CN218495918U

CN218495918U - Heat exchange tube and heat exchanger

Info

Publication number: CN218495918U
Application number: CN202221944743.0U
Authority: CN
Inventors: 武永强; 王小勇; 岳清学; 卢杏斌
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-07-25
Filing date: 2022-07-25
Publication date: 2023-02-17
Anticipated expiration: 2032-07-25

Abstract

The utility model discloses a heat exchange tube and heat exchanger. The heat exchange tube includes body and two at least spiral vortex structures, adjacent two form the fluid flow way between the spiral vortex structure, spiral vortex structure includes a plurality of vortex teeth that are the heliciform and distribute. The utility model discloses a heat exchange tube and heat exchanger through set up the interval between the vortex tooth, under the prerequisite of guaranteeing intraductal heat transfer area, can make partial fluid can carry out the cross flow through the interval and take place the secondary vortex, the inside turbulent degree of effectual reinforcing body utilizes the interval to form sharp portion on with the vortex tooth moreover, and this sharp portion can pierce through the boundary layer, effectively reduces the flow resistance, improves heat exchange efficiency. The space faces to the side face of the turbulence tooth, so that fluid flowing in the space can scour the turbulence tooth to generate turbulence again, the fluid flows to generate turbulence, the turbulence and the damage of a boundary layer, and the method is particularly effective for the fluid with low Reynolds number and high viscosity.

Description

Heat exchange tube and heat exchanger

Technical Field

The utility model relates to a indirect heating equipment technical field, more specifically the theory that says so, it relates to a heat exchange tube and heat exchanger.

Background

The high-efficiency heat exchange tube is widely applied to various heat exchangers, the energy efficiency, the size and the cost of a heat exchange unit are directly influenced by the heat exchange performance, and the improvement of the performance of the heat exchange tube is particularly important under the requirements of energy conservation and emission reduction and double carbon at present. The heat exchange tube is a dividing wall type heat exchange element, and one fluid flows in the tube and exchanges heat with another fluid outside the tube through the tube wall. Therefore, to enhance heat exchange, internal teeth are usually added to the tube to reduce the heat transfer resistance in the tube. Conventional internal tooth structures are continuous thread structures with trapezoidal or triangular cross sections, and although they can increase the heat transfer area in the pipe and enhance the fluid disturbance in the pipe, they have limited capability of breaking the boundary layer, and can increase the flow resistance in the pipe and increase the pressure loss. Meanwhile, for fluids (such as ethylene glycol and the like) with high viscosity and low Reynolds number, the capacity of enhancing heat exchange by simply relying on the fluids is limited. Finally causing the problem of low heat exchange efficiency of the heat exchange tube.

SUMMERY OF THE UTILITY MODEL

The utility model discloses a heat exchange tube and heat exchanger has solved among the prior art continuous thread line structure to the fluid flow resistance too big and cause the pressure loss too big and heat exchange efficiency to promote limited problem.

The utility model discloses a heat exchange tube, including body and two at least spiral vortex structures, adjacent two form fluid flow channel between the spiral vortex structure, spiral vortex structure includes a plurality of vortex teeth that are the heliciform and distribute, and is same the spiral vortex is structural, adjacent two interval has between the vortex tooth, interval and adjacent two fluid flow channel intercommunication.

In two adjacent spiral vortex structures, the interval in one spiral vortex structure is towards the side of the vortex tooth in the other spiral vortex structure.

And the turbulence teeth are provided with flow passing grooves which are communicated with the adjacent two fluid flow channels.

The cross section of the overflow groove is triangular, and the angle range of the vertex angle beta of the triangle is 5-90 degrees; and/or the depth h3 of the overflow groove has a value ranging from 0.05mm to 0.5mm.

The width a of the space has a value ranging from 0.2mm to 4mm.

The cross-section of vortex tooth is triangle-shaped, follows spiral flow structure's helix direction, the height of vortex tooth is crescent or reduces gradually.

Spiral vortex structure includes first helical structure and second helical structure, first helical structure with the second helical structure interval set up in on the internal surface of body, it is adjacent first helical structure with form between the second helical structure fluid flow channel, and follow the same direction of spiral, in the first helical structure the height of vortex tooth increases gradually, in the second helical structure the height of vortex tooth reduces gradually.

The numerical range of the height h1 of the spoiler teeth in the first spiral structure is 0.25mm to 0.9mm; and/or the height h2 of the spoiler teeth in the second spiral structure ranges from 0.15mm to 0.8mm.

The vortex tooth have set up in bottom surface on the internal surface of body with keep away from the side edge of bottom surface, the side edge with the angular range of the contained angle theta between the plane in bottom surface place is 15 to 75.

Another aspect of the utility model provides a heat exchanger, including foretell heat exchange tube.

The utility model discloses a heat exchange tube and heat exchanger through set up the interval between the vortex tooth, under the prerequisite of guaranteeing intraductal heat transfer area, can make partial fluid carry out the cross flow through the interval and take place the secondary vortex, the inside turbulent degree of effectual reinforcing body utilizes the interval to form sharp portion on with the vortex tooth moreover, and this sharp portion can pierce through the boundary layer, effectively reduces the flow resistance, improves heat exchange efficiency. The intervals face the side of the turbulence teeth, so that fluid flowing in the intervals can scour the turbulence teeth to generate turbulence again, the fluid flows to generate turbulence, disturb and damage a boundary layer, the low Reynolds number and high-viscosity fluid are particularly effective, the spiral turbulence structures with different heights can further reduce fluid flow resistance, and pressure loss generated by the heat exchange tube is reduced.

Drawings

Fig. 1 is a schematic structural view of an inner surface of a heat exchange tube according to an embodiment of the present invention;

FIG. 2 is a schematic view of fluid flow within a heat exchange tube of an embodiment of the present invention;

fig. 3 is another schematic structural view of the inner surface of a heat exchange tube according to an embodiment of the present invention;

fig. 4 is a schematic structural view of a spoiler tooth according to an embodiment of the present invention;

fig. 5 is another schematic structural view of a spoiler tooth according to an embodiment of the present invention;

legend: 1. a pipe body; 2. a spiral flow disturbing structure; 3. a fluid flow passage; 4. turbulence teeth; 5. spacing; 6. a flow through groove; 7. a first helical structure; 8. a second helix.

Detailed Description

The present invention is further illustrated by the following examples, but is not limited to the contents of the specification.

As shown in fig. 1 to 5, the utility model provides a heat exchange tube, including body 1 and two at least spiral vortex structures 2, adjacent two form fluid flow channel 3 between the spiral vortex structure 2, spiral vortex structure 2 includes a plurality of vortex teeth 4 that are the heliciform and distribute, and is same on the spiral vortex structure 2, adjacent two interval 5 has between the vortex tooth 4, interval 5 and adjacent two fluid flow channel 3 communicates. After the fluid gets into body 1, the fluid can flow along fluid flow channel 3 under spiral vortex structure 2's water conservancy diversion effect, partial fluid can produce the cross flow in interval 5 simultaneously, thereby flow between two adjacent fluid flow channels 3, through set up interval 5 between vortex tooth 4, under the prerequisite of guaranteeing intraductal heat transfer area, can make partial fluid carry out the cross flow through interval 5 and take place the secondary vortex, the inside turbulent degree of effectual reinforcing body 1, and utilize interval 5 to form sharp portion on with vortex tooth 4, this sharp portion can pierce through the boundary layer, effectively reduce flow resistance, and the heat exchange efficiency is improved.

In two adjacent spiral vortex structures 2, one in spiral vortex structure 2 interval 5 is towards another in spiral vortex structure 2 the side of vortex tooth 4. Fluid flowing in the interval 5 can erode the turbulence teeth 4 to generate turbulence again, so that fluid flows to generate turbulence, disturbance and damage a boundary layer, the fluid is particularly effective for fluid with low Reynolds number and high viscosity, and the secondary turbulence generated by combining the spiral turbulence structure 2 and the interval 5 is used for realizing tertiary turbulence of the fluid and effectively improving the heat exchange efficiency of the heat exchange tube.

Wherein, the angle range of the helical angle alpha of the helical turbulent structure 2 is 0 degree to 80 degrees. Preferably 45. The quantity scope of spiral vortex structure 2 is 6 to 90, specifically confirms according to the length and the pipe diameter size of body 1.

The width b of the fluid channel 3 ranges from 0.15mm to 3mm, that is, the distance between two adjacent spiral turbulence structures 2 ranges from 0.15mm to 3mm.

And a flow passing groove 6 is formed in the turbulence teeth 4, and the flow passing groove 6 is communicated with the two adjacent fluid flow channels 3. The overflow groove 6 can increase the number of edges on the turbulence teeth 4, thereby increasing the effect of puncturing the fluid boundary layer and further increasing the turbulence effect of the turbulence teeth 4 on the fluid. The fluid that flows out in interval 5 can flow through vortex tooth 4 through overflow groove 6, further increases the vortex of vortex tooth 4 to the fluid and the effect of boundary layer destruction.

The cross-section of the overflow groove 6 is triangular, the triangular structure is a stable structure, the structure stability of the turbulence teeth 4 is ensured in the process of flushing the fluid, so that the turbulence effect in the heat exchange tube is ensured, wherein the angle range of the vertex angle beta of the triangular structure is 5-90 degrees.

The depth h3 of the overflow groove 6 ranges from 0.05mm to 0.5mm. The overflow groove 6 is prevented from being too deep to influence the structural strength of the turbulence teeth 4, and meanwhile, the overflow groove 6 is prevented from being too shallow to realize the turbulence effect on fluid.

The number of the overflowing grooves 6 ranges from 1 to 3, and is specifically determined according to the length of the disturbing flow teeth 4.

The width a of the spacing 5 has a value in the range of 0.2mm to 4mm. The spiral turbulence structure 2 that the 5 too big intervals can make 4 spoilers form can't carry out reliable vortex to the fluid, and when 5 intervals were too little, the fluid can't flow through 5 intervals, and then can't utilize 5 intervals to carry out the vortex.

The cross-section of vortex tooth 4 is triangle-shaped, follows spiral vortex structure 2's helix direction, vortex tooth 4's height crescent or diminish gradually. Through the change of height for vortex tooth 4 can carry out the vortex to the fluid of different positions, makes the boundary layer obtain all-round destruction, smashes, and then increases vortex effect of vortex tooth 4, makes intraductal heat transfer obtain fully improving.

Preferably, the cross-section of the spoiler tooth 4 is isosceles triangle, so that fluid can enter from any end of the pipe body 1 to obtain a good spoiler heat exchange effect.

Spiral vortex structure 2 includes first helical structure 7 and second helical structure 8, first helical structure 7 with second helical structure 8 interval set up in on the internal surface of body 1, it is adjacent first helical structure 7 with form between the second helical structure 8 fluid flow channel 3, and follow the same spiral direction, in the first helical structure 7 vortex tooth 4's height increases gradually, in the second helical structure 8 vortex tooth 4's height reduces gradually. That is, the arrangement direction of the turbulence teeth 4 in the first spiral structure 7 is opposite to the arrangement direction of the turbulence teeth 4 in the second spiral structure 8, when the fluid passes through the turbulence teeth 4 in the first spiral structure 7 and the turbulence teeth 4 in the second spiral structure 8, the fluid can fluctuate, and collide along with the change of height, so that the flow of a multi-dimensional and full-flow field is formed, the flow line of the fluid in the whole pipe body 1 can generate omnibearing disturbance, the turbulence degree of the fluid is greatly improved, the boundary layer of the fluid is damaged and crushed in an omnibearing manner, and the heat exchange in the pipe is fully improved.

Specifically, the height h1 of the spoiler teeth 4 in the first helical structure 7 ranges from 0.25mm to 0.9mm.

Specifically, the height h2 of the spoiler teeth 4 in the second spiral structure 8 ranges from 0.15mm to 0.8mm.

The spoiler teeth 4 are provided with bottom surfaces arranged on the inner surface of the pipe body 1 and side edges far away from the bottom surfaces, and the angle range of an included angle theta between the side edges and the plane where the bottom surfaces are located is 15-75 degrees. The height difference between the two ends of the turbulence teeth 4 is adjusted by adjusting the included angle theta, so that the turbulence effect of the turbulence teeth 4 on fluid is adjusted. Meanwhile, the heights of two side faces forming the interval 5 can be controlled, the shape of the interval 5 is further controlled, and the turbulence effect of the interval 5 on fluid is increased.

It is to be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. Not all embodiments are exhaustive. All obvious changes or variations led out by the technical scheme of the utility model are still in the protection scope of the utility model.

Claims

1. A heat exchange tube, its characterized in that: including body (1) and two at least spiral vortex structures (2), adjacent two form fluid flow channel (3) between spiral vortex structure (2), spiral vortex structure (2) are including a plurality of vortex teeth (4) that are heliciform and distribute, and are same on spiral vortex structure (2), adjacent two interval (5) have between vortex tooth (4), interval (5) and adjacent two fluid flow channel (3) intercommunication.

2. The heat exchange tube of claim 1, wherein: in two adjacent spiral vortex structures (2), one in spiral vortex structure (2) interval (5) are towards another in spiral vortex structure (2) the side of vortex tooth (4).

3. The heat exchange tube of claim 1, wherein: and the turbulence teeth (4) are provided with flow passing grooves (6), and the flow passing grooves (6) are communicated with the adjacent two fluid flow channels (3).

4. A heat exchange tube according to claim 3, wherein: the cross section of the overflow groove (6) is triangular, and the angle range of the vertex angle beta of the triangle is 5-90 degrees; and/or the depth h3 of the overflow groove (6) has a value ranging from 0.05mm to 0.5mm.

5. The heat exchange tube of claim 1, wherein: the width a of the spacing (5) has a value in the range of 0.2mm to 4mm.

6. The heat exchange tube of claim 1, wherein: the cross section of each turbulence tooth (4) is triangular, and the height of each turbulence tooth (4) is gradually increased or reduced along the spiral line direction of the spiral turbulence structure (2).

7. The heat exchange tube of claim 6, wherein: spiral vortex structure (2) include first helical structure (7) and second helical structure (8), first helical structure (7) with second helical structure (8) interval set up in on the internal surface of body (1), adjacent first helical structure (7) with form between second helical structure (8) fluid flow channel (3), and follow the same spiral direction, in first helical structure (7) the height of vortex tooth (4) increases gradually, in second helical structure (8) the height of vortex tooth (4) reduces gradually.

8. The heat exchange tube of claim 7, wherein: the height h1 of the turbulence teeth (4) in the first spiral structure (7) is within a numerical range of 0.25mm to 0.9mm; and/or the height h2 of the spoiler teeth (4) in the second helical structure (8) ranges from 0.15mm to 0.8mm.

9. The heat exchange tube of claim 6, wherein: the vortex tooth (4) have set up in bottom surface on the internal surface of body (1) and keep away from the side edge of bottom surface, the side edge with the angular range of the contained angle theta between the plane in bottom surface place is 15 to 75.

10. A heat exchanger, characterized by: comprising the heat exchange tube of any one of claims 1 to 9.