CN108827045B - A kind of loop circuit heat pipe of uniform pressure - Google Patents
A kind of loop circuit heat pipe of uniform pressure Download PDFInfo
- Publication number
- CN108827045B CN108827045B CN201810488378.9A CN201810488378A CN108827045B CN 108827045 B CN108827045 B CN 108827045B CN 201810488378 A CN201810488378 A CN 201810488378A CN 108827045 B CN108827045 B CN 108827045B
- Authority
- CN
- China
- Prior art keywords
- tedge
- separating device
- collector
- shell
- condensation
- 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.)
- Expired - Fee Related
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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
- 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
- F28D15/0266—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 with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
Abstract
The present invention provides a kind of heat pipes, including evaporation collector, condensation collector, tedge and return pipe, separating device is set in the tedge, the separating device includes core and shell, the core setting is in the shell, the shell is connected and fixed with heat transfer tube wall, and the core includes multiple concentric tubes and fin, and the fin connects adjacent concentric tube；Intercommunicating pore is set on the concentric tube and/or fin.The present invention passes through setting intercommunicating pore, it can guarantee to interconnect between adjacent annular distance, pressure that can uniformly between annular distance, so that the fluid of high pressure runner flows to low pressure, liquid and gas can also further be separated while fluid flows simultaneously, be conducive to further stablize two-phase flow.
Description
Technical field
The invention belongs to heat pipe field more particularly to a kind of heat exchange heat pipes.
Background technique
Hot pipe technique is George Ge Luofo of U.S. Los Alamos (Los Alamos) National Laboratory in 1963
One kind of (George Grover) invention is known as the heat transfer element of " heat pipe ", it takes full advantage of heat-conduction principle and phase transformation is situated between
The heat of thermal objects is transmitted to outside heat source rapidly by the quick thermal transport property of matter through heat pipe, and the capacity of heat transmission is more than to appoint
The capacity of heat transmission of what known metal.
The industries such as aerospace, military project were widely used in front of hot pipe technique, since being introduced into radiator manufacturing, so that
People change the mentality of designing of traditional heat sinks, get rid of the list for obtaining more preferable heat dissipation effect by high air quantity motor merely
One radiating mode makes radiator obtain satisfied heat transfer effect using hot pipe technique, opens heat dissipation industry new world.At present
Heat pipe is widely used in various heat exchange equipments, including nuclear power field, such as the UTILIZATION OF VESIDUAL HEAT IN of nuclear power etc..
On the one hand, heat pipe is in evaporation process, inevitably in carrying of liquids to tedge, simultaneously as condensation end
Exothermic condensation so that liquid also inevitably enters tedge, so that tedge there are liquid in condensation end
Interior fluid is liquid-vapor mixture, while heat pipe in the process of running can be because of the on-condensible gas of aging generation, on-condensible gas one
As rise to the condensation end on heat pipe top, the presence of on-condensible gas leads to the pressure increase in condensation end of heat pipe, and pressure makes
Flowing in the upward riser of liquid.Greatly affect the efficiency of heat exchange.
On the other hand, condensation this section of collector, because the space of this section becomes larger suddenly, space are exported to from tedge
Variation will lead to quickly flowing upwards out and assemble for gas, therefore spatial variations will lead to the vapour phase (vapour group) of aggregation from tedge
Position enters condensation collector, and due to gas (vapour) liquid density contrast, air mass leaves adapter tube position and will move rapidly upward, and air mass is former empty
Between position the liquid of wall surface is pushed away by air mass while will also spring back and hit wall surface rapidly, formed impingement phenomenon.Gas (vapour) liquid phase
More discontinuous, air mass aggregation is bigger, and Impact energy is bigger.Impingement phenomenon will cause biggish noise vibration and mechanical shock, right
Equipment damages.
The present inventor also devises a kind of multitube separating device in applying in front, shown in Figure 6.But such dress
It sets and finds in operation, because being to be closely linked between pipe, the space A formed between three root canals is relatively
Small, because the convex arc that space A is three root canals is formed, most of area stenosis of space A will cause fluid and be difficult to enter
Pass through, cause fluid short, to affect the heat exchange of fluid, good current stabilization can not be played the role of.Simultaneously as above-mentioned knot
More root canal subgroups of structure are combined, and manufacture is difficult.
In view of the above-mentioned problems, the present invention is improved on the basis of invention in front, a kind of new heat pipe is provided, from
And solve the problems, such as that the coefficient of heat transfer in the case where heat pipe heat exchanging is low and its heat exchange is non-uniform.
Summary of the invention
The present invention provides a kind of new heat pipes, to solve the technical issues of front occurs.
To achieve the goals above, technical scheme is as follows:
A kind of heat pipe, including evaporation collector, condensation collector, tedge and return pipe, the tedge and evaporation collector and
Condensation collector is connected, and the evaporation collector is located at lower part, and the condensation collector is located at top, and the fluid is in evaporation collector
Heat absorption evaporation, enters condensation collector by tedge, condenses after being exchanged heat in condensation collector, the fluid of condensation passes through reflux
Pipe returns to evaporation collector；Separating device is set in the tedge, the multiple separating devices of setting in same root tedge, along upper
The short transverse of riser, the spacing between adjacent separating device constantly reduce.
Preferably, the ever-reduced amplitude of spacing between adjacent separating device is got over along the short transverse of tedge
Come bigger.
Preferably, separating device is arranged in the tedge, the separating device includes core and shell, the core
In the shell, the shell is connected and fixed with heat transfer tube wall, and the core includes multiple concentric tubes and fin, the rib for setting
Piece connects adjacent concentric tube.
Preferably, intercommunicating pore is arranged on the concentric tube and fin.
Preferably, the extended line of the fin passes through the center of circle of concentric tube
Preferably, the multiple separating devices of setting in tedge, the height that distance rises tube inlet is H, adjacent separation dress
It the distance between sets as S, S=F1(H), meet following require:
S’<0,S”>0。
Preferably, the multiple separating devices of setting in tedge, the height that distance rises tube inlet is H, separating device
Length is C, C=F2(H), meet following require:
C’>0,C”>0。
Preferably, the multiple separating devices of setting in tedge, the height that distance rises tube inlet is H, separating device
Annular distance diameter is D, D=F3(H), meet following require:
D’<0,D”>0。
Preferably, groove is arranged in the rising inside pipe wall, the shell of the separating device is arranged in groove, described outer
The inner wall of shell and the aligning inner of tedge.
Preferably, tedge is welded for multi-segment structure, separating device is arranged in the junction of multi-segment structure.
Preferably, the distance between adjacent separating device is S, the length of separating device is C, and the outer diameter of heat exchanger tube is W,
The radius of neighboring concentric pipe is respectively R2And R1, wherein R2>R1, the radian of the circular arc between adjacent fin is h, is met as follows
It is required that:
S/C=a-b*LN (W/E)；
E=((h*R2 2-h*R1 2)/2)1/2；
Wherein LN is logarithmic function, and a, b are parameters, wherein 4.9 < a < 6.1,1.3 <b < 2.1；
Wherein the spacing of separating device is the both ends the distance between opposite with adjacent separating device；
34<W<58mm；
19<C<27mm；
50<S<70mm。
Preferably, a=5.42, b=1.72.
Compared with prior art, the present invention has the advantage that:
1) present invention is changed by the spacing of separating device, there are when Gas- liquid two-phase flow in tedge, augmentation of heat transfer,
Weaken the vibration of tedge simultaneously, reduces noise level.
2) the present invention provides a kind of separating devices of Novel structure, separate two-phase fluid relative to by separating device
At liquid and gas, liquid phase is divided into small liquid group, gas phase is divided into minute bubbles, inhibits the reflux of liquid phase, promotes gas phase suitable
Channel Group is dynamic, plays the role of regime flow, has the effect of vibration and noise reducing, improves heat transfer effect.Separate relative to multitube and fills
It sets, further increases steady flow result, augmentation of heat transfer, and be simple to manufacture.
3) present invention is equivalent in tedge by setting annular and separation device and increases inner area, enhance heat exchange,
Improve heat transfer effect.
4) present invention avoids only because vehicle repair major is divided in the entire cross-section location of tedge
Tedge inner wall is split, thus entirely rise realized on tube section expand liquid-vaqor interface and vapour phase boundary layer with it is cold
But the contact area of wall surface and enhance disturbance, reduce noise and vibration, enhance heat transfer.
5) distance, the length of separating device of the invention by being arranged between adjacent separating device in tedge short transverse
The rule variation of the parameters size such as outer diameter of degree, annular distance reduces noise to further reach steady flow result, improves heat exchange effect
Fruit.
6) present invention widely grind by heat exchange rule caused by the variation to annular and separation device parameters
Study carefully, when meeting flow resistance, realizes the best relation formula of the effect of vibration and noise reducing.
Detailed description of the invention
Fig. 1 is heat pipe structure schematic diagram of the invention；
Fig. 2 separating device cross-sectional structure schematic diagram of the present invention；
Fig. 3 is separating device of the present invention arrangement schematic diagram in tedge；
Fig. 4 is another schematic diagram that separating device of the present invention is arranged in tedge.
Fig. 5 is that separating device of the present invention arranges cross-sectional view in tedge.
Fig. 6 is that separating device of the present invention arranges radian scale diagrams in tedge.
Fig. 7 is the structural schematic diagram of the two-phase flow tube shell type heat exchanger in background technique.
In figure: 1, evaporation collector, 2, condensation collector, 3, tedge, 4, separating device, 41 separating device shells, 42 annular distances,
43 fins, 44 concentric tubes, 5, return pipe
Specific embodiment
Specific embodiments of the present invention will be described in detail with reference to the accompanying drawing.
Herein, if without specified otherwise, it is related to formula, "/" indicates that division, "×", " * " indicate multiplication.
A kind of heat pipe as shown in Figure 1, including evaporation collector 1, condensation collector 2, tedge 3 and return pipe 5, the rising
Pipe 3 is connected with evaporation collector 1 and condensation collector 2, and the evaporation collector 1 is located at lower part, and the condensation collector 2 is located at top,
The fluid enters condensation collector 2 in evaporation 1 interior suction thermal evaporation of collector, by tedge 3, exchanges heat in condensation collector 2
After condense, the fluid of condensation returns to evaporation collector 1 by return pipe 5.
As illustrated in figures 4-5, annular and separation device 4 is set in tedge 3.The structure of the annular and separation device 4 is shown in figure
3.As shown in figure 3, the separating device 4 includes core and shell 41, the core is arranged in shell 41, the shell with it is upper
Riser inner wall is connected and fixed, and the core includes multiple concentric tubes 44 and fin 43, and the fin 43 connects adjacent concentric tube
44.It is limited between the concentric tube 44 that adjacent fin 43 and its fin 43 connect and forms annular distance 42.
Annular and separation device is arranged in the present invention in heat exchanger tube, by separating device by the liquid and gas in two-phase fluid
It is separated, liquid phase is divided into small liquid group, gas phase is divided into minute bubbles, inhibits the reflux of liquid phase, promotes the smooth stream of gas phase
It is dynamic, play the role of regime flow, has the effect of vibration and noise reducing.Relative to multitube separating device, current stabilization is further increased
Effect, augmentation of heat transfer, and be simple to manufacture.
The present invention is equivalent to by setting annular and separation device and increases interior heat exchange area in heat exchanger tube, enhanced and changed
Heat improves heat transfer effect.
The present invention is because all cross-section locations by gas-liquid two-phase in all heat exchanger tubes are divided, thus entire
The segmentation of gas-liquid interface and gas phase boundary and the contact area of cooling wall are realized on heat exchange tube section and enhances disturbance, greatly
Big reduces noise and vibration, enhances heat transfer.
Preferably, preferably, intercommunicating pore is arranged on the concentric tube 44 and/or fin 43.
Intercommunicating pore is set between adjacent annular distance, the connection between annular distance 42 is realized by intercommunicating pore.
Pass through setting intercommunicating pore, it is ensured that it is interconnected between adjacent annular distance, pressure that can uniformly between annular distance,
It so that the fluid of high pressure runner flows to low pressure, while can also further separate liquid and gas while fluid flows, have
Stablize two-phase flow conducive to further.
Preferably, the extended line of the fin passes through the center of circle of concentric tube.
Preferably, heat exchange pipeline is passed through in condensation collector 2, in the fluid in the heat exchange pipeline and condensation collector 2
Steam exchanges heat.
Preferably, tedge 3 and evaporation collector 1 are all endothermic sections.
Preferably, setting is more in tedge 3 along the flow direction (i.e. the short transverse of Fig. 2) of fluid in tedge 3
A separating device 4, from the entrance of tedge to the outlet of tedge, the distance between adjacent separating device is shorter and shorter.If away from
It is H with a distance from tube inlet from rising, the distance between adjacent separating device is S, S=F1(H), i.e. S is using height H as variable
Function, S ' are the first order derivatives of S, meet following require:
S'<0；
Main cause is that carrier's liquid is understood in uphill process because of the steam in tedge, in uphill process, on
Riser is constantly heated, and causes the steam in biphase gas and liquid flow more and more, because the vapour phase in stream-liquid two-phase flow is more and more,
Exchange capability of heat in tedge can increase with vapour phase and weaken relatively, and vibration and its noise also can be continuous with vapour phase increase
Increase.Therefore the distance between the adjacent separating device for needing to be arranged is shorter and shorter.
In addition, exporting to condensation this section of collector, because the space of this section becomes larger suddenly, the variation in space from tedge
It will lead to quickly flowing upwards out and assemble for gas, therefore spatial variations will lead to the vapour phase (vapour group) of aggregation from tedge position
Into condensation collector, due to gas (vapour) liquid density contrast, air mass leaves adapter tube position and will move rapidly upward, and air mass original space bit
It sets and the liquid of wall surface is pushed away by air mass while will also spring back and hit wall surface rapidly, form impingement phenomenon.Gas (vapour) liquid phase is more not
Continuously, air mass aggregation is bigger, and water hammer energy is bigger.Impingement phenomenon will cause biggish noise vibration and mechanical shock, to equipment
It damages.Therefore in order to avoid the generation of this phenomenon, the distance between adjacent separating device being arranged at this time is shorter and shorter,
To constantly separate gas phase and liquid phase in fluid delivery process, to reduce vibration and noise to the full extent.
It is found through experiments that, by above-mentioned setting, can both reduce vibration and noise to the full extent, while can mention
High heat transfer effect.
Further preferably, from the entrance of tedge 3 to the outlet of tedge 3, the distance between adjacent separating device is more next
Shorter amplitude is continuously increased.That is S " is the second derivative of S, meets following require:
S">0；
It is found through experiments that, by being improved simultaneously so set, 9% or so vibration and noise can be further decreased
7% or so heat transfer effect.
Preferably, the length of each separating device 4 remains unchanged.
Preferably, other than the distance between adjacent separating device 4, separating device others parameter (such as length,
Caliber etc.) it remains unchanged.
Preferably, along the short transverse of tedge 3, the multiple separating devices 4 of setting in tedge 3, from tedge 3
For entrance to the outlet of tedge 3, the length of separating device 4 is increasingly longer.I.e. the length of separating device is C, C=F2(X), C ' is
The first order derivative of C meets following require:
C'>0；
Further preferably, from the entrance of tedge to the outlet of tedge, the increasingly longer amplitude of the length of separating device
It is continuously increased.That is C " is the second derivative of C, meets following require:
C">0；
The variation of the distance between for example adjacent separating device of specific reason is identical.
Preferably, the distance between adjacent separating device remains unchanged.
Preferably, the length in addition to separating device is outside one's consideration, separating device others parameter (such as adjacent spacing, caliber
Deng) remain unchanged.
Preferably, along the short transverse of tedge 3, the multiple separating devices of setting in tedge 3, from tedge 3
For entrance to the outlet of tedge 3, the hydraulic diameter of the annular distance 41 in different separating devices 4 is smaller and smaller.That is the ring of separating device
Hole hydraulic diameter is D, D=F3(X), D ' is the first order derivative of D, meets following require:
D'<0；
Preferably, the annular distance hydraulic diameter of separating device is smaller and smaller from the entrance of tedge to the outlet of tedge
Amplitude be continuously increased.I.e.
D " is the second derivative of D, meets following require:
D”>0。
The variation of the distance between for example adjacent separating device of specific reason is identical.
Preferably, the length of separating device and the distance of adjacent separating device remain unchanged.
Preferably, other than the annular distance hydraulic diameter of separating device, separating device others parameter (such as length, phase
The distance between adjacent separating device etc.) it remains unchanged.
Further preferably, as shown in figure 3, groove is arranged inside the tedge 3, the shell 42 of the separating device 4 is set
It sets in groove.
Preferably, the aligning inner of the inner wall of shell 42 and tedge 3.By alignment, so that tedge inner wall table
Reach on face in the same plane, guarantees the smooth of surface.
Preferably, the thickness of shell 42 is less than the depth of groove, tedge inner wall can be made to form groove in this way,
To carry out augmentation of heat transfer.
Further preferably, as shown in figure 4, tedge 3 is welded for multi-segment structure, the junction setting point of multi-segment structure
Every device 4.This mode makes being simple to manufacture for the tedge that separating device is arranged, and cost reduces.
It is learnt by analyzing and testing, the spacing between separating device cannot be excessive, leads to damping noise reduction if excessive
Effect it is bad, while can not be too small, cause resistance excessive if too small, similarly, the outer diameter of annular distance can not it is excessive or
Too small, the effect for also resulting in damping noise reduction is bad or resistance is excessive, therefore the present invention is through a large number of experiments, preferentially full
The normal flow resistance of foot (total pressure-bearing be 2.5Mpa hereinafter, the on-way resistance of single riser be less than or equal to 5Pa/M)
In the case of, so that being optimal of damping noise reduction, has arranged the optimal relationship of parameters.
Preferably, the length of separating device is C, heat exchanger tube preferably, the distance between adjacent separating device is S
Outer diameter be W, the radius of neighboring concentric pipe is respectively R2And R1, wherein R2>R1, the radian of the circular arc between adjacent fin is
H meets following require:
S/C=a-b*LN (W/E)；
E=((h*R2 2-h*R1 2)/2)1/2；
Wherein LN is logarithmic function, and a, b are parameters, wherein 4.9 < a < 6.1,1.3 <b < 2.1；
34<W<58mm；
19<C<27mm；
50<S<70mm。
Preferably, 5.3 < a < 5.6,1.5 <b < 1.8；
Preferably, a=5.42, b=1.72.
Wherein the interval S of separating device is the both ends the distance between opposite with adjacent separating device；I.e. front separates dress
The distance between the front end of the tail end set and separating device below.Referring specifically to the mark of Fig. 4.
Shell 41 is actually considered as outermost concentric tube to participate in calculating together in above formula.
Radian h is the radian limited with the medium line of fin 43, referring to Fig. 6；The radius of concentric tube is respectively R2And R1Be with
The average value of the internal diameter of concentric tube and outer diameter calculates.
Preferably, rising length of tube L between 3000-5500mm.Further preferably, between 3500-4500mm.
By the preferred of the optimal geometric scale of above-mentioned formula, can be realized under the conditions of meeting normal flow resistance,
Damping noise reduction reaches optimum efficiency.
Further preferably, as the increase of W/R, a constantly reduce, b constantly increases.
For parameters such as other parameters, such as tube wall, shell wall thickness according to normal standard setting.
Preferably, hot tube fluid is water.
Preferably, annular distance 42 extends in the whole length direction of separating device 4.I.e. the length of annular distance 42, which is equal to, separates dress
Set 4 length.
Preferably, the caliber of the evaporation collector 1 is less than the caliber of condensation collector 2.
The internal diameter for evaporating collector is R1, and the internal diameter for condensing collector is R2, as preferably then 0.45 < R1/R2 < 0.88.
By above-mentioned setting, can further augmentation of heat transfer, can be improved 7% or more heat exchange efficiency.
Although the present invention has been disclosed in the preferred embodiments as above, present invention is not limited to this.Any art technology
Personnel can make various changes or modifications, therefore protection scope of the present invention is answered without departing from the spirit and scope of the present invention
When being defined by the scope defined by the claims..
Claims (1)
1. a kind of loop circuit heat pipe, including evaporation collector, condensation collector, tedge and return pipe, the tedge and evaporation collector
It is connected with condensation collector, the evaporation collector is located at lower part, and the condensation collector is located at top, and fluid is in evaporation collector interior suction
Thermal evaporation enters condensation collector by tedge, condenses after being exchanged heat in condensation collector, the fluid of condensation passes through return pipe
Return to evaporation collector；It is characterized in that, separating device is arranged in the tedge, the separating device includes core and shell,
In the shell, the shell is connected and fixed with heat transfer tube wall, and the core includes multiple concentric tubes and rib for the core setting
Piece, the fin connect adjacent concentric tube；Intercommunicating pore is set on the concentric tube and/or fin.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810488378.9A CN108827045B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe of uniform pressure |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810488378.9A CN108827045B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe of uniform pressure |
| CN201710294949.0A CN107144161B (en) | 2017-04-28 | 2017-04-28 | The annular and separation device loop circuit heat pipe of spacing variation in a kind of short transverse |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710294949.0A Division CN107144161B (en) | 2017-04-28 | 2017-04-28 | The annular and separation device loop circuit heat pipe of spacing variation in a kind of short transverse |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108827045A CN108827045A (en) | 2018-11-16 |
| CN108827045B true CN108827045B (en) | 2019-05-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810489936.3A Expired - Fee Related CN108827047B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe |
| CN201810488378.9A Expired - Fee Related CN108827045B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe of uniform pressure |
| CN201710294949.0A Expired - Fee Related CN107144161B (en) | 2017-04-28 | 2017-04-28 | The annular and separation device loop circuit heat pipe of spacing variation in a kind of short transverse |
| CN201810489115.XA Expired - Fee Related CN108827046B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe of multi-segment structure |
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| CN201810489936.3A Expired - Fee Related CN108827047B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe |
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| CN201710294949.0A Expired - Fee Related CN107144161B (en) | 2017-04-28 | 2017-04-28 | The annular and separation device loop circuit heat pipe of spacing variation in a kind of short transverse |
| CN201810489115.XA Expired - Fee Related CN108827046B (en) | 2017-04-28 | 2017-04-28 | A kind of loop circuit heat pipe of multi-segment structure |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107131781B (en) * | 2017-05-09 | 2018-10-19 | 山东大学 | A kind of variation of length can not condensing body annular and separation device heat exchanger |
| CN111504099B (en) * | 2017-08-03 | 2021-02-09 | 山东大学 | Rod-fin loop heat pipe with size-variable flow stabilizer |
| CN110806021B (en) * | 2018-08-05 | 2021-05-11 | 山东鑫光节能科技有限公司 | Temperature-controlled trough type solar heat collector system |
| CN110806024B (en) * | 2018-08-05 | 2020-08-28 | 伟迈云科技股份有限公司 | Trough type solar heat collector system with size of stabilizing device |
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| SU1098373A1 (en) * | 1982-11-03 | 1985-11-30 | Предприятие П/Я В-2679 | Heat-exchanging pipe |
| US20040099408A1 (en) * | 2002-11-26 | 2004-05-27 | Shabtay Yoram Leon | Interconnected microchannel tube |
| CN204881271U (en) * | 2015-08-20 | 2015-12-16 | 华北电力大学 | Shell and tube type heat exchanger of interpolation segmentation silk screen |
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- 2017-04-28 CN CN201810489936.3A patent/CN108827047B/en not_active Expired - Fee Related
- 2017-04-28 CN CN201810488378.9A patent/CN108827045B/en not_active Expired - Fee Related
- 2017-04-28 CN CN201710294949.0A patent/CN107144161B/en not_active Expired - Fee Related
- 2017-04-28 CN CN201810489115.XA patent/CN108827046B/en not_active Expired - Fee Related
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|---|---|---|---|---|
| CN2901053Y (en) * | 2006-04-29 | 2007-05-16 | 林国策 | Small low pressure steam boiler |
| CN101639374A (en) * | 2009-08-26 | 2010-02-03 | 姚贤卿 | Multiphase flow rectifying device |
| CN102588699A (en) * | 2012-02-29 | 2012-07-18 | 北京中油联自动化技术开发有限公司 | Flow equalizer |
| CN104279770A (en) * | 2014-10-11 | 2015-01-14 | 南京工业大学 | Solar medium-high-temperature loop heat pipe steam generator |
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| Publication number | Publication date |
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| CN107144161B (en) | 2018-07-13 |
| CN108827046B (en) | 2019-05-07 |
| CN107144161A (en) | 2017-09-08 |
| CN108827046A (en) | 2018-11-16 |
| CN108827047A (en) | 2018-11-16 |
| CN108827047B (en) | 2019-05-07 |
| CN108827045A (en) | 2018-11-16 |
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