CN112954970A - Low-thermal-resistance phase-change cold plate and radiator - Google Patents
Low-thermal-resistance phase-change cold plate and radiator Download PDFInfo
- Publication number
- CN112954970A CN112954970A CN202110161689.6A CN202110161689A CN112954970A CN 112954970 A CN112954970 A CN 112954970A CN 202110161689 A CN202110161689 A CN 202110161689A CN 112954970 A CN112954970 A CN 112954970A
- Authority
- CN
- China
- Prior art keywords
- phase change
- phase
- region
- independent
- cold plate
- 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.)
- Granted
Links
Images
Classifications
-
- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
- H05K7/00—Constructional details common to different types of electric apparatus
- H05K7/20—Modifications to facilitate cooling, ventilating, or heating
- H05K7/2029—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant with phase change in electronic enclosures
- H05K7/20327—Accessories for moving fluid, for connecting fluid conduits, for distributing fluid or for preventing leakage, e.g. pumps, tanks or manifolds
Abstract
The invention relates to a low-thermal resistance phase change cold plate and a radiator, and the scheme comprises a cold plate main body, a gas phase working medium outlet connector, a liquid phase working medium inlet connector and a phase change cavity, wherein the phase change cavity comprises a gas phase gathering region which is arranged at the top of the phase change cavity and is communicated with the gas phase working medium outlet connector, a liquid phase region which is arranged at the bottom of the phase change cavity and is communicated with the liquid phase working medium inlet connector, and a phase change region which is arranged between the gas phase gathering region and the liquid phase region; the phase change region is divided into a plurality of independent phase change regions through a plurality of shunting ribs, and a non-heating region is arranged between two connected independent phase change regions; the widths of the non-heating areas are smaller than those of the independent phase change areas, each non-heating area corresponds to one independent phase change area, and liquid-phase and gas-phase working media of each independent phase change area are independently guided to the phase change areas and escape from the phase change areas.
Description
Technical Field
The invention relates to the technical field of phase change radiators, in particular to a low-thermal resistance phase change cold plate and a radiator.
Background
The existing phase change cold plate radiator generally adopts parallel straight flow channels, after a refrigerant medium absorbs heat and is gasified in the flow channels, a gaseous gas phase refrigerant floats upwards along the flow channels, accumulates in a gas phase area at the upper part of a phase change generation area, escapes from the radiator through a gas phase refrigerant outlet, is circularly liquefied through an outer pipeline, releases heat and is cooled, and then returns to the phase change radiator, so that refrigeration cycle is realized. The phase change cold plate radiator does not need to be driven by an external circulating pump, gas-liquid circulating flow is carried out under the action of gravity, the flowing direction of cooling working media and bubbles generated after phase change is opposite to the gravity direction, the pressure of a liquefaction area is reduced after the bubbles are liquefied, the pressure of a gas phase area is larger, and gas-liquid circulating flow is realized under the drive of pressure difference and gravity.
The upper part and the lower part of a phase change area of the phase change cold plate radiator are heated simultaneously, a liquid phase working medium is vaporized simultaneously, and a vaporized gas phase working medium at the lower part of the phase change area floats upwards due to gravity and is gathered with a vaporized gas phase working medium at the upper part of the phase change area, so that the gas content at the upper part of the phase change area is far higher than that at the lower part. The heat quantity which can be taken away by the gas-phase working medium is far less than that which is taken away by the vaporization of the liquid working medium, so that more heat quantity is accumulated on the upper part of the phase change area, and the temperature is higher. The overall temperature uniformity of the cold plate is poor. When the generation speed of the vapor bubbles in the phase change cold plate radiator exceeds the speed of the vapor bubbles separated from the heated surface to form an air film, the liquid working medium and the heated surface are separated by a layer of air film, and particularly the generated air film can further influence the heat dissipation of a flow passage where the heating source is arranged.
In addition, the existing phase change cold plate does not realize the transfer of the gas phase working medium in the flow channel where the heating source is arranged, so that the heat transfer coefficient is reduced, and the temperature of the wall surface is increased. The existing phase change cold plate has the bottleneck problem of overlarge power for high-power components. When the thermal power is too high, the generation rate of the gas-phase working medium in the existing phase-change radiator is greater than the transfer rate, and the liquid-phase working medium is completely converted into the gas-phase working medium, so that the heat transfer is deteriorated, and the temperature of the table top of the radiator is sharply increased.
In view of the above, there is a need for a low thermal resistance phase change cold plate and a heat sink that can solve the above problems, reduce thermal resistance, and improve heat dissipation efficiency.
Disclosure of Invention
The invention aims to solve the problems in the prior art and provides a phase change cold plate with low thermal resistance and a radiator.
In order to realize the purpose of the invention, the invention adopts the following technical scheme: a low-thermal resistance phase-change cold plate comprises a cold plate main body, a gas phase working medium outlet connector, a liquid phase working medium inlet connector and a phase-change cavity, wherein the phase-change cavity comprises a gas phase gathering region arranged at the top of the phase-change cavity and communicated with the gas phase working medium outlet connector, a liquid phase region arranged at the bottom of the phase-change cavity and communicated with the liquid phase working medium inlet connector, and a phase-change region arranged between the gas phase gathering region and the liquid phase region;
the phase change region is divided into a plurality of independent phase change regions through a plurality of shunting ribs, and a non-heating region is arranged between two connected independent phase change regions;
the widths of the non-heating areas are smaller than those of the independent phase change areas, each non-heating area corresponds to one independent phase change area, and liquid-phase and gas-phase working media of each independent phase change area are independently guided to the phase change areas and escape from the phase change areas.
The working principle and the beneficial effects are as follows: 1. by separately guiding the liquid phase working medium and the gas phase working medium of each independent phase change area to the phase change area and escaping out of the phase change area, the smooth transfer of the gas phase working medium in a flow channel where a lower heating source installation position is located can be realized, the gas content of the upper part of the phase change area is reduced, the defect that the upper gas phase working medium and the lower gas phase working medium of the original phase change area are all gathered together is overcome, the thermal resistance of the upper phase change area is reduced, and the whole heat exchange capacity is enhanced, wherein the phase change area is a heating area;
2. compared with the existing structure, the single volume of the main ribs is reduced, and the main ribs are divided into more and thinner shunting ribs, so that the spacing distance of the ribs in the phase change area is enlarged, the influence of a gas phase working medium on a wall surface is reduced, the gas phase working medium quickly escapes to a gas phase working medium gathering area, gas bubbles are reduced to gather on the heat exchange surface and the surface of a flow passage to form a gas film, and the influence of thermal resistance on heat dissipation is increased;
3. compared with the structure with only a plurality of vertical phase change regions in the prior art, the structure can better solve the problem of large temperature difference between the upper part and the lower part of the cold plate table surface in the phase change regions, and realize better temperature uniformity of the cold plate table surface;
4. the structure of this scheme has solved the bottleneck problem of the power that generates heat that exists because of liquid phase working medium is whole to be changed into gaseous phase working medium well, has promoted phase change radiator assembly power density, makes the phase change cold drawing radiator of the same size specification can assemble more powerful components and parts that generate heat.
Furthermore, the reposition of redundant personnel rib is including cutting off rib and vertical rib, cut off the rib and be the broken line setting, adjacent two cut off the rib and form the first runner of air feed liquid working medium circulation, cut off the rib and hold the second runner that chamber side formed gas-liquid working medium circulation with the phase transition, every be equipped with an independent phase transition district in the second runner, be equipped with an independent phase transition district and non-heating area in every second runner, vertical rib is located first runner and second runner respectively. By adopting the structure, the first flow channel and the second flow channel can be effectively changed into the broken line arrangement from the vertical arrangement through the broken line arrangement of the partition ribs, the independent phase change area and the non-heating area in the second flow channel can be inclined into two parts, therefore, when the phase change occurs in the independent phase change area, the generated bubbles can not be accumulated at the upper part of the phase change area to form an air film as before, the heat resistance is increased to influence the heat dissipation, in addition, the rising distance of the bubbles in a single phase change area is shortened, the escape capacity of the bubbles is obviously improved, the air film is avoided, the heat resistance is greatly reduced, the heat dissipation capacity is improved, the integral heat dissipation of the cold plate is more uniform, in addition, the area of the phase change area is reduced, but the quantity is increased, the limited phase change area in the cold plate can be better utilized, the space utilization rate is improved, and the.
Furthermore, the independent phase change regions and the non-heating regions are arranged in a staggered mode. This setting for independent phase transition district is not unified to be located upper portion or lower part, but independent phase transition district and the crisscross setting in non-heating area on upper portion, independent phase transition district and the crisscross setting in non-heating area of lower part also, so can utilize limited phase transition district in the cold plate to the maximum, also furthest reduced because the thermal resistance that the bubble gathered and produced, influence between the adjacent runner is littleer simultaneously, both sides are non-heating district or phase transition appearance intracavity wall about independent phase transition district, both sides are also independent phase transition district or phase transition appearance intracavity wall about the non-heating district, consequently, adjacent runner influence is littleer.
Furthermore, the non-heating area is located at the narrow end of the second flow channel, and the independent phase change area is located at the wide end of the second flow channel and the wide end of the first flow channel respectively. According to the arrangement, each independent phase change area can be widened on the premise that smooth circulation of the gas-liquid working medium is guaranteed as far as possible, the space utilization rate is increased, the escape capacity of bubbles can be obviously enhanced, the phenomenon of bubble accumulation is reduced, the thermal resistance is reduced, the heat dissipation efficiency is improved, the influence of the wall surface on the gas-phase working medium is reduced, and the gas-phase working medium floats upwards quickly and escapes to the gas-phase working medium gathering area.
And a liquid phase flow channel is arranged between the liquid phase area and the phase change area, the liquid phase flow channel at least comprises a top section communicated with a liquid phase working medium inlet joint, a bottom section communicated with one end of the liquid phase area and a flow section arranged between the top section and the bottom section, and the middle position of the flow section is communicated with the bottom of one independent phase change area. The arrangement can well meet the supply of liquid phase working media of each independent phase change area, and particularly, the independent phase change areas close to the inner wall of the phase change containing cavity improve the overall heat exchange capacity of the cold plate, so that the overall heat exchange of the cold plate is more uniform.
Further, when a non-heating area in the same first flow channel is located above the independent phase change area, a first inclined flow channel is arranged between the top of the independent phase change area and the bottom of the non-heating area. With the arrangement, the bubbles generated during phase change can be better guided to the non-heating area to rise quickly through the first inclined flow channel.
Further, when a non-heating area in the same first flow channel is located below the independent phase change area, a second inclined flow channel is arranged between the top of the non-heating area and the bottom of the independent phase change area. The arrangement can be better matched with the spatial arrangement of the first inclined flow passage.
Further, the vertical ribs separate the independent phase change area and the non-heating area into a plurality of flow channels respectively. The arrangement can better separate gas-liquid working media while increasing the heat exchange area, and particularly reduce the accumulation of gas-phase working media, namely bubbles, during phase change, so that the gas-phase working media can more uniformly and quickly rise to the gas-phase gathering area at the top to be discharged.
A low-thermal resistance phase change heat radiator comprises the low-thermal resistance phase change cold plate and a heat radiation table cover plate welded with the cold plate through vacuum brazing or gas shielded welding. Compared with the existing radiator with the same volume, the phase change radiator made by the cold plate has better heat dissipation capability, improves the assembly power density of the phase change radiator, and can be assembled with a heating element with higher power.
Furthermore, a brazing filler metal layer of 0.05-1 mm is arranged between the cold plate and the radiating table top cover plate. The arrangement ensures the sealing property between the cold plate and the radiating table cover plate and ensures the strength of the whole radiator.
Drawings
FIG. 1 is a schematic diagram of a prior art configuration;
FIG. 2 is a schematic structural view of the present invention;
FIG. 3 is a schematic view showing the flow direction of the liquid phase working medium and the gas phase working medium in FIG. 2;
FIG. 4 is a schematic diagram of an external view of a low thermal resistance phase change heat sink;
FIG. 5 is a temperature difference comparison between the upper and lower portions of the phase change region of the phase change cold plate;
FIG. 6 is a trend graph of FIG. 5;
FIG. 7 is a phase change cold plate table temperature comparison graph;
FIG. 8 is a trend graph of FIG. 7;
FIG. 9 is a schematic diagram of a preferred embodiment of independent phase change regions;
FIG. 10 is a schematic view of a preferred embodiment of the non-heat generating region.
In the figure, 1, a cold plate body; 2. a gas phase working medium outlet joint; 3. a liquid phase working medium inlet joint; 4. a phase change cavity; 5. a gas phase accumulation zone; 6. a liquid phase region; 7. a phase change region; 8. an independent phase change region; 9. a non-heat-generating region; 10. separating ribs; 11. a vertical rib; 12. a first flow passage; 13. a second flow passage; 14. a liquid phase flow channel; 141. a top section; 142. a bottom section; 143. a flow-through section; 15. a cover plate of the heat dissipation table top.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments that can be derived by one of ordinary skill in the art from the embodiments given herein are intended to be within the scope of the present invention.
It will be understood by those skilled in the art that in the present disclosure, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship indicated in the drawings for ease of description and simplicity of description, and do not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus, the above terms should not be construed as limiting the present invention.
Referring to fig. 1, a phase change cold plate with a straight flow channel structure in the prior art is shown in the figure, in which the upper and lower parts of a phase change region are heated simultaneously, a liquid phase working medium is vaporized simultaneously, and a vaporized gas phase working medium at the lower part of the phase change region floats upwards due to gravity and is gathered with a vaporized gas phase working medium at the upper part of the phase change region, so that the gas content at the upper part of the phase change region is much higher than that at the lower part. The heat quantity which can be taken away by the gas-phase working medium is far less than that which is taken away by the vaporization of the liquid working medium, so that more heat quantity is accumulated on the upper part of the phase change area, and the temperature is higher. The overall temperature uniformity of the cold plate is poor. When the generation speed of the vapor bubbles in the phase change cold plate radiator exceeds the speed of the vapor bubbles separated from the heated surface to form an air film, the liquid working medium and the heated surface are separated by a layer of air film, and particularly the generated air film can further influence the heat dissipation of a flow passage where the heating source is arranged.
Therefore, referring to fig. 2 for improvement of the present scheme, the low thermal resistance phase change cold plate includes a cold plate main body 1, a gas phase working medium outlet connector 2, a liquid phase working medium inlet connector 3 and a phase change container 4, where the phase change container 4 includes a gas phase gathering region 5 disposed on the top of the phase change container 4 and communicated with the gas phase working medium outlet connector 2, a liquid phase region 6 disposed at the bottom of the phase change container 4 and communicated with the liquid phase working medium inlet connector 3, and a phase change region 7 disposed between the gas phase gathering region 5 and the liquid phase region 6, where the cold plate has a structure except for the internal phase change container 4 and a liquid phase flow channel 14, and other structures are substantially.
Referring to fig. 3, specifically, the phase change region 7 is divided into a plurality of independent phase change regions 8 by a plurality of dividing ribs, a non-heating region 9 is disposed between two connected independent phase change regions 8, each dividing rib includes a partition rib 10 and a vertical rib 11, the partition ribs 10 are arranged in a broken line, two adjacent partition ribs 10 form a first flow channel 12 for flowing gas-liquid working medium, the partition ribs 10 and the side of the phase change accommodating chamber 4 form a second flow channel 13 for flowing gas-liquid working medium, an independent phase change region 8 is disposed in each second flow channel 13, an independent phase change region 8 and a non-heating region 9 are disposed in each second flow channel 13, and the vertical ribs 11 are respectively disposed in the first flow channel 12 and the second flow channel 13. By adopting the structure, the arrangement of the broken lines of the partition ribs 10 can effectively change the vertical arrangement of the first flow passage 12 and the second flow passage 13 into the arrangement of the broken lines, the independent phase change region 8 and the non-heat generating region 9 in the second flow path 13 may be inclined in two parts, so that when a phase change occurs in the independent phase change region 8, the generated bubbles do not accumulate at the upper part of the phase change region 7 to form an air film as before, which causes the increase of thermal resistance to influence the heat dissipation, but also obviously improves the escape capacity of the bubbles because the rising distance of the bubbles in the single phase change region 7 is shortened, thereby avoiding the generation of air film, greatly reducing thermal resistance, improving heat dissipation capacity, leading the heat dissipation of the whole cold plate to be more uniform, and because the area of the phase change region 7 becomes smaller, but the number is increased, the limited phase change region 7 in the cold plate can be better utilized, the space utilization rate is improved, and the heat exchange efficiency is improved.
The flow directions of the liquid phase working medium and the gas phase working medium are clearly shown in fig. 3.
Specifically, the widths of the non-heating areas 9 are smaller than the widths of the independent phase change areas 8, each non-heating area 9 corresponds to one independent phase change area 8, liquid-phase and gas-phase working mediums of each independent phase change area 8 are independently guided to the phase change area 7 and escape from the phase change area 7, the independent phase change areas 8 are arranged in a staggered mode with the non-heating areas 9, the non-heating areas 9 are located at the narrow ends of the second flow channels 13, the independent phase change areas 8 are respectively located at the wide ends of the second flow channels 13 and the wide ends of the first flow channels 12, the independent phase change areas 8 are not uniformly arranged at the upper portion or the lower portion, the independent phase change areas 8 at the upper portion and the non-heating areas 9 are arranged in a staggered mode, the independent phase change areas 8 at the lower portion and the non-heating areas 9 at the lower portion are also arranged in a staggered mode, therefore, the limited phase change areas 7 in the cold plate can be utilized to the, both sides are non-heating area 9 or phase transition appearance chamber 4 inner wall about independent phase transition district 8, both sides are independent phase transition district 8 or phase transition appearance chamber 4 inner wall about non-heating area 9 also, therefore adjacent runner influence is littleer, and can guarantee under the smooth and easy prerequisite of gas-liquid working medium circulation as far as possible, widen every independent phase transition district 8, increase space utilization, consequently, can show the escape capacity who strengthens the bubble, reduce the phenomenon production that the bubble gathers, just also reduced the thermal resistance, the radiating efficiency is improved, and it receives the wall influence still to reduce gaseous phase working medium, make gaseous phase working medium come-up fast, escape to gaseous phase working medium and gather the district.
Specifically, when the non-heat-generating region 9 in the same first flow channel 12 is located above the independent phase change region 8, a first inclined flow channel is provided between the top of the independent phase change region 8 and the bottom of the non-heat-generating region 9.
Specifically, when the non-heat-generating region 9 in the same first flow channel 12 is located below the independent phase change region 8, a second inclined flow channel is provided between the top of the non-heat-generating region 9 and the bottom of the independent phase change region 8.
Specifically, the vertical ribs 11 divide the independent phase change region 8 and the non-heat generation region 9 into a plurality of flow channels, respectively. The arrangement can better separate gas-liquid working media while increasing the heat exchange area, particularly reduce the accumulation of gas-phase working media, namely bubbles, during phase change, and enable the gas-phase working media to more uniformly and quickly rise to the gas-phase gathering area 5 at the top for discharge.
Preferably, a liquid phase flow channel 14 is further arranged between the liquid phase region 6 and the phase change region 8, the liquid phase flow channel 14 at least comprises a top section 141 connected with the liquid phase working medium inlet connector 3, a bottom section 142 connected with one end of the liquid phase region 6, and a flow section 143 arranged between the top section 141 and the bottom section 142, and the middle position of the flow section 143 is connected with the bottom of one independent phase change region 8. This setting can satisfy the supply of the liquid phase working medium of every independent phase transition district 8 well, especially is close to the independent phase transition district 8 of phase transition appearance chamber 4 inner wall, improves the holistic heat transfer ability of cold drawing for the whole heat transfer of cold drawing is more even.
Preferably, the whole cold plate body 1 is processed in an integrated mode, such as milling and broaching, so that the cold plate is prevented from deforming in the processing and using processes, and the thickness of the cold plate is about 30 to 50 mm.
In order to more clearly and intuitively show the independent phase change area 8 and the non-heating area 9 in the scheme, please refer to fig. 9 and 10, it can be seen that the non-heating area 9 replaces the main rib position in fig. 1, and the flow rate is significantly increased.
Referring to fig. 4, a low thermal resistance phase change heat sink includes the above-mentioned low thermal resistance phase change cold plate, and further includes a heat dissipation table cover plate 15 welded to the cold plate body 1 by vacuum brazing or gas shielded welding. Compared with the existing radiator with the same volume, the phase change radiator made by the cold plate has better heat dissipation capability, improves the assembly power density of the phase change radiator, and can be assembled with a heating element with higher power.
Specifically, a brazing filler metal layer of 0.05-1 mm is arranged between the cold plate and the radiating table top cover plate 15, and the welding temperature is 300-1200 ℃. The arrangement ensures the sealing performance between the cold plate and the radiating table top cover plate 15 and ensures the strength and the sealing performance of the whole radiator. The liquid phase working medium, namely the cooling liquid medium, adopts fluorocarbon, fluorinated liquid or acetone and other working media. The boiling point is-20 to 80 ℃ and the heat of vaporization is 50 to 500J/g at normal temperature and pressure. The heat absorption capacity of the phase-change evaporator is about 15 to 20 times of that of a single-phase water cooling system, so that the heat exchange capacity of the radiator is greatly enhanced.
In this embodiment, in order to better demonstrate the effect of this solution, through a comparison test with the prior art heat sink, the results shown in fig. 5-8 are obtained on the premise of matching different load devices, and it can be seen that under different thermal power loads, the heat dissipation effect of the low thermal resistance phase change heat sink of this solution is significantly better than that of the prior art heat sink, where the original phase change heat sink is the prior art heat sink.
Wherein fig. 5 is a comparison of temperature differences at the upper and lower portions of the phase change region 7 of the phase change cold plate, fig. 6 is a trend graph of fig. 5, fig. 7 is a comparison of the mesa temperature of the phase change cold plate, and fig. 8 is a trend graph of fig. 7.
The present invention is not described in detail in the prior art, and therefore, the present invention is not described in detail.
It is understood that the terms "a" and "an" should be interpreted as meaning that a number of one element or element is one in one embodiment, while a number of other elements is one in another embodiment, and the terms "a" and "an" should not be interpreted as limiting the number.
Although the terms of the cold plate main body 1, the gas phase working medium outlet connector 2, the liquid phase working medium inlet connector 3, the phase change containing cavity 4, the gas phase gathering region 5, the liquid phase region 6, the phase change region 7, the independent phase change region 8, the non-heat generating region 9, the partition ribs 10, the vertical ribs 11, the first flow channel 12, the second flow channel 13, the liquid phase flow channel 14, the top section 141, the bottom section 142, the circulation section 143, the heat dissipation table top cover plate 15, etc. are used more frequently, the possibility of using other terms is not excluded. These terms are used merely to more conveniently describe and explain the nature of the present invention; they are to be construed as being without limitation to any additional limitations that may be imposed by the spirit of the present invention.
The present invention is not limited to the above-mentioned preferred embodiments, and any other products in various forms can be obtained by anyone in the light of the present invention, but any changes in the shape or structure thereof, which have the same or similar technical solutions as those of the present application, fall within the protection scope of the present invention.
Claims (10)
1. A low thermal resistance phase change cold plate comprises a cold plate main body, a gas phase working medium outlet connector, a liquid phase working medium inlet connector and a phase change cavity, and is characterized in that the phase change cavity comprises a gas phase gathering region arranged at the top of the phase change cavity and communicated with the gas phase working medium outlet connector, a liquid phase region arranged at the bottom of the phase change cavity and communicated with the liquid phase working medium inlet connector, and a phase change region arranged between the gas phase gathering region and the liquid phase region;
the phase change region is divided into a plurality of independent phase change regions through a plurality of shunting ribs, and a non-heating region is arranged between two connected independent phase change regions;
the widths of the non-heating areas are smaller than those of the independent phase change areas, each non-heating area corresponds to one independent phase change area, and liquid-phase and gas-phase working media of each independent phase change area are independently guided to the phase change areas and escape from the phase change areas.
2. The phase change cold plate with low thermal resistance according to claim 1, wherein the flow dividing ribs comprise partition ribs and vertical ribs, the partition ribs are arranged in a broken line, two adjacent partition ribs form a first flow passage for gas-liquid working medium to flow through, the partition ribs and the side edge of the phase change containing cavity form a second flow passage for gas-liquid working medium to flow through, an independent phase change region is arranged in each second flow passage, an independent phase change region and a non-heating region are arranged in each second flow passage, and the vertical ribs are respectively positioned in the first flow passage and the second flow passage.
3. The phase change cold plate with low thermal resistance as claimed in claim 2, wherein the independent phase change regions are staggered with the non-heat generating regions.
4. The phase change cold plate with low thermal resistance as claimed in claim 2, wherein the non-heat generating region is located at the narrow end of the second flow channel, and the independent phase change regions are located at the wide end of the second flow channel and the wide end of the first flow channel, respectively.
5. The phase change cold plate with low thermal resistance as claimed in claim 1, wherein a liquid phase flow channel is further disposed between the liquid phase region and the phase change region, the liquid phase flow channel at least comprises a top section connected to the liquid phase working medium inlet, a bottom section connected to one end of the liquid phase region, and a flow section disposed between the top section and the bottom section, and an intermediate position of the flow section is connected to the bottom of one of the independent phase change regions.
6. The phase change cold plate with low thermal resistance as claimed in claim 2, wherein when the non-heat generating region in the same first flow channel is located above the independent phase change region, a first inclined flow channel is provided between the top of the independent phase change region and the bottom of the non-heat generating region.
7. The phase change cold plate with low thermal resistance as claimed in claim 2, wherein when the non-heat-generating region in the same first flow channel is located below the independent phase change region, a second inclined flow channel is provided between the top of the non-heat-generating region and the bottom of the independent phase change region.
8. The phase change cold plate with low thermal resistance as claimed in claim 2, wherein the vertical ribs separate the independent phase change region and the non-heating region into a plurality of flow channels.
9. A low thermal resistance phase change heat sink comprising a low thermal resistance phase change cold plate of any one of claims 1 to 8, further comprising a heat sink table cover plate welded to the cold plate by vacuum brazing or gas shielded welding.
10. The phase change heat radiator with low thermal resistance according to claim 9, wherein a solder layer of 0.05-1 mm is arranged between the cold plate and the cover plate of the heat dissipation table top.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110161689.6A CN112954970B (en) | 2021-02-05 | 2021-02-05 | Low-thermal-resistance phase-change cold plate and radiator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110161689.6A CN112954970B (en) | 2021-02-05 | 2021-02-05 | Low-thermal-resistance phase-change cold plate and radiator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112954970A true CN112954970A (en) | 2021-06-11 |
| CN112954970B CN112954970B (en) | 2022-04-12 |
Family
ID=76242589
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110161689.6A Active CN112954970B (en) | 2021-02-05 | 2021-02-05 | Low-thermal-resistance phase-change cold plate and radiator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112954970B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116345011A (en) * | 2023-05-31 | 2023-06-27 | 天津力神电池股份有限公司 | Battery module and battery pack |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103940271A (en) * | 2014-05-06 | 2014-07-23 | 北京德能恒信科技有限公司 | Heat pipe heat exchange system with evaporative condenser |
| WO2016208180A1 (en) * | 2015-06-26 | 2016-12-29 | パナソニックＩｐマネジメント株式会社 | Cooling device and electronic apparatus having same mounted thereon |
| CN206294463U (en) * | 2016-11-23 | 2017-06-30 | 杭州祥博传热科技股份有限公司 | A kind of novel water-cooled radiator |
| CN109862756A (en) * | 2019-03-11 | 2019-06-07 | 北京航空航天大学 | The active heat control system of low latitude emergency and method based on porous material evaporation-cooled device |
| CN110282596A (en) * | 2019-05-23 | 2019-09-27 | 华北电力大学 | The microchannel boiling heat transfer system and method staggeredly divided based on vapour-liquid heterogeneous fluid |
| EP3545732A1 (en) * | 2016-11-25 | 2019-10-02 | Iceotope Limited | Fluid cooling system |
| US20200003497A1 (en) * | 2018-06-29 | 2020-01-02 | The Boeing Company | Additively manufactured heat transfer device |
-
2021
- 2021-02-05 CN CN202110161689.6A patent/CN112954970B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103940271A (en) * | 2014-05-06 | 2014-07-23 | 北京德能恒信科技有限公司 | Heat pipe heat exchange system with evaporative condenser |
| WO2016208180A1 (en) * | 2015-06-26 | 2016-12-29 | パナソニックＩｐマネジメント株式会社 | Cooling device and electronic apparatus having same mounted thereon |
| CN206294463U (en) * | 2016-11-23 | 2017-06-30 | 杭州祥博传热科技股份有限公司 | A kind of novel water-cooled radiator |
| EP3545732A1 (en) * | 2016-11-25 | 2019-10-02 | Iceotope Limited | Fluid cooling system |
| US20200003497A1 (en) * | 2018-06-29 | 2020-01-02 | The Boeing Company | Additively manufactured heat transfer device |
| CN109862756A (en) * | 2019-03-11 | 2019-06-07 | 北京航空航天大学 | The active heat control system of low latitude emergency and method based on porous material evaporation-cooled device |
| CN110282596A (en) * | 2019-05-23 | 2019-09-27 | 华北电力大学 | The microchannel boiling heat transfer system and method staggeredly divided based on vapour-liquid heterogeneous fluid |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116345011A (en) * | 2023-05-31 | 2023-06-27 | 天津力神电池股份有限公司 | Battery module and battery pack |
| CN116345011B (en) * | 2023-05-31 | 2023-08-11 | 天津力神电池股份有限公司 | Battery module and battery pack |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112954970B (en) | 2022-04-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10962307B2 (en) | Stacked heat exchanger | |
| US7093647B2 (en) | Ebullition cooling device for heat generating component | |
| JP2008171840A (en) | Liquid-cooling heat sink and design method thereof | |
| CN110035642A (en) | A kind of liquid-cooled heat-conducting block and water-cooling type radiator | |
| CN112954970B (en) | Low-thermal-resistance phase-change cold plate and radiator | |
| CN109548363A (en) | A kind of porous media liquid cooling device for cooling, production method and application method | |
| CN107062963B (en) | A kind of alternating expression micro-channel condenser for hair cell regeneration | |
| EP2802832B1 (en) | Heat exchanger | |
| CN106415184A (en) | Heat transfer apparatus | |
| CN214125861U (en) | Low-thermal-resistance phase-change cold plate | |
| JP2010212402A (en) | Ebullient cooling device | |
| CN210399237U (en) | Radiating component, radiator and air conditioner | |
| CN109671690B (en) | Multi-head spiral flow channel liquid cooler for heat dissipation of electronic component | |
| CN112584678A (en) | Phase change heat dissipation device for inverter and inverter | |
| KR20110087917A (en) | Refrigerator | |
| CN217929007U (en) | Heat radiator | |
| CN111479456A (en) | Physical heat radiation structure and cooling assembly | |
| CN107230929B (en) | Radiator, radiating component, radiating chassis and laser | |
| CN213046504U (en) | Cooking utensil with cooling function | |
| CN213747477U (en) | Cooling device for vacuum heat insulation valve box | |
| CN219415279U (en) | Novel refrigerating device | |
| CN217504464U (en) | High-power gas-liquid phase change radiator | |
| CN215864812U (en) | High-performance loop heat pipe radiator | |
| CN212231967U (en) | Physical heat radiation structure and cooling assembly | |
| CN211951056U (en) | High-efficient heat dissipation chamber and have oil cooler of this high-efficient heat dissipation chamber |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CP03 | Change of name, title or address | ||
| CP03 | Change of name, title or address |
Address after: No. 55, Gaoxin 9th Road, Qiaonan Block, Xiaoshan Economic and Technological Development Zone, Xiaoshan District, Hangzhou City, Zhejiang Province, 310000 Patentee after: Xiangbo heat transfer technology Co.,Ltd. Address before: 310000 room 702, building 3, No. 371, Mingxing Road, Xiaoshan Economic and Technological Development Zone, Xiaoshan District, Hangzhou City, Zhejiang Province Patentee before: XENBO (HANGZHOU) HEAT TRANSFER SCIENCE & TECHNOLOGY CO.,LTD. |