CN219415806U

CN219415806U - Heat exchanger for improving refrigerant distribution uniformity

Info

Publication number: CN219415806U
Application number: CN202320334340.2U
Authority: CN
Inventors: 王纯刚
Original assignee: Hangzhou Jiatong Electric Appliance Technology Co ltd
Current assignee: Hangzhou Jiatong Electric Appliance Technology Co ltd
Priority date: 2023-02-28
Filing date: 2023-02-28
Publication date: 2023-07-25
Anticipated expiration: 2033-02-28

Abstract

The utility model discloses a heat exchanger for improving the distribution uniformity of a refrigerant, and aims to solve the defect that the conventional heat exchanger cannot uniformly distribute the refrigerant to each flat tube, so that the cold quantity is low. The utility model comprises a collecting pipe and flat pipes with two ends respectively connected between the collecting pipes, wherein the collecting pipe comprises a pipe body and a collecting pipe cover, the pipe body comprises an inner pipe and an outer pipe, the end part of the collecting pipe is connected with a liquid exchange pipe, the liquid exchange pipe is communicated with the inner pipe, the inner pipe is provided with circulation holes which are spirally distributed, and the included angle between the axis of the circulation hole which is closer to the liquid exchange pipe and the collecting pipe cover is larger along the length direction of the collecting pipe. Through the structure of the inner tube and the outer tube and the spiral flow holes arranged on the inner tube, the flow resistance of each position is balanced, and the hydraulic pressure of each position is adjusted, so that the refrigerant is distributed more uniformly.

Description

Heat exchanger for improving refrigerant distribution uniformity

Technical Field

The present utility model relates to the field of thermal management, and more particularly, to a heat exchanger that improves refrigerant distribution uniformity.

Background

The heat exchanger can be used as an evaporator and a condenser, and is respectively connected with two sides of the compressor, and heat exchange is carried out between the heat exchanger and the outside or other heat transfer media through the refrigerant. The heat exchanger can efficiently transfer heat or cold through a large amount of heat exchange area provided by the heat exchanger.

The heat exchanger is mainly composed of a collecting pipe for throttling, flat pipes passing through the refrigerant and fins connected between the adjacent flat pipes. The collecting pipe is used for distributing and converging the refrigerant, distributing the refrigerant into each flat pipe as uniformly as possible, transferring heat to the fins in a heat conduction mode, and exchanging heat with the outside through the huge heat transfer area of the fins.

The flow in each flat pipe needs to be close to the collecting pipe, so that the distribution uniformity is improved. The current collecting pipe is higher in hydraulic pressure at the position closer to the refrigerant inlet, the flow rate in the flat pipe connected with the corresponding position is higher, and correspondingly, the flow rate of the flat pipe far away from the refrigerant inlet is low. In this process, a problem of low coldness occurs.

In view of this, the present application aims to realize a heat exchanger that improves the uniformity of refrigerant distribution, i.e., refrigerant.

Disclosure of Invention

The utility model overcomes the defect that the existing heat exchanger cannot uniformly distribute the refrigerant to each flat tube, so that the cold quantity is low, and provides the heat exchanger for improving the distribution uniformity of the refrigerant.

In order to solve the technical problems, the utility model adopts the following technical scheme:

the utility model provides an improve heat exchanger of refrigerant distribution homogeneity, includes the pressure manifold and connects respectively between the pressure manifold at both ends, and wherein, the pressure manifold includes body and collector tube lid, and body is including inner tube and outer tube, and the end connection of pressure manifold has the trading liquid pipe, trading liquid pipe intercommunication inner tube, is equipped with the circulation hole that is the heliciform and arranges on the inner tube, along the length direction of pressure manifold, is close to the axis of the circulation hole of trading liquid pipe and the contained angle of collector tube lid is big more.

At present, in order to improve the uniformity of the refrigerant flow of the heat exchanger, that is, the collecting pipe, a plurality of spacers are generally arranged in the collecting pipe, so that the flow cross-sectional area of the collecting pipe in the axial direction is artificially reduced, and the flow cross-sectional area is increased from small along the flow direction of the refrigerant, thereby enabling the hydraulic flow rates of all parts to be similar. The present application provides, inter alia, another form. The flow holes are arranged on the surface of the inner pipe in a spiral manner, the included angle between the flow holes and the flow pipe cover, namely the inlet of the flat pipe, is adjusted, the included angle is increased when the flow pipe cover is closer to the refrigerant inlet, the resistance is increased, the included angle is reduced when the flow pipe cover is further away from the refrigerant inlet, the resistance is reduced, and the flow rates of the flat pipes are similar through adjustment so that the resistance and the hydraulic pressure of all positions are similar, and the uniformity of refrigerant distribution is improved by the method.

Preferably, the cross section of the inner tube is arc-shaped, and two ends of the inner tube are respectively and fixedly connected to the inner wall surface of the outer tube. The structure reuses one wall surface and reduces the complexity of each part. The fixed connection mode is welding connection.

Preferably, the respective flow holes are communicated in a groove shape. The manner in which the grooves are formed is such that the flow resistance change at each location is more linear and the curve change is more continuous.

Preferably, the flow holes are flat holes. The flat holes are beneficial to adjusting the flow resistance.

Preferably, adjacent flow holes are arranged at equal intervals. The equidistant arrangement of the flow holes also facilitates the linearity and continuity of the flow resistance variation at each location.

Preferably, the axis of the flow opening furthest from the tube is perpendicular to the plane of the manifold cover, where the flow resistance is minimal.

Preferably, the axis included angle of the through holes of the inner tube near the two ends is 60 degrees. The included angle of the flowing hole farthest from the flowing hole is 60 degrees, and the corresponding included angle of the liquid exchange tube at the other end is 60 degrees because the angle between the axis of the liquid exchange tube and the collecting tube cover is smaller to zero degrees.

Compared with the prior art, the utility model has the beneficial effects that: through the structure of the inner tube and the outer tube and the spiral flow holes arranged on the inner tube, the flow resistance of each position is balanced, and the hydraulic pressure of each position is adjusted, so that the refrigerant is distributed more uniformly.

Drawings

FIG. 1 is a schematic diagram of the structure of the present utility model;

FIG. 2 is a schematic view of a tubular body with equally spaced flat holes according to the present utility model;

FIG. 3 is a cross-sectional view of the body of the pipe of the present utility model;

FIG. 4 is a schematic view of a channel-shaped tubular body of the present utility model;

in the figure:

header 1, flat pipe 2, body 3, collector cap 4, inner tube 5, outer tube 6, trading pipe 7, circulation hole 8, closing cap 9.

Detailed Description

The disclosure is further described below with reference to the drawings and examples.

It should be noted that the following detailed description is illustrative and is intended to provide further explanation of the present application. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

Examples:

the utility model provides an improve heat exchanger of refrigerant distribution homogeneity, as shown in FIG. 1, including collecting pipe 1 and both ends connect respectively between collecting pipe 1, wherein, collecting pipe 1 includes body 3 and collector cap 4, body 3 is including inner tube 5 and outer tube 6, the tip of collecting pipe 1 has closing cap 9, closing cap 9 is connected with trading liquid pipe 7, trading liquid pipe 7 intercommunication inner tube 5, be equipped with on the inner tube 5 and be the circulation hole 8 that the heliciform was arranged, along the length direction of collecting pipe 1, the axis that is close to the circulation hole 8 of trading liquid pipe 7 is bigger with the contained angle of collector cap 4 more.

As shown in fig. 3, the cross section of the inner tube 5 is arc-shaped, and both ends of the inner tube 5 are fixedly connected to the inner wall surface of the outer tube 6, respectively. The structure reuses one wall surface and reduces the complexity of each part. The fixed connection mode is welding connection. As shown in fig. 4, in some embodiments, each of the communication holes 8 is formed in a groove shape. The manner in which the grooves are formed is such that the flow resistance change at each location is more linear and the curve change is more continuous. The inner tube 5 and the outer tube 6 are cylinders with two separated ends on the premise of not having the sealing cover 9, and the inner tube 5 and the outer tube 6 enclose two closed spaces in the cross section direction.

The flow holes 8 are flat holes. The flat holes are beneficial to adjusting the flow resistance. In other embodiments, as shown in fig. 2, adjacent flow holes 8 are equally spaced. The equidistant arrangement of the flow openings 8 also facilitates a linear and continuous variation of the flow resistance at each location.

Wherein the axis of the flow opening 8 furthest from the tube 7 is perpendicular to the plane of the manifold cover 4, where the flow resistance is minimal. The included angle of the axes of the flow holes 8 at the positions close to the two ends of the inner tube 5 is 60 degrees. The included angle of the flow hole 8 furthest from the flow hole is 60 degrees, and the corresponding included angle of the liquid exchange tube 7 at the other end is 60 degrees because the angle between the axis of the liquid exchange tube 7 and the collecting tube cover 4 is smaller to zero degrees.

At present, in order to improve the uniformity of the refrigerant flow of the heat exchanger, that is, the collecting pipe 1, a plurality of spacers are generally arranged in the collecting pipe 1, so that the flow cross-sectional area of the collecting pipe 1 in the axial direction is artificially reduced, and the flow cross-sectional area is increased from small along the flow direction of the refrigerant, thereby the hydraulic flow velocity of each part is similar. The present application provides, inter alia, another form. Namely, in the form of an inner tube 5 and an outer tube 6, the refrigerant is separated, through the circulation holes 8 which are spirally arranged on the surface of the inner tube 5, the included angle between the refrigerant and the collecting tube cover 4, namely the inlet of the flat tube 2, is adjusted, the included angle is increased when the refrigerant is closer to the inlet of the refrigerant, the resistance is increased, the included angle is reduced when the refrigerant is farther from the inlet of the refrigerant, the resistance is reduced, and the resistance and the hydraulic pressure of each position are similar through adjustment, so that the flow of each flat tube 2 is similar, and the uniformity of refrigerant distribution is improved by the method.

The above-described embodiments are merely preferred embodiments of the present utility model, and the present utility model is not limited in any way, and other variations and modifications may be made without departing from the technical aspects set forth in the claims.

Claims

1. The utility model provides an improve heat exchanger of refrigerant distribution homogeneity, its characterized in that, including the pressure manifold and both ends connect the flat pipe between the pressure manifold respectively, wherein, the pressure manifold includes body and collector cap, and body is including inner tube and outer tube, and the end connection of pressure manifold has the trading pipe, trading pipe intercommunication inner tube, is equipped with the circulation hole that is the heliciform and arranges on the inner tube, along the length direction of pressure manifold, the axis that is close to the circulation hole of trading pipe and the contained angle of collector cap are bigger more.

2. The heat exchanger for improving refrigerant distribution uniformity according to claim 1, wherein the cross section of the inner tube is arc-shaped, and both ends of the inner tube are fixedly connected to the inner wall surface of the outer tube, respectively.

3. A heat exchanger for improving refrigerant distribution uniformity according to claim 2, wherein each of the flow holes communicates in a groove shape.

4. A heat exchanger for improving refrigerant distribution uniformity according to claim 3, wherein the flow holes are flat holes.

5. A heat exchanger for improving refrigerant distribution uniformity according to claim 2, wherein adjacent flow holes are arranged at equal intervals.

6. A heat exchanger for improving uniformity of refrigerant distribution according to any one of claims 1 to 5, wherein the axis of the flow hole farthest from the tube is perpendicular to the plane of the header cover.

7. The heat exchanger for improving refrigerant distribution uniformity according to claim 6, wherein the axis included angle of the flow holes of the inner tube near both ends is 60 degrees.