CN113587494A

CN113587494A - Heat exchanger

Info

Publication number: CN113587494A
Application number: CN202010366051.1A
Authority: CN
Inventors: 童仲尧; 杨永龙
Original assignee: Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Current assignee: Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Priority date: 2020-04-30
Filing date: 2020-04-30
Publication date: 2021-11-02
Anticipated expiration: 2040-04-30
Also published as: CN113587494B

Abstract

The invention discloses a heat exchanger, which comprises a first header, the heat exchanger comprises a first header and a plurality of heat exchange tubes, wherein each header is provided with a plurality of tube holes, the first end of each heat exchange tube penetrates through the tube hole of the first header, the second end of each heat exchange tube penetrates through the tube hole of the second header, at least one header comprises an inner tube and an outer tube, the outer tube is arranged on the outer side of the inner tube in the wall thickness direction, the outer tube is provided with an inner wall surface and an outer wall surface which are opposite in the wall thickness direction, the inner wall surface of the outer tube is attached to the outer wall surface of the inner tube, each tube hole comprises an inner tube hole formed in the tube wall of the inner tube and an outer tube hole formed in the tube wall of the outer tube, the inner tube hole penetrates through the tube wall of the inner tube, the outer tube hole penetrates through the tube wall of the outer tube, the outer tube comprises a plurality of sub-outer tube segments which are arranged along the circumferential direction of the outer tube, and a single outer tube hole is arranged on one sub-outer tube segment or two adjacent sub-outer tube segments in the circumferential direction of the outer tube. The heat exchanger has the advantages of high compressive strength, low stamping forming difficulty, high processing precision, low assembling difficulty and the like.

Description

Heat exchanger

Technical Field

The invention belongs to the technical field of heat exchange, and particularly relates to a heat exchanger.

Background

Parallel flow heat exchangers, such as multichannel heat exchangers, are common devices in heat exchange systems and generally include a heat exchange tube and two parallel headers, wherein a tube wall of each header is provided with a heat exchange tube hole, for example, by stamping, and the heat exchange tube hole is formed in the tube wall of each header, the heat exchange tube is generally a flat tube, two ends of the heat exchange tube respectively extend into the header through the heat exchange tube hole, and the heat exchange tube and the headers are welded to each other. The refrigerant in the heat exchanger usually has a certain pressure, and the pressure resistance (i.e. strength) is the main performance index of the heat exchanger, and many solutions for improving the pressure resistance, such as increasing the thickness of the collecting pipe, have been proposed in the related art, but there is a problem of difficulty in processing and manufacturing.

Disclosure of Invention

The embodiment of the invention provides a heat exchanger, the header of which is combined, so that the strength is improved, and the inner pipe and the outer pipe can be processed separately, thereby reducing the manufacturing difficulty.

A heat exchanger according to an embodiment of the present invention includes a first header, a second header, and a plurality of heat exchange tubes, each of the first header and the second header having a plurality of tube holes arranged at intervals in a longitudinal direction of the header, the heat exchange tubes having a first end portion penetrating the tube holes of the first header and a second end portion penetrating the tube holes of the second header, the heat exchange tubes including at least one passage to communicate the first header and the second header, at least one of the first header and the second header including an inner tube and an outer tube, the outer tube being provided outside in a wall thickness direction of the inner tube, the outer tube having opposite inner and outer wall surfaces in a wall thickness direction thereof, the inner tube having opposite inner and outer wall surfaces in a wall thickness direction thereof, and the inner wall surface of the outer tube being in conformity with the outer wall surface of the inner tube, the pipe holes comprise inner pipe holes formed in the pipe wall of the inner pipe and outer pipe holes formed in the pipe wall of the outer pipe, the inner pipe holes penetrate through the pipe wall of the inner pipe, the outer pipe holes penetrate through the pipe wall of the outer pipe, the outer pipe comprises a plurality of sub outer pipe sections arranged along the circumferential direction of the outer pipe, and a single outer pipe hole is arranged on one sub outer pipe section or two adjacent sub outer pipe sections in the circumferential direction of the outer pipe.

The heat exchanger provided by the embodiment of the invention has the advantages of high compressive strength, low stamping forming difficulty, high processing precision and easiness in assembly.

Optionally, the number of the sub outer tube sections is two or three, a side surface is arranged between an inner wall surface and an outer wall surface of each sub outer tube section, the side surfaces are respectively connected with the inner wall surface and the outer wall surface, and adjacent side surfaces of adjacent sub outer tube sections in the circumferential direction of the outer tube are attached or spaced.

Optionally, the outer tube includes a first sub outer tube section and a second sub outer tube section, the outer tube hole includes a first sub outer tube hole and a second sub outer tube hole, the first sub outer tube hole is located in the first sub outer tube section, and an opening is provided at the one side surface of the first sub outer tube section, the second sub outer tube hole is located in the second sub outer tube section, and an opening is provided at the one side surface of the second sub outer tube section, the side surface of the first sub outer tube section is adjacent to the side surface of the second sub outer tube section in the outer tube circumferential direction, and the opening of the first sub tube hole is opposite to the opening of the second sub tube hole in the outer tube circumferential direction.

Optionally, the outer tube aperture is located on one of the sub-outer tube sections, the outer tube aperture being substantially rectangular in outline and closed at outline edges on an outer wall surface of the one sub-outer tube section.

Optionally, the wall thickness of the one sub-outer tube section having the outer tube bore is smaller than the wall thickness of the remaining sub-outer tube sections.

Optionally, the first outer sub-pipe section is provided with a positioning groove, an opening of the positioning groove is formed in one side face of the first outer sub-pipe section, one circumferential side of the second outer sub-pipe section is provided with a positioning protrusion, and the positioning groove of the first outer sub-pipe section is matched with the positioning protrusion of the second outer sub-pipe section.

Optionally, the wall thickness of the first and/or second sub outer tube sections varies in the circumferential direction of the outer tube, the first sub outer tube section having a wall thickness of one side of the first sub outer tube bore that is smaller than the wall thickness of the other side in the circumferential direction of the first sub outer tube section and/or the second sub outer tube section having a wall thickness of one side of the second sub outer tube bore that is smaller than the wall thickness of the other side in the circumferential direction of the second sub outer tube section.

Optionally, the inner tube and the outer tube are both round tubes, and the outer peripheral profile of the tube hole is substantially rectangular.

Optionally, the outer tube aperture is provided with a skirt remote from the outer periphery of the inner tube.

Optionally, the ratio of the wall thickness of the inner tube to the wall thickness of the outer sub-tube sections of the outer tube is in the range of 0.2-5.

Optionally, the inner pipe has an inner pipe weld extending along its length, the boundaries between the inner pipe weld and adjacent sub-outer pipe sections being staggered circumferentially of the inner pipe.

Drawings

Fig. 1 is a partial perspective view of a heat exchanger according to a first embodiment of the present invention.

Fig. 2 is a schematic plan view of fig. 1.

Fig. 3 is a partial perspective view of a heat exchanger according to a second embodiment of the present invention.

Fig. 4 is a schematic plan view of fig. 3.

Fig. 5 is a partial perspective view of a heat exchanger according to a third embodiment of the present invention.

Fig. 6 is a schematic plan view of fig. 5.

Fig. 7 is a partial perspective view of a heat exchanger according to a fourth embodiment of the present invention.

Fig. 8 is a partial perspective view of a heat exchanger according to a fifth embodiment of the present invention.

Fig. 9 is a partial perspective view of a heat exchanger according to a sixth embodiment of the present invention.

Fig. 10 is a partial perspective view of a heat exchanger according to a seventh embodiment of the present invention.

Fig. 11 is a schematic plan view of fig. 10.

Fig. 12 is a partial perspective view of a heat exchanger according to an eighth embodiment of the present invention.

Fig. 13 is a schematic plan view of fig. 12.

Fig. 14 is a partial perspective view of a heat exchanger according to a ninth embodiment of the present invention.

Fig. 15 is a schematic plan view of fig. 14.

Fig. 16 is a partial perspective view of a heat exchanger according to a tenth embodiment of the present invention.

Fig. 17 is a partial perspective view of a heat exchanger according to an eleventh embodiment of the present invention.

Fig. 18 is a partial perspective view of a heat exchanger according to a twelfth embodiment of the present invention.

Fig. 19 is a partial perspective view of a heat exchanger according to a thirteenth embodiment of the present invention.

Fig. 20 is a partially exploded view of the outer tube of the header of the heat exchanger shown in fig. 19.

Fig. 21 is a partial perspective view of a heat exchanger according to a fourteenth embodiment of the invention.

Fig. 22 is a schematic plan view of fig. 21.

Fig. 23 is a partially exploded schematic view of a heat exchanger according to a fifteenth embodiment of the present invention.

Fig. 24 is an assembled schematic view of the heat exchanger according to fig. 23.

Fig. 25 is a partial perspective view of a heat exchanger according to a sixteenth embodiment of the present invention.

Fig. 26 is a partial perspective view of a heat exchanger according to a seventeenth embodiment of the invention.

Fig. 27 is a schematic plan view of fig. 26.

Fig. 28 is a partial perspective view of a heat exchanger according to an eighteenth embodiment of the present invention.

Fig. 29 is a partial perspective view of a heat exchanger according to a nineteenth embodiment of the invention.

Fig. 30 is a schematic plan view of fig. 29.

Fig. 31 is a partial perspective view of a heat exchanger according to a twentieth embodiment of the invention.

Fig. 32 is a schematic plan view of fig. 31.

Fig. 33 is a partial perspective view of a heat exchanger according to a twenty-first embodiment of the invention.

Fig. 34 is a schematic plan view of fig. 33.

FIG. 35 is a schematic view of a header of a heat exchanger according to an embodiment of the present invention.

FIG. 36 is a schematic view of a heat exchanger according to an embodiment of the present invention.

Detailed Description

Reference will now be made in detail to embodiments of the present application, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present application and should not be construed as limiting the present application.

The strength of the header of the heat exchanger affects the pressure resistance of the heat exchanger, and after the header and the heat exchange tubes are assembled to form the heat exchanger, different parts of the heat exchanger bear different refrigerant pressures, so that the pressure resistance requirements are different. In order to improve the strength of the header, it is common practice in the related art to increase the wall thickness of the header. However, the inventor finds and realizes that although the strength of the header can be increased by increasing the wall thickness of the header, so that the pressure resistance is improved, the wall thickness of the header is increased because the heat exchange pipe holes in the pipe wall of the header are generally formed by stamping, the processing difficulty of the heat exchange pipe holes is increased, the heat exchange pipe holes are difficult to be stamped and formed at one time, the processing precision of the heat exchange pipe holes is also influenced, and the matching difficulty of the heat exchange pipes and the heat exchange pipe holes is increased. The difficulty of installing or welding other fittings to the header is also increased after the wall thickness of the header is increased.

The present invention is directed to solving, at least to some extent, one of the technical problems in the related art.

A heat exchanger 1 according to an embodiment of the present invention is described below with reference to the drawings.

As shown in fig. 1 to 36, a heat exchanger 1 according to an embodiment of the present invention includes a header 10 and a plurality of heat exchange tubes 20, and as shown in fig. 36, the header 10 includes a first header 10a, a second header 10 b. Each of the first header 10a and the second header 10b has a plurality of tube holes arranged at intervals in a length direction of the header. In other words, the first header 10a has a plurality of tube holes arranged at intervals in the length direction of the first header 10a, and the second header 10b has a plurality of tube holes arranged at intervals in the length direction of the second header 10 b.

At least one of the first header 10a and the second header 10b includes an inner tube 110 and an outer tube 120. The outer tube 120 is provided outside the inner tube 110 in the wall thickness direction, the outer tube 120 has an inner wall surface 1224 and an outer wall surface 1225 facing each other in the wall thickness direction, the inner tube 110 has an inner wall surface 112 and an outer wall surface 113 facing each other in the wall thickness direction, and the inner wall surface 1224 of the outer tube 120 is in contact with the outer wall surface 113 of the inner tube 110.

The tube holes include an inner tube hole 111 formed on a tube wall of the inner tube 110 and an outer tube hole 121 formed on a tube wall of the outer tube 120. The inner pipe holes 111 penetrate the wall of the inner pipe 110, and the outer pipe holes 121 penetrate the wall of the outer pipe 120. The outer tube 120 includes a plurality of sub outer tube sections 122 arranged along a circumferential direction of the outer tube 120, and a single outer tube hole 121 is provided on one sub outer tube section 122 or on two adjacent sub outer tube sections 122.

The heat exchange tube 20 has a first end 210 and a second end 220, i.e., the heat exchange tube 20 has a first end 210 and a second end 220 in the length direction thereof. The first end portion 210 of the heat exchange tube 20 extends through the tube hole of the first header 10a, and the second end portion 220 of the heat exchange tube 20 extends through the tube hole of the second header 10 b. The heat exchange tube 20 includes at least one channel for communicating the first header 10a and the second header 10 b.

According to the heat exchanger 1 of the embodiment of the invention, by making at least one of the first header 10a and the second header 10b include the inner tube 110 and the outer tube 120, the wall thickness (thickness) of each of the inner tube 110 and the outer tube 120 is reduced relative to the wall thickness of the header. It is thereby possible to make the wall thickness of the header larger in the case where the wall thickness of the inner pipe 110 and the wall thickness of the outer pipe 120 are smaller, so that the pressure resistance (pressure resistance) of the header can be effectively improved, that is, the pressure resistance of the header can be effectively improved.

Moreover, since the wall thickness of the inner tube 110 and the wall thickness of the outer tube 120 are small, the difficulty of press forming the inner tube hole 111 and the outer tube hole 121, that is, the difficulty of press forming the tube holes, can be greatly reduced. The machining accuracy of the pipe holes (the inner pipe hole 111 and the outer pipe hole 121) can be further ensured so as to effectively reduce the difficulty of fitting the heat exchange pipe 20 with the pipe holes (the inner pipe hole 111 and the outer pipe hole 121). In addition, since the outer tube 120 is formed of a plurality of sub-outer tube sections 122, the heat exchange tube 20 may be first inserted into the inner tube hole 111 of the inner tube 110 and then the plurality of sub-outer tube sections 122 are assembled, thereby reducing the difficulty of assembly.

According to the heat exchanger 1 of the embodiment of the invention, the pressure resistance strength of the header can be effectively improved under the condition of greatly reducing the stamping forming difficulty of the pipe holes and ensuring the processing precision of the pipe holes, and further, the pressure resistance strength of the heat exchanger can be improved.

Therefore, the heat exchanger 1 according to the embodiment of the invention has the advantages of high compressive strength, low stamping forming difficulty, high processing precision, easy assembly and the like. Particularly in a system using a high-temperature high-pressure refrigerant, it is advantageous to reduce the concentration of thermal stress on the header while improving the pressure resistance. Further, when pitting occurs on the wall of either of the inner and outer tubes, the interface between the inner and outer tubes can block or retard the rapid progression of such corrosion in the direction of the wall thickness, improving the corrosion resistance of the header.

In the following description, for convenience of description, the first header 10a including the inner pipe 110 and the outer pipe 120 is described as an example. However, it is to be understood that the present invention is not limited thereto, and the second header 10b may include the inner tube 110 and the outer tube 120, and both the first header 10a and the second header 10b may include the inner tube 110 and the outer tube 120.

As shown in fig. 1-30, in some embodiments of the present invention, a heat exchanger 1 may include a first header 10a, a second header 10b, and a plurality of heat exchange tubes 20. The first header 10a includes an inner pipe 110 and an outer pipe 120. The outer tube 120 is provided outside the inner tube 110 in the thickness direction, and the inner wall surface 1224 of the outer tube 120 is in contact with the outer wall surface 113 of the inner tube 110.

The material of the inner tube 110 may be different from the material of the outer tube 120, i.e., the inner tube 110 and the outer tube 120 may be made of different materials. Alternatively, the strength of the inner tube 110 may be greater than the strength of the outer tube 120, i.e., the strength of the outer tube 120 may be less than the strength of the inner tube 110. Since the refrigerant flows in the inner pipe 110, the inner pipe 110 is a main pressure receiving member. By making the strength of the outer tube 120 smaller than that of the inner tube 110, the manufacturing cost of the outer tube 120 and, therefore, the heat exchanger 1 can be reduced while ensuring the pressure resistant strength of the first header 10 a.

Alternatively, the corrosion resistance of the outer tube 120 is higher than the corrosion resistance of the inner tube 110, i.e., the corrosion resistance of the inner tube 110 is lower than the corrosion resistance of the outer tube 120. Since the inner tube 110 is not substantially exposed to the external environment, the inner tube 110 is corroded to a much lesser degree than the outer tube 120. By making the corrosion resistance of the inner pipe 110 lower than that of the outer pipe 120, the manufacturing cost of the inner pipe 110 and, therefore, the heat exchanger 1 can be reduced while the corrosion resistance of the first header 10a is ensured.

The first header 10a has a plurality of tube holes arranged at intervals in a length direction thereof, the tube holes including inner tube holes 111 formed on a tube wall of the inner tube 110 and outer tube holes 121 formed on a tube wall of the outer tube 120. The outer tube 120 includes a plurality of sub outer tube sections 122 arranged along a circumferential direction of the outer tube 120, and the outer tube hole 121 is formed on at least one of the sub outer tube sections 122.

Wherein the longitudinal direction of the outer tube 120, the longitudinal direction of the inner tube 110 and the longitudinal direction of the header are coincident, the longitudinal direction of the header is shown by an arrow a in fig. 16, and the longitudinal direction of the heat exchange tube 20 is shown by an arrow B in fig. 16.

As shown in fig. 1-28, and particularly in fig. 23, the inner tube 110 and the outer tube 120 are each a circular tube, and the tube holes include a first groove wall surface, a second groove wall surface, a third groove wall surface, and a fourth groove wall surface. The first and second groove wall surfaces are disposed opposite to each other in the longitudinal direction of the inner pipe 110 (the longitudinal direction of the outer pipe 120), and the third and fourth groove wall surfaces are disposed opposite to each other in the circumferential direction of the inner pipe 110 (the circumferential direction of the outer pipe 120). Wherein a distance between the first groove wall surface and the second groove wall surface is smaller than a distance between the third groove wall surface and the fourth groove wall surface. In other words, the outer peripheral profile of the tube bore is generally rectangular.

Accordingly, each of the inner pipe hole 111 and the outer pipe hole 121 includes a fifth groove wall surface, a sixth groove wall surface, a seventh groove wall surface, and an eighth groove wall surface. The fifth and sixth groove wall surfaces are disposed opposite to each other in the longitudinal direction of the inner pipe 110 (the longitudinal direction of the outer pipe 120), and the seventh and eighth groove wall surfaces are disposed opposite to each other in the circumferential direction of the inner pipe 110 (the circumferential direction of the outer pipe 120). Wherein a distance between the fifth groove wall surface and the sixth groove wall surface is smaller than a distance between the seventh groove wall surface and the eighth groove wall surface.

Optionally, each of the inner tube apertures 111 and the outer tube apertures 121 is an oblong slot. Correspondingly, the pipe hole is a long circular hole groove.

The first end portion 210 of the heat exchange tube 20 extends through the tube hole of the first header 10a, and the second end portion 220 of the heat exchange tube 20 extends through the tube hole of the second header 10 b. That is, the first end portion 210 of the heat exchange tube 20 penetrates the outer tube hole 121 and the inner tube hole 111 of the first header 10a, and the second end portion 220 of the heat exchange tube 20 penetrates the outer tube hole 121 and the inner tube hole 111 of the second header 10b, so that the heat exchange tube 20 communicates the first header 10a and the second header 10 b.

For a more clear and accurate understanding, the assembly process of the heat exchanger 1 will be described below by taking as an example that both the first header 10a and the second header 10b include the inner tube 110 and the outer tube 120.

In assembling the heat exchanger 1, the first end portion 210 of the heat exchange tube 20 may be first inserted through the inner tube hole 111 of the first header 10a, and the second end portion 220 of the heat exchange tube 20 may be inserted through the inner tube hole 111 of the second header 10b, so that the heat exchange tube 20 is assembled with the inner tube 110 of the first header 10a and the inner tube 110 of the second header 10 b. Then, the sub-outer tube sections 122 having the outer tube holes 121 are fitted over the heat exchange tube 20 such that the ends of the heat exchange tube 20 penetrate the outer tube holes 121, and the plurality of sub-outer tube sections 122 are assembled together such that the outer tube 120 is fitted over the inner tube 110.

The inner tube 110 and the outer tube 120 and the two adjacent sub-outer tube segments 122 may be welded together, for example, in a furnace. Further, these components may be connected together in other ways known in the art.

The outer sub-tube segments 122 may be two (as shown in fig. 1-26) or three (as shown in fig. 27 and 28). This can reduce the difficulty of assembling the inner tube 110 and the outer tube 120 together, as well as the difficulty of assembling a plurality of sub-outer tube segments 122 together to form the outer tube 120.

The inner wall surface 1224 and the outer wall surface 1225 of the outer sub-tube section 122 have a side surface 1221 therebetween, the side surface 1221 is connected to the inner wall surface 1224 and the outer wall surface 1225, and the adjacent side surfaces 1221 of the outer sub-tube sections 122 adjacent to each other in the circumferential direction of the outer tube 120 are fitted or spaced apart. That is, each of the sub outer tube sections 122 has two sides 1221 in the circumferential direction of the outer tube 120, and the sides 1221 extend in the length direction of the outer tube 120.

Alternatively, the side surfaces 1221 of the plurality of sub-outer tube sections 122 are sequentially joined along the circumference of the outer tube 120. For example, the side surfaces 1221 of the plurality of sub-outer tube sections 122 are welded in sequence along the circumferential direction of the outer tube 120, that is, each pair of two side surfaces 1221 adjacent to each other in the circumferential direction of the outer tube 120 are welded together.

As shown in fig. 1, 2, 25 and 26, the outer tube bore 121 is located on one of the sub-outer tube sections 122. For example, the outer tube 120 may include two sub-outer tube sections 122, the two sub-outer tube sections 122 being opposite in the extending direction of the heat exchange tube 20, and the outer tube hole 121 being formed in one sub-outer tube section 122. The outer tube bore 121 is substantially rectangular in profile and closed at the profile edges on the outer wall surface of one of the sub-outer tube sections 122.

As shown in fig. 3-24, the outer tube 120 includes a first sub outer tube section 1226 and a second sub outer tube section 1227, and the outer tube holes 121 include a first sub outer tube hole 1211 and a second sub outer tube hole 1212. The first sub outer tube hole 1211 is located on the first sub outer tube section 1226, and the first sub outer tube hole 1211 is provided with an opening on one side surface 1221 of the first sub outer tube section 1226, the second sub outer tube hole 1212 is located on the second sub outer tube section 1227, and the second sub outer tube hole 1212 is provided with an opening on one side surface 1221 of the second sub outer tube section 1227.

The side surface 1221 of the first sub outer tube section 1226 is adjacent to the side surface 1221 of the second sub outer tube section 1227 in the circumferential direction of the outer tube 120, and the opening of the first sub outer tube hole 1211 is opposite to the opening of the second sub outer tube hole 1212 in the circumferential direction of the outer tube 120 so as to form the outer tube hole 121. In other words, the first sub outer tube hole 1211 is formed on one sub outer tube section 122 of two sub outer tube sections 122 adjacent in the circumferential direction of the outer tube 120, and the second sub outer tube hole 1212 is formed on the other sub outer tube section 122.

For example, the outer tube 120 may include two sub-outer tube segments 122, and the opposing directions of the two sub-outer tube segments 122 are perpendicular (orthogonal) to the extending direction of the heat exchange tube 20, i.e., the two sub-outer tube segments 122 are opposed in a direction perpendicular to the extending direction of the heat exchange tube 20. One of the sub-outer tube sections 122 forms a first sub-outer tube aperture 1211, and the other sub-outer tube section 122 forms a second sub-outer tube aperture 1212.

As shown in fig. 19 and 20, of the two adjacent side surfaces 1221 of two adjacent sub-outer tube sections 122 in the circumferential direction of the outer tube 120, the side surface 1221 of one sub-outer tube section 122 is provided with the positioning groove 123, and the side surface 1221 of the other sub-outer tube section 122 is provided with the positioning projection 124 that is engaged with the positioning groove 123, that is, the positioning projection 124 is engaged in the positioning groove 123. This can reduce the difficulty in assembling the plurality of sub outer pipe sections 122 and improve the accuracy of assembling the plurality of sub outer pipe sections 122.

Specifically, the first sub outer tube section 1226 is provided with the positioning groove 123, an opening of the positioning groove 123 is provided on one side 1221 of the first sub outer tube section 1226, one side of the second sub outer tube section 1227 in the circumferential direction is provided with the positioning protrusion 124, and the positioning groove 123 of the first sub outer tube section 1226 is matched with the positioning protrusion 124 of the second sub outer tube section 1227.

As shown in fig. 10 and 11, of the two adjacent side surfaces 1221 of at least two adjacent sub-outer tube sections 122 in the circumferential direction of the outer tube 120, the side surface 1221 of one sub-outer tube section 122 is provided with a recess, and the side surface 1221 of the other sub-outer tube section 122 is provided with a projection 126 that fits in the recess.

As shown in fig. 12 and 13, of the two adjacent side surfaces 1221 of at least two adjacent sub-outer tube sections 122 in the circumferential direction of the outer tube 120, the side surface 1221 of one sub-outer tube section 122 is provided with a lap portion 128 that laps over the outer wall of the other sub-outer tube section 122. As a result, the thickness of the joint of the at least two adjacent sub-outer tube sections 122 can be increased, and the compressive strength of the joint of the at least two adjacent sub-outer tube sections 122 can be increased.

Optionally, the lap joint 128 is welded to the outer wall of the other sub-outer tube section 122. Optionally, the inner tube 110 has an inner tube weld extending along its length, the overlap 128 opposing the inner tube weld in a radial direction of the outer tube 120 (radial direction of the inner tube 110), such that a portion of the outer tube 120 opposing the inner tube weld in the radial direction of the outer tube 120 has a wall thickness greater than a wall thickness of the remainder of the outer tube 120. Thereby, the pressure resistance strength of the inner pipe 110 at the inner pipe weld can be improved, and the pressure resistance of the heat exchanger 1 can be improved.

As shown in fig. 5 and 6, the wall thickness of the outer tube 120 varies along the circumferential direction of the outer tube 120. For example, the wall thickness of the outer tube 120 gradually increases from the outer tube hole 121 toward a direction away from the outer tube hole 121 in the circumferential direction of the outer tube 120. That is, the wall thickness of the outer tube 120 increases and then decreases from the outer tube hole 121 in the circumferential direction (clockwise and counterclockwise) of the outer tube 120.

Alternatively, the inner pipe 110 has an inner pipe weld extending along its length, and the outer pipe hole 121 is opposed to the inner pipe weld in the radial direction of the outer pipe 120 (the radial direction of the inner pipe 110). The wall thickness of the outer tube 120 gradually increases from the outer tube hole 121 toward a direction away from the outer tube hole 121 in the circumferential direction of the outer tube 120. In other words, the wall thickness of the portion of the outer tube 120 that is radially opposite the inner tube weld is greater than the wall thickness of the remaining portion of the outer tube 120. Thereby, the pressure resistance strength of the inner pipe 110 at the inner pipe weld can be improved, and the pressure resistance of the heat exchanger 1 can be improved.

Optionally, the wall thickness of the first sub outer tube section 1226 and/or the second sub outer tube section 1227 varies along the circumference of the outer tube 120. The first sub outer tube section 1226 has a wall thickness of one side of the first sub outer tube hole 1211 smaller than a wall thickness of the other side in the circumferential direction of the first sub outer tube section 1226. The second sub outer tube section 1227 has a wall thickness of one side of the second sub outer tube hole 1212 smaller than that of the other side of the second sub outer tube section 1227 in the circumferential direction.

Therefore, the difficulty of punch forming of the first sub-outer tube hole 1211 and the second sub-outer tube hole 1212 can be further reduced, that is, the difficulty of punch forming of the outer tube hole 121 can be further reduced, so that the machining precision of the outer tube hole 121 can be further improved, and the difficulty of matching the heat exchange tube 20 and the outer tube hole 121 can be further effectively reduced.

The wall thickness of the first sub-outer tube section 1226 (the second sub-outer tube section 1227, the outer tube 120, and the inner tube 110) is: the dimension of the first sub outer tube section 1226 (the second sub outer tube section 1227, the outer tube 120, the inner tube 110) in the radial direction of the inner tube 110.

As shown in fig. 29 and 30, the first sub-outer tube section 1226 has a smaller wall thickness than the second sub-outer tube section 1227. Specifically, the outer tube bore 121 is located on the first sub-outer tube section 1226. Therefore, the difficulty of punch forming of the outer tube hole 121 can be further reduced, so that the machining precision of the outer tube hole 121 can be further improved, and the difficulty of matching the heat exchange tube 20 and the outer tube hole 121 can be further effectively reduced.

The ratio of the wall thickness of the inner tube 110 to the wall thickness of the outer tube section 122 of the outer tube 120 is in the range of 0.2 to 5, i.e. the ratio of the wall thickness of the inner tube 110 to the wall thickness of the outer tube 120 is in the range of 0.2 to 5.

As shown in fig. 21 and 22, the inner pipe 110 has an inner pipe weld (not shown) extending along its length, the boundary between the inner pipe weld and the adjacent sub-outer pipe section 122 being offset in the circumferential direction of the inner pipe 110. For example, the junction between adjacent sub-outer tube sections 122 is offset from the inner tube weld in the circumferential direction of the inner tube 110. In other words, the junction between adjacent sub-outer tube sections 122 is not opposite the inner tube weld in the radial direction of the inner tube 110 (the radial direction of the outer tube 120). Thereby, the pressure resistance strength of the inner pipe 110 at the inner pipe weld can be improved, and the pressure resistance of the heat exchanger 1 can be improved.

The inventor finds that in use, moisture in the air is easy to enter a welding seam between the heat exchange tube and the header, and the moisture in the welding seam is easy to freeze and expand when the heat exchanger is in a low-temperature working condition, so that the joint of the header and the heat exchange tube is leaked.

As shown in fig. 1, 2 and 18, the outer tube bore 121 is provided with a skirt 127 distal from the outer periphery of the inner tube 110. In other words, the skirt 127 may extend in the radial direction of the outer tube 120 (the radial direction of the inner tube 110) from the outer tube 120 in a direction away from the inner tube 110. For example, the skirt 127 may extend in the extending direction of the heat exchange tube 20 from the outer tube 120 in a direction away from the inner tube 110.

By providing the skirt 127 at the outer peripheral edge of the outer tube hole 121 remote from the inner tube 110, moisture in the air can be prevented from entering the weld between the heat exchange tube 20 and the outer tube 120 and the weld between the heat exchange tube 20 and the inner tube 110 by the skirt 127. Therefore, the freezing and expansion of the moisture in the welding seam can be avoided, and further, the leakage of the joint of the heat exchange tube 20 and the outer tube 120 and the joint of the heat exchange tube 20 and the inner tube 110 can be avoided.

Alternatively, the skirt 127 may be attached to the heat exchange tube 20, for example, the skirt 127 may be welded to the heat exchange tube 20. Thereby, moisture in the air can be further prevented from entering the welding seam between the heat exchange tube 20 and the outer tube 120 and the welding seam between the heat exchange tube 20 and the inner tube 110, and thus, the leakage of the connection between the heat exchange tube 20 and the outer tube 120 and the connection between the heat exchange tube 20 and the inner tube 110 can be further prevented.

As shown in fig. 1, 2 and 18, the skirt 127 may be annular, and the skirt 127 may be sleeved on the heat exchange tube 20. Thereby, moisture in the air can be further prevented from entering the welding seam between the heat exchange tube 20 and the outer tube 120 and the welding seam between the heat exchange tube 20 and the inner tube 110, and thus, the leakage of the connection between the heat exchange tube 20 and the outer tube 120 and the connection between the heat exchange tube 20 and the inner tube 110 can be further prevented. Alternatively, the skirt 127 may be integrally press-formed on at least one of the sub-outer tube sections 122 of the outer tube 120, i.e., the skirt 127 is obtained when the outer tube bore 121 is press-formed.

As shown in fig. 16, the heat exchanger 1 may further include a band 30, and the band 30 is fastened to the outer peripheral wall of the outer tube 120 of the at least one header. In other words, the clasping ring 30 may be sleeved over the outer tube 120 of at least one header. Thereby, the inner tube 110 and the outer tube 120 can be more firmly fitted together, so that the relative displacement of the inner tube 110 and the outer tube 120 before the welding of the inner tube 110 and the outer tube 120 can be avoided, and the assembling accuracy of the heat exchanger 1 can be improved.

As shown in fig. 7 and 8, the side 1221 of at least one of the outer sub-sections 122 of the outer tube 120 is provided with a mounting plate 1291. The mounting plate 1291 can be connected to a support (not shown) of the heat exchanger 1 by means of hoops, straps or springs or the like. Optionally, the mounting plate 1291 has mounting holes 1292. Thereby more conveniently and more securely coupling the mounting plate 1291 and the bracket together.

Alternatively, as shown in fig. 8, two adjacent side surfaces 1221 of two adjacent sub-outer tube sections 122 in the circumferential direction of the outer tube 120 are provided with mounting plates 1291, the two mounting plates 1291 are attached to each other, and the mounting holes 1292 of the two mounting plates 1291 are opposite to each other. Whereby the header and the bracket can be more conveniently and more stably coupled together.

As shown in fig. 9, a mounting boss 1293 is provided on the outer wall of at least one of the outer sub-sections 122 of the outer tube 120, and the mounting boss 1293 has a receptacle 1294 for mounting an adapter (not shown). Alternatively, for the outer sub-pipe section 122 provided with the mounting bosses 1293, the two side surfaces 1221 of the outer sub-pipe section 122 are symmetrical with respect to the mounting bosses 1293, i.e., the mounting bosses 1293 are located at the middle of the outer wall of the outer sub-pipe section 122 in the circumferential direction of the outer pipe 120.

As shown in fig. 17, the end 1222 of at least one of the sub-outer tube segments 122 of the outer tube 120 is provided with a positioning projection 1223. The end cover 40 of the heat exchanger 1 is provided with a positioning groove, and the positioning projection 1223 is fitted in the positioning groove of the end cover 40. The end cap 40 can thereby be more accurately and more securely mounted to the header to improve the strength of the connection of the header and the end cap 40.

As shown in fig. 18, a portion of the outer tube 120 between the adjacent two heat exchange tubes 20 in the length direction of the outer tube 120 is provided with a waterproof elastic layer (not shown in the figure). The heat exchanger 1 may further include a compression ring 50, the compression ring 50 is sleeved on the portion of the outer tube 120, and the waterproof elastic layer is located between the outer tube 120 and the compression ring 50, so that the waterproof elastic layer is elastically deformed under the compression action of the compression ring 50. By providing the waterproof elastic layer and the clamp ring 50 for clamping the waterproof elastic layer, not only can moisture be prevented from entering the weld between the heat exchange tube 20 and the header, but also the connection strength of the heat exchange tube 20 and the header can be increased.

A header 10 according to an embodiment of the present invention is described below with reference to the drawings.

As shown in fig. 1 to 30, the header 10 according to the embodiment of the present invention has a plurality of tube holes arranged at intervals along the length direction of the header 10. The header 10 includes an inner pipe 110 and an outer pipe 120, the outer pipe 120 being provided outside in the wall thickness direction of the inner pipe 110. The outer tube 120 has an inner wall surface 1224 and an outer wall surface 1225 facing each other in the wall thickness direction, the inner tube 110 has an inner wall surface 112 and an outer wall surface 113 facing each other in the wall thickness direction, and the inner wall surface 1224 of the outer tube 120 is in contact with the outer wall surface 113 of the inner tube 110.

The tube holes include an inner tube hole 111 formed on a tube wall of the inner tube 110 and an outer tube hole 121 formed on a tube wall of the outer tube 120. The inner pipe holes 111 penetrate the wall of the inner pipe 110, and the outer pipe holes 121 penetrate the wall of the outer pipe 120. The outer tube 120 is divided into a plurality of outer tube portions 122a in the circumferential direction of the outer tube 120, and the outer tube portion 122a having the outer tube holes 121 has a wall thickness smaller than that of the remaining outer tube portions 122 a.

The header 10 according to the embodiment of the present invention is formed by including the inner tube 110 and the outer tube 120 such that the wall thickness (thickness) of each of the inner tube 110 and the outer tube 120 is reduced relative to the wall thickness of the header 10, i.e., the wall thickness of the header 10 is equal to the wall thickness of the inner tube 110 plus the wall thickness of the outer tube 120.

It is thereby possible to make the wall thickness of the header 10 large with the wall thickness of the inner pipe 110 and the wall thickness of the outer pipe 120 small, so that the pressure resistance strength (pressure resistance performance) of the header 10, that is, the pressure resistance strength of the header 10 can be effectively improved.

Moreover, since the wall thickness of the inner tube 110 and the wall thickness of the outer tube 120 are small, the difficulty of press forming of the inner tube hole 111 and the outer tube hole 121, that is, the difficulty of press forming of the tube holes, can be greatly reduced. Thereby, the machining accuracy of the pipe holes (the inner pipe hole 111 and the outer pipe hole 121) can be ensured, so that the difficulty of fitting the heat exchange pipe 20 with the pipe holes (the inner pipe hole 111 and the outer pipe hole 121) can be effectively reduced. In addition, since the outer tube 120 is formed of a plurality of sub-outer tube sections 122, the heat exchange tube 20 may be first inserted into the inner tube hole 111 of the inner tube 110 and then the plurality of sub-outer tube sections 122 are assembled, thereby reducing the difficulty of assembly.

Moreover, by making the wall thickness of the outer tube portion 122a having the outer tube hole 121 smaller than the wall thickness of the remaining outer tube portion 122a, the difficulty of press forming of the outer tube hole 121 can be further reduced, so that the machining accuracy of the outer tube hole 121 can be further improved, so as to further effectively reduce the difficulty of fitting the heat exchange tube 20 with the outer tube hole 121.

That is, the header 10 according to the embodiment of the present invention can effectively improve the pressure-resistant strength of the header 10 and thus the pressure-resistant strength of the heat exchanger 1, while greatly reducing the difficulty in press-forming the pipe holes and ensuring the machining accuracy of the pipe holes.

Therefore, the header 10 according to the embodiment of the present invention has advantages of high compressive strength, low difficulty in press forming, high machining accuracy, easy assembly with the heat exchange tube 20, and the like.

As shown in fig. 29 and 30, the outer tube 120 is divided into a first outer tube portion 1221a and a second outer tube portion 1222a in the circumferential direction of the outer tube 120, and an outer tube hole 121 is formed in the first outer tube portion 1221 a. The wall thickness of the first outer tube portion 1221a is smaller than the wall thickness of the second outer tube portion 1222a, the wall thickness of the first outer tube portion 1221a is constant, and the wall thickness of the second outer tube portion 1222a is constant. Whereby the structure of the header 10 can be made more rational.

As shown in fig. 31 to 34, the header 10 includes a pipe body 110a and a fitting part 120a, the pipe body 110a having a first end and a second end, the pipe body 110a having a plurality of pipe holes arranged at intervals along a length direction thereof. The pipe wall of the pipe body 110a has an engagement groove extending from the first end of the pipe body 110a to the second end of the pipe body 110a in the longitudinal direction, the engagement member 120a is engaged in the engagement groove, and the engagement member 120a is attached to a wall surface of the engagement groove. The tube holes include a first sub-tube hole formed on a tube wall of the tube body 110a and penetrating the tube wall of the tube body 110a and a second sub-tube hole formed on the fitting part 120a and penetrating the fitting part 120 a.

The header 10 according to the embodiment of the present invention is configured by including the pipe body 110a and the fitting part 120a, and the pipe body 110a has the fitting groove, so that the wall thickness (thickness) of each of the portion of the pipe body 110a having the fitting groove (the portion is hereinafter referred to as a fitting groove portion) and the fitting part 120a is reduced relative to the wall thickness of the header 10, that is, the wall thickness of the header 10 is equal to the wall thickness of the fitting groove portion of the pipe body 110a plus the wall thickness of the fitting part 120 a.

It is thereby possible to make the wall thickness of the header 10 large in the case where the wall thickness of the fitting groove portion of the pipe body 110a and the wall thickness of the fitting member 120a are small, so that the pressure resistance strength (pressure resistance performance) of the header 10, that is, the pressure resistance strength of the header 10 can be effectively improved.

Moreover, since the wall thickness of the engaging groove portion of the tube body 110a and the wall thickness of the engaging member 120a are small, the difficulty of press forming of the first sub-tube hole and the second sub-tube hole, that is, the difficulty of pressing the tube holes, can be greatly reduced. Thereby, the machining accuracy of the pipe holes (the first sub-pipe hole and the second sub-pipe hole) can be ensured, so that the difficulty in matching the heat exchange pipe 20 with the pipe holes (the first sub-pipe hole and the second sub-pipe hole) can be effectively reduced.

Alternatively, the fitting groove is formed on the inner wall surface (as shown in fig. 31 and 32) or the outer wall surface (as shown in fig. 33 and 34) of the pipe body 110 a.

In the description of the present application, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present application and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the present application.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present application, "plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through intervening media. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In this application, the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples" and the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the application. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present application, and that variations, modifications, substitutions and alterations may be made to the above embodiments by those of ordinary skill in the art within the scope of the present application.

Claims

1. A heat exchanger comprising a first header, a second header, and a plurality of heat exchange tubes, each of the first header and the second header having a plurality of tube holes arranged at intervals in a length direction of the header, the heat exchange tubes having a first end portion penetrating the tube holes of the first header and a second end portion penetrating the tube holes of the second header, the heat exchange tubes including at least one passage to communicate the first header and the second header, at least one of the first header and the second header comprising an inner tube and an outer tube, the outer tube being provided outside in a wall thickness direction of the inner tube, the outer tube having opposite inner and outer wall surfaces in a wall thickness direction thereof, the inner tube having opposite inner and outer wall surfaces in the wall thickness direction thereof, and the inner wall surface of the outer tube being in abutment with the outer wall surface of the inner tube, the pipe holes comprise inner pipe holes formed in the pipe wall of the inner pipe and outer pipe holes formed in the pipe wall of the outer pipe, the inner pipe holes penetrate through the pipe wall of the inner pipe, the outer pipe holes penetrate through the pipe wall of the outer pipe, the outer pipe comprises a plurality of sub outer pipe sections arranged along the circumferential direction of the outer pipe, and a single outer pipe hole is arranged on one sub outer pipe section or two adjacent sub outer pipe sections in the circumferential direction of the outer pipe.

2. The heat exchanger according to claim 1, wherein the number of the sub outer tube sections is two or three, side surfaces are provided between an inner wall surface and an outer wall surface of the sub outer tube sections, the side surfaces are respectively connected to the inner wall surface and the outer wall surface, and adjacent side surfaces of the sub outer tube sections adjacent in the circumferential direction of the outer tube are attached to or spaced apart from each other.

3. The heat exchanger of claim 2, wherein the outer tube includes a first sub outer tube section and a second sub outer tube section, the outer tube hole includes a first sub outer tube hole and a second sub outer tube hole, the first sub outer tube hole is located in the first sub outer tube section and is provided with an opening at the one side surface of the first sub outer tube section, the second sub outer tube hole is located in the second sub outer tube section and is provided with an opening at the one side surface of the second sub outer tube section, the side surface of the first sub outer tube section is adjacent to the side surface of the second sub outer tube section in an outer tube circumferential direction, and the opening of the first sub tube hole is opposite to the opening of the second sub tube hole in the outer tube circumferential direction.

4. The heat exchanger of claim 2, wherein the outer tube aperture is located on one of the sub-outer tube sections, the outer tube aperture having a generally rectangular profile and closed profile edges on an outer wall surface of the one sub-outer tube section.

5. The heat exchanger of claim 4, wherein the wall thickness of the one of the outer tube sub-sections having the outer tube apertures is less than the wall thickness of the remaining outer tube sub-sections.

6. The heat exchanger according to claim 3 or 4, wherein the first outer sub-tube section is provided with a positioning groove, an opening of the positioning groove is provided on one side surface of the first outer sub-tube section, one side of the second outer sub-tube section in the circumferential direction is provided with a positioning projection, and the positioning groove of the first outer sub-tube section is matched with the positioning projection of the second outer sub-tube section.

7. A heat exchanger according to claim 3, wherein the wall thickness of the first and/or second sub outer tube sections varies in the circumferential direction of the outer tube, the first sub outer tube section having one side with a smaller wall thickness than the other side in the circumferential direction of the first sub outer tube section and/or the second sub outer tube section having one side with a smaller wall thickness than the other side in the circumferential direction of the second sub outer tube section.

8. A heat exchanger according to claims 1 to 5, wherein the inner and outer tubes are round tubes, the tube holes having a generally rectangular peripheral profile.

9. A heat exchanger according to claims 1-5, wherein the outer tube apertures are provided with a skirt remote from the outer periphery of the inner tube.

10. A heat exchanger according to claims 1-5, characterised in that the ratio of the wall thickness of the inner tube to the wall thickness of the outer tube sections of the outer tube is in the range of 0.2-5.

11. The heat exchanger according to any one of claims 1 to 4, wherein the inner tube has an inner tube weld extending along its length, the boundaries between the inner tube weld and adjacent sub-outer tube sections being staggered in the circumferential direction of the inner tube.