disturbs and blocks to set up more fin to the fluid on the flow direction of second fluid usually, make second fluid and fin fully exchange heat promote heat transfer effect, but also increased the flow resistance of second fluid simultaneously, need pay higher pump work.

Disclosure of Invention

This application aim at provides a heat exchanger, not only promotes the heat transfer effect of whole heat exchanger to be favorable to reducing the flow resistance of second fluid passage.

The embodiment of the application provides a heat exchanger, which at least comprises a first fluid channel and a second fluid channel which are adjacently arranged, wherein the first fluid channel is formed by encircling a first plate sheet and a second plate sheet which are arranged in a stacked manner, the second fluid channel is formed by encircling a second plate sheet, a third plate sheet and a fin sheet which is positioned between the second plate sheet and the third plate sheet which are arranged in a stacked manner,

the first plate comprises a first base plate and a plurality of first bulges protruding towards a second plate, a first groove is formed between every two adjacent first bulges, the second plate comprises a second base plate and a plurality of second bulges protruding towards the first plate, a second groove is formed between every two adjacent second bulges, and the first bulges and the second bulges are oppositely arranged;

the second protrusion forms a second pit on the side facing the fin plate, the second pit comprises a pit bottom and a pit side, the second groove forms a second flat part surrounding the second pit on the side facing the fin plate, and the fin plate facing the second plate is in contact with at least part of the second flat part;

the fin plate divides the second fluid channel into a plurality of first sub-channels, at least part of the first sub-channels are communicated with the second pits, the distance between the bottoms of the pits of the adjacent second pits along the length direction of the heat exchanger is a1, the minimum size of the second flat part between the adjacent second pits along the length direction of the heat exchanger is a2, wherein a2 is not more than 0.3a 1.

Because a side and the first fluid contact of second slab, another side and second fluid contact, the structure of second slab directly influences the heat transfer effect of first fluid passage side and second fluid passage side and then influences the heat transfer effect between first fluid passage and the second fluid passage, this application is protruding through setting up a plurality of seconds towards first slab convex at the second slab, the second is protruding towards first fluid passage promptly, thereby increase the heat transfer area of second arch and first fluid and in order to promote the heat transfer effect of first fluid passage, the second arch forms the second pit in one side towards the fin board, the circulation space of second fluid passage is increased to the second pit, thereby reduce second fluid passage's pressure drop. In addition, a second groove is formed between the second bulges, a second flat part surrounding the second pit is formed on one side, facing the fin plate, of the second groove, and the fin plate is in contact with at least part of the second flat part so as to transfer heat of the second plate to the fin plate, so that the heat exchange area of the second fluid channel is increased, and the heat exchange efficiency inside the second fluid channel is enhanced.

According to the heat exchanger, the distance a1 between the pit bottoms of the adjacent second pits and the relation between the minimum size a2 of the second flat part between the adjacent second pits along the length direction of the heat exchanger are controlled along the length direction of the heat exchanger, so that the blocking of the second flat part to the fluid is reduced, the flowing of the fluid between the adjacent second pits is enhanced, the heat exchange efficiency at the second pits is enhanced, the pressure drop is effectively reduced, the heat exchange effect of the heat exchanger is improved, and when the second fluid flows at the adjacent second pits, the disturbance and the mixing between the second fluid at the second pits and the second fluid at the fin plates are enhanced, so that the heat exchange is more uniform, the heat transfer area between the fin plates and the second flat part is reduced by reducing the area of the second flat part, the heat exchange at the second pits is increased by balancing the heat exchange efficiency of the fin plates, and as the thermal resistance exists between the fin plates and the second plates, the heat exchange efficiency of the second pits is high, the heat exchange between the fin plate and the second pits is balanced by controlling the relation between the distance a1 between the bottoms of the pits of the adjacent second pits and the minimum size a2 of the second flat part between the adjacent second pits along the length direction of the heat exchanger, the heat exchange effect of the second fluid channel can be strengthened to the maximum extent, the pressure drop is effectively controlled, and the mutual limitation between the heat exchange performance and the fluid pressure drop in the prior art is broken.

Drawings

FIG. 1 is a schematic structural diagram of a heat exchanger according to the present application;

FIG. 2 is a schematic illustration of an exploded structure of a first plate, a second plate, a fin plate, and a third plate of the present application;

FIG. 3 is a partial structural view of a portion of the fin structure of the fin plate of the present application;

FIG. 4 is a perspective view of a portion of the fin structure of the fin plate of the present application;

FIG. 5 is a schematic view of a partially assembled construction of the heat exchanger of the present application;

FIG. 6 is an enlarged view of a partially assembled configuration of the heat exchanger of the present application;

FIG. 7 is a schematic view of another partially assembled construction of the heat exchanger of the present application;

FIG. 8 is an enlarged view of another partially assembled construction of the heat exchanger of the present application;

FIG. 9 is a partial structural view of the second plate of the present application on the side facing the first plate;

FIG. 10 is a partial schematic view of a second plate of the present application on a side facing the fin plate;

FIG. 11 is a schematic view of the distribution of the contact positions between the fin plate and the second plate according to the present application;

fig. 12 is a schematic diagram of the contact position distribution of a fin plate and a heat exchange plate in the prior art.

Detailed Description

Referring to fig. 1 to 10, the present application provides a heat exchanger, which at least includes a first fluid passage 5 and a second fluid passage 6 that are adjacently disposed, where the first fluid passage 5 and the second fluid passage 6 may be a plurality of alternately disposed, or a multi-fluid passage structure such as a third fluid passage may also be disposed, the first fluid passage 5 and the second fluid passage 6 are not communicated with each other, the first fluid passage 5 is surrounded by a first plate 1 and a second plate 2 that are stacked, the second fluid passage 6 is surrounded by a second plate 2, a third plate 3 that are stacked, and a fin plate 4 that is located between the second plate 2 and the third plate 3, the first plate 1, the second plate 2, the fin plate 4, and the third plate 3 may be fixed by brazing, and of course, the heat exchanger may further include other plates that are different from the first plate 1, the second plate 2, and the third plate 3, the fin plates 4 may have the same structure, or may be provided with multiple kinds of fin plates 4 having different structures, the first fluid passage 5 may be provided with other plates or fins except the first plate 1 and the second plate 1 to enclose the first fluid passage 5, and the second fluid passage 6 may be provided with other plates or fins except the second plate 2, the third plate 3, and the fin plates 4 to enclose the second fluid passage 6. The first plate 1, the second plate 2, the third plate 3 and the fin plate 4 may be provided with angular holes for communicating a first fluid or a second fluid, specifically, the first fluid passage 5 is used for the first fluid to flow through, and the second fluid passage 6 is used for the second fluid to flow through.

In some embodiments, referring to fig. 2, 5-8, the first plate 1 includes a first base plate 11 and a plurality of first protrusions 12 protruding toward the second plate 2, a first groove 13 is formed between adjacent first protrusions 12, the second plate 2 includes a second base plate 21 and a plurality of second protrusions 22 protruding toward the first plate 1, a second groove 23 is formed between adjacent second protrusions 22, the first protrusion 12 and the second protrusion 22 are oppositely disposed, and the first groove 13 and the second groove 23 are oppositely disposed, wherein, as shown in fig. 8, the contact between the tops of the first protrusion 12 and the second protrusion 22 not only enhances the mounting strength between the first plate 1 and the second plate 2, but also the first fluid flows in a channel formed by the first groove 13 and the second groove 23, and the flow path of the first fluid can be effectively controlled.

Of course, the first protrusion 12 and the second protrusion 22 may be aligned with each other, or may be staggered with a certain distance, so that the first protrusion top 121 and the second protrusion top 221 at least partially contact each other.

In addition, when the strength of the first plate 1 and the second plate 2 is sufficient, the tops of the first protrusion 12 and the second protrusion 22 may not be in contact, and a predetermined distance is provided between the first protrusion 12 and the second protrusion 22 for the first fluid to flow, so as to increase the uniformity of heat exchange of the first fluid.

As shown in fig. 6, the first protrusions 12 form first recesses 14 on the side facing away from the second plate, the first grooves 13 form first flat portions 15 on the side facing away from the second plate, the second protrusions 22 form second recesses 24 on the side facing the fin plate 4, as shown in fig. 6-10, second pocket 24 includes a pocket bottom 241 and pocket sides 242, second grooves 23 form a second flat 25 surrounding second pocket 24 on the side facing fin plate 4, the second flat portion 25 shown in fig. 10 includes a circular arc top portion between two adjacent second recesses 24 formed at the back of the second groove 23 and a flat portion surrounded by four adjacent second recesses 24, in other embodiments, the second flat portion 25 between two adjacent second recesses 24 may have a planar structure with the same width between two adjacent second recesses 24, or a planar structure with different widths. Wherein the fin plate 4 facing the second plate 2 is in contact with at least part of the second flat portion 25, the fin plate 4 exchanging heat by contact with the second flat portion 25 of the second plate 2, thereby transferring heat of the second plate 2 to the fin plate 4 to increase the heat exchange area of the second fluid channel 6 to enhance the heat exchange at the center of the second fluid channel 6.

As shown in fig. 7 and 8, the fin plate 4 divides the second fluid channel into a plurality of first sub-channels 61, at least a portion of the first sub-channels 61 are communicated with the second dimples 24, and the distance between the dimple bottoms 241 of adjacent second dimples 24 is a1, the minimum dimension of the second flat portion 25 between adjacent second dimples 24 in the length direction of the heat exchanger is a2, i.e., the length direction of the heat exchanger shown in fig. 8, the minimum distance between the dimple tops of adjacent second dimples 24 is a2 ≦ 0.3a1, if a2 > 0.3a1, the minimum dimension of the second flat portion 25 between adjacent second dimples 24 in the length direction of the heat exchanger is relatively large, the flow resistance of the second fluid at the dimples is large, and the second fluid is difficult to flow across the second flat portions 25 between adjacent second dimples 24, and the second pit 24 is located near the wall surface, the heat exchange efficiency is higher here, and the second fluid can not smoothly flow here, influences the heat exchange effect of second pit 24 department. The heat exchanger reduces the resistance of the second flat part 25 to the fluid by controlling the relationship between the distance a1 between the pit bottoms 241 of the adjacent second pits 24 and the minimum dimension a2 of the second flat part 25 between the adjacent second pits 24 along the length direction of the heat exchanger, thereby enhancing the heat exchange efficiency of the fluid flowing between the adjacent pits, effectively reducing the pressure drop and improving the heat exchange effect of the heat exchanger, furthermore, the fin plate 4 divides the second fluid channel into a plurality of first sub-channels 61, at least part of the first sub-channels 61 are communicated with the second pits 24, when the second fluid flows between the adjacent second pits 24, the disturbance and mixing between the second fluid at the second pits 24 and the second fluid at the fin plate 4 are enhanced, so that the heat exchange is more uniform, the heat transfer area between the fin plate 4 and the second flat part 25 is reduced by reducing the area of the second flat part 25, the heat exchange at the pits is increased by balancing the heat exchange efficiency of the fin plate 4, because the heat resistance exists between the fin plate 4 and the second plate 2, and the heat exchange efficiency at the second pits 24 is higher, the heat exchange between the fin plate 4 and the pits is balanced by controlling the relation between the distance a1 between the pit bottoms 241 of the adjacent second pits 24 and the minimum size a2 of the second flat part 25 between the adjacent second pits 24 along the length direction of the heat exchanger, the heat exchange effect of the second fluid channel can be strengthened to the maximum extent, the pressure drop is effectively controlled, and the mutual limitation between the heat exchange performance and the fluid pressure drop in the prior art is broken.

In the prior art, the contact area between the fin plate 4 and the second plate 2 is mainly increased, so that more heat is transferred to the fin plate 4 to enhance the heat exchange at the center of the second fluid channel, and the heat exchange effect of the whole heat exchanger is improved in a pressure drop manner by increasing the disturbance and the blockage of the fin plate 4 to the fluid, even if the second plate 2 is provided with the protrusions protruding towards the first fluid channel 5, the distance between the protrusions is too large, the distance between the pits formed at the side of the second fluid channel is too large, the second fluid is difficult to flow across the adjacent pits, the fluidity of the fluid in the pits is poor, and further the high-efficiency heat exchange area at the position is wasted, and the pressure drop cannot be effectively reduced, and technical personnel in the related art can improve the heat exchange effect of the second fluid channel by changing the structure of the fin plate 4, and do not think that the heat exchange at the pits is balanced by the structure at the pits and the relationship of the fin plate 4 to enhance the heat exchange at the pits, thereby promoting the whole heat exchange effect. The heat exchanger technology focuses on balancing two technical indexes of heat exchange performance and fluid pressure drop, and for an application scene with high requirements on the heat exchange performance and the fluid pressure drop, the main technical means is realized by increasing the number of fluid channels and the heat exchange area, so that the cost is increased, the weight and the volume of a heat exchanger product are further increased, and certain adverse factors are introduced to the installation and even the service life.

In the embodiment provided by the present application, as shown in fig. 9-11, the second plate 2 is provided with a main heat exchange area, the main heat exchange area is distributed with second pits 24 and second flat portions 25, as shown in fig. 11, the contact area of the second flat portions 25 of the main heat exchange area and the fin plate 4 is S1, the area of the dark part is S1, the orthographic area of the main heat exchange area in the plane of the second base plate 21 is S, and the whole rectangular area is S as shown in fig. 11, wherein S1/S is less than or equal to 0.25. Of course, the second concave portion 24 and the second flat portion 25 may be partially formed at other positions of the second substrate 21 than the main heat transfer area.

As shown in fig. 12, in the prior art, the heat exchange plate is provided with oval protrusions protruding away from the fin plate, the oval row protrusions form pits on one side facing the fin plate, the distance between adjacent pits is equivalent to the size of the oval row protrusions in the length direction of the heat exchanger, the distance between adjacent pits is too large, fluid is difficult to flow between adjacent pits, and the fluid heat exchange performance at the position is poor, and as shown in fig. 12, the part s1 with dark color is the contact area between the fin plate and the heat exchange plate, the ratio of the contact area between the fin plate and the heat exchange plate is obviously larger than that shown in fig. 11, the contact area between the fin plate and the heat exchange plate is too large, the flow of fluid between the fin plates is not smooth, especially the flow between the pits, the pressure drop of the fluid is too large, and the heat exchange performance is not good, under the working condition that the requirements on heat exchange performance and pressure drop are high, the heat exchange performance can be improved only by increasing the volume of the heat exchanger through the number of the heat exchange plates.

In the embodiment, the contact area S1 between the second flat part 25 of the main heat exchange zone and the fin plate 4 and the orthographic projection area S of the main heat exchange zone in the plane of the second substrate 21 are controlled to satisfy S1/S ≤ 0.25, so that the contact area between the fin plate 4 and the second flat part 25 is reduced, the ratio of the second flat part 25 to the second concave part 24 is reasonably distributed, the heat exchange between the fin plate 4 and the second concave part 24 is distributed, the heat exchange effect at the second concave part 24 is improved, in addition, the contact area between the fin plate 4 and the second flat part 25 is controlled within the above range, as shown in fig. 11, the contact position between the second flat part and the fin plate is communicated with front, rear, left and right flow areas, the fluid of each channel can flow mutually to improve the heat exchange uniformity of the second fluid, the ratio of the second concave part 24 is improved, and the mixing and disturbance of the second fluid at the second concave part 24 and the second fluid near the fin plate 4 are improved, the heat at the second pit 24 is quickly taken away, the whole heat exchange effect is improved, and moreover, the fluid at the second pit 24 and the fluid near the fin plate 4 are quickly mixed and then flow through the first sub-channel 61 at the fin plate 4, so that the pressure drop of the second fluid channel is effectively reduced. If S1/S is greater than 0.25, in order to ensure the contact area between the fin plate 4 and the second flat portion 25, reduce the ratio of the second concave pits 24, the high heat exchange area at the second concave pits 24 cannot be effectively utilized, so that the heat exchange performance cannot be effectively improved, and S1 is too large, the second fluid cannot smoothly flow in each first sub-channel 61, which not only affects the heat exchange uniformity, but also cannot effectively reduce the pressure drop.

In some embodiments, as shown in fig. 3-7, the fin plate 4 includes a plurality of top portions 41, a plurality of bottom portions 42, and fin portions 43 connecting adjacent top portions 41 and bottom portions 42, with first sub-channels 61 formed between adjacent fin portions 43, at least a portion of the top portions 41 being in contact with the second flat portion 25 of the second plate 2. In the length direction of the heat exchanger, the fin portion 43 includes a first fin portion 431 and a second fin portion 432, the first fin portion 431 and the second fin portion 432 are arranged in a staggered manner in the width direction of the heat exchanger, that is, in the left-right direction as shown in fig. 4, the second flat portion 25 extends in the length direction of the heat exchanger, a plurality of saw teeth portions are formed on the second flat portion 25 along both sides of the width direction of the heat exchanger, a window 433 is formed between the adjacent first fin portion 431 and the second fin portion 432, and the window 433 is communicated with the second pit 24. The fin portions 43 of the fin plate 4 extend along the flowing direction of the second fluid, so that the resistance of the fin plate 4 to the second fluid is reduced, the second fluid smoothly flows at the first sub-channels 61 between the fin portions 43, the second fluid from the second pits 24 is quickly taken away, the heat exchange efficiency at the second pits 24 is improved, and the pressure drop of the second fluid channels is effectively reduced, in addition, the disturbance of the second fluid at each first sub-channel 61 can be improved by the aid of the plurality of first fin portions 431 and the plurality of second fin portions 432 which are arranged in a staggered mode, the heat exchange effect at the fin plate 4 is improved, the window 433 of the fin plate 4 is communicated with the second pits 24, and the second fluid at the second pits 24 can smoothly flow to the first sub-channels 61 to be sufficiently mixed with the second fluid at the fin plate 4. Of course, the fin plate 4 may be mounted by rotating it by an angle, for example, by 90 °.

In other embodiments, as shown in fig. 6, the fin plate 4 is provided with a top portion, a fin portion, a bottom portion, and a fin portion which are periodically distributed along the width direction of the heat exchanger, the side of the second plate 2 facing the fin plate 4 is provided with a second recess 24 and a second flat portion 25 which are periodically distributed, at least a portion of the adjacent top portion contacting the second flat portion 25 is provided with no more than two top portions which are not contacted with the second flat portion 25, since the period of the fin portion of the fin plate 4 may be different from the period of the second recess 24 of the second plate 2, the contact ratio of the top portion of the fin plate 4 to the second flat portion 25 is controlled to adjust the flow uniformity of the fluid and the heat exchange efficiency of the fin plate 4, and the heat exchange efficiency at the second recess 24 and the fin plate 4 is balanced, so as to maximize the overall heat exchange performance of the heat exchanger, and of course, along the width direction of the heat exchanger, the top portions of fin plates 4 may all be in contact with second flat portion 25, thereby improving heat exchange efficiency at fin plates 4.

In some embodiments, as shown in fig. 7, in the width direction of the heat exchanger, i.e., the left-right direction shown in fig. 7, the maximum width of the second concave pit 24 is b1, i.e., the distance between the tops of the second concave pits 24, and the width of the top of the fin plate 4 is c1, i.e., the width of the straight section of the top of the fin plate 4, wherein b1 is not less than c1, so as to ensure that the top 41 of the fin plate 4 does not block the second concave pit 24, especially when the period of the fin portion 43 of the fin plate 4 is different from that of the second concave pit 24, the second concave pit 24 is communicated with the first sub-channel 61 at the fin plate 4, and when the front and back structures of the fin plate 4 are the same, by controlling the width of the top 41 of the fin plate 4, the flow resistance at the second concave pit 24 and the fin plate 4 can be balanced, and the overall heat exchange effect can be maximally improved.

The second flat parts 25 of the second plate 2 are located on the first plane, the top parts 41 of the fin plate 4 are located on the second plane, the first plane is parallel to the second plane, in the direction perpendicular to the first plane, the depth of the second pits 24 is smaller than the height of the fin plate 4, the relationship between the depth of the second pits 24 and the height of the fin plate 4 is controlled, so that the heat exchange area at the fin plate 4 is ensured, the pressure drop of the second fluid channel is reduced through the first sub-channels 61 which are smooth to flow at the fin plate 4, and the pressure drop at the second pits 24 is also reduced, so that the pressure drop is effectively controlled while the heat exchange effect is improved.

In some embodiments, the depths of the second recesses 24 may be different, and the heights of the first protrusions 12 and the second protrusions 22 may be staggered, so as to improve the structural reliability of the heat exchanger and ensure that at least a portion of the first protrusions 12 and the second protrusions 22 are in contact.

In some embodiments, the dimple side 242 of the second dimple 24 includes a plurality of slopes gradually shrinking from the flat portion 25 to the dimple bottom 241, or the dimple side 242 of the second dimple 24 is a curved surface shrinking from the flat portion 25 to the dimple bottom 241, and by controlling the dimple side 242 of the second dimple 24 to be a structure shrinking from the flat portion 25 to the dimple bottom 241, the flow difference between the central region and the near-wall region of the first fluid channel 5 is established, the heat transfer from the near-wall region to the central region is enhanced, and the heat exchange performance of the first fluid channel 5 is further improved.

Further, as shown in fig. 8, the first protrusion 12 includes a first protrusion top 121 and a first protrusion side 122, the second protrusion 22 includes a second protrusion top 221 and a second protrusion side 222, the first protrusion top 121 and the second protrusion top 221 are at least partially in contact, the first protrusion side 122 is contracted from the first groove 13 to the first protrusion top 121, and the second protrusion side 222 is contracted from the second groove 23 to the second protrusion top 221, so that the cross section of the second sub-channel 51 enclosed by the first groove 13 and the second groove 23 is a structure with a large middle and small upper and lower ends, the heat transfer from the near-avoiding area to the central area is further enhanced, and the heat exchange performance of the first fluid channel 5 is improved.

As shown in fig. 5 to 8, the first protrusion 12 is similar to a quadrangular pyramid, 4 first grooves 13 are arranged around the first protrusion 12, adjacent first grooves 13 intersect with each other, the extending direction of each first groove 13 is staggered with the length direction of the heat exchanger, the first sub-channel 61 extends along the length direction of the heat exchanger, the extending direction of the first sub-channel 61 is arranged at an angle with the extending direction of the first groove 13, the adjacent first grooves 13 are arranged at an angle, so that the first flat portions 15 enclose a diamond shape, the first fluid flows in the staggered second sub-channel 51, the turbulence of the first fluid is improved, the flow path of the first fluid is extended, the heat exchange effect of the first fluid is improved, the second fluid extends along the length direction of the heat exchanger, the pressure drop of the second fluid is reduced, and the second sub-channel 51 is staggered with the first sub-channel 61, the heat exchange is more uniform.

As shown in fig. 7 and 8, the third plate 3 includes a third substrate 31 and third protrusions 32 protruding away from the fin plate 4, third grooves 33 are formed between adjacent third protrusions 32, third recesses 34 are formed in the third protrusions 32 on the side facing the fin plate 4, the third grooves 33 form a third flat portion surrounding the third recesses 34 on the side facing the fin plate 4, the fin plate 4 facing the third plate 3 contacts at least a portion of the third flat portion, the top portion 41 of the fin plate 4 contacts the second flat portion 25 of the second plate 2 in the second fluid passage, the bottom portion 42 of the fin plate 4 contacts the third flat portion of the third plate 3, a plurality of first sub-passages 61 are formed between the fin plates 4, the second recesses 24 of the second plate 2 are located above the top portion 41 of the fin plate 4, the third recesses 34 of the third plate 3 are located below the bottom portion 42 of the fin plate 4, and the second recesses 24 and the third recesses 34 communicate with the first sub-passages 61, therefore, the second fluid channel not only improves the heat exchange performance and reduces the pressure drop through the second pit 24, but also further improves the heat exchange performance and reduces the pressure drop through the third pit 34 of the third plate, and the third plate 3 is arranged in the same structure as the first plate 1, so that the whole heat exchanger is sequentially and repeatedly arranged in a manner of keeping the first plate 1, the second plate 2, the fin plate, the first plate 1, the second plate 2 and the fin plate 4, and the structure of the heat exchanger is simplified. Of course, the third plate 3 may also have a different structure from the first plate 1, for example a planar structure as shown in fig. 5 and 6.

The heat exchanger provided by the present invention has been described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the core concepts of the present invention. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.

Claims (10)

1. A heat exchanger at least comprises a first fluid channel and a second fluid channel which are adjacently arranged, wherein the first fluid channel is formed by encircling of at least a first plate and a second plate which are arranged in a stacked mode, the second fluid channel is formed by encircling of at least a second plate, a third plate and a fin plate positioned between the second plate and the third plate which are arranged in a stacked mode,

the first plate comprises a first base plate and a plurality of first bulges protruding towards a second plate, a first groove is formed between every two adjacent first bulges, the second plate comprises a second base plate and a plurality of second bulges protruding towards the first plate, a second groove is formed between every two adjacent second bulges, and the first bulges and the second bulges are oppositely arranged;

the second protrusion forms a second pit on the side facing the fin plate, the second pit comprises a pit bottom and a pit side, the second groove forms a second flat part surrounding the second pit on the side facing the fin plate, and the fin plate facing the second plate is in contact with at least part of the second flat part;

the fin plate divides the second fluid channel into a plurality of first sub-channels, at least part of the first sub-channels are communicated with the second pits, the distance between the bottoms of the pits of the adjacent second pits along the length direction of the heat exchanger is a1, the minimum size of the second flat part between the adjacent second pits along the length direction of the heat exchanger is a2, wherein a2 is not more than 0.3a 1.

2. The heat exchanger of claim 1, wherein the second plate is provided with a main heat exchange region, the main heat exchange region is distributed with the second pits and the second flat portions, the contact area of the second flat portions and the fin plate is S1, and the orthographic area of the main heat exchange region in the plane of the second base plate is S, wherein S1/S is less than or equal to 0.25.

3. The heat exchanger of claim 2, wherein the fin plate includes a plurality of top portions, a plurality of bottom portions, and fin portions connecting adjacent top and bottom portions, adjacent fin portions forming the first sub-passage therebetween, at least a portion of the top portions being in contact with the second flat portion of the second plate.

4. The heat exchanger of claim 3, wherein the fin portions comprise first fin portions and second fin portions along a length direction of the heat exchanger, the first fin portions and the second fin portions are staggered along a width direction of the heat exchanger, and a window is formed between adjacent first fin portions and adjacent second fin portions, and the window is communicated with the second recess.

5. The heat exchanger of claim 3, wherein the top portions of the fin plates are each in contact with the second flat portion in a width direction of the heat exchanger; alternatively, the first and second electrodes may be,

and no more than two top parts which are not in contact with the second flat part are arranged between the adjacent top parts which are at least partially in contact with the second flat part along the width direction of the heat exchanger.

6. The heat exchanger of claim 1, wherein the well side of the second well comprises a plurality of slopes tapering from the second flat to the well bottom; alternatively, the first and second electrodes may be,

the side portion of the second recess is a curved surface that converges from the second flat portion toward the bottom of the recess.

7. The heat exchanger of any one of claims 3 to 5, wherein the maximum width of the second dimples in the width direction of the heat exchanger is b1, and the width of the top portions of the fin plates is c1, wherein b1 is not less than c 1; and/or the presence of a gas in the gas,

the second flat parts of the second plate are located on a first plane, the top parts of the fin plate are located on a second plane, the first plane is parallel to the second plane, and the depth of the second concave pit is smaller than the height of the fin plate in the direction perpendicular to the first plane.

8. The heat exchanger of any one of claims 1 to 6, wherein the third plate comprises a third base plate and third protrusions protruding away from the fin plate, wherein a third groove is formed between adjacent third protrusions, wherein the third protrusions form a third recess on a side facing the fin plate, wherein the third groove forms a third flat portion surrounding the third recess on a side facing the fin plate, and wherein the fin plate facing the third plate is in contact with at least a portion of the third flat portion.

9. The heat exchanger of any of claims 1-6, wherein the first projection comprises a first projection top and a first projection side, and the second projection comprises a second projection top and a second projection side, the first projection top and the second projection top being at least partially in contact, the first projection side converging from the first channel to the first projection top, and the second projection side converging from the second channel to the second projection top.

10. The heat exchanger of claim 9, wherein a plurality of first grooves are provided around the first projection, adjacent first grooves intersect, and the extending direction of the first sub-passage is disposed at an angle to the extending direction of the first grooves.

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