CN111256389B

CN111256389B - Heat exchanger

Info

Publication number: CN111256389B
Application number: CN201811455990.2A
Authority: CN
Inventors: 请求不公布姓名
Original assignee: Zhejiang Sanhua Automotive Components Co Ltd
Current assignee: Zhejiang Sanhua Automotive Components Co Ltd
Priority date: 2018-11-30
Filing date: 2018-11-30
Publication date: 2023-03-28
Anticipated expiration: 2038-11-30
Also published as: CN111256389A

Abstract

The invention discloses a heat exchanger, which comprises a shell and a heat exchange core body, wherein the heat exchange core body comprises a flat pipe, a refrigerant flow channel is formed in the flat pipe, the flat pipe is provided with a plurality of parallel straight parts and a bending part for transitionally connecting two adjacent straight parts, at least one part of the flat pipe is positioned in the shell, a cooling liquid flow channel is formed in the shell, the cooling liquid flow channel of the shell is divided into at least two side-by-side cooling liquid flows along the direction parallel to the straight parts of the flat pipe, and the flow directions of the two adjacent cooling liquid flows are opposite; the shell is provided with a hollow protruding part at the turning part of two adjacent cooling liquid flows; the protruding part is located above or below the direction change position of the flat pipe, and an inner cavity of the protruding part is communicated with two adjacent cooling liquid flows with opposite flow directions. The heat exchanger can prolong the flow of cooling liquid, improve the heat exchange efficiency and has higher pressure bearing capacity.

Description

Heat exchanger

Technical Field

The invention relates to the technical field of heat exchange devices, in particular to a heat exchanger applicable to CO ₂ A heat exchanger for refrigerant.

Background

CO ₂ Is a novel environment-friendly refrigeration working medium, can reduce global greenhouse effect, can solve the problem of environmental pollution caused by compounds, and has good economical efficiency and practicability.

With CO ₂ The compression type refrigeration cycle system of the working medium can be applied to most of the refrigeration and heating fields. However, the operating pressure of such air conditioning systems is high, and this characteristic of such systems needs to be fully considered when designing CO2 heat exchange devices, and the component design is still not mature, so that such systems are not widely used.

In general, CO ₂ The heat exchanger mainly has tube fin formula, microchannel, board-like, bushing type and shell and tube formula, and traditional CO2 microchannel heat exchanger adopts refrigerant and air forced convection's mode heat transfer, and heat exchange efficiency is lower, and simultaneously, in order to satisfy the operating pressure requirement, the wall thickness of spare part sets up thickly, and casing and joint processing are comparatively complicated.

Therefore, how to modify the heat exchanger to accommodate CO ₂ The air conditioning system and the heat pump system of working media are problems to be solved urgently by technical personnel in the field.

Disclosure of Invention

The invention aims to provide a heat exchanger. The heat exchanger can prolong the flow of cooling liquid, improve the heat exchange efficiency and has higher pressure bearing capacity.

In order to achieve the purpose, the heat exchanger provided by the invention comprises a shell and a heat exchange core body, wherein the heat exchange core body comprises a flat pipe, a refrigerant flow channel is formed inside the flat pipe, the flat pipe is provided with a plurality of parallel straight parts and a bending part for transitionally connecting the adjacent two straight parts, at least one part of the flat pipe is positioned inside the shell, a coolant flow channel is formed inside the shell, the coolant flow channel is divided into at least two side-by-side coolant flows along the direction parallel to the straight parts of the flat pipe, the coolant flow channel comprises the coolant flow, and the flow directions of the adjacent two coolant flows are opposite; the shell is provided with a hollow protruding part at the joint of two adjacent cooling liquid flows; the protruding portion is located above or below the bending portion of the flat pipe, a certain distance is kept between the inner top surface or the inner bottom surface of the inner cavity of the protruding portion and the flat pipe, and the inner cavity of the protruding portion is communicated with two adjacent cooling liquid flows in opposite flow directions.

The heat exchanger that this technical scheme provided, including casing and heat transfer core, at least a part of the flat pipe of heat transfer core is located inside the casing, the inside coolant liquid runner of casing divide into two at least coolant liquid flows, and be equipped with hollow protruding portion on the casing, two adjacent coolant liquid flows of cavity intercommunication through the protruding portion, in operation, after the coolant liquid gets into the casing, at first distributed to first coolant liquid flow, after flowing to the contralateral, through the cavity of protruding portion, get into second coolant liquid flow, after contralateral flow to, flow from the casing, carry out the heat exchange with the intraductal refrigerant that flows through of flat in the flow process. The cooling liquid flow channel is divided into at least two cooling liquid flows and communicated through the protruding part cavity, so that the circulation path of the cooling liquid can be prolonged, and the heat exchange performance can be improved.

Drawings

FIG. 1 is an isometric view of a heat exchanger disclosed in an embodiment of the invention;

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

FIG. 3 is a side view of the heat exchanger shown in FIG. 1;

FIG. 4 is a top view of the heat exchanger shown in FIG. 1;

FIG. 5 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 4;

FIG. 6 is a cross-sectional view taken along line B-B of FIG. 4;

FIG. 7 is a cross-sectional view taken along line C-C of FIG. 4;

fig. 8 is a schematic end view of one end of the heat exchanger shown in fig. 1 provided with a refrigerant inlet and outlet connecting seat;

FIG. 9 is a cross-sectional view taken along line D-D of FIG. 8;

FIG. 10 is a schematic structural view of the flange plate shown in FIG. 2;

FIG. 11 is a schematic view of the structure of the separator shown in FIG. 2;

fig. 12 is a schematic view illustrating the principle of preventing the coolant from being short-circuited from the innermost side by relatively offsetting the center of the water pipe of the first coolant collecting portion from the center of the first coolant flow path.

In the figure:

1. the shell 2, the heat exchange core body 3, the mounting plate 4, the mounting hole 5, the flat pipe 51, the straight part 52, the bent part 53, the flow hole 6, the cooling liquid inlet 7, the cooling liquid outlet 8, the refrigerant inlet 9, the refrigerant outlet 10, the upper shell 11, the lower shell 12, the outward flange 13, the saw-tooth-shaped bulge 14, the flange plate 15, the refrigerant inlet connecting seat 16, the refrigerant outlet connecting seat 17, the waist-shaped counterbore 18, the pore channel 19, the notch 20, the internal cavity 21, the protruding part 22, the inlet first collecting part 23, the outlet second collecting part 24, the partition plate 25, the turned edge 26, the fin (simplified drawing) 27, the internal top surface

Detailed Description

In order that those skilled in the art will better understand the disclosure, the invention will be described in further detail with reference to the accompanying drawings and specific embodiments.

In this document, terms such as "front, rear, left, and right" are established based on positional relationships shown in the drawings, and the corresponding positional relationships may vary depending on the drawings, and therefore, they are not to be construed as absolute limitations on the scope of protection; moreover, relational terms such as "first" and "second," and the like, may be used solely to distinguish one element from another element having the same name, without necessarily requiring or implying any actual such relationship or order between such elements.

Referring to fig. 1, fig. 2 and fig. 3, fig. 1 is an isometric view of a heat exchanger according to an embodiment of the present invention; FIG. 2 is an exploded view of the heat exchanger of FIG. 1; fig. 3 is a side view of the heat exchanger shown in fig. 1.

In one embodiment, the heat exchanger provided by the invention is applicable to CO ₂ Heat exchanger for refrigerant, with conventional CO ₂ Compared with a heat exchanger, the heat exchanger has the advantages of higher heat exchange efficiency, strong bearing capacity, simple installation and processing, light weight and low cost.

As shown in the figure, the heat exchanger mainly comprises a shell 1 and a heat exchange core body 2, wherein the bottom of the shell 1 is provided with a mounting plate 3, two ends of the mounting plate 3 exceed the shell for a certain distance in the front-back direction, a mounting hole 4 is formed in the shell, and no other component is arranged in the axis direction of the mounting hole 4 to shield the shell, so that the mounting operation is convenient.

Heat transfer core 2 includes that two are arranged side by side and are made a round trip the flat pipe 5 of bending in succession along snakelike route together, two flat pipe 5 all have a plurality of straight portions 51 that are parallel to each other and the diversion of a plurality of two adjacent straight portions of transitional coupling portion of bending 52, one of them flat pipe 5 is outer flat pipe, another flat pipe 5 is interior flat pipe, because outer flat pipe is located the outside, consequently, the range of bending of its portion of bending is great relatively, have the arc portion of end flat portion and connection end flat portion and two adjacent straight portions 51, the central angle of arc portion is 90, interior flat pipe is located the inboard, consequently, the range of bending of its portion of bending is less relatively, can only have the arc portion of connecting two adjacent straight portions 51, the central angle of arc portion is 180. Of course, the bending portion of the outer flat tube may also be in an arc shape with a central angle of 180 degrees, and similarly, the bending portion of the inner flat tube may also have an end flat portion.

It is understood that the flat tube portion may not only be formed by two flat tubes 5 in parallel, but also be formed by bending one flat tube 5 continuously in the above manner, and may also be formed by arranging three or more flat tubes 5 in parallel and bending the flat tubes together continuously in the above manner, that is, the number of the flat tubes 5 may be further increased or decreased, which may be determined according to actual needs.

The structure of the flat pipe 5 can be seen in fig. 6, one or more rows of flow holes 53 are uniformly distributed on the cross section of the flat pipe to form a refrigerant flow channel, the flow holes 53 are preferably circular or in other shapes, the hydraulic diameter of the flow holes 53 is preferably in the range of 0.3mm to 1.5mm, the hole center distance is preferably 0.5mm to 2.5mm, the width of the flat pipe is preferably 20mm to 60mm, and in the width direction, the flat pipe part can also be realized by two or more flat pipes 5 side by side, that is, two or more layers of flat pipes 5 can be arranged in the longitudinal direction shown in the figure.

Because the flat pipe 5 bends continuously in a snake shape, the formed refrigerant flow channel correspondingly has a plurality of flows, each time the flat pipe 5 bends, a reverse flow is added, the flat pipe 5 shown in the figure has seven bending parts in total, and eight flows are formed, so that the heat exchange efficiency is improved.

Bend and be snakelike flat pipe 5 and hold inside casing 1, the inside coolant liquid runner that forms of casing 1, be used for letting in the coolant liquid and carry out heat exchange with flat pipe 5, flat pipe 5 occupies the inside partial space of casing 1, flat pipe 5 outside is the partly of coolant liquid runner, between flat pipe 5's straight portion 51, between flat pipe 5's the portion 52 of bending, and all form the coolant liquid runner between flat pipe 5 and casing 1's the internal surface, be equipped with fin 26 in the coolant liquid runner that forms between the straight portion 51 and the coolant liquid runner that forms between straight portion 51 and the casing 1 lateral wall, with the intensive heat transfer effect, except fin 26, the coolant liquid runner also can design the surface ripple formula and strengthen heat transfer structure or the point wave formula and strengthen heat transfer structure.

The coolant runner and the coolant runner of flat pipe 5 are isolated from each other, coolant inlet 6 and coolant outlet 7 of heat exchanger set up in same one side (front side top) of casing 1, coolant inlet 8 and coolant outlet 9 of heat exchanger also set up in same one side (rear side tip) of casing 1, coolant inlet 8 and coolant outlet 9 also can set up in the different side, coolant inlet 6 and coolant outlet 7 also can set up in one of the four corners position of heat exchanger, comparatively nimble, moreover, coolant or coolant can get into from casing 1 top, flow out from casing 1 below.

The shell 1 comprises an upper shell 10 and a lower shell 11, the upper shell 10 and the lower shell 11 are provided with buckle structures and are connected in a welding mode, the heat exchange core body 2 is assembled and then is installed in the shell 1, and then the shell is placed in a tunnel furnace or a vacuum furnace to be welded.

Specifically, go up shell 10 and lower shell 11 and be equipped with welded connection's flanging 12, wherein, be equipped with zigzag protrusion 13 on the three flanging of last shell 10, after last shell 10 and lower shell 11 are assembled, before welding, through the pressure equipment instrument, can make zigzag protrusion 13 from the outside buckle on lower shell 11's flanging 12, directly assemble heat exchanger into an organic whole, welding frock has been simplified, the upper and lower shell contact parallel and level has been guaranteed simultaneously, welding quality is improved, the realization of the technology of flattening can conveniently be realized in the setting of a plurality of zigzag protrusion 13.

Referring to fig. 10, fig. 10 is a schematic structural view of the flange plate shown in fig. 2.

As shown in the figure, after the upper housing 10 and the lower housing 11 are assembled, the flat tube leading-out end is an open end, the open end is provided with a flange plate 14, the jointing surface of the upper housing and the lower housing and the flange plate 14 are welded, and the end of the flat tube 5 passes through the flange plate 14 and is communicated with a refrigerant inlet connecting seat 15 and a refrigerant outlet connecting seat 16 on the flange plate.

The welding line of the upper and lower shells is perpendicular to the welding line of the upper and lower shells and the flange plate 14, and the two welding lines are perpendicular to each other, so as to form the isolation of the cooling liquid flow passage from the outside, form a sealed shell 1, and bear CO ₂ The high pressure generated by the refrigerant in operation can not generate the leakage phenomenon.

The hole used for penetrating through the flat tube 5 on the external surface of the flange plate 14 is a waist-shaped counter bore 17, the refrigerant inlet and outlet connecting seat is in an inverted L shape, the refrigerant inlet and outlet connecting seat and the refrigerant outlet are arranged on the external surface of the flange plate 14 in a bilateral symmetry manner, the refrigerant inlet and outlet connecting seat are provided with a duct 18 used for leading in and out refrigerant, two jacks used for inserting the flat tube 5 are respectively arranged on one surface attached to the flange plate 14, the flat tube 5 is inserted into the refrigerant inlet and outlet connecting seat for a certain distance after being led out from the interior of the shell 1 and is communicated with the duct 18 connected with the refrigerant inlet and outlet and used for leading in and out refrigerant, the transverse part of the refrigerant inlet and outlet connecting seat is also provided with a longitudinal through hole and a counter bore, the depth of the waist-shaped counter bore 17 on the flange plate 14 is equal to the line diameter of a welding ring used during welding, a cavity for containing the welding ring can be formed with the refrigerant inlet and outlet connecting seat after assembly, the welding ring can prevent the solder from flowing around in the welding process, ensure the quality of the welding gap, and improve the pressure resistance.

After welding, the flat pipe 5 is welded with the refrigerant inlet and outlet connecting seat, the flat pipe 5 is welded with the flange plate 14, and the refrigerant inlet and outlet connecting seat is also welded with the flange plate 14. The structure of mutually welding the flat tube, the connecting seat and the flange plate can effectively improve the compression resistance and prevent high-pressure CO ₂ The refrigerant leaks from the flat tube leading-out part.

In addition, the upper edge and the lower edge of the flange plate 14 are respectively provided with a notch 19 in the middle position, wherein the length of the notch at the lower edge is greater than that of the notch at the upper edge, and the edges of the port parts of the upper shell and the lower shell are respectively provided with a sawtooth-shaped bulge 13 which can wrap and buckle the flange plate 14 from the notch 19 after being bent.

Because the welding surface formed by the flanging 12 is added on the basis of welding, the strength of the welded shell is enhanced, and because of the existence of the buckle structure, the self relative position of the heat exchanger before entering the furnace for welding is fixed, the investment of a welding tool can be saved, the tool for fixing the periphery of the shell and the flange plate 14 is saved, and the purposes of strengthening welding, self-fixing and welding-free tool are realized.

The coolant flow channel inside the shell 1 is divided into two parallel coolant flows along the direction parallel to the straight portion of the flat pipe 5, the widths of the two coolant flows in the left and right directions are approximately the same, the flow directions are opposite, the shell 1 is provided with a protruding portion 21, and the two coolant flows are conducted at the turning position through an inner cavity 20 of the protruding portion 21.

With continued reference to fig. 4 to 9, fig. 4 is a top view of the heat exchanger shown in fig. 1; FIG. 5 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 4; FIG. 6 is a cross-sectional view taken along line B-B of FIG. 4; FIG. 7 is a cross-sectional view taken along line C-C of FIG. 4; FIG. 8 is a schematic diagram of an end portion of the heat exchanger shown in FIG. 1 having refrigerant inlet and outlet connection seats; fig. 9 is a cross-sectional view taken along line D-D of fig. 8.

As shown in the figure, the housing 1 is provided with a hollow protrusion 21 at the turning position of the two coolant flows, the protrusion 21 is arranged on the upper shell 10 and located above the turning position of the flat tube 5, and the inner cavity 20 of the upper shell is transitionally communicated with the two coolant flows.

The internal cavity 20 has the opening position that faces flat pipe 5 downwards, and half and the first coolant liquid flow of opening position switch on mutually at the tail end, and the other half and the second coolant liquid flow of opening position switch on mutually at the head end, and the coolant liquid flows into the second coolant liquid flow after internal cavity 20 from first coolant liquid flow, and 180 conversion takes place for the flow direction, and the flow direction of two coolant liquid flows is opposite promptly.

The inner cavity 20 extends transversely above the flat tube 5, and the projection of the inner cavity is substantially rectangular, and coincides with the flat tube bending portion 52 and the partial flat portion 51 of the two conducted coolant flows in the projection direction (see fig. 9), that is, the projection of the bending portion of the flat tube 5 close to the protruding portion 21 on the side where the protruding portion 21 of the housing 1 is located on the protruding portion 21, and at least a part of the projection of the flat tube 5 close to the protruding portion 21 on the side where the protruding portion 21 of the housing 1 is located on the protruding portion 21. Therefore, all the flow passages in the first cooling liquid flow path and all the flow passages in the second cooling liquid flow path can be completely communicated, and the non-communicated dead flow passage area is avoided.

The size of the protruding part 21 is proportional to the diameter of the cooling liquid inlet and outlet apertures, the cross-sectional area of the inner cavity 20 is slightly larger than that of the cooling liquid inlet and outlet connecting pipe, moreover, the protruding part 21 can be arranged on the upper shell 10 and also on the lower shell 11, if a plurality of cooling liquid flows are arranged, one part of the protruding part 21 can be arranged on the upper shell 10, the other part of the protruding part 21 can be arranged on the lower shell 11, and the protruding part 21 can be rectangular or in other shapes, such as special-shaped shapes, and the like.

The shell 1 is provided with a hollow inlet first collecting portion 22 and a hollow outlet second collecting portion 23, the inlet first collecting portion 22 and the outlet second collecting portion 23 are located on one side, opposite to the protruding portion 21, of the shell 1, the projection of the bending portion, close to the inlet first collecting portion 22, of the flat pipe 5 on one side, where the inlet first collecting portion 22 is located, of the flat pipe 5 is located on the inlet first collecting portion 22, the projection of the bending portion, close to the outlet second collecting portion 23, of the flat pipe 5 on one side, where the outlet second collecting portion 23 is located, of the flat pipe 5 is located on the outlet second collecting portion 23, at least one part of the projection, close to the inlet first collecting portion 22, of the flat pipe 5 on one side, where the inlet first collecting portion 22 is located, of the shell 1 is located, and at least one part of the projection, close to the outlet second collecting portion 23, of the flat pipe 5 on one side, where the outlet second collecting portion 23 is located, of the flat pipe 1 is located on the outlet second collecting portion 23.

As can be seen from fig. 5, 7, and 9, after the flat tube 5 is continuously bent and installed inside the housing 1, a small distance is left between the bent portion 52 at the front end thereof and the inner surface of the front wall of the housing 1, the bent portion 52 at the rear end thereof is almost attached to the inner surface of the flange plate 14, the top thereof is almost attached to the inner top surface of the housing 1, the bottom thereof is also almost attached to the inner bottom surface of the housing 1, and the flow channels formed by dividing the flat tube 5 inside the housing are laterally communicated with each other through a small gap, and are almost isolated from each other, so that all the flow channels corresponding to the inlet first collecting portion 22 of the housing can form a first coolant flow path after being laterally communicated with each other through the inlet first collecting portion 22, the coolant can flow into the flow channels of the first coolant flow path through the inlet first collecting portion 22, the flow channels corresponding to the outlet second collecting portion 23 of the housing 1 can form a second coolant flow path after being laterally communicated with each other through the outlet second collecting portion 23, and the coolant flowing out of the second coolant flow path can flow to the outlet 23 and finally flow out of the coolant 7.

The housing 1 is provided with separating ribs between the inlet first collecting portion 22 and the outlet second collecting portion 23, so that it is ensured that the inlet coolant only enters the first coolant flow path and the outlet coolant only originates from the second coolant flow path.

In order to ensure that the first coolant flow path and the second coolant flow path are separated from each other and to avoid short-circuiting of the coolant between the different flow paths, a partition plate 24 may be inserted between the heat exchange cores.

A partition plate 24 is arranged at the separation position of two adjacent cooling liquid flow paths in the shell 1, the partition plate 24 is parallel to the flat part 51 of the flat pipe 5, the two adjacent cooling liquid flow paths are positioned at two sides of the partition plate 24, the partition plate 24 is welded and fixed with the inner wall of the shell 1, and at least one part of the partition plate 21 is positioned in the area between the inlet first collecting part 22 and the outlet second collecting part 23.

The partition plate 24 is inserted between two flat portions at the partition of the coolant flow path, the upper and lower edges of the partition plate are connected with the upper and lower surfaces of the inner surface of the housing 1, respectively, the front edge of the partition plate is connected with the side wall of the inner surface of the housing 1, a certain distance is left between the rear edge of the partition plate and the bending portion 52 of the flat tube 5, and a certain distance is kept between one side of the partition plate 24 close to the protruding portion 21 and the inner top surface 27 of the protruding portion 21. If the protruding portion 21 is provided on the lower case 11, a certain distance is maintained between the side of the partition plate 24 close to the protruding portion 21 and the inner bottom surface of the protruding portion 21.

Referring to fig. 11, fig. 11 is a schematic structural view of the partition shown in fig. 2.

As shown in the figure, the upper, lower edge and front side edge of the baffle 24 are all provided with flanges 25 forming welding faces, and are connected with the inner surface of the shell 1 in a welding way through the flanges 25, the area of the welding faces can be increased through the flanges 25, under the premise of realizing the function of the baffle, the pressure bearing capacity in the shell is increased, and the improvement of the internal pressure strength of the shell 1 is realized.

If the coolant uses three or more flow paths, the inlet first collecting portion 22, the outlet second collecting portion 23, and the protruding portion 21 may be divided by providing a corresponding number of ribs and separators.

Referring to fig. 12, fig. 12 is a schematic view illustrating the principle of preventing the coolant from being short-circuited from the innermost side by relatively deviating the center of the water pipe of the first coolant collecting portion from the center of the first coolant flow path.

As shown in the figure, the shell 1 is provided with a cooling liquid inlet 6 and a cooling liquid outlet 7, the cooling liquid inlet 6 is provided with an inlet first collecting portion 22, the center of the cooling liquid inlet 6 is outwards deviated from the center of the inlet first collecting portion 22, namely, the distance a is larger than the distance B; likewise, the coolant outlet 7 is provided with an outlet second collecting portion 23, and the center of the coolant outlet 7 is offset outward from the center of the outlet second collecting portion 23.

As shown in fig. 7, the cavity of the inlet first collecting portion 22 is in a cavity shape gradually enlarging from the coolant inlet 6 to the inside of the housing, the inside of the cavity is rounded and gradually transited, and the slope of the inner wall of the cavity on the side close to the outlet second collecting portion 23 is smaller than that of the inner wall on the side far from the outlet second collecting portion 23; similarly, the chamber of the outlet second collecting portion 23 has a chamber shape gradually decreasing from the inside of the case toward the coolant outlet 7, and the slope of the inner wall on the side close to the inlet first collecting portion 22 is smaller than the slope of the inner wall on the side far from the inlet first collecting portion 22.

So set up, the circulation passageway that is close to baffle 24 is little, and the flow resistance is big, has reduced the rivers (as the arrow shows) from the innermost short circuit for the coolant liquid can flow toward the outside, has realized the more even distribution of water route in the flow.

The above embodiments are merely preferred embodiments of the present invention, and are not limited thereto, and on the basis of the above embodiments, various embodiments can be obtained by performing targeted adjustment according to actual needs. For example, the coolant flow channel may be another micro-channel structure, or may be welded or riveted to the flange plate 14 by using the integrated housing 1 (e.g., a 3D printing housing), or may be a counter-flow coolant or a counter-flow coolant, or the like. This is not illustrated here, since many implementations are possible.

The heat exchanger can prolong the circulation path of the cooling liquid, increase the flow rate of the cooling liquid under the same flow, increase the heat exchange coefficient of the cooling liquid, obviously improve the heat exchange efficiency, and can make the distribution of the cooling liquid more uniform by eccentrically arranging the inlet first collecting part 22 and the outlet second collecting part 23, and can promote the heat exchanger to bear CO through triple welding of flat pipes, flange plates and connecting seats, flanging of a partition plate, two circles of welding of mutually vertical shells and zigzag convex buckles of the shells ₂ The high-pressure capacity of the refrigerant guarantees the sealing performance, avoids the leakage phenomenon, and has the advantages of small volume, light weight, low cost and the like compared with the technical scheme of improving the pressure-bearing capacity by simply increasing the wall thickness of parts.

The heat exchanger provided by the present invention has been described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the core concepts of the present invention. It should be noted that, for those skilled in the art, without departing from the principle of the present invention, it is possible to make various improvements and modifications to the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.

Claims

1. A heat exchanger comprises a shell and a heat exchange core body, wherein the heat exchange core body comprises a flat pipe, a refrigerant flow channel is formed in the flat pipe, the flat pipe is provided with a plurality of straight parts which are parallel to each other and bending parts which are in transition connection with two adjacent straight parts, at least one part of the flat pipe is positioned in the shell, and a coolant flow channel is formed in the shell; the shell is provided with a hollow protruding part at the joint of two adjacent cooling liquid flows; the protruding part is positioned above or below the bending part of the flat pipe, a certain distance is kept between the inner top surface or the inner bottom surface of the inner cavity of the protruding part and the flat pipe, and the inner cavity of the protruding part is communicated with two adjacent cooling liquid flows with opposite flow directions; the shell is provided with a hollow first collecting portion and a hollow second collecting portion, and the first collecting portion and the second collecting portion are located on one side, opposite to the protruding portion, of the shell; the first collecting portion is provided with a cooling liquid inlet, and the second collecting portion is provided with a cooling liquid outlet; the center of the cooling liquid inlet is outwards deviated from the center of the first collecting portion, and the center of the cooling liquid outlet is outwards deviated from the center of the second collecting portion.

2. The heat exchanger according to claim 1, wherein a projection of a bent portion of the flat tube, which is close to the protruding portion, on a side of the housing where the protruding portion is located at the protruding portion, and at least a part of a projection of a straight portion of the flat tube, which is close to the protruding portion, on the side of the housing where the protruding portion is located at the protruding portion.

3. The heat exchanger according to claim 2, wherein a projection of a bent portion of the flat tube close to the first collecting portion on a side of the shell where the first collecting portion is located at the first collecting portion, a projection of a bent portion of the flat tube close to the second collecting portion on a side of the shell where the second collecting portion is located at the second collecting portion, at least a portion of a projection of a straight portion of the flat tube close to the first collecting portion on a side of the shell where the first collecting portion is located at the first collecting portion, and at least a portion of a projection of a straight portion of the flat tube close to the second collecting portion on a side of the shell where the second collecting portion is located at the second collecting portion.

4. The heat exchanger according to claim 3, wherein the cavity of the first collecting portion has a cavity shape gradually enlarged from the coolant inlet to the inside of the case, the cavity of the second collecting portion has a cavity shape gradually reduced from the inside of the case to the coolant outlet, the slope of the inner wall of the first collecting portion on the side close to the second collecting portion is smaller than the slope of the inner wall on the side far from the second collecting portion, and the slope of the inner wall of the second collecting portion on the side close to the first collecting portion is smaller than the slope of the inner wall on the side far from the first collecting portion.

5. The heat exchanger according to claim 3 or 4, wherein the area of the projection of the straight portion on the first collecting portion, the second collecting portion, and the protruding portion is smaller than the area of the remaining portion.

6. The heat exchanger according to any one of claims 1 to 5, wherein a partition plate is provided in the housing, two adjacent coolant passages are provided on both sides of the partition plate, the partition plate is parallel to the flat portions of the flat tubes, the partition plate is welded to the inner wall of the housing, and at least a part of the partition plate is provided in a region between the first collecting portion and the second collecting portion in the housing.

7. The heat exchanger of claim 6, wherein the spacer is interposed between the flat portions of the flat tubes at the flow path division of the coolant, the lateral edges of the spacer adjacent to the first and second collecting portions are connected to the side walls of the inner surface of the housing, the lateral edges of the spacer adjacent to the protrusion are spaced apart from the bent portions of the flat tubes, and the side of the spacer adjacent to the protrusion is spaced apart from the inner top or bottom surface of the protrusion.

8. The heat exchanger of claim 7, wherein the lateral edges of the partition connected with the inner wall of the shell are provided with flanges, the flanges are welded with the inner wall of the shell, the shell comprises an upper shell and a lower shell, and the upper shell and the lower shell are provided with a plurality of buckling structures and are welded.

9. The heat exchanger of claim 8, wherein the upper and lower housings are provided with welded flanges, and the snap structure comprises saw-tooth projections on the flanges of the upper or lower housings, the saw-tooth projections engaging the flanges of the lower or upper housings from outside.

10. The heat exchanger according to any one of claims 1 to 9, wherein the heat exchanger is provided with a flange plate, the flange plate covers the open end of the shell, the shell is welded to the abutting surface of the flange plate, the flange plate is provided with a waist-shaped counter bore matched with the flat tube, one end of the flat tube extends into the counter bore, the flat tube is welded and fixed to the inner wall of the counter bore, the heat exchanger is provided with a refrigerant inlet connecting seat and a refrigerant outlet connecting seat, the refrigerant inlet connecting seat and the refrigerant outlet connecting seat are provided with a refrigerant inlet and a refrigerant outlet, the refrigerant inlet connecting seat and the refrigerant outlet connecting seat are welded and fixed to the flange plate, the refrigerant inlet is communicated with one end of the flat tube, and the refrigerant outlet is communicated with the other end of the flat tube; the flat tubes include two or more flat tubes arranged side by side and bent together to form the straight portion and the bent portion.