CN105241286A - Inner-fin heat pipe - Google Patents
Inner-fin heat pipe Download PDFInfo
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- CN105241286A CN105241286A CN201510781664.0A CN201510781664A CN105241286A CN 105241286 A CN105241286 A CN 105241286A CN 201510781664 A CN201510781664 A CN 201510781664A CN 105241286 A CN105241286 A CN 105241286A
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- sloping portion
- heat pipe
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- tube wall
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Abstract
The invention provides a heat pipe. The heat pipe comprises a flat pipe, wherein the flat pipe comprises parallel pipe walls; a fluid channel is formed between the adjacent pipe walls. The heat pipe comprises fins arranged in the flat pipe, and the fins are arranged between the pipe walls; the fins comprise inclined portions inclining to the pipe walls, and protrusions are machined on the inclined portions in a stamped manner, so that fluid on the two sides of the inclined portions is continuous through holes formed in the inclined portions in a stamped manner; and the protrusions extend outwards from the inclined portions in the flowing direction of the fluid. Stamped protruded plate fin heat dissipation pieces are arranged in the heat pipe, and therefore the problem that the heat exchange efficiency of the noncondensable gas is low is solved, energy is greatly saved, and the problem that the heat exchange efficiency of the heat pipe is low is solved.
Description
Technical field
The invention belongs to heat pipe field, particularly relate to a kind of 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, form fluid passage between described adjacent tube wall, it is characterized in that, heat pipe comprises the fin be arranged in flat tube, described fin is arranged between tube wall, described fin comprises the sloping portion favouring tube wall, and sloping portion processes projection by impact style, thus the hole that the fluid of sloping portion both sides is formed by impact style on sloping portion is communicated with; Described projection stretches out from sloping portion along fluid 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 fin comprises horizontal component, described horizontal component and tube walls parallel and stick together with tube wall, and described sloping portion is connected with horizontal component; Described projection is isosceles triangle, the base of described isosceles triangle is arranged on sloping portion, the distance of adjacent tube wall is H, the length on isosceles triangle base is h, the distance of adjacent sloping portion is w, and the drift angle of isosceles triangle is b, and the angle of the bearing of trend of described projection and the flow direction of fluid is a, the angle of the acute angle between sloping portion and tube wall is c, meets following formula:
c6*h/H=c1*Ln(L*sin(a)/（w*sin(c))+c2,
sin(b/2)=c3+c4*sin(a)-c5*(sin(a))
2，
Wherein Ln is logarithmic function, and c1, c2, c3, c4, c5 are coefficients,
0.24<c1<0.25,0.68<c2<0.70,0.87<c3<0.88，0.68<c4<0.70，1.14<c5<1.15,
5.0<c6<6.5；
19°<a<71°，55°<b<165°,90°<c<70°；
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 that L is the distance of summit to base mid point of isosceles triangle with the relative face of adjacent sloping portion along the distance on tube wall direction.
As preferably, c1=0.245, c2=0.694,
c3=0.873，c4=0.691，c5=1.1454，c6=6.13。
As preferably, described sloping portion is multiple, and described sloping portion 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 sloping portion arranges multiple projection, and along the flow direction of fluid, described angle a is more and more less.
As preferably, same sloping portion arranges multiple projection, and multiple projection is staggered to stretch out from sloping portion both sides.
As preferably, the length that described projection extends is L, and same sloping portion 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 sloping portion, as preferably, base is identical with the angle of inclination of sloping portion, and the drift angle of described isosceles triangle is b, and same sloping portion 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 sloping portion, as preferably, base is identical with the angle of inclination of sloping portion, and the base of described isosceles triangle is S1, and same sloping portion 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 sloping portion 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 sloping portion plane;
Fig. 7 is another schematic diagram that the present invention arranges raised structures sloping portion 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 sloping portion both sides.
Reference numeral is as follows:
1 heat pipe, 2 fluid passages, 3 tube walls, 4 sloping portions, 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 sloping portion 4 tilted with tube wall 3, and described sloping portion is parallel to each other.By impact style processing projection 6 on sloping portion 4, thus the fluid of sloping portion 4 both sides is communicated with by the hole that sloping portion 4 is formed by impact style; Described projection 6 stretches out from sloping portion 4.
Described flat tube can be integration manufacture, also can be split manufacture.
Because sloping portion 4 is parallel to each other, between therefore adjacent sloping portion 4 and upper and lower tube wall, constitute parallelogram passage.
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 apsacline fin, and described fin 7 comprises horizontal component 5 and sloping portion 4, and described horizontal component 5 is parallel with tube wall 3 and stick together with tube wall 3, and described sloping portion 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 sloping portion 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, the length that described projection 6 extends is L, and along the flow direction of fluid, same sloping portion 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 sloping portion 4, and as preferably, base is identical with the angle of inclination of sloping portion, the drift angle of described isosceles triangle is b, along the flow direction of fluid, same sloping portion 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 sloping portion, as preferably, base is identical with the angle of inclination of sloping portion, and the base length of described isosceles triangle is h, along the flow direction of fluid, same sloping portion 4 arranges multiple projection 6, along the flow direction of fluid, same sloping portion 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 sloping portion 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 sloping portion 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 sloping portion 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.
The distance of adjacent tube wall is H, and the length on isosceles triangle base is h, and the distance of adjacent sloping portion is w, and the angle of the acute angle between sloping portion and tube wall is c, meets following formula:
c6*h/H=c1*Ln(L*sin(a)/（w*sin(c))+c2,
sin(b/2)=c3+c4*sin(a)-c5*(sin(a))
2，
Wherein Ln is logarithmic function, and c1, c2, c3, c4, c5 are coefficients,
0.24<c1<0.25,0.68<c2<0.70,0.87<c3<0.88，0.68<c4<0.70，1.14<c5<1.15,
5.0<c6<6.5；
19°<a<71°，55°<b<165°,90°<c<70°；
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 that L is the distance of summit to base mid point of isosceles triangle with the relative face of adjacent sloping portion along the distance on tube wall direction.
As preferably, c1=0.245, c2=0.694,
c3=0.873，c4=0.691，c5=1.1454，c6=6.13。
As preferably, 85 ° of <c<80 °.
As preferably, along with the increase of angle c, c6 is more and more less.
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 2.5 × h<S1<3.8 × h, and wherein S1 is with the distance of the mid point on the base of adjacent two isosceles triangle projections.Be preferably 3.0 × 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 3.2*L<S2<5.2*L.Be preferably S2=4.5*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.
For the concrete dimensional parameters do not mentioned, design according to normal heat exchanger.
As preferably, as shown in Figure 10, sloping portion is arranged multiple projection 6, described projection extends to the not homonymy of sloping portion
As preferably, same sloping portion is arranged arranges projection more, and to arrange projection different to the extension side of sloping portion from other at least one row's projection.
As preferably, adjacent projection of often arranging extends to the not homonymy of sloping portion.
By setting like this, fluid can be made in the passage of sloping portion 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, form fluid passage between described adjacent tube wall, it is characterized in that, heat pipe comprises the fin be arranged in flat tube, described fin is arranged between tube wall, described fin comprises the sloping portion favouring tube wall, and sloping portion processes projection by impact style, thus the hole that the fluid of sloping portion both sides is formed by impact style on sloping portion is communicated with; Described projection stretches out from sloping portion along fluid 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 fin comprises horizontal component, described horizontal component and tube walls parallel and stick together with tube wall, and described sloping portion is connected with horizontal component; Described projection is isosceles triangle, the base of described isosceles triangle is arranged on sloping portion, the distance of adjacent tube wall is H, the length on isosceles triangle base is h, the distance of adjacent sloping portion is w, and the drift angle of isosceles triangle is b, and the angle of the bearing of trend of described projection and the flow direction of fluid is a, the angle of the acute angle between sloping portion and tube wall is c, meets following formula:
c6*h/H=c1*Ln(L*sin(a)/（w*sin(c))+c2,
sin(b/2)=c3+c4*sin(a)-c5*(sin(a))
2，
Wherein Ln is logarithmic function, and c1, c2, c3, c4, c5 are coefficients,
0.24<c1<0.25,0.68<c2<0.70,0.87<c3<0.88，0.68<c4<0.70，1.14<c5<1.15,
5.0<c6<6.5；
19°<a<71°，55°<b<165°,90°<c<70°；
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 that L is the distance of summit to base mid point of isosceles triangle with the relative face of adjacent sloping portion along the distance on tube wall direction.
4. heat pipe as claimed in claim 3, is characterized in that, c1=0.245, c2=0.694,
c3=0.873，c4=0.691，c5=1.1454，c6=6.13。
5. heat pipe as claimed in claim 1 or 2, it is characterized in that, described sloping portion is multiple, and described sloping portion 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 |
|---|---|---|---|
| CN201510781664.0A CN105241286B (en) | 2015-11-16 | 2015-11-16 | Inner-fin heat pipe |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510781664.0A CN105241286B (en) | 2015-11-16 | 2015-11-16 | Inner-fin heat pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105241286A true CN105241286A (en) | 2016-01-13 |
| CN105241286B CN105241286B (en) | 2017-05-17 |
Family
ID=55039022
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510781664.0A Expired - Fee Related CN105241286B (en) | 2015-11-16 | 2015-11-16 | Inner-fin heat pipe |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108444321A (en) * | 2018-03-16 | 2018-08-24 | 青岛金玉大商贸有限公司 | A kind of condenser pipe extends to the heat pipe evaporator of the variation of the length rule in water tank |
| CN110057139A (en) * | 2019-05-30 | 2019-07-26 | 宁波奥克斯电气股份有限公司 | A kind of evaporator and air conditioner |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2253448Y (en) * | 1996-02-14 | 1997-04-30 | 张心颖 | Split assembled heat pipe solar water heater |
| 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 |
| CN204142069U (en) * | 2014-10-08 | 2015-02-04 | 贵州晟泰铝业有限公司 | A kind of aluminum heat radiating flat tube |
-
2015
- 2015-11-16 CN CN201510781664.0A patent/CN105241286B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2253448Y (en) * | 1996-02-14 | 1997-04-30 | 张心颖 | Split assembled heat pipe solar water heater |
| 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 |
| CN204142069U (en) * | 2014-10-08 | 2015-02-04 | 贵州晟泰铝业有限公司 | A kind of aluminum heat radiating flat tube |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108444321A (en) * | 2018-03-16 | 2018-08-24 | 青岛金玉大商贸有限公司 | A kind of condenser pipe extends to the heat pipe evaporator of the variation of the length rule in water tank |
| CN110057139A (en) * | 2019-05-30 | 2019-07-26 | 宁波奥克斯电气股份有限公司 | A kind of evaporator and air conditioner |
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| Publication number | Publication date |
|---|---|
| CN105241286B (en) | 2017-05-17 |
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