WO2007145352A1 - ヒートシンクおよび冷却器 - Google Patents
ヒートシンクおよび冷却器 Download PDFInfo
- Publication number
- WO2007145352A1 WO2007145352A1 PCT/JP2007/062197 JP2007062197W WO2007145352A1 WO 2007145352 A1 WO2007145352 A1 WO 2007145352A1 JP 2007062197 W JP2007062197 W JP 2007062197W WO 2007145352 A1 WO2007145352 A1 WO 2007145352A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- fin
- fins
- fin group
- heat sink
- Prior art date
Links
- 238000005192 partition Methods 0.000 claims abstract description 5
- 239000003507 refrigerant Substances 0.000 claims description 170
- 238000001816 cooling Methods 0.000 claims description 47
- 238000009835 boiling Methods 0.000 claims description 24
- 239000002826 coolant Substances 0.000 abstract description 11
- 239000004065 semiconductor Substances 0.000 description 22
- 238000002955 isolation Methods 0.000 description 20
- 238000010438 heat treatment Methods 0.000 description 12
- 230000000694 effects Effects 0.000 description 10
- 239000007788 liquid Substances 0.000 description 9
- 239000012071 phase Substances 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 230000020169 heat generation Effects 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000001052 transient effect Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 239000011810 insulating material Substances 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 239000012808 vapor phase Substances 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
Classifications
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L23/00—Details of semiconductor or other solid state devices
- H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
- H01L23/46—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids
- H01L23/473—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids by flowing liquids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
-
- 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
- H05K7/2089—Modifications to facilitate cooling, ventilating, or heating for power electronics, e.g. for inverters for controlling motor
- H05K7/20936—Liquid coolant with phase change
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L2924/00—Indexing scheme for arrangements or methods for connecting or disconnecting semiconductor or solid-state bodies as covered by H01L24/00
- H01L2924/0001—Technical content checked by a classifier
- H01L2924/0002—Not covered by any one of groups H01L24/00, H01L24/00 and H01L2224/00
Definitions
- the present invention relates to a heat sink and a cooler for performing heat exchange.
- a power laser diode, a computer CPU (Central Processing Unit), or a power converter such as an inverter generates heat when driven.
- Such equipment can be damaged or deteriorate in performance due to the heat generated by the equipment itself. Or it may adversely affect the parts placed around the heating element.
- Such a heating element is cooled by a cooler in order to remove heat.
- Some coolers have a heat sink, and the heat sink includes fins. By forming fins on the heat sink, the heat transfer area for radiating heat is expanded, and the efficiency of heat exchange can be improved.
- a heating element is disposed on a heat sink and heat is supplied to a channel group composed of a heat sink fin and base.
- a body cooling device is disclosed.
- an inflow port for supplying cooling water to the channel group is provided, an inflow side header is provided between the inflow port and the channel group, and an outflow side is provided downstream of the channel / le group.
- a header is provided. Disclosure that the relationship Wb> Wc> Wa is established when the width Wb of the channel near the inlet, the width Wc of the channel far from the inlet, and the width Wa of the center channel are set. Has been. According to this heating element cooling device, it is disclosed that the heating element can be cooled uniformly.
- the surface of the base is provided with a plurality of fins, the fins are arranged at an equal pitch, and the thickness of the fin located at the edge of the hose
- a radiator in which fins having different thicknesses are arranged so that the thickness of the fin located at the center of the base is the thinnest. According to this radiator, it is disclosed that a uniform flow velocity can be given to each fin of the radiator without making the overall size of the radiator large, and the cooling effect of the fin can be utilized to the maximum.
- Japanese Patent Application Laid-Open No. 9 1 2 3 0 8 1 discloses a boiling water cooling device. Inside the cooling tank, there are bulkheads that divide the cooling tank into three refrigerant chambers according to the IGBT (Insulated Gate Bipolar Transistor) module attached on the surface, and the boiling of each refrigerant chamber A boiling cooling device is disclosed that is provided with a plurality of refrigerant flow control plates that divide the region into one vertical direction. The refrigerant flow control plate is provided so as to be inclined at equal intervals in the vertical direction in the boiling region.
- IGBT Insulated Gate Bipolar Transistor
- each refrigerant chamber partitioned by the partition wall is provided with an outflow passage through which boiling steam flows out on one side of the boiling region, and an inflow passage through which condensate flows in on the other side. ing.
- this boiling cooling device it is disclosed that in the boiling region inside the refrigerant tank, it is possible to prevent the lowering of the heat radiation performance on the upper side.
- the liquid cooling part and the air cooling part are integrally formed, and the heat absorbing surface of the liquid cooling part is joined to the heat generating part that locally generates heat.
- a cooling device for electronic equipment is disclosed.
- the liquid cooling section is provided with a liquid cooling pump for circulating the refrigerant in the flow passage.
- This electronic device cooling device is disclosed as having excellent heat conduction efficiency and heat dissipation performance. .
- Japanese Patent Application No. 2 0 0 5— 1 1 6 8 7 7 discloses a cooling system in which the maximum heat dissipation amount of the radiator is equal to or less than the maximum heat generation amount of I G B ⁇ . According to this cooling system, it is disclosed that a radiator for radiating heat absorbed from a heating element such as IGBT can be reduced in size.
- a cooler in which a refrigerant flow path is formed by fins, as disclosed in the above-mentioned Japanese Patent Laid-Open No. 2 0 0 1 -3 5 2 0 2 5.
- the space between the fins becomes the refrigerant flow path.
- heat exchange is performed while the refrigerant flows along the main surface of the fin.
- each refrigerant flow path the pressure decreases as it goes downstream. At this time, there may be a difference in the configuration of the flow path due to a manufacturing error or the like.
- the magnitude of pressure loss in each flow path is different and the flow rate of the refrigerant flowing in each flow path is different. As a result, cooling is not uniformly performed on the surface of the cooler. There was a case. For example, when the flow rate fluctuates transiently, the amount of change in pressure loss in each flow path is different, making it difficult to equalize the flow rate for each flow path. .
- a boundary layer of refrigerant is formed on the surface of the fin. Since the boundary layer becomes larger (thick) as it goes downstream, heat transfer deteriorates and cooling capacity deteriorates as it goes downstream. For this reason, the cooling capacity may be different between the upstream region and the downstream region of the refrigerant flow path.
- the cooler When the cooler is a boiling cooler, the ratio of the gas phase to the liquid phase increases toward the downstream side of the flow path. As it goes to the downstream side of the flow path, heat transfer worsens and cooling capacity deteriorates. In particular, when there is a difference in the refrigerant flow rate to each flow path, there is an extremely shortage of liquid coolant in the downstream area of the flow path where the flow rate is low, and burnout described later occurs. There was a problem.
- An object of the present invention is to provide a heat sink and a cooler that can perform uniform cooling.
- the heat sink according to the present invention comprises a plurality of fins.
- the fin is formed to be a partition wall of the refrigerant flow path.
- the fin is formed so that the cooling medium flows along the surface.
- a merge space is formed so that the refrigerant above the flow path isolated by the fins merges.
- the merging space is formed in the middle of the flow path formed by the fin.
- the plurality of objects to be cooled are arranged in the direction of the refrigerant flow path.
- a merge space is formed between the regions located immediately below.
- the fin includes a plurality of first fins and a plurality of second fins.
- the heat sink includes a first fin group arranged such that main surfaces of the plurality of first fins are parallel to each other.
- the heat sink includes a second fin group arranged such that main surfaces of the plurality of second fins are substantially parallel to each other.
- the second fin group is arranged such that the main surface of the second fin is substantially parallel to the main surface of the first fin.
- the merge space is formed by arranging the first fin group and the second fin group apart from each other.
- the object to be cooled is arranged inside a region where each of the first fin group and the second fin group is formed, and the joining space is between the first fin group and the second fin group. Is formed.
- the second fin group is formed so as to be displaced from the first fin group in a direction perpendicular to the flow path of the refrigerant.
- the fins are arranged so that their main surfaces are substantially parallel to each other.
- the fin includes an opening.
- the merge space is formed by the opening.
- the opening is formed in a region between the plurality of objects to be cooled.
- the fin is preferably formed to have a microchannel structure.
- the heat sink is preferably applied to a cooler of a power converter.
- the cooler based on this invention is equipped with the above-mentioned heat sink, the case where the said fin is arrange
- a main header portion is formed inside the case to communicate with the refrigerant supply pipe and supply the refrigerant to the plurality of flow paths.
- a sub-header portion is formed in the case so as to communicate with the main header portion and supply refrigerant to the merge space. In the above invention, preferably, it is formed to perform boiling cooling.
- the refrigerant supply pipe is connected to a refrigerant supply device for supplying the refrigerant while being pressurized. ing.
- a heat sink and a cooler capable of performing uniform cooling can be provided.
- FIG. 1 is a schematic perspective view of a cooler in the first embodiment.
- FIG. 2 is a first schematic cross-sectional view of the cooler in the first embodiment.
- FIG. 3 is a second schematic cross-sectional view of the cooler in the first embodiment.
- FIG. 4 is a third schematic cross-sectional view of the cooler in the first embodiment.
- FIG. 5 is a fourth schematic cross-sectional view of the cooler in the first embodiment.
- FIG. 6 is an enlarged schematic diagram illustrating the state of the refrigerant at the end of the fin in the present invention.
- FIG. 7 is a graph illustrating heat transfer in a region from the front end portion of the fin toward the rear side in the present invention.
- FIG. 8 is a first schematic cross-sectional view of the cooler in the second embodiment.
- FIG. 9 is a second schematic cross-sectional view of the cooler in the second embodiment.
- FIG. 10 is a first schematic cross-sectional view of the cooler in the third embodiment.
- FIG. 11 is a second schematic cross-sectional view of the cooler in the third embodiment.
- FIG. 12 is a third schematic cross-sectional view of the cooler in the third embodiment. Best mode for carrying out the invention,
- the cooler in the present embodiment is a cooler for cooling a heating element such as an IGBT.
- the cooler in the present embodiment includes a heat sink.
- water which is a liquid, is used as the refrigerant.
- the cooler in the present embodiment is a so-called forced cooling type in which refrigerant is supplied by a refrigerant supply device. It is a cooler.
- the object to be cooled in the present embodiment is a semiconductor element 21.
- the heat sink in the present embodiment includes a plate member 19.
- the plate member 19 is formed in a flat plate shape.
- the semiconductor element 21 is bonded to the surface of the plate member 19.
- the semiconductor elements 21 are spaced apart from each other. In the present embodiment, nine semiconductor elements 21 are joined to the plate member 19.
- the plurality of semiconductor elements 21 are arranged in the vertical direction and the horizontal direction.
- the cooler has a case 1 1.
- Case 11 is formed in a substantially rectangular parallelepiped shape. Inside the case ⁇ , heat sink fins to be described later are arranged.
- the cooler in the present embodiment includes a refrigerant supply pipe 12 and a refrigerant discharge pipe 13.
- the refrigerant supply pipe 12 and the refrigerant discharge pipe 13 are arranged so as to protrude from one surface of the case 11.
- the refrigerant supply pipe 12 is connected to a supply pump 22 as a refrigerant supply device.
- the supply pump 22 is configured to pressurize the refrigerant and supply it to the cooler.
- FIG. 2 shows a first schematic cross-sectional view of the cooler in the present embodiment.
- the heat sink in the present embodiment includes a plurality of fin groups.
- the heat sink has a first fin group 1.
- First fin group 1 includes a plurality of first fins 1a.
- the first fin l a is formed in a flat plate shape.
- the plurality of first fins la are arranged such that the main surfaces are parallel to each other.
- the space between the case 11 and the first fin 1a or the space between the first fins 1a forms a refrigerant flow path.
- the heat sink in the present embodiment includes the second fin group 2.
- the second fin group 2 includes a plurality of second fins 2a.
- Second fin group 2 in the present embodiment has the same configuration as first fin group 1.
- the second fin 2a has the same configuration as the first fin la.
- the cooler in the present embodiment includes a third fin group 3.
- the third fin group 3 includes a plurality of third fins 3a.
- the third fin group 3 has the same configuration as the first fin group 1.
- the third fin 3a has the same configuration as the first fin la.
- Each fin group in the present embodiment is joined to the back surface of the plate member 19.
- Each fin group is arranged to stand on the main surface on the back side of the plate member 19.
- First fin group 1, second fin group 2 and third fin group 3 in the present embodiment are arranged in a straight line.
- the first fin 1a, the second fin 2a, and the third fin 3a force are arranged in a straight line.
- the first fin 1a, the second fin 2a, and the third fin 3a are arranged in the same plane from a supply-side main header portion 3 1 described later to a discharge-side main header portion 3 2 described later. .
- the first fin group 1 and the second fin group 2 are arranged with a space therebetween.
- the second fin group 2 and the third fin group 3 are spaced apart.
- a merge space 36 is formed for the refrigerant flowing through the respective flow paths to merge.
- a merge space 37 is formed between the second fin group 2 and the third fin group 3.
- the merge spaces 3 6 and 3 7 in the present embodiment are formed at regular intervals along the refrigerant flow path.
- the merge spaces 3 6 and 3 7 are formed in the middle of the flow path from the supply side main header portion 31 to the discharge side main header portion 3 2.
- the merge spaces 3 6 and 3 7 are formed in the middle of the refrigerant flow path formed by the fins.
- each of the first fin group 1, the second fin group 2, and the third fin group 3 is formed by arranging three pieces.
- the first fin group 1, the second fin group 2, and the third fin group 3 are arranged in the horizontal direction.
- Each fin group is arranged in the vertical direction.
- first fin group 1, second fin group 2, and third fin group 3 are arranged along the flow path through which the refrigerant flows.
- nine fin groups are formed.
- each fin group is arranged in a region corresponding to the position of semiconductor element 21 arranged on the surface of the cooler.
- Each fin group is disposed so as to include a region in which the region where the semiconductor element 21 of the plate member 19 is disposed is projected on the back side of the plate member 19.
- the semiconductor element 21 is arranged inside the region where each fin group is formed.
- the cooler in the present embodiment has a supply-side main header as a supply-side main header.
- the supply-side main header portion 31 communicates with the refrigerant supply pipe 12.
- the supply-side main header portion 31 is formed so as to be able to store a refrigerant.
- the supply-side main header portion 31 communicates with the refrigerant flow path formed by the first fin 1 a and the case 11.
- the cooler in the present embodiment includes sub-headers for supplying a refrigerant to each of merge spaces 36 and 37.
- sub-headers 41 to 43 are formed by separating members 14 and 15 disposed between the fin groups.
- notched portions for supplying the refrigerant to the merge spaces 3 6 and 3 7 are formed on the plate-like members forming the sub-headers 4 1 to 4 3.
- the isolation members 14 and 15 are configured.
- the cooler in the present embodiment includes a separating member 14 disposed between the first fin groups 1.
- a sub header portion 4 1 is formed by a space sandwiched between the two separating members 14.
- the two separating members 14 are arranged at a distance from each other.
- the separating member 14 is arranged such that the main surface is substantially parallel to the main surface of the first fin 1a. Similar to the separating member 14 arranged between the first fin groups 1, two separating members 14 are arranged between the second fin groups 2.
- a sub header portion 4 2 is formed by a space sandwiched between the two isolation members 14.
- a separating member 15 is disposed between the third fin groups 3.
- the separating member 15 is formed so that the cross-sectional shape is a U-shape.
- a sub-header portion 43 is formed by the space inside the separating member 15.
- the separating member 15 is formed so that the end portions of the sub-headers 4 1 to 4 3 are closed.
- the separating member 14 disposed between the first fin groups 1 and the separating member 14 disposed between the second fin groups 2 are disposed away from each other.
- the separating member 14 and the separating member 15 arranged between the second fin groups 2 are arranged apart from each other.
- the separating members 14 and 15 are arranged so that the refrigerant can be supplied to the joining spaces 36 and 37, respectively.
- Supply side main header section 3 1 is formed by isolation members 1 4 and isolation members 1 5
- the sub-headers 4 1 to 4 3 communicated with each other.
- the supply main header section 31 is formed so as to be able to supply the refrigerant flowing from the refrigerant supply pipe 12 to the sub header sections 41 to 43.
- the separating members 14 and 15 constituting the sub header portions 41 to 43 are disposed between the regions where the semiconductor elements 21 are disposed. In other words, the separating members 14 and 15 are arranged avoiding the region where the semiconductor element 21 is arranged.
- the sub header portions 41 to 43 are formed so as to avoid a region where the semiconductor element 32 is disposed.
- the cooler includes a discharge-side main header portion 32 as a discharge-side header portion.
- the discharge-side main header 3 2 communicates with the refrigerant discharge pipe 1 3.
- the discharge-side main header section 32 is arranged downstream of the area where the fins are arranged.
- the discharge-side main header portion 3 2 communicates with the refrigerant flow path formed by the third fin 3 a and the case 11.
- FIG. 3 shows a second schematic cross-sectional view of the cooler in the present embodiment.
- FIG. 3 is a cross-sectional view taken along line I I I and I I I in FIG.
- the heat sink 23 includes a first fin l a, a second fin 2 a, and a third fin 3 a.
- the first fin l a, the second fin 2 a, and the third fin 3 a are joined to the plate member 19 so as to be disposed inside the case 11.
- Case 11 has a U-shaped cross-section.
- the plate member 19 is joined to the end surface of the case 11.
- a first fin la, a second fin 2a, and a third fin 3a are arranged directly under each semiconductor element 21.
- the first fin la, the second fin 2 a, and the third fin 3 a are disposed so as to straddle the back surface of the plate member 19 and the inner surface of the case 11.
- First fin 1 a, second fin 2 a, and third fin 3 a in the present embodiment are in contact with the inner surface of case 11.
- FIG. 4 shows a third schematic cross-sectional view of the cooler in the present embodiment. 4 is a cross-sectional view taken along the line IV-IV in FIG.
- the separating members 14 and 15 are joined to the back surface of the plate member 19 and the inner surface of the case 11.
- a notched portion is formed in the separating member that forms the sub header portions 41 to 43, and the sub header portions 41 to 43 are joined together.
- 3 Communicate with 6.
- the separating member 14 and the separating member 15 are arranged so as to be separated from each other, a notched portion is formed in the separating member forming the sub-headers 4 1 to 4 3.
- the sub header portions 4 1 to 4 3 communicate with the merge space 3 7.
- the refrigerant is supplied from refrigerant supply pipe 12 as indicated by arrow 71.
- the refrigerant flows into the region where the first fin group 1 is disposed via the supply-side main header portion 31.
- the refrigerant enters the space sandwiched between the case 11 and the first fin la, the space sandwiched between the first fins 1a, and the space sandwiched between the isolation member 14 and the first fin 1a.
- the refrigerant flows along the main surface of each fin 1a.
- the refrigerant flows linearly.
- the fins become the partition walls of the refrigerant flow path.
- the refrigerant absorbs heat from the first fin 1a.
- the semiconductor element 21 bonded to the surface of the plate member 19 corresponding to the first fin group 1 can be mainly cooled.
- the refrigerant that has passed through the first fin group 1 flows into the merge space 36.
- the merge space 36 the refrigerants that have passed through the respective flow paths of the first fin group 1 are mixed together.
- the refrigerant stored in the merge space 36 flows into the second fin group 2.
- each second fin 2a is cooled.
- the refrigerant that has passed through the second fin group 2 flows into the merge space 37.
- the merge space 37 the refrigerants that have passed through the respective channels of the second fin group 2 are mixed together.
- the refrigerant stored in the merge space 3 7 flows into the third fin group 3.
- each third fin 3a is cooled.
- 3rd fin group 3 As a result of cooling, the semiconductor element 21 bonded to the surface of the plate member 19 corresponding to the third fin group 3 can be mainly cooled.
- the refrigerant that has passed through the third fin group 3 reaches the discharge side main header portion 32 as indicated by an arrow 74.
- the refrigerant is discharged from the discharge side main header portion 3 2 through the refrigerant discharge pipe 13 to the outside of the cooler as indicated by an arrow 72.
- part of the refrigerant flowing into the cooler flows into the sub header sections 41 to 43 through the supply side main header section 31 as indicated by an arrow 75.
- no significant heat exchange is performed in the sub-headers 4 1 to 4 3.
- a part of the refrigerant flows into the merge space 36 after passing through the sub-header portion 41 as indicated by an arrow 76 a.
- the refrigerant that has not yet undergone heat exchange is injected into the space between the first fin group 1 and the second fin group 2 from the sub header portions 4 1 to 4 3.
- the refrigerant flows from the sub-header part 41 force into the sub-header part 42.
- the refrigerant that has passed through the secondary header part 42 flows into the merge space 37 as indicated by an arrow 76 b. That is, even in the merged space formed between the second fin group 2 and the third fin group 3, a refrigerant that is not substantially subjected to heat exchange is injected from the sub header sections 41 to 43.
- the sub-headers 41 to 43 in the present embodiment are formed so that the cross-sectional area is larger than the refrigerant flow path in which heat exchange is performed.
- the distance between the separating members forming the sub header portion is formed to be larger than the distance between the fins in each fin group.
- FIG. 5 shows a fourth schematic cross-sectional view of the cooler in the present embodiment.
- FIG. 5 is a cross-sectional view taken along the line V—V in FIG.
- Each flow path in the present embodiment is formed so that the cross-sectional shape is rectangular.
- the refrigerant flowing into first fin group 1 from supply-side main header portion 31 progresses through the flow path and rises in temperature. Also, the pressure drops. Refrigerant is in each channel, heat exchange status and channel Differences in configuration can cause differences in pressure loss.
- the pressures can be made substantially uniform by mixing refrigerants that have passed through different flow paths. That is, by flowing into the merge space 36 after passing through the first fin group 1, the variation in pressure loss when flowing through the first fins 1a is alleviated.
- the refrigerant flowing into the second fin group 2 flows from the merge space 36, the refrigerant can be supplied to the respective flow paths with substantially uniform pressure. Therefore, it is possible to supply the refrigerant almost uniformly to the respective flow paths in the region where the second fin group 2 is formed.
- the flow distribution to each flow path can be made substantially uniform. As a result, the object to be cooled arranged on the surface of the cooler can be cooled uniformly.
- the merge space becomes a pressure buffer space, so that the flow rate of the refrigerant in each flow path can be made constant. The effects of transient fluctuations can be reduced.
- a temperature difference occurs in the refrigerant that has passed through each flow path in the region where the first fin group 1 is formed.
- the refrigerant mixes with each other in the merge space 36, so that the temperature becomes uniform.
- the temperature of the refrigerant flowing into the region of the second fin group 2 can be made substantially uniform, and the region in which the second fin group 2 is formed can be almost uniformly cooled.
- FIG. 6 shows an enlarged schematic diagram of each fin.
- a merge space 36 is formed between the first fin l a and the second fin 2 a.
- the refrigerant flows along the direction in which the first fin 1a and the second fin 2a are arranged.
- the refrigerant enters the first fin 1a in the direction indicated by the arrow 73.
- the boundary layer 8 becomes thicker downstream. As a result, heat transfer at the fin surface is reduced. That is, when the boundary layer 8 becomes thicker, the thermal resistance increases, and heat transfer from the first fin to the refrigerant deteriorates.
- Figure 7 shows a graph of the heat transfer rate at the surface along the direction of flow from the front end of each fin.
- the heat transfer coefficient is high at the front end of the fin.
- the heat transfer rate decreases as it goes downstream.
- boundary layer 8 grown in the portion of merge space 36 can be divided. As a result, deterioration of the heat transfer coefficient in the second fin 2a can be suppressed.
- the refrigerant collides with the front end portion of the second fin 2a. A new boundary layer 8 develops along the surface of the second fin 2a.
- the boundary layer is thin at the front end of the second fin 2a, high heat transfer can be obtained (leading edge effect).
- a new boundary layer 8 is generated and developed. With this force, the boundary layer can be divided again by the merge space 37 formed between the second fin group 2 and the third fin group 3. After this, the leading edge effect can be obtained again at the front end of the third fin 3a.
- the cooler in the present embodiment can repeatedly obtain the leading edge effect at the end of the fin in contact with the merge space, and can achieve a high heat transfer coefficient. As a result, high cooling performance can be obtained.
- the heat sink includes a plurality of fins, and a merge space is formed so that the refrigerant in the flow path isolated by the fins merges.
- the merge space is formed in the middle of the flow path formed by the fins.
- a first fin group including a plurality of first fins and a second fin group including a plurality of second fins are provided.
- the second fin group is arranged so that the main surface of the second fin is substantially parallel to the main surface of the first fin.
- the merge space is formed by arranging the first fin group and the second fin group apart from each other. Yes. With this configuration, the merge space can be easily formed.
- the first fin group and the second fin group are not limited to this form, and the first fin of the first fin group and the second fin of the second fin group may not be arranged linearly.
- the second fin group may be formed so as to be displaced from the first fin group in the direction perpendicular to the refrigerant flow path. By doing so, it is possible to improve the cooling performance by promoting disturbance of the refrigerant flow.
- the first fin group and the second fin group have the same configuration, but the present invention is not limited to this configuration, and the first fin group and the second fin group have different configurations. It does not matter.
- the number of first fins included in the first fin group may be different from the number of second fins included in the second fin group.
- the cooler in the present embodiment includes sub header sections 41 to 43 for supplying the refrigerant to the merge space. Since each of the sub header sections 41 to 43 communicates with the supply side main header section 31, it is possible to supply the refrigerant that has not undergone substantially heat exchange to the merge space. A refrigerant having a low temperature can be injected into the merge space, and an increase in the temperature of the refrigerant can also be suppressed on the downstream side. As a result, substantially uniform cooling can be performed even in the flow direction of the refrigerant. As the refrigerant goes downstream, the pressure drop due to pressure loss increases.
- the pressure difference with the sub-header portion becomes large, and the amount of refrigerant supplied can be increased.
- the temperature of the refrigerant is rising, more low-temperature refrigerant can be supplied from the sub-header portion to the high temperature portion, effectively suppressing the temperature rise of the refrigerant. be able to.
- the outlet temperature of the cooler can be lowered and a design with a large margin can be performed.
- the size of the sub-header is preferably such that the pressure drop is smaller than the pressure drop of the flow path constituted by at least fins. Alternatively, it is preferable that the pressure drop generated in the sub-header portion is substantially negligible. In the case of the present embodiment, the size of the sub header portion is, for example, almost the flow path configured by the space between the fins in the cross section perpendicular to the direction in which the refrigerant flows. 5 times or more is preferable. When the cooler in the present invention is a boiling type cooler, the shortage of refrigerant can be alleviated. Also, burnout can be effectively avoided.
- boiling cooling In a boiling-type cooler, the refrigerant boils inside the cooler and enters a two-phase state of liquid and gas phase.
- so-called boiling cooling that continues cooling in this state, uniform and high-performance cooling can be realized by the endothermic heat due to the latent heat accompanying the phase change and the temperature maintaining effect at the boiling point.
- the heat generation amount of the heating element connected to the cooler is large, there is a problem that a burnout transition from nucleate boiling to film boiling may occur on the fin surface, which is the heat transfer surface. is there. When burnout occurs, the surface of the fin is covered with steam and heat transfer becomes extremely worse.
- the flow rate can be made uniform in each flow path, and the burnout caused by a partial shortage of refrigerant in the low flow path can be suppressed.
- the refrigerant can be supplied to each flow path from the sub header portion through the merge space, and the occurrence of burnout due to the lack of the refrigerant can be suppressed.
- the cooler in the present invention can be applied to a cooler having a microchannel structure in which the cross-sectional area of the flow path is small.
- the hydraulic diameter D is, for example, not less than 0.6 mm and not more than 3 mm. Or, in a microchannel structure with a smaller channel, the hydraulic diameter D is ⁇ 6 mm or less.
- the hydraulic diameter D is expressed by the following formula.
- A is the cross-sectional area of the flow path
- L is the circumferential length (wetting edge length or cross-sectional length) in the cross-sectional shape.
- each flow path is miniaturized, so the heat transfer area can be expanded by integration. Alternatively, the heat transfer rate can be increased. In a cooler having a microchannel structure, the size can be reduced and the cooling capacity can be improved.
- the micro channel structure has a problem that since the flow path is small, the pressure loss when passing through the flow path is large, and it is difficult to evenly distribute the refrigerant to each flow path.
- Each fin in the present embodiment is formed in a flat plate shape, but is not limited to this form, and the fin may be formed so that the coolant flows along the surface. Further, the height of each fin is not limited, and the present invention can be applied to a heat sink having fins of any height.
- each separating member is formed by forming a notched portion for supplying the refrigerant in the merged space with respect to the hollow member forming the sub header portion.
- the present invention is not limited to this configuration, and the members constituting the sub header portion may be formed so as to supply the refrigerant from the sub header portion to the merge space.
- an opening (a hole) or a step for supplying the coolant to the merge space may be formed in the member forming the sub header portion.
- the cross-sectional shape of each flow path is formed to be a rectangle, but this is not a limitation, and the cross-sectional shape of each flow path may be a circle or a stand. Any shape such as a shape can be employed.
- the refrigerant supply pipe and the refrigerant discharge pipe for supplying the refrigerant to the cooler are formed on one surface of the case.
- the refrigerant supply pipe may be formed so as to supply the refrigerant to each fin.
- the refrigerant discharge pipe is formed so that the refrigerant passing through each fin can be discharged.
- a semiconductor element is taken as an example of a body to be cooled.
- the present invention is not limited to this form, and can be applied to a heat sink and a cooler for cooling an arbitrary body to be cooled. it can.
- the present invention can be applied to a cooler of a power converter such as a cooler for cooling the CPU of a computer.
- FIG. 8 shows a first schematic cross-sectional view of the cooler in the present embodiment.
- FIG. 8 is a schematic cross-sectional view corresponding to the cross-sectional view of FIG. 3 in the first embodiment.
- the cooler in the present embodiment includes a heat sink 24.
- the heat sink 24 includes a plurality of fins.
- the fin 7 is formed so as to extend from the supply side main header portion 31 to the discharge side main header portion 32.
- the fin 7 is disposed inside the case 1 1.
- a plurality of fins 7 are arranged so that the main surfaces are parallel to each other (not shown).
- the fin 7 has an opening 51 for forming the merge space 36.
- the fin 7 includes an opening 52 for forming the merge space 37.
- the openings 5 1 and 5 2 are formed in a region between the semiconductor elements 2 1.
- the opening 51 has a quadrangular planar shape.
- the opening 52 has a circular planar shape.
- FIG. 9 shows a second schematic cross-sectional view of the cooler in the present embodiment.
- FIG. 9 is a schematic cross-sectional view corresponding to the cross-sectional view of FIG. 4 in the first embodiment.
- the cooler in the present embodiment includes a separating member 16.
- the isolation member 16 has a U-shaped cross section.
- the separating member 16 is formed to extend from the supply side main header portion 31 to the discharge side main header portion 32.
- the isolation member 16 has an opening 53 for communicating with the merge space 36.
- the isolation member 16 has an opening 54 for communicating with the merge space 37.
- the openings 5 3 and 5 4 are formed in substantially parallel planar portions of the U-shape facing each other.
- the opening 53 has a quadrangular planar shape.
- the opening 53 is formed at the end of the separating member 16 in the width direction.
- the opening 54 has a circular planar shape.
- the opening portion 5 4 is formed at a substantially central portion in the width direction of the separating member 16.
- the opening is formed in the fin.
- Each merging space is formed by an opening formed in the fin. Also with this configuration, the same operations and effects as in the first embodiment can be obtained. Also, the coolant can be supplied to the merge space by forming the opening in the isolation member for constituting the sub header portion.
- the opening formed in the fin and the isolation member in the present embodiment has a planar shape that is formed in a quadrangle or a circle, but is not limited to this form, and an arbitrary shape can be adopted as the shape of the opening. .
- the opening formed in the fin and the opening formed in the isolation member are formed so as to have substantially the same shape and size.
- each member is formed.
- the openings formed in may have different shapes and sizes.
- a cutout portion may be formed instead of a part of the openings.
- a heat sink and a cooler according to Embodiment 3 according to the present invention will be described with reference to FIGS.
- the cooler in the present embodiment is different from that in the first embodiment in the configuration of the sub header section.
- FIG. 10 shows a first schematic cross-sectional view of the cooler in the present embodiment.
- the cooler in the present embodiment includes a heat sink 25.
- Heat sink 2 5 Including material 2-5.
- the heat sink 25 includes a first fin group 4.
- the first fin group 4 includes a plurality of first fins 1a.
- the plurality of first fins la are arranged such that the main surfaces are parallel to each other.
- the heat sink 25 includes a second fin group 5.
- the second fin group 5 includes a plurality of second fins 2a.
- the second fin group 5 has the same configuration as the first fin group 4.
- the heat sink 25 includes a third fin group 6.
- the third fin group 6 includes a plurality of third fins 3a.
- the third fin group 6 has the same configuration as the first fin group 4.
- a merge space 36 is formed between the first fin group 4 and the second fin group 5.
- a merge space 3 7 is formed between the second fin group 5 and the third fin group 6.
- the cooler in the present embodiment includes a case 18.
- the first fin group 4, the second fin group 5, and the third fin group 6 are arranged inside the case 18.
- FIG. 11 shows a second schematic cross-sectional view of the cooler in the present embodiment.
- FIG. 11 is a cross-sectional view taken along the line XI—XI in FIG.
- Case 18 in the present embodiment has side wall 18a.
- Case 18 has an isolation wall 18 b.
- the separation wall 1 8 b is formed in a plate shape.
- the isolation wall 18 b is joined to the side wall 18 a.
- Separation wall 18 b in the present embodiment is formed so that the main surface is substantially parallel to the main surface of plate member 19.
- the isolation wall 1 8 b divides the space inside the case 18.
- a fin group such as the first fin group 4 including the first fin 1a is arranged between the ones.
- the other space constitutes a sub-header section 44.
- the secondary header portion 4 4 is formed by a space sandwiched between the isolation wall 1 8 b and the outer wall of the case 18.
- the isolation wall 18 b has openings 18 c and 18 d for supplying refrigerant to the merge spaces 36 and 37, respectively.
- the openings 18 c and 18 d are formed between regions where the semiconductor element 21 is disposed.
- openings 1 8 c and 1 8 d are formed with an interval between each other.
- the opening portion 18 c is formed so that the planar shape is circular.
- the opening portion 18 d is formed so that the planar shape is rectangular.
- FIG. 12 shows a third schematic cross-sectional view of the cooler in the present embodiment.
- FIG. 12 is a cross-sectional view taken along the line XII-XII in FIG. Opening 1 8 d They are formed at regular intervals. Further, the opening portion 18 c is also formed with a certain interval.
- the refrigerant is supplied from the refrigerant supply pipe 12 to the supply side main header section 31 as indicated by an arrow 71.
- the refrigerant flows from the supply side main header portion 31 into the region where the first fin group 4 is formed.
- the refrigerant reaches the merge space 36 after passing through the first fin group 4.
- the refrigerant flows from the merge space 36 into the region where the second fin group 5 is formed.
- the refrigerant passing through the second fin group 5 reaches the merge space 37.
- the refrigerant flows from the merge space 37 into the region where the third fin group 6 is formed.
- the refrigerant flows into the discharge side main header portion 32 from the region where the third fin group 6 is formed.
- the refrigerant is discharged from the discharge side main header portion 3 2 through the refrigerant discharge pipe 13 as indicated by an arrow 72.
- the refrigerants that have passed through the respective flow paths are mixed with each other.
- a part of the refrigerant that has flowed into supply-side main header portion 31 flows into sub header portion 44 as indicated by arrow 79.
- the refrigerant that has flowed into the sub header section 44 flows into the merge space 36 through the opening section 18 c as indicated by an arrow 80.
- the refrigerant flowing into the sub header portion 4 4 flows into the merge space 37 through the opening .18 d. In this way, the refrigerant that has not undergone substantial heat exchange from the main header portion can be supplied to the merge spaces into the merge spaces 36, 37.
- the cooler is separated by a flow path that directly contributes to cooling of the fins, a sub header section, and a force isolation wall 18 b.
- a sub-header portion is formed between the fins.
- the sub-header portion in this embodiment has a sub-header in a space isolated from the space where the fins are arranged.
- a header portion is formed. For this reason, it is difficult to be directly affected by the thermal effect of the semiconductor element, and the temperature of the refrigerant supplied from the sub header portion can be maintained at a lower temperature.
- the refrigerant in the sub-header part is affected by the heat-generating element. May be affected.
- the heat of the heating element can be blocked by the isolation wall 18 b, and the low-temperature refrigerant can be reliably supplied to the merge space.
- the material of the isolation wall is not limited, but it is preferably formed of a heat insulating material. With this configuration, the temperature increase of the refrigerant in the sub header portion can be more effectively suppressed.
- the flow path cross-sectional area of the sub header portion is large, the pressure loss in the sub header portion can be further reduced. As a result, even on the downstream side, a large amount of refrigerant can be supplied from the sub header section to the merge space.
- the opening formed in the isolation wall has a circular or quadrangular planar shape.
- the present invention is not limited to this shape, and any shape can be adopted.
- the opening may be a long hole extending along the merge space.
- Other configurations, operations, and effects are the same as those in the first and second embodiments, and thus description thereof will not be repeated here.
- the present invention is applicable to, for example, a heat sink or a cooler for cooling a semiconductor element constituting an electric device (PCU: power control unit) that controls a rotating electric machine for driving a hybrid vehicle.
- PCU power control unit
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN200780022420.8A CN101473432B (zh) | 2006-06-14 | 2007-06-12 | 散热装置以及冷却器 |
US12/304,891 US8291967B2 (en) | 2006-06-14 | 2007-06-12 | Heat sink and cooler |
DE112007001424.5T DE112007001424B4 (de) | 2006-06-14 | 2007-06-12 | Kühler |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006164956A JP4675283B2 (ja) | 2006-06-14 | 2006-06-14 | ヒートシンクおよび冷却器 |
JP2006-164956 | 2006-06-14 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007145352A1 true WO2007145352A1 (ja) | 2007-12-21 |
Family
ID=38831860
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/062197 WO2007145352A1 (ja) | 2006-06-14 | 2007-06-12 | ヒートシンクおよび冷却器 |
Country Status (5)
Country | Link |
---|---|
US (1) | US8291967B2 (ja) |
JP (1) | JP4675283B2 (ja) |
CN (1) | CN101473432B (ja) |
DE (1) | DE112007001424B4 (ja) |
WO (1) | WO2007145352A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010021406A (ja) * | 2008-07-11 | 2010-01-28 | Toyota Industries Corp | 半導体装置 |
JP2013048204A (ja) * | 2011-07-28 | 2013-03-07 | Kyocera Corp | 流路部材、これを用いた熱交換器および電子部品装置ならびに半導体製造装置 |
US8472193B2 (en) | 2008-07-04 | 2013-06-25 | Kabushiki Kaisha Toyota Jidoshokki | Semiconductor device |
CN108257930A (zh) * | 2016-12-28 | 2018-07-06 | 三菱自动车工程株式会社 | 一种冷却装置 |
Families Citing this family (52)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8081462B2 (en) * | 2007-09-13 | 2011-12-20 | Rockwell Automation Technologies, Inc. | Modular liquid cooling system |
JP4992808B2 (ja) * | 2008-04-16 | 2012-08-08 | トヨタ自動車株式会社 | 熱交換器の製造方法 |
JP5114324B2 (ja) * | 2008-07-07 | 2013-01-09 | 株式会社豊田自動織機 | 半導体装置 |
JP4485583B2 (ja) | 2008-07-24 | 2010-06-23 | トヨタ自動車株式会社 | 熱交換器及びその製造方法 |
JP4867998B2 (ja) * | 2009-01-16 | 2012-02-01 | 株式会社豊田自動織機 | 産業車両用電気部品ユニットおよび該ユニットを有する産業車両 |
WO2010131317A1 (ja) | 2009-05-11 | 2010-11-18 | トヨタ自動車株式会社 | 熱交換器、半導体装置、及び、これらの製造方法 |
EP2259310B1 (en) * | 2009-06-05 | 2020-04-08 | Siemens Gamesa Renewable Energy A/S | Integrated heat exchanger |
US8933557B2 (en) | 2009-08-10 | 2015-01-13 | Fuji Electric Co., Ltd. | Semiconductor module and cooling unit |
JP2011058754A (ja) * | 2009-09-11 | 2011-03-24 | Toshiba Corp | 熱交換媒体および熱交換器 |
JP2011134979A (ja) * | 2009-12-25 | 2011-07-07 | Fuji Electric Co Ltd | 液体冷却式ヒートシンク |
JP2011134978A (ja) * | 2009-12-25 | 2011-07-07 | Fuji Electric Co Ltd | 流体冷却式ヒートシンク |
JP5714836B2 (ja) * | 2010-04-17 | 2015-05-07 | モレックス インコーポレイテドMolex Incorporated | 熱輸送ユニット、電子基板、電子機器 |
WO2011132736A1 (ja) * | 2010-04-21 | 2011-10-27 | 富士電機システムズ株式会社 | 半導体モジュール及び冷却器 |
EP2431699A1 (en) * | 2010-09-20 | 2012-03-21 | Thermal Corp. | Cooling apparatus |
US8797741B2 (en) * | 2010-10-21 | 2014-08-05 | Raytheon Company | Maintaining thermal uniformity in micro-channel cold plates with two-phase flows |
US20130068433A1 (en) * | 2011-03-17 | 2013-03-21 | Shreekanth Murthy Muthigi | Heat exchanger |
EP2523215B1 (en) * | 2011-05-13 | 2015-02-18 | ABB Oy | Liquid cooling element |
EP2711983B1 (en) * | 2011-05-16 | 2022-06-15 | Fuji Electric Co., Ltd. | Semiconductor module cooler |
TWI438388B (zh) * | 2011-05-20 | 2014-05-21 | Wistron Corp | 液冷式散熱裝置 |
CN102278902B (zh) * | 2011-07-04 | 2013-01-23 | 中国科学院广州能源研究所 | 换热器及其制造方法 |
EP2574157A1 (de) * | 2011-09-23 | 2013-03-27 | AEG Power Solutions B.V. | Leistungselektronikbaugruppe und Anordnung umfassend wenigstens eine solche Leistungselektronikbaugruppe |
JP2013216216A (ja) * | 2012-04-10 | 2013-10-24 | Ntn Corp | インバータ装置の冷却構造 |
JP6140818B2 (ja) * | 2013-05-17 | 2017-05-31 | 株式会社ソニー・インタラクティブエンタテインメント | 電子機器及びその製造方法 |
US9832908B2 (en) | 2013-05-17 | 2017-11-28 | Sony Interactive Entertainment Inc. | Electronic apparatus |
JP6196815B2 (ja) * | 2013-06-05 | 2017-09-13 | 新光電気工業株式会社 | 冷却装置及び半導体装置 |
JP6374301B2 (ja) * | 2013-12-24 | 2018-08-15 | 東京エレクトロン株式会社 | ステージ、ステージの製造方法、熱交換器 |
JP2015159254A (ja) * | 2014-02-25 | 2015-09-03 | 三桜工業株式会社 | 冷却装置及び冷却装置の製造方法 |
JP6156283B2 (ja) * | 2014-08-07 | 2017-07-05 | 株式会社デンソー | 電力変換装置 |
JP6336364B2 (ja) * | 2014-09-12 | 2018-06-06 | 株式会社ティラド | ヒートシンク |
WO2016117342A1 (ja) * | 2015-01-21 | 2016-07-28 | パナソニックIpマネジメント株式会社 | 冷却装置およびこれを搭載した電子機器 |
US9538691B2 (en) * | 2015-04-15 | 2017-01-03 | Ford Global Technologies, Llc | Power inverter for a vehicle |
CN105451523A (zh) * | 2015-12-28 | 2016-03-30 | 联想(北京)有限公司 | 散热装置及电子设备 |
US10014238B2 (en) * | 2016-07-19 | 2018-07-03 | Ge Energy Power Conversion Technology Ltd | Method, system, and electronic assembly for thermal management |
JP6324457B2 (ja) * | 2016-09-20 | 2018-05-16 | 三菱電機株式会社 | 電気機器 |
JP6868633B2 (ja) * | 2016-09-23 | 2021-05-12 | 住友精密工業株式会社 | 冷却装置 |
US10136564B2 (en) * | 2016-09-30 | 2018-11-20 | Denso Corporation | Power converter |
KR102599984B1 (ko) * | 2016-10-06 | 2023-11-09 | 엘지전자 주식회사 | Igbt 모듈 냉각 열 교환기 |
TWI624640B (zh) * | 2017-01-25 | 2018-05-21 | 雙鴻科技股份有限公司 | 液冷式散熱裝置 |
JP6636996B2 (ja) * | 2017-07-11 | 2020-01-29 | ファナック株式会社 | Ldモジュール冷却装置及びレーザ装置 |
JP6981250B2 (ja) * | 2017-12-28 | 2021-12-15 | セイコーエプソン株式会社 | 冷却装置およびプロジェクター |
CN208227548U (zh) * | 2018-04-18 | 2018-12-11 | 哈曼国际工业有限公司 | 电子装置和用于电子装置的散热装置 |
US10840167B2 (en) * | 2018-11-19 | 2020-11-17 | Advanced Micro Devices, Inc. | Integrated heat spreader with configurable heat fins |
JP6881516B2 (ja) * | 2019-07-29 | 2021-06-02 | 株式会社富士通ゼネラル | 隔壁式熱交換器 |
US20220246495A1 (en) * | 2019-09-04 | 2022-08-04 | Mitsubishi Electric Corporation | Heat sink and semiconductor module |
JP7388145B2 (ja) | 2019-11-19 | 2023-11-29 | 株式会社レゾナック | 半導体冷却装置 |
CN110848822A (zh) * | 2019-11-21 | 2020-02-28 | 青岛海尔空调器有限总公司 | 散热构件、散热器和空调器 |
CN110993576B (zh) * | 2019-12-23 | 2021-10-15 | 西安华为技术有限公司 | 一种散热装置及通信设备 |
WO2021186891A1 (ja) * | 2020-03-18 | 2021-09-23 | 富士電機株式会社 | 半導体モジュール |
US11326836B1 (en) * | 2020-10-22 | 2022-05-10 | Asia Vital Components Co., Ltd. | Vapor/liquid condensation system |
US11175102B1 (en) * | 2021-04-15 | 2021-11-16 | Chilldyne, Inc. | Liquid-cooled cold plate |
US20220373236A1 (en) * | 2021-05-20 | 2022-11-24 | Carrier Corporation | Heat exchanger for power electronics |
US20230128951A1 (en) * | 2021-10-27 | 2023-04-27 | Carrier Corporation | Heat exchanger for power electronics |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006054456A (ja) * | 2004-08-02 | 2006-02-23 | Asml Holding Nv | コンパクトなマイクロチャネル式層状熱交換のための方法及びシステム |
JP2006054434A (ja) * | 2004-06-29 | 2006-02-23 | Cooligy Inc | 熱を発生するデバイスにおける所望のホットスポットを冷却するための柔軟な流体輸送のための方法及び装置 |
Family Cites Families (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4386505A (en) * | 1981-05-01 | 1983-06-07 | The Board Of Trustees Of The Leland Stanford Junior University | Refrigerators |
US4494171A (en) * | 1982-08-24 | 1985-01-15 | Sundstrand Corporation | Impingement cooling apparatus for heat liberating device |
US4694378A (en) * | 1984-12-21 | 1987-09-15 | Hitachi, Ltd. | Apparatus for cooling integrated circuit chips |
US4730666A (en) * | 1986-04-30 | 1988-03-15 | International Business Machines Corporation | Flexible finned heat exchanger |
JP2769632B2 (ja) * | 1989-06-09 | 1998-06-25 | 功 皆川 | 整畦機 |
US5016090A (en) * | 1990-03-21 | 1991-05-14 | International Business Machines Corporation | Cross-hatch flow distribution and applications thereof |
US5088005A (en) * | 1990-05-08 | 1992-02-11 | Sundstrand Corporation | Cold plate for cooling electronics |
JPH05206339A (ja) | 1992-01-27 | 1993-08-13 | Matsushita Electric Ind Co Ltd | 放熱器 |
JP3010602U (ja) | 1994-10-26 | 1995-05-02 | 東洋ラジエーター株式会社 | 電子部品冷却器 |
US5604665A (en) * | 1995-06-30 | 1997-02-18 | International Business Machines Corporation | Multiple parallel impingement flow cooling with tuning |
JPH0923081A (ja) | 1995-07-05 | 1997-01-21 | Nippondenso Co Ltd | 沸騰冷却装置 |
DE19643717A1 (de) * | 1996-10-23 | 1998-04-30 | Asea Brown Boveri | Flüssigkeits-Kühlvorrichtung für ein Hochleistungshalbleitermodul |
JPH10200278A (ja) | 1997-01-13 | 1998-07-31 | Yaskawa Electric Corp | 冷却装置 |
US6169658B1 (en) * | 1999-10-13 | 2001-01-02 | Trw Inc. | Plenumless air cooled avionics rack |
US6301109B1 (en) * | 2000-02-11 | 2001-10-09 | International Business Machines Corporation | Isothermal heat sink with cross-flow openings between channels |
JP2001352025A (ja) | 2000-06-05 | 2001-12-21 | Toshiba Corp | 発熱体冷却装置 |
JP3857060B2 (ja) * | 2001-02-09 | 2006-12-13 | 株式会社東芝 | 発熱体冷却装置 |
JP2002314280A (ja) * | 2001-04-10 | 2002-10-25 | Denki Kagaku Kogyo Kk | 回路基板の冷却構造及び冷却方法 |
JP3880812B2 (ja) * | 2001-06-04 | 2007-02-14 | 東芝三菱電機産業システム株式会社 | 冷却器 |
CN1316224C (zh) * | 2001-09-05 | 2007-05-16 | 昭和电工株式会社 | 散热器、带有该散热器的控制装置、具备该装置的工作机械 |
JP3781018B2 (ja) | 2002-08-16 | 2006-05-31 | 日本電気株式会社 | 電子機器の冷却装置 |
US7806168B2 (en) * | 2002-11-01 | 2010-10-05 | Cooligy Inc | Optimal spreader system, device and method for fluid cooled micro-scaled heat exchange |
US7188622B2 (en) * | 2003-06-19 | 2007-03-13 | 3M Innovative Properties Company | Filtering face mask that has a resilient seal surface in its exhalation valve |
JP3908705B2 (ja) * | 2003-08-29 | 2007-04-25 | 株式会社東芝 | 液冷装置及び液冷システム |
JP4052221B2 (ja) | 2003-10-09 | 2008-02-27 | 株式会社デンソー | 冷却システム |
US7188662B2 (en) * | 2004-06-04 | 2007-03-13 | Cooligy, Inc. | Apparatus and method of efficient fluid delivery for cooling a heat producing device |
US7190580B2 (en) * | 2004-07-01 | 2007-03-13 | International Business Machines Corporation | Apparatus and methods for microchannel cooling of semiconductor integrated circuit packages |
US7139172B2 (en) * | 2004-07-01 | 2006-11-21 | International Business Machines Corporation | Apparatus and methods for microchannel cooling of semiconductor integrated circuit packages |
JP2007294891A (ja) * | 2006-03-30 | 2007-11-08 | Dowa Metaltech Kk | 放熱器 |
-
2006
- 2006-06-14 JP JP2006164956A patent/JP4675283B2/ja not_active Expired - Fee Related
-
2007
- 2007-06-12 US US12/304,891 patent/US8291967B2/en not_active Expired - Fee Related
- 2007-06-12 DE DE112007001424.5T patent/DE112007001424B4/de not_active Expired - Fee Related
- 2007-06-12 CN CN200780022420.8A patent/CN101473432B/zh not_active Expired - Fee Related
- 2007-06-12 WO PCT/JP2007/062197 patent/WO2007145352A1/ja active Search and Examination
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006054434A (ja) * | 2004-06-29 | 2006-02-23 | Cooligy Inc | 熱を発生するデバイスにおける所望のホットスポットを冷却するための柔軟な流体輸送のための方法及び装置 |
JP2006054456A (ja) * | 2004-08-02 | 2006-02-23 | Asml Holding Nv | コンパクトなマイクロチャネル式層状熱交換のための方法及びシステム |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8472193B2 (en) | 2008-07-04 | 2013-06-25 | Kabushiki Kaisha Toyota Jidoshokki | Semiconductor device |
US8958208B2 (en) | 2008-07-04 | 2015-02-17 | Kabushiki Kaisha Toyota Jidoshokki | Semiconductor device |
JP2010021406A (ja) * | 2008-07-11 | 2010-01-28 | Toyota Industries Corp | 半導体装置 |
JP2013048204A (ja) * | 2011-07-28 | 2013-03-07 | Kyocera Corp | 流路部材、これを用いた熱交換器および電子部品装置ならびに半導体製造装置 |
CN108257930A (zh) * | 2016-12-28 | 2018-07-06 | 三菱自动车工程株式会社 | 一种冷却装置 |
Also Published As
Publication number | Publication date |
---|---|
JP4675283B2 (ja) | 2011-04-20 |
US8291967B2 (en) | 2012-10-23 |
DE112007001424T5 (de) | 2009-04-23 |
US20090250195A1 (en) | 2009-10-08 |
DE112007001424B4 (de) | 2014-06-26 |
JP2007335588A (ja) | 2007-12-27 |
CN101473432A (zh) | 2009-07-01 |
CN101473432B (zh) | 2011-11-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2007145352A1 (ja) | ヒートシンクおよび冷却器 | |
US8472193B2 (en) | Semiconductor device | |
JP4649359B2 (ja) | 冷却器 | |
US8427832B2 (en) | Cold plate assemblies and power electronics modules | |
JP4333587B2 (ja) | ヒートシンクおよび冷却ユニット | |
US7278474B2 (en) | Heat exchanger | |
US20070017662A1 (en) | Normal-flow heat exchanger | |
KR20190016945A (ko) | 압력 강하가 감소된 마이크로채널 증발기 | |
JP2009266937A (ja) | 積層型冷却器 | |
JP4941398B2 (ja) | 積層型冷却器 | |
JP2011192730A (ja) | 冷却器、積層冷却器および中間プレート | |
JP2010278286A (ja) | ヒートシンク装置 | |
JP4013883B2 (ja) | 熱交換器 | |
JP2011071398A (ja) | 半導体冷却構造 | |
JP2008300447A (ja) | 放熱装置 | |
JP2008235572A (ja) | 電子部品冷却装置 | |
JP4572911B2 (ja) | 熱交換器 | |
KR20180109668A (ko) | 전기소자 냉각용 열교환기 | |
JP7431719B2 (ja) | パワーデバイス用冷却器 | |
JP2007115940A (ja) | 熱分散プレート | |
JP2004028378A (ja) | 熱交換器 | |
KR100921625B1 (ko) | 적층형 열교환기 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200780022420.8 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 07767126 Country of ref document: EP Kind code of ref document: A1 |
|
DPE1 | Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 12304891 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120070014245 Country of ref document: DE |
|
RET | De translation (de og part 6b) |
Ref document number: 112007001424 Country of ref document: DE Date of ref document: 20090423 Kind code of ref document: P |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 07767126 Country of ref document: EP Kind code of ref document: A1 |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8607 |
|
DPE1 | Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101) |