CN212205727U - Heat exchanger - Google Patents

Abstract

The application discloses a heat exchanger, which comprises a collector group and a plurality of heat exchange assemblies; the plurality of heat exchange assemblies are arranged at intervals along the axial direction of the collecting pipe; each heat exchange component comprises a fin plate and at least one heat exchange tube; the heat exchange component comprises a main heat exchange area, and the heat exchange pipe is fixedly connected to the surface of the fin plate; or the fin plate comprises a plurality of sub-plates, and the heat exchange tube is connected between two adjacent sub-plates; the heat exchange tube is connected between the two collecting pipes in the length direction, and the inner cavity of the heat exchange tube is communicated with the inner cavities of the two collecting pipes; the heat exchange tube at least partially protrudes out of at least one side of the fin plate; and at least one pair of adjacent heat exchange tubes are arranged in a staggered manner in the main heat exchange areas corresponding to the two adjacent heat exchange assemblies, and the two heat exchange tubes of the pair belong to the two adjacent heat exchange assemblies. The heat exchanger is beneficial to improving the uniformity of the flow cross section of the air side flow channel of the heat exchanger, and further the performance of a heat exchanger product is improved.

Description

Heat exchanger

Technical Field

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

Background

Heat exchange devices are required to be used in automobile, household or commercial air conditioning systems, and one scheme in the related art is that the heat exchanger comprises an integrated heat exchange tube and a fin plate; as shown in fig. 1, fin plates 10 and heat exchange tubes 20 of the same structure and integrated are arranged in a plurality of rows. In the related art, after the heat exchange assemblies consisting of the plurality of integrated heat exchange tubes 20 and the fin plates 10 are arranged, the heat exchange tubes 20 of the plurality of heat exchange assemblies correspondingly form a plurality of rows, and the heat exchange tubes 20 protrude towards the air side flow channel relative to the fin plates 10, so that the air side flow channel has large pressure drop, the heat exchanger has poor heat exchange performance, high energy consumption and easy frosting.

SUMMERY OF THE UTILITY MODEL

The heat exchanger is beneficial to improving the uniformity of the flow cross section of the air side flow channel of the heat exchanger, and further the performance of a heat exchanger product is improved.

The application provides a heat exchanger, which comprises a header group and a plurality of heat exchange assemblies;

the collecting pipe group comprises two collecting pipes which are respectively positioned at two sides of the heat exchange assembly in the length direction, and each collecting pipe comprises a longitudinal pipe body and an inner cavity of the collecting pipe;

the plurality of heat exchange assemblies are arranged at intervals along the axial direction of the collecting pipe; the gaps between the adjacent heat exchange assemblies form air side flow channels; each heat exchange component comprises a fin plate and at least one heat exchange tube; the heat exchange assembly comprises a main heat exchange area, and the heat exchange tube is fixedly connected to the surface of the fin plate in the main heat exchange area; or the fin plate comprises a plurality of sub-plates, and the heat exchange tube is connected between two adjacent sub-plates;

the heat exchange tube is connected between the two collecting pipes in the length direction, the inner cavity of the heat exchange tube is communicated with the inner cavities of the two collecting pipes, and the inner cavity of the heat exchange tube and the inner cavity of the collecting pipe form a part of a refrigerant flow channel; at least part of the heat exchange tube protrudes out of at least one side of the fin plate in the arrangement direction of the heat exchange assemblies; and at least one pair of adjacent heat exchange tubes are arranged in a staggered manner in the main heat exchange areas corresponding to the two adjacent heat exchange assemblies, wherein the two heat exchange tubes of the pair belong to the two adjacent heat exchange assemblies respectively.

The heat exchange tubes corresponding to the heat exchange assemblies are favorably prevented from being intensively arranged on the path of the air side flow channel, the uniformity of the circulation section of the air side flow channel is favorably realized, the influence of the flow channel structure which is suddenly expanded and contracted on fluid pressure drop is reduced, and the heat exchange performance of the heat exchanger is improved.

Drawings

Fig. 1 is a schematic view of an integrated structure of a fin and a heat exchange tube of the related art;

FIG. 2 is a schematic perspective view of a heat exchanger provided herein;

FIG. 3 is an exploded view of the heat exchanger provided in FIG. 2 of the present application;

FIG. 4 is a schematic structural view of one embodiment of a heat exchange assembly provided herein;

FIG. 5 is a schematic structural view of another embodiment of a heat exchange assembly provided herein;

FIG. 6 is a schematic structural view of another embodiment of a heat exchange assembly provided herein;

FIG. 7 is an enlarged schematic view of one embodiment of a partial structure of a heat exchange assembly provided herein;

FIG. 8 is a schematic perspective view of another heat exchanger provided herein;

FIG. 9 is a schematic perspective view of another heat exchanger provided herein;

FIG. 10 is an enlarged schematic view of another embodiment of a partial structure of a heat exchange assembly provided herein;

FIG. 11 is an enlarged schematic view of one embodiment of a partial structure of a header provided herein;

FIG. 12 is an enlarged schematic view of another embodiment of a partial structure of a heat exchange assembly provided herein;

FIG. 13 is an enlarged schematic view of one embodiment of a partial structure of a header provided herein;

FIG. 14 is a schematic block diagram of one embodiment of a multi-pass heat exchanger provided herein;

FIG. 15 is a schematic block diagram of one embodiment of the connection of a second header to a fourth header provided herein;

fig. 16 is a schematic structural view of another embodiment of the connection of the second header and the fourth header provided in the present application;

FIG. 17 is a schematic block diagram of another embodiment of a multi-pass heat exchanger provided herein;

FIG. 18 is a schematic block diagram of another embodiment of a multi-pass heat exchanger provided herein;

fig. 19 is another schematic diagram of the multi-pass heat exchanger provided in fig. 18 of the present application.

Detailed Description

The technical solutions in the embodiments of the present application will be described clearly and completely with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

Referring to fig. 2 and 3, the present application provides a heat exchanger 10 comprising a header group and a plurality of heat exchange assemblies 101. The header group comprises two headers 100 respectively positioned at two sides of the heat exchange assembly 101 in the length direction, and each header 100 comprises a longitudinal pipe body 201 and a header inner cavity 202. The length direction of the heat exchange assembly 101 is indicated by a solid line segment L with arrows on both sides in fig. 2, and the width direction of the heat exchange assembly 101 is indicated by a solid line segment W with arrows on both sides in fig. 2.

The heat exchange assemblies 101 are connected to the header 100, a plurality of heat exchange assemblies 101 are arranged at intervals along the axial direction of the header 100, the axial direction of the header 100 can refer to the direction indicated by the dotted line in fig. 2, and the gaps between adjacent heat exchange assemblies 101 form air side flow passages.

Each of the plurality of heat exchange assemblies 101 includes a fin plate 203 and at least one heat exchange tube 204. The heat exchange assemblies 101 are arranged at intervals, and the gaps between the adjacent heat exchange assemblies 101 can circulate heat exchange air flows, and the heat exchange air flows can be arranged on the two surfaces of the fin plate 203 opposite to each other by referring to the direction indicated by the arrow in fig. 4.

The heat exchange assembly 101 includes a main heat exchange region 301, and the fin plate 203 is integrally combined with a heat exchange pipe 204 in the main heat exchange region 301, wherein the heat exchange pipe 204 is fixedly connected to a surface of the fin plate 203, or the fin plate 203 includes a plurality of sub-plates 2031, and the heat exchange pipe 204 is connected between two adjacent sub-plates 2031. The heat exchange tube 204 is connected between the two collecting pipes 100 in the length direction, the heat exchange tube 204 includes an inner cavity 2041, the inner cavity 2041 of the heat exchange tube 204 is communicated with the inner cavities 202 of the two collecting pipes 100, and the inner cavity 2041 of the heat exchange tube 204 and the inner cavity 202 of the collecting pipe 100 form a part of a refrigerant flow passage.

The heat exchange assembly 101 further includes two connection areas 302 located at two sides of the main heat exchange area 301 in the length direction, referring to fig. 10 and fig. 12, the ends of the connection areas 302 are mainly used for being connected and fixed with the header pipe 100, the heat exchange assembly 101 may not be provided with the fin plate 203 in the connection areas 302, that is, the heat exchange pipe 204 may exceed the fin plate 203 in the length direction, and the ends of the heat exchange pipes 204 exceeding the fin plate 203 are connected with the header pipe 100 in a matching manner.

Wherein the header 100 is used for conveying a refrigerant, the refrigerant is conveyed to the heat exchange tube 204 through the header 100. The heat exchange pipe 204 can exchange heat with the fin plate 203, thereby raising or lowering the temperature of the fin plate 203. The fin plate 203 is capable of exchanging heat with the gas surrounding the fin plate 203, thereby raising or lowering the temperature of the gas surrounding the fin plate 203.

The heat exchange pipe 204 is formed on the surface of the fin plate 203, or the heat exchange pipe 204 is connected between two adjacent sub-plates 2031, and most of the heat exchange pipe 204 in the length direction is in contact with the fin plate 203, so that the heat exchange area between the heat exchange pipe 204 and the fin plate 203 is maximized, and the heat exchange amount and the heat exchange efficiency between the heat exchange pipe 204 and the fin plate 203 are also maximized.

At least a part of the heat exchange tube 204 protrudes from at least one side of the fin plate 203 in the arrangement direction of the heat exchange assembly 101. In one embodiment provided by the present application, the height of the heat exchange tube 204 in the arrangement direction of the heat exchange assemblies 101 is greater than the thickness of the fin plate 203. Alternatively, the fin plate 203 may be a relatively thin elongated plate-like structure, and the fin plate may include two opposite surfaces. The height or the diameter of the heat exchange tube 204 in the arrangement direction of the heat exchange assembly 101 is larger than the thickness of the fin plate 203, so that the heat exchange tube 204 protrudes from at least one surface of the fin plate 203, regardless of whether the heat exchange tube 204 is connected between two adjacent sub-portions 2031 or the heat exchange tube 204 is formed on the surface of the fin plate 203.

Referring to the projection of the main heat exchange area part of the plurality of heat exchange assemblies 101 illustrated in fig. 4 on the plane perpendicular to the length direction of the heat exchange assemblies 101, at least one pair of adjacent heat exchange tubes 204 are arranged in a staggered manner in the main heat exchange areas corresponding to the two adjacent heat exchange assemblies 101, wherein the two heat exchange tubes 204 of the pair respectively belong to the two adjacent heat exchange assemblies 101.

In the schematic of fig. 4, the heat exchange tubes 204 of one heat exchange assembly 101 are arranged in a staggered manner with the heat exchange tubes 204 of another adjacent heat exchange assembly 101. The heat exchange tube 204 is larger in diameter than the fin plate 203, and corresponds to the main heat exchange area of the adjacent heat exchange assembly 101, and the staggered arrangement is favorable for avoiding the heat exchange tube 204 from being intensively arranged in the air side flow channel. Seen from the whole flow channel at the air side, the position with the larger flow section and the position with the smaller flow section are homogenized, the influence of the flow channel structure with the sudden expansion and the sudden contraction on the fluid pressure drop is reduced, the heat exchange energy consumption is favorably reduced, the air with the same flow can provide more heat exchange amount, and therefore the heat exchange performance of the heat exchanger 10 is improved. At the same time, it helps to retard frost formation of the heat exchanger 10.

In an embodiment provided by the application, the thickness of the fin plate 203 is 0.05-0.5 mm, the inner diameter of the tube of the heat exchange tube 204 is 0.4-3.0 mm, the outer diameter of the tube of the heat exchange tube 204 is 0.6-5 mm, the tube spacing between adjacent heat exchange tubes 204 is 3-20 mm, and the spacing between adjacent heat exchange assemblies 101 is 1.4-6 mm in a single heat exchange assembly 101.

Further, this application provides an optional implementation mode, and the thickness of fin plate 203 is 0.2mm, and the inside diameter of the pipe of heat exchange tube 204 is 1.1mm, and the pipe external diameter of heat exchange tube 204 is 1.6mm, and the tube pitch of adjacent heat exchange tube 204 is 12mm, and the interval between adjacent heat exchange assemblies 101 is 1.8 mm.

As shown in fig. 2, the longitudinal direction of the heat exchange assembly 101 is substantially perpendicular to the axial direction of the header 100.

In one embodiment provided herein, and referring to the illustrations of fig. 5 and 6, heat exchange tubes 204 are welded to the surface of fin plate 203 in the primary heat exchange zone 301. Through setting up heat exchange tube 204 protrusion in the surface of fin board 203, the surface of fin board 203 forms concave-convex structure, and when heat transfer air current flowed through fin board 203 surface, this concave-convex structure can disturb heat transfer air current to improve fin board 203 and heat transfer air current's heat transfer volume and heat exchange efficiency. Meanwhile, the heat exchange tube 204 is welded on the surface of the fin plate 203, so that the heat exchange area of the air side flow channel can be increased.

In the same heat exchange assembly 101, at least one heat exchange tube 204 is convexly arranged on the surface of the same side of the fin plate 203. Of course, the heat exchange tubes 204 may be disposed on the fin plates 203 in various ways, and the heat exchange tubes 204 may be disposed on a single surface of the fin plates 203, or one fin plate 203 may include a plurality of regions, such as a first region where the heat exchange tubes 204 are disposed on one surface of the fin plates 203 and a second region where the heat exchange tubes 204 are disposed on the other surface of the fin plate 203 opposite to the first region. Of course, all the fin plates 203 may be divided into regions, and the heat exchange tubes 204 may be disposed on different surfaces of the fin plates 203 in different regions, for example, for the front m fin plates 203, the heat exchange tubes 204 are disposed on one surface of the corresponding fin plate 203, and for the back n fin plates 203, the heat exchange tubes 204 are disposed on the other surface of the corresponding fin plate 203.

Optionally, in two adjacent heat exchange assemblies 101, the heat exchange tube 204 of one heat exchange assembly 101 and the heat exchange tube 204 of the other heat exchange assembly 101 are located on different sides of the fin plate 203 where they are located. The advantage that sets up like this lies in, the heat exchange tube of these two heat exchange assemblies 101 can arrange simultaneously in the air runner that the clearance between these two heat exchange assemblies 101 formed, because the heat exchange tube dislocation set of two heat exchange assemblies 101, help forming the air runner in continuous winding and meandering flow path, increase the heat transfer coefficient of air runner, improve the heat transfer effect in this runner, the air runner circulation cross-section that the clearance between these two heat exchange assemblies 101 formed is comparatively even, or, the air runner that the clearance between these two heat exchange assemblies 101 formed can be kept away from simultaneously to the heat exchange tube of these two heat exchange assemblies 101, the wall of this air runner both sides all does not set up the heat exchange tube, the circulation cross-section is comparatively even, consequently, be favorable to improving the homogeneity of air side runner, thereby improve the heat transfer performance of heat exchanger.

The fin plates 203 are arranged at intervals, optionally, the fin plates 203 are arranged in parallel at equal intervals, so that heat exchange airflow uniformly passes through the fin plates, and meanwhile, the wind resistance of the heat exchange airflow passing through the fin plates 203 is reduced. Or the adjacent fin plates 203 can be arranged at unequal intervals, which is not limited by the present invention.

As shown in fig. 5, on a plane perpendicular to the length direction of the heat exchange assembly 101, the cross section of the fin plate 203 is a continuous zigzag shape, and the cross section of the heat exchange tube 204 is a diamond shape, wherein the fin plate 203 has an included angle adapted to the diamond shape at the peak and/or the valley of the zigzag shape, and the heat exchange tube 204 combines with the fin plate 203 based on two adjacent side walls 2043 of the diamond shape to make the fin plate 203 form a semi-surrounding arrangement with the heat exchange tube 204.

The fin plate 203 is designed to be a continuous broken line shape, and the area of the fin plate 203 in the width direction is large, so that the heat exchange area of the fin plate 203 and the heat exchange airflow is increased. Airflow vortexes can be formed between the wave crests and the wave troughs of the fin plates 203, so that the residence time of heat exchange airflow between the fin plates 203 is longer, and the heat exchange efficiency is improved.

In addition to the broken line type cross section, as shown in fig. 6, on a plane perpendicular to the length direction of the heat exchange assembly 101, the cross section of the fin plate 203 is in a wave shape, and the cross section of the heat exchange tube 204 is in a circular or elliptical shape, which is schematically illustrated as a circular heat exchange tube 204 in fig. 6.

The fin plate 203 includes a plurality of straight portions 2033 and a plurality of curved portions 2032, the curved portions 2032 being located between two adjacent straight portions 2033, the curved portions 2032 forming peaks and valleys of a wave shape. Part of the outer surface of the heat exchange tube 204 is fixedly combined with the arc portion 2032 of the fin plate 203, wherein the curvature of the combined part of the heat exchange tube 204 and the arc portion 2032 is the same as the curvature of the arc portion 2032 in size and direction.

Referring to fig. 4, the heat exchanging pipe 204 includes a pipe body 2042 at the periphery of an inner cavity 2041 thereof, and a plurality of sub-plates 2031 of the fin plate 203 are integrally formed with the pipe body 2042 through a casting process or integrally formed through an extrusion process.

The tube body 2042 of the heat exchange tube 204 and the plurality of sub-plates 2032 of the fin plate 203 can be integrally formed through a pouring process or an extrusion process, which is equivalent to that the inner cavity 2041 of the heat exchange tube 204 is formed in the fin plate 203, a part of the fin plate 203 forms the tube body 2042 of the heat exchange tube 204, and the parts of the fin plate 203 located at the two sides of the heat exchange tube 204 form the sub-plates 2032. An alternative extrusion process is by mating a first die for forming the inner cavity 2041 of the heat exchange tube 204 with a second die having a cavity forming the remainder of the heat exchange assembly 101, the two dies being mated such that the heat exchange assembly 101 is extruded from an opening in the cavity of the second die.

In a single heat exchange assembly 101, the ratio of the area of the outer surface of the heat exchange assembly 101 to the area of the sum of the inner surfaces of all the heat exchange tubes 204 is 5-45. When the flow cross section of the heat exchange tube 204 can be circular, square, rectangular, polygonal isosceles trapezoid or special-shaped, the area of the heat exchange tube 204 is positively correlated with the inner diameter or equivalent inner diameter thereof, the inner diameter of the heat exchange tube affects the speed of the refrigerant with the same volume flowing through the heat exchange tube 204, the ratio of the area of the outer surface of the heat exchange assembly 101 to the sum of the inner surfaces of all the heat exchange tubes 204 is 5-45, the range is defined to ensure that the inner surface area of the heat exchange tube cannot be too large under the condition that the area of the outer surface of the heat exchange assembly 101 is constant, namely the diameter of the heat exchange tube is as small as possible, the refrigerant at the center of the flow cross section of the heat exchange tube 204 can also fully exchange heat with the tube body 2042 of the heat exchange tube 204, and the heat; meanwhile, the wind resistance of the heat exchange tube 204 is reduced, and certainly, the inner surface area of the heat exchange tube 204 also needs to be ensured not to be too small, the tube diameter of the heat exchange tube 204 at least needs to be larger than the thickness of the fin plate 203, and the heat exchange performance of the heat exchanger 10 is improved on the premise of ensuring the smaller refrigerant filling amount. Furthermore, the ratio of the area of the outer surface of the heat exchange component 101 to the area of the sum of the inner surfaces of all the heat exchange tubes 204 is 20-30.

The plurality of heat exchange assemblies 101 are all of the same structure and shape, and one heat exchange assembly 101 in two adjacent heat exchange assemblies 101 is turned over by 180 degrees relative to the other heat exchange assembly 101.

In one embodiment provided in the present application, two adjacent heat exchange assemblies 101 constitute a basic unit, in which a second heat exchange assembly 101 is turned 180 ° with respect to a first heat exchange assembly 101 and then arranged opposite to the first heat exchange assembly 101, and then a plurality of heat exchange assemblies 101 are arrayed in the basic unit. The arrangement mode realizes staggered arrangement of the heat exchange tubes 204, is beneficial to reducing air side pressure drop and is beneficial to delaying frosting.

In a single heat exchange assembly 101, the number of the heat exchange tubes 204 is greater than or equal to 2, and may be 3, 4, 5, and the like, and the plurality of heat exchange tubes 204 are arranged at intervals in the width direction of the heat exchange assembly 101.

As shown in fig. 7, the fin plate 203 comprises a body 400 and a plurality of bridges 401 protruding from the surface of the body 400, the projections of the bridges 401 on the surface of the body 400 have elongated shapes extending along the length direction of the heat exchange assembly 101, and bridge holes 402 are formed between the bridges 401 and the surface of the body 400, and the bridge holes 402 are used for passing the heat exchange air flow.

The shape of the bridge opening 402 of the bridge plate 401 may be an arch, a semicircle, a square, an isosceles trapezoid, etc. The heat exchange air flow can be blown through the bridge holes 402 as it passes through the fin plates 203. The top of the bridge piece 401 may abut or be spaced a distance from the fin plate 203 of another heat exchange assembly 101. The arrangement of the bridge fins 401 can enhance heat exchange and improve the heat exchange efficiency between the fin plate 203 and air.

Referring to fig. 8, 9, 10, 12, the heat exchange assembly 101 includes two connection zones 302 located on either side of the main heat exchange zone 301 in its length direction. The size of the end of at least one connection region 302 in the width direction of the heat exchange member 101 in the two connection regions 302 is smaller than the size of the main heat exchange region 301 in the width direction of the heat exchange member 101. The pipe body 201 of the header 100 is provided with an insertion part matched with the tail end of the connection area 302, and at the insertion part, the pipe body 201 of the header 100 is hermetically connected with the tail end of the connection area 302 of the heat exchange assembly 101. The inner cavity 2041 of the heat exchange tube 204 is communicated with the inner cavities 202 of the two collecting pipes 100, and the inner cavity 2041 of the heat exchange tube 204 and the inner cavity 202 of the collecting pipe 100 form a part of a refrigerant flow passage.

Since the size of the end of at least one of the two connection regions 302 in the width direction of the heat exchange module 101 is smaller than the size of the main heat exchange region 301 in the width direction of the heat exchange module 101, the fin plates and the heat exchange tube 204 may be optionally subjected to necking treatment in the connection region 302, for example, by removing a portion of the fin plate 203, and bending and gathering the heat exchange tube 204.

In the embodiment provided by the application, in the length direction of the heat exchange assembly 101, the length of the heat exchange tube 204 is greater than that of the fin plate 203, and both sides of the heat exchange tube 204 in the length direction of the heat exchange assembly 101 exceed the fin plate 203. The portion of the heat exchange tube 204 located in the main heat exchange zone 301 forms a main section 501. At each connection area 302 of the heat exchange assembly 101, the heat exchange tube 204 includes a mounting section 503 and a mating section 502. The end of the connection region 302 forms a mounting section 503, and the mating section 502 is connected between the mounting section 503 and the main section 501. That is, the heat exchange tube 204 comprises a main body section 501, two installation sections 503 and two matching sections 502, two installation sections 503 are respectively formed at two ends of the heat exchange tube 204 in the length direction, the two matching sections 502 are respectively located at two sides of the main body section 501 in the length direction, and the matching sections 502 are connected between the installation sections 503 and the main body section 501.

Referring to fig. 10, the plurality of heat exchange tubes 204 of the heat exchange assembly 101 includes at least one first heat exchange tube 204 ', and the fitting section 502 of the first heat exchange tube 204' is bent with respect to the main body section 501 thereof, so that the mounting sections 503 of the plurality of heat exchange tubes 204 are disposed to be gathered in the width direction of the heat exchange assembly 101 compared to the main body section 501.

This application provides an optional implementation way to this kind of heat exchange assembly's preparation, and its heat exchange tube 204 of the heat exchange assembly of preliminary working can be the same with fin plate 203's length, and the processing procedure of second step can be close to terminal position of heat exchange assembly 101 and remain heat exchange tube 204 simultaneously to fin plate 203 excision partly, bends the processing to many heat exchange tubes 204 that remain for the installation section 503 of many heat exchange tubes 204 compares main part section 501 and gathers together the setting on heat exchange assembly 101's width direction. Of course, the heat exchange unit 101 may be obtained without cutting the fin plate 203, for example, by integrally processing the heat exchange unit 101.

The installation sections 503 of the plurality of heat exchange tubes 204 may be gathered into one or more rows in the width direction of the heat exchange assembly 101, and in the case of multiple rows, that is, the installation sections 503 of the plurality of heat exchange tubes 204 may be spread in the length direction of the heat exchange assembly 101 before being gathered.

In the length direction of the heat exchange assembly 101, the length of the main body section 501 is greater than or equal to the length of the fin plate 203. The fitting section 502 and the mounting section 503 both extend beyond the fin plate 203 in the length direction of the heat exchange assembly 101.

The collecting main 100 is a cylindrical tube with a substantially circular cross section, and the outer diameter of the collecting main 100 is smaller than or equal to the distance between the main body sections 501 of the two heat exchange tubes 204 farthest away in the heat exchange assembly 101.

The tube body 201 of the header 100 is provided with an insertion portion, at which the tube body 201 of the header 100 is hermetically connected with the mounting section 503 of the heat exchange tube 204. The collecting main 100 and the fin plate 203 are arranged at intervals or are arranged in an abutting mode, or the pipe body 201 of the collecting main 100 is fixedly connected with the fin plate 203.

Referring to fig. 11, the insertion portion includes a plurality of insertion holes 205, and the insertion holes 205 penetrate through the tube 201 of the header 100. The size of the insertion hole 205 is matched with the end of the heat exchange tube 204, the insertion holes 205 are distributed at intervals on the tube body 201 of the collecting main 100, the installation sections 503 of the heat exchange tubes 204 are correspondingly arranged at intervals, the installation sections 503 of the heat exchange tubes 204 are inserted into the collecting main 100 through the insertion holes 205, and the tube body 201 of the collecting main 100 is hermetically connected with the tube body 2042 of the heat exchange tube 204 at the insertion hole 205. The number of the inserting holes 205 is matched with the number of the heat exchange tubes 204, and a one-to-one correspondence relationship is formed.

The plurality of insertion holes 205 are distributed in a plurality of rows in the axial direction of the header 100. The rows of the plugging holes 205 of the collecting main 100 are alternately arranged in a staggered way. On a plane perpendicular to the length direction of the heat exchange assembly 101, the projection of the central connecting line of each row of the plugging holes is approximately perpendicular to the axial direction of the header 100, a plurality of heat exchange tubes 204 of one heat exchange assembly 101 are arranged corresponding to at least one row of the plugging holes 205, and the number of the heat exchange tubes 204 of the heat exchange assembly 101 is matched with the number of the corresponding at least one row of the plugging holes 205.

In a single heat exchange assembly 101, the axes of the installation sections 503 of the plurality of heat exchange tubes 204 are all located on the same plane, the installation sections 503 of the heat exchange tubes 204 are arranged in parallel, and the plurality of heat exchange tubes 204 are arranged corresponding to one row of the insertion holes 205.

As shown in fig. 10 and 12, the plurality of heat exchange tubes 204 comprises a first heat exchange tube 204' and a second heat exchange tube 204 ", wherein the axes of the main body section 501, the fitting section 502 and the mounting section 503 of the second heat exchange tube 204" are coincident, and the axial direction of the second heat exchange tube 204 "is substantially parallel to the length direction of the heat exchange assembly 101.

The main body section 501, the matching section 502 and the mounting section 503 of the first heat exchange tube 204 ' are substantially straight tubes, the axial directions of the main body section 501 and the mounting section 503 of the first heat exchange tube 204 ' are substantially parallel to the length direction of the heat exchange assembly 101, and the matching section 502 of the first heat exchange tube 204 ' is obliquely arranged from one end of the main body section 501 close to the header 100 to the direction of the second heat exchange tube 204 ".

The number of the first heat exchange tubes 204 'is greater than or equal to 2, the number of the second heat exchange tubes 204' is greater than or equal to 1, the first heat exchange tubes 204 'are closer to the edge of the heat exchange assembly 101 in the width direction than the second heat exchange tubes 204', and the plurality of first heat exchange tubes 204 'are distributed on two sides of the second heat exchange tubes 204' in the width direction of the heat exchange assembly 101.

In an example, the number of the first heat exchange tubes 204 'is 4, and the number of the second heat exchange tubes 204 "is 1, then two first heat exchange tubes 204' may be respectively arranged on two sides of the second heat exchange tubes 204" in the width direction of the heat exchange assembly 101, or one first heat exchange tube 204 'is arranged on one side of the second heat exchange tube 204 ", and three first heat exchange tubes 204' are arranged on the other side of the second heat exchange tube 204". In another example, the number of the first heat exchange tubes 204 ' is 4, the number of the second heat exchange tubes 204 "is 2, then 2 second heat exchange tubes 204" are located at the middle position of the heat exchange assembly 101 in the width direction, 2 second heat exchange tubes 204 "are taken as a unit, 4 first heat exchange tubes 204 ' are distributed at two sides of the unit, and the number of the first heat exchange tubes 204 ' at two sides is not limited too much.

In this embodiment, for example, the heat exchange assembly 101 includes 3 heat exchange tubes 204, as shown in fig. 10 and 12, that is, one second heat exchange tube 204 ″ and two first heat exchange tubes 204 ', the matching portion 502 of the first heat exchange tube 204' on both sides in the width direction of the heat exchange assembly 101 is bent toward the second heat exchange tube 204 ″ to converge, and when the heat exchange assembly 101 is connected to the collecting main 100, only the heat exchange tube 204 is inserted into the collecting main 100.

Referring to fig. 10, a certain gap may be left between the gathered heat exchange tubes 204, and the single heat exchange tubes 204 are respectively inserted into the insertion holes 205 of the collecting main 100.

Or, referring to fig. 12, there is no gap or little gap between the mounting sections 503 of the gathered heat exchange tubes 204, for example, a plurality of mounting sections 503 of the heat exchange tubes 204 are sequentially attached to each other or a plurality of mounting sections 503 of the heat exchange tubes 204 are sequentially welded to form an integral structure, and the integral structure is integrally inserted into the header 100. Correspondingly, referring to a partial structural schematic diagram of the header 100 in fig. 13, the inserting portion includes a mounting groove 207 adapted to the mounting sections 503 of the plurality of heat exchange tubes 204, the mounting sections 503 of the plurality of heat exchange tubes 204 are integrally inserted into the header 100 through the mounting groove 207, and at the mounting groove 207, the tube bodies 201 of the header 100 are hermetically connected to the tube bodies 2042 of the heat exchange tubes 204.

The mounting grooves 207 are also distributed in multiple rows along the axial direction of the collecting main 100, two adjacent mounting grooves 207 are arranged in a staggered manner, meanwhile, the mounting grooves 207 can be in a slender shape, such as a rectangle or an oblong shape, in the direction perpendicular to the axial direction of the collecting main 100, and the shape of the mounting grooves 207 can be matched with the outer contour of the mounting sections 503 of the multiple heat exchange tubes 204 which are gathered together into an integral structure.

Compared with the main body section 501, the mounting sections 503 of the plurality of heat exchange tubes 204 are gathered in the width direction of the heat exchange assembly 101, so that when the mounting sections 503 of the heat exchange tubes 204 are connected with the collecting pipe 100, the size of the collecting pipe 100 in the width direction of the heat exchange assembly 101 is favorably reduced, the size of the collecting pipe 100 is favorably reduced integrally, the thermal resistance influence caused by the wall thickness of the collecting pipe 100 is reduced, the heat exchange performance of the heat exchanger is improved, meanwhile, the welding difficulty can be reduced due to the relatively small welding size, the leakage risk is further reduced, and the stability of the heat exchanger is improved.

The present application further provides a heat exchanger 10 that includes a plurality of headers 100 and a plurality of heat exchange assemblies 101.

The manifold 100 includes an elongated tube body 201 and a manifold chamber 202. The axial directions of the plurality of headers 100 are substantially parallel, the plurality of heat exchange assemblies 101 are arranged at intervals in the axial direction of the header 100, and an air side flow passage is formed by a gap between adjacent heat exchange assemblies 101.

The heat exchange assembly 101 comprises a fin plate 203 and a plurality of heat exchange tubes 204, and the heat exchange assembly 101 comprises a main heat exchange zone 301. In the main heat exchange area 301, a plurality of heat exchange tubes 204 are distributed at intervals in the width direction of the heat exchange assembly 101, wherein the heat exchange tubes 204 are fixedly connected to the surface of the fin plate 203, or the fin plate 203 comprises a plurality of sub-plates 2031, and the heat exchange tubes 204 are connected between two adjacent sub-plates 2031. For each heat exchange assembly 101, in the length direction of the heat exchange assembly 101, the length of the heat exchange tube 204 is greater than that of the fin plate 203, and two ends of the heat exchange tube 204 in the length direction exceed the fin plate 203.

The plurality of heat exchange tubes 204 of the heat exchange assembly 101 are divided into at least two groups along the width direction of the heat exchange assembly 101, the number of each group of heat exchange tubes 204 is at least one, and each group of heat exchange tubes 204 is connected between the two collecting pipes 100.

For the adjacent two groups of heat exchange tubes 204, the inner cavities 2041 of the two groups of heat exchange tubes 204 are respectively communicated with the inner cavities 202 of two different collecting main 100 on one side in the length direction of the heat exchange tubes 204. The inner cavities 2041 of the two groups of heat exchange tubes 204 are communicated with the inner cavity 202 of the same header 100 on the other side, or the inner cavities of the two groups of heat exchange tubes 204 are respectively communicated with the inner cavities 202 of two different headers 100 on the other side, and the inner cavities 202 of the two headers 100 on the other side are communicated, so that the refrigerant flows in the inner cavities 2041 of the two groups of heat exchange tubes 204 in opposite directions.

In a transverse direction of the heat exchange assembly 100, the heat exchanger 10 has at least two refrigerant flow passes formed by the plurality of heat exchange assemblies 101 and the plurality of headers 100. In the main heat exchange area 301 corresponding to the plurality of heat exchange assemblies 101, the heat exchange tubes 204 of the plurality of heat exchange assemblies 101 are alternately arranged in a staggered manner in the axial direction of the collecting main 100 by taking the heat exchange assemblies 101 as a unit.

The tube body 201 of each collecting tube 100 is provided with a plurality of plugging holes 205, the plurality of plugging holes 205 are arranged at intervals, the plurality of plugging holes 205 are provided with a plurality of rows in the axial direction of the collecting tube 100, the number of the plugging holes 205 in each row is matched with the number of the heat exchange tubes 204 connected to the collecting tube 100 in a single heat exchange assembly 101, the plurality of rows of plugging holes 205 are arranged along the axial direction of the collecting tube 100 in an alternating staggered manner, the size of each plugging hole 205 is matched with the size of each heat exchange tube 204, and the tube body 201 of the collecting tube 100 is hermetically connected with the tube body 2042 of each heat.

As shown in fig. 14, each of the plurality of heat exchange tubes 204 is a straight tube extending in the length direction of the heat exchange assembly 101, the plurality of headers 100 includes a first header 1001, a second header 1002, a third header 1003 and a fourth header 1004, the first header 1001 and the third header 1003 are arranged side by side, and the second header 1002 and the fourth header 1004 are arranged side by side.

The first header 1001 and the second header 1002 are disposed opposite to each other in the length direction of the heat exchange assembly 101. The third header 1003 and the fourth header 1004 are disposed opposite to each other in the longitudinal direction of the heat exchange module 101.

The heat exchanger 10 has two refrigerant flow passes in the width direction of the heat exchange assembly 101, each refrigerant flow pass comprising at least one heat exchange tube 204 of each heat exchange assembly 101. The two collecting pipes 100 are in a group, each refrigerant flowing return stroke comprises a group of collecting pipes 100, and the two collecting pipes 100 in the group are respectively positioned at two sides of the heat exchange pipe 204 corresponding to the refrigerant flowing return stroke.

Therefore, by arranging the heat exchange tubes 204 matched with the refrigerant flowing return stroke and the collecting pipe 100, a plurality of refrigerant flowing return strokes of the heat exchanger can be realized, the length of the flowing path of the refrigerant can be prolonged, and the heat exchange performance of the heat exchanger can be improved.

Referring to fig. 15, the second header 1002 abuts against the fourth header 1004, the pipe bodies 201 of the second header 1002 and the fourth header 1004 are provided with first communication holes 208, and the first communication holes 208 of the second header 1002 are aligned with the first communication holes 208 of the fourth header 1004, so that the inner cavities 202 of the second header 1002 and the inner cavities 202 of the fourth header 1004 are communicated through the abutting first communication holes 208 at the position where the pipe bodies 201 abut against each other.

In order to ensure the connection stability of the second header 1002 and the fourth header 1004, in an alternative manner, referring to fig. 15, the heat exchanger 10 includes a first connecting body 209, the first connecting body 209 is at least partially located between the second header 1002 and the fourth header 1004, the first connecting body 209 has a shape of a substantially triangular prism, two of the three sides of the first connecting body 209 are recessed to form an arc-shaped concave surface, the shape of the two arc-shaped concave surfaces corresponds to the shape of part of the surfaces of the second header 1002 and the fourth header 1004, and the part of the surfaces of the second header 1002 and the fourth header 1004 are welded to at least part of the surfaces of the arc-shaped concave surfaces. Wherein, the welding mode can be brazing.

Further, the first connecting body 209 is opened with a second communicating hole 210 penetrating the two concave surfaces. The pipe body 201 of the second header 1002 and the pipe body 201 of the fourth header 1004 are both provided with third communication holes 211. The two sides of the second communication hole 210 are aligned with the third communication hole 211 of the second header 1002 and the third communication hole 211 of the fourth header 1004, respectively, the pipe body 201 of the second header 1002 is spaced from the pipe body 201 of the fourth header 1004 at a position where the third communication hole 211 is opened, and the third communication hole 211 of the second header 1002 and the third communication hole 211 of the fourth header 1004 are communicated through the second communication hole 210, so that the inner cavity 202 of the second header 1002 is communicated with the inner cavity 202 of the fourth header 1004.

As shown in fig. 16, in another alternative, the heat exchanger 10 includes a second connector 212, the second connector 212 is provided with a fourth communication hole 213, the second header 1002 and the fourth header 1004 are provided with fifth communication holes 214 corresponding to the fourth communication holes 213, the second connector 212 is welded between the second header 1002 and the fourth header 1004, the second connector 212 may be in a long plate shape, a side of the second connector 212 facing the second header 1002 is an arc-shaped inner concave surface that fits with the pipe body of the second header 1002, a side of the second connector 212 facing the second header 1002 is an arc-shaped inner concave surface that fits with the pipe body of the fourth header 1004, two sides of the fourth communication hole 213 are respectively aligned with the fifth communication holes 214 of the second header 1002 and the fifth communication holes 214 of the fourth header 1004, and the inner cavities 202 of the second header 1002 and the fourth header 1004 are communicated with each other through the fifth communication holes 214 and the fourth communication holes 213.

Referring to fig. 17, the present application further provides a method without providing the first connection body 209 or the second connection body 212, in the heat exchanger 10 provided in the present application, the multiple collecting pipes 100 include a first collecting pipe 1001, a second collecting pipe 1002, and a third collecting pipe 1003, the first collecting pipe 1001 and the third collecting pipe 1003 are arranged side by side, the first collecting pipe 1001 and the third collecting pipe 1003 are located on one side of the heat exchange assembly 101 in the length direction, and the second collecting pipe 1002 is located on the other side of the heat exchange assembly 101 in the length direction.

The multiple groups of heat exchange tubes 204 comprise a first group of heat exchange tubes S1 and a second group of heat exchange tubes S2 which are adjacent in the width direction of the heat exchange assembly 101, the first group of heat exchange tubes S1 is connected between the first collecting pipe 1001 and the second collecting pipe 1002, and the second group of heat exchange tubes S2 is connected between the third collecting pipe 1003 and the second collecting pipe 1002. The number of the first group of heat exchange tubes S1 and the number of the second group of heat exchange tubes S2 are both greater than or equal to 1, the number of the first group of heat exchange tubes S1 and the number of the second group of heat exchange tubes S2 may be the same or different, and in the embodiment provided by the application, the number of the first group of heat exchange tubes S1 is 2, and the number of the second group of heat exchange tubes S2 is 1.

Each heat exchange tube 204 of the first group of heat exchange tubes S1 has a first end 11 connected to the first header 1001 and a second end 12 connected to the second header 1002, and each heat exchange tube 204 of the second group of heat exchange tubes S2 has a third end 13 connected to the third header 1003 and a fourth end 14 connected to the second header 1002, wherein the second end 12 and the fourth end 14 converge in the width direction of the heat exchange assembly 101 between the first end 11 and the third end 13 as compared to between the second end 11 and the fourth end 14.

The second end portion 12 and the fourth end portion 14 which are gathered together may be integrally inserted into the second collecting pipe 1002 by being attached to each other, or integrally inserted into the second collecting pipe 1002 by being welded into an integral structure, or may be respectively inserted into the second collecting pipe 1002, which is not limited by the present application.

As shown in fig. 18, 3 refrigerant flow passes are illustrated. At least two refrigerant flow returns are communicated in series to form a part of the refrigerant flow channel, and the refrigerant flow directions of the two adjacent refrigerant flow returns are opposite. Of course, the refrigerant flow path may also include more flow path return paths, such as 4-way return, 5-way return, etc., which should not be limited too much in this application.

As shown in fig. 19, for example, in the case of 3 passes, one fifth collecting pipe 1005 and one sixth collecting pipe 1006 are added to 2 passes, the first collecting pipe 1001, the third collecting pipe 1003 and the fifth collecting pipe 1005 are arranged in parallel, the second collecting pipe 1002, the fourth collecting pipe 1004 and the sixth collecting pipe 1006 are arranged in parallel, and the inner cavity 202 of the third collecting pipe 1003 is communicated with the inner cavity 202 of the fifth collecting pipe 1005, so that the 3 refrigerant flow path passes have a flow direction similar to a serpentine twist. Similarly, a first connection body 209 or a second connection body 212 may be disposed between the third header 1003 and the fifth header, and the function of the first connection body 209 or the second connection body 212 is described in detail above and will not be described herein again.

In the above embodiment, the plurality of headers 100 may be all cylindrical tubes having a perfect circle cross section, and the plurality of headers 100 may have the same tube diameter size.

Similarly, referring to fig. 4 and 5, in the heat exchanger 10 in which at least two refrigerants flow back passes, the cross section of the fin plate 203 is a continuous zigzag shape or a wave shape on a plane perpendicular to the length direction of the heat exchange assembly 101, and the cross section of the heat exchange tube 204 is matched with the wave crest or the wave trough of the zigzag shape or the wave shape. Part of the outer surface of the heat exchange tube 204 is welded and fixed with the wave crest or the wave trough of the broken line shape or the wave shape, so that the fin plate 203 is partially arranged in a surrounding manner towards the heat exchange tube 204 at the wave crest or the wave trough of the broken line shape or the wave shape.

Although the present application has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the application, and all changes, substitutions and alterations that fall within the spirit and scope of the application are to be understood as being covered by the following claims.

Claims (10)

1. A heat exchanger (10) comprising a plurality of heat exchange assemblies (101) and a header group;

the collecting pipe group comprises two collecting pipes (100) which are respectively positioned at two sides of the heat exchange assembly (101) in the length direction, and each collecting pipe (100) comprises a longitudinal pipe body (201) and a collecting pipe inner cavity (202);

a plurality of heat exchange assemblies (101) are arranged at intervals along the axial direction of the collecting pipe (100); gaps between adjacent heat exchange assemblies (101) form air side flow channels; each heat exchange assembly (101) comprises a fin plate (203) and at least one heat exchange tube (204); the heat exchange assembly (101) comprises a main heat exchange area (301), and the heat exchange tube (204) is fixedly connected to the surface of the fin plate (203) at the main heat exchange area (301); or the fin plate (203) comprises a plurality of sub-plates (2031), and the heat exchange tube (204) is connected between two adjacent sub-plates (2031);

the heat exchange tube (204) is connected between the two collecting pipes (100) in the length direction, an inner cavity (2041) of the heat exchange tube (204) is communicated with the inner cavities (202) of the two collecting pipes (100), and the inner cavity (2041) of the heat exchange tube (204) and the inner cavity (202) of the collecting pipe (100) form a part of a refrigerant flow channel; at least part of the heat exchange tube (204) protrudes out of at least one side of the fin plate (203) in the arrangement direction of the heat exchange assemblies (101); and at least one pair of adjacent heat exchange tubes (204) are arranged in a staggered manner in the main heat exchange areas (301) corresponding to the two adjacent heat exchange assemblies (101), wherein the two heat exchange tubes (204) of the pair belong to the two adjacent heat exchange assemblies (101) respectively.

2. The heat exchanger (10) of claim 1, wherein the heat exchange tube (204) has a length greater than the length of the fin plate (203) in the longitudinal direction of the heat exchange assembly (101), and both ends of the heat exchange tube (204) extend beyond the fin plate (203) in the longitudinal direction of the heat exchange assembly (101); the collecting pipe (100) is provided with a plug hole (205) matched with the end of the heat exchange pipe (204); in the plug hole (205), the tube body (201) of the collecting tube (100) is hermetically connected with the tube body (2042) of the heat exchange tube (204); the pipe body (201) of the collecting pipe (100) and the fin plate (203) are arranged at intervals or in abutting joint, or the pipe body (201) of the collecting pipe (100) is fixedly connected with the fin plate (203).

3. The heat exchanger (10) according to claim 1, wherein the heat exchange tubes (204) are welded to the surface of the fin plate (203) within the main heat exchange zone (301); in the same heat exchange assembly (101), the at least one heat exchange tube (204) is convexly arranged on the surface of the same side of the fin plate (203), in two adjacent heat exchange assemblies (101), the heat exchange tube (204) of one heat exchange assembly (101) and the heat exchange tube (204) of the other heat exchange assembly (101) are positioned on different sides of the fin plate (203) where the heat exchange tube (204) of the other heat exchange assembly (101) is positioned, and the heat exchange tube (204) of the one heat exchange assembly (101) and the heat exchange tube (204) of the other adjacent heat exchange assembly (101) are arranged in a staggered mode in the main heat exchange areas corresponding to the two heat exchange assemblies (101).

4. The heat exchanger (10) according to claim 2 or 3, wherein the cross section of the fin plate (203) is a continuous zigzag shape and the cross section of the heat exchange tube (204) is a diamond shape on a plane perpendicular to the length direction of the heat exchange assembly (101); the heat exchange tube (204) is combined with the fin plate (203) based on two adjacent side walls of the rhombic shape of the heat exchange tube (204) so that the fin plate (203) forms a semi-surrounding arrangement for the heat exchange tube (204).

5. The heat exchanger (10) of claim 2 or 3, wherein the cross-section of the fin plate (203) in a plane perpendicular to the length direction of the heat exchange assembly (101) is wave-shaped; the cross section of the heat exchange tube (204) is circular or elliptical;

the fin plate (203) comprises a plurality of straight line portions (2033) and a plurality of curved portions (2032), the curved portions (2032) are located between two adjacent straight line portions (2033), and the curved portions (2032) form peaks and troughs of the wave shape; part of the outer surface of the heat exchange tube (204) is fixedly combined with an arc part (2032) of the fin plate (203), wherein the curvature of the combined part of the heat exchange tube (204) and the arc part (2032) is the same as the curvature of the arc part (2032) in size and direction.

6. The heat exchanger (10) of claim 1, wherein the heat exchange tube (204) comprises a tube body (2042) at the periphery of its inner cavity, and the plurality of sub-plates (2031) of the fin plate (203) are integrally formed with the tube body (2042) by a casting process or by an extrusion process.

7. The heat exchanger (10) according to any one of claims 1 to 3, wherein in a single heat exchange assembly (101), the ratio of the area of the outer surface of the heat exchange assembly (101) to the area of the sum of the inner surfaces of all heat exchange tubes (204) is 5 to 45.

8. The heat exchanger (10) of any one of claims 1 to 3, wherein the plurality of heat exchange assemblies (101) are all of the same structure and shape, and one (101) of two adjacent heat exchange assemblies (101) is arranged to be turned 180 ° relative to the other heat exchange assembly (101).

9. The heat exchanger (10) according to any one of claims 1 to 3, wherein the length direction of the heat exchange assembly (101) is approximately perpendicular to the axial direction of the collecting main (100), the number of the heat exchange tubes (204) in a single heat exchange assembly (101) is greater than or equal to 3, and the plurality of heat exchange tubes (204) are arranged at intervals in the width direction of the heat exchange assembly (101).

10. The heat exchanger (10) according to any one of claims 1 to 3, wherein the fin plate (203) comprises a body (400) and a plurality of bridges (401) protruding from the surface of the body (400), the projections of the bridges (401) on the surface of the body (400) have an elongated shape extending along the length direction of the heat exchange assembly (101), and a bridge hole (402) is formed between the bridges (401) and the surface of the body (400), and the bridge hole (402) is used for passing the heat exchange air flow.

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