HEAT EXCHANGER

Abstract

A heat exchanger can include a plurality of flat tubes each having a heat exchange channel for a flow of a heat exchange medium, and a first collector pipe and a second collector pipe connected to distal sections of the plurality of flat tubes and disposed side by side. Chambers of the first collector pipe and the second collector pipe can be in communication with the heat exchange channels of the flat tubes. The flat tube includes a main body section, a distal section, and a torsion section connected therebetween. The main body section and the distal sections can be straight sections. The first collector pipe and the second collector pipe can be provided with mounting holes for the distal section being inserted into. A length direction of the mounting hole can be inclined to the axis of the first collector pipe or the axis of the second collector pipe.

Description

TECHNICAL FIELD

The present application relates to a field of heat exchange, and particularly, to a heat exchanger.

BACKGROUND

With the continuous development of new energy vehicles, the application of environmentally friendly CO2 refrigerant in automotive air conditioning systems has been attracted to the researchers in the related field. CO2 refrigerant has outstanding advantages of low greenhouse effect index (GMP=1), low ozone depletion potential (ODP=0), non-flammability, non-toxicity, and stable chemical properties. CO2 refrigerant has a relatively great latent heat of evaporation and extremely high refrigeration capacity per unit volume, therefore, a compressor and components for the CO2 refrigerant can have small sizes. However, a heat emission process and a heat absorption process of CO2 refrigerant are carried out under a condition of transcritical state, and a heat exchanger using CO2 as heat exchange medium is required to have relatively high pressure resistance. The pressure resistance of the heat exchanger is high when a collector pipe has a small diameter.

SUMMARY

According to a first aspect of an embodiment of the present application, a heat exchanger is provided to solve the problem of insufficient pressure resistance of the heat exchanger by reducing the diameter of the collector pipe.

The heat exchanger includes a collector pipe and a flat tube.

The flat tube includes a generally flat main body portion, a first end portion inserted thereto, and a second end portion inserted thereto. The first end portion and the second end portion are twisted towards a same side respect to the main body portion. There is an angle α between a plane defined by a length direction and a width direction of the main body portion and a plane defined by length directions and width directions of the first distal section or the second distal section, wherein α≠90°.

The collector pipe defines a mounting hole for at least a section of the first end portion or at least a section of the second end portion being inserted thereto and connected thereto. The length direction of the main body section is substantially perpendicular to an axis of the collector pipe. There is an angle β between a length direction of the mounting hole and an axis of the collector pipe, wherein β≠90°.

Optionally, the included angle α between the plane defined by the length direction and the width direction of the main body section and the plane defined by the length directions and the width directions of the distal section satisfies 15°≤α<40°, and the included angle (between the length direction of the mounting hole and the axis of the collector pipe satisfies 50°<β≤75°.

Optionally, the planes defined by the length directions and the widths direction of the two distal sections of the flat tube are substantially parallel with each other.

Optionally, the plane defined by the length direction and the width direction of the main body section is substantially perpendicular to the axis of the collector pipe.

Optionally, the heat exchanger further includes a partition plate, the collector pipe is provided with a partition plate groove, the partition plate is inserted into and connected to the partition plate groove to partition the collector pipe into two or more chambers that are isolated from each other.

Optionally, the collector pipe includes a first collector pipe and a second collector pipe, the first collector pipe is provided with the partition plate groove, the partition plate is inserted into and connected to the partition plate groove to partition the first collector pipe into a first chamber and a second chamber that are isolated from each other;

a plurality of flat tubes is stacked to form core portions for heat exchange, the core portion includes a first core portion formed by a part of the plurality of flat tubes, and a second core portion formed by another part of the plurality of flat tubes; and

flat tubes of the first core portion have one end inserted into and connected to the first collector pipe to communicate heat exchange channels of the flat tubes with the first chamber, and flat tubes of the second core portion have one end inserted into and connected to the first collector pipe to communicate heat exchange channels of the flat tubes with the second chamber.

Optionally, the core portions further include a third core portion from by a third part of the plurality of flat tubes, and the partition plate partitions the second collector pipe into a third chamber and a fourth chamber that are isolated from each other;

the flat tubes of the first core portion have another end inserted into and connected to the second collector pipe to communicate heat exchange channels of the flat tubes with the third chamber, the flat tubes of the second core portion have another end inserted into and connected to the second collector pipe to communicate heat exchange channels of the flat tubes with the third chamber, and heat exchange channels of flat tubes of the third core portion communicate the second chamber with the fourth chamber.

Optionally, a length direction of the partition plate groove is not perpendicular to an axis of the first collector pipe or an axis of the second collector pipe.

Optionally, a length direction of the mounting hole in the first collector pipe is substantially parallel with the partition plate groove; or a length direction of a mounting hole in the second collector pipe is substantially parallel with a length direction of the partition plate groove.

Optionally, the partition plate includes a first surface and a second surface that have a larger area that are opposite to each other and have large areas, and a first side surface and a second side surface that adjoin the first surface and the second surface; the first surface and the second surface are parallel with each other, a perpendicular line of the first side surface of the partition plate is not perpendicular to a perpendicular line of the first surface and a perpendicular line of the second surface and the second side surface of the partition plate is not perpendicular to the perpendicular line of the first surface and the second surface.

Optionally, the heat exchanger further includes an inlet member and an outlet member;

the inlet member includes a tube portion and a distribution portion that are connected to each other, the tube portion extends from a first end of the first collector pipe to the second chamber, the distribution portion is directly adjacent to the second chamber, the distribution portion is internally provided with a flow path arranged along a length direction of the first collector pipe and a plurality of distribution holes distributed along a length direction of the flow path, the plurality of distribution holes communicates the flow path with the second chamber, and the tube portion is in communication with the flow path; and

the outlet member is disposed at the first end of the first collector pipe and in communication with the first chamber of the first collector pipe.

Optionally, the heat exchanger further includes a distribution tube, each of the first collector pipe and the second collector pipe has a first end and a second end that are opposite to each other along a length direction, the third chamber is closer to the first end of the second collector pipe than the fourth chamber, and the distribution tube extends from the first end of the second collector pipe through the third chamber to communicate with the fourth chamber; and

the partition plate inserted into a partition plate groove of the second collector pipe is a perforated partition plate.

Optionally, the heat exchanger further includes a connecting member, and a third collector pipe and a fourth collector pipe that are arranged side by side, an axis of the third collector pipe is substantially parallel with an axis of the fourth collector pipe, and the third collector pipe and the fourth collector pipe are spaced apart from the first collector pipe and the second collector pipe by a predetermined distance; the connecting member is disposed in a gap between the first collector pipe and the second collector pipe that are arranged side by side or between the third collector pipe and the fourth collector pipe that are arranged side by side, and two collector pipes that are arranged side by side are in communication with each other through the connecting member.

Optionally, the third collector pipe and the fourth collector pipe are each provided with a mounting hole, into which the distal section is to be inserted;

the core portion further includes a fourth core portion formed by a part of the plurality of flat tubes, and a fifth core portion formed by another part of the plurality of flat tubes;

the partition plate partitions the first collector pipe into a first chamber and a second chamber that are isolated from each other, and partitions the second collector pipe into a third chamber and a fourth chamber that are isolated from each other; a part of flat tubes of the fourth core portion communicates the first chamber with an inner chamber of the third collector pipe, and another part of the flat tubes of the fourth core portion communicates the second chamber with the inner chamber of the third collector pipe; a part of flat tubes of the fifth core portion communicates the third chamber with an inner chamber of the fourth collector pipe, and another part of the flat tubes of the fifth core portion communicates the fourth chamber with the inner chamber of the fourth collector pipe; and the connecting member communicates the second chamber with the fourth chamber.

Optionally, the connecting member is directly adjacent to the second chamber and the fourth chamber, the connecting member is provided with a plurality of through-holes along a length direction of the connecting member, and the plurality of through-holes communicates the second chamber with the fourth chamber.

Optionally, the connecting member is disposed between the first collector pipe and the second collector pipe, the first collector pipe and the second collector pipe are both in cylindrical shapes, and surfaces of the connecting member to be attached to the first collector pipe and the second collector pipe are arcuate concave surfaces.

Optionally, the heat exchanger further includes a connecting member disposed between the third collector pipe and the fourth collector pipe.

Optionally, the third collector pipe and the fourth collector pipe are both in cylindrical shapes, and surfaces of the connecting member to be attached to the third collector pipe and the fourth collector pipe are arcuate concave surfaces.

In the heat exchanger according to the above embodiments, the flat tube has twisted sections at two ends close to the collector pipe, such that the flat tube is twisted and obliquely inserted into the collector pipes. In this way, a diameter of the collector pipe is unnecessary to be larger than a width of the flat tube, thereby facilitating reducing the diameter of the collector pipe and enhancing the pressure resistance of the collector pipe.

The additional aspects and advantages of the present application will be described below.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1A to FIG. 13 are structural schematic diagrams of a heat exchanger according to an embodiment of the present application; and FIG. 14 to FIG. 21 are structural schematic diagrams of a heat exchanger according to another embodiment, wherein

FIG. 1A is a structural schematic diagram of a heat exchanger provided by an embodiment of the present application;

FIG. 1B is a structural schematic diagram of a distribution portion of the heat exchanger shown in FIG. 1A;

FIG. 2A is a structural schematic diagram of the heat exchanger shown in FIG. 1A, which is provided with another inlet member;

FIG. 2B is a structural schematic diagram of the inlet member shown in FIG. 2A;

FIG. 3 is a structural schematic diagram of the heat exchanger shown in FIG. 1A, which is provided with a distribution tube;

FIG. 4 is a side view of the heat exchanger shown in FIG. 3;

FIG. 5A is a perspective view of a flat tube;

FIG. 5B is a side view of the flat tube;

FIG. 5C is a front view of the flat tube;

FIG. 5D is a top view of the flat tube;

FIG. 6 is a partial structural schematic diagram of a first collector pipe;

FIG. 7 is a partial structural schematic diagram of the flat tube;

FIG. 8 is a schematic diagram in another viewing angle of a partial structure of the flat tube shown in FIG. 7;

FIG. 9 is a schematic diagram in another viewing angle of a partial structure of the first collector pipe shown in FIG. 6;

FIG. 10 is a schematic diagram of a partial structure of the heat exchanger shown in FIG. 1;

FIG. 11A is a perspective schematic diagram of a partition plate;

FIG. 11B is a structural schematic diagram in another viewing angle of the partition plate 40;

FIG. 11C is a top view of the partition plate;

FIG. 11D is a side view of the partition plate;

FIG. 12 is a perspective schematic view of a partition plate with a hole;

FIG. 13 is a structural schematic view of the distribution tube;

FIG. 14 is a structural schematic view of another heat exchanger provided by an embodiment of the present application;

FIG. 15 is a partial structural schematic diagram of the heat exchanger shown in FIG. 14;

FIG. 16A is a top view of the heat exchanger shown in FIG. 14;

FIG. 16B is a front view of the heat exchanger shown in FIG. 14;

FIG. 16C is a bottom view of the heat exchanger shown in FIG. 14;

FIG. 16D is a structural schematic diagram of a first collector pipe and a second collector pipe connected thereto;

FIG. 17A is an exploded view of a partial structure of the heat exchanger shown in FIG. 14;

FIG. 17B is a structural schematic diagram of a connecting member;

FIG. 17C is a structural schematic diagram of the second collector pipe;

FIG. 18A is an exploded view of another partial structure of the heat exchanger shown in FIG. 14;

FIG. 18B is a structural schematic diagram of a connecting member;

FIG. 18C is a structural schematic diagram of a fourth collector pipe;

FIG. 19A to 19D are structural schematic diagrams of a flat tube twisted towards the same side, wherein

FIG. 19A is a structural schematic diagram of the flat tube before being twisted;

FIG. 19B is a structural schematic diagram of the flat tube being partially twisted;

FIG. 19C is another structural schematic diagram of the flat tube being partially twisted;

FIG. 19D is a structural schematic diagram of the flat tube after being partially twisted;

FIG. 20 is a structural schematic diagram of a flat tube twisted towards different sides; and

FIG. 21 is a structural schematic diagram of another partition plate provided by an embodiment of the present application.

DESCRIPTION OF EMBODIMENTS

Embodiments will be described in detail herein, which are illustrated in the accompanying drawings. Unless otherwise indicated, in the description regarding the drawings, identical reference signs represent the same or similar elements in the different drawings. The implementations described in the following embodiments are not all of the implementations consistent with the present application. Instead, they are merely examples of devices and methods consistent with some aspects of the present application detailed in the pending claims.

The terms used in the embodiments of the present application are merely for the purpose of describing specific embodiment, rather than limiting the present application. The terms “a”, “an”, “the” and “said” in a singular form in the embodiments of the present application and the attached claims are also intended to include plural forms thereof, unless noted otherwise.

It should be understood that the terms “first”, “second”, and similar terms do not denote limitations of sequence, quantity, or importance, but are merely used to distinguish different components. Similarly, the words “a”, “an”, or the like do not denote a limitation of quantity, but indicates at least one; and when not explicitly stated, “a plurality of” mentioned in the present application means two or more. Unless otherwise indicated, the terms “front”, “rear”, “lower” and/or “upper” are used for convenience of description and are not limited to one location or one spatial orientation. The expression such as “comprising” or “including” means that an element or object followed by “comprising” or “including” encompasses listed elements or objects and their equivalents following “comprising” or “including”, without excluding other elements or objects.

A heat exchanger and a heat exchange system according to the some embodiments of the present application will be described in detail below with reference to the accompanying drawings. The features in the embodiments described below may be complementary to each other or combined with each other without contradiction.

FIG. 1 to FIG. 13 are structural schematic diagrams of a heat exchanger 100 according to an embodiment of the present application. The heat exchanger 100 can be applied in various types of heat exchange systems such as air conditioners. The heat exchanger 100 mainly exchanges heat through a refrigerant inside the heat exchanger and air flowing outside the heat exchanger to provide a relatively comfortable ambient temperature.

Referring to FIG. 1, and further referring to FIG. 2 to FIG. 13 when necessary, the heat exchanger 100 includes a core portion for heat exchange formed by stacking a plurality of flat tubes 30, and a first collector pipe 10 and a second collector pipe 20 that are connected to ends of the plurality of flat tubes 30 and are arranged side by side.

The flat tube 30 is a micro-channel flat tube, and the flat tube 30 is internally provided with a micro-channel. In combination with FIG. 5, the heat exchanger 30 includes a first tube portion 31, a second tube portion 32, and a bent portion 33 connecting the first tube portion 31 with the second tube portion 32. It is also possible that the flat tube 30 is not a micro-channel flat tube, that is, the channel inside the flat tube is not a micro-channel. It should be noted that the first tube portion 31, the bent portion 33 and the second tube portion 32 of the flat tube 30 are of an integral structure, i.e., each flat tube 30 is formed by bending one flat tube.

At least one of the first tube portion 31 and the second tube portion 32 includes a main body section, a distal section, and a twisted section connecting the main body section with the distal section. It should be understood that, the main body section is the main heat exchange area in the heat exchanger 100. Therefore, the main body section generally has a much greater length than the twisted section and the distal section. In an example, each of the first tube portion 31 and the second tube portion 32 includes the main body section, the distal section, and the twisted section. The first tube section 31 includes a main body section 311, a distal section 313, and a twisted section 312 connecting the main body section 311 with the distal section 313. The second tube portion 32 includes a main body section 321, a distal section 323, and a twisted section 322 connecting the main body section 321 with the distal section 323. The main body sections 311, 321 and the distal sections 313, 323 are all straight sections that are not twisted and deformed.

In a specific implementation process, the twisted section 312 can be formed by twisting the heat exchange tube region that is originally straight, i.e., the main body section 311, the twisted section 312, and the distal section 313 are of an integral structure. A direction of twisting can be either clockwise or counterclockwise.

Moreover, taking the first tube portion 31 as an example, the twisted section 312 formed by twisting forms an angle α between a plane of the main body section 311 and a plane of the distal section 313. In other words, the angle α is limited between a plane S1 defined by a length direction L3 and a width direction W3 of the main body section 311 and a plane S2 defined by a length direction and a width direction of the distal section 313, in combination with FIG. 7 and FIG. 8. The angle α is also called as a twist angle α. The inventors, in combination with their own experiences on production and processing technology, have found the optimal range of the twist angle α: 15°≤α<40° through mathematical modeling and model optimization calculation and analysis.

The first collector pipe 10 defines a mounting hole 14, the second collector pipe 20 defines a mounting hole 24, and the two distal sections 313, 323 of each flat tube 30 are inserted into the mounting holes 14, 24, respectively.

The heat exchanger 100 further includes a partition plate 40. Correspondingly, the first collector pipe 10 defines a partition plate groove 15, and the partition plate 40 is inserted into the partition plate groove 15 to divide the first collector pipe 10 into a first chamber 11 and a second chamber 12 separated from each other. Further, the core portion includes a first core portion 301 formed by a part of the plurality of flat tubes 30, and a second core portion 302 formed by another part of the plurality of flat tubes 30. One end of each flat tube 30 forming the first core portion 301 communicates with the first chamber 11, and the other end thereof communicates with a chamber of the second collector pipe 20. One end of each of the flat tubes 30 forming the second core portion 302 communicates with the chamber of the second collector pipe 20, and the other end thereof communicates with the second chamber 12 of the first collector pipe 10.

Referring to FIGS. 1A-2B, the first chamber 11 of the first collector pipe 10 communicates with an inlet allowing a heat exchange medium to flow into the heat exchanger 100, and the second chamber 12 of the first collector pipe 10 communicates with an outlet allowing the heat exchange medium to flow out the heat exchanger 100. In this way, the heat exchange medium flows into the first chamber 11 of the first collector pipe 10 from the inlet, and flows into the chamber of the second collector pipe 20 after the heat exchange via the first core portion 301; then flows into the second chamber 12 after the heat exchange via the second core portion 302, and flows out through the outlet communicating with the second chamber 12. Therefore, a four-flow path arrangement of the heat exchange medium can be achieved in the heat exchanger.

The heat exchanger 100 further includes an inlet member 51 (in combination with FIG. 1A) or 52 (in combination with FIG. 2A), and an outlet member 56. The first and second collector pipes 10, 20 each has a first end 101 and a second end 103 opposite with each other along a length direction. The first chamber 11 is closer to the first end 101 of the first collector pipe 10 than the second chamber 12. Both ends of each of first and second collector pipes 10, 20 can be provided with end caps 19 to seal the collector pipes. The end cap 19 and the collector pipe can be integrally formed or can be independently provided. The end cap 19 can be a built-in end cap or an external end cap, which is not specifically limited in the present application and can be configured according to the specific application environment. The inlet member 51 includes a tube portion 511 and a distribution portion 512 connected thereto. The tube portion 511 extends from the first end 101 of the first collector pipe 10 to the distribution portion 512. The distribution portion 512 is disposed directly adjacent to the second chamber 12. The distribution portion 512 internally defines a flow path 5122 disposed along the length direction of the first collector pipe 10 and a plurality of distribution holes 5121 disposed along a length direction of the flow path 5122 (in conjunction with FIG. 1B). The distribution hole 5121 can be a circular hole or a waist hole. A plurality of through-holes (not shown) are formed in a wall of the first collector pipe 10 at the second chamber 12 corresponding to these distribution holes 5121. The tube portion 511 can be inserted into and connected to the flow path 5122 of the distribution portion 512. The distribution hole 5121 communicates the flow path 5122 with the second chamber 12 such that the refrigerant entering from the tube portion 511 is substantially uniformly distributed into the second chamber 12 through the respective distribution holes. The distribution portion 512 can be a block-shaped component that is independent of the tube portion 511. The distribution section 512 can be disposed between the first collector pipe 10 and the second collector pipe 20. The first and second collector pipes 10, 20 are both cylindrical, and correspondingly, surfaces (not shown) of the distribution portion 512 attached to the first and second collector pipes 10, 20 are arcuate concave surfaces. The first and second collector pipes 10, 20 can be fixed to the surface of the distribution portion 512 by welding (e.g., brazing). The block-shaped distribution portion 512 can support the first collector pipe 10 and the second collector pipe 20 on both sides thereof to improve the stability of the product.

Referring to FIG. 2B, the inlet member 52, as a whole, is tubular and includes an outer tube portion 521 and an inner tube portion 522. The outer tube portion 521 is disposed outside the first and second collector pipes 10, 20 and extends from the first end 101 of the first header 10 to the second end 103 along the length direction of the first collector pipe 10. The inner tube portion 522 has one end connected to the outer tube portion 521 and the other end extending into the second chamber 12 through the end cap 19 disposed at the second end 103.

The outlet member 56 is disposed at the first end 101, for example, being inserted into the first chamber 11 through the end cap 19 disposed at the first end 101. The inlet member 51 or 52 and the outlet member 56 are disposed at the same side of the collector pipes (at the first end 101 of the first and second collector pipes 10, 20), which facilitates the installation of the heat exchanger 100 and reduces the installation space, thereby facilitating a reduction of volume.

Referring to FIG. 3 and FIG. 4, the second collector pipe 20 of the heat exchanger 100 is provided with a partition plate groove 25 for the partition plate 40 being inserted to divide the second collector pipe 20 into two chambers that are separate from each other. The partition plate grooves 15 and 25 are staggered.

Further, the core portion includes the first core portion 301 formed by a part of the plurality of flat tubes 30, the second core portion 302 formed by another part of the plurality of flat tubes 30, and a third core portion 303 formed by the rest part of the plurality of flat tubes 30.

Referring to FIG. 3, FIG. 4 and FIG. 10, the partition plate 40 divides the first collector pipe 10 into a first chamber 11 and a second chamber 12 that are separated from each other. The partition plate 40 divides the second collector pipe 20 into a third chamber 21 and a fourth chamber 22 that are separated from each other. The flat tubes 30 of the first core portion 301 communicate the first chamber 11 and the third chamber 21. The flat tubes 30 of the second core 302 communicate the third chamber 21 and the second chamber 12. The flat tubes 30 of the third core portion 303 communicate the second chamber 12 and the fourth chamber 22.

Further, two or more partition plate grooves 15, 25 can be provided, so as to obtain more flow path arrangement of the heat exchange medium inside the heat exchanger 100.

By providing the partition plate 40 in the above technical solutions, a length of a refrigerant passage inside the heat exchanger is increased, which is beneficial to improve a heat exchange efficiency of the heat exchanger 100.

Referring to FIG. 6 and FIG. 10, still taking the first collector pipe 10 as an example, a length direction of the mounting hole 14 is not perpendicular to an axis R1 of the first collector pipe 10. An angle β is formed between the length direction of the mounting hole 14 and the axis R1 of the first collector pipe 10. The plane S1 defined by the length direction L3 and the width direction W3 of the main body section 311 is generally perpendicular to the axis R1 of the collector pipe 10. In this way, a sum of the angle β and the angle α is equal to 90 degrees. The inventors have found that the optimal range of the angle β is: 50°<β≤75°. The structure in which the plane S1 is perpendicular to the collector pipe 10 facilitates a circulation of air among the flat tubes, thereby improving the heat exchange efficiency of the heat exchanger. By such an inclined arrangement of the mounting hole 14, the flat tubes 30 are obliquely inserted into the collector pipes (including the first collector pipe 10 and the second collector pipe 20), so that a diameter of the collector pipe is unnecessary to be larger than a width of the flat tube, thereby reducing the diameter of the collector pipe and increasing the pressure resistance of the flat tubes. At the same time, it is also advantageous to reduce the volume and weight of the collector pipe.

Referring to FIG. 6 and FIG. 9, the length direction of the partition plate groove 15 is also not perpendicular to the axis R1 of the collector pipe 10. An angle is formed between the length direction of the partition plate groove 15 and the axis R1 of the collector pipe 10. In an alternative embodiment, the length direction of the partition plate groove 15 is substantially parallel with the length direction of the mounting hole 14. That is to say, the angle formed between the length direction of the partition plate groove 15 and the axis R1 of the collector pipe 10 is equal to β. Such design facilitates a reduction of a distance between the flat tubes 30 on both sides of the partition plate groove 15, and thus the heat exchanger 100 has a more compact structure, which is beneficial to reduce of the volume of the heat exchanger 100.

Referring to FIGS. 6, 9 and 11A to 11D, the partition plate 40 includes a first surface 41 and a second surface 42 that are opposite to each other and have a relatively large areas, and a first side surface 43 and a second side surface 44 adjacent to the first and second surfaces. In an embodiment, the width direction W2 of the partition plate groove 15 is parallel with the axis R1 of the collector pipe 10. The first surface 41 is substantially parallel to the second surface 42, and a perpendicular line V1 of the first side surface 43 is substantially parallel with a perpendicular line V2 of the second side surface 44. Correspondingly, the perpendicular line V1 of the first side surface 43 of the partition plate is not perpendicular to a perpendicular line V3 of the first surface 41 and the second surface 42, and the perpendicular line V2 of the second side surface 44 of the partition plate is not perpendicular to the perpendicular line V3 of the first surface 41 and the second surface 42. The first side surface 43 is not perpendicular to the first surface 41 (or the second surface 42) and an angle is formed therebetween. Similarly, the second side surface 44 is inclined to the first surface 41 (or the second surface 42), and is not perpendicular to the first surface 41 (or the second surface 42). In this way, when the partition plate 40 is inserted into and connected to the partition plate groove 15, a portion of each of the first side surface 43, the second side surface 44, the first surface 41, and the second surface 42, is attached to each groove surface. In other embodiments, the width direction W2 of the partition plate groove can be not parallel to the axis of the collector pipe, which is not specifically limited in the present application.

Referring to FIG. 3, FIG. 4, FIG. 12, and FIG. 13, the heat exchanger 100 includes a distribution tube 53. The third chamber 21 is closer to the first end 101 of the second header 10 than the fourth chamber 22, and the distribution tube 53 extends from the first end 101 through the third chamber 21 and communicates with the fourth chamber 22. The distribution tube 53 is provided with a plurality of distribution holes 531. When the refrigerant is introduced into the fourth chamber 22 through the distribution tube 53, the refrigerant is distributed into the fourth chamber 22 through the distribution holes 531, such that the distribution of the refrigerant is more uniform, thereby improving the heat exchange efficiency of the heat exchanger. In the meantime, by providing the distribution tube 53, the inlet and outlet ports of the refrigerant in the heat exchanger 100 can be arranged at the same side of the heat exchanger 100, facilitating the installation in a narrow space. Correspondingly, the partition plate 40 inserted into the partition plate groove 25 is a perforated partition plate. For example, the partition plate 40 further includes a hole 45 for the distribution tube 53 passing through. It should be noted that the hole 45 is disposed at an end of the partition plate 40 far away from the flat tube 30 to reduce the interference between the distribution tube 53 and the end of the flat tube 30, which is beneficial to improve a fluidity of the refrigerant and further improve the heat exchange efficiency of the heat exchanger 100.

Further, fins 310 are disposed between adjacent flat tubes 30. It should be noted that, the fin 310 disposed at the first tube portion 31 and the fin 310 disposed at the second tube portion 32 can be the same fin. In this way, the heat exchange area of the fin 310 can be increased, which is advantageous for improving the heat exchange efficiency of the heat exchanger 100. It is also possible that the fin 310 disposed at the first tube portion 31 and the fin disposed at the second tube portion 32 can be separated fins, which is not specifically limited in the present application and can be provided according to the specific application environment.

The heat exchanger 100 further includes a side plate 90 to fix the heat exchanger 100. It should be noted that the fins 310 can also be provided between the side plate 90 and the flat tubes 30. Certainly, the side plate 90 near to the first tube portion 31 and the side plate 90 near to the second tube portion 32 can be an integral side plate, which is conducive to enhance the stability of the heat exchanger. It is also possible that the side plate 90 near to the first tube portion 31 and the side plate 90 near to the second tube portion 32 are independent side plates.

It should be understood that a specific structure of the second tube portion 32 is similar to that of the first tube portion 31, and the specific description of the second tube portion 32 may refer to the related description of the first tube portion 31. Correspondingly, the specific structure of the second collector pipe 20 is similar to that of the first collector pipe 10. The specific description of the second collector pipe 20 may refer to the related description of the first collector pipe 10, particularly the mounting hole 24 and the partition plate groove 25.

Referring to FIGS. 1 to 4, the plane S2 defined by the length direction and the width direction of the distal section 313 is substantially parallel with the plane S3 defined by the length direction and the width direction of the distal section 323. In an embodiment, the plane S2 is parallel with the S3. This can facilitate the installation of the flat tubes 30.

When the heat exchanger 100 is in operation, the refrigerant flows into the fourth chamber 22 of the second collector pipe through the distribution tube 53, and then flows into the flat tubes 30 of the third core portion 303 from the fourth chamber 22, so as to enter the second chamber 12 of the first collector pipe 10. Thereafter, the refrigerant flows into the flat tube 30 of the second core portion 302 from the second chamber 12, and then flows into the third chamber 21 of the second collector pipe 20. Subsequently, the refrigerant flows into the flat tubes 30 of the first core portion 301, then flows into the first chamber 11 of the first collector pipe 10 and flows out through the first end 101 of the first chamber 11. At this point, one heat exchange process of the refrigerant is completed in the heat exchanger 100. It is also possible that, when the heat exchanger 100 is in operation, the heat exchange can be performed by the refrigerant in an opposite flow direction, i.e., flowing from the first end 101 of the first chamber 11, and flowing out of the heat exchanger 100 from the distribution tube 53.

Referring to FIG. 14, another heat exchanger 200 is illustrated which can be applied in various types of heat exchange systems, such as air conditioners. The heat exchanger 200 mainly exchanges heat between the refrigerant inside the heat exchanger and air flowing out of the heat exchanger, so as to provide a relatively comfortable ambient temperature.

Referring to FIGS. 7, 14-21, the heat exchanger 200 includes a core portion for heat exchange formed by stacking a plurality of flat tubes 30, a first collector pipe 10 and a second collector pipe 20 that are connected to ends of the plurality of flat tubes 30 and are arranged side by side, a connecting member 81, a third collector pipe 60 and a fourth collector pipe 70. The third collector pipe 60 and the fourth collector pipe 70 are provided with mounting holes 64, 74, into which the distal sections 33 are to be inserted. It should be noted that the mounting holes 64, 74, and 14, 24 in the heat exchanger 200 are provided in a similar way as the mounting holes 14 and 24 in the heat exchanger 100 shown in FIG. 1 to FIG. 13 described above, which will not be repeated hereafter.

The flat tube includes a main body section 34, a distal section, and a twisted section 37 connecting the main body section 34 with the distal section 36, 38. In an embodiment, the twisted section 37 is provided close to each of the ends of the flat tube 30. Referring to FIG. 19A to FIG. 19D, the flat tube 30 includes a main body section 34, a first distal section 36, a second distal section 38, a first twisted section 35 connecting the main body section 34 and the first distal section 36, and a second twisted section 37 connecting the main body section 34 and the second distal section 38. The main body section 34, the first distal section 36 and the second distal section 38 are all straight sections without being twisted and deformed.

The first twisted section 35 is formed by twisting. An angle α is formed between the main body section 34 and the first distal section 36 (in combination with FIG. 7 and FIG. 8). The inventors, in combination with their own experiences on production and processing technology, have found the optimal range of the twist angle α: 15°≤α<40° through mathematical modeling and model optimization calculation and analysis. Similarly, the second twisted section 37 is formed by twisting. An angle is formed between the main body section 34 and the second distal section 38, which is substantially equal to the angle α. The optimal range of the angle is the same as the above optimal range of 15°≤α<40°. The flat tube 30 is twisted in a similar way as the heat exchanger 100 shown in FIG. 1 to FIG. 13, for which reference can be made to the above related description and which will not be repeated herein.

It should be noted that, the main body section 34 is the main heat exchange area in the heat exchanger 200. Thus, the main body section 34 has a much greater length than the first twisted section 35, the first distal section 36, the second twisted section 37 and the second distal section 38.

The first collector pipe 10 is provided with mounting holes 14, and the first distal sections 36 or the second distal sections 38 of the flat tubes 30 are inserted into the mounting holes 14, respectively. The second collector pipe 20 is provided with mounting holes 24, and the first distal sections 36 or the second distal sections 38 of the flat tubes 30 are inserted into the mounting holes 24, respectively.

The heat exchanger 200 further includes at least two partition plates 40, and the first collector pipe 10 is provided with a partition plate groove 15, one of the partition plates 40 is inserted into the partition plate groove 15 to divide the first collector pipe 10 into a plurality of separated chambers. The second collector pipe 20 is provided with a partition plate groove 25, one of at least two partition plates 40 is inserted into the partition plate groove 25 to divide the second collector pipe 20 into a plurality of separated chambers.

It should be noted that the partition plate 40 can be an oblique partition plate without any hole, which has the same structure as that of the heat exchanger 100 shown in FIG. 1 to FIG. 13 as described above. The partition plate 40 also can be a non-oblique partition plate (in combination with FIG. 21). The partition plate groove 15 and the partition plate groove 25 are provided correspondingly to the partition plates 40 and match with the partition plates 40. For example, if the partition plate 40 is oblique, the partition plate groove 15 or the partition plate groove 25 can be provided with reference to the partition plate groove shown in FIG. 1 to FIG. 13 as described above. If the partition plate 40 is not oblique, the length direction L2 of the corresponding partition plate groove is substantially perpendicular to the axis R1 of the collector pipe, which can be set according to the specific application environment and is not limited in the present application.

When the first twisted section 35 and the second twisted section 37 are twisted towards the same side, the same side twist described in some embodiments of the present application emphasizes a relative position between the first distal section 36 and the second distal section 38. In a specific implementation, after the twisting, the plane S6 of the first distal section 36 is substantially parallel with the plane S4 of the second distal section 38. Alternatively, the length directions L1 of the two mounting holes that are provided on the collector pipes are substantially parallel with each other when being viewed from a direction of the mounting holes of the collector pipe 10. Specifically, the same side twist will be described in detail in combination with FIG. 19A to FIG. 19D. The flat tube 30 includes two surfaces S11 each having a relatively large area. The surface S11 includes a first section surface S111 located at the first distal section 36, a second section surface S112 located at the first twisted section 35, a third section surface S113 located at the main body section 34, a fourth section surface S114 located at the second twisted section 37, and a five section surface S115 located at the second distal section 38. Viewed from a top-to-bottom direction, it can be seen that a position of the second distal section 38 after the twisting is actually obtained by twisting the second twisted section 37 counterclockwise; and likewise, it can be seen that a position of the first distal section 36 is obtained by twisting the first twisted section 35 counterclockwise. After the twisting, the first section surface S111 and the fifth section surface S115 of the flat tube 30 face towards a same direction. Further, a normal line of the first section surface S111 is substantially parallel with a normal line of the fifth section surface S115. The same side twist can be also interpreted to mean that the first distal section 36 includes a first side 361 having a relatively small area and extending in a thickness direction of the first distal section 36, the second distal section 38 includes a second side 381 having a relatively small area and extending in a thickness direction of the second distal section 38, and the first side 361 and the second side 381 are located on a same side of the flat tube 30. The main body section 34 includes a third side 341 having a relatively small area, and the third side 341 extends along a thickness direction T6 of the main body section, and the third side 341 extends along a length direction L6 of the main body section 34 to both ends to form the first side 361 of the first distal section 36 and the second side 381 of the second distal section 38. The first side 361 and the second side 381 are located at a same side of the plane L6 defined by the length direction L6 and a width direction W6 of the main body section 34, i.e., the plane where the third section surface S113 is located.

In addition, the first twisted section 35 and the second twisted section 37 of the flat tube 30 can also be twisted towards opposite sides (in conjunction with FIG. 20). In some embodiments of the present application, being twisted towards opposite sides means that the plane S7 can be theoretically regarded as a plane obtained by reversely twisting the plane S4 by 180° when the twist angle is the same as the angle α. That is, after being twisted towards opposite sides, the first section surface S111 and the fifth section surface S115 face towards exactly opposite directions. The first side 361 and the second side 381 are located on both sides of the plane defined by the length direction L6 and the width direction W6 of the main body section 34, i.e., the plane where the third section surface S113 is located.

Based on a large number of experimental data and actual production operations, the inventors have found that, when the twist angle α satisfies 15°≤α<40°, problems such as deformation and distortion of the flat tube body during twisting can be effectively alleviated by producing the flat tube through the same side twisting, when comparing with other twist manners such as twisting towards opposite sides, thereby increasing the yield of the flat tubes.

The core portion includes a fourth core portion 304 formed by a part of the plurality of flat tubes 30, and a fifth core portion 305 formed by another part of the plurality of flat tubes 30.

The partition plate 40 divides the first collector pipe 10 into a first chamber 11 and a second chamber 12 that are separated from each other, and also divides the second collector pipe 20 into a third chamber 21 and a fourth chamber 22 that are separated from each other. Correspondingly, a part of the flat tubes 30 of the fourth core portion 304 communicates the first chamber 11 with an inner chamber of the third collector pipe 60. Another part of the flat tubes 30 of the fourth core portion 304 communicates the second chamber 12 with the inner chamber of the third collector pipe 60. A part of the flat tubes 30 of the fifth core portion 305 communicates the third chamber 21 with an inner chamber of the fourth collector pipe 70. Another part of the flat tubes 30 of the fifth core portion 301 communicates the fourth chamber 22 with the inner chamber of the fourth collector pipe 70. The connecting member 81 communicates the second chamber 12 with the fourth chamber 22.

Further, the connecting member 81 is adjacent to the second chamber 12 and the fourth chamber 22. A plurality of through-holes 815 is distributed along the length direction L4 of the connecting member 81 and communicates the second chamber 12 with the fourth chamber 22. In an embodiment, the plurality of through-holes 815 is evenly distributed. It is also possible that the plurality of through-holes 815 is unevenly distributed. It can be set according to the specific application environment, which is not limited in the present application. The first collector pipe 10 is correspondingly provided with connecting holes 18 that cooperate with the through-holes 815, respectively. The second collector pipe 20 is correspondingly provided with connecting holes 28 that cooperate with the through-holes 815, respectively. The inventors, in combination with their own experience in production and processing technology, have found that the optimal range of diameter (D) of the connecting holes 18, 28 is 2 mm≤D≤4 mm. It is preferable that the diameter D is 2.5 mm (in combination with FIG. 16D).

Further, the connecting member 81 is disposed between the first collector pipe 10 and the second collector pipe 20. Both of the first and second collector pipes 10, 20 are cylindrical shapes. Each surface 813 of the connecting member 81 attached to the first and second collector pipes 10, 20 is an arcuate concave surface (in combination with FIG. 17A to FIG. 17C) that matches with outer wall surfaces of the first and second collector pipes 10, 20. The first and second collector pipes 10, 20 can be fixed to the connecting member 81 by welding (for example, brazing). The connecting member 81 can support the first collector pipe 10 and the second collector pipe 20 on both sides thereof, thereby improving the stability of the product. In addition, in the automotive air conditioners using CO2 as refrigerant, the related heat exchangers are required to have relatively high pressure resistance. The first and second collector pipes use cylindrical tubes to increase the strength thereof. In order to establish the communication between the two collector pipes, in the present technical solution, the connecting member is used to communicate the first collector pipe with the second collector pipe, and such communication has higher stability than the communication formed by a tangency of the first and second collector pipes.

The connecting member 81 includes a first surface 811 and a second surface 812 opposite to the first surface 811. Optionally, a width W4 of the first surface 811 is greater than a width W5 of the second surface 812.

The heat exchanger further includes a connecting member 82 disposed between the third collector pipe 60 and the fourth collector pipe 70.

In an optional embodiment, the third and fourth collector pipes 60, 70 are both cylindrical shapes, and a surface 813 of the connecting member 82 attached to the third and fourth collector pipes 60, 70 is an accurate concave surface. The third and fourth collector pipes 60, 70 and the connecting member 82 can be fixed by welding (e.g., brazing) (in combination with FIG. 18A to FIG. 18C). The connecting member 82 can support the third collector pipe 60 and the fourth collector pipe 70 on both sides thereof, thereby further improving the stability of the product.

Further, the first collector pipe 10 is provided with an external port 17 communicating with the first chamber 11. An external connecting portion 16 is correspondingly disposed at the external port 17. The second collector pipe 20 is provided with an external port 27 that is in communication with the third chamber 21. An external connecting portion 26 is correspondingly disposed at the external port 27. The external port 17 and the external port 27 are staggered, which facilitates the installation of the heat exchanger 200. It is also possible that the external ports 17 and 27 are aligned with each other.

Further, fins 310 are disposed between adjacent flat tubes 30. The fin 310 disposed at a side where the first collector pipe 10 and the third collector pipe 60 are located and the fin 310 disposed at a side where the second collector pipe 20 and the fourth collector pipe 70 are located can correspond to a same fin, thereby increasing the heat exchange area and improving the heat exchange effect. It is also possible that two different fins are provided.

The heat exchanger 200 further includes a side plate 90 to fix the heat exchanger 200. It should be noted that a fin 310 can also be disposed between the side plate 90 and the flat tube 30. The side plate 90 at the first end 101 can be an integral side plate, thereby enhancing the stability of the heat exchanger. The side plate 90 at the first end 101 can also be two separate side plates. It is also possible that the side plate 90 at the second end 103 can also be an integral side plate, or two separate side plates.

When the heat exchanger 200 is in operation, the refrigerant flows into the first chamber 11 from the external connecting portion 16 of the first collector pipe 10 via the external port 17, the refrigerant further flows into a part of the flat tubes 30 of the first core portion 304 from the first chamber 11, and flows in the flat tubes 30 towards the third collector pipe 60, which is taken as a first flow path of the refrigerant. Thereafter, the refrigerant flows into the third collector pipe 60, flows from the first end 101 of the third collector pipe 60 to the second end 103, the refrigerant further flows into a part of the flat tubes 30 of the second core portion 305 from the third collector pipe 60, and flows in the flat tubes 30 towards the first collector pipe 10, which is taken as a second flow path of the refrigerant. Then, the refrigerant flows into the second chamber 12 of the first collector pipe 10, flows into the fourth chamber 22 of the second collector pipe 20 through the through-holes 815 of the connecting member 81, and then the refrigerant flows towards the fourth collector pipe 70 via another part of the flat tubes 30 of the second core portion, which is taken as a third flow path. Then, the refrigerant flows into the fourth collector pipe 70, flows from the second end 103 of the fourth collector pipe 70 to the first end, and then the refrigerant flows to the third chamber 21 of the second collector pipe 20 via another part of the flat tubes 30 of the first core portion 304, which is taken as a fourth flow path. Finally, the refrigerant flows out the heat exchanger from the external port 27 of the second collector pipe 20 via the external connecting portion 26. At this point, a heat exchange process of the refrigerant is completed in the heat exchanger 200. When the refrigerant flows in the heat exchanger 200, the first flow path, the second flow path, the third flow path, and the fourth flow path correspond to a highest temperature, a secondary highest temperature, a secondary lowest temperature, and a lowest temperature, respectively. A part of the air passes through the lowest temperature and the highest temperature sequentially, and the other part passes through the secondary lowest temperature and the secondary highest temperature. Compared with the four flow paths of the bending structure, in the present case, a temperature gradient between the flow paths is more suitable, and a temperature difference between the air and each flow path can be fully utilized, such that the air after the heat exchange by the heat exchanger has more uniform temperature. It should be noted that the heat exchanger 200 includes, but is not limited to, 2 flow paths or 4 flow paths, and the heat exchanger 200 can include other numbers of flow paths, such as 6 flow paths, 8 flow paths, 10 flow paths, and the like.

It is also possible that, when the heat exchanger 200 is in operation, the flow direction of the refrigerant can be opposite to the flow direction described above, i.e., the refrigerant flows in from the external port 27 and flows out from the external port 17. The present application is not limited thereto, and can be set according to specific applications.

In the above embodiments, the collector pipes are arranged side by side to form at least two layers of heat exchange structures, and multiple heat exchanges can be performed on the air flowing outside the flat tubes, so as to ensure a sufficient heat exchange of the air. By providing the partition plate, the length of the refrigerant passage inside the heat exchanger is increased, thereby improving the heat exchange efficiency of the heat exchanger. In addition, the flat tube is provided with the twisted sections close to both ends, the flat tube is twisted and obliquely inserted into the collector pipe, such that the diameter of the collector pipe is unnecessary to be larger than the width of the flat tube, thereby facilitating reducing the diameter of the collector pipe and enhancing the pressure resistance of the collector pipe with the same material and the same wall thickness.

The present application further provides a heat exchange system, and the heat exchange system includes the above heat exchanger 100 or the above heat exchanger.

The present application further provides an electric auto or an electric vehicle including the above heat exchange system.

The above merely describes the preferred embodiments of the present application, rather than forms any limitation of the present application. Although the present application has been disclosed in the preferred embodiments that are not intended to limit the present application, those skilled in the related art, by referring the technical content disclosed above, can make some variations or modifications to obtain equivalent embodiments without departing from the technical solutions of the present application. In accordance with the technical spirit of the present application, any simple variations, equivalent changes and modifications to the above embodiments without departing from the technical scope of the present application shall fall within the protection scope of the present application.

Claims

1. A heat exchanger, comprising: a collector pipe comprising a mounting hole; anda flat tube comprising a main body section that is substantially flat, a first distal section, and a second distal section, the first distal section and the second distal section being twisted towards a same side with respect to the main body section, and at least a portion of the first distal section and at least a portion of the second distal section being inserted into and connected to the mounting hole;wherein an angle located between a plane defined by a length direction and a width direction of the main body section and a plane defined by a length direction and a width direction of the first distal section or the second distal section is α, where α≠90°; andwherein the length direction of the main body section is substantially perpendicular to an axis of the collector pipe, and an angle defined between a length direction of the mounting hole and the axis of the collector pipe is β, where β≠90°.

2. The heat exchanger according to claim 1, wherein the angle α between the plane defined by the length direction and the width direction of the main body section and the plane defined by the length direction and the width direction of the distal section satisfies 15°≤α<40°, and the angle β between the length direction of the mounting hole and the axis of the collector pipe satisfies 50°<β≤75°.

3. The heat exchanger according to claim 2, wherein the planes defined by the length directions and the widths direction of the two distal sections of the flat tube are substantially parallel with each other, respectively.

4. The heat exchanger according to claim 1, wherein the plane defined by the length direction and the width direction of the main body section is substantially perpendicular to the axis of the collector pipe.

5. The heat exchanger according to claim 1, further comprising a partition plate, wherein the collector pipe is provided with a partition plate groove, and the partition plate is inserted into and connected to the partition plate groove to divide the collector pipe into at least two chambers that are separated from each other.

6. The heat exchanger according to claim 5, wherein the collector pipe comprises a first collector pipe and a second collector pipe, the first collector pipe is provided with the partition plate groove, the partition plate is inserted into and connected to the partition plate groove to divide the first collector pipe into a first chamber and a second chamber that are separated from each other; a plurality of flat tubes are stacked to form a core portion for heat exchange, the core portion comprises a first core portion formed by a part of the plurality of flat tubes, and a second core portion formed by another part of the plurality of flat tubes; andeach of flat tubes of the first core portion has one end inserted into and connected to the first collector pipe to communicate heat exchange channels of the flat tubes with the first chamber, and each of flat tubes of the second core portion have one end inserted into and connected to the first collector pipe to communicate heat exchange channels of the flat tubes with the second chamber.

7. The heat exchanger according to claim 6, wherein the core portion further comprises a third core portion formed by a third part of the plurality of flat tubes, and the partition plate divides the second collector pipe into a third chamber and a fourth chamber that are separated from each other; and each of the flat tubes of the first core portion has another end inserted into and connected to the second collector pipe to communicate heat exchange channels of the flat tubes with the third chamber, each of the flat tubes of the second core portion has another end inserted into and connected to the second collector pipe to communicate heat exchange channels of the flat tubes with the third chamber, and heat exchange channels of flat tubes of the third core portion communicate the second chamber with the fourth chamber.

8. The heat exchanger according to claim 5, wherein α length direction of the partition plate groove is not perpendicular to an axis of the first collector pipe or an axis of the second collector pipe.

9. The heat exchanger according to claim 6, wherein α length direction of the mounting hole in the first collector pipe is substantially parallel with the partition plate groove; or a length direction of a mounting hole in the second collector pipe is substantially parallel with a length direction of the partition plate groove.

10. The heat exchanger according to claim 5, wherein the partition plate comprises a first surface and a second surface opposite to each other and with relatively large areas, and a first side surface and a second side surface connected between the first surface and the second surface; and the first surface and the second surface are parallel with each other, a perpendicular line of the first side surface of the partition plate is not perpendicular to a perpendicular line of the first surface and the second surface, and a perpendicular line of the second side surface of the partition plate is not perpendicular to the perpendicular line of the first surface and the second surface.

11. The heat exchanger according to claim 6, further comprising an inlet member and an outlet member; wherein the inlet member comprises a tube portion and a distribution portion connected thereto, the tube portion extends from a first end of the first collector pipe to the second chamber, the distribution portion is adjacent to the second chamber, the distribution portion is internally provided with a flow path extending along a length direction of the first collector pipe and a plurality of distribution holes arranged along a length direction of the flow path, the plurality of distribution holes communicate the flow path with the second chamber, and the tube portion is in communication with the flow path; andthe outlet member is disposed at the first end of the first collector pipe and in communication with the first chamber of the first collector pipe.

12. The heat exchanger according to claim 7, wherein the heat exchanger further comprises a distribution tube, each of the first collector pipe and the second collector pipe has a first end and a second end that are opposite to each other along a length direction, the third chamber is closer to the first end of the second collector pipe than the fourth chamber, and the distribution tube extends from the first end of the second collector pipe through the third chamber to communicate with the fourth chamber; and the partition plate inserted into the partition plate groove of the second collector pipe is a perforated partition plate.

13. The heat exchanger according to claim 1, wherein the heat exchanger further comprises a connecting member, and a third collector pipe and a fourth collector pipe arranged side by side, an axis of the third collector pipe is substantially parallel with an axis of the fourth collector pipe, and the third collector pipe and the fourth collector pipe are spaced apart from the first collector pipe and the second collector pipe by a predetermined distance; and the connecting member is disposed in a gap between the first collector pipe and the second collector pipe arranged side by side or between the third collector pipe and the fourth collector pipe arranged side by side, and the two collector pipes arranged side by side are in communication with each other through the connecting member.

14. The heat exchanger according to claim 6, wherein each of the third collector pipe and the fourth collector pipe has a plurality of mounting holes to be inserted by the distal sections, respectively; the core portion further comprises a fourth core portion formed by a part of the plurality of flat tubes, and a fifth core portion formed by another part of the plurality of flat tubes;the partition plate divides the first collector pipe into a first chamber and a second chamber separated from each other, the partition plate divides the second collector pipe into a third chamber and a fourth chamber separated from each other;a part of flat tubes of the fourth core portion communicates the first chamber with an inner chamber of the third collector pipe, and another part of the flat tubes of the fourth core portion communicates the second chamber with the inner chamber of the third collector pipe;a part of flat tubes of the fifth core portion communicates the third chamber with an inner chamber of the fourth collector pipe, and another part of the flat tubes of the fifth core portion communicates the fourth chamber with the inner chamber of the fourth collector pipe; andthe connecting member communicates the second chamber with the fourth chamber.

15. The heat exchanger according to claim 6, wherein the connecting member is adjacent to the second chamber and the fourth chamber, the connecting member is provided with a plurality of through-holes arranged along a length direction of the connecting member, and the plurality of through-holes communicates the second chamber with the fourth chamber.

16. The heat exchanger according to claim 6, wherein the connecting member is disposed between the first collector pipe and the second collector pipe, both of the first collector pipe and the second collector pipe are cylindrical shapes, and surfaces of the connecting member to be attached to the first collector pipe and the second collector pipe are arcuate concave surfaces.

17. The heat exchanger according to claim 13, further comprising a connecting member disposed between the third collector pipe and the fourth collector pipe.

18. The heat exchanger according to claim 17, wherein both of the third collector pipe and the fourth collector pipe are cylindrical shapes, and surfaces of the connecting member to be attached to the third collector pipe and the fourth collector pipe are arcuate concave surfaces.

19. A heat exchanger, comprising: a collector pipe defining a mounting hole and a partition plate groove;a flat tube comprising a main body section, a first distal section, and a second distal section, at least one of the first distal section and the second distal section being twisted with respect to the main body section, and at least one of the first distal section and the second distal section being inserted into and connected to the mounting hole; anda partition plate inserted into and connected to the partition plate groove to divide the collector pipe into at least two chambers that are separated from each other;wherein the partition plate groove is not perpendicular to an axis of the collector pipe, the mounting hole is not perpendicular to an axis of the collector pipe, and the partition plate is parallel with at least one of the first distal section and the second distal section.

20. The heat exchanger according to claim 19 wherein an angle α between a plane defined by a length direction and a width direction of the main body section and a plane defined by a length direction and a width direction of the distal section satisfies 15°≤α<40°, and an angle β between a length direction of the mounting hole and an axis of the collector pipe satisfies 50°<β≤75°.