CN105333758A - Right-angle internally-finned heat tube - Google Patents
Right-angle internally-finned heat tube Download PDFInfo
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- CN105333758A CN105333758A CN201510826826.8A CN201510826826A CN105333758A CN 105333758 A CN105333758 A CN 105333758A CN 201510826826 A CN201510826826 A CN 201510826826A CN 105333758 A CN105333758 A CN 105333758A
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- heat pipe
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- 239000012530 fluid Substances 0.000 claims abstract description 57
- 230000005494 condensation Effects 0.000 claims description 21
- 238000009833 condensation Methods 0.000 claims description 21
- 238000001704 evaporation Methods 0.000 claims description 19
- 230000008020 evaporation Effects 0.000 claims description 19
- 238000000034 method Methods 0.000 claims description 8
- 239000000203 mixture Substances 0.000 claims description 6
- 230000008569 process Effects 0.000 claims description 4
- 230000001154 acute effect Effects 0.000 claims description 3
- 238000004080 punching Methods 0.000 abstract description 5
- 230000017525 heat dissipation Effects 0.000 abstract description 3
- 230000008859 change Effects 0.000 description 13
- 238000002474 experimental method Methods 0.000 description 12
- 238000012546 transfer Methods 0.000 description 8
- 239000007789 gas Substances 0.000 description 6
- 239000007788 liquid Substances 0.000 description 6
- 230000005855 radiation Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000003467 diminishing effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
-
- 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
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with 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
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a heat tube. The heat tube comprises a flat tube, wherein the flat tube comprises tube walls parallel to each other; a fluid channel is formed between the adjacent tube walls; the heat tube comprises a fin arranged in the flat tube; the fine is arranged between the tube walls and comprises a vertical part which is vertical to the tube walls; a protrusion is processed on the vertical part in a punching manner, so that fluid on two sides of the vertical part communicates with a hole formed in the vertical part in a punching manner; the protrusion extends outwards from the vertical part in the flowing direction of the fluid. Through the heat tube, a plate fin heat dissipation plate of the punched protrusion is arranged in the heat tube, so that the problem of low heat exchange efficiency of non-condensable gas is solved, the energy is greatly saved, and the problem of low efficiency of a heat exchange system of the heat tube is overcome.
Description
Technical field
The invention belongs to heat pipe field, particularly relate to a kind of right angle inner fin heat pipe.
Background technology
Hot pipe technique is the heat transfer element that one that George Ge Luofo (GeorgeGrover) of U.S. Los Alamos (LosAlamos) National Laboratory in 1963 invents is called " heat pipe ", it takes full advantage of the Rapid Thermal hereditary property of heat-conduction principle and phase change medium, be delivered to rapidly outside thermal source by the heat of thermal objects through heat pipe, its capacity of heat transmission exceedes the capacity of heat transmission of any known metal.
The industry such as aerospace, military project is widely used in before hot pipe technique, since being introduced into radiator manufacturing, people are made to change the mentality of designing of traditional heat sinks, break away from simple dependence high air quantity motor to obtain the single radiating mode of better radiating effect, adopt hot pipe technique to make radiator obtain satisfied heat transfer effect, open heat radiation industry new world.Current heat pipe is widely used in various heat transmission equipment.
Generally, heat pipe comprises evaporation ends and condensation end, the fluid heat absorption evaporation of evaporator section, carry out condensation to condensation end, no matter transfer heat to outside fluid, be evaporation ends or condensation end, the situation of biphase gas and liquid flow can be there is in heat transfer process, and aging along with heat pipe, some on-condensible gases can be produced in heat pipe, thus cause the reduction of heat pipe heat exchanging coefficient.
In addition, heat pipe evaporation ends and condensation end are in heat transfer process, and evaporation ends is different with each position heat exchange amount of condensation end, thus causes Local Heat Transfer uneven.
For the problems referred to above, the invention provides a kind of new heat pipe, thus the problem that the coefficient of heat transfer is low and heat exchange is uneven when solving heat pipe heat exchanging.
Summary of the invention
The invention provides a kind of new heat pipe, thus solve the technical problem occurred above.
To achieve these goals, technical scheme of the present invention is as follows:
A kind of heat pipe, comprise flat tube, described flat tube comprises tube wall parallel to each other, forms fluid passage, it is characterized in that between described adjacent tube wall, heat pipe comprises the fin be arranged in flat tube, described fin is arranged between tube wall, and described fin comprises the vertical component perpendicular to tube wall, it is characterized in that, vertical component processes projection by impact style, thus the hole that the fluid of vertical component both sides is formed by impact style on vertical component is communicated with; Described projection stretches out from vertical component along mixture flow direction.
As preferably, heat pipe comprises evaporation ends and condensation end, and fin is arranged on described evaporation ends and/or condensation end.
As preferably, described projection is isosceles triangle, the base of described isosceles triangle is arranged on vertical component, be preferably perpendicular to tube wall, the distance of adjacent tube wall is H, and the length on isosceles triangle base is h, the distance of adjacent vertical component is w, the drift angle of isosceles triangle is b, and the angle of the bearing of trend of described projection and the flow direction of mixture is a, meets following formula:
c6*h/H=c1*Ln(L*sin(a)/w)+c2,
sin(b/2)=c3+c4*sin(a)-c5*(sin(a))
2，
Wherein Ln is logarithmic function, and c1, c2, c3, c4, c5, c6 are coefficients,
0.237<c1<0.255,0.675<c2<0.703,0.867<c3<0.885，0.673<c4<0.711，
1.135<c5<1.152,
6.5<c6<7.5；
19°<a<71°，55°<b<165°；
10mm<w<15mm，6mm<H<14mm；
0.19<L*sin(a)/w<0.41,0.29<c6*h/H<0.47；
H be with the relative face of adjacent tube wall between distance, W is with the distance in the relative face of adjacent vertical component, and L is the distance of summit to base mid point of isosceles triangle.
As preferably, c1=0.243, c2=0.696,
c3=0.878，c4=0,689，c5=1.142,c6=7.1。
As preferably, described vertical component is multiple, and described vertical component is parallel to each other.
As preferably, the angle that described projection and the flow direction of fluid are formed is acute angle.
As preferably, the angle of the bearing of trend of described projection and the flow direction of fluid is a, and same vertical component arranges multiple projection, and along the flow direction of fluid, described angle a is more and more less.
As preferably, same vertical component arranges multiple projection, and multiple projection is staggered to stretch out from vertical component both sides.
As preferably, the length that described projection extends is L, and same vertical component arranges multiple projection, and along the flow direction of fluid, described length L is increasing.
As preferably, described projection is isosceles triangle, the base of described isosceles triangle is arranged on vertical component, as preferably, base is identical with the vertical angle of vertical component, and the drift angle of described isosceles triangle is b, and same vertical component arranges multiple projection, along the flow direction of fluid, described drift angle b is increasing.
As preferably, described projection is isosceles triangle, the base of described isosceles triangle is arranged on vertical component, as preferably, base is identical with the vertical angle of vertical component, and the base of described isosceles triangle is S1, and same vertical component arranges multiple projection, along the flow direction of fluid, described S1 is more and more less.
Compared with prior art, plate type heat exchanger of the present invention and heat exchange tube wall thereof have following advantage:
1) the present invention is by the change of outside fin regularity, makes heat pipe heat radiation on the whole even, avoids heat pipe local temperature overheated, cause radiating effect excessively poor, extend the heat pipe life-span.
2) the present invention by arranging the plate wing fin of projection of punching press in heat pipe, solves the problem that heat exchange efficiency containing on-condensible gas or two phase flow is low, saved the energy greatly, overcome the inefficient problem of heat pipe heat exchanging system.
3) aperture that punching press " projection " is formed, by the impact of " projection " downstream pressure field, can realize pressure and the mass exchange of fin media of both sides, damage, enhanced heat exchange to the stability of viscous sublayer and liquid film;
4) by a large amount of experiments, the physical dimension of best heat pipe is determined;
5) be H by the distance of the adjacent tube wall of design, the length on isosceles triangle base is h, the distance of adjacent vertical component is w, the drift angle of isosceles triangle is b, the angle of the bearing of trend of described projection and the flow direction of fluid is the change of the parameters such as a along fluid flow direction, improves heat exchange efficiency or reduces fluid pressure.
Accompanying drawing explanation
Fig. 1 is the structural representation of heat pipe of the present invention;
Fig. 2 is heat pipe evaporation ends of the present invention or condensation end cross-sectional structure schematic diagram;
Fig. 3 is the structural representation of outer setting fin heat pipe evaporation ends of the present invention or condensation end cross section;
Fig. 4 is the present invention's cross section structural representation of heat pipe inner fin;
Fig. 5 is the modified node method schematic diagram of outer setting fin heat pipe evaporation ends of the present invention or condensation end cross section;
Fig. 6 is the schematic diagram that the present invention arranges raised structures vertical component plane;
Fig. 7 is another schematic diagram that the present invention arranges raised structures vertical component plane;
Fig. 8 is denation structural representation of the present invention;
Fig. 9 is the tangent plane structural representation in denation runner of the present invention;
The structural representation that Figure 10 projection of the present invention extends to vertical component both sides.
Reference numeral is as follows:
1 heat pipe, 2 fluid passages, 3 tube walls, 4 vertical components, 5 horizontal components, 6 projections, 7 fins, 8 evaporator sections, 9 adiabatic sections, 10 condensation segments, 11 outside fin.
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.
Herein, if do not have specified otherwise, relate to formula, "/" represents division, "×", " * " represent multiplication.
As shown in Figure 1, a kind of heat pipe 1, comprise evaporation ends 8, condensation end 10, preferably also comprise adiabatic end 9, evaporation ends 8 absorbs heat, the fluid evaporator sealed in heat pipe, then fluid enters condensation end 10, pass to outside through heat by condensation end, the fluid then after heat exchange becomes liquid, then flows to evaporation ends 8.
As shown in Figure 2, described heat pipe 1 comprises flat tube, and described flat tube comprises tube wall 3 parallel to each other, forms fluid passage 2 between described adjacent tube wall 3.Fin 7 is set in flat tube 1 inside, preferably fin 7 is set in the evaporation ends 8 and/or condensation end 10 of heat pipe 1.Described fin 7 comprises the vertical component 4 vertical with tube wall 3, and described vertical component is parallel to each other.By impact style processing projection 6 on vertical component 4, thus the fluid of vertical component 4 both sides is communicated with by the hole that vertical component 4 is formed by impact style; Described projection 6 stretches out from vertical component 4.
Described flat tube can be integration manufacture, also can be split manufacture.
By arranging projection 6, there is following advantage:
1) on the one hand can breakable layer laminar sublayer, do not lose heat exchange area, and " point " and " hole " can disturbance fluid on differing heights respectively, enhanced heat exchange;
2) aperture that punching press projection is formed, by the impact of projection downstream pressure field, can realize pressure and the mass exchange of fin media of both sides, damage, enhanced heat exchange to the stability of viscous sublayer and liquid film.
3) for the fluid containing on-condensible gas or two-phase fluid, can the contact area of expansion gas-liquid interface and gas phase boundary and cooling wall be realized by " projection " and strengthen disturbance.
In evaporation ends 8 and/or condensation end, take above-mentioned measure, the heat exchange efficiency of fluid can greatly be improve.Compared with normal fluid heat transfer, the heat exchange efficiency of 15-25% can be improved.
As preferably, the angle that described projection 6 and the flow direction of fluid are formed is acute angle, it should be noted that, herein and the flow direction of fluid mentioned below refer to fluid from evaporation ends to the flow direction of condensation end.
As preferably, as shown in Figure 4, described fin 7 is vertical-type fin, and described fin 7 comprises horizontal component 5 and vertical component 4, and described horizontal component 5 is parallel with tube wall 3 and stick together with tube wall 3, and described vertical component 4 is connected with horizontal component 5.
In Fig. 6, the flow direction of fluid is from left to right.But left and right herein just illustrates the flow direction of fluid along projection, do not represent actual certain left and right flowing.
As shown in Figure 9, the angle of the described bearing of trend of projection 6 and the flow direction of fluid is a, and as shown in Figure 6, along the flow direction of fluid, same vertical component 4 arranges multiple projection 6, and along the flow direction of fluid, described angle a is increasing.
Found through experiments, large by the change gradually of angle a, compared with identical with angle a, higher heat exchange efficiency can be realized, approximately can improve the heat exchange efficiency of about 10%.
As preferably, along the flow direction of mixture, it is more and more less that angle a becomes large amplitude.Found through experiments, change the amplitude that the change of angle a is large, when can ensure heat exchange efficiency, reduce flow resistance further, approximately can reduce the flow resistance of about 5%.
As preferably, the length that described projection 6 extends is L, and along the flow direction of fluid, same vertical component 4 arranges multiple projection 6, and along the flow direction of fluid, described length L is increasing.Found through experiments, large by the change gradually of length L, compared with identical with length L, higher heat exchange efficiency can be realized, approximately can improve the heat exchange efficiency of about 9%.
As preferably, along the flow direction of fluid, it is more and more less that length L becomes large amplitude.Found through experiments, the amplitude that the change of length L is large is more and more less, when can ensure heat exchange efficiency, reduces flow resistance further, approximately can reduce the flow resistance of about 5%.
As preferably, described projection 6 is isosceles triangle, the base of described isosceles triangle is arranged on vertical component 4, and as preferably, base is identical with the vertical direction of vertical component, the drift angle of described isosceles triangle is b, along the flow direction of fluid, same vertical component 4 arranges multiple projection 6, along the flow direction of fluid, when base length remains unchanged, described projection drift angle b is more and more less.Found through experiments, by diminishing gradually of projection drift angle b, compared with identical with drift angle b, higher heat exchange efficiency can be realized, approximately can improve the heat exchange efficiency of about 7%.
As preferably, along the flow direction of fluid, the amplitude that drift angle b diminishes is more and more less.Found through experiments, the amplitude that drift angle b diminishes is more and more less, when can ensure heat exchange efficiency, reduces flow resistance further, approximately can reduce the flow resistance of about 4%.
As preferably, described projection 6 is isosceles triangle, and the base of described isosceles triangle is arranged on vertical component, as preferably, base is identical with the vertical direction of vertical component, and the base length of described isosceles triangle is h, along the flow direction of fluid, same vertical component 4 arranges multiple projection 6, along the flow direction of fluid, same vertical component 4 arranges multiple projection, when drift angle remains unchanged, along the flow direction of fluid, described h is increasing.Found through experiments, large by the change gradually of h, compared with identical with h, higher heat exchange efficiency can be realized, approximately can improve the heat exchange efficiency of about 7%.
As preferably, along the flow direction of fluid, it is more and more less that h becomes large amplitude.Found through experiments, it is more and more less that h becomes large amplitude, when can ensure heat exchange efficiency, reduces flow resistance further, approximately can reduce the flow resistance of about 5%.
As preferably, along the flow direction of fluid, same vertical component arranges many row's projections 6, and as shown in Figures 6 and 7, often the distance of arranging between projection is S2, and along the flow direction of fluid, described S2 is increasing.Why so arrange, main purpose is large by the change of S2, realizes, when ensureing heat exchange efficiency, reducing flow resistance further.Found through experiments, flow resistance reduces about 10%.
Described S2 is for calculating distance with the base of the projection of adjacent row.
As preferably, as shown in Figure 7, many row's projections 6 are shifted structure.In Fig. 7, fluid flows from top to bottom.But herein up and down the flow direction of fluid along projection is just described, do not represent actual certain upper current downflow.
Find in an experiment, the distance of adjacent tube wall 3 can not be excessive, cross the reduction that conference causes heat exchange efficiency, too small meeting causes flow resistance excessive, in like manner, for the base length of isosceles triangle, drift angle, projection, the distance of fin vertical component and the angle of fluid flow direction all can not be excessive or too small, excessive or too smallly the change of the reduction of heat exchange efficiency or flow resistance all can be caused large, therefore in the distance of adjacent tube wall 3, the base length of isosceles triangle, drift angle, projection, an optimized size relationship is met between fin vertical component and the angle of fluid flow direction.
Therefore, the present invention is thousands of numerical simulations by the heat exchanger of multiple different size and test data, meeting in industrial requirements pressure-bearing situation (below 10MPa), when realizing maximum heat exchange amount, the dimensionally-optimised relation of the heat exchange tube wall of the best summed up.
As preferably, described projection is isosceles triangle, the base of described isosceles triangle is arranged on vertical component, and perpendicular to tube wall, the distance of adjacent tube wall is H, and the length on isosceles triangle base is h, the distance of adjacent vertical component is w, the drift angle of isosceles triangle is b, and the angle of the bearing of trend of described projection and the flow direction of mixture is a, meets following formula:
c6*h/H=c1*Ln(L*sin(a)/w)+c2,
sin(b/2)=c3+c4*sin(a)-c5*(sin(a))
2，
Wherein Ln is logarithmic function, and c1, c2, c3, c4, c5, c6 are coefficients,
0.237<c1<0.255,0.675<c2<0.703,0.867<c3<0.885，0.673<c4<0.711，
1.135<c5<1.152,
6.5<c6<7.5；
19°<a<71°，55°<b<165°；
10mm<w<15mm，6mm<H<14mm；
0.19<L*sin(a)/w<0.41,0.29<c6*h/H<0.47；
H be with the relative face of adjacent tube wall between distance, W is with the distance in the relative face of adjacent vertical component, and L is the distance of summit to base mid point of isosceles triangle.
As preferably, c1=0.243, c2=0.696,
c3=0.878，c4=0,689，c5=1.142,c6=7.1。
By the geometric scale of the best of " projection " that go out of above-mentioned formula, heat exchange efficiency can be improved, can realize only to viscous sublayer or comprise liquid film and to the strengthening comprising gas phase boundary different scale internal thermal resistance, avoiding measures is excessive, causes unnecessary drag losses simultaneously.
As preferably, the base of the adjacent projection of described same row all on one wire, the protrusion distance that same row is adjacent is S1, described 2.8 × h<S1<3.6 × h, and wherein S1 is with the distance of the mid point on the base of adjacent two isosceles triangle projections.Be preferably 3.1 × h=S1.
As preferably, the base of the isosceles triangle of the projection of adjacent row is parallel to each other, and the summit of isosceles triangle is L to the distance of base mid point, and the distance S2 of adjacent row is 3.4*L<S2<5.0*L.Be preferably S2=4.3*L.
When the base of the isosceles triangle of adjacent row is different, take the weighted average on two bases to calculate.
As preferably, the angle of the isosceles triangle of same row is identical with base.Namely shape is identical, is equal shape.
For formula above, for the projection that front and rear row size is different, be also still suitable for.
As preferably, the wall thickness of fin is 0.6-1.1mm; As preferably, 0.8-1.0mm.
For the concrete dimensional parameters do not mentioned, design according to normal heat exchanger.
As preferably, as shown in Figure 10, vertical component is arranged multiple projection 6, described projection extends to the not homonymy of vertical component
As preferably, same vertical component is arranged arranges projection more, and to arrange projection different to the extension side of vertical component from other at least one row's projection.
As preferably, adjacent projection of often arranging extends to the not homonymy of vertical component.
By setting like this, fluid can be made in the passage of vertical component both sides to replace heat exchanging tampering, improve heat exchange efficiency further.With compared with the same side, can about 8% be improved.
As preferably, as shown in Figure 2, at the outer setting fin 11 of the tube wall 3 of heat pipe 1, preferably at described evaporation ends 8 and/or condensation end 10 outer setting fin.
As preferably, described fin is straight tabular, the bearing of trend of fin along the flow direction of fluid, namely as shown in Figure 2, along the direction perpendicular to paper.
As preferably, along the flow direction of fluid, outside fin 11 highly constantly increases, and the amplitude highly increased is increasing.By increasing fin height, thus increase the heat exchange area of fin.Experiment finds, by setting like this, compared with identical with fin height, can improve the heat exchange efficiency of about 5%.
As preferably, as shown in Figure 5, along the centre of heat pipe 1 cross section to both sides, the height of described fin 11 constantly reduces.Wherein, be positioned at the centre position of heat pipe 1, the height of fin is the highest.
Because found by test, heat pipe is maximum in middle part heat radiation, from middle part to both sides, heat radiation diminishes gradually, therefore by arranging the outside fin height change of heat pipe, make the area of dissipation of heat pipe maximum at middle part like this, minimum in both sides, make middle part heat-sinking capability maximum, meet the heat dissipation law of heat pipe heat like this, make heat pipe heat radiation on the whole even, avoid heat pipe local temperature overheated, cause radiating effect excessively poor, cause the shortening in heat pipe life-span.
As preferably, from centre to both sides, the amplitude that the height of described fin 11 reduces constantly increases.
By above-mentioned setting, be also the heat dissipation law meeting heat pipe, improve the heat exchange efficiency of heat pipe further, increase the life-span of heat pipe.
As preferably, described heat pipe is gravity assisted heat pipe.
As preferably, the inside of described heat pipe arranges capillary materials.
As preferably, the running temperature of described heat pipe is 100-500 DEG C, as preferably 250-400 degree Celsius.
Although the present invention discloses as above with preferred embodiment, the present invention is not defined in this.Any those skilled in the art, without departing from the spirit and scope of the present invention, all can make various changes or modifications, and therefore protection scope of the present invention should be as the criterion with claim limited range.
Claims (6)
1. a heat pipe, comprise flat tube, described flat tube comprises tube wall parallel to each other, forms fluid passage, it is characterized in that between described adjacent tube wall, heat pipe comprises the fin be arranged in flat tube, described fin is arranged between tube wall, and described fin comprises the vertical component perpendicular to tube wall, it is characterized in that, vertical component processes projection by impact style, thus the hole that the fluid of vertical component both sides is formed by impact style on vertical component is communicated with; Described projection stretches out from vertical component along mixture flow direction.
2. heat pipe as claimed in claim 1, heat pipe comprises evaporation ends and condensation end, and fin is arranged on described evaporation ends and/or condensation end.
3. heat pipe as claimed in claim 1 or 2, it is characterized in that, described projection is isosceles triangle, the base of described isosceles triangle is arranged on vertical component, and the distance of adjacent tube wall is H, and the length on isosceles triangle base is h, the distance of adjacent vertical component is w, the drift angle of isosceles triangle is b, and the angle of the bearing of trend of described projection and the flow direction of mixture is a, meets following formula:
c6*h/H=c1*Ln(L*sin(a)/w)+c2,
sin(b/2)=c3+c4*sin(a)-c5*(sin(a))
2，
Wherein Ln is logarithmic function, and c1, c2, c3, c4, c5, c6 are coefficients,
0.237<c1<0.255,0.675<c2<0.703,0.867<c3<0.885，0.673<c4<0.711，
1.135<c5<1.152,
6.5<c6<7.5；
19°<a<71°，55°<b<165°；
10mm<w<15mm，6mm<H<14mm；
0.19<L*sin(a)/w<0.41,0.29<c6*h/H<0.47；
H be with the relative face of adjacent tube wall between distance, W is with the distance in the relative face of adjacent vertical component, and L is the distance of summit to base mid point of isosceles triangle.
4. plate-fin heat exchanger as claimed in claim 3, is characterized in that, c1=0.243, c2=0.696,
c3=0.878，c4=0,689，c5=1.142,c6=7.1。
5. heat pipe as claimed in claim 1 or 2, it is characterized in that, described vertical component is multiple, and described vertical component is parallel to each other.
6. heat pipe as claimed in claim 1 or 2, it is characterized in that, the angle that described projection and the flow direction of fluid are formed is acute angle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510826826.8A CN105333758B (en) | 2015-11-25 | 2015-11-25 | Right-angle internally-finned heat tube |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510826826.8A CN105333758B (en) | 2015-11-25 | 2015-11-25 | Right-angle internally-finned heat tube |
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| Publication Number | Publication Date |
|---|---|
| CN105333758A true CN105333758A (en) | 2016-02-17 |
| CN105333758B CN105333758B (en) | 2017-03-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510826826.8A Expired - Fee Related CN105333758B (en) | 2015-11-25 | 2015-11-25 | Right-angle internally-finned heat tube |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2018177443A1 (en) * | 2017-03-28 | 2018-10-04 | 杭州三花家电热管理系统有限公司 | Heat conduction assembly, heat conduction device, and preparation method for heat conduction assembly |
| CN108775131A (en) * | 2018-08-24 | 2018-11-09 | 浙江宏博新型建材有限公司 | A kind of safe floor of heat dissipation |
| CN109162405A (en) * | 2018-08-24 | 2019-01-08 | 浙江宏博新型建材有限公司 | A kind of wall heatiing panel |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2470774Y (en) * | 2001-02-28 | 2002-01-09 | 杨洪武 | Hollow toothed heat-tube exchanger |
| JP2002016201A (en) * | 2000-06-29 | 2002-01-18 | Showa Denko Kk | Heat pipe |
| CN1805133A (en) * | 2005-01-14 | 2006-07-19 | 杨洪武 | Plate-type heat-pipe radiator |
| US20070012430A1 (en) * | 2005-07-18 | 2007-01-18 | Duke Brian E | Heat exchangers with corrugated heat exchange elements of improved strength |
-
2015
- 2015-11-25 CN CN201510826826.8A patent/CN105333758B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002016201A (en) * | 2000-06-29 | 2002-01-18 | Showa Denko Kk | Heat pipe |
| CN2470774Y (en) * | 2001-02-28 | 2002-01-09 | 杨洪武 | Hollow toothed heat-tube exchanger |
| CN1805133A (en) * | 2005-01-14 | 2006-07-19 | 杨洪武 | Plate-type heat-pipe radiator |
| US20070012430A1 (en) * | 2005-07-18 | 2007-01-18 | Duke Brian E | Heat exchangers with corrugated heat exchange elements of improved strength |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2018177443A1 (en) * | 2017-03-28 | 2018-10-04 | 杭州三花家电热管理系统有限公司 | Heat conduction assembly, heat conduction device, and preparation method for heat conduction assembly |
| CN108775131A (en) * | 2018-08-24 | 2018-11-09 | 浙江宏博新型建材有限公司 | A kind of safe floor of heat dissipation |
| CN109162405A (en) * | 2018-08-24 | 2019-01-08 | 浙江宏博新型建材有限公司 | A kind of wall heatiing panel |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105333758B (en) | 2017-03-22 |
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