CN212457513U

CN212457513U - Heat exchanger and air conditioner

Info

Publication number: CN212457513U
Application number: CN202021643736.8U
Authority: CN
Inventors: 郭忠玉; 杨瑞琦; 徐勇程; 马腾飞
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2020-08-10
Filing date: 2020-08-10
Publication date: 2021-02-02
Anticipated expiration: 2030-08-10

Abstract

The application provides a heat exchanger and an air conditioner, which comprise fins, wherein each fin comprises a corrugated section, each corrugated section extends in a corrugated shape, the wave crest of each corrugated section is a plane, and the extending direction of the wave crest is the same as the extending direction of the corrugated section; the heat exchanger comprises at least two fins, a heat dissipation channel is formed between every two adjacent fins, and wave crests of the adjacent fins are arranged oppositely. The application provides a heat exchanger, air conditioner can increase the disturbance of heat transfer fluid when the heat dissipation passageway flows, improves the heat transfer coefficient of convection, and then has improved the heat transfer performance of heat exchanger.

Description

Heat exchanger and air conditioner

Technical Field

The application belongs to the technical field of air conditioning, and particularly relates to a heat exchanger and an air conditioner.

Background

The finned tube heat exchanger is a heat exchanger commonly used in various industries such as refrigeration air-conditioning, chemical engineering and the like at present. Most of fins on the existing heat exchanger are corrugated fins, and the corrugated fins have lower heat exchange coefficients due to the structural reasons, so that the heat exchange performance of the heat exchanger is reduced.

SUMMERY OF THE UTILITY MODEL

Therefore, the technical problem that this application will be solved lies in providing a heat exchanger, air conditioner, can increase the disturbance when heat transfer fluid flows in heat dissipation channel, improves the heat transfer coefficient of convection, and then has improved the heat transfer performance of heat exchanger.

In order to solve the above problems, the present application provides a heat exchanger, including a fin, where the fin includes a corrugated section, the corrugated section extends in a corrugated shape, a peak of the corrugated section is a plane, and an extending direction of the peak is the same as an extending direction of the corrugated section;

the heat exchanger comprises at least two fins, a heat dissipation channel is formed between every two adjacent fins, and wave crests of the adjacent fins are arranged oppositely.

Preferably, the ripple section includes at least one the crest, the ripple section still includes first domatic and second domatic, first domatic setting is in the first end of crest, the second domatic setting is in the second end of domatic, first domatic with the crest becomes the obtuse angle setting, the second domatic with the crest becomes the obtuse angle setting.

Preferably, the angle formed by the first slope surface and the wave crest is between 120 and 165 °, and/or the angle formed by the second slope surface and the wave crest is between 120 and 165 °.

Preferably, the extending direction of the wave crest is a first direction;

the projection of the first slope surface in the plane where the peak is located is a first projection, and the length of the first projection along the first direction is greater than that of the peak along the first direction; and/or the projection of the second slope surface in the plane where the peak is located is a second projection, and the length of the second projection along the first direction is greater than the length of the peak along the first direction.

Preferably, the first slope surface and the second slope surface are symmetrically arranged by taking a perpendicular bisector of the peak as a symmetry axis.

Preferably, the wave trough of the wave section is a plane, and the wave trough and the wave crest are arranged in parallel.

Preferably, the length of the peak and the length of the valley in the extending direction of the peak are the same.

Preferably, the fin further includes an initial section, the initial section is disposed on an upstream side of the corrugated section along a flow direction of the heat exchange fluid in the heat dissipation channel, the initial section is disposed in parallel with the wave crest, and the initial sections of the adjacent fins are disposed opposite to each other.

Preferably, the fin further includes an end section, the end section is disposed on a downstream side of the corrugated section along a flow direction of the heat exchange fluid in the heat dissipation channel, the end section is disposed in parallel with the wave crest, and the end sections of the adjacent fins are disposed opposite to each other.

Preferably, the corrugated section comprises 3 peaks, 3 peaks are located in the same plane, the corrugated section comprises 2 troughs, and 2 troughs are located in the same plane.

Preferably, the corrugated section includes a first peak, a second peak and a third peak, the first peak, the second peak and the third peak are sequentially arranged along a flowing direction of the heat exchange fluid in the heat dissipation channel, the first peak and the third peak are located in a first plane, the second peak is located in a second plane, and the first plane is parallel to the second plane.

Preferably, the second peak is located on one side of the first plane close to the trough.

Preferably, the fin is provided with a mounting hole, the mounting hole is provided with a pipe sleeve, the pipe sleeve and the mounting hole are coaxially arranged, the heat exchanger comprises a heat exchange pipe, and the heat exchange pipe is sleeved in the mounting hole and the pipe sleeve.

Preferably, a flanging structure is arranged on the circumferential outer wall of one end, far away from the fins, of the pipe sleeve, and the flanging structure is perpendicular to the outer wall of the pipe sleeve.

In another aspect of the present application, an air conditioner is provided, which includes the heat exchanger as described above.

Advantageous effects

The embodiment of the utility model provides an in provide a heat exchanger, air conditioner, can increase the disturbance of heat transfer fluid when flowing in heat dissipation channel, improve the heat transfer coefficient to convection, and then improved the heat transfer performance of heat exchanger.

Drawings

Fig. 1 is a schematic structural view of a heat exchanger according to embodiment 1 of the present application;

FIG. 2 is a schematic structural view of a fin according to embodiment 1 of the present application;

FIG. 3 is a side view of a fin according to embodiment 1 of the present application;

fig. 4 is a schematic view illustrating the circulation of a heat dissipating fluid in a heat dissipating channel according to embodiment 1 of the present application;

FIG. 5 is a schematic structural view of a fin according to embodiment 2 of the present application;

fig. 6 is a side view of a fin according to embodiment 2 of the present application.

The reference numerals are represented as:

1. a fin; 11. wave crest; 111. a second peak; 12. a trough of a wave; 13. a first slope surface; 14. a second slope surface; 15. an initial segment; 16. a last stage; 17. mounting holes; 18. pipe sleeve; 181. a flanging structure; 2. a heat exchange tube.

Detailed Description

With combined reference to fig. 1 to 4, according to embodiment 1 of the present application, a heat exchanger includes a fin 1, the fin 1 includes a corrugated section, the corrugated section extends in a corrugated shape, a peak 11 of the corrugated section is a plane, an extending direction of the peak 11 is the same as an extending direction of the corrugated section, the heat exchanger includes at least two fins 1, a heat dissipation channel is formed between adjacent fins 1, and the peaks 11 of adjacent fins 1 are arranged oppositely. The wave crests 11 of the corrugated sections are arranged to be planes, and meanwhile, the wave crests 11 of the adjacent fins 1 are arranged oppositely, so that the disturbance of heat dissipation fluid in a heat dissipation channel can be enhanced, the convective heat transfer coefficient of the sides of the fins 1 is improved, the heat transfer coefficient of the sides of the fins 1 is enhanced, the heat transfer performance and the energy efficiency ratio of the whole heat exchanger are improved, the whole size of the heat exchanger can be correspondingly reduced, and the cost is greatly reduced. Through the adoption of the method, the air inlet speed and the temperature gradient are enhanced in synergy, and the heat transfer capacity is further enhanced.

Further, in a wet condition, by arranging the wave crests 11 to be flat, channels are provided for the flow of the condensation droplets. Under the wet working condition, condensation liquid drops on the surface of the fin 1 are gathered on the wave crest 11 along the two sides of the wave crest 11 under the action of airflow drag force, the liquid drops flow out of the fin 1 along the wave crest 11 under the action of gravity, the stagnation of the condensation liquid drops on the surface of the fin 1 is reduced, the air resistance is reduced, and the heat exchange capacity of the heat exchanger under the wet working condition is improved.

Further, under the frosting working condition, the wave crest 11 is set to be a plane and also provides a liquid drainage channel, so that the discharging of the defrosting water is facilitated, the frosting amount of the next frosting period is reduced, and the fin 1 structure is more convenient to defrost.

Further, the extending direction of the corrugated segment is the extending direction of the whole corrugated segment, and is not the extending direction of one of the corrugated segments. As shown in fig. 3, the extending direction of the corrugated portion extends in the left-right direction. The extending direction of the wave peak 11 is the same as the extending direction of the wave section, that is, the wave peak 11 also extends in the left-right direction in fig. 3.

Further, the profile of the outer edge of the fin 1 is approximately rectangular, and the corrugated sections and the wave crests 11 extend in the direction of the short side of the rectangle.

Further, adjacent fins 1 are corrugated, and the heat dissipation channels also extend in a corrugated manner.

Further, in this embodiment, the number of the fins 1 is plural, the fins 1 are arranged in parallel, and all the fins 1 have the same structure and are arranged in an aligned manner.

Further, in this embodiment, the heat exchange fluid flowing through the heat dissipation channel is air.

The ripple section includes at least one crest 11, and the ripple section still includes first domatic 13 and the domatic 14 of second, and first domatic 13 sets up the first end at crest 11, and the domatic 14 setting of second is at domatic second end, and first domatic 13 becomes the obtuse angle setting with crest 11, and the domatic 14 of second becomes the obtuse angle setting with crest 11.

Furthermore, the first slope surface 13 and the second slope surface 14 are arranged, and the first slope surface 13 and the second slope surface 14 are arranged at an obtuse angle with the wave crest 11, so that the formation of turbulent flow is ensured.

The angle formed by the first slope surface 13 and the wave crest 11 is 120-165 degrees, the angle formed by the second slope surface 14 and the wave crest 11 is 120-165 degrees, and the heat dissipation effect can reach the best.

The extending direction of the wave crest 11 is a first direction; the projection of the first slope 13 in the plane of the peak 11 is a first projection, and the length of the first projection along the first direction is greater than that of the peak 11 along the first direction; the projection of the second slope 14 in the plane where the peak 11 is located is a second projection, and the length of the second projection along the first direction is greater than that of the peak 11 along the first direction, so that the heat dissipation effect can be optimal.

Further, as shown in fig. 3, the length of the first slope surface 13 and the second slope surface 14 in the horizontal direction is smaller than the length of the peak 11 in the horizontal direction.

The first slope surface 13 and the second slope surface 14 are symmetrically arranged by taking a perpendicular bisector of the peak 11 as a symmetry axis, so that the whole body formed by the first slope surface 13, the peak 11 and the second slope surface 14 is an isosceles trapezoid, and a section of the heat dissipation channel positioned on the first slope surface 13, the peak 11 and the second slope surface 14 is also an isosceles trapezoid. The air flows along the trapezoidal heat dissipation channel, the disturbance of the air inlet is increased, the heat exchange coefficient of the convective heat transfer between the air and the fins 1 is improved, the air inlet speed and the temperature gradient are enhanced in cooperation, the heat exchange efficiency of the side of the fins 1 is effectively improved, and the heat transfer capacity is enhanced. And further, the heat exchange capacity and the energy efficiency ratio of the whole machine can be improved, so that the overall size of the heat exchanger can be reduced, and the cost can be greatly reduced.

The wave trough 12 of the corrugated section is a plane, the wave trough 12 and the wave crest 11 are arranged in parallel, and a discharge channel is provided for condensed liquid drops and defrosting water on the fin 1.

Further, by providing the valleys 12 as flat surfaces, channels are provided for the flow of condensation droplets in wet conditions. Under the wet working condition, condensation liquid drops on the surface of the fin 1 are gathered on the wave troughs 12 along the two sides of the wave troughs 12 under the action of airflow drag force, the liquid drops flow out of the fin 1 along the wave troughs 12 under the action of gravity, the detention of the condensation liquid drops on the surface of the fin 1 is reduced, the air resistance is reduced, and the heat exchange capacity of the heat exchanger under the wet working condition is improved.

Further, under the frosting working condition, the wave troughs 12 are arranged to be planes which also provide a liquid drainage channel, so that the discharging of the defrosting water is facilitated, the frosting amount of the next frosting period is reduced, and the fins 1 are more convenient to defrost.

Furthermore, the wave crests 11 and the wave troughs 12 are arranged simultaneously and form opposite parallel planes, so that condensation and defrosting water can be discharged timely. The problem of among the prior art condensate droplet block air runner, increased heat transfer thermal resistance is solved, condensate droplet worsens the heat transfer effect. Meanwhile, the problems that defrosting water is remained on the surface of the heat exchanger fin 1 under the defrosting working condition in the prior art, the air flow resistance is increased, and the heat transfer is deteriorated are solved.

The lengths of the wave crests 11 and the wave troughs 12 in the extending direction of the wave crests 11 are the same, so that the radiating fluid is guaranteed to generate turbulent flow, and meanwhile, the condensation and defrosting water are guaranteed to be smoothly discharged.

Further, as shown in fig. 3, the peaks 11 and the valleys 12 extend in the horizontal direction.

Fin 1 still includes initial segment 15, and initial segment 15 sets up at the ripple section along the upstream side of heat transfer fluid flow direction in heat dissipation channel, and initial segment 15 sets up with crest 11 parallel arrangement, and adjacent fin 1's initial segment 15 sets up relatively, through setting up initial segment 15, guarantees that cooling fluid can be steady enter into in the heat dissipation channel.

Further, the start section 15 is provided at the air intake end of the fin 1, i.e., the left end as viewed in fig. 3.

Further, as shown in fig. 3, the start section 15 is horizontally disposed.

The fins 1 further comprise end sections 16, the end sections 16 are arranged on the downstream side of the corrugated sections along the flowing direction of the heat exchange fluid in the heat dissipation channel, the end sections 16 are arranged in parallel with the wave crests 11, the end sections 16 of the adjacent fins 1 are arranged oppositely, and the end sections 16 are arranged to ensure that the cooling fluid can be stably discharged out of the heat dissipation channel.

Further, the initial section 15 is provided at the discharge end of the fin 1, i.e., the right end as viewed in fig. 3.

Further, as shown in fig. 3, the end section 16 is horizontally disposed.

Specifically, in this embodiment, the corrugated section includes 3 peaks 11, 3 peaks 11 are located in the same plane, and the corrugated section includes 2

troughs

12, and 2 troughs 12 are located in the same plane.

Further, as shown in fig. 3, 3 peaks 11 are located in the same horizontal plane, and 2 valleys 12 are located in the same horizontal plane.

The heat exchanger comprises a heat exchange tube 2, wherein the heat exchange tube 2 is sleeved in the mounting hole 17 and the pipe sleeve 18, and the mounting hole 17 is arranged to provide a mounting position for the heat exchange tube 2.

Further, the inner wall of the mounting hole 17 is closely attached to the outer wall of the heat exchange tube 2.

Further, as shown in fig. 3, a tube sleeve 18 is provided on the upper surface of the fin 1.

The peripheral outer wall of one end, far away from the fin 1, of the pipe sleeve 18 is provided with a flanging structure 181, and the flanging structure 181 is perpendicular to the outer wall of the pipe sleeve 18, so that the adjacent pipe sleeves 18 are tightly attached to each other.

Further, adjacent sleeves are butted, and the flanging structures 181 are attached to the circumferences of the adjacent mounting holes 17.

In another aspect of the present embodiment, an air conditioner is provided, which includes the heat exchanger as described above.

Example 2

Referring to fig. 5 to 6 in combination, according to embodiment 2 of the present application, a difference from embodiment 1 is that a ripple section includes a first peak 11, a second peak 111, and a third peak 11, where the first peak 11, the second peak 111, and the third peak 11 are sequentially arranged along a flow direction of a heat transfer fluid in a heat dissipation channel, the first peak 11 and the third peak 11 are located in a first plane, the second peak 111 is located in a second plane, and the first plane is parallel to the second plane, that is, the second peak 111 is not located in the same plane as the first peak 11 and the second peak 111, which also can enhance disturbance of the heat transfer fluid in the heat dissipation channel, improve a convection heat transfer coefficient on the side of the fin 1, and enhance a heat transfer effect on the side of the fin 1, thereby improving a heat transfer performance and an energy efficiency ratio of the entire heat exchanger.

Furthermore, the second wave crest 111 is located on one side of the first plane close to the wave trough 12, so that the air circulation channel is widened, the pressure drop of the air flow is reduced, the heat exchange capacity of the heat exchanger is improved, and the total pressure drop is reduced.

It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.

The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed. The foregoing is only a preferred embodiment of the present application, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present application, and these modifications and variations should also be considered as the protection scope of the present application.

Claims

1. A heat exchanger is characterized by comprising a fin (1), wherein the fin (1) comprises a corrugated section, the corrugated section extends in a corrugated shape, wave crests (11) of the corrugated section are planes, and the extending direction of the wave crests (11) is the same as that of the corrugated section;

the heat exchanger comprises at least two fins (1), a heat dissipation channel is formed between the adjacent fins (1), and wave crests (11) of the adjacent fins (1) are arranged oppositely.

2. The heat exchanger according to claim 1, wherein the corrugated section comprises at least one of the wave crests (11), the corrugated section further comprising a first ramp (13) and a second ramp (14), the first ramp (13) being disposed at a first end of the wave crest (11), the second ramp (14) being disposed at a second end of the ramp, the first ramp (13) being disposed at an obtuse angle to the wave crest (11), and the second ramp (14) being disposed at an obtuse angle to the wave crest (11).

3. A heat exchanger according to claim 2, characterised in that the angle of the first slope surface (13) to the wave crest (11) is 120-165 ° and/or the angle of the second slope surface (14) to the wave crest (11) is 120-165 °.

4. A heat exchanger according to claim 2, characterised in that the direction of extension of the wave crests (11) is a first direction;

the projection of the first slope (13) in the plane of the peak (11) is a first projection, and the length of the first projection along the first direction is greater than that of the peak (11); and/or the projection of the second slope (14) in the plane of the peak (11) is a second projection, and the length of the second projection along the first direction is greater than the length of the peak (11) along the first direction.

5. A heat exchanger according to claim 2, characterized in that the first ramp surface (13) and the second ramp surface (14) are arranged symmetrically with respect to a perpendicular bisector of the crest (11).

6. The heat exchanger according to claim 1, characterized in that the valleys (12) of the corrugated section are plane surfaces, the valleys (12) being arranged in parallel with the peaks (11).

7. The heat exchanger according to claim 6, characterized in that the crests (11) and troughs (12) are of the same length in the direction of extension of the crests (11).

8. The heat exchanger according to claim 1, characterized in that the fins (1) further comprise an initial section (15), the initial section (15) being arranged on an upstream side of the corrugated section in a flow direction of the heat exchange fluid in the heat dissipation channel, the initial section (15) being arranged in parallel with the wave crest (11), the initial sections (15) of adjacent fins (1) being arranged opposite.

9. The heat exchanger according to claim 1, wherein the fins (1) further comprise end sections (16), the end sections (16) being disposed on a downstream side of the corrugated sections in a flow direction of the heat exchange fluid in the heat dissipation channel, the end sections (16) being disposed in parallel with the crests (11), the end sections (16) of adjacent fins (1) being disposed opposite to each other.

10. The heat exchanger according to claim 1, characterized in that the corrugated section comprises 3 of the peaks (11), 3 of the peaks (11) lying in the same plane, and 2 of the troughs (12), 2 of the troughs (12) lying in the same plane.

11. The heat exchanger according to claim 1, wherein the corrugated section comprises a first crest (11), a second crest (111), and a third crest (11), the first crest (11), the second crest (111), and the third crest (11) are arranged in sequence along a flow direction of the heat exchange fluid in the heat dissipation channel, the first crest (11) and the third crest (11) are located in a first plane, the second crest (111) is located in a second plane, and the first plane is parallel to the second plane.

12. A heat exchanger according to claim 11, characterised in that the second wave crests (111) are located on the side of the first plane adjacent to the wave troughs (12).

13. The heat exchanger according to claim 1, characterized in that the fin (1) is provided with a mounting hole (17), the mounting hole (17) is provided with a pipe sleeve (18), the pipe sleeve (18) is coaxially arranged with the mounting hole (17), and the heat exchanger comprises a heat exchange pipe (2), and the heat exchange pipe (2) is sleeved in the mounting hole (17) and the pipe sleeve (18).

14. The heat exchanger according to claim 13, characterized in that the circumferential outer wall of the end of the pipe sleeve (18) remote from the fin (1) is provided with a flanging structure (181), and the flanging structure (181) is arranged perpendicular to the outer wall of the pipe sleeve (18).

15. An air conditioner characterized by comprising the heat exchanger according to any one of claims 1 to 14.