CN115682784A - Heat exchanger - Google Patents

Abstract

The application discloses a heat exchanger, including the heat transfer core, the heat transfer core includes many slab, the heat transfer core includes first sub-core to nth sub-core along the range upon range of orientation of many slab in proper order, N is greater than or equal to 3, first flow includes first flow to nth flow, first flow is located first sub-core to nth sub-core respectively to nth flow, first flow includes a plurality of first inter-plate passageways of corresponding sub-core in first sub-core to the nth sub-core respectively to the nth flow, first flow communicates in proper order to the nth flow, the quantity of the first inter-plate passageway that the definition is located first flow is A1, the quantity of the first inter-plate passageway that the definition is located the nth flow is An, the total quantity of the first inter-plate passageway of definition heat transfer core is N, wherein:

A1<and An, optimizing the heat exchange performance of the heat exchanger by controlling the relation among A1, an, N and N.

Description

Heat exchanger

Technical Field

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

Background

Generally, fluid channels in the heat exchanger are set to be a plurality of flows so as to prolong the flow path of fluid and improve the heat exchange effect of the heat exchanger.

Disclosure of Invention

An object of this application is to provide a heat exchanger to be favorable to improving the heat transfer effect of heat exchanger.

In order to achieve the purpose, the following technical scheme is adopted in the application: a heat exchanger comprises a heat exchange core body, wherein the heat exchange core body comprises a plurality of plate sheets, the plate sheets are stacked to form a plurality of inter-plate channels, the inter-plate channels comprise first inter-plate channels and second inter-plate channels, the heat exchange core body further comprises a first flow channel and a second flow channel which are not communicated with each other, the first inter-plate channels are part of the first flow channel, the second inter-plate channels are part of the second flow channel, the heat exchange core body sequentially comprises a first sub-core body, a second sub-core body, an 8230and An nth sub-core body along the stacking direction of the plate sheets, the first flow channel comprises An inlet, a first flow channel, a second flow channel, an 8230, and An nth flow channel, the inlet of the first flow channel is communicated with the first flow channel, the first process is located in the first sub-core body, the second process is located in the second sub-core body, \8230, the nth process is located in the nth sub-core body, the first process comprises first interplate channels located in the first sub-core body, the second process comprises first interplate channels located in the second sub-core body, \8230, the nth process comprises first interplate channels located in the nth sub-core body, the N-1 process is communicated with the adjacent process, the number of the first interplate channels located in the first process is defined as A1, the number of the first interplate channels located in the nth process is defined as An, and the total number of the first interplate channels of the heat exchange core body is defined as N, wherein: n is more than or equal to 3, N (An-A1)/N is more than or equal to 1.1 and A1 is less than An.

The beneficial effect of this application: the fluid exchanges heat in a first flow, and the conditions are met by controlling A1, an, N and N:

and the number of the first interplate channels of the last process of the heat exchanger is larger than that of the first interplate channels of the first process, the relationship between the difference (An-A1) between the number of the first interplate channels of the last process of the heat exchanger and the number of the first interplate channels of the first process and the number of the first interplate channels of each average process of the heat exchanger is adjusted, and the number of the first interplate channels of the first process and the number of the first interplate channels of the last process are adjusted relative to the number of the first interplate channels of the heat exchange core bodyThe proportion of the total number of the channels is beneficial to the fluid in the last flow to quickly flow out of the heat exchanger, so that the pressure drop of the last flow of the heat exchanger is reduced, the reduction of the pressure drop of the last flow of the heat exchanger is beneficial to reducing the pressure drop of the first flow of the heat exchanger, and the reduction of the pressure drop of the first flow of the heat exchanger is beneficial to improving the heat exchange effect of the first flow because the heat exchange coefficient of the fluid in the first flow of the heat exchanger is larger, so that the heat exchange quantity of the heat exchanger is improved, and the heat exchange effect of the heat exchanger is further beneficial to improving.

Drawings

FIG. 1 is a perspective view of one perspective of one embodiment of a heat exchanger of the present application;

FIG. 2 is an exploded view of the heat exchanger shown in FIG. 1;

FIG. 3 is a schematic cross-sectional view of the heat exchanger shown in FIG. 1;

FIG. 4 is a schematic view of a portion A of FIG. 3;

FIG. 5 is a schematic view of a portion of the enlarged structure at B in FIG. 3;

FIG. 6 is another schematic cross-sectional configuration of the heat exchanger shown in FIG. 1;

FIG. 7 is a schematic view of a portion of the enlarged structure at C in FIG. 6;

FIG. 8 is an enlarged partial schematic view of FIG. 6 at D;

fig. 9 is a perspective view of a sheet at one view angle of the first sub-core;

fig. 10 is a perspective view of another view of the plate located in the first sub-core;

fig. 11 is a partial cross-sectional structural view of a plate located in the first sub-core;

FIG. 12 is a perspective view of a first plate from one perspective;

FIG. 13 is a perspective view of another perspective of the first plate;

fig. 14 is a perspective view of a sheet at one view angle of the second sub-core;

FIG. 15 is a perspective view of a second plate from one perspective;

fig. 16 is a perspective view from one perspective of a sheet located in the third sub-core;

FIG. 17 is a schematic refrigerant flow path diagram of the heat exchanger shown in FIG. 1;

FIG. 18 is another schematic medium flow path of the heat exchanger shown in FIG. 1;

FIG. 19 is a refrigerant flow path schematic of another embodiment of the heat exchanger of the present application;

FIG. 20 is an enlarged partial schematic view of FIG. 19 at E;

FIG. 21 is a partial cross-sectional structural view of a fin;

FIG. 22 is a refrigerant flow path schematic of yet another embodiment of the heat exchanger of the present application;

FIG. 23 is another refrigerant flow path schematic of the heat exchanger shown in FIG. 22;

FIG. 24 is a further refrigerant flow path schematic of the heat exchanger shown in FIG. 22;

FIG. 25 is a refrigerant flow path schematic of yet another embodiment of the heat exchanger of the present application;

FIG. 26 is another refrigerant flow path schematic of the heat exchanger shown in FIG. 25;

fig. 27 is a further refrigerant flow path schematic of the heat exchanger shown in fig. 25.

Detailed Description

The present invention is further illustrated in the following detailed description and specific examples in conjunction with fig. 1-27, wherein numerous specific details are set forth in order to provide a thorough understanding of the present invention. Those skilled in the art will appreciate that the specific components, devices, and features illustrated in the accompanying drawings and described herein are merely exemplary and should not be considered as limiting.

With reference to fig. 1 to 27, a heat exchanger 10 includes a heat exchange core 20, the heat exchange core 20 includes a plurality of plates 30, the plurality of plates 30 are stacked and form inter-plate passages, each inter-plate passage includes a first inter-plate passage 25 and a second inter-plate passage 26, the heat exchange core 20 further includes a first flow channel and a second flow channel that are not communicated with each other, the first inter-plate passage 25 is a part of the first flow channel, the second inter-plate passage 26 is a part of the second flow channel, the first flow channel is used for fluid circulation, the fluid circulating in the heat exchanger 10 is in a gas-liquid two-phase state, the second flow channel is used for circulation of another medium, and the another medium may be water, a coolant added with an antifreeze, or the like; the heat exchange core 30 sequentially comprises a first sub-core body 81, a second sub-core body 82, 8230, an nth sub-core body, n is more than or equal to 3, a plurality of first inter-plate channels 25 are respectively positioned between the first sub-core body 81 and the nth sub-core body, the first flow channel comprises an inlet, a first flow path 50, a second flow path 51, 8230, the nth flow path is positioned between the nth sub-core body, the inlet of the first flow path is communicated with the first flow path 50, the first flow path 50 is positioned on the first sub-core body 81, the second flow path 51 comprises first inter-plate channels positioned on the second sub-core body 82, the second flow path 51 is positioned on the second sub-core body 82, the nth flow path comprises first inter-plate channels positioned on the nth sub-core body, the n-1 flow path is communicated with the adjacent flow path, the plate 30 comprises the first inter-plate channels 40 to the nth-1 plate, the first inter-plate channels are positioned between the nth sub-core body 82, the n-plate channels are positioned on the nth sub-core body, the n side plates 41 are positioned between the first inter-plate channels, the first inter-plate channels are positioned between the first sub-core body 40, the first flow path 25 is positioned on the second sub-plate 40, the second side plates, the n side plates 25 comprises a plurality of the first sub-plate 40, and the second inter-plate 40 side plates 40, and the plurality of the n side plates 40 side plates 25 are positioned between the plurality of the first flow path, the plurality of the n side plates 40 are positioned between the first side plates 40; specifically, the plate 30 includes a first corner hole 31, a second corner hole 32, a third corner hole 33 and a fourth corner hole 34, the first corner holes 31 of the multiple plates 30 are at least partially aligned in the stacking direction of the multiple plates 30 to form a first pore passage 21, the second corner holes 32 of the multiple plates 30 are at least partially aligned in the stacking direction of the multiple plates 30 to form a second pore passage 22, the third corner holes 33 of the multiple plates 30 are at least partially aligned in the stacking direction of the multiple plates 30 to form a third pore passage 23, the fourth corner holes 34 of the multiple plates 30 are at least partially aligned in the stacking direction of the multiple plates 30 to form a fourth pore passage 24, the first pore canal 21 and the second pore canal 22 are located on the same side of the width direction of the plate 30, the width direction of the plate 30 is Wb direction shown in fig. 9, the third pore canal 23 and the fourth pore canal 24 are located on the same side of the width direction of the plate 30, the first pore canal 21 and the third pore canal 23 are located on different sides of the width direction of the plate 30, the first plate 40 separates the first pore canal 21 into a first sub-pore canal 211 and a second sub-pore canal 212, the first sub-pore canal 211 is farther from the second plate 41 than the second sub-pore canal 212, the second plate 41 separates the second pore canal 22 into a third sub-pore canal 221 and a fourth sub-pore canal 222, the fourth sub-pore canal 222 is farther from the first plate 40 than the third sub-pore canal 221, a plurality of first inter-plate passages 25 located on the side of the first plate 40 away from the second plate 41 communicate the first sub-pore canal 211 with the third sub-pore canal 221, a plurality of first inter-plate passages 25 located between the first plate 40 and the second plate 41 communicate the third sub-pore canal 221 with the second sub-pore 212, at least part of the first interplate channels 25 on the side of the second plate 41 away from the first plate 40 communicate with the second sub-channels 212 and the fourth sub-channels 222, the first flow path 50 includes a plurality of first interplate channels 25 on the side of the first plate 40 away from the second plate 41, the second flow path 51 includes a plurality of first interplate channels 25 between the first plate 40 and the second plate 41, the third flow path 52 includes a plurality of first interplate channels 25 on the side of the second plate 41 away from the first plate 40, fluid flowing into the first flow path of the heat exchanger 10 exchanges heat firstly in the first flow path 50, and then exchanges heat sequentially in the second flow path 51, the third flow path 52, and the like, the flow directions of the fluid in the two adjacent flow paths are different, and the heat exchange effect of the heat exchanger 10 is improved by prolonging the flow path of the gas-liquid two-phase fluid in the heat exchanger 10.

It is understood that the shape of the plate 30 may be any shape such as a circle, a triangle, etc.; plural in the specification means two or more; the first sheet 40 to the nth sheet serve as the separation flow path, the sheet 30 may not include the first sheet 40 to the nth sheet, and the first flow path 50 to the nth flow path may be separated in other manners. The fluid flowing through the first flow passage of the heat exchanger is a gas-liquid two-phase refrigerant, but of course, the fluid flowing through the first flow passage may be a medium other than the refrigerant.

The heat exchanger 10 further comprisesThe first side plate 11 and the second side plate 12 are located on different sides of the heat exchange core 20 along the stacking direction of the plurality of plates 30, the first side plate 11 is located on one side of the first plate 40 departing from the second plate 41, the second side plate 12 is located on one side of the second plate 41 departing from the first plate 40, and the first side plate 11 and the second side plate 12 are respectively and fixedly connected with the outermost plates 30 of the corresponding heat exchange core 20; the number of the flow paths of the heat exchanger 10 is N, N is greater than or equal to 3, the number of the first interplate channels 25 located in the first flow path 50 is defined as A1, the number of the first interplate channels 25 located in the nth flow path is defined as An, and the total number of the first interplate channels 25 of the heat exchange core 20 is defined as N, wherein:

in An embodiment of the present application, the heat exchanger 10 serves as An evaporator, a gas-liquid two-phase fluid exchanges heat in the first process 50, the fluid in the first process 50 of the heat exchanger 10 is mainly in a liquid state, the fluid in the last process of the heat exchanger 10 is mainly in a gas state, the heat exchange coefficient of the fluid in the first process 50 is greater than that of the fluid in the last process, and the conditions are satisfied by controlling A1, an, N, and N:

and the number of the first interplate channels of the last flow of the heat exchanger is greater than that of the first interplate channels of the first flow, the relationship between the difference (An-A1) between the number of the first interplate channels of the last flow of the heat exchanger and the number of the first interplate channels of the first flow and the number of the first interplate channels of each average flow of the heat exchanger is adjusted, the ratio of the number of the first interplate channels of the first flow 50 and the number of the first interplate channels of the last flow to the total number of the first interplate channels of the heat exchange core is adjusted, and the rapid outflow of the fluid mainly in a gaseous state from the heat exchanger in the last flow is facilitated, so that the pressure drop of the last flow of the heat exchanger is reduced, and the n-1 flow is communicated with the flow adjacent to the flow, and the reduction of the pressure drop of the last flow of the heat exchanger is facilitatedThe pressure drop of the first flow of the heat exchanger is reduced, because the heat exchange coefficient of the fluid in the first flow of the heat exchanger is larger, the reduction of the pressure drop of the first flow of the heat exchanger is beneficial to improving the heat exchange effect of the first flow, thereby improving the heat exchange quantity of the heat exchanger, because the heat exchange coefficient of the fluid in the last flow of the heat exchanger is smaller, and the number of channels between the first plates in the last flow is more, thereby influencing the heat exchange effect of the heat exchanger on the whole, reducing the heat exchange quantity of the heat exchanger, and controlling the heat exchange quantity of the heat exchanger

Is not less than 0.25 and not more than 1.1, so that the above-mentioned increase amount of the heat exchange amount is larger than the decrease amount of the heat exchange amount, thereby improving the heat exchange effect of the heat exchanger 10 as a whole.

It will be understood that the number A1 of first plate interspaces 25 in the first pass 50, the number An of first plate interspaces 25 in the nth pass, the number N of passes of the heat exchanger 10 and the total number N of first plate interspaces 25 of the heat exchanger core 20 may also be such that:

a1 and An satisfy:

the ratio of the number of the first inter-plate channels of the first flow path 50 to the total number of the first inter-plate channels of the heat exchange core 20 and the number of the first inter-plate channels of the last flow path is further reduced, the ratio of the number of the first inter-plate channels of the last flow path to the total number of the first inter-plate channels of the heat exchange core 20 and the number of the first inter-plate channels of the first flow path 50 is increased, and the increase amount of the heat exchange amount between the refrigerant and another medium in the first flow path 50 is larger than the decrease amount of the heat exchange amount between the refrigerant and another medium in the last flow path, so that the heat exchange effect of the heat exchanger 10 is integrally further improved; in other embodiments, the heat exchanger 10 may also be used as an intermediate heat exchanger, and the first flow path is a high pressure flow path and will not be described in detail.

In some embodiments, with reference to fig. 1-18, the heat exchanger 10 further includes a first connection pipe 13 and a second connection pipe 14, the first connection pipeThe connecting pipe 13 is fixedly connected with the first side plate 11, the first connecting pipe 13 is communicated with the first sub-pore passage 211, specifically, the first connecting pipe 13 penetrates through the first side plate 11 and is communicated with the first sub-pore passage 211, and the first connecting pipe 13 is used as an inlet of the first flow passage; the second connecting pipe 14 is fixedly connected with the second side plate 12, the second connecting pipe 14 is communicated with the fourth sub-aperture 222, and specifically, the second connecting pipe 14 penetrates through the second side plate 12 and is communicated with the fourth sub-aperture 222; the number of passes N =3 for the heat exchange core 20, the third pass 52 comprises a plurality of first plate-to-plate channels 25 on the side of the second plate 41 facing away from the first plate 40, the number A1 of first plate-to-plate channels 25 in the first pass 50, the number A3 of first plate-to-plate channels 25 in the third pass 52 and the total number N of first plate-to-plate channels 25 of the heat exchange core 20 are such that:

the number of first interplate channels 25 located in the second pass 51 is defined as A2, A1 and A2 satisfying:

in addition, A2 < A3, the ratio of the liquid state of the refrigerant in the third flow path 52 is lower in the third flow path 52 compared with the first flow path 50 and the second flow path 51, the main heat exchange area of the heat exchanger 10 is in the first flow path 50 and the second flow path 51, by controlling the relationship between A1, A3 and N, the heat exchange effect and the pressure drop of the first flow path 50 and the third flow path 52 are optimized, by controlling the ratio between A1 and A2, excessive or insufficient number of channels between the first plates in the second flow path 51 is avoided, excessive number of channels between the first plates in the second flow path 51 is avoided, so that the refrigerant is uniformly distributed in each channel 25 between the first plates in the second flow path 51 of the second flow path 51, the heat exchange effect of the refrigerant in the second flow path 51 of the heat exchanger 10 with another medium is improved, excessive number of channels between the first plates in the second flow path 51 is avoided, and thus the second flow path 51 is ensured to have enough heat exchange area to ensure that the refrigerant in the second flow path 51 has a better heat exchange effect with another medium, and to avoid the pressure drop increase in the second flow path 51 of the refrigerant 10; the number of the flow of the heat exchanger is controlled to be 3, so that the refrigerant mainly in a gaseous state flows out of the heat exchanger quickly after exchanging heat with another medium in the third flow 52The heat exchanger 10 is used for reducing the pressure drop caused by the circulation of the refrigerant mainly in the gaseous state in the first flow path, and reducing the influence on the heat exchange between the refrigerant in the first flow path 50 and the refrigerant in the second flow path 51 of the heat exchanger 10 and another medium as much as possible.

A1 and A2 are both smaller than A3, so that the refrigerant mainly in the gaseous state in the third flow path 52 can flow out quickly, the pressure drop of the heat exchanger can be reduced, if A1 and A2 are larger than A3, the refrigerant mainly in the gaseous state in the third flow path 52 can not flow out quickly, and the pressure drop of the heat exchanger can not be reduced easily.

It is understood that the first adapter tube 13 and the second adapter tube 14 can also be a joint or the like; the second connecting pipe 14 may also not be fixedly connected to the second side plate 12, the second connecting pipe 14 penetrates through the first side plate 11 and the second plate 41, the outer wall of the second connecting pipe 14 is fixedly connected to the first side plate 11 and the second plate 41, respectively, one end of the second connecting pipe 14 is located on one side of the first side plate 11 away from the heat exchange core 20, and the other end of the second connecting pipe 14 is communicated with the fourth sub-duct 222, so that the first connecting pipe 13 and the second connecting pipe 14 are located on the same side of the height direction of the heat exchanger 10, and the height direction of the heat exchanger 10 is the Ha direction shown in fig. 1, thereby reducing the height of the heat exchanger 10 and facilitating the installation of the heat exchanger 10.

In some embodiments, with reference to fig. 1-16 and 19-20, the heat exchanger core 20 has a flow number n of 4, the plate 30 comprises a first plate 40 to a third plate 42, the third plate 42 is located on the side of the second plate 41 facing away from the first plate 40, the third plate 42 divides the second sub-channel 212 into a first cavity 2121 and a second cavity 2122, the first cavity 2121 is closer to the first plate 40 than the second cavity 2122, the first plate passages 25 between the first plate 40 and the second plate 41 communicate with the third sub-channel 221 and the first cavity 2121, the first plate passages 25 between the second plate 41 and the third plate 42 communicate with the first cavity 2121 and the fourth sub-channel 222, the first plate passages 25 on the side of the third plate 42 facing away from the second plate 41 communicate with the fourth sub-channel 222 and the second cavity 2122, the first flow 50 comprises the first passages 25 on the side of the first plate 40 facing away from the second plate 41, the second flow comprises the third plate passages 51 between the first plate 40 and the second plate 41, and the third plate passages 25 between the second plate 41, and the first flow 50 comprises the third plate 41The process 52 includes a plurality of first interplate passages 25 between the second plate 41 and the third plate 42, the fourth process 53 includes a plurality of first interplate passages 25 on the side of the third plate 42 away from the second plate 41, the first connection pipe 13 is fixedly connected to the first plate 11, the first connection pipe 13 is communicated with the first sub-port 211, the second connection pipe 14 is fixedly connected to the second plate 12, and the second connection pipe 14 is communicated with the second cavity 2122, specifically, the first connection pipe 13 penetrates through the first plate 11 and is communicated with the first sub-port 211, and the second connection pipe 14 penetrates through the second plate 12 and is communicated with the second cavity 2122; the number A1 of first plate interspaces 25 in the first pass 50, the number A4 of first plate interspaces 25 in the fourth pass 53 and the total number N of first plate interspaces 25 of the heat exchanger core 20 satisfy:

the number of first plate-to-plate passages 25 in the second flow path 51 is defined as A2, and the number of first plate-to-plate passages 25 in the third flow path 52 is defined as A3, wherein:

compared to the first to third flow paths 50 to 52, the number of the first interplate passages 25 in the fourth flow path 54 is the largest, that is, the number of the first interplate passages in the first to third flow paths 50 to 52 is smaller than that in the fourth flow path 54; the number 25 of the first interplate channels in each of the second flow path 51 to the fourth flow path 54 is not less than the number 25 of the first interplate channels in the first flow path 50, if the heat exchanger 10 needs to have a high heat exchange effect, the flow path of the refrigerant in the heat exchanger 10 is extended by the arrangement of the four flow paths, so that the heat exchange effect of the heat exchanger 10 is improved, the heat exchange effect and the pressure drop of the first flow path 50 and the fourth flow path 53 are optimized by controlling the ratio of the number of the first interplate channels 25 in the first flow path 50 and the fourth flow path 53, and the refrigerant in the first flow path 50 and the other interplate channel isThe medium still has stronger heat exchange capacity after heat exchange, the number of channels between the first plates in the second flow path 51 and the third flow path 52 is controlled to be more than that in the first flow path 50, so that the refrigerant still having stronger heat exchange capacity can effectively exchange heat with another medium in the second flow path 51 and the third flow path 52, and the number of channels between the first plates in the second flow path 51 and the third flow path 52 is controlled not to be more than that in the fourth flow path 53, so that the heat exchanger is prevented from having more channels between the first plates 25 on the basis of better heat exchange effect, and the height of the heat exchanger is prevented from being too large, so that the heat exchanger is convenient to install.

In some embodiments, with reference to fig. 9-16, the plate 30 includes a first base surface 35 and a second base surface 36 perpendicular to the stacking direction of the plurality of plates 30, the plate 30 further includes a plurality of first protrusions 37 protruding from the first base surface 35, at least a portion of the first protrusions are located in the first plate passages 25, as shown in fig. 9-11, the first protrusions 37 include first top end portions 371 and first bottom end portions 372, the first top end portions 371 are located on a side of the first base surface 35 facing away from the second base surface 36, the first top end portions 371 are ends of the first protrusions 37 away from the first base surface 35 of the plate 30 in the stacking direction of the plurality of plates 30, and when an end of the first protrusion 37 away from the first base surface 35 of the plate 30 is an end point or a plane or a line segment, the first top end portions 371 are corresponding end points or plane center points or line segment midpoints of the plane or the line segment; at least part of the first protrusions 37 are arranged along the length direction of the plate 30, the length direction of the plate 30 is the Lb direction shown in fig. 9, the plate 30 further includes a plurality of first recesses 38 recessed in the second base surface 36 and corresponding to the first protrusions 37, that is, at least part of the first recesses 38 are arranged along the length direction of the plate 30, and the first protrusions 37 and the first recesses 38 are provided on the plate 30, so that the flow disturbing capacity of the plate 30 on the refrigerant in the first flow channel and another medium in the second flow channel is improved, and the heat exchange effect of the heat exchanger 10 is further improved.

It is understood that, in the stacking direction of the plurality of plates 30, a portion of the first protrusion 37 protrudes from the first base surface 35 of the plate 30, another portion of the first protrusion 37 also protrudes from the second base surface 36 of the plate 30, the first top end 371 is located at the portion of the first protrusion 37 protruding from the first base surface 35 and is away from the first base surface 35 in the stacking direction of the plurality of plates 30, the first bottom end 372 is located at the portion of the first protrusion 37 protruding from the second base surface 36 and is away from the second base surface 36 in the stacking direction of the plurality of plates 30, the first bottom end 372 is away from the second base surface 36 of the plate 30 in the stacking direction of the plurality of plates 30, and like the first top end 371, the first bottom end 372 may be an end point or a midpoint of a center point or a line segment of a plane.

As shown in fig. 9-11 and 14, 16, the distance between the first top end 371 of two adjacent first protrusions 37 in the length direction of the sheet 30 is defined as L1, the length direction of the sheet 30 is defined as Lb direction shown in fig. 9, the distance between the first top end 371 and the first bottom end 372 of the first protrusion 37 in the stacking direction of the plurality of sheets 30 is defined as H1, the sheet 30 located in the first sub-core 81 is defined as B1, the ratio of L1 to H1 of the sheet 30 located in the second sub-core 82 is defined as B2, the ratio of L1 to H1 of the sheet 30 located in the third sub-core 83 is defined as B3, wherein: b1 is more than or equal to 2 and less than or equal to 3.2, B2 is more than or equal to 3.2 and less than or equal to 4, B3 is more than or equal to 3.2 and less than or equal to 4,

by controlling the sizes of the plates B1, B2 and B3, the turbulent flow capacity of the plates 30 positioned in the first sub-core 81 and the second sub-core 82 to the refrigerant and another medium is enhanced, and the turbulent flow capacity of the plates 30 positioned in the third sub-core 83 to the refrigerant and the another medium is weakened, so that the refrigerant mainly in a gaseous state in the third flow 52 can quickly flow out of the heat exchanger 10, thereby reducing the pressure drop of the heat exchanger, the reduction of the pressure drop is beneficial to the heat exchange between the refrigerant in the first flow 50 of the heat exchanger and the another medium, although the heat exchange effect between the refrigerant in the third flow 52 and the another medium is weakened, the heat exchange effect between the first flow 50 and the second flow 51 is improved, the reduction of the heat exchange amount in the third flow 52 is smaller than the increase of the heat exchange amount in the first flow 50 and the second flow 51, thereby improving the heat exchange effect of the heat exchanger 10 as a whole, on the basis, the plates 30 in the third flow 52 still have a certain turbulent flow capacity to the refrigerant, thereby ensuring a certain heat exchange effect of the third flow 52 of the heat exchanger 10, further ensuring and improving the performance of the heat exchanger 10, and realizing the heat exchange performance of the heat exchanger 10, and realizing the heat exchanger 1010 optimization of heat exchange performance and pressure drop.

It is understood that the ratio of L1 to H1 in the specification is

The value of (c).

The first sub-core 81 to the third sub-core 83 each include the second interplate passages 26, the difference between the average flow area of the first interplate passages 25 located in the first sub-core 81 and the average flow area of the second interplate passages 26 is defined as C1, it should be understood that the average flow area in the description is equivalent to the flow cross-sectional area of the passage having a constant cross-sectional area along the extension direction of the passage, the difference between the average flow area of the first interplate passages 25 located in the second sub-core 82 and the average flow area of the second interplate passages 26 is defined as C2, the difference between the average flow area of the first interplate passages 25 located in the third sub-core 83 and the average flow area of the second interplate passages 26 is defined as C3, and the differences C1, C2, C3 are the size obtained by subtracting the average flow area of the corresponding first interplate passages 25 from the average flow area of the corresponding second interplate passages 26, wherein: c1 is more than or equal to C2 is more than or equal to 1.02 multiplied by C3; the larger the difference between the average flow areas of the first interplate channel 25 and the second interplate channel 26 adjacent to the plate 30 is, the stronger the turbulence effect of the plate 30 on the medium in the adjacent interplate channels is, and the larger the C1 value and the C2 value of the plate respectively located in the first sub-core 81 and the second sub-core 82 are than the C3 value located in the third sub-core 83, so that the turbulence capacity of the plate 30 in the first flow 50 and the second flow 51 on the refrigerant and another medium is improved, the convenience is brought to the rapid outflow of the refrigerant mainly in the gaseous state in the third flow 52, and the heat exchange performance and the pressure drop of the heat exchanger 10 are optimized.

As shown in fig. 9 to 11 and 14, 16, the first protruding portion 37 includes a first extending portion 71, a first bending portion 70, and a second extending portion 72, the first extending portion 71 and the second extending portion 72 are located on different sides of the first bending portion 70, the first bending portion 70 connects the first extending portion 71 and the second extending portion 71, the first bending portion 70, and the second extending portion 72 are V-shaped protrusions, the first bending portion 70 is a sharp corner of the V-shaped protrusion, the sharp corner of the V-shaped protrusion points in a direction substantially parallel to the length direction of the plate 30,the pointing directions of the V-shaped convex sharp angles of two adjacent sheets 30 are opposite, the minimum included angle between the first extending part and the second extending part of the first convex part 37 of the sheet 30 positioned in the first sub-core 81 is defined as D1, the maximum included angle between the first extending part and the second extending part of the first convex part of the sheet 30 positioned in the second sub-core 82 is defined as D2, the minimum included angle between the first extending part and the second extending part of the first convex part of the sheet 30 positioned in the second sub-core 82 is defined as D3, and the maximum included angle between the first extending part and the second extending part of the first convex part of the sheet 30 positioned in the third sub-core 83 is defined as D4, wherein: 165 DEG or more D1 is not less than 125 DEG, 125 DEG or more D2 is not less than 40 DEG, 125 DEG or more D3 is not less than 40 DEG, 125 DEG or more D4 is not less than 40 DEG,

the medium flowing in the heat exchanger 10 is influenced by gravity, the medium generally flows along the first extension or the second extension in the concave area between two adjacent first protrusions 37, if the included angle between the first extension and the second extension is too small, part of the medium tends to flow along the first extension or the second extension, so that the medium flows through the corresponding interplate channel more easily, if the included angle between the first extension and the second extension is larger, part of the medium tends to flow in a manner of crossing the first protrusions 37 instead of flowing along the first extension and the second extension, so that the medium flows through the corresponding interplate channel more difficultly, and the flow pattern of the medium is more complicated, i.e. the increase of the included angle between the first extension and the second extension improves the turbulence capability of the corresponding plate 30 on the medium, the decrease of the included angle between the first extension and the second extension reduces the turbulence capability of the corresponding plate 30 on the medium, and the heat exchange performance and pressure drop of the heat exchanger 10 are optimized by controlling the sizes of D1, D2, D3 and D4.

In some embodiments, with reference to fig. 12-13, the first plate 40 includes a third base 401 and a fourth base 402 perpendicular to the stacking direction of the plurality of plates 30, the first plate 40 further includes a plurality of second protrusions 403 protruding from the third base 401, at least a portion of the second protrusions are located in the first plate passages 25, the second protrusions 403 include a second top end portion and a second bottom end portion, the second top end portion is far from the third base 401 of the first plate 40 along the stacking direction of the plurality of plates, and like the first top end portion 371, the second top end portion may be an end point or a plane center point or a line segment center point; at least part of the second raised portions 403 are arranged along the length direction of the first plate 40, the length direction of the first plate 40 is the Lc direction shown in fig. 12, the first plate 40 further includes a plurality of second recessed portions 404 recessed in the fifth plane and corresponding to the second raised portions 403, that is, at least part of the second recessed portions 404 are arranged along the length direction of the first plate 40, along the stacking direction of the plurality of plates, one side of the first plate 40 is the second inter-plate channel 26, and the other side of the first plate 40 is the first inter-plate channel 25 of the first flow path 50.

It will be understood that, in the thickness direction of the first plate 40, one side of the second protrusion 403 protrudes relative to the third base 401 of the first plate 40, the other side of the second protrusion 403 may protrude relative to the fourth base 402, the second top end is located at the portion of the second protrusion 403 protruding from the third base 401 and away from the third base 401 in the thickness direction of the first plate 40, and the second bottom end is located at the portion of the second protrusion 403 protruding from the fourth base 402 and away from the fourth base 402 in the thickness direction of the first plate 40.

A distance between the second top ends of two adjacent second convex portions 403 in the length direction of the first sheet 40 is defined as L2, and a distance from the second top ends to the second bottom ends of the second convex portions 403 in the thickness direction of the first sheet 40 is defined as H2, wherein:

by controlling

The first plate 40 has a strong flow disturbing capability for the gas-liquid two-phase refrigerant in the adjacent first interplate channels 25 and the other medium in the second interplate channels 26, so as to improve the heat exchange effect of the first flow 50 of the heat exchanger 10, and especially, in the case that the number of the plates 30 located in the first sub-core 81 is small, the number of the first interplate channels 25 in the first flow 50 is small, and the structural arrangement of the first plate 40 is easy to influence the adjacent first flow 50 in the first interplate channels 25 of the first flow 50The flow of the gas-liquid two-phase refrigerant affects the heat exchange effect of the first flow path 50 of the heat exchanger 10, and the structural arrangement of the first plate 40 has a significant effect on the heat exchange effect of the first flow path 50 of the heat exchanger 10.

Each of the first sub-core 81 to the third sub-core 83 includes the second interplate channels 26, the difference between the average flow area of the first interplate channels 25 located in the first sub-core 81 and the average flow area of the second interplate channels 26 is defined as C1, the difference between the average flow area of the first interplate channels 25 located in the second sub-core 82 and the average flow area of the second interplate channels 26 is defined as C2, the difference between the average flow area of the first interplate channels 25 located in the third sub-core 83 and the average flow area of the second interplate channels 26 is defined as C3, the difference between the average flow areas of the first interplate channels 25 and the second interplate channels 26 adjacent to the first plate 40 is defined as C4, and the differences C1, C2, C3, and C4 are the magnitude of the average flow area of the corresponding second interplate channels 26 minus the average flow area of the corresponding first interplate channels 25, wherein: c1 is more than or equal to C2 and more than or equal to 1.02 multiplied by C3, and C4 is more than or equal to 1.02 multiplied by C2; the increase of the difference of the average flow areas of the first plate interplate channels 25 and the second plate interplate channels 26 adjacent to the first plate 40 improves the turbulence capability of the first plate 40 on the refrigerant and another medium, and further improves the heat exchange effect of the heat exchanger 10.

As shown in fig. 12 to 13, the second protruding portion 403 includes a third extending portion, a second bending portion and a fourth extending portion, the third extending portion and the fourth extending portion are located on different sides of the second bending portion, the second bending portion connects the third extending portion and the fourth extending portion, the third extending portion, the second bending portion and the fourth extending portion are V-shaped protrusions, the second bending portion is a pointed angle of the V-shaped protrusion, the pointed angle of the V-shaped protrusion of the first plate 40 points in a direction opposite to the pointed angle of the V-shaped protrusion of two adjacent plates 30, an included angle between the third extending portion and the fourth extending portion of the second protruding portion 403 of the first plate 40 is defined as D5, where: 165 degrees is more than or equal to D5 is more than or equal to 125 degrees; by controlling the value of D5, the turbulence capacity of the first plate 40 to media in the adjacent first interplate channels and second interplate channels is improved, and the heat exchange effect of the first flow of the heat exchanger is further improved.

Heat exchange coreThe body 20 further includes a plurality of fins 60, at least a part of the fins 60 are located in the first interplate passages 25, each of the fins 60 includes a base plate portion 61 and a protruding portion 62, as shown in fig. 21, the protruding portion 62 protrudes from the base plate portion 61, the protruding portion 62 includes a protruding tip portion 63, like the first tip portion 371, the protruding tip portion 63 may be an end point or a plane center point or a line segment center point, at least a part of the protruding portions 62 are arranged along a length direction of the fins 60, the length direction of the fins 60 is an Ld direction shown in fig. 21, a distance between the protruding tip portions 63 of two adjacent protruding portions 62 along the length direction of the fins 60 is defined as L3, a maximum thickness of the fins 60 along a stacking direction of the plurality of sheets 30 is defined as H3, the fins 60 located in the first sub-core 81 are defined as E1, the fins 60 located in the second sub-core 82 are defined as E2, a ratio of L3 to H3 is defined as E3, the fins 60 located in the third sub-core 83 are defined as E3, a ratio of L3 to H3 is defined as E3, and a ratio of L3 to H3

A value of (a), wherein: e1 is more than or equal to 1.1 and less than or equal to 1.75, E2 is more than or equal to 1.75 and less than or equal to 3, E3 is more than or equal to 1.75 and less than or equal to 3,

the larger the value E of the fin 60 is, the larger the turbulence capability of the fin 60 to the refrigerant and another medium is, by controlling the values E of the fins 60 in the first flow 50, the second flow 51 and the third flow 52, the turbulence effect of the fin 60 to the gas-liquid two-phase refrigerant in the first flow 50 is improved, and the turbulence effect of the fin 60 to the gas-liquid two-phase refrigerant in the second flow 51 and the third flow 52 is reduced, so that the heat exchange performance and the pressure drop of the heat exchanger 10 are optimized finally.

In some embodiments, referring to fig. 15, the second plate 41 includes a fifth base surface and a sixth base surface 412 perpendicular to the stacking direction of the plurality of plates 30, the second plate 41 further includes a plurality of third protrusions protruding from the fifth base surface, at least a portion of the third protrusions are located in the first inter-plate channel 25, the third protrusions include a third top end portion and a third bottom end portion, the third top end portion and the third bottom end portion are located on different sides of the third protrusions along the thickness direction of the second plate 41, the third top end portion and the third bottom end portion may be end points or line segment midpoints or plane midpoints, as with the first top end portion 371, at least a portion of the third protrusions are arranged along the length direction of the second plate 41, the length direction of the second plate 41 is the Le direction shown in fig. 15, and the second plate 41 further includes a plurality of third recesses 414 recessed in the sixth base surface 412 and corresponding to the third protrusions.

It is understood that one side of the third protrusion along the stacking direction of the multiple plates protrudes from the fifth base surface, and the other side of the third protrusion along the thickness direction of the second plate 41 may also protrude from the sixth base surface 412, and the length directions of the plate, the first plate, the second plate and the fin are parallel to each other.

A distance between the third top ends of two third convex portions adjacent in the length direction of the second sheet 41 is defined as L4, and a distance from the third top end to the third bottom end of the third convex portion in the thickness direction of the second sheet 41 is defined as H4, where:

second plate

The value is smaller than that of the first plate 40, so that the gas-liquid two-phase refrigerant in the first inter-plate channel 25 on the adjacent side of the second plate 41 can flow out quickly, the pressure drop of the heat exchanger 10 is reduced, and meanwhile, the second plate 41 still has a certain flow disturbing capacity, so that the heat exchanger 10 is ensured to have a certain heat exchange effect, and especially when the plates located in the second sub-core 82 and the third sub-core 83 are fewer, the structural arrangement of the second plate 41 has a more obvious influence on the heat exchange effect of the second flow 51 and the third flow 52 of the heat exchanger 10.

The first to third sub-cores 81 to 83 each include second interplate channels, defining the average flow area of the first interplate channels 25 adjacent to the second plate 41 minus the average flow area of the adjacent second interplate channels 26 as C5, wherein: c5 is less than or equal to 0.98 multiplied by C4; the value of C5 of the second plate 41 is smaller than that of C4, so that the turbulent flow effect of the second plate 41 on the refrigerant in the adjacent first interplate channels is reduced, and the pressure drop of the heat exchanger 10 is reduced.

As shown in fig. 15, the third protruding portion includes a fifth extending portion, a third bending portion, and a sixth extending portion, the fifth extending portion and the sixth extending portion are located at two sides of the third bending portion, the third bending portion connects the fifth extending portion and the sixth extending portion, the fifth extending portion, the third bending portion, and the sixth extending portion are V-shaped protrusions, an included angle between the fifth extending portion and the sixth extending portion, which defines the third protruding portion of the second plate 41, is D6, where: d6 is not more than 0.93 multiplied by D5, the value of D6 is smaller than the value of D5 of the first plate 40, the turbulent flow effect of the second plate 41 on the refrigerant in the adjacent first interplate channels 25 is reduced, and the pressure drop of the heat exchanger 10 is reduced.

In some embodiments, with reference to fig. 1 to 18, the first plate 40 divides the third channel 23 into a fifth sub-channel 231 and a sixth sub-channel 232, the fifth sub-channel 231 is farther from the second plate 41 than the sixth sub-channel 232, the second plate 41 divides the fourth channel 24 into a seventh sub-channel 241 and an eighth sub-channel 242, the eighth sub-channel 242 is farther from the first plate 40 than the seventh sub-channel 241, the second plate-to-plate channels 26 on the side of the first plate 40 facing away from the second plate 41 communicate with the fifth sub-channel 231 and the seventh sub-channel 241, the second plate-to-plate channels 26 between the first plate 40 and the second plate 41 communicate with the seventh sub-channel 241 and the sixth sub-channel 232, the second plate-to-plate channels 26 on the side of the second plate 41 facing away from the first plate 40 communicate with the sixth sub-channel 232 and the eighth sub-channel 242, the second channel is used for coolant to flow, the fifth sub-channel 231, the first plate channel 25 on the side of the first plate 40 facing away from the second plate 41, the eighth sub-channel 242 is located between the second plate 40 and the second plate 41, the coolant channels are located between the second plate 40 and the extended coolant channels 242, thereby increasing the coolant flow path between the second plate 41 and the second plate 40.

In some embodiments, with reference to fig. 22-27, the plate 30 includes a first corner hole 31, a second corner hole 32, and a third corner hole 33, the first corner holes 31 of the multiple plates 30 are at least partially aligned along a stacking direction of the multiple plates 30 to form a first porthole 21, the second corner holes 32 of the multiple plates 30 are at least partially aligned along the stacking direction of the multiple plates 30 to form a second porthole 22, the third corner holes 33 of the multiple plates 30 are at least partially aligned along the stacking direction of the multiple plates 30 to form a third porthole 23, the first porthole 21 and the second porthole 22 are located on the same side of the plate 30 in the width direction, and the first porthole 21 and the third porthole 23 are located on different sides of the plate 30 in the width direction;

the first sheet 40 divides the first pore passage 21 into a first sub pore passage 211 and a second sub pore passage 212, the first sub pore passage 211 is far away from the second sheet 41 than the second sub pore passage 212, the second sheet 41 divides the second pore passage 22 into a third sub pore passage 221 and a fourth sub pore passage 222, the fourth sub pore passage 222 is far away from the first sheet 40 than the third sub pore passage 221, the third pore passage 23 is divided into a fifth sub pore passage 231 and a sixth sub pore passage 232 by the second sheet 41, the sixth sub pore passage 232 is far away from the first sheet 40 than the fifth sub pore passage 231, a plurality of first inter-plate passages 25 on the side of the first sheet 40 far away from the second sheet 41 are communicated with the first sub pore passage 211 and the fifth sub pore passage 231, a plurality of first inter-plate passages 25 between the first sheet 40 and the second sheet 41 are communicated with the fifth sub pore passage 231 and the second sub pore passage 212, and a plurality of first inter-plate passages 25 on the side of the second sheet 41 far away from the first sheet 40 are communicated with the second sub pore passage 212 and the fourth sub pore passage 222; or, the first plate 40 divides the third pore canal 23 into a fifth sub pore canal 231 and a sixth sub pore canal 232, the fifth sub pore canal 231 is farther away from the second plate 41 than the sixth sub pore canal 232, the second plate 41 divides the first pore canal 21 into a first sub pore canal 211 and a second sub pore canal 212, the second sub pore canal 212 is farther away from the first plate 40 than the first sub pore canal 211, the first plate 40 divides the second pore canal 22 into a third sub pore canal 221 and a fourth sub pore canal 222, the third sub pore canal 221 is farther away from the second plate 41 than the fourth sub pore canal 222, a plurality of first inter-plate passages 25 on one side of the first plate 40 departing from the second plate 41 are communicated with the fifth sub pore canal 231 and the first sub pore canal 211, a plurality of first inter-plate passages 25 between the first plate 40 and the second plate 41 are communicated with the first sub pore canal 211 and the fourth sub pore canal 222, and a plurality of first inter-plate passages 25 on one side of the second plate 41 departing from the first plate 40 are communicated with the fourth sub pore canal 222 and the second plate 212. The first flow path 50 is diagonal flow, the second flow path 51 is diagonal flow or parallel flow, the third flow path 52 is parallel flow, the heat exchange effect of the first flow path 50 is improved by prolonging the flow path of the refrigerant in the first flow path 50 and improving the distribution uniformity of the refrigerant in the first plate-to-plate channels 25 of the first flow path 50, and the flow path of the refrigerant in the third flow path 52 is shorter, so that the refrigerant mainly in a gas state in the third flow path 52 can rapidly flow out, the pressure drop of the heat exchanger is reduced, and the heat exchange performance and the pressure drop of the heat exchanger are optimized finally.

It should be noted that: although the present invention has been described in detail with reference to the above-mentioned embodiments, it should be understood by those skilled in the art that the present invention may be modified and equivalents may be substituted for those skilled in the art, and all technical solutions and modifications that do not depart from the spirit and scope of the present invention should be covered by the claims of the present invention.

Claims (10)

1. A heat exchanger comprises a heat exchange core body, wherein the heat exchange core body comprises a plurality of plate sheets, the plate sheets are arranged in a stacked mode to form a plurality of inter-plate channels, the inter-plate channels comprise first inter-plate channels and second inter-plate channels, the heat exchange core body further comprises first flow channels and second flow channels, the first inter-plate channels are not communicated with each other, the first inter-plate channels are part of the first flow channels, the second inter-plate channels are part of the second flow channels, and the heat exchange core body is characterized in that: the heat exchange core sequentially comprises a first sub-core body, a second sub-core body, a flow path I8230and a flow path I n along the lamination direction of the plate sheets, wherein the first flow path comprises an inlet, a first flow path I8230and a flow path I n, the inlet of the first flow path is communicated with the first flow path, the first flow path I is positioned on the first sub-core body, the second flow path I8230is positioned on the second sub-core body, the flow path I n is positioned on the sub-core body, the first flow path I comprises first inter-plate channels positioned on the first sub-core body, the second flow path I8230comprises first inter-plate channels positioned on the second sub-core body, the flow path I n-1 is communicated with the flow path adjacent to the first inter-plate channels, and the flow path I n-1 is positioned on the second sub-core bodyDefining the number of first plate-to-plate channels in said first pass as A1, defining the number of first plate-to-plate channels in said nth pass as An, defining the total number of first plate-to-plate channels of said heat exchange core as N, wherein: n is more than or equal to 3,

A1<An。

2. the heat exchanger of claim 1, wherein: the number A1 of first interplate channels in the first pass and the number An of first interplate channels in the nth pass satisfy:

3. the heat exchanger of claim 2, wherein: n =3, the number of first interplate channels located in the second flow path is defined as A2, A1 and A2 satisfying:

and, A2 < A3.

4. The heat exchanger of claim 2, wherein: n =4, the number of first interplate passages in the second flow path is defined as A2, and the number of first interplate passages in the third flow path is defined as A3, wherein:

the number of the first interplate channels located in the first flow to the third flow is respectively less than the number of the first interplate channels located in the fourth flow, and the number of the first interplate channels in each of the second flow to the fourth flow is not less than the number of the first interplate channels located in the first flow.

5. The heat exchanger of claim 3, wherein: the plate comprises a first base surface and a second base surface which are perpendicular to the stacking direction of a plurality of plates, the plate further comprises a plurality of first protruding parts protruding from the first base surface, at least part of the first protruding parts are positioned in the first inter-plate channel, each first protruding part comprises a first top end part and a first bottom end part, and at least part of the first protruding parts are arranged along the length direction of the plate;

defining a distance between first top ends of two first convex portions adjacent to each other along the length direction of the plate as L1, defining a distance from the first top ends of the first convex portions to the first bottom ends of the first convex portions along the stacking direction of a plurality of plates as H1, defining a ratio of L1 to H1 of the plate positioned in the first sub-core as B1, defining a ratio of L1 to H1 of the plate positioned in the second sub-core as B2, defining a ratio of L1 to H1 of the plate positioned in the third sub-core as B3, wherein:

or, the first sub-core to the third sub-core each include the second interplate channels, a difference between an average flow area of the first interplate channels located in the first sub-core and an average flow area of the second interplate channels is defined as C1, a difference between an average flow area of the first interplate channels located in the second sub-core and an average flow area of the second interplate channels is defined as C2, and a difference between an average flow area of the first interplate channels located in the third sub-core and an average flow area of the second interplate channels is defined as C3, where: c1 is more than or equal to C2 is more than or equal to 1.02 multiplied by C3;

or, the first protruding part comprises a first extending part, a first bending part and a second extending part, the first extending part and the second extending part are located on different sides of the first bending part, the first bending part is connected with the first extending part and the second extending part, the first bending part and the second extending part are protruding in a V shape, the minimum included angle between the first extending part and the second extending part of the first protruding part of the plate of the first sub-core body is defined as D1, and the minimum included angle between the first extending part and the second extending part of the first protruding part of the plate of the first sub-core body is defined as D1The maximum included angle between the first extending part and the second extending part of the first protruding part of the plate of the second sub-core body is D2, the minimum included angle between the first extending part and the second extending part of the first protruding part of the plate of the second sub-core body is D3, and the maximum included angle between the first extending part and the second extending part of the first protruding part of the plate of the third sub-core body is D4, wherein:

6. the heat exchanger of claim 3 or 5, wherein: the plate comprises a first plate, the first plate is positioned between the first flow path and the second flow path, the first plate comprises a third base surface and a fourth base surface which are perpendicular to the stacking direction of the plates, the first plate further comprises a plurality of second protruding parts protruding from the third base surface, at least part of the second protruding parts are positioned in the first inter-plate channels, each second protruding part comprises a second top end part and a second bottom end part, and at least part of the second protruding parts are arranged along the length direction of the first plate;

defining a distance between second top ends of two second convex portions adjacent in the length direction of the first plate as L2, and defining a distance from the second top end to the second bottom end of the second convex portion in the stacking direction of a plurality of plates as H2, wherein:

or, the first sub-core to the third sub-core each include the second interplate channels, a difference between an average flow area of the first interplate channels located in the first sub-core and an average flow area of the second interplate channels is defined as C1, a difference between an average flow area of the first interplate channels located in the second sub-core and an average flow area of the second interplate channels is defined as C2, a difference between an average flow area of the first interplate channels located in the third sub-core and an average flow area of the second interplate channels is defined as C3, and a difference between an average flow area of the first interplate channels adjacent to the first plate pieces and an average flow area of the second interplate channels adjacent to the first plate pieces is defined as C4, where: c1 is more than or equal to C2 and more than or equal to 1.02 multiplied by C3, and C4 is more than or equal to 1.02 multiplied by C2;

or, the second protruding portion includes a third extending portion, a second bending portion and a fourth extending portion, the third extending portion and the fourth extending portion are located on different sides of the second bending portion, the second bending portion is connected to the third extending portion and the fourth extending portion, the third extending portion, the second bending portion and the fourth extending portion are V-shaped protrusions, an included angle between the third extending portion and the fourth extending portion of the second protruding portion of the first plate is defined as D5, wherein: 165 degree is more than or equal to D5 is more than or equal to 125 degree.

7. The heat exchanger of claim 3 or 5, wherein: the heat exchange core body comprises a plurality of fins, at least part of the fins are located in the first interplate channels, the fins comprise a base plate portion and protruding portions, the protruding portions protrude from the base plate portion, the protruding portions comprise protruding top end portions, at least part of the protruding portions are arranged along the length direction of the fins, the distance between the protruding top end portions of two adjacent protruding portions along the length direction of the fins is defined as L3, the maximum thickness of the fins along the stacking direction of the plates is defined as H3, the fin located in the first sub-core body is defined as E1 according to the ratio of L3 to H3, the fin located in the second sub-core body is defined as E2 according to the ratio of L3 to H3, and the fin located in the third sub-core body is defined as E3 according to the ratio of L3 to H3, wherein: e1 is more than or equal to 1.1 and less than or equal to 1.75,

8. the heat exchanger of claim 6, wherein: the second plate is positioned between the second flow path and the third flow path, the second plate comprises a fifth base surface and a sixth base surface which are perpendicular to the stacking direction of the plurality of plates, the second plate further comprises a plurality of third bulges protruding from the fifth base surface, at least part of the third bulges are positioned in the first plate-to-plate channels, the third bulges comprise third top ends and third bottom ends, and at least part of the third bulges are arranged along the length direction of the second plate;

defining a distance between the third top ends of two adjacent third convex portions along the length direction of the second plate as L4, and defining a distance from the third top end to the third bottom end of the third convex portion along the stacking direction of the plurality of plates as H4, wherein:

or defining the difference of the average flow area of the first interplate channels and the second interplate channels adjacent to the second plate as C5, wherein: c5 is less than or equal to 0.98 multiplied by C4;

or, the third protruding portion includes a fifth extending portion, a third bending portion, and a sixth extending portion, the fifth extending portion and the sixth extending portion are located on different sides of the third bending portion, the third bending portion connects the fifth extending portion and the sixth extending portion, the fifth extending portion, the third bending portion, and the sixth extending portion are V-shaped protrusions, an included angle between the fifth extending portion and the sixth extending portion of the third protruding portion of the second plate is defined as D6, where: d6 is less than or equal to 0.93 multiplied by D5.

9. The heat exchanger of claim 8, wherein: the plate sheet comprises a first angle hole, a second angle hole, a third angle hole and a fourth angle hole, wherein the first angle holes of the plate sheet are at least partially aligned along the stacking direction of the plate sheets to form a first pore channel, the second angle holes of the plate sheet are at least partially aligned along the stacking direction of the plate sheets to form a second pore channel, the third angle holes of the plate sheet are at least partially aligned along the stacking direction of the plate sheets to form a third pore channel, the fourth angle holes of the plate sheet are at least partially aligned along the stacking direction of the plate sheets to form a fourth pore channel, the first pore channel and the second pore channel are positioned on the same side of the width direction of the plate sheet, the third pore channel and the fourth pore channel are positioned on the same side of the width direction of the plate sheet, and the first pore channel and the third pore channel are positioned on different sides of the width direction of the plate sheet, the first sheet divides the first pore passage into a first sub pore passage and a second sub pore passage, the first sub pore passage is far away from the second sheet than the second sub pore passage, the second sheet divides the second pore passage into a third sub pore passage and a fourth sub pore passage, the fourth sub pore passage is far away from the first sheet than the third sub pore passage, a plurality of first inter-plate passages positioned on one side of the first sheet, which is far away from the second sheet, are communicated with the first sub pore passage and the third sub pore passage, a plurality of first inter-plate passages positioned between the first sheet and the second sheet are communicated with the third sub pore passage and the second sub pore passage, and a plurality of first inter-plate passages positioned on one side of the second sheet, which is far away from the first sheet, are communicated with the second sub pore passage and the fourth sub pore passage;

the first plate piece divides the third hole channel into a fifth sub-hole channel and a sixth sub-hole channel, the fifth sub-hole channel is far away from the second plate piece than the sixth sub-hole channel, the second plate piece divides the fourth hole channel into a seventh sub-hole channel and an eighth sub-hole channel, the eighth sub-hole channel is far away from the first plate piece than the seventh sub-hole channel, a plurality of second inter-plate channels positioned on one side of the first plate piece, which is far away from the second plate piece, are communicated with the fifth sub-hole channel and the seventh sub-hole channel, a plurality of second inter-plate channels positioned between the first plate piece and the second plate piece are communicated with the seventh sub-hole channel and the sixth sub-hole channel, and a plurality of second inter-plate channels positioned on one side of the second plate piece, which is far away from the first plate piece, are communicated with the sixth sub-hole channel and the eighth sub-hole channel.

10. The heat exchanger of claim 3 or 5, wherein: the plate sheets comprise a first corner hole, a second corner hole and a third corner hole, the first corner holes of a plurality of the plate sheets are at least partially aligned along the stacking direction of the plurality of the plate sheets to form a first pore passage, the second corner holes of a plurality of the plate sheets are at least partially aligned along the stacking direction of the plurality of the plate sheets to form a second pore passage, the third corner holes of a plurality of the plate sheets are at least partially aligned along the stacking direction of the plurality of the plate sheets to form a third pore passage, the first pore passage and the second pore passage are positioned on the same side in the width direction of the plate sheets, and the first pore passage and the third pore passage are positioned on different sides in the width direction of the plate sheets;

the first sheet divides the first pore passage into a first sub-pore passage and a second sub-pore passage, the first sub-pore passage is farther away from the second sheet than the second sub-pore passage, the second sheet divides the second pore passage into a third sub-pore passage and a fourth sub-pore passage, the fourth sub-pore passage is farther away from the first sheet than the third sub-pore passage, the second sheet divides the third pore passage into a fifth sub-pore passage and a sixth sub-pore passage, the sixth sub-pore passage is farther away from the first sheet than the fifth sub-pore passage, a plurality of first inter-plate passages on one side of the first sheet, which is far away from the second sheet, are communicated with the first sub-pore passage and the fifth sub-pore passage, a plurality of first inter-plate passages between the first sheet and the second sheet are communicated with the fifth sub-pore passage and the second sub-pore passage, and a plurality of first inter-plate passages on one side of the second sheet, which is far away from the first sheet, are communicated with the second sub-pore passage and the fourth sub-pore passage; or, the first plate divides the third hole channel into a fifth sub-hole channel and a sixth sub-hole channel, the fifth sub-hole channel is farther away from the second plate than the sixth sub-hole channel, the second plate divides the first hole channel into a first sub-hole channel and a second sub-hole channel, the second sub-hole channel is farther away from the first plate than the first sub-hole channel, the first plate divides the second hole channel into a third sub-hole channel and a fourth sub-hole channel, the third sub-hole channel is farther away from the second plate than the fourth sub-hole channel, a plurality of first inter-plate channels located on one side of the first plate departing from the second plate are communicated with the fifth sub-hole channel and the first sub-hole channel, a plurality of first inter-plate channels located between the first plate and the second plate are communicated with the first sub-hole channel and the fourth sub-hole channel, and a plurality of first inter-plate channels located on one side of the second plate departing from the first plate are communicated with the fourth sub-hole channel and the second sub-hole channel.

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