CN118224900A - Heat exchanger, heat exchange system and vehicle - Google Patents

Abstract

A heat exchanger, a heat exchange system and a vehicle, the heat exchanger comprising a shell and fins; the shell encloses a receiving cavity, the shell has a first inlet and a first outlet, the first inlet and the first outlet are suitable for connecting the receiving cavity and an external space; a plurality of fins are received in the receiving cavity, the fins extend along a first direction, the plurality of fins are arranged at intervals along a second direction, the first direction and the second direction intersect, the gap between two adjacent fins forms a flow channel, the width of the flow channel between two adjacent fins in the second direction is D, Wherein, L _W is the length of the fin after being flattened in the first direction, L ₀ is the straight length of the flow channel in the first direction, H is the height of the fin in the third direction, δ is the average thickness of the fin, and η is a constant of 0.85. The heat exchanger has high space utilization and high heat exchange efficiency.

Description

Heat exchangers, heat exchange systems and vehicles

Technical Field

The present application relates to the field of heat exchange technology, and in particular to a heat exchanger, a heat exchange system and a vehicle.

Background Art

Existing heat exchangers all have the problems of low space utilization and insufficient heat exchange efficiency, so how to provide a heat exchanger with high space utilization and high heat exchange efficiency becomes the key.

Summary of the invention

The purpose of the present application is to provide a heat exchanger, a heat exchange system and a vehicle to solve the problems of low space utilization and insufficient heat exchange efficiency of the heat exchanger.

To achieve the purpose of this application, this application provides the following technical solutions:

In a first aspect, the present application provides a heat exchanger, comprising a shell and fins; the shell encloses a receiving cavity, the shell having a first inlet and a first outlet, the first inlet and the first outlet being adapted to communicate the receiving cavity with an external space; a plurality of fins are received in the receiving cavity, the fins extend along a first direction, the plurality of fins are arranged at intervals along a second direction, the first direction and the second direction intersect, a gap between two adjacent fins forms a flow channel, and a width of the flow channel between two adjacent fins in the second direction is D, in mm, Wherein, L _W is the total length of the fin after being flattened in the first direction, in mm, L ₀ is the straight length of the flow channel in the first direction, in mm, H is the height of the fin in the third direction, δ is the average thickness of the fin, in mm, and η is a constant of 0.85.

In one embodiment, the fin is bent and extended along the first direction, and a plurality of the fins are arranged at equal intervals along the second direction.

In one embodiment, the fin is connected to at least one inner surface of the shell by welding.

In one embodiment, the heat exchanger further includes a connecting portion, and two adjacent fins are connected via the connecting portion.

In one embodiment, the number of the fins is greater than or equal to 3, and the connecting portion includes a first connecting portion and a second connecting portion. The fin located in the middle in the second direction is connected to two adjacent fins through the first connecting portion and the second connecting portion respectively. There is a gap between the first connecting portion and the second connecting portion in a third direction, and the third direction, the first direction and the second direction intersect; the first connecting portion and the second connecting portion both extend along the first direction and are multiple, and the first connecting portion and the second connecting portion are alternately arranged along the second direction.

In one implementation, the value range of L _W is 1.5 mm-1100 mm.

In one embodiment, the value range of H is 0.5 mm-50 mm.

In one embodiment, the value range of L0 is 1mm-1000mm

In one embodiment, the value range of δ is 0.1 mm-50 mm.

In one embodiment, the value range of D is 0 mm-101 mm.

In one embodiment, the value range of D is 0.1 mm-50 mm.

In one embodiment, the heat exchanger further includes a positioning wing, the positioning wing is connected to the outer surface of the shell, the positioning wing and the shell are an integrally formed structure; the positioning wing includes a positioning portion.

In a second aspect, the present application further provides a heat exchange system, comprising a heat-exchange component and a heat exchanger according to any one of the various embodiments of the first aspect, wherein the heat-exchange component is suitable for heat exchange through the heat exchanger.

In one embodiment, the heat exchange component is rigidly connected to the heat exchanger via a solder layer.

In a third aspect, the present application further provides a vehicle, comprising the heat exchange system described in any one of the embodiments of the second aspect.

The heat exchanger provided by the present invention, by arranging multiple fins for heat dissipation in the shell, and using the gaps between the multiple fins to form a flow channel, allows the heat exchange medium flowing in from the first inlet to pass through the flow channel, so that the heat exchange medium can fully exchange heat with the fins; by satisfying the above relationship, the heat exchanger can obtain a better heat exchange effect, thereby effectively improving the heat exchange efficiency, and can also reduce the volume of the heat exchanger, making its structure compact, reducing the space required for the heat exchanger, increasing the unit mass power density and thus improving the efficiency, matching the actual vehicle installation requirements. By satisfying the above relationship, the liquid cooling power of the heat exchanger can reach more than 1200W, and the junction temperature of the heat dissipation component can be less than 95°C.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to more clearly illustrate the implementation methods of the present application or the technical solutions in the prior art, the drawings required for use in the implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some implementation methods of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

FIG1 is a top view of a heat exchanger according to an embodiment;

FIG2 is a bottom view of a heat exchanger according to an embodiment;

FIG3 is a top view of a heat exchanger with a cover plate removed in one embodiment;

FIG4 is an appearance diagram of a substrate and fins according to an embodiment;

FIG. 5 is a schematic cross-sectional view of a heat sink according to an embodiment.

Description of reference numerals:

100-heat exchanger, 10-housing, 20-heat sink;

11-substrate, 111-first surface, 112-second surface, 12-peripheral plate, 13-cover plate, 14-first inlet, 15-first outlet, 21-fin, 22-first connecting part, 23-second connecting part, 31-flow channel, 51-positioning wing, 52-positioning part.

DETAILED DESCRIPTION

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

It should be noted that when a component is said to be "fixed to" another component, it can be directly on the other component or there can be a central component. When a component is said to be "connected to" another component, it can be directly connected to the other component or there can be a central component at the same time.

Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as those commonly understood by those skilled in the art to which this application belongs. The terms used in this application and in the specification are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and/or" used in this application includes any and all combinations of one or more of the related listed items.

In conjunction with the accompanying drawings, some embodiments of the present application are described in detail below. In the absence of conflict, the following embodiments and features in the embodiments can be combined with each other.

The present application provides a heat exchange system, comprising a heat element to be dissipated and a heat exchanger, wherein the heat exchanger is used to dissipate heat from the heat element to be dissipated.

Optionally, the heat dissipation component may be a chip, which generates a large amount of heat during operation, so the heat can be dissipated through a heat exchanger.

The life of the heat sink (especially the chip) is directly related to its junction temperature. Poor liquid cooling will directly lead to an increase in the chip junction temperature and a shortened chip life. The increase in temperature will also increase the chip's forward current (when powered by a constant voltage), increase the reverse current, increase thermal stress, and accelerate aging. It can be seen that improving the cooling effect and controlling the chip junction temperature are one of the most important issues in the design and manufacture of heat exchangers.

The heat exchanger can be used to pass a heat exchange medium, thereby achieving heat exchange through the flow of the heat exchange medium. The heat exchange medium can be a liquid or a gas, and can also be a phase change material.

It is understandable that the heat exchanger can be used not only for heat exchange but also for heat supply, that is, when the heat element to be cooled is at a low temperature, the heat exchanger can be used to provide heat for it.

In one embodiment, please refer to Figures 1 to 3, the heat exchanger 100 includes a shell 10 and a plurality of fins 21. The shell 10 encloses a receiving cavity, and the shell 10 includes a substrate 11, and the substrate 11 includes a first surface 111 and a second surface 112 opposite to each other. The substrate 11 is provided with a first inlet 14 and a first outlet 15 arranged at intervals in a first direction X, and the first inlet 14 and the first outlet 15 communicate with the receiving cavity and the external space, and the second surface 112 is used to set the heat dissipation element; a plurality of fins 21 are accommodated in the receiving cavity and connected to the first surface 111, and the fins 21 extend along the first direction X, and the plurality of fins 21 are arranged at intervals along the second direction Y, and the first direction X and the second direction Y intersect and are parallel to the first surface 111, and the gap between two adjacent fins 21 in the second direction Y forms a flow channel 31.

As shown in FIG1 , the top view of the housing 10 can be a rounded rectangle, that is, it includes two opposite arc sides and two opposite straight sides. The housing 10 includes a base plate 11, a cover plate 13 and a peripheral plate 12, and the base plate 11 of the cover plate 13 is arranged relatively. The base plate 11 and the peripheral plate 12 are connected and are an integrated structure. The cover plate 13 is connected to the peripheral plate 12 and is detachably connected to the peripheral plate 12. Therefore, the base plate 11, the cover plate 13 and the peripheral plate 12 are connected to enclose the accommodating cavity together.

In one embodiment, the substrate 11 includes a length direction (a direction in which two arc sides are arranged oppositely), a width direction (a direction in which two straight sides are arranged oppositely), and a thickness direction. The length direction is a first direction X, the width direction is a second direction Y, and the thickness direction is a third direction Z. In order to facilitate the description of the specific structure of the heat exchanger 100, the first direction X, the second direction Y, and the third direction Z mentioned below can all be set with reference to the direction of the substrate 11.

The first surface 111 and the second surface 112 are two opposite surfaces in the thickness direction of the substrate 11. In one embodiment, the first surface 111 and the second surface 112 are both planes.

The first inlet 14 and the first outlet 15 are both provided on the substrate 11 and penetrate the first surface 111 and the second surface 112. The first inlet 14 and the first outlet 15 are spaced apart in the first direction X. It can be understood that the first inlet 14 can be close to the left arcuate edge in the figure, and the first outlet 15 can be close to the right arcuate edge in the figure.

The heat dissipation element may be connected to the second surface 112 , and the connection method includes but is not limited to welding, gluing or clamping.

In one embodiment, the fin 21 may be a plate-shaped structure, connected to the substrate 11 , and extending along the first direction X. In some examples, after the cover 13 closes the accommodating cavity, a surface of the fin 21 facing away from the substrate 11 may be connected to the cover 13 .

Exemplarily, the shapes of the multiple fins 21 can be exactly the same, so after the multiple fins 21 are arranged at intervals, the gap formed can be the flow channel 31. The flow channel 31 is used to guide the heat exchange medium. It can be understood that since the flow channel 31 is formed by the gap between the fins 21, the shape of the flow channel 31 should be determined according to the shape of the fins 21.

In one embodiment, the cross-section of the fin 21 can be cylindrical, elliptical, square, diamond, etc. Any structure optimized or inferred based on the structure of the present invention should be included in the protection scope of the present invention.

In one embodiment, the flow channel 31 may be a straight flow channel 31 , or may be a curved flow channel 31 , or may be a corrugated flow channel 31 , or may be a louver-type flow channel 31 , or may be a microporous flow channel 31 .

The specific flow mode of the heat exchange medium in the accommodating chamber may be to enter the accommodating chamber from the first inlet 14 , and then flow out from the first outlet 15 through the flow channel 31 .

The heat exchanger 100 provided by the present invention is characterized in that the flow channel 31 for the heat exchange medium to flow is pre-formed by the fins 21 encapsulated inside the heat exchanger 100. Thus, the heat generated by the heat element to be radiated can be directly dissipated through the heat exchange medium in the heat exchanger 100, avoiding other secondary connection structures or the problem of using silicone to achieve combined heat conduction, and also reducing the disadvantages of the split structure fixed by screws.

The heat exchanger 100 provided by the present invention has a plurality of flow channels 31 disposed in the receiving chamber, and the heat exchange medium in the flow channel 31 circulates through the first inlet 14 and the first outlet 15 to complete the heat exchange. After the heat exchange medium flows out of the heat exchanger 100, it reaches the cold source (or heat source) for external heat exchange, and then circulates back into the heat exchanger 100 after the external heat exchange is completed, and heat absorption or heat release is achieved through this process.

The heat exchanger 100 provided by the present invention connects a plurality of fins 21 for heat dissipation to the first surface 111 of the substrate 11, and forms a flow channel 31 by using the gaps between the plurality of fins 21, so that the heat exchange medium flowing in from the first inlet 14 can pass through the flow channel 31, so that the heat exchange medium can fully exchange heat with the fins 21; the present application arranges the heat exchange element on the second surface 112 of the substrate 11, so that the heat generated by the heat exchange element can be directly transferred to the fins 21, and the heat transfer path is the shortest, so that the heat exchange efficiency of the heat exchanger 100 for the heat exchange element is improved; and the first inlet 14, the first outlet 15, the fins 21 and the heat exchange element are all arranged on the substrate 11, so that the four are designed based on the substrate 11, and the space in the accommodating cavity is only suitable for the fins 21, without being affected by other components, thereby improving the space utilization rate in the accommodating cavity, so that the heat exchanger 100 can have a higher space utilization rate.

In one embodiment, referring to FIG3 , the fin 21 is bent and extended along the first direction X, and a plurality of fins 21 are arranged at equal intervals along the second direction Y. Specifically, as shown in FIG3 , the top view shape of the fin 21 may be wavy, so it is bent and extended along the first direction X.

The fins 21 are bent and extended along the first direction X, which has the advantage of increasing the area of a single fin 21 ; compared with a straight structure, the bent fins 21 can have a larger area for heat exchange with the heat exchange medium, thereby improving the heat exchange efficiency.

In one embodiment, the fins 21 and the base plate 11 are welded, and the fins 21 are perpendicular to the base plate 11. The base plate 11 and the fins 21 are connected by welding, that is, the fins 21 and the base plate 11 form a conjoined structure. Each fin 21 is distributed in parallel on the base plate 11 at the same spacing and is connected to the base plate 11 at an angle of 90°.

In one embodiment, the fins 21 are connected to the base plate 11 and are arranged in a staggered or parallel manner. The parameters, i.e., the size and height of the fins 21, the number, spacing, and thickness of the fins 21 and the flow channels 31 can be adjusted according to the use conditions.

In one embodiment, the plurality of fins 21 are arranged in multiple rows and/or multiple columns on the substrate 11 , and the fins 21 in two adjacent rows or two adjacent columns are arranged side by side or staggered.

In one embodiment, the spacing between any two adjacent fins 21 in the same row or column is equal.

In one embodiment, the heat exchanger 100 further includes a connecting portion, and two adjacent fins 21 are connected via the connecting portion.

Specifically, the fins 21 and the connecting portion can be integrally formed. Two adjacent fins 21 are connected by the connecting portion, so that the two adjacent fins 21 and the connecting portion can jointly enclose a flow channel 31. The heat on the fins 21 can also be transferred to the connecting portion, and the heat is thus conducted out through the connecting portion, so compared with independent fins 21, the connecting portion further increases the heat exchange area, thereby obtaining the maximum heat exchange effect.

In one embodiment, please refer to Figures 4 and 5, the heat exchanger 100 includes a heat sink 20, the heat sink 20 includes a fin 21, a first connection portion 22 and a second connection portion 23, the fin 21 is connected to the first connection portion 22 and the second connection portion 23 at two opposite ends in the third direction Z, and the three directions intersect with the first surface 111; the first connection portion 22 and the second connection portion 23 both extend along the first direction X and are both multiple, and the multiple first connection portions 22 and the multiple second connection portions 23 are alternately arranged along the second direction Y.

Specifically, the plurality of fins 21 may be an integrated structure, that is, a part of the heat sink 20. As shown in Fig. 5, it is a cross section of the heat sink 20, and the heat sink 20 may be a wavy or curved structure formed by stamping a metal plate.

In one embodiment, the fin 21 is a portion of the heat sink 20 that is perpendicular to the substrate 11. The fin 21 includes a first connection portion 22 and a second connection portion 23 in its thickness direction. The first connection portion 22 and the second connection portion 23 are both portions of the heat sink 20 that are parallel to the substrate 11.

It can be understood that the first connection portion 22 connects adjacent fins 21 and is connected to the base plate 11. The second connection portion 23 connects adjacent fins 21 and is connected to the cover plate 13. Therefore, the first connection portion 22 and the second connection portion 23 are respectively connected to two opposite surfaces.

In order to obtain the maximum heat exchange effect, the present invention can further increase the heat exchange area inside the accommodating cavity. By setting the heat sink 20 and increasing the heat exchange area of the heat sink 20 through the first connecting part 22 and the second connecting part 23, compared with the independent fins 21, the connecting part further increases the heat exchange area, thereby obtaining the maximum heat exchange effect.

In one embodiment, the fin 21 and the flow channel 31 satisfy the relationship: Wherein, L _W is the total length of the fin 21 after flattening in the length direction of the substrate 11, in mm, L ₀ is the straight length of the flow channel 31 in the length direction of the substrate 11, in mm, D is the width of the flow channel 31 in the width direction of the substrate 11, in mm, H is the height of the fin 21 in the thickness direction of the substrate 11, in mm, is the average thickness of the fin 21, in mm, and η is a constant of 0.85. It should be explained that the average thickness δ of the fin 21 is the average value of the thicknesses of multiple fins.

Specifically, since the heat sink 20 (fins 21) in the heat exchanger 100 is the main factor affecting the heat exchange effect, and the size of the flow channel 31 is affected by the total length design of the unfolded plane of the heat sink 20, the distribution height design of the fins 21, the maximum thickness design of the fins 21, the length design of the direction of the flow channel 31 arranged by the fins 21, etc.; therefore, the flow channels 31 with different distribution relationships have a large difference in the overall heat exchange efficiency of the heat exchanger 100.

It can be understood that in the above embodiment, the fin 21 is bent and extended along the first direction, so the actual total length L _W of the fin 21 should be greater than the length of the flow channel L _0. Of course, the fin 21 can also extend straight along the first direction, in which case the actual total length L _W of the fin 21 is equal to the length of the flow channel L _0. The test method of L _W is to construct a fin 21 model and measure the length of its profile curve through UG (Unigraphics NX, interactive CAD/CAM system) software. Please refer to the dotted line part in Figure 3, that is, the length of the curved surface of the fin 21 in the fluid flow direction, in mm.

It needs to be explained that if there are n fins, the width of each fin is a1, a2...an; where a1 accounts for the proportion of all fins f1, a2 accounts for the proportion of all fins f2...an accounts for the proportion of all fins fn; then the mean value of the average thickness δ of the fin 21 is a1*f1+a2*f2+...+an*fn/f1+f2+...fn.

By satisfying the above relationship, the heat exchanger 100 can obtain a better heat exchange effect, thereby effectively improving the heat exchange efficiency, and can also reduce the volume of the heat exchanger 100, making its structure compact, reducing the space required for the heat exchanger 100, increasing the unit mass power density and thus improving the efficiency, matching the actual vehicle installation requirements. Preferably, by satisfying the above relationship, the liquid cooling power of the heat exchanger 100 can reach more than 1200W, and the junction temperature of the heat dissipation element can be less than 95°C.

In one embodiment, the value range of L _W is 1.5 mm-1100 mm. Exemplarily, the value of L _W can be 1.5 mm, 5 mm, 10 mm, 50 mm, 100 mm, 200 mm, 500 mm, 800 mm, 1000 mm, 1100 mm. When L _W meets this range, the actual length of the fin 21 will not be too long or too short, and the manufacturing difficulty is reduced while ensuring that the flow channel 31 has a sufficient length.

In one embodiment, the value range of H is 0.5mm-50mm. Exemplarily, the value of H can be 0.5mm, 1mm, 5mm, 10mm, 20mm, 25mm, 30mm, 40mm, 50mm. When H meets this range, the height of the fin 21 is controlled within a suitable range, and the thickness of the heat exchanger 100 is avoided to be too thick while ensuring sufficient heat exchange area.

In one embodiment, the value range of _L0 is 1mm-1000mm. Exemplarily, the value of _L0 can be 1mm, 5mm, 10mm, 50mm, 100mm, 200mm, 500mm, 800mm, 900mm, 1000mm. When _L0 meets this range, the heat exchanger 100 has a sufficiently long flow channel 31 to facilitate heat exchange through the fins.

In one embodiment, the value range of δ is 0.1mm-50mm. Exemplarily, the value of δ can be 0.1mm, 1mm, 5mm, 10mm, 20mm, 25mm, 30mm, 40mm, 50mm. When δ satisfies this range, the average thickness of the fin 21 is controlled within a suitable position, which can not only ensure the width of the flow channel 31, but also facilitate the replacement of the fin 21 at a later time.

In one embodiment, the value range of D is 0mm-101mm. Exemplarily, the value of D can be 0mm, 1mm, 5mm, 10mm, 20mm, 25mm, 30mm, 40mm, 50mm, 101mm. When D satisfies this range, the width of the flow channel 31 is within a suitable range, and the flow rate of the heat exchange medium per unit time is within a suitable range, thereby reducing the process difficulty of forming the flow channel 31 while achieving efficient heat exchange.

In one embodiment, the value range of D is 0.1mm-50mm. Exemplarily, the value of D can be 0.1mm, 1mm, 5mm, 10mm, 20mm, 25mm, 30mm, 40mm, 50mm. When D meets this range, the heat exchange effect is further improved to ensure efficient heat exchange.

In one embodiment, referring to FIG. 1 , the heat exchanger 100 further includes a positioning wing 51 , which is connected to the circumference of the shell 10 , and the positioning wing 51 and the shell 10 are an integrally formed structure; the positioning wing 51 includes a positioning portion 52 .

Specifically, the positioning wings 51 can be connected to the periphery of the base plate 11, or to the periphery of the peripheral plate 12. The one-piece molding structure avoids the problem of heat loss between the positioning wings 51 and the base plate 11, and improves the installation accuracy of the base plate 11 and the components while improving the heat conduction.

Optionally, the heat exchanger 100 can be placed horizontally when in operation, that is, the base plate 11 is parallel to the horizontal plane. Of course, in other embodiments, the heat exchanger 100 can also be arranged at an angle of 45° to 135°.

Optionally, the positioning portion 52 can be a positioning hole, or a positioning protrusion. It can also be a positioning buckle. It can be understood that the role of the positioning portion is that when multiple heat exchangers are connected, they can be mutually positioned and fixed through the positioning portions.

The housing 10 and the positioning wing 51 are integrally formed, and the positioning wing 51 is a conjoined structure rooted and grown on the housing 10. The heat conduction problem of the positioning structure and the housing 10 being closely connected by using a transition is avoided, the heat conduction is improved, and the installation accuracy of the housing 10 is improved.

In one embodiment, the heat exchange system includes a heat dissipation element, a solder layer and a heat exchanger 100. The heat dissipation element and the heat exchanger 100 may refer to the embodiments provided above. The solder layer may be a metal layer formed after the heat dissipation element and the heat exchanger 100 are welded. The heat generated by the heat dissipation element may be transferred to the heat exchanger 100 through the solder layer. The heat dissipation element and the heat exchanger 100 are rigidly connected by the solder layer, so that a good heat transfer effect can be obtained.

In one embodiment, the present application further provides a vehicle, a heat exchange system according to any one of the above embodiments. The above heat exchange system is used for heat exchange inside the vehicle, which can realize multi-layer spatial three-dimensional layout and force, making the structure inside the vehicle compact, the space utilization rate high, and the installation and disassembly of the heat exchange system in the vehicle more convenient.

In order to illustrate the above-mentioned embodiments, the present invention is further described below through examples.

In an exemplary embodiment, the model can be obtained based on Design of Experiments (DOE) and simulated by the following 10 groups of heat exchangers, with detailed parameters shown in Table 1.

Example 1

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, wherein the heat exchanger meets the following conditions:

Relational formula:

D∈{0.77, 11.84}

D=1.1, which satisfies the relationship.

Example 2

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, and includes most of the structures in Embodiment 1, except that:

Relational formula:

D∈{0.65,9.86}

D=9, which satisfies the relationship.

Example 3

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, and includes most of the structures in Embodiment 1, except that:

Relational formula:

D∈{0.79, 11.85}

D=1.5, which satisfies the relationship.

Example 4

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, and includes most of the structures in Embodiment 1, except that:

Relational formula:

D∈{0.72，11.78}

D=5, which satisfies the relationship.

Example 5

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, wherein the heat exchanger meets the following conditions:

Relational formula:

D∈{6.66，80.42}

D=35, which satisfies the relationship.

Example 6

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, wherein the heat exchanger meets the following conditions:

Relational formula:

D∈{8.99,36.65}

D=10, which satisfies the relationship.

Example 7

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, wherein the heat exchanger meets the following conditions:

Relational formula: D∈{0.57,6.10}

D=1, satisfying the relationship.

Example 8

This embodiment is used to illustrate the heat exchanger disclosed in the present invention, wherein the heat exchanger meets the following conditions:

Relational formula:

D∈{8.92，101.12}

D=80, which satisfies the relationship.

Comparative Example 1

This comparative example is used to compare and illustrate the heat exchanger disclosed in the present invention, including most of the structures in Example 1, and the difference is that:

Relational formula:

D∈{0.77, 11.84}

D=0.1, the relationship is not satisfied.

Comparative Example 2

This comparative example is used to compare and illustrate the heat exchanger disclosed in the present invention, including most of the structures in Example 1, and the difference is that:

Relational formula:

D∈{0.77, 11.84}

D=50, which does not satisfy the relationship.

Performance Testing

The heat exchangers provided in the above embodiments and comparative examples were subjected to the following performance tests. Chips of the same power were installed on the heat exchangers obtained in the embodiments and comparative examples, and the center temperature of the chips was detected after the chips were started and run for 2 hours. The test results were filled in Table 1.

Table 1

In the description of the embodiments of the present application, it should be noted that the orientation or positional relationship of terms such as "center", "up", "down", "left", "right", "vertical", "horizontal", "inside" and "outside" are based on the orientation or positional relationship described in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application.

What is disclosed above is only a preferred embodiment of the present application, and it certainly cannot be used to limit the scope of rights of the present application. Ordinary technicians in this field can understand that all or part of the processes of implementing the above embodiment and equivalent changes made according to the claims of the present application are still within the scope covered by the present application.

Claims (11)

1. A heat exchanger, comprising:

a housing enclosing a receiving chamber, the housing having a first inlet and a first outlet, the first inlet and the first outlet being adapted to communicate the receiving chamber with an external space;

The fins are accommodated in the accommodating cavity, extend along the first direction, are distributed at intervals along the second direction, the gaps between two adjacent fins form flow channels, the width of the flow channels between the two adjacent fins in the second direction is D, the unit is mm, Wherein L _W is the total length of the fin after flattening in the first direction, the unit is mm, L ₀ is the straight line length of the runner in the first direction, the unit is mm, H is the height of the fin in the third direction, δ is the average thickness of the fin, the unit is mm, η is a constant of 0.85, and the first direction, the second direction and the third direction intersect.

2. The heat exchanger of claim 1, wherein the fins extend curvedly in the first direction, and wherein a plurality of the fins are equally spaced apart in the second direction.

3. The heat exchanger of claim 1, wherein the fins are welded to at least one inner surface of the housing.

4. The heat exchanger of claim 1, further comprising a connection portion through which adjacent two of the fins are connected.

5. The heat exchanger according to claim 4, wherein the number of the fins is 3 or more, the connection portions include a first connection portion and a second connection portion, the fin located in the middle in the second direction and two adjacent fins are connected by the first connection portion and the second connection portion, respectively, the first connection portion and the second connection portion are spaced apart in the third direction, and the first connection portion and the second connection portion each extend in the first direction.

6. The heat exchanger according to claim 5, wherein,

The first connecting portions and the second connecting portions are multiple, and the first connecting portions and the second connecting portions are alternately arranged along the second direction.

7. A heat exchanger according to claim 1 wherein,

The value range of L _W is 1.5mm-1100mm;

and/or H is in the value range of 0.5mm-50mm;

and/or L0 has a value ranging from 1mm to 1000mm;

and/or, the value range of delta is 0.1mm-50mm;

And/or D is in the range of 0mm-101mm.

8. The heat exchanger of claim 7, wherein D has a value in the range of 0.1mm to 50mm.

9. The heat exchanger of claim 1, further comprising a locating fin attached to an outer surface of the housing, the locating fin and the housing being of an integrally formed construction; the positioning wing comprises a positioning part.

10. A heat exchange system comprising a heat exchange member and a heat exchanger according to any one of claims 1 to 9, the heat exchange member being adapted to exchange heat through the heat exchanger.

11. A vehicle comprising the heat exchange system of claim 10.