CN105258542B - Ladder-shaped inner finned heat pipe - Google Patents
Ladder-shaped inner finned heat pipe Download PDFInfo
- Publication number
- CN105258542B CN105258542B CN201510828877.4A CN201510828877A CN105258542B CN 105258542 B CN105258542 B CN 105258542B CN 201510828877 A CN201510828877 A CN 201510828877A CN 105258542 B CN105258542 B CN 105258542B
- Authority
- CN
- China
- Prior art keywords
- heat pipe
- sloping portion
- fin
- tube wall
- fluid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Abstract
The invention provides a heat pipe. The heat pipe comprises a flat pipe and fins arranged in the flat pipe, wherein the flat pipe comprises pipe walls which are parallel to each other; a fluid passage is formed between the adjacent pipe walls; the fins are arranged between the pipe walls; the fins comprise inclined parts inclined to the pipe walls, and bulges are formed on the inclined parts by machining in a stamping manner, thereby causing fluid at the two sides of the inclined parts to be communicated through holes which are formed in the inclined parts in a stamping manner; and the bulges extend outwards from the inclined parts along the fluid flow direction. The heat pipe has the beneficial effects that the problem of low heat transfer efficiency of the heat pipe containing non-condensable gases is solved by arranging the stamped and bulged plate-fin cooling plates in the heat pipe, energy sources are greatly saved, and the problem of low efficiency of a heat pipe heat transfer system is overcome.
Description
Technical field
The invention belongs to heat pipe field, more particularly to a kind of inner fin heat pipe.
Background technology
Hot pipe technique is George Ge Luofo of U.S. Los Alamos (Los Alamos) National Laboratory in 1963
One kind that (George Grover) is invented is referred to as the heat transfer element of " heat pipe ", and it is taken full advantage of heat-conduction principle and is situated between with phase transformation
The quick thermal transport property of matter, is delivered to rapidly the heat of thermal objects outside thermal source through heat pipe, and its capacity of heat transmission exceedes appoints
The capacity of heat transmission of what known metal.
The industries such as aerospace, military project are widely used in before hot pipe technique, since being introduced into radiator manufacturing so that
People change the mentality of designing of traditional heat sinks, broken away from it is simple by high air quantity motor obtaining the list of more preferable radiating effect
One radiating mode, using hot pipe technique so that radiator obtains satisfied heat transfer effect, opens radiating industry new world.At present
Heat pipe is widely used in various heat transmission equipments.
Generally, heat pipe includes evaporation ends and condensation end, and the fluid heat absorption evaporation of evaporator section is carried out to condensation end cold
It is solidifying, the fluid of outside is transferred heat to, either, can there is biphase gas and liquid flow in evaporation ends or condensation end in heat transfer process
Situation, it is and aging with heat pipe, some on-condensible gases can be produced in heat pipe, so as to cause the drop of heat pipe heat exchanging coefficient
It is low.
Additionally, heat pipe evaporation ends and condensation end are in heat transfer process, each position heat exchange amount of evaporation ends and condensation end is not
Together, so as to causing Local Heat Transfer uneven.
For the problems referred to above, the invention provides a kind of new heat pipe, so as to solve the heat exchange in the case of heat pipe heat exchanging
The problem that coefficient is low and its heat exchange is uneven.
The content of the invention
The invention provides a kind of new heat pipe, so as to the technical problem for solving above to occur.
To achieve these goals, technical scheme is as follows：
A kind of heat pipe, including flat tube, the flat tube include tube wall parallel to each other, shape between the adjacent tube wall
Into fluid passage, it is characterised in that heat pipe includes the fin being arranged in flat tube, the fin is arranged between tube wall, its
It is characterised by, the fin is trapezoidal fin, and the trapezoidal fin includes the sloping portion and horizontal component for favouring tube wall, incline
Inclined portion is divided to two trapezoidal waists of composition, on sloping portion processes bur by impact style, so that sloping portion both sides
The hole connection that fluid is formed by impact style on sloping portion；The bur from sloping portion along mixture flow direction to
Outer extension.
Preferably, heat pipe includes evaporation ends and condensation end, fin is arranged on the evaporation ends and/or condensation end.
Preferably, described trapezoidal for isosceles trapezoid, the bur is isosceles triangle, the base of the isosceles triangle
It is arranged on sloping portion, the distance of adjacent tube wall is H, and the length on isosceles triangle base is h, adjacent sloping portion
Distance is w, and the drift angle of isosceles triangle is b, and the bearing of trend of the bur is a with the angle of the flow direction of mixture, full
Sufficient equation below：
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,
0.235<c1<0.255, 0.678<c2<0.71,0.80<c3<0.90,0.66< c4<0.72,
1.12 <c5<1.16,7.5<c6<8.5；
19°<a<71 °, 55 °<b<165°；
10mm<w<15mm, 6mm<H<14mm；
0.18<L*sin(a)/w<0.42, 0.28<c6*h/H<0.48；
H is that, with the distance between relative face of adjacent tube wall, W is in isosceles trapezoid waist with the midpoint on isosceles triangle base
On point in the distance that another waist of isosceles trapezoid is extended to parallel to tube wall direction, L for isosceles triangle summit to base
The distance at midpoint；
The acute angle on the base of isosceles trapezoid be c, 90 °<c<70°
Preferably, c1=0.242, c2=0.69,
C3=0.85, c4=0,67, c5=1.140, c6=8.
Preferably, the plurality of sloping portion is parallel to each other.
Preferably, the angle formed by the flow direction of described projection and fluid is acute angle.
Preferably, the bearing of trend of the projection is a with the angle of the flow direction of fluid, same rake sets up separately
Multiple projections are put, along the flow direction of fluid, described angle a is less and less.
Preferably, same sloping portion arranges multiple projections, multiple projections are interlocked from two epitaxial lateral overgrowth of sloping portion
Stretch.
Preferably, the length that the projection extends is L, same sloping portion arranges multiple projections, along fluid
Flow direction, described length L are increasing.
Preferably, the projection is isosceles triangle, the base of the isosceles triangle is arranged on sloping portion, is made
For preferred, base is identical with the angle of inclination of sloping portion, and the drift angle of the isosceles triangle is b, and same rake sets up separately
Multiple projections are put, along the flow direction of fluid, described drift angle b is increasing.
Preferably, the projection is isosceles triangle, the base of the isosceles triangle is arranged on sloping portion, is made
For preferred, base is identical with the angle of inclination of sloping portion, and the base of the isosceles triangle is S1, and same rake sets up separately
Multiple projections are put, along the flow direction of fluid, described S1 is less and less.
Compared with prior art, plate type heat exchanger of the invention and its heat exchange tube wall have the following advantages：
1）The present invention is by the regular change of outside fin so that heat pipe heat radiation is uniform on the whole, it is to avoid heat pipe local
Temperature overheating, causes radiating effect excessively poor, extends the heat pipe life-span.
2）The plate wing fin of projection of the present invention by arranging punching press in heat pipe, solves containing on-condensible gas or two
The low problem of the heat exchange efficiency that mutually flows, has greatly saved the energy, has overcome the low problem of heat pipe heat exchanging system efficiency.
3）The aperture that punching press " projection " is formed, by the impact of " projection " downstream pressure field, is capable of achieving fin media of both sides
Pressure and mass exchange, the stability of viscous sublayer and liquid film is damaged, enhanced heat exchange；
4）By substantial amounts of experiment, it is determined that the physical dimension of optimal heat pipe；
5）It is H by the distance for designing adjacent tube wall, the length on isosceles triangle base is h, adjacent sloping portion
Distance be w, the drift angle of isosceles triangle is b, and the bearing of trend of the projection is a etc. with the angle of the flow direction of fluid
Change of the parameter along fluid flow direction, improves heat exchange efficiency or reduces Fluid pressure.
Description of the drawings
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 that fin heat pipe evaporation ends or condensation end cross section are arranged outside the present invention；
Fig. 4 is the cross section structural representation of one heat pipe inner fin of the present invention；
Fig. 5 is the improved structure schematic diagram that fin heat pipe evaporation ends or condensation end cross section are arranged outside the present invention；
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 the 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 projections of the present invention extend to sloping portion both sides.
Reference 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 is adiabatic
Section, 10 condensation segments, 11 outside fins.
Specific embodiment
Below in conjunction with the accompanying drawings the specific embodiment of the present invention is described in detail.
Herein, if no specified otherwise, it is related to formula, "/" represents division, and "×", " * " represent multiplication.
As shown in figure 1, a kind of heat pipe 1, including evaporation ends 8, condensation end 10, preferably also includes adiabatic end 9, evaporation ends 8 are inhaled
Heat, the fluid evaporator sealed in heat pipe, then into condensation end 10, Jing heats pass to outside by condensation end to fluid, then
Fluid after heat exchange becomes liquid, then flows into evaporation ends 8.
As shown in Fig. 2 the heat pipe 1 includes flat tube, the flat tube includes tube wall 3 parallel to each other, described adjacent
Tube wall 3 between formed fluid passage 2.Fin 7 is set inside flat tube 1, preferably in evaporation ends 8 and/or the condensation of heat pipe 1
Fin 7 is set in end 10.The fin is trapezoidal fin, and the trapezoidal fin includes sloping portion 4 and the water for favouring tube wall
Flat part, sloping portion 4 constitute trapezoidal two waist..Projection 6 is processed by impact style on sloping portion 4, so that inclining
The fluid of 4 both sides of inclined portion point is by being connected by the hole that impact style is formed on sloping portion 4；The projection 6 is from sloping portion 4
Stretch out.
The flat tube can be integration manufacture, or split manufacture.
By arranging projection 6, have the following advantages：
1）On the one hand laminar sublayer can be destroyed, does not lose heat exchange area, and " point " and " hole " can respectively not
With fluid, enhanced heat exchange are disturbed on height；
2）The aperture that punching press projection is formed, by the impact of projection downstream pressure field, is capable of achieving the pressure of fin media of both sides
Power and mass exchange, damage to the stability of viscous sublayer and liquid film, enhanced heat exchange.
3）For the fluid containing on-condensible gas or two-phase fluid, can by " projection " realize expand gas-liquid interface with
And gas phase boundary and cooling wall contact area and strengthen disturbance.
Above-mentioned measure is taken in evaporation ends 8 and/or condensation end, the heat exchange efficiency of fluid can greatly be improve.With
Normal fluid heat transfer is compared, it is possible to increase the heat exchange efficiency of 15-25%.
Preferably, the angle formed by the flow direction of described projection 6 and fluid is acute angle, it should be noted that
The flow direction of mentioned fluid refers to flow direction of the fluid from evaporation ends to condensation end herein and below.
Preferably, as shown in figure 4, described fin 7 is apsacline fin, the fin 7 includes horizontal component 5 and inclines
Inclined portion points 4, the horizontal component 5 is parallel with tube wall 3 and sticks together with tube wall 3, the sloping portion 4 and horizontal component 5
Connection.
In Fig. 6, the flow direction of fluid is from left to right.But left and right herein simply illustrates fluid along the flowing of projection
Direction, is not offered as actual certain left and right flowing.
As shown in figure 9, the bearing of trend of the projection 6 is a with the angle of the flow direction of fluid, as shown in fig. 6, along
The flow direction of fluid, same sloping portion 4 arrange multiple projections 6, and along the flow direction of fluid, described angle a gets over
Come bigger.
It is found through experiments, by becoming larger for angle a, compared with angle a is identical, it is possible to achieve higher changes
The thermal efficiency, can about improve 10% or so heat exchange efficiency.
Preferably, along the flow direction of mixture, the amplitude that angle a becomes big is less and less.It is found through experiments, becomes
Change the big amplitude of the change of angle a, it is ensured that in the case of heat exchange efficiency, further reduce flow resistance, about can reduce
5% or so flow resistance.
Preferably, the length that the projection 6 extends is L, along the flow direction of fluid, same sloping portion 4 sets
Multiple projections 6 are put, along the flow direction of fluid, described length L is increasing.Be found through experiments, by length L by
Gradual change is big, compared with length L is identical, it is possible to achieve higher heat exchange efficiency, can about improve 9% or so heat exchange effect
Rate.
Preferably, along the flow direction of fluid, the amplitude that length L becomes big is less and less.It is found through experiments, length
The amplitude that the change of L is big is less and less, it is ensured that in the case of heat exchange efficiency, further reduces flow resistance, about can drop
Low 5% or so flow resistance.
Preferably, the projection 6 is isosceles triangle, the base of the isosceles triangle is arranged on sloping portion 4,
Preferably, base is identical with the angle of inclination of sloping portion, the drift angle of the isosceles triangle is b, along the flowing of fluid
Direction, same sloping portion 4 arrange multiple projections 6, and along the flow direction of fluid, on base, length keeps constant situation
Under, described projection drift angle b is less and less.It is found through experiments, by tapering into for projection drift angle b, with the complete phases of drift angle b
With compared with, it is possible to achieve higher heat exchange efficiency, 7% or so heat exchange efficiency can be about improved.
Preferably, along the flow direction of fluid, the amplitude that drift angle b diminishes is less and less.It is found through experiments, drift angle
The amplitude that b diminishes is less and less, it is ensured that in the case of heat exchange efficiency, further reduces flow resistance, about can reduce
4% or so flow resistance.
Preferably, the projection 6 is isosceles triangle, the base of the isosceles triangle is arranged on sloping portion,
Preferably, base is identical with the angle of inclination of sloping portion, the base length of the isosceles triangle is h, along fluid
Flow direction, same sloping portion 4 arrange multiple projections 6, and along the flow direction of fluid, same sloping portion 4 is arranged
Multiple projections, in the case where drift angle keeps constant, along the flow direction of fluid, described h is increasing.Sent out by experiment
Existing, becoming larger by h, compared with h is identical, it is possible to achieve higher heat exchange efficiency can about improve 7% or so
Heat exchange efficiency.
Preferably, along the flow direction of fluid, the amplitude that h becomes big is less and less.It is found through experiments, h becomes big
Amplitude is less and less, it is ensured that in the case of heat exchange efficiency, further reduces flow resistance, can about reduce by 5% or so
Flow resistance.
Preferably, along the flow direction of fluid, same sloping portion arranges multiple rows of projection 6, as shown in Figures 6 and 7, often
The distance between row's projection is S2, and along the flow direction of fluid, described S2 is increasing.Why it is arranged such, mainly
Purpose is big by the change of S2, realizes, in the case where heat exchange efficiency is ensured, further reducing flow resistance.Sent out by experiment
Existing, flow resistance reduces by 10% or so.
The S2 is the base of the projection with adjacent row as computed range.
Preferably, as shown in fig. 7, multiple rows of projection 6 is shifted structure.In Fig. 7, fluid is to flow from top to bottom.But herein
Simply explanation fluid, along the flow direction of projection, is not offered as reality and necessarily flows up and down up and down.
Find in an experiment, the distance of adjacent tube wall 3 can not be excessive, crossing conference causes the reduction of heat exchange efficiency, too small meeting
Cause flow resistance excessive, in the same manner, base length, drift angle, projection, the distance of fin sloping portion for isosceles triangle with
The angle of fluid flow direction all can not be excessive or too small, the excessive or too small reduction or flowing that can all cause heat exchange efficiency
The change of resistance is big, therefore the base length of the distance in adjacent tube wall 3, isosceles triangle, drift angle, projection, fin sloping portion
An optimized size relationship is met and the angle of fluid flow direction between.
Therefore, the present invention is the thousands of numerical simulations and test data by multiple various sizes of heat exchangers,
In the case of meeting industrial requirements pressure-bearing（Below 10MPa）, in the case where maximum heat exchange amount is realized, the optimal heat exchange for summing up
The dimensionally-optimised relation of tube wall.
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,
The angle of the acute angle between sloping portion and tube wall is c, meets equation below：
Preferably, described trapezoidal for isosceles trapezoid, the bur is isosceles triangle, the base of the isosceles triangle
It is arranged on sloping portion, the distance of adjacent tube wall is H, and the length on isosceles triangle base is h, adjacent sloping portion
Distance is w, and the drift angle of isosceles triangle is b, and the bearing of trend of the bur is a with the angle of the flow direction of mixture, full
Sufficient equation below：
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,
0.235<c1<0.255, 0.678<c2<0.71,0.80<c3<0.90,0.66< c4<0.72,
1.12 <c5<1.16,7.5<c6<8.5；
19°<a<71 °, 55 °<b<165°；
10mm<w<15mm, 6mm<H<14mm；
0.18<L*sin(a)/w<0.42, 0.28<c6*h/H<0.48；
H is that, with the distance between relative face of adjacent tube wall, W is in isosceles trapezoid waist with the midpoint on isosceles triangle base
On point in the distance that another waist of isosceles trapezoid is extended to parallel to tube wall direction, L for isosceles triangle summit to base
The distance at midpoint；
The acute angle on the base of isosceles trapezoid be c, 90 °<c<70°
Preferably, c1=0.242, c2=0.69,
C3=0.85, c4=0,67, c5=1.140, c6=8.
Preferably, with the increase of angle c, c6 is less and less.
Preferably, 9<H<12mm.
By the optimal geometric scale of " projection " that go out of above-mentioned formula, heat exchange efficiency can be improved, while can be real
Now only to viscous sublayer or comprising liquid film and to the reinforcing comprising gas phase boundary different scale internal thermal resistance, it is to avoid measure
Degree, causes unnecessary drag losses.
Preferably, the base of the adjacent projection of described same row is all on one wire, the adjacent projection of same row
Distance is S1, the 2.5 × h<S1<3.8 × h, wherein S1 are with the midpoint on the base of two neighboring isosceles triangle projection
Distance.Preferably 3.0 × h=S1.
Preferably, the base of the isosceles triangle of the projection of adjacent row is parallel to each other, the summit of isosceles triangle is on earth
The distance at side midpoint be L, adjacent row apart from S2 be 3.2*L<S2<5.2*L.Preferably S2=4.7*L
When the base of the isosceles triangle of adjacent row is different, take the weighted mean on two bases to calculate.
Preferably, the angle of the isosceles triangle of same row is identical with base.I.e. shape is identical, is equal
Shape.
For formula above, the projection different for front and rear row size, also still it is suitable for.
Preferably, the wall thickness of fin is 0.6-1.1mm；Preferably, 0.8-1.0mm.
For the concrete dimensional parameters do not mentioned, it is designed according to normal heat exchanger.
Preferably, as shown in Figure 10, multiple projections 6, difference of the projection to sloping portion are arranged on sloping portion
Side extends
Preferably, same sloping portion arranges multiple rows of projection, at least row's projection is with other row's projections to rake
The extension side divided is different.
Preferably, adjacent projection of often arranging extends to the not homonymy of sloping portion.
By being arranged such, fluid can be caused to replace heat exchanging tampering in the passage of sloping portion both sides, further carried
High heat exchange efficiency.Compared with the same side, it is possible to increase 8% or so.
Preferably, as shown in Fig. 2 the outside of tube wall 3 in heat pipe 1 arranges fin 11, preferably in the evaporation ends 8
And/or fin is set outside condensation end 10.
Preferably, the fin is straight panel shape, the flow direction of the bearing of trend of fin along fluid, i.e., such as Fig. 2 institutes
Show, along perpendicular to the direction of paper.
Preferably, along the flow direction of fluid, 11 height of outside fin constantly increases, and the amplitude that height increases is got over
Come bigger.By increasing fin height, so as to increase the heat exchange area of fin.Experiment finds, by being arranged such, high with fin
The identical heat exchange efficiency compared, about 5% can be improved of degree.
Preferably, as shown in figure 5, along the centre of 1 cross section of heat pipe to both sides, the height of the fin 11 constantly subtracts
It is few.Wherein, positioned at the centre position of heat pipe 1, the height highest of fin.
Because being found by experiment that, heat pipe is most in middle part radiating, and from middle part to both sides, radiating is tapered into, therefore logical
Cross the outside fin height change that heat pipe is set, so that the area of dissipation of heat pipe is maximum at middle part, it is minimum in both sides so that
Middle part heat-sinking capability is maximum, so meets the heat dissipation law of heat pipe heat so that heat pipe heat radiation is uniform on the whole, it is to avoid heat pipe office
Portion's temperature overheating, causes radiating effect excessively poor, causes the shortening in heat pipe life-span.
Preferably, from centre to both sides, the amplitude that the height of the fin 11 is reduced constantly increases.
By above-mentioned setting, and meet the heat dissipation law of heat pipe, further improve the heat exchange efficiency of heat pipe, increase heat pipe
Life-span.
Preferably, the heat pipe is gravity assisted heat pipe.
Preferably, the inside of the heat pipe arranges capillary materials.
Preferably, the running temperature of the heat pipe is 100-500 DEG C, as preferably 250-400 degree Celsius.
Although the present invention is disclosed as above with preferred embodiment, the present invention is not limited to this.Any art technology
Personnel, without departing from the spirit and scope of the present invention, can make various changes or modifications, therefore protection scope of the present invention should
When being defined by claim limited range.
Claims (4)
1. a kind of heat pipe, including flat tube, the flat tube include tube wall parallel to each other, are formed between the adjacent tube wall
Fluid passage, it is characterised in that heat pipe includes the fin being arranged in flat tube, the fin is arranged between tube wall, and which is special
Levy and be, the fin is trapezoidal fin, and the trapezoidal fin includes the sloping portion and horizontal component for favouring tube wall, incline
Part constitutes trapezoidal two waist, processes bur by impact style, so that the stream of sloping portion both sides on sloping portion
The hole connection that body is formed by impact style on sloping portion；The bur is outside along mixture flow direction from sloping portion
Extend；
Described trapezoidal for isosceles trapezoid, the bur is isosceles triangle, and the base of the isosceles triangle is arranged on rake
On point, 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, isosceles
The drift angle of triangle is b, and the bearing of trend of the bur is a with the angle of the flow direction of mixture, meets equation below：
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,
0.235<c1<0.255, 0.678<c2<0.71,0.80<c3<0.90,0.66< c4<0.72,
1.12 <c5<1.16,7.5<c6<8.5；
19°<a<71 °, 55 °<b<165°；
10mm<w<15mm, 6mm<H<14mm；
0.18<L*sin(a)/w<0.42, 0.28<c6*h/H<0.48；
H is the distance between relative face of adjacent tube wall, adjacent sloping portion apart from w be isosceles triangle base midpoint
In the distance that another waist of isosceles trapezoid is extended to parallel to tube wall direction, L is isosceles triangle to point on isosceles trapezoid waist
Summit to base midpoint distance；
The acute angle on the base of isosceles trapezoid be c, 90 °<c<70°.
2. heat pipe as claimed in claim 1, it is characterised in that c1=0.242, c2=0.69,
C3=0.85, c4=0.67, c5=1.140, c6=8.
3. heat pipe as claimed in claim 1 or 2, it is characterised in that the plurality of sloping portion is parallel to each other.
4. heat pipe as claimed in claim 1 or 2, it is characterised in that what the flow direction of described projection and fluid was formed
Angle is acute angle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510828877.4A CN105258542B (en) | 2015-11-25 | 2015-11-25 | Ladder-shaped inner finned heat pipe |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510828877.4A CN105258542B (en) | 2015-11-25 | 2015-11-25 | Ladder-shaped inner finned heat pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105258542A CN105258542A (en) | 2016-01-20 |
| CN105258542B true CN105258542B (en) | 2017-04-12 |
Family
ID=55098331
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510828877.4A Active CN105258542B (en) | 2015-11-25 | 2015-11-25 | Ladder-shaped inner finned heat pipe |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105258542B (en) |
Citations (5)
| 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 |
| JP2006234267A (en) * | 2005-02-24 | 2006-09-07 | Denso Corp | Ebullient cooling device |
| CN101363696A (en) * | 2008-09-03 | 2009-02-11 | 赵耀华 | Flat hot pipe for cooling electron device and processing technology thereof |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 CN201510828877.4A patent/CN105258542B/en active Active
Patent Citations (5)
| 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 |
| JP2006234267A (en) * | 2005-02-24 | 2006-09-07 | Denso Corp | Ebullient cooling device |
| CN101363696A (en) * | 2008-09-03 | 2009-02-11 | 赵耀华 | Flat hot pipe for cooling electron device and processing technology thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105258542A (en) | 2016-01-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105423789B (en) | Triangular inner-fin heat pipe | |
| CN105202955B (en) | A kind of heat pipe of external setting fin | |
| JPH02287094A (en) | Heat exchanger | |
| US20030178188A1 (en) | Micro-channel heat exchanger | |
| KR20170063543A (en) | Corrugated fins for heat exchanger | |
| CN105333758B (en) | Right-angle internally-finned heat tube | |
| CN106642826A (en) | Heat exchanger | |
| CN105241286B (en) | Inner-fin heat pipe | |
| CN107709917A (en) | The interior fin of heat exchanger | |
| JPS6334393B2 (en) | ||
| CN105387741B (en) | A kind of heat exchanger plate group of Novel asymmetric channel design | |
| CN105258542B (en) | Ladder-shaped inner finned heat pipe | |
| CN105241289B (en) | The inner fin heat pipe that a kind of projection length gradually changes | |
| CN105241294B (en) | Triangular protruding stab plate-fin heat exchanger | |
| US20100294474A1 (en) | Heat exchanger tube | |
| CN105258537B (en) | Parallelogram plate-fin heat exchanger | |
| CN212620242U (en) | Radiating tube structure with wavy flying wings | |
| CN211626225U (en) | Heat-transfer pipe heat radiation structure | |
| CN203731744U (en) | Stable parallel flow heat exchanger | |
| CN105157459B (en) | It is a kind of that the right angle plate-fin heat exchanger that bur is set is condensed for non-azeotrope multicomponent mixture | |
| CN105180692B (en) | A kind of fin and plate type heat exchanger for the condensation of non-azeotrope multicomponent mixture | |
| JP3957021B2 (en) | Heat exchanger | |
| CN109855451B (en) | Steam heat exchanger capable of uniformly distributing flow | |
| CN105318768B (en) | A kind of inclined plate type fin | |
| CN205066522U (en) | A triangle -shaped finned plate heat exchanger that is used for bur that sets up of non -azeotropic multi -component mixture condensation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190402 Address after: 230000 B-1512, west of Ganquan Road, Shushan District, Hefei, Anhui. Patentee after: Anhui Eagle Dragon Industrial Design Co., Ltd. Address before: 266075 room 0201, block A, 75 Fuzhou South Road, Shinan District, Qingdao, Shandong. Patentee before: Zhao Wei |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190821 Address after: 526000 Dazhou, Mugang Town, Zhaoqing City, Guangdong Province, to the north of Xincun, West Economic Co-operatives Patentee after: Zhaoqing Meisheng Electrical Heater Co., Ltd. Address before: Ganquan road Shushan District of Hefei City, Anhui Province, 230000 West hillock road to the South Wild Garden commercial office building room B-1512 Patentee before: Anhui Eagle Dragon Industrial Design Co., Ltd. |
|
| TR01 | Transfer of patent right |