阅读说明：本技术 一种换热器 (Heat exchanger ) 是由 不公告发明人 于 2018-06-29 设计创作，主要内容包括：发明公开了一种换热器,包括第一板片和第二板片,第一板片的第一板面侧设置有若干凸部,在第一板片的第二板面与相邻的第二板片的第一板面之间设置有翅片,而在第一板片设置有凸部一侧与相邻的第二板片的第二板面之间没有设置翅片,并且凸部的高度小于翅片的高度。这种换热器在第一流体通道中通过翅片提高扰流性,在第二流体通道中则通过若干凸部结构提高扰流性,可以使得第一流体通道中可以流通低压流体,第二流体通道中可以流通高压流体。(The invention discloses a heat exchanger which comprises a first plate and a second plate, wherein a plurality of convex parts are arranged on the side of a first plate surface of the first plate, fins are arranged between a second plate surface of the first plate and a first plate surface of the adjacent second plate, no fin is arranged between the side of the first plate provided with the convex parts and the second plate surface of the adjacent second plate, and the height of the convex parts is smaller than that of the fins. The heat exchanger has the advantages that the turbulence performance is improved through the fins in the first fluid channel, and the turbulence performance is improved through the structures of the plurality of convex parts in the second fluid channel, so that low-pressure fluid can flow in the first fluid channel, and high-pressure fluid can flow in the second fluid channel.)

1. A heat exchanger comprises a heat exchange core body, wherein the heat exchange core body comprises a plurality of first plate sheets, a plurality of second plate sheets and fins, the heat exchange core body is characterized in that the first plate sheets comprise first plate surfaces, a plurality of convex parts protruding out of the first plate surfaces and second plate surfaces opposite to the first plate surfaces, the second plate sheets comprise first plate surfaces and second plate surfaces opposite to the first plate surfaces, the heat exchange core body is formed by matching and installing the plurality of first plate sheets and the plurality of second plate sheets which are sequentially stacked, a first fluid channel and a second fluid channel which are mutually isolated are formed in the heat exchange core body, the fins are arranged between the second plate surfaces of the first plate sheets and the first plate surfaces of the adjacent second plate sheets, a first channel is formed between the second plate surfaces of the first plate sheets and the first plate surfaces of the adjacent second plate sheets, and the first channel is a part of the first fluid channel, and a second channel is formed between the first plate surface of the first plate and the second plate surface of the adjacent second plate, the second channel is a part of the second fluid channel, the height of the fin is greater than that of the convex part, and the ratio of the height of the fin to that of the convex part is greater than 1 and less than 4.

2. The heat exchanger of claim 1, wherein the first plate further comprises a first corner hole portion and a second corner hole portion recessed in the first plate surface, a third corner hole portion and a fourth corner hole portion protruding from the first plate surface, and a first concave portion and a second concave portion recessed in the first plate surface, wherein a convex structure corresponding to the first concave portion and the second concave portion of the first plate is arranged on the second plate surface side of the first plate, the first concave portion and the second concave portion of the first plate are connected, the second concave portion is arranged between the third corner hole portion and the fourth corner hole portion, and most of the convex portions are distributed on two sides of the first concave portion.

3. The heat exchanger of claim 2, wherein a portion of the protrusions are disposed in a region between a first corner hole portion and a second corner hole portion of the first plate, and a portion of the protrusions are disposed in a corner portion of the first plate adjacent to the first corner hole portion and a corner portion adjacent to the second corner hole portion;

the width of the two end parts of the first concave part of the first plate is larger than that of the middle part, and the width of the two end parts of the first concave part of the first plate is larger than that of the second concave part.

4. The heat exchanger according to claim 3, wherein the second plate further includes a first corner hole portion and a second corner hole portion protruding from the first plate surface, and a first concave portion and a second concave portion recessed from the first plate surface, wherein a convex structure corresponding to the first concave portion and the second concave portion of the second plate is provided on the second plate surface side of the second plate, the first concave portion and the second concave portion are connected, the second concave portion is provided between the first corner hole portion and the second corner hole portion of the second plate, the width of both end portions of the first concave portion of the second plate is larger than the width of the middle portion, and the width of both end portions of the first concave portion of the second plate is larger than the width of the second concave portion of the second plate.

5. The heat exchanger of claim 4, wherein the fin is disposed between a first plate face of the second plate and an adjacent second plate face of the first plate, the second plate is further provided with a third corner hole and a fourth corner hole, the fin includes the first porthole area corresponding to the first corner hole portion, the second porthole area corresponding to the second corner hole portion, the third porthole area corresponding to the third corner hole, the fourth porthole area corresponding to the fourth corner hole, and the cutaway area corresponding to the first recess, and a portion of the fin is located between the first corner hole portion and the second corner hole portion.

6. The heat exchanger of claim 5, wherein the fins are fenestrated fins, and the center lines of the windows of the fenestrated fins and the center lines of the flow channels of the fenestrated fins are parallel to the width direction of the third corner holes.

7. The heat exchanger according to claim 5, wherein the convex portion, the third corner hole portion and the fourth corner hole portion of the first plate are in contact with and fixed by welding to the second plate surface of the adjacent second plate, the convex structure corresponding to the second concave portion of the second plate is in contact with and fixed by welding to the first plate surface of the adjacent first plate, the convex structure corresponding to the first concave portion of the second plate is in contact with and fixed by welding to the first concave portion of the adjacent first plate, the depth of the first concave portion of the first plate is smaller than that of the second concave portion of the first plate, and the depth of the first concave portion of the second plate is smaller than that of the second concave portion of the second plate.

8. The heat exchanger according to any one of claims 1 to 7, further comprising top and bottom plates on either side of the heat exchange core, the bottom plate being disposed adjacent one of the first plates, the fins being disposed between the bottom plate and the adjacent first plate, and the top plate being disposed adjacent one of the second plates, the number of the first channels being one greater than the number of the second channels.

Technical Field

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

Background

Plate-fin heat exchangers are usually composed of plates and fins. A fluid channel is formed after the fins are arranged between two adjacent plates; a plurality of the plates are stacked in different modes according to actual requirements and are brazed into a whole to form a plate bundle; and assembling the plate bundle and corresponding parts such as an end socket, a connecting pipe, a support and the like to form the plate-fin heat exchanger.

Compared with the traditional heat exchanger, the plate-fin heat exchanger has a secondary surface and a very compact structure, the disturbance of the fins on the fluid continuously breaks the boundary layer of the fluid, and meanwhile, the plate-fin heat exchanger has very high efficiency due to the high heat conductivity of the plates and the fins.

Although the fin can improve the turbulence of the fluid, the problems of larger flow resistance and low pressure resistance exist at the same time, so that the plate-fin heat exchanger is difficult to be suitable for heat exchange between low-pressure fluid and high-pressure fluid.

Disclosure of Invention

In order to solve the technical problems, the invention provides a heat exchanger, which comprises a heat exchange core body, wherein the heat exchange core body comprises a plurality of first plate sheets, a plurality of second plate sheets and fins, and is characterized in that the first plate sheets comprise first plate surfaces, a plurality of convex parts protruding out of the first plate surfaces and second plate surfaces opposite to the first plate surfaces, the second plate sheets comprise first plate surfaces and second plate surfaces opposite to the first plate surfaces, the heat exchange core body is formed by matching and installing the plurality of first plate sheets and the plurality of second plate sheets which are sequentially stacked, a first fluid channel and a second fluid channel which are mutually isolated are formed in the heat exchange core body, the fins are arranged between the second plate surfaces of the first plate sheets and the first plate surfaces of the second plate sheets, and a first channel is formed between the second plate surfaces of the first plate sheets and the first plate surfaces of the second plate sheets, the first channel is a part of the first fluid channel, a second channel is formed between a first plate surface of the first plate and a second plate surface of the second plate, the second channel is a part of the second fluid channel, the height of the fin is greater than that of the convex part 15, and the ratio of the height of the fin to the height of the convex part is greater than 1 and less than 4.

The provided heat exchanger comprises a first plate and a second plate, wherein a plurality of convex parts are arranged on the side of the first plate, fins are arranged between the second plate of the first plate and the first plate of the adjacent second plate, no fin is arranged between the side of the convex part of the first plate and the second plate of the adjacent second plate, and the height of the convex part is smaller than that of the fin. The heat exchanger has the advantages that the turbulence performance is improved through the fins in the first fluid channel, and the turbulence performance is improved through the structures of the plurality of convex parts in the second fluid channel, so that low-pressure fluid can flow in the first fluid channel, and high-pressure fluid can flow in the second fluid channel.

Drawings

FIG. 1 is a schematic perspective view of one embodiment of a heat exchanger of the present invention.

Fig. 2 is a partially exploded schematic view of the base plate and heat exchange core of the heat exchanger of fig. 1.

Fig. 3 is a schematic view of a first plate configuration of the heat exchanger shown in fig. 1.

Figure 4 is a schematic view of a second plate configuration of the heat exchanger of figure 1.

Fig. 5 is a schematic view of the bottom plate structure of the heat exchanger shown in fig. 1.

Fig. 6 is a schematic view of a fin structure of the heat exchanger shown in fig. 1.

Fig. 7 is a schematic view of the second plate of the heat exchanger of fig. 1 in combination with fins.

Fig. 8 is a perspective view of a portion of the second plate and fin combination of the heat exchanger shown in fig. 1.

Fig. 9 is a schematic partial cross-sectional view of the heat exchange core of the heat exchanger of fig. 1.

Detailed Description

The following describes embodiments of the present invention with reference to the drawings.

Fig. 1 is a schematic perspective view of an embodiment of the heat exchanger of the present invention, and fig. 2 is a schematic partially exploded view of a bottom plate and a heat exchange core of the heat exchanger shown in fig. 1, and as shown in the figure, in the embodiment, the heat exchanger includes a top plate 3, a heat exchange core 1 and a bottom plate 2, and the heat exchange core includes a plurality of first plates 11, a plurality of second plates 12 and a plurality of fins 7. In this embodiment one of the first plates 11 is arranged adjacent to the bottom plate 2, between the bottom plate 2 and the first plate 11 is arranged a fin 7, which fin 7 is also part of the heat exchanger core 1, and one of the second plates 12 is arranged adjacent to the top plate 3.

A plurality of first plates 11 and a plurality of second plates 12 which are sequentially stacked are matched and installed to form a heat exchange core body 1, and a first fluid channel and a second fluid channel which are mutually isolated are arranged in the heat exchange core body 1. The heat exchanger further comprises a first connecting pipe 5 and a second connecting pipe 6, wherein the first connecting pipe 5 comprises a first interface channel 51, the second connecting pipe 6 comprises a second interface channel 61, the first interface channel 51 and the second interface channel 61 are respectively communicated with the first fluid channel, and the first interface channel 51 is communicated with the second interface channel 61 through the first fluid channel.

The heat exchanger further comprises an adapter 4, wherein the adapter 4 comprises a third interface channel 41 and a fourth interface channel 42, the third interface channel 41 and the fourth interface channel 42 are respectively communicated with the second fluid channel, and the third interface channel 41 is communicated with the fourth interface channel 42 through the second fluid channel. It should be noted here that the adapter 4 may also include two parts as the first adapter 5 and the second adapter 6, and the structure of the adapter adopted in this embodiment is beneficial to the installation of the external pipeline, and two external pipes respectively communicated with the third interface channel 41 and the fourth interface channel 42 may be fixedly installed by one pressing block, so that the installation is convenient, and the material is also saved.

As shown in fig. 2 and 3, the first plate 11 includes a first plate 110, a first corner hole 101 and a second corner hole 102 recessed in the first plate 110, a third corner hole 103 and a fourth corner hole 104 protruding from the first plate 110, a plurality of protrusions 115 protruding from the first plate 110, and a first recess 116 and a second recess 117 recessed in the first plate 110.

First corner hole 111 is provided in first corner hole 101, second corner hole 112 is provided in second corner hole 102, third corner hole 113 is provided in third corner hole 103, and fourth corner hole 114 is provided in fourth corner hole 104. The first corner hole 111 and the second corner hole 112 are circular holes, the first corner hole 111 is communicated with the fourth port 42, and the second corner hole 112 is communicated with the third port 41. The third and fourth holes 113 and 114 are oval holes, the third hole 113 is communicated with the second port 61, and the fourth hole 114 is communicated with the first port 51. Here, it should be noted that the third corner hole 113 and the fourth corner hole 114 may have other shapes such as a circular shape.

The protruding portions 115 are distributed in the area of the first board surface 110, and in this embodiment, most of the protruding portions 115 are distributed between the first corner hole portion 101 and the third corner hole portion 103, and between the second corner hole portion 102 and the fourth corner hole portion 104. In order to improve the heat exchange performance of the heat exchanger, a convex portion 115 is also disposed between the first corner hole portion 101 and the second corner hole portion 102, and the convex portion 115 may perform a flow guiding function, thereby improving a heat transfer coefficient of a region between the first corner hole portion 101 and the second corner hole portion 102. Similarly, the convex portions 115 may be provided at the corners of the first plate 11 adjacent to the first corner hole 101 and the second corner hole 102, and the convex portions 115 may also serve as a flow guide, so that the heat transfer coefficient of the corner regions may be increased.

The first concave portion 116 is connected to the second concave portion 117, the second concave portion 117 is disposed between the third corner hole portion 103 and the fourth corner hole portion 104, the first concave portion 116 is disposed in the distribution area of the convex portion 115, that is, most of the convex portion 115 is distributed on two sides of the first concave portion 116, in this embodiment, the convex portion 115 is distributed on two sides of the first concave portion 116 more uniformly, and at least a part of the convex portion is distributed symmetrically on two sides of the first concave portion 116. The arrangement mode can improve the turbulence of the fluid and simultaneously can ensure that the fluid is uniformly distributed, thereby improving the heat exchange performance of the heat exchanger.

The first concave part 116 is in a dumbbell-shaped structure with the width of the two end parts being larger than that of the middle part, the first concave part 116 can play a role in guiding flow, uniform distribution of fluid is facilitated, flow resistance is low, and heat exchange performance can be improved.

In the embodiment, the width of the two end portions of the first recess 116 is greater than the width of the second recess 117, and this arrangement makes the area of the heat exchange region between the first corner hole 111 and the second corner hole 112 larger, which is beneficial to improving the heat exchange performance of the heat exchanger.

It should be noted here that a concave structure (not shown in the figure) corresponding to the convex structure and a convex structure (not shown in the figure) corresponding to the concave structure are provided on the side of the second plate surface (not shown in the figure) opposite to the first plate surface 110 of the first plate 11.

As shown in fig. 2 and 4, the second plate 12 includes a first plate 120, first and second corner hole portions 105 and 106 protruding from the first plate 120, and first and second concave portions 116 and 117 recessed in the first plate 110.

The first corner hole portion 105 is provided with a first corner hole 121, the second corner hole portion 106 is provided with a second corner hole 122, and the second plate is further provided with a third corner hole 123 and a fourth corner hole 124. The first corner hole 121 and the second corner hole 122 are circular holes, the first corner hole 121 is communicated with the fourth port 42, and the second corner hole 122 is communicated with the third port 41. The third and fourth corner holes 123 and 124 are oval holes, the third corner hole 123 communicates with the second port 61, and the fourth corner hole 124 communicates with the first port 51. It should be noted here that the third corner hole 123 and the fourth corner hole 124 may have other shapes such as a circular shape.

The first concave portion 126 and the second concave portion 127 are connected, and the second concave portion 127 is provided between the third corner hole portion 105 and the fourth corner hole portion 106. The first concave portion 126 is in a dumbbell-shaped structure with the width of the two end portions larger than that of the middle portion, the first concave portion 126 can play a role in guiding flow, uniform distribution of fluid is facilitated, flow resistance is low, and heat exchange performance can be improved.

In the present embodiment, the width of both end portions of the first recess 126 is larger than the width of the second recess 127. The arrangement mode enables the area of the heat exchange area between the first corner hole 121 and the second corner hole 122 to be larger, and is beneficial to improving the heat exchange performance of the heat exchanger.

It should be noted here that a concave structure corresponding to the convex structure and a convex structure corresponding to the concave structure are provided on the second plate surface (not shown in the figure) side of the second plate 12 opposite to the first plate surface 120.

As shown in fig. 6 and 7, the first plate surface 120 of the second plate 12 is provided with a fin 7. The fin 7 includes a first porthole area 71 corresponding to the first corner hole portion 105, a second porthole area 72 corresponding to the second corner hole portion 106, a third porthole area 73 corresponding to the third corner hole 123, a fourth porthole area 74 corresponding to the fourth corner hole 124, and a cutaway area 75 corresponding to the first recess 126. And a part of the fin 7 is positioned between the first corner hole part 105 and the second corner hole part 106, so that on one hand, the flow guiding effect can be achieved, and on the other hand, the turbulence of the cooling liquid in the area is improved, so that the cooling liquid and the refrigerant can fully exchange heat in the refrigerant inlet and outlet area, and the heat exchange performance is improved. And no fin is arranged between the third hole 123 and the fourth hole 124, and because the refrigerant is less in the areas near the third hole 123 and the fourth hole 124, the arrangement mode can match the amount of the cooling liquid and the amount of the refrigerant, thereby being beneficial to improving the heat exchange performance.

As shown in fig. 8, in the present embodiment, the fin 7 is a fenestration fin, and the center line of the window 76 of the fenestration fin 7 and the center line of the flow channel 75 of the fenestration fin 7 are parallel to the width direction of the third angular hole 123. This is advantageous for reducing the flow resistance of the coolant, thereby improving the heat exchange performance. Here, the width direction of the third hole 123 is the width direction of the lumbar circular hole, and when the third hole 123 has another structure, the width direction is still the same as the width direction of the lumbar circular hole.

As shown in fig. 2 to 9, the first plate surface 110 of the first plate 11 is disposed opposite to the second plate surface of the second plate 12, the convex portion 115, the third corner hole portion 13, and the fourth corner hole portion 14 of the first plate 11 are in contact with and fixed by welding to the second plate surface of the second plate 12, the convex structure corresponding to the second concave portion 127 of the second plate 12 is in contact with and fixed by welding to the first plate surface of the first plate 11, and the convex structure corresponding to the first concave portion 126 of the second plate 12 is in contact with and fixed by welding to the first concave portion 116 of the first plate 11, so that a part of the second fluid channel is formed between the first plate surface 110 of the first plate 11 and the second plate surface of the second plate 12. And the depth of the first concave part 116 of the first plate 11 is smaller than the depth of the second concave part 117 of the first plate 11, and the depth of the first concave part 126 of the second plate 12 is smaller than the depth of the second concave part 127 of the second plate 12, so that the structure is simple to process and install, and the area of the first plate surface is larger, which is beneficial to improving the heat exchange performance.

Since the convex structures corresponding to the first concave portion 126 and the second concave portion 127 of the second plate 12 play a role of blocking, the refrigerant flowing in from the first corner hole 111 sequentially passes through the region where the convex portion 115 on one side of the first concave portion 116 of the first plate 11 is located, the region where the second concave portion 117 of the first plate 11 is located, and the region where the convex portion 115 on the other side of the first concave portion 116 of the first plate 11 is located, and then flows out from the second corner hole 112.

The second plate surface of the first plate 11 is arranged opposite to the first plate surface 120 of the second plate 12, the fin 7 is arranged between the second plate surface of the first plate 11 and the first plate surface 120 of the second plate 12, the first corner hole portion 105 and the second corner hole portion 106 of the second plate 12 are in contact with and fixed by welding the corresponding protruding structures of the first corner hole portion 101 and the second corner hole portion 102 of the first plate 11, the protruding structure corresponding to the second concave portion 117 on the second plate surface side of the first plate 11 is in contact with and fixed by welding the first plate surface 120 of the second plate 12, and the protruding structure corresponding to the first concave portion 116 of the first plate 11 is in contact with and fixed by welding the first concave portion 126 of the second plate 12. This forms part of the first fluid passageway between the first plate face 120 of the second plate 12 and the second plate face of the first plate 11.

Because the corresponding convex structures of the first concave part 116 and the second concave part 117 of the first plate 11 play a role of blocking, the cooling liquid flowing in from the third angle hole 123 sequentially passes through the fin area on one side of the first concave part 126 of the second plate 12, the area where the second concave part 127 of the second plate 12 is located and the fin area on the other side of the first concave part 126 of the second plate 12, and then flows out from the fourth angle hole 123, and the turbulence performance of the cooling liquid can be improved by arranging the fins, and the performance of the heat exchanger is improved.

In this embodiment, the channel formed between the second plate surface of the first plate 11 and the first plate surface 120 of the second plate 12 is a first channel (not shown in the figure), the channel formed between the first plate surface 110 of the first plate 11 and the second plate surface of the second plate 12 is a second channel (not shown in the figure), and the number of the first channels is one more than that of the second channels, so that the refrigerant can sufficiently absorb heat, thereby ensuring the superheat degree.

As shown in fig. 9, the distance between the second plate surface of the first plate 11 and the first plate surface 120 of the second plate 12 (i.e., the height of the fin 7) is h2, the distance between the first plate surface 110 of the first plate 11 and the second plate surface of the second plate 12 (i.e., the height of the projection 15) is h1, and the following conditions are satisfied: 1< H2/H1 < 4. This arrangement can improve the heat transfer coefficient.

The foregoing is illustrative of the present invention and is not to be construed as limiting thereof in any way. Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can now make numerous changes and modifications to the disclosed embodiments, and equivalents thereof, without departing from the scope of the invention as set forth in the claims below. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present invention are still within the scope of the protection of the technical solution of the present invention, unless the contents of the technical solution of the present invention are departed.