CN212340038U - Super-cooled pipe and air conditioning unit - Google Patents

Abstract

The application provides a supercooling pipe and an air conditioning unit. The supercooling pipe comprises a pipe body and fins arranged on the outer surface of the pipe body, circulation holes are formed in the fins, and the circulation holes are used for circulating a refrigerant. By applying the technical scheme of the utility model, the refrigerant is circulated through the circulation holes, on one hand, the refrigerant flowing through the outer surface of the pipe body can flow through the circulation holes, and the flow resistance of the refrigerant is reduced; on the other hand, the circulation holes can also damage the boundary layer of the refrigerant attached to the fins, reduce thermal resistance and fluid resistance, and improve the heat exchange performance of the supercooling pipe.

Description

Super-cooled pipe and air conditioning unit

Technical Field

The utility model relates to an air conditioning equipment technical field particularly, relates to a subcooled tube and air conditioning unit.

Background

In the refrigeration and air-conditioning industry, the water-cooled heat exchanger is rapidly developed and applied due to compact structure and wide applicability. Commercial water-cooled heat exchangers are mostly shell and tube heat exchangers. The shell-and-tube condenser is an important part of a large-scale air conditioning system, and aims to condense gaseous refrigerant into liquid refrigerant by taking out energy required to be discharged through secondary refrigerant (such as water, glycol and the like) in a phase change mode.

In order to maximally achieve the expected condensation heat exchange effect and improve the heat exchange performance of the commercial unit, an overcooling region (such as baffling overcooling and soaking overcooling) is often arranged at the bottom of the shell and tube, the overcooling region generally adopts overcooling tubes different from the condensation region, and the quality of the heat exchange performance of the overcooling region has very important influence on the non-phase-change heat exchange of the overcooling region. In the heat exchange process of the supercooling region, the refrigerant outside the supercooling pipe exchanges heat with the secondary refrigerant in the pipe through the pipe wall of the supercooling pipe, and the heat exchange is enhanced by enhancing the expanded area and increasing the disturbance in the pipe.

The heat exchange is enhanced mainly from three ways outside the supercooling pipe: firstly, the flow pressure drop of the refrigerant is reduced by a strengthening means so as to achieve the purpose of reducing the flow resistance of the refrigerant; and the secondary reinforcing pipe can enhance the disturbance of the refrigerant outside the pipe and the turbulence degree of the fluid.

At present, a condenser pipe on a condenser condensation side is often directly used as a supercooling pipe, and the reinforcing effect of local characteristics such as tooth-shaped angles and opening grooves on heat exchange and the weakening effect on flow resistance are often ignored. In the shell-and-tube condenser, a refrigerant flows outside a supercooling pipe, and when the refrigerant exchanges heat with fluid flowing in the pipe through the supercooling pipe, the problems of insufficient heat exchange and low system energy efficiency caused by the over-small disturbance amount and pressure loss to a certain degree due to the defect of the fin-shaped structural design exist.

SUMMERY OF THE UTILITY MODEL

The embodiment of the utility model provides a supercooled tube and air conditioning unit to solve the technical problem that causes the pressure loss easily that the wing-shaped structure of supercooled tube exists among the prior art.

The embodiment of the application provides a supercooling pipe, which comprises a pipe body and fins arranged on the outer surface of the pipe body, wherein circulation holes are formed in the fins and used for circulating a refrigerant.

In one embodiment, the flow holes open at the root of the fins.

In one embodiment, the flow openings open at the upper part of the fins.

In one embodiment, the flow holes are spaced apart along the height of the fin.

In one embodiment, the flow holes are round holes, oval holes or polygonal holes.

In one embodiment, the fin is notched at the top.

In one embodiment, the kerf slots extend from the top of the fin to the root of the fin or the bottom of the fin.

In one embodiment, the kerf slot is a trapezoidal, V-shaped or arcuate slot.

In one embodiment, the plurality of the notch grooves form a tooth-shaped structure between two adjacent notch grooves.

In one embodiment, the fins are provided obliquely with respect to the surface of the tube body, and the fins are inclined toward the refrigerant flow direction of the outer surface of the tube body.

In one embodiment, the angle between the fins and the tube body is α, and α is 70 ° to 85 °.

In one embodiment, the fins are helically wound around the tube body in an axial direction of the tube body.

In one embodiment, the number of the fins is 5 to 60 per inch in the axial direction of the tube body, and the helix angle of the fins is 89.8 to 87.5 °.

In one embodiment, the inner surface of the tubular body is provided with an internal tooth arrangement.

The application also provides an air conditioning unit, which comprises the supercooling pipe, wherein the supercooling pipe is the supercooling pipe.

In the above embodiment, the refrigerant is circulated through the circulation hole, so that on one hand, the refrigerant flowing through the outer surface of the pipe body can flow through the circulation hole, and the flow resistance of the refrigerant is reduced; on the other hand, the circulation holes can also damage the boundary layer of the refrigerant attached to the fins, reduce thermal resistance and fluid resistance, and improve the heat exchange performance of the supercooling pipe. It should also be noted that the flow openings may also serve to increase the heat transfer area.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification. In the drawings:

fig. 1 is a partial perspective view of an embodiment of a supercooling pipe according to the present invention;

FIG. 2 is a schematic front view of a partial structure of the supercooling pipe of FIG. 1;

fig. 3 is a schematic sectional structure view of a-a side of the partial structure of the supercooling pipe of fig. 2.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the following embodiments and accompanying drawings. The exemplary embodiments and descriptions of the present invention are provided to explain the present invention, but not to limit the present invention.

In order to solve the above-mentioned problem that exists among the prior art, the utility model provides a super-cooled tube, this super-cooled tube have local structure of reinforceing to reduce the pressure drop, increase the disturbance to the refrigerant, improve the heat transfer performance of super-cooled tube.

As shown in fig. 1 and 3, the embodiment of the supercooling pipe of the present invention includes a pipe body 10 and a fin 20 disposed on an outer surface of the pipe body 10, wherein a circulation hole 21 is formed in the fin 20, and the circulation hole 21 is used for circulating a refrigerant.

By applying the technical scheme of the utility model, the refrigerant is circulated through the circulation holes 21, on one hand, the refrigerant flowing through the outer surface of the pipe body 10 can flow through the circulation holes 21, and the flow resistance of the refrigerant is reduced; on the other hand, the circulation holes 21 can also destroy the boundary layer of the refrigerant attached to the fins 20, reduce the thermal resistance and the fluid resistance, and improve the heat exchange performance of the supercooling pipe. It should be noted that the flow holes 21 may also serve to increase the heat transfer area to some extent.

More preferably, in the present embodiment, the flow holes 21 are formed in the root portions of the fins 20. In general, since the root of the fin 20 is likely to have a problem of adhesion of the refrigerant to form a boundary layer, the flow holes 21 are formed in the root of the fin 20 in a targeted manner, thereby preferably breaking the boundary layer of the refrigerant adhering to the fin 20.

Optionally, as shown in fig. 3, the distance H2 between the root of the fin 20 and the bottom end of the fin 20 is 0.05-0.2 mm.

As an alternative embodiment, the flow holes 21 are also opened in the upper part of the fins 20. The circulation holes 21 formed in the upper portions of the fins 20 may also serve to break the boundary layer of the refrigerant adhering to the fins 20, but the flow resistance of the refrigerant is more reduced.

As shown in fig. 1 and 3, as a more preferred embodiment, the flow holes 21 are formed in the fin 20 at intervals in the height direction of the fin 20. Thereby ensuring that the flow openings 21 provide the beneficial effects described above for the fin 20 as a whole.

It should be noted that the increase of the number of the circulation holes 21 can effectively increase the disturbance of the fluid, and further reduce the pressure drop of the refrigerant medium, thereby improving the heat exchange efficiency of the supercooling pipe. Preferably, the number of the flow holes 21 may be set as required.

As an alternative embodiment, the flow openings 21 are round openings. As other alternative embodiments, the flow holes 21 may also be elliptical holes or polygonal holes.

As shown in fig. 1 and 3, in the present embodiment, a slit groove 22 is formed in the top of the fin 20. By forming the slit groove 22 on the top of the fin 20, the refrigerant flow resistance can be reduced by the slit groove 22 itself. Optionally, the plurality of the cut-out grooves 22 are formed, and a tooth-shaped structure is formed between two adjacent cut-out grooves 22. The toothed structure formed by the notch grooves 22 is utilized to continuously break the refrigerant boundary layer to reduce heat transfer resistance, so that the non-phase change heat exchange between the liquid refrigerant and the pipe wall is enhanced, the turbulence and disturbance to the refrigerant are increased, the boundary layer of the refrigerant medium is reduced, and the heat exchange capability is enhanced.

In a preferred embodiment, the notch 22 extends from the top of the fin 20 to the root of the fin 20 or the bottom of the fin 20, so as to better reduce the flow resistance of the refrigerant and greatly reduce the turbulence of the refrigerant. It should be noted that the root of the fin 20 refers to a structural position near the bottom end of the fin 20, and the bottom of the fin 20 refers to the bottom end of the fin 20.

As an alternative embodiment, the cut-out groove 22 is a trapezoidal groove, as shown in fig. 3. Optionally, the depth H1 of the trapezoid-shaped groove is 0.2-1.95 mm, the width L1 of the bottom of the trapezoid-shaped groove is 0.05-1 mm, and the included angle beta between the side edges of the trapezoid-shaped groove is 10-120 degrees.

As other alternative embodiments not shown in the figures, the cut-out groove 22 is a V-shaped groove or an arc-shaped groove.

Since the pressure loss of the refrigerant outside the tube body 10 may be a negative factor of the heat exchange effect when exchanging heat with the supercooling tube, as shown in fig. 2, the fin 20 is inclined with respect to the surface of the tube body 10, and the fin 20 is inclined toward the refrigerant flowing direction of the outer surface of the tube body 10 as a preferred embodiment. The structure is used for reducing the pressure drop of the refrigerant, reducing the resistance of the refrigerant in the circulation process, effectively reducing the pressure drop and improving the heat exchange effect. Preferably, in the technical solution of the present embodiment, an included angle between the fin 20 and the tube body 10 is α, and α is 70 ° to 85 °.

Alternatively, in the solution of the present embodiment, the fins 20 are spirally wound around the tube body 10 in the axial direction of the tube body 10. Preferably, the number of the fins 20 is 5 to 60 per inch in the axial direction of the tube 10, and the helix angle of the fins 20 is 89.8 to 87.5 °.

As an alternative embodiment, shown in fig. 1, the inner surface of the tubular body 10 is provided with an internal tooth arrangement 30. The internal tooth structure 30 can enhance the disturbance effect on the refrigerant in the tube body 10, so as to further enhance the non-phase change convection heat transfer inside and outside the tube body 10. Preferably, the internal tooth structure 30 is helically distributed on the inner surface of the tubular body 10.

The utility model also provides an air conditioning unit, this air conditioning unit include foretell subcooling pipe, adopt foretell subcooling pipe, can the effectual super-cooled rate that improves the refrigerant, and then help improving air conditioning unit's efficiency.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not intended to limit the present invention, and it will be apparent to those skilled in the art that various modifications and variations can be made in the embodiments of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (15)

1. The supercooling pipe comprises a pipe body (10) and fins (20) arranged on the outer surface of the pipe body (10), and is characterized in that circulation holes (21) are formed in the fins (20), and the circulation holes (21) are used for circulating a refrigerant.

2. The supercooling tube of claim 1, wherein the flow hole (21) is opened at a root of the fin (20).

3. The supercooling tube of claim 2, wherein the circulation hole (21) is opened at an upper portion of the fin (20).

4. The supercooling tube of claim 3, wherein the circulation holes (21) are spaced apart on the fin (20) in a height direction of the fin (20).

5. The supercooling pipe of any one of claims 1 to 4, wherein the flow holes (21) are circular holes, elliptical holes or polygonal holes.

6. The supercooling tube of claim 1, wherein the fin (20) is formed with a cut groove (22) at the top thereof.

7. The supercooling tube of claim 6, wherein the notch groove (22) extends from a top of the fin (20) to a root of the fin (20) or a bottom of the fin (20).

8. The supercooling pipe of claim 6 or 7, wherein the notch groove (22) is a trapezoidal groove, a V-shaped groove, or an arc-shaped groove.

9. The supercooling pipe of claim 6, wherein the cut grooves (22) are plural, and a tooth structure is formed between adjacent two cut grooves (22).

10. The supercooling tube of claim 1, wherein the fin (20) is inclined with respect to a surface of the tube body (10), and the fin (20) is inclined toward a refrigerant circulating direction of an outer surface of the tube body (10).

11. The supercooling tube of claim 10, wherein an angle α between the fin (20) and the tube body (10) is 70 ° to 85 °.

12. The supercooling tube of claim 1, wherein the fin (20) is spirally wound around the tube body (10) in an axial direction of the tube body (10).

13. The supercooling tube of claim 12, wherein the number of the fins (20) is 5 to 60 per inch in the axial direction of the tube body (10), and the helix angle of the fins (20) is 89.8 to 87.5 °.

14. The supercooling pipe of claim 1, wherein an inner surface of the pipe body (10) is provided with an internal tooth structure (30).

15. An air conditioning unit comprising a subcooling pipe, wherein the subcooling pipe is as claimed in any one of claims 1 to 14.

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