CN212362917U

CN212362917U - Microchannel shell and tube heat exchanger

Info

Publication number: CN212362917U
Application number: CN201922469155.0U
Authority: CN
Inventors: 胡匡昱
Original assignee: Kunshan Fangjia Machinery Co ltd
Current assignee: Kunshan Fangjia Machinery Co ltd
Priority date: 2019-12-31
Filing date: 2019-12-31
Publication date: 2021-01-15
Anticipated expiration: 2029-12-31

Abstract

The utility model provides a microchannel shell and tube heat exchanger, includes a long tube-shape heat transfer cavity and refrigerant pipeline subassembly the ascending both ends in the axial of heat transfer cavity are led to respectively have the water route to take over, refrigerant pipeline subassembly includes the heat exchange tube, and this heat exchange tube sets up in the heat transfer cavity, the lumen of this heat exchange tube is as refrigerant flow path, its characterized in that: the inner diameter range of the heat exchange tube is 0.5mm-3 mm. In addition, the heat exchange chamber is provided with an end plate in a disc shape. Adopt the utility model discloses can effectively reduce shell and tube heat exchanger's cost, still be favorable to improving heat exchange efficiency simultaneously.

Description

Microchannel shell and tube heat exchanger

Technical Field

The utility model relates to a heat exchanger field, especially a microchannel shell and tube heat exchanger.

Background

The shell-and-tube heat exchanger is widely applied, and has the main advantages of having a series waterway flow, not forming a local dead zone and avoiding the failure problem caused by frost damage. Therefore, the shell-and-tube heat exchanger is particularly suitable for occasions with high reliability requirements. However, the existing shell-and-tube heat exchangers on the market still have certain disadvantages. The heat exchange tube of the shell-and-tube heat exchanger is generally made of copper tubes, and the size range is 7.00mm-15.88mm, so that the shell-and-tube heat exchanger has the problem of high cost. Meanwhile, the heat exchange tube has a large tube diameter, so that the flow velocity of the refrigerant is low, the heat exchange coefficient of the shell-and-tube heat exchanger is low, and the problem of low heat exchange efficiency exists. In addition, the existing shell-and-tube heat exchanger generally adopts a plane end plate, the pressure resistance of the plane is weak, the failure is avoided by increasing the thickness of the end plate, and the design further causes high cost.

In view of this, how to design a shell and tube heat exchanger with low cost and high heat exchange efficiency is the subject of the research of the utility model.

Disclosure of Invention

The utility model provides a microchannel shell and tube heat exchanger, its purpose, the problem with high costs, heat exchange efficiency is low is solved.

In order to achieve the above purpose, the utility model adopts the technical scheme that:

the utility model provides a microchannel shell and tube heat exchanger, includes a long tube-shape heat transfer cavity and refrigerant pipeline subassembly the ascending both ends in the axial of heat transfer cavity are led to respectively have the water route to take over, refrigerant pipeline subassembly includes the heat exchange tube, and this heat exchange tube setting is in the heat transfer cavity, the lumen of this heat exchange tube is as refrigerant flow path, and its innovation lies in: the inner diameter range of the heat exchange tube is 0.5mm-3 mm.

The relevant content in the above technical solution is explained as follows:

1. in the above scheme, the heat exchange chamber comprises a long cylindrical shell and two end plates, wherein the two axial ends of the heat exchange chamber are respectively provided with one end plate which is a disc-shaped body, the disc-shaped body faces to the inner side of the heat exchange chamber, and the height of the arch is preferably 5mm to 10 mm.

2. In the scheme, the end plate is provided with round holes, the number of the round holes is matched with the number of the heat exchange tubes, the aperture of the round holes is matched with the outer diameter of the heat exchange tubes, and the heat exchange tubes are inserted into the round holes for brazing and forming.

3. In the above scheme, the end plate is provided with a plurality of stepped protrusions, the protrusions include first step planes, the first step planes are perpendicular to the axial direction of the shell, and the circular holes are formed in the first step planes.

4. Preferably, the first step plane is taken as a tread of the step, and the depth of the tread is 1.2 to 1.4 times of the outer diameter of the heat exchange tube. More preferably, the depth of the tread is 1.25 times the outer diameter of the heat exchange tube.

5. Preferably, the distance between the first step planes on the adjacent protrusions is 0.1 to 0.2 times of the outer diameter of the heat exchange tube.

6. In the scheme, a refrigerant collecting box is arranged on one surface of the end plate facing the outside of the heat exchange cavity; an end cover is arranged on the refrigerant collecting box and is a disk-shaped body, and the disk-shaped body is arched towards the inner side of the heat exchange cavity; and the end cover is provided with a refrigerant pipe interface.

7. In the above aspect, the elongated tubular housing is erected in the axial direction thereof.

The utility model has the advantages as follows:

the shell and tube heat exchanger of this scheme adopts the heat exchange tube microchannel, combines the setting of disk body end plate to and the preferred of low price material, can ensure to realize shell and tube heat exchanger cost's reduction by a wide margin. In addition, the volume and the weight can be reduced, so that the use convenience is effectively improved.

In addition, the heat exchange tube microchannel scheme is adopted, so that the flow velocity of the refrigerant can be improved, the heat exchange coefficient of the shell and tube heat exchanger is improved, and the heat exchange efficiency is improved.

Drawings

Fig. 1 is a cross-sectional view of a microchannel shell-and-tube heat exchanger according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view of an end plate according to an embodiment of the present invention;

fig. 3 is a sectional view of a second microchannel shell-and-tube heat exchanger according to an embodiment of the present invention.

In the above drawings: 1. a heat exchange chamber; 11. a waterway adapter; 12. a housing; 13. an end plate; 131. a protrusion; 132. a first step plane; 2. a refrigerant line assembly; 21. a heat exchange pipe; 22. a refrigerant header tank; 221. an end cap; 222. a refrigerant tube interface.

Detailed Description

The invention will be further described with reference to the following drawings and examples:

the first embodiment is as follows: referring to fig. 1, a microchannel shell and tube heat exchanger includes a cylindrical heat exchange chamber 1 and a refrigerant line assembly 2. The long cylindrical heat exchange chamber 1 is vertically arranged in the axial direction, and water path connecting pipes 11 are respectively led out from two ends of the heat exchange chamber 1 in the axial direction; the refrigerant pipeline assembly 2 comprises a heat exchange tube 21, the heat exchange tube 21 is arranged in the heat exchange chamber 1, the tube cavity of the heat exchange tube 21 is used as a refrigerant flow path, and the inner diameter range of the heat exchange tube 21 is 0.5mm-3 mm.

The heat exchange chamber 1 comprises a long cylindrical shell 12 and two end plates 13, the two axial ends of the heat exchange chamber 1 are respectively provided with the end plates 13, the end plates 13 are disc-shaped bodies, the disc-shaped bodies face the inner side of the heat exchange chamber 1 and are arched, and the arched height is 5mm to 10 mm.

The end plate 13 is provided with round holes, the number of the round holes is matched with the number of the heat exchange tubes 21, the aperture of the round holes is matched with the outer diameter of the heat exchange tubes 21, and the heat exchange tubes 21 are inserted into the round holes for brazing and forming.

Fig. 2 is a cross-sectional view of the end plate 13 in the form of a disk-shaped body in the axial direction of the heat exchange chamber 1, and is in the form of a circular ring step when viewed in the axial direction of the heat exchange chamber 1. Referring to fig. 2, the end plate 13 is provided with a plurality of stepped protrusions 131, the protrusions 131 include first stepped planes 132, the first stepped planes 132 are perpendicular to the axial direction of the housing 12, and the circular holes are disposed on the first stepped planes 132. The first step plane 132 is used as a tread of the step, and the depth of the tread can be 1.2 to 1.4 times of the outer diameter of the heat exchange tube 21. In this embodiment, the depth of the tread is preferably 1.25 times the outer diameter of the heat exchange tube 21.

The interval between the first step planes 132 adjacent to the protrusions 131 may be 0.1 to 0.2 times the outer diameter of the heat exchange pipe 21. In the present embodiment, the interval is 0.1 times the outer diameter of the heat exchange tube 21.

A refrigerant header box 22 is arranged on one surface of the end plate 13 facing the outside of the heat exchange chamber 1; an end cover 221 is arranged on the refrigerant collecting box 22, the end cover 221 is a disk-shaped body, and the disk-shaped body is arched towards the inner side of the heat exchange chamber 1; the end cover 221 is provided with a refrigerant pipe interface 222.

In this embodiment, the heat exchange tube 21 and the end plate 13 are made of titanium, or stainless steel; the material of the housing 12 is preferably metallic iron.

In the present embodiment, the above-described fixed connection of the end plate 13 and the heat exchange tube 21 is preferably brazing welding; the fixed connection of the heat exchange tube 21 is preferably a brazed connection.

The end plate 13 and the heat exchange tube 21 are preferably welded by copper rings: arranging a copper ring outside the heat exchange tube 21, melting the copper ring in a welding furnace, and infiltrating into a gap between the end plate and the heat exchange tube 21 to form a welding structure; the heat exchange tube 21 can also be welded by a copper ring: a copper ring is disposed outside the heat exchange tubes 21, and a welded structure is formed by melting the copper ring in a welding furnace and infiltrating into gaps between the heat exchange tubes 21.

Example two: as shown in fig. 3, the microchannel shell-and-tube heat exchanger includes a long cylindrical shell and two end plates, wherein two ends of the heat exchange chamber in the axial direction are respectively provided with one end plate, and the end plates are disk-shaped bodies, which is different from the first embodiment only in that: the disc-shaped body is arched towards the outer side of the heat exchange chamber, and the rest parts are the same as those of the first embodiment, and are not described again. The implementation can basically achieve the working effect of the heat exchanger as in the first embodiment, but the effect may be slightly poor.

Other embodiments and structural changes of the present invention are described below as follows:

1. the heat exchange tubes can be straight tubes which are vertically arranged, and can also be curved tubes which are bent in a continuous S shape, such as the following applications: 201820632861.5, or other heat exchange tubes disclosed in the prior art, as disclosed in application No.: 201720539764.7; but not limited to straight tube, S pipe or U type tubular form, can replace wantonly the utility model discloses the heat exchange tube shape of heat exchange tube function all should be included into the protection scope of the utility model. As would be readily understood and accepted by those skilled in the art.

2. The surface of the end plate of the disc-shaped body facing the inner side of the heat exchange cavity is provided with the stepped bulges, and the stepped bulges are mainly used for reducing the welding difficulty, so that the surface of the end plate facing the outer side of the heat exchange cavity is not limited on the premise of meeting the welding requirement.

3. The long cylindrical heat exchange chamber is arranged vertically in the axial direction. The long cylindrical heat exchange chamber is arranged in an axial horizontal arrangement mode, the working effect of the heat exchanger according to the embodiment is basically achieved, and the effect is possibly slightly poor.

4. The connection of above-mentioned device is not restricted to the welding, can replace wantonly the utility model discloses the connected mode of fixed connection function should all be included into the utility model discloses a protection scope. For example, the end plate and the heat exchange tube can also be welded by using copper foil: the end plate is covered with a layer of copper foil, the heat exchange tube penetrates through the copper foil, and a welding structure is formed by melting the copper foil in a welding furnace and infiltrating into a gap between the end plate and the heat exchange tube.

The above embodiments are only for illustrating the technical concept and features of the present invention, and the purpose of the embodiments is to enable people skilled in the art to understand the contents of the present invention and to implement the present invention, which cannot limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered by the protection scope of the present invention.

Claims

1. The utility model provides a microchannel shell and tube heat exchanger, includes a long tube-shape heat transfer cavity (1) and refrigerant pipeline subassembly (2) the ascending both ends of axial of heat transfer cavity (1) are led out respectively and are had water route takeover (11), refrigerant pipeline subassembly (2) include heat exchange tube (21), and this heat exchange tube (21) set up in heat transfer cavity (1), and the lumen of this heat exchange tube (21) is as refrigerant flow path, its characterized in that: the inner diameter range of the heat exchange tube (21) is 0.5mm-3 mm.

2. The microchannel shell and tube heat exchanger of claim 1, wherein: the heat exchange chamber (1) comprises a long cylindrical shell (12) and two end plates (13), the two ends of the heat exchange chamber (1) in the axial direction are respectively provided with one end plate (13), the end plates (13) are disc-shaped bodies, and the disc-shaped bodies face the inner side of the heat exchange chamber (1) to be arched.

3. The microchannel shell and tube heat exchanger of claim 2, wherein: the height of the end plate (13) arched towards the inner side of the heat exchange chamber (1) is 5mm to 10 mm.

4. The microchannel shell and tube heat exchanger of claim 1, wherein: the heat exchange chamber (1) comprises a long cylindrical shell (12) and two end plates (13), the two ends of the heat exchange chamber (1) in the axial direction are respectively provided with one end plate (13), the end plates (13) are disc-shaped bodies, and the disc-shaped bodies face the outer side of the heat exchange chamber (1) in an arched mode.

5. The microchannel shell and tube heat exchanger of claim 2 or 4, wherein: round holes are formed in the end plate (13), the number of the round holes is matched with the number of the heat exchange tubes (21), the aperture of each round hole is matched with the outer diameter of each heat exchange tube (21), and the heat exchange tubes (21) are inserted into the round holes to be brazed and formed.

6. The microchannel shell and tube heat exchanger of claim 5, wherein: the end plate (13) is provided with a plurality of stepped protrusions (131) on the surface facing the inner side of the heat exchange chamber (1), the protrusions (131) comprise first step planes (132), the first step planes (132) are perpendicular to the axial direction of the shell (12), and the circular holes are formed in the first step planes (132).

7. The microchannel shell and tube heat exchanger of claim 6, wherein: and the first step plane (132) is taken as a stepped tread, and the depth of the tread is 1.2 to 1.4 times of the outer diameter of the heat exchange tube (21).

8. The microchannel shell and tube heat exchanger of claim 6, wherein: the distance between the first step planes (132) on the adjacent bulges (131) is 0.1 to 0.2 times of the outer diameter of the heat exchange tube (21).

9. The microchannel shell and tube heat exchanger of claim 2, wherein: a refrigerant header box (22) is arranged on one surface of the end plate (13) facing the outside of the heat exchange chamber (1);

an end cover (221) is arranged on the refrigerant collecting box (22), the end cover (221) is a disk-shaped body, and the disk-shaped body is arched towards the inner side of the heat exchange chamber (1);

and a refrigerant pipe interface (222) is arranged on the end cover (221).

10. The microchannel shell and tube heat exchanger of claim 1, wherein: the long cylindrical heat exchange chamber (1) is vertically arranged in the axial direction.