WO2020042425A1

WO2020042425A1 - Heat exchange tube and air conditioner

Info

Publication number: WO2020042425A1
Application number: PCT/CN2018/120241
Authority: WO
Inventors: 刘华; 张治平; 岳清学; 胡东兵; 王春连; 胡海利
Original assignee: 珠海格力电器股份有限公司
Priority date: 2018-08-30
Filing date: 2018-12-11
Publication date: 2020-03-05
Also published as: CN109099748A

Abstract

A heat exchange tube and an air conditioner. The heat exchange tube comprises a tube body (10) and fins (20) that are disposed on an outer surface of the tube body (10), wherein a channel (30) is formed between adjacent fins (20); each fin (20) is provided with a communication groove (21); the communication groove (21) communicates adjacent channels (30); and the communication groove (21) is used for circulating refrigerant. The area of a discharge channel for liquid refrigerant after condensation is increased, the capacity to discharge the refrigerant is reinforced, and the refrigerant can better circulate on the surface of the heat exchange tube, thus avoiding lowering heat exchange efficiency that is caused by a heat resistance increase due to an excessive increase in the thickness of the liquid refrigerant on the surface of the heat exchange tube.

Description

Heat exchange tubes and air conditioners

Related applications

This application is based on a Chinese patent application with an application number of 201811003111.2, an application date of August 30, 2018, and an invention name of "Heat Exchanger and Air Conditioner", and claims its priority. This application is incorporated herein as a whole.

Technical field

The present disclosure relates to the field of refrigeration technology, and in particular, to a heat exchange tube and an air conditioner.

Background technique

In the air conditioning and refrigeration industry, water-cooled condensers have developed rapidly due to their compact structure and wide applicability. High efficiency, energy saving and replacement of new refrigerants are still the main research directions at present. Water-cooled heat exchangers are mostly horizontal shell-and-tube heat exchangers. Freon is taken in the shell side and water is taken in the tube side. In the condenser, a factor that has a relatively large effect on its heat exchange is the performance of the heat exchange tubes in the shell. Inside the shell side, the refrigerant outside the condensing tube undergoes a phase change for heat exchange. The refrigerant condenses outside the tube to form a liquid film covering the surface of the heat exchange tube. The presence of this liquid film increases the thermal resistance on the refrigerant side. Perform heat exchange. Therefore, the thermal resistance distribution mainly exists outside the tube. According to the weak-side strengthening principle, it is particularly important to strengthen the outside of the tube, and the heat resistance outside the tube should be minimized to improve the heat transfer performance.

For the external strengthening of condensing tubes, the current general strengthening technology is to use a combination cutter to extrude metal fins that spirally expand along the circumference of the tube through a combination cutter, and perform secondary rolling on the fins to form a boss and sharp corners. . The main strengthening mechanism is to increase the surface area outside the tube. The thinned liquid film reduces the thermal resistance by using different bosses and sharp corners and radius of curvature. The lower fins are spirally connected and form channels. Drain the liquid refrigerant. In this way, a convex plate and a sharp, sharp-angled thin liquid film are formed. At the same time, the formed convex plate also increases the resistance of the liquid film to drip and remove.

Experimental research on single-tube heat transfer of high-efficiency tubes found that during the condensation process of the condensing tube, the vapor refrigerant condenses on the surface of the condensing tube, and the liquid refrigerant formed by the condensation flows along the channel between the tube fins and below the condensing tube, and along the The channels formed between the fins and the fins are drained away. However, in the traditional condensation tube, the channels formed between the fins and the fins are spirally connected in the axial direction during the enhanced condensation process, and the lateral channels cannot be connected in the lower part. Therefore, as the condensation strength of the liquid refrigerant increases, the thickness of the liquid refrigerant increases, and the thermal resistance increases. In severe cases, the liquid refrigerant will form a flood on the surface of the heat exchange tube, reducing the effective heat exchange area and causing the condensation effect to decline.

Summary of the Invention

The embodiments of the present disclosure provide a heat exchange tube and an air conditioner to solve the technical problem that the liquid refrigerant existing on the surface of the heat exchange tube during use is obviously flooded on the surface.

An embodiment of the present disclosure provides a heat exchange tube including a tube body and fins disposed on an outer surface of the tube body. A channel is formed between adjacent fins, and a communication groove is formed on the fin. The communication grooves will be adjacent to each other. The communication channel is connected, and the communication groove is used for circulating the refrigerant.

In some embodiments, the fins are coiled on the outer surface in a circumferential direction of the outer surface, and the communication groove is opened on the fins in the axial direction of the outer surface.

In some embodiments, the fins are spirally arranged on the outer surface.

In some embodiments, the fins are multiple, and the multiple fins are spaced apart on the outer surface.

In some embodiments, the communication groove is opened deep on the fin to the bottom of the fin, or is opened to a predetermined length from the bottom of the fin.

In some embodiments, there are a plurality of communication grooves, and the plurality of communication grooves are disposed at intervals on the fins.

In some embodiments, the communication groove is disposed at an angle β with respect to the extending direction of the fin, and 0 ° <β≤90 °.

In some embodiments, the cross-section of the communication groove is V-shaped, U-shaped, or Y-shaped.

In some embodiments, a boss structure is pressed on the fin, and the boss structure is used to increase the surface area of the fin.

In some embodiments, the boss structure includes a groove portion on the top of the fin and a sharp corner portion protruding relative to the side of the fin.

In some embodiments, the boss structure is disposed at an angle α with respect to the extending direction of the fin, 15 ° ≦ α ≦ 65 °.

In some embodiments, an inner rib structure is formed on the inner surface of the pipe body, and the inner rib structure is used to increase the surface area of the inner surface.

In some embodiments, the inner rib structure is arranged on the inner surface in a spiral shape, and the inner rib structure is arranged at an angle λ with respect to the center of the pipe body, 15 ° ≦ λ ≦ 60 °.

In some embodiments, the inner rib structure has a trapezoidal or triangular cross section.

The present disclosure also provides an air conditioner including a heat exchange tube, and the heat exchange tube is the above-mentioned heat exchange tube.

In the above embodiment, the communication grooves formed on the fins can make adjacent channels communicate, increase the area of the liquid refrigerant discharge channel after condensation, strengthen the refrigerant discharge capacity, and allow the refrigerant to be better on the surface of the heat exchange tube. Ground circulation. Furthermore, the excessive increase of the thickness of the liquid refrigerant on the surface of the heat exchange tube can be avoided, the flooding phenomenon on the surface of the heat exchange tube can be avoided, the effective heat exchange area can be ensured, and the heat exchange effect can be increased.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings constituting a part of the present disclosure are used to provide a further understanding of the present disclosure. The exemplary embodiments of the present disclosure and the description thereof are used to explain the present disclosure, and do not constitute an improper limitation on the present disclosure. In the drawings:

1 is a schematic diagram of an overall structure of an embodiment of a heat exchange tube according to the present disclosure;

FIG. 2 is a partial structural schematic diagram of the heat exchange tube of FIG. 1; FIG.

FIG. 3 is a partially enlarged structure diagram of FIG. 2; FIG.

4 is a schematic plan view of the structure of FIG. 3;

FIG. 5 is a schematic view of the front view structure of FIG. 3; FIG.

6 is a schematic structural view of the right side of FIG. 3;

FIG. 7 is a schematic sectional structural view of the heat exchange tube of FIG. 6.

detailed description

In order to make the objectives, technical solutions, and advantages of the present disclosure more clear, the present disclosure is further described in detail below in conjunction with the embodiments and the accompanying drawings. Here, the exemplary embodiments of the present disclosure and the description thereof are used to explain the present disclosure, but are not intended to limit the present disclosure.

FIG. 1 illustrates an embodiment of a heat exchange tube according to the present disclosure. The heat exchange tube includes a tube body 10 and a fin 20 disposed on an outer surface 11 of the tube body 10. A channel is formed between adjacent fins 20. 30. The fin 20 is provided with a communication groove 21. The communication groove 21 communicates with adjacent channels 30. The communication groove 21 is used for circulating a refrigerant.

Applying the technical solution of the present disclosure, through the communication groove 21 provided on the fin 20, the adjacent channels 30 can be communicated, the area of the discharge channel of the liquid refrigerant after condensation is increased, the refrigerant discharge capacity is enhanced, and the refrigerant can be exchanged in The surface of the tube circulates better. Furthermore, the excessive increase of the thickness of the liquid refrigerant on the surface of the heat exchange tube can be avoided, the flooding phenomenon on the surface of the heat exchange tube can be avoided, the effective heat exchange area can be ensured, and the heat exchange effect can be increased.

In the technical solutions of some embodiments, as shown in FIG. 2, the fins 20 are coiled on the outer surface 11 in the circumferential direction of the outer surface 11, and the communication groove 21 is opened on the fins 20 in the axial direction of the outer surface 11. It should be noted that the above-mentioned winding arrangement along the circumferential direction of the outer surface 11 may be provided along the radial direction of the outer surface 11 or in a direction at an angle to the radial direction; Opening in the axial direction also refers to communicating adjacent channels 30 in the axial direction or in a direction at an angle to the axial direction.

In some embodiments, as shown in FIGS. 1 and 2, the fins 20 are spirally arranged on the outer surface 11. As another optional implementation manner, the fins 20 are multiple, and the multiple fins 20 are disposed at intervals on the outer surface 11, that is, a plurality of annular fins 20 are disposed on the outer surface 11.

As shown in FIG. 3 and FIG. 6, in the technical solutions of some embodiments, the cross section of the communication groove 21 is Y-shaped, and the depth of the communication groove 21 on the fin 20 is opened to a predetermined length from the bottom of the fin 20. As another optional implementation manner, it is also feasible that the communication groove 21 is deeply opened on the fin 20 to the bottom of the fin 20. It should be noted that the depth of the communication groove 21 on the fin 20 should be as deep as possible on the basis of ensuring the stress intensity of the fin 20.

In addition, as another optional implementation manner, the cross-section of the communication groove 21 may also be V-shaped or U-shaped.

In the technical solutions of some embodiments, there are a plurality of communication grooves 21, and the plurality of communication grooves 21 are disposed at intervals on the fin 20. By providing a plurality of communication grooves 21, the refrigerant discharge capacity can be further enhanced, so that the refrigerant can flow better on the surface of the heat exchange tube. It has been found through experiments that the number of communication grooves 21 uniformly distributed from 30 to 100 along the circumferential direction of the fins 20 can have a good refrigerant discharge capability.

In the technical solutions of some embodiments, as shown in FIG. 3 and FIG. 4, the communication groove 21 is set at an angle β with respect to the extending direction of the fin 20, and 0 ° <β ≦ 90 °. Since the outer surface 11 of the fin 20 is spirally arranged, allowing the communication groove 21 to be arranged at an angle relative to the fin 20 is also beneficial to the circulation of the refrigerant in the axial direction. In addition, it is also possible to make the communication groove 21 perpendicular to the extending direction of the fin 20.

As shown in FIGS. 3 and 5, as a preferred embodiment, the fin 20 is pressed with a boss structure 22. The boss structure 22 is used to increase the surface area of the fins 20 and can improve heat exchange efficiency during heat exchange. As shown in FIGS. 5 and 6, in the technical solutions of some embodiments, the boss structure 22 includes a groove portion 221 on the top of the fin 20 and a sharp corner portion 222 protruding from the side of the fin 20. In this way, while increasing the heat exchange area, the sharp corners on the surface of the condenser tube are increased and strengthened. Using the characteristics of the large curvature of the corners 222 and the grooves 221, the refrigerant liquid film is thinned, thereby strengthening local condensation and condensation. The ability to play a role in strengthening the upper layer of the condenser tube to reduce the thickness of the liquid film adhered to the fins on the surface of the condenser tube when the refrigerant vapor condenses.

As shown in FIG. 4, in the technical solutions of some embodiments, the boss structure 22 is disposed at an angle α with respect to the extending direction of the fin 20, and 15 ° ≦ α ≦ 65 °. Similarly, in the technical solutions of some embodiments, the outer surface 11 of the fin 20 is spirally arranged, so that the boss structure 22 is arranged at an angle with respect to the fin 20, which is also conducive to the circulation of the refrigerant in the axial direction. Heat exchange.

In some embodiments, the groove portion 221 is formed by extruding the top of the original fin using a knurling die to form a groove portion structure having a depth of 0.1 to 0.45 mm and a width of 0.01 to 0.35 mm. . While forming the groove portion 221, due to the good plasticity of the metal material itself, two sharp corner portions 222 are naturally formed on both sides of the fin 20, and the structure of the sharp corner portions 222 extending to the side of the fin 20 is 0.05 ~ 0.2mm.

As shown in FIGS. 1 and 7, in the technical solutions of some embodiments, an inner rib structure 40 is formed on the inner surface of the pipe body 10. In use, the inner rib structure 40 is used to increase the surface area of the inner surface, which can improve the heat exchange efficiency during heat exchange, and also increases the degree of disturbance of the fluid in the tube, which can further enhance the heat exchange efficiency.

In the technical solutions of some embodiments, the inner rib structure 40 is spirally disposed on the inner surface, and the inner rib structure 40 is disposed at an angle λ with respect to the center of the pipe body 10, 15 ° ≦ λ ≦ 60 °. In some embodiments, the inner rib structures 40 are multiple, and the multiple inner rib structures 40 are evenly distributed on the inner surface. In some embodiments, there are 10 to 80 internal rib structures.

In the technical solutions of some embodiments, the inner surface of the pipe body 10 is rolled into a spiral convex rib structure 40 with a core of a pressure groove. The inner rib structure 40 is disposed at an angle λ with respect to the center of the pipe body 10, and the protrusion height of the inner rib structure 40 from the inner surface is 0.2 to 0.60 mm.

As shown in FIG. 2, in the technical solutions of some embodiments, the cross section of the inner rib structure 40 is trapezoidal, and the cross section shaped inner rib structure 40 is more convenient for processing and has better heat exchange capability. In some embodiments, the bottom of the inner rib structure 40 is integrated with the inner surface and has a smooth transition with the inner surface, and the two corners have a smooth transition. As another optional implementation manner, the cross section of the inner rib structure 40 may also be triangular.

In the technical solution of the present disclosure, the above-mentioned heat exchange tube is processed by a dedicated fin processing equipment, and an extrusion molding and chipless processing process is adopted. In this case, a mother pipe with an outer diameter of 19.05mm and a wall thickness of 1.1mm is used for processing. A grooved mold is used to roll the grooves on the mother tube outside the tube, and the formed grooves are pressed with a combination tool to form independent fins that spiral in the axial direction. Deformation caused by processing fins on the independent fins To form a communication groove. At the same time, the top of the fins is simultaneously extruded with a knurling die to form a boss structure. The inner rib structure 40 is reinforced and synchronized. While the outer surface is squeezed by a combination cutter, the inner side is formed by a multi-head grooved core.

It should be noted that the technical solution of the above heat exchange tube is particularly applicable to a condenser tube.

The present disclosure also provides an air conditioner including the above-mentioned heat exchange tube. The air conditioner using the above heat exchange tube has better heat exchange performance and higher refrigeration efficiency.

The above are only preferred embodiments of the present disclosure, and are not intended to limit the present disclosure. For those skilled in the art, the embodiments of the present disclosure may have various modifications and changes. Any modification, equivalent replacement, or improvement made within the spirit and principle of this disclosure shall be included in the protection scope of this disclosure.

Claims

A heat exchange tube includes a tube body (10) and fins (20) provided on an outer surface (11) of the tube body (10), and adjacent fins (20) are formed between A channel (30), wherein the fin (20) is provided with a communication groove (21), and the communication groove (21) communicates with the adjacent channel (30), and the communication groove (21) is used for In circulation refrigerant.
The heat exchange tube according to claim 1, wherein the fins (20) are coiled on the outer surface (11) in a circumferential direction of the outer surface (11), and the communication groove (21) The fin (20) is opened along the axial direction of the outer surface (11).
The heat exchange tube according to claim 2, wherein the fins (20) are spirally arranged on the outer surface (11).
The heat exchange tube according to claim 2, wherein the fins (20) are plural, and the plural fins (20) are spaced apart on the outer surface (11).
The heat exchange tube according to claim 1, wherein the communication groove (21) is opened deep on the fin (20) to the bottom of the fin (20), or is opened to a distance from the fin (20) The position of the bottom of the predetermined length.
The heat exchange tube according to claim 1, wherein there are a plurality of communication grooves (21), and the plurality of communication grooves (21) are disposed at intervals on the fins (20).
The heat exchange tube according to claim 1, wherein the communication groove (21) is disposed at an angle β with respect to an extending direction of the fin (20), and 0 ° <β≤90 °.
The heat exchange tube according to claim 1, wherein a cross section of the communication groove (21) is V-shaped, U-shaped, or Y-shaped.
The heat exchange tube according to claim 1, wherein a boss structure (22) is pressed on the fin (20), and the boss structure (22) is used to increase the size of the fin (20). Surface area.
The heat exchange tube according to claim 9, wherein the boss structure (22) includes a groove portion (221) on the top of the fin (20), and a portion opposite to the fin (20) Sharp corners (222) protruding from the side.
The heat exchange tube according to claim 9, wherein the boss structure (22) is disposed at an angle α with respect to the extending direction of the fins (20), 15 ° ≤α≤65 °.
The heat exchange tube according to claim 1, wherein an inner rib structure (40) is formed on an inner surface of the pipe body (10), and the inner rib structure (40) is used to increase the Surface area.
The heat exchange tube according to claim 12, wherein the inner rib structure (40) is provided on the inner surface in a spiral shape, and the inner rib structure (40) is opposite to the tube body (10). The center is set at an angle λ, 15 ° ≤λ≤60 °.
The heat exchange tube according to claim 12, wherein a cross section of the inner rib structure (40) is trapezoidal or triangular.
An air conditioner includes a heat exchange tube, wherein the heat exchange tube is the heat exchange tube according to any one of claims 1 to 14.