CN112944992A - Heat exchange tube, heat exchanger and air conditioner - Google Patents
Heat exchange tube, heat exchanger and air conditioner Download PDFInfo
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- CN112944992A CN112944992A CN201911260055.5A CN201911260055A CN112944992A CN 112944992 A CN112944992 A CN 112944992A CN 201911260055 A CN201911260055 A CN 201911260055A CN 112944992 A CN112944992 A CN 112944992A
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- exchange tube
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- side tooth
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- 238000001704 evaporation Methods 0.000 claims description 32
- 230000008020 evaporation Effects 0.000 claims description 32
- 238000000034 method Methods 0.000 claims description 4
- 239000012530 fluid Substances 0.000 abstract description 53
- 230000001965 increasing effect Effects 0.000 abstract description 14
- 238000005728 strengthening Methods 0.000 abstract description 5
- 230000000694 effects Effects 0.000 description 18
- 238000009833 condensation Methods 0.000 description 17
- 230000005494 condensation Effects 0.000 description 17
- 239000002184 metal Substances 0.000 description 14
- 238000012546 transfer Methods 0.000 description 13
- 239000003507 refrigerant Substances 0.000 description 8
- 238000009825 accumulation Methods 0.000 description 6
- 230000009286 beneficial effect Effects 0.000 description 5
- 239000010408 film Substances 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 230000002708 enhancing effect Effects 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000003313 weakening effect Effects 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000003014 reinforcing effect Effects 0.000 description 2
- 238000009834 vaporization Methods 0.000 description 2
- 230000008016 vaporization Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 241000791841 Alectis ciliaris Species 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000011552 falling film Substances 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
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- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a heat exchange tube, a heat exchanger and an air conditioner, wherein the heat exchange tube comprises: the pipe base member (1) and tooth main part (2) of setting on pipe base member (1) inner wall, the upper end of tooth main part (2) sets up relative side tooth (3) that set up more than two, including relative first side tooth (31) and the second side tooth (32) that set up, the top of first side tooth (31) is towards the direction that deviates from second side tooth (32) and is extended, the top of second side tooth (32) is towards the direction that deviates from first side tooth (31) extends. The side tooth tip part can effectively destroy the boundary layer and strengthen the turbulence degree of the fluid, when the non-phase-change fluid flows through the inner wall of the heat exchange tube, the fluid boundary layer at the position close to the wall surface of the heat exchange tube is fully destroyed, the thermal resistance is reduced, the heat exchange is enhanced, the PEC coefficient in the tube is effectively increased by the tooth shape which improves the strengthening performance in the tube and reduces the pressure drop of the fluid, and the heat exchange in the tube is strengthened.
Description
Technical Field
The invention belongs to the technical field of heat exchange, and particularly relates to a heat exchange tube, a heat exchanger and an air conditioner.
Background
Heat exchange tubes are used primarily to facilitate heat exchange between a fluid on one side of the tube and a fluid on the other side of the tube, and are commonly used in various heat transfer devices such as flooded evaporators, falling film evaporators, condensers and dry evaporators, absorption chillers, and single phase coolers and heaters used in the refrigeration, petrochemical, and food processing industries. Water, aqueous glycol solutions, refrigerants (e.g., R134a, R410A, etc.), ammonia, petrochemical liquids, and other mixtures, etc. are used in these applications.
When heat is transferred through the heat exchange tube, there is always a certain resistance, which is called heat transfer resistance. The total thermal resistance of the heat exchange tube is the sum of thermal resistances of the inside and outside of the tube, the wall of the tube and dirt, and in order to improve the heat transfer efficiency, the heat exchange is always enhanced by various methods to reduce the thermal resistance, such as increasing the heat exchange area inside and outside the tube, and the like. In order to reduce the thermal resistance in the tube and enhance the heat exchange in the tube, a common method is to process thread-shaped protrusions in the tube. Through the thread-shaped bulges (internal teeth) in the tube, the disturbance of fluid in the tube can be enhanced, the fluid heat transfer boundary layer is damaged, and the heat transfer area is increased, so that the heat exchange of the tube side can be enhanced, the heat resistance in the tube is reduced, and the total heat exchange capacity of the heat exchange tube is improved. For the application of phase change heat transfer in the pipe, the thread-shaped internal teeth can also improve the wettability in the pipe and increase the vaporization core, thereby promoting the phase change heat exchange in the pipe.
However, the thread-shaped internal teeth are simple in structure and can only promote fluid disturbance once, heat exchange tube manufacturers often enhance disturbance by adjusting structural parameters of the thread-shaped internal teeth to promote heat transfer, and the enhancement effect is limited after all. For the requirement of the design of the 'high-efficiency energy-saving' heat exchanger, the heat exchange efficiency is further improved, the heat exchange efficiency needs to be continuously improved for heat exchange in the pipe, the shape and the structure of the thread-shaped internal teeth in the pipe need to be changed, and the disturbance and the like in the pipe are further enhanced.
The heat exchange tube in the prior art has limited reinforcing effect on the heat exchange effect due to the one-time disturbance of the inner teeth of the single thread, and the heat resistance in the tube needs to be further reduced under the design requirement of the high-efficiency energy-saving heat exchanger, so that the heat transfer capacity of the heat exchange tube is enhanced, and the like.
Disclosure of Invention
Therefore, the invention aims to solve the technical problem of overcoming the defect that the heat exchange tube in the prior art has limited reinforcing effect on the heat exchange effect due to single-thread internal tooth one-time disturbance, and provides a heat exchange tube, a heat exchanger and an air conditioner.
The present invention provides a heat exchange tube, comprising:
the pipe base member with set up the tooth main part on the pipe base member inner wall, the upper end of tooth main part sets up the relative side tooth that sets up more than two, including relative first side tooth and the second side tooth that sets up, the top of first side tooth towards deviate from the direction of second side tooth extends, the top of second side tooth towards deviate from the direction of first side tooth extends.
Preferably, the first and second electrodes are formed of a metal,
the tooth main body and the two side teeth form Y-shaped teeth with Y-shaped longitudinal sections; and/or the free end of the first side tooth and/or the second side tooth is a tip.
Preferably, the first and second electrodes are formed of a metal,
the tooth main body and the side teeth form a tooth unit, the number of the tooth units is more than two, and in two adjacent tooth units, a semi-closed evaporation cavity is formed between a first side tooth in one tooth unit and a second side tooth in the other tooth unit.
Preferably, the first and second electrodes are formed of a metal,
in the cross section of the pipe base body, 6-90 tooth units are arranged along the circumferential direction, and the circumferential distance is 0.1-6 mm; and/or the thickness L of the tooth main body is 0.2-5 mm; and/or the crest angle theta of the first side tooth and the second side tooth is 0.05-180 degrees; and/or the height h1 of the tooth main body is 0.15-0.6 mm; and/or the height h2 of the side teeth is 0.05-0.45 mm.
Preferably, the first and second electrodes are formed of a metal,
the plurality of tooth units are arranged on the inner wall of the pipe base body along a spiral line to form a group of spiral teeth.
Preferably, the first and second electrodes are formed of a metal,
in each row of the spiral teeth, a plurality of the tooth units are arranged in sequence in a discontinuous mode, and a groove is formed between every two adjacent tooth units.
Preferably, the first and second electrodes are formed of a metal,
the overall height h3 of the groove is 0.15-0.6 mm; and/or the width of the groove is 0.1-3.0 mm.
Preferably, the first and second electrodes are formed of a metal,
the helical angle beta of the helical teeth is 0-75 degrees, and/or a plurality of rows of helical teeth are arranged on the outer wall of the tube base body in an upward row and are arranged at intervals.
The invention also provides a heat exchanger which comprises the heat exchange tube in any one of the preceding items.
The invention also provides an air conditioner, which comprises the heat exchange tube or the heat exchanger.
The heat exchange tube, the heat exchanger and the air conditioner provided by the invention have the following beneficial effects:
1. according to the invention, two side teeth extending towards two different directions are formed on the tooth main body, the inner teeth are Y-shaped, the fins extend towards two sides, and the grooves are formed in the top, so that the internal flowing fluid can be further disturbed, the tip parts of the side teeth can effectively destroy boundary layers and strengthen the turbulence degree of the fluid, when the non-phase-change fluid flows through the inner wall of the heat exchange tube, the fluid boundary layer at the position close to the wall surface of the heat exchange tube is fully destroyed, the thermal resistance is reduced, and the heat exchange is enhanced, the PEC coefficient in the tube is effectively increased by the tooth shape for improving the strengthening performance in the tube and reducing the pressure drop of the fluid, the heat exchange in the tube is strengthened, the heat exchange is not required to be enhanced by increasing the flow velocity in the prior art; the Y-shaped threaded rack is provided with the interrupted tooth grooves, so that an additional path for fluid flow is further increased, the mixing of the fluid is enhanced, and the accumulation of a boundary layer of the fluid close to the inner surface of the pipe is reduced. The interrupted Y-shaped reinforced internal tooth surface can effectively increase the heat exchange area, and make the fluid generate five times of disturbance in the pipe, thus intensifying the turbulence degree and weakening the accumulation degree of the boundary layer, thus greatly enhancing the heat exchange capability of the internal tooth of the common thread.
2. The evaporation cavity is formed on the inner wall of the heat exchange tube through the adjacent side teeth in the two adjacent tooth units, so that the effect of increasing the density of the evaporation cavity on the heat exchange tube (the density of the evaporation cavity on the heat exchange tube with the same area is increased), the evaporation of a refrigerant is facilitated, and the evaporation strengthening efficiency of the heat exchange tube is improved; in the condensation working condition, the two side teeth with the sharp-end (thorn-shaped) structures are beneficial to puncturing a refrigerant liquid film, so that the condensation heat exchange effect is improved; meanwhile, the discharge of condensate is facilitated in the circumferential direction under the condensation working condition, and the thermal resistance of the pipe wall is reduced; therefore, the evaporation heat exchange efficiency of the heat exchange tube and the condensation heat exchange efficiency of the heat exchange tube can be improved under both the heating working condition and the refrigerating working condition.
Drawings
FIG. 1 is a partial three-dimensional block diagram of a heat exchange tube of the present invention;
FIG. 2 is a partially enlarged schematic view of a portion O of FIG. 1;
FIG. 3 is a cross-sectional view of the heat exchange tube of the present invention in an axial direction;
FIG. 4 is a partially enlarged structural view of a portion A in FIG. 3;
FIG. 5 is a partially enlarged structural view of a portion B in FIG. 3;
FIG. 6 is a partial three-dimensional block diagram of the heat exchange tube of the present invention (alternate embodiment);
fig. 7 is a partially enlarged schematic view of a portion C in fig. 6.
The reference numbers in the figures denote:
1. a tube base; 2. a tooth body; 3. side teeth; 31. a first side tooth; 32. a second side tooth; 4. an evaporation chamber; 5. and (4) a groove.
Detailed Description
As shown in fig. 1 to 7, the present invention provides a heat exchange tube comprising:
pipe base member 1 is in with the setting tooth main part 2 on the pipe base member 1 inner wall, the upper end of tooth main part 2 sets up the relative side tooth 3 that sets up more than two, including relative first side tooth 31 and the second side tooth 32 that sets up, the top of first side tooth 31 towards deviating from the direction of second side tooth 32 is extended the top of second side tooth 32 towards deviating from the direction of first side tooth 31 is extended
According to the invention, two side teeth extending towards two different directions are formed on the tooth main body, the inner teeth are Y-shaped, the fins extend towards two sides, and the grooves are formed in the top, so that the flow of the internal flowing fluid can be further disturbed, the tip parts of the fins can effectively destroy the boundary layer and strengthen the turbulence degree of the fluid, when the non-phase-change fluid flows through the inner wall of the heat exchange tube, the fluid boundary layer at the position close to the wall surface of the heat exchange tube is fully destroyed, the thermal resistance is reduced, and the heat exchange is enhanced.
Preferably, the first and second electrodes are formed of a metal,
the tooth main body 2 and the two side teeth 3 are formed into Y-shaped teeth with Y-shaped longitudinal sections; and/or the free end of the first side tooth 31 and/or the second side tooth 32 is a tip. The tooth main body and the side teeth form an optimal structure form, the tip parts of the fins can effectively destroy a boundary layer and strengthen the turbulence degree of fluid, and when non-phase-change fluid flows through the inner wall of the heat exchange tube, the fluid boundary layer at the position of the heat exchange tube close to the wall surface is fully destroyed, so that the thermal resistance is reduced, and the heat exchange is enhanced.
Preferably, the first and second electrodes are formed of a metal,
the tooth main body 2 and the side teeth 3 are formed into one tooth unit, the tooth unit is more than two, and in two adjacent tooth units, a semi-closed evaporation cavity 4 is formed between a first side tooth 31 in one tooth unit and a second side tooth 32 in the other tooth unit.
The evaporation cavity is formed on the inner wall of the heat exchange tube through the adjacent side teeth in the two adjacent tooth units, so that the effect of increasing the density of the evaporation cavity on the heat exchange tube (the density of the evaporation cavity on the heat exchange tube with the same area in distribution) is achieved during phase change heat exchange, the evaporation of a refrigerant is facilitated greatly, and the evaporation strengthening efficiency of the heat exchange tube is improved; in the condensation working condition, the two side teeth with the sharp-end (thorn-shaped) structures are beneficial to puncturing a refrigerant liquid film, so that the condensation heat exchange effect is improved; meanwhile, the discharge of condensate is facilitated in the circumferential direction under the condensation working condition, and the thermal resistance of the pipe wall is reduced; therefore, the evaporation heat exchange efficiency of the heat exchange tube and the condensation heat exchange efficiency of the heat exchange tube can be improved under both the heating working condition and the refrigerating working condition.
Preferably, the first and second electrodes are formed of a metal,
in the cross section of the pipe base body, 6-90 tooth units are arranged along the circumferential direction, and the circumferential distance is 0.1-6 mm; and/or the thickness L of the tooth main body 2 is 0.2-5 mm; and/or the crest angle theta of the first side tooth 31 and the second side tooth 32 is 0.05-180 degrees; and/or the height h1 of the tooth main body 2 is 0.15-0.6 mm; and/or the height h2 of the side teeth is 0.05-0.45 mm. This is the preferred dimensional relationship of the tooth crest height, thickness and included angle of the tooth unit, tooth body of the present invention, and can effectively increase the space volume of the evaporation chamber between the side teeth, and cannot make the distance between the tooth crests too small to allow the fluid to enter the evaporation chamber.
Preferably, the first and second electrodes are formed of a metal,
the plurality of tooth units are arranged on the inner wall of the pipe base body 1 along a spiral line to form a group of spiral teeth. The spiral teeth form can enable the outer wall of the heat exchange tube to generate the effect of heat exchange enhancement on fluid along the spiral line, namely, a plurality of evaporation cavities arranged along the spiral line are provided during evaporation, and a plurality of fin tips arranged along the spiral line during condensation, so that the heat exchange effect on the fluid including evaporation and condensation can be respectively enhanced.
Preferably, the first and second electrodes are formed of a metal,
in an alternative embodiment (see fig. 6-7), in each row of the helical teeth, a plurality of the tooth units are arranged in sequence at intervals, and a groove 5 is formed between two adjacent tooth units. The spiral teeth form can enable the outer wall of the heat exchange tube to generate the effect of heat exchange enhancement on fluid along the spiral line, namely, a plurality of evaporation cavities arranged along the spiral line are provided during evaporation, and a plurality of puncture tips arranged along the spiral line during condensation, so that the heat exchange effect on the fluid including evaporation and condensation can be respectively enhanced. The Y-shaped threaded rack is provided with the interrupted tooth grooves, so that an additional path for fluid flow is further increased, the mixing of the fluid is enhanced, and the accumulation of a boundary layer of the fluid close to the inner surface of the pipe is reduced. The interrupted Y-shaped reinforced internal tooth surface can effectively increase the heat exchange area, and make the fluid generate five times of disturbance in the pipe, thus intensifying the turbulence degree and weakening the accumulation degree of the boundary layer, thus greatly enhancing the heat exchange capability of the internal tooth of the common thread.
Preferably, the first and second electrodes are formed of a metal,
the overall height h3 of the groove 5 is 0.15-0.6 mm; and/or the width of the groove is 0.1-3.0 mm. The discontinuous internal tooth structure changes the flow pattern of the fluid of the heat exchange tube, and compared with continuous internal thread teeth, the internal tooth structure changes the flow pattern of the fluid from two-dimensional flow to three-dimensional flow, greatly enhances the turbulence degree of the fluid and strengthens heat exchange. Meanwhile, the discontinuity of the teeth reduces the resistance of the inner wall to fluid and the pressure drop of the inlet and the outlet of the single tube, and the discontinuous teeth reduce the weight of a single heat exchange tube relative to continuous teeth and reduce the cost of the heat exchange tube.
Preferably, the first and second electrodes are formed of a metal,
the helix angle beta of the helical teeth is 0-75 degrees, and/or the outer wall of the tube base body 1 is provided with a plurality of rows of helical teeth which are arranged at intervals. The spiral teeth are arranged at intervals, so that the effect of flow resistance is formed on the fluid at intervals, and the rotary flow is formed, and the evaporation heat exchange effect and the condensation heat exchange effect of the fluid along the axial direction are further improved.
The invention also provides a heat exchanger which comprises the heat exchange tube in any one of the preceding items. According to the invention, the two side teeth extending towards two different directions are formed on the tooth main body, the evaporation cavity can be formed on the inner wall of the heat exchange tube through the adjacent side teeth in the two adjacent tooth units, so that the effect of increasing the density of the evaporation cavity on the heat exchange tube (the density of the evaporation cavity on the heat exchange tube with the same area is increased) is achieved, the refrigerant evaporation is facilitated greatly, and the evaporation strengthening efficiency of the heat exchange tube is improved; in the condensation working condition, the two side teeth with the sharp-end (thorn-shaped) structures are beneficial to puncturing a refrigerant liquid film, so that the condensation heat exchange effect is improved; meanwhile, the discharge of condensate is facilitated in the circumferential direction under the condensation working condition, and the thermal resistance of the pipe wall is reduced; therefore, the evaporation heat exchange efficiency of the heat exchange tube and the condensation heat exchange efficiency of the heat exchange tube can be improved under both the heating working condition and the refrigerating working condition.
The invention also provides an air conditioner, which comprises the heat exchange tube or the heat exchanger.
The invention is realized by adopting the following scheme: the heat exchange tube with the interrupted Y-shaped reinforced internal teeth comprises a tube body of a heat transfer tube and fins (namely a tooth main body) on the inner side of the tube body, wherein the fins are spirally wound in the tube body along the axial direction, the roots of the fins are connected with the tube body into a whole, the tooth main body and side teeth form a Y shape, and gaps are formed in the circumferential direction of the fins; the Y-shaped thread fin is provided with a discontinuous fin groove along the thread. In order to enhance the heat exchange in the pipe, the internal teeth of the internal thread of the pipe are usually adopted to enhance the disturbance and destroy the boundary layer, but the enhancement effect of the heat exchange effect is limited by only one-time disturbance of the internal teeth of the single thread, and the heat resistance in the pipe needs to be further reduced under the design requirement of a high-efficiency energy-saving heat exchanger, so that the heat transfer capacity of the heat exchange pipe is enhanced. The invention aims to provide a novel reinforced heat exchange tube with a tooth-shaped structure in the tube, which can further enhance the heat exchange in the tube.
The invention has the following beneficial effects: the internal teeth have a certain spiral angle with the axial direction, a certain number of threaded racks can enable fluid to spirally rotate in the pipe, so that disturbance is enhanced, the internal teeth with a certain height can also damage a boundary layer, and the heat exchange area is increased, so that heat exchange is enhanced; in addition, the internal teeth are Y-shaped, the top of each fin is provided with a Y-shaped fin, the fins extend towards two sides, the top of each fin is provided with a groove, the flow of the fluid flowing inside can be further disturbed, and the tip of each fin can effectively destroy a boundary layer and strengthen the turbulence degree of the fluid; furthermore, the Y-shaped thread rack is provided with the interrupted tooth grooves, so that an additional path for fluid flow is increased, the mixing of the fluid is enhanced, and the accumulation of a boundary layer of the fluid close to the inner surface of the pipe is reduced. The interrupted Y-shaped reinforced internal tooth surface can effectively increase the heat exchange area, and make the fluid generate five times of disturbance in the pipe, thus intensifying the turbulence degree and weakening the accumulation degree of the boundary layer, thus greatly enhancing the heat exchange capability of the internal tooth of the common thread.
In phase change heat transfer, the Y-shaped internal teeth can also provide an evaporation and vaporization core and effectively pierce a condensate film, so that the phase change heat transfer performance of the refrigerant in the pipe is promoted. When fluid in the pipe passes through the Y-shaped internal teeth in the pipe, the fluid is firstly disturbed in a rotating way along a spiral line to enhance turbulent flow, and the Y-shaped internal teeth with a certain height can destroy a boundary layer; two small fins of the Y-shaped internal teeth can further disturb the fluid for many times, and the sharp small fins can effectively pierce a boundary layer and prevent the fluid in the boundary layer from being accumulated; the discontinuous grooves on the spiral line can also enable fluid to flow in a cross mode, the fluid is violently collided when flowing through the grooves, the turbulence degree is further enhanced, the heat exchange efficiency in the pipe is enhanced, the thermal resistance in the pipe is reduced, and therefore the total heat exchange efficiency of the heat exchange pipe can be improved.
In a specific embodiment, the inner diameter of the heat exchange tube is 16.4mm, the number of the Y-shaped inner teeth is 45, the overall height h1 is 0.4mm, and the height h2 of the Y-shaped fins is 0.15 mm; the thickness of the fin is 0.3mm, the angle theta of the fin is 60 degrees, and the helical angle beta is 45 degrees; the distance between the grooves on the spiral line is 1mm, and the height of the grooves is 0.3 mm. When the pipe is used for single-phase heat transfer of water in the pipe, the heat exchange performance of the pipe type is improved by about 30 percent compared with that of a common threaded internal gear pipe with the same parameters through tests.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, 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 invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (10)
1. A heat exchange tube, its characterized in that: the method comprises the following steps:
the pipe base member (1) and setting are in tooth main part (2) on pipe base member (1) inner wall, the upper end of tooth main part (2) sets up relative side tooth (3) that sets up more than two, including relative first side tooth (31) and the second side tooth (32) that set up, the top of first side tooth (31) towards deviate from the direction of second side tooth (32) extend the top of second side tooth (32) towards deviate from the direction of first side tooth (31) extends.
2. The heat exchange tube of claim 1, wherein:
the tooth main body (2) and the two side teeth (3) are formed into Y-shaped teeth with Y-shaped longitudinal sections; and/or the free end of the first side tooth (31) and/or the second side tooth (32) is pointed.
3. A heat exchange tube according to claim 1 or 2, wherein:
the tooth main body (2) and the side teeth (3) form a tooth unit, the number of the tooth units is more than two, and in two adjacent tooth units, a semi-closed evaporation cavity (4) is formed between a first side tooth (31) in one tooth unit and a second side tooth (32) in the other tooth unit.
4. A heat exchange tube according to claim 3, wherein:
in the cross section of the pipe base body, 6-90 tooth units are arranged along the circumferential direction, and the circumferential distance is 0.1-6 mm; and/or the thickness L of the tooth main body (2) is 0.2-5 mm; and/or the crest angle theta of the first side tooth (31) and the second side tooth (32) is 0.05-180 DEG; and/or the height h1 of the tooth main body (2) is 0.15-0.6 mm; and/or the height h2 of the side teeth is 0.05-0.45 mm.
5. A heat exchange tube according to any one of claims 3 to 4, wherein:
the plurality of tooth units are arranged on the inner wall of the pipe base body (1) along a spiral line to form a group of spiral teeth.
6. The heat exchange tube of claim 5, wherein:
in each row of helical teeth, a plurality of tooth units are arranged in sequence in a discontinuous mode, and a groove (5) is formed between every two adjacent tooth units.
7. The heat exchange tube of claim 6, wherein:
the overall height h3 of the groove (5) is 0.15-0.6 mm; and/or the width of the groove is 0.1-3.0 mm.
8. The heat exchange tube of claim 5, wherein:
the spiral angle beta of the spiral teeth is 0-75 degrees, and/or a plurality of rows of spiral teeth are arranged on the outer wall of the tube base body (1) at intervals.
9. A heat exchanger, characterized by: comprising the heat exchange tube of any one of claims 1-8.
10. An air conditioner, characterized in that: comprising the heat exchange tube of any one of claims 1-8 or the heat exchanger of claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911260055.5A CN112944992A (en) | 2019-12-10 | 2019-12-10 | Heat exchange tube, heat exchanger and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911260055.5A CN112944992A (en) | 2019-12-10 | 2019-12-10 | Heat exchange tube, heat exchanger and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112944992A true CN112944992A (en) | 2021-06-11 |
Family
ID=76225764
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911260055.5A Pending CN112944992A (en) | 2019-12-10 | 2019-12-10 | Heat exchange tube, heat exchanger and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112944992A (en) |
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2019
- 2019-12-10 CN CN201911260055.5A patent/CN112944992A/en active Pending
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