CN100554856C - A kind of intensify heat transfer pipe - Google Patents
A kind of intensify heat transfer pipe Download PDFInfo
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- CN100554856C CN100554856C CNB2008100196859A CN200810019685A CN100554856C CN 100554856 C CN100554856 C CN 100554856C CN B2008100196859 A CNB2008100196859 A CN B2008100196859A CN 200810019685 A CN200810019685 A CN 200810019685A CN 100554856 C CN100554856 C CN 100554856C
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- 239000000463 material Substances 0.000 claims abstract description 10
- 238000009835 boiling Methods 0.000 abstract description 13
- 239000007788 liquid Substances 0.000 abstract description 9
- 238000009833 condensation Methods 0.000 abstract description 5
- 230000005494 condensation Effects 0.000 abstract description 5
- 238000009826 distribution Methods 0.000 abstract description 5
- 238000009834 vaporization Methods 0.000 description 9
- 230000008016 vaporization Effects 0.000 description 9
- 238000000034 method Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000003754 machining Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 238000005520 cutting process Methods 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 238000003825 pressing Methods 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000010327 methods by industry Methods 0.000 description 1
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Abstract
A kind of intensify heat transfer pipe belongs to the heat-exchanging part technical field.It comprises body and by the material on the described body along the radial direction of body extend and the outer surface of body around body in the shape of a spiral shape extend form constitute the outer fin of one with body, constitute the minute yardstick conduit at least one side surface of described outer fin.Advantage: owing to constitute the minute yardstick conduit on the side surface of at least one side of fin outside, therefore help to make the surface increase heat exchange area of outer fin and the disturbance that has improved convection cell, strengthened the outer forced-convection heat transfer of pipe, heat transfer coefficient is significantly improved; When intensify heat transfer pipe of the present invention was used for evaporimeter, the minute yardstick conduit can increase the number of the nucleus of boiling greatly, and boiling heat transfer is strengthened under the situation of low heat flow density; When intensify heat transfer pipe of the present invention was used for condenser, the minute yardstick conduit can improve the distribution of outer fin surface thickness of liquid film, makes condensation heat transfer be strengthened.
Description
Technical Field
The invention relates to a reinforced heat transfer pipe which is used as a heat exchange part of an evaporator and a condenser in a refrigeration and air-conditioning system, belonging to the technical field of heat exchange parts.
Background
In the fields of refrigeration, air conditioning, process engineering, petrochemical engineering, energy and power engineering and the like, the boiling or condensation of liquid on the outer surface of a tube bundle is involved. Especially for the evaporator and the condenser used in the refrigeration and air-conditioning system, the phase-change heat-exchange thermal resistance of the refrigerant when the refrigerant boils or condenses outside the tube is equal to or even larger than the forced convection heat-exchange thermal resistance inside the tube, so the strengthening of the phase-change heat-exchange outside the tube can have obvious effect on improving the heat transfer performance of the evaporator and the condenser.
Studies on the nucleate boiling mechanism indicate that boiling of a liquid requires the presence of a core of vaporization. Under the condition of a given degree of superheat of the heating surface, the bubbles can grow up only when the radius of the vaporization core is larger than the minimum radius required for bubble growth, and nucleate boiling can be carried out. While cavities formed by grooves and/or cracks in the heated surface are most likely to be the vaporization cores. In the boiling process, after the bubbles grow and separate from the cavities, due to the action of the surface tension of the liquid, part of steam trapped by the cavities is difficult to flow into the liquid and be completely expelled, so that the steam becomes a new vaporization core, new bubbles grow, and the boiling process is continuously continued. It is known that to enhance nucleate boiling heat transfer, it is critical to form numerous vaporization nuclei on the heating surface. Therefore, much of the development work of the enhanced boiling heat transfer surface starting in the 70's of the 20 th century has been spread around the formation of numerous structures on the heating surface, and it is known in numerous documents, for example, heat exchange tubes for evaporators disclosed in chinese patent ZL95246323.7 (grant No. CN2257376Y) and chinese patent ZL03207498.0 (grant No. CN2662187Y), the outer surfaces of which are spiral fins having a T-shaped top pressed to constitute a grooved structure; the heat exchange tubes disclosed in chinese patent ZL95118177.7 (grant No. CN1090750C) and chinese patent ZL02263461.4 (grant No. CN2557913Y) have no spiral fins with helical teeth uniformly distributed along the circumferential direction on the outer surface, and the tips of the fins are extended to both sides by applying pressure to the fins to form a cavity structure; a heat exchange tube disclosed in chinese patent application publication No. CN1366170A (application No. 02101870.7), the outer surface of which is formed with fins by a machining method, and secondary grooves are formed at the bottoms of primary grooves between the fins; the heat exchange tube disclosed in chinese patent publication No. CN1100517A (application No. 94116309.1) has fins on its outer surface pressed to incline toward one side, and a cavity structure is formed by pressing a groove on the shoulder of the fin; the heat exchange tube for evaporator disclosed in chinese patent ZL02264793.7 (publication No. CN2572324Y) has a cavity structure formed by forming a spiral plate with saw-tooth structure on its outer surface by machining and pressing a chute at the top of the saw-tooth; the heat exchange tube disclosed in chinese patent application publication CN1731066A (application No. 200510041468.6) has fins and transverse spines formed on the outer surface by machining to form a compound cavity structure.
The common feature of the outer wall surface of the heat exchange tube, which is commonly called as the structure of the outer fin, in the above documents is that the heat exchange tube has a groove structure or a cavity structure with a slightly smaller opening, so as to construct a place or carrier forming a vaporization core, thereby achieving the effect of enhancing boiling heat exchange.
In recent years, people are still dedicated to exploring the structure of the surface of the fin, and a heat transfer pipe which obtains a larger number of vaporization cores and further improves the heat exchange coefficient of phase change heat exchange is expected to be obtained.
However, the published literature has not shown any technical suggestion that the structure of the outer fins on the outside of the heat exchange tubes of the evaporator and the condenser can significantly improve the phase change heat transfer coefficient.
Disclosure of Invention
The invention aims to provide a reinforced heat transfer pipe which can enable the surface of an outer fin to have a larger heat exchange area so as to embody ideal heat transfer performance.
The invention is to accomplish the task by providing a reinforced heat transfer pipe, which comprises a pipe body and an outer fin which is formed by extending materials on the pipe body along the radius direction of the pipe body and spirally extending the outer surface of the pipe body around the pipe body to form a whole with the pipe body, wherein at least one side surface of the outer fin is provided with a micro-scale channel, the upper part of the outer fin is provided with a groove, a tooth table is formed between two adjacent grooves, the depth of the groove is less than the height of the outer fin, the groove and the tooth table form a saw-tooth shape for the outer fin, and at least 1 arc-shaped micro-scale channel extending from the root part to the top part of the tooth table is arranged on at least one of a pair of tooth table side surfaces at two sides of the groove which the tooth table faces.
The inner wall of the tube body is provided with inner fins.
The inner fins are spirally formed on the inner wall of the tube body.
The micro-scale channels of the present invention are formed in a mesh-like form on at least one side surface of the outer fin.
The groove width of the microscale channel is 0.001-0.5mm, and the groove depth is 0.001-0.2 mm.
The average spacing between the microscale channels of the present invention is in the range of 0.005-5.0 mm.
The average spacing is the arithmetic average of the area enclosed by the centerlines of adjacent microscale channels divided by the lengths of the two centerlines.
The width of the arc-shaped micro-scale channel is 0.001-0.5mm, and the depth is 0.001-0.2 mm.
Tooth top edges extend from two sides of the top of the tooth table, and the top edges of the fins on the adjacent outer fins are mutually connected, so that a closed cavity structure is formed in the space between the two adjacent outer fins.
Compared with the finned tube in the prior art, the reinforced heat transfer tube has the advantages that: because the micro-scale channel is formed on the side surface of at least one side of the outer fin, the heat exchange area of the surface of the outer fin is increased, the disturbance to fluid is improved, forced convection heat exchange outside the tube is enhanced, and the heat transfer coefficient is obviously improved; when the enhanced heat transfer pipe is used for an evaporator, the number of the evaporation cores can be greatly increased through the micro-scale channel, so that boiling heat transfer is enhanced under the condition of low heat flux density; when the reinforced heat transfer pipe is used for a condenser, the micro-scale channel can improve the distribution of the thickness of the liquid film on the surface of the outer fin, so that the condensation heat transfer is reinforced.
Drawings
FIG. 1 is a schematic view of a heat transfer enhancement tube according to an embodiment of the present invention.
FIG. 2 is a block diagram of another embodiment of the enhanced heat transfer tube of the present invention.
FIG. 3 is a schematic diagram of a reinforced heat transfer tube of the structure shown in FIG. 1.
Fig. 4 is a schematic diagram illustrating a manufacturing process of the heat-transfer enhancement pipe of fig. 2.
Fig. 5 is an enlarged sectional view a-a of fig. 4.
Fig. 6 is a schematic diagram of the calculation of the position of the micro-scale channel.
Fig. 7 is a schematic structural view of a microscale channel slotter knife.
Fig. 8 is an enlarged schematic view of another embodiment of a microscale channel slotter knife.
FIG. 9 is a schematic diagram of the path of the micro-scale groove at different rotation speed ratios of the pipe body and the cutter.
Detailed Description
Example 1:
referring to fig. 1, an outer fin 2 is formed by one-step forming and rolling on the outer wall of a tube body 1 with an inner fin 17 to manufacture a reinforced heat transfer tube, the outer fin 2 is formed by extending the material on the tube body 1 outwards along the radius direction of the tube body 1, and is of an integral structure with the tube body 1, a thermal contact resistance is arranged between the outer fin and the tube body 1, and the outer fin 2 extends spirally around the tube body 1 on the outer surface of the tube body 1; while rolling the outer fin 2, machining dense micro-scale channels 3 on the side surface of the outer fin 2 by a cutter, wherein the micro-scale channels 3 are a cluster of dense curves drawn by a micro-scale channel slotting cutter 9 (shown in fig. 3 and 4) during relative rotation with the outer fin 2, and the cluster of curves forms a grid-shaped structure on the two side surfaces of the outer fin 2, and the specific size parameters of the micro-scale channels 3 of the grid-shaped structure are as follows: the groove width is 0.1mm, the groove depth is 0.02mm, and the average spacing is 0.5 mm. The structure of the grid-shaped micro-scale channel 3 increases disturbance, destroys a boundary layer, obviously increases heat exchange area and strengthens a heat transfer process. For boiling heat exchange, a large number of vaporization cores with extremely small vaporization radii are added on the surface of the outer fin 2; for condensation heat exchange, the tension distribution of the liquid film can be changed, the thickness of the liquid film is further reduced on the whole, and the heat exchange performance is improved. Since the material extruded during the processing of the micro-scale channels 3 also increases the height of the outer fins 2 a little bit, but does not reduce the strength of the tube body 1, the weight of the tube body 1 can be reduced while the heat transfer performance is further improved.
Referring to fig. 2, when the reinforced heat transfer tube is used in a heat exchange tube of a condenser, after rolling an outer fin 2 and cutting micro-scale grooves 3 in the side surface of the outer fin 2, grooves 4 are cut in the outer fin 2 by a tooth top grooving tool 11 (shown in fig. 4), tooth platforms 5 are formed between adjacent grooves 4, the depth of each groove 4 is smaller than the height of the outer fin 2, and the outer fin 2 is formed in a zigzag shape by the grooves 4 and the tooth platforms 5; at the same time, a microscale channel slotter knife 9 (shown in fig. 3 and 4) scores at least one arcuate microscale channel 6 extending from the root to the tip of the tooth table 5 on the surface of the tooth table 5 opposite the sides of the groove 4, the arcuate microscale channel 6 being scored by the microscale channel slotter knife 9 during relative rotation of the side surfaces of the tooth table 5. The additional arc-shaped micro-scale channel 6 on the side surface of the tooth platform 5 can improve the surface tension distribution of a liquid film on the side surface of the tooth platform 5 and is beneficial to improving the overall condensation heat exchange performance.
Still referring to fig. 2, when the heat-exchanging tube is used for a heat-exchanging tube of an evaporator, after the above-mentioned machining, the micro-scale channels 3 are carved on the side surfaces of the outer fins 2 and the arc-shaped micro-scale channels 6 are carved on the side surfaces of the tooth platforms 5, the material on the top of the tooth platforms 5 is extended to both sides to form fin top edges 5a, the fin top edges 5a are mutually corresponding to the fin top edges 5a formed by extending the material on the top of the tooth platforms 5 of the adjacent outer fins 2 to both sides, so that the space between the two adjacent outer fins 2 is in a cavity structure, and the micro-scale channels 3 on the side surfaces of the outer fins 2 and the arc-shaped micro-scale channels 6 on the side surfaces of the tooth platforms 5 are in an internal structure of the cavity, and these micro-scale channels 3 and the arc-shaped micro-scale channels 6 not only increase the internal heat-exchanging area of the cavity, but also ensure that the cavity still has, the cavity is always in an activated state, so that the heat exchange tube still has higher heat exchange performance at low heat flow density. When the enhanced heat transfer pipe of the invention is used for a heat exchange pipe of an evaporator, the tooth table 5 and the arc-shaped micro-scale groove 6 are not required to be arranged.
Example 2:
referring to fig. 3 and 6, an outer fin slotter knife 7, an outer fin forming knife 8 and a micro-scale channel slotter knife 9 are provided, and the set of knives is installed on a knife rest 16 (also called a knife shaft), wherein the edge of the micro-scale channel slotter knife 9 is uniformly provided with a plurality of knife edges 10 (shown in fig. 6), the outer fin 2 is formed on the tube body 1 by one-step extrusion, and the typical dimension is that the diameter of the tube body 1 at the root of the outer fin 2 is 20 mm. In the relative rotation process of the pipe body 1 and the cutter, the outer fin 2 with the height of 2mm is formed by the outer fin slotting cutter 7 and the outer fin forming cutter 8, and the micro-scale groove 3 with the regular groove width of 0.08mm, the groove depth of 0.05mm and the average groove distance of 0.5mm is scribed on the side surface of the outer fin 2 by the knife edge 10 (shown in figure 6) on the micro-scale groove slotting cutter 9. The definition of the average slot pitch mentioned here is: the area enclosed by the centerlines of adjacent microscale channels 3 is divided by the arithmetic average of the lengths of the two centerlines.
Referring to fig. 6, the position of the micro-scale channel 3 on the side surface of the outer fin 2 is calculated by setting the radius of the deepest position of the micro-scale channel 3 on the outer fin 2 as R, the distance from the knife edge 10 to the axis of the micro-scale channel slotting cutter 9 as R, and the angular velocity of the rotation of the tube body 1 as ω1The angular velocity of rotation of the microscale channel slotter knife 9 is ω2If the coordinate system is set on the tube 1, i.e. the tube 1 is stationary, the micro-scale groove slotting tool 9 is not limited by ω, if the coordinate system is set on the tube 1, i.e. the tube 1 is stationary2Around the axial position (X, Y) ═ O, O of the tube 1, the rotation is performed at an angular velocity ω1Revolution, then, the trajectory that the knife edge 10 makes on the side surface of the outer fin 2 can be calculated by the following formula:
X＝ρ·Cosθ
Y＝ρ·Sinθ
wherein,
θ＝arctan(Y′/X′)+ω1·t
X′＝r+R-R·Cos(ω2·t)
Y′＝-R·Sin(ω2·t)
referring to fig. 9, which shows the shape of more micro-scale channels 3 scribed on the side surface of the outer fin 2, the calculation parameters are: the radius R of the deepest position of the micro-scale channel 3 on the outer fin 2 is 8mm, the distance R from the knife edge 10 to the axle center of the micro-scale channel slotting cutter 9 is 20mm, the distance S between the adjacent knife edges 10 is 1mm, and the rotating speed is higher than omega2/ω10.35, 0.40, 0.47, 0.65 and 1.20, respectively, and the shape of the micro-scale channel 3 is illustrated in particular by fig. 9a, 9b, 9c, 9d and 9e, respectively, of the five single columns in fig. 9.
The calculated parameters for the microscale channel 3 shown in fig. 6 are R16 mm, R40 mm, ω2/ω1＝R/R is 0.4, and the distance between adjacent edges 10 on the microscale channel slotter knife 9 is 1 mm.
Referring to fig. 7, the micro-scale channel slotter knife 9 can be made of a disc-shaped thin blade 12 with a toothed edge 10 at both edges, and the teeth can be triangular saw teeth, rectangular teeth, or other shapes, and the embodiment selects triangular saw teeth. A concave gasket 13 is clamped between the two thin blades 12, two convex gaskets 14 are respectively arranged at two ends, namely one side back to the concave gasket 13, the diameters of the concave gasket 13 and the convex gasket 14 are smaller than the diameter of the thin blade 12, and after the cutter is fastened, the edge 10 of the thin blade 12 slightly tilts towards two sides along the axial direction of the cutter. Since the diameter of the concave and convex shims 13, 14 is smaller than that of the thin blade 12, the thin blade 12 has a certain elasticity and does not form an excessively deep cut in the outer fin 2. Such thin blades 12 are proposed for heat transfer tubes in which the outer fins 2 are trapezoidal in cross section.
Referring to fig. 8, the micro-scale channel slotting tool 9 can also be made by configuring the micro-scale channel slotting tool 9 as a disk-shaped blade 15 with a toothed edge at the edge, and deflecting the toothed edge 15a of the disk-shaped blade 15 alternately towards two sides to form the illustrated toothed edge 15a, wherein the teeth can be triangular saw teeth, rectangular saw teeth or other shapes, and the embodiment selects triangular saw teeth.
Example 3:
referring to fig. 4 and 5 in conjunction with fig. 2, a heat-transfer reinforced tube of the present invention is illustrated in fig. 2 and used as a condenser tube.
The specific structure comprises a pipe body 1 and an outer fin 2 formed on the outer wall surface of the pipe body 1, grooves 4 are cut in the outer fin 2, tooth platforms 5 are formed between two adjacent grooves 4, the depth of each groove 4 is smaller than the height of the outer fin 2, the grooves 4 and the tooth platforms 5 enable the outer fin 2 to form a saw-tooth shape, 1-2 arc-shaped micro-scale channels 6 (shown in figure 5) extending from the root parts of the tooth platforms 5 to the tops of the tooth platforms 5 are arranged on the surfaces of the tooth platforms 5 opposite to each other on two sides of the groove 4, micro-scale channels 3 are formed on the side surfaces of the outer fin 2, the height of each outer fin 2 is 1.2mm, the height of each tooth platform 5 is 0.8mm, the widths of the micro-scale channels 3 and the arc-shaped micro-scale channels 6 are respectively 0.05mm, and.
During manufacturing, a first group of processing cutter groups consisting of an outer fin slotting cutter 7 and an outer fin forming cutter 8 are adopted to form the outer fins 2 on the outer wall surface of the pipe body 1; a second group of processing tools is formed by a wing top slotting cutter 11 and a micro-scale channel slotting cutter 9, a plurality of cutter edges 10 are uniformly arranged on the edge of the micro-scale channel slotting cutter 9, the group of tools rotate at a specific rotating speed, and the rotating speed ratio omega2/ω1＝1.14R/R, a fin top slotting cutter 11 cuts the grooves 4 on the outer fins 2, and a micro-scale channel slotting cutter 9A disc blade 15 with a toothed blade 15a at the edge shown in fig. 8, wherein the teeth pitch of the saw teeth at the edge of the disc is 0.5mm, the saw teeth are inclined towards the two sides of the disc in a staggered manner, the tooth tips of the saw teeth form the toothed blade 15a, and a group of arc-shaped microscale channels 6 extending from the root to the top of the tooth table 5 are carved on the side surfaces of the grooves 4 opposite to the adjacent grooves 4, and the processing mode of the group of blades for the outer fins 2 is shown in fig. 4; a third group of processing cutters are formed by an outer fin forming cutter 8 and a micro-scale channel slotting cutter 9, a plurality of cutter edges 10 are uniformly arranged on the edge of the micro-scale channel slotting cutter 9, and the cutters are arranged at a rotation speed ratio omega2/ω1＝And (3) rotating as R/R, cutting the redundant material fins extending from the bottom of the groove 4 to the two sides of the outer fin 2 in the process of cutting the groove 4 by using an outer fin forming knife 8, and scribing regular and dense micro-scale channels 3 on the side surfaces of the outer fin 2 by using a micro-scale channel slotting knife 9.
Example 4:
referring to fig. 4 and 5 in conjunction with fig. 2, a reinforced heat transfer tube of the present invention is illustrated as being used as an evaporator tube and is schematically illustrated in fig. 2.
The heat transfer tube comprises a tube body 1 and outer fins 2 formed on the outer wall surface of the tube body 1, wherein dense micro-scale channels 3 are formed on the side surfaces of the outer fins 2, grooves 4 are also cut on the outer fins 2, tooth platforms 5 are formed between every two adjacent grooves 4, the depth of each groove 4 is smaller than the height of each outer fin 2, the outer fins 2 are formed into a sawtooth shape by the grooves 4 and the tooth platforms 5, materials on the tops of the tooth platforms 5 extend towards two sides by flat rollers to form fin top edges 5a, the fin top edges 5a are mutually connected with fin top edges 5a formed by extending towards two sides by the same way of the materials on the tops of the tooth platforms 5 of the adjacent outer fins 2, and therefore the two adjacent outer fins 2 are in a cavity structure, and the micro-scale channels 3 on the side surfaces of the outer fins 2 are in an internal micro structure of a cavity. The height of the outer fin 2 obtained in this example was 0.98mm, the groove width of the micro-scale channel 3 was 0.02mm, and the groove depth was 0.01 mm. In the manufacturing process, two micro-scale channel slotting tools 9 are adopted, the tooth pitch of a toothed edge 10 at the edge of each micro-scale channel slotting tool 9 is 0.5mm, and the two micro-scale channel slotting tools 9The knife edge 10 is staggered by half a pitch, and the rotating speed ratio omega2/ω1＝＝r/R1So as to scribe a grid-like distribution of micro-scale channel surface structures with a spacing of 0.25mm on the side surface of the outer fin 2.
Claims (9)
1. A reinforced heat transfer pipe comprises a pipe body (1) and an outer fin (2) which is formed by extending the material on the pipe body (1) along the radius direction of the pipe body (1) and spirally extending around the pipe body (1) on the outer surface of the pipe body (1) and is integrated with the pipe body (1), characterized in that at least one side surface of the outer fin (2) is provided with a micro-scale channel (3), the upper part of the outer fin (2) is provided with a groove (4), a tooth table (5) is formed between two adjacent grooves (4), the depth of the groove (4) is less than the height of the outer fin (2), the outer fins (2) are formed into a saw-toothed shape by the grooves (4) and the tooth platforms (5), and at least 1 arc-shaped microscale channel (6) extending from the root parts to the tops of the tooth platforms (5) is formed in at least one tooth platform side surface of a pair of tooth platform side surfaces on the two corresponding sides of the grooves (4) which are faced by the tooth platforms (5).
2. The enhanced heat transfer tube according to claim 1, wherein the inner wall of the tube body (1) is formed with inner fins (17).
3. The enhanced heat transfer tube according to claim 2, wherein the inner fin (17) is formed in a spiral state on the inner wall of the tube body (1).
4. The enhanced heat transfer tube according to claim 1, wherein the micro-scale channels (3) are formed in a mesh-like manner on at least one side surface of the outer fin (2).
5. The enhanced heat transfer tube according to claim 1 or 4, wherein the micro-scale channels (3) have a groove width of 0.001 to 0.5mm and a groove depth of 0.001 to 0.2 mm.
6. The enhanced heat transfer tube according to claim 1 or 4, wherein the micro-scale channels (3) have an average pitch of 0.005 to 5.0 mm.
7. The enhanced heat transfer tube of claim 6, wherein the average pitch is the arithmetic average of the area encompassed by the centerlines of adjacent microscale channels (3) divided by the lengths of those two centerlines.
8. The enhanced heat transfer tube of claim 1, wherein the arcuate microscale channels (6) have a width of 0.001 to 0.5mm and a depth of 0.001 to 0.2 mm.
9. The enhanced heat transfer tube according to claim 1, wherein the tooth platforms (5) have tooth crest edges (5a) extending from both sides of the top portion thereof, and the fin crest edges (5a) of the adjacent outer fins (2) are in contact with each other so that the space between the two adjacent outer fins (2) forms a closed cavity structure.
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| Application Number | Priority Date | Filing Date | Title |
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| CNB2008100196859A CN100554856C (en) | 2008-03-12 | 2008-03-12 | A kind of intensify heat transfer pipe |
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| CNB2008100196859A CN100554856C (en) | 2008-03-12 | 2008-03-12 | A kind of intensify heat transfer pipe |
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| CN100554856C true CN100554856C (en) | 2009-10-28 |
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| RU2505760C2 (en) * | 2008-09-09 | 2014-01-27 | Конинклейке Филипс Электроникс, Н.В. | Heat exchanger with horizontal finning for cryogenic cooling with repeated condensation |
| CN104949564A (en) * | 2015-07-08 | 2015-09-30 | 赤峰宝山能源（集团）贺麒铜业有限责任公司 | Straight tooth and high-low tooth internal thread heat transfer pipe |
| CN110195994B (en) * | 2019-04-29 | 2021-07-13 | 西安交通大学 | High-efficiency composite double-side reinforced heat transfer pipe |
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Effective date of registration: 20200622 Address after: 215562, No. 18 Yang Dong Road, Yang Yang garden, Xinzhuang Town, Suzhou, Jiangsu, Changshou City Patentee after: JIANGSU CUILONG PRECISION COPPER TUBE Corp. Address before: 215562, No. 18 Yang Dong Road, Yang Yang garden, Xinzhuang Town, Jiangsu, Changshou City Co-patentee before: University of Shanghai for Science and Technology Patentee before: JIANGSU CUILONG PRECISION COPPER TUBE Corp. |
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