WO2015087530A1 - 冷媒分配装置および冷却装置 - Google Patents
冷媒分配装置および冷却装置 Download PDFInfo
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- WO2015087530A1 WO2015087530A1 PCT/JP2014/006096 JP2014006096W WO2015087530A1 WO 2015087530 A1 WO2015087530 A1 WO 2015087530A1 JP 2014006096 W JP2014006096 W JP 2014006096W WO 2015087530 A1 WO2015087530 A1 WO 2015087530A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- pipe
- main body
- heat
- distribution device
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
- F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/06—Control arrangements therefor
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- 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
- H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
- H05K7/208—Liquid cooling with phase change
- H05K7/20818—Liquid cooling with phase change within cabinets for removing heat from server blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/17—Size reduction
Definitions
- the present invention relates to a refrigerant distribution device and a cooling device for a cooling device that cools exhaust heat of electronic equipment.
- a method of using the phase change of the refrigerant and circulating without using a pump to absorb the heat of the electronic device is considered. This method is very economical because no power is used for the circulation of the refrigerant. Further, when an insulating refrigerant is used as the internal refrigerant, even if a part is damaged and the internal refrigerant leaks, the influence on the electronic device is very small. Therefore, the means utilizing the phase change of the refrigerant is very effective means for absorbing the exhaust heat of the electronic equipment such as a server in the data center that is not allowed to stop.
- FIG. 1 is a schematic diagram of a cooling device that absorbs exhaust heat of the electronic device 6, and FIG. 2 is a view of the cooling device attached to a rack 5 in which the electronic device 6 is housed.
- the heat receiver 1 that absorbs the exhaust heat of the electronic device 6 is installed on the exhaust side of the rack 5 in which many electronic devices 6 are stored.
- a heat radiator 2 is installed in the upper part of the heat receiver 1, and the heat receiver 1 and the heat radiator 2 are constituted by two pipes, a gas phase pipe 3 through which the gas phase refrigerant passes and a liquid phase pipe 4 through which the liquid phase refrigerant passes. It is communicated.
- a refrigerant is sealed inside, and in the heat receiver 1, the liquid-phase refrigerant boils by receiving external heat, and changes into a gas-phase refrigerant.
- the phase-changed gas-phase refrigerant moves to the radiator 2 through the gas-phase pipe 3 due to its buoyancy, and is deprived of heat by a cooler such as a fan or a water-cooling device. Change.
- the liquid-phase refrigerant passes through the liquid-phase tube 4 and descends due to its gravity, and returns to the heat receiver 1.
- the rack 5 on which the electronic device 6 such as a server is mounted has a height of about 2 m, which is often used in a data center or the like.
- the system shown in FIG. 2 is applied to a rack of this size, there is a problem that the refrigerant accumulates in the lower part due to the weight of the liquid-phase refrigerant and the refrigerant is not supplied to the upper heat receiver 1.
- Patent Document 1 and Patent Document 1 disclose a technique in which a plurality of heat receivers are divided into a plurality of stages in the vertical direction, and a plurality of refrigerant distribution devices are provided at locations where each liquid phase tube branches into a plurality of heat receivers. 2 is disclosed.
- the liquid phase refrigerant flows into the refrigerant distributor, and the liquid phase refrigerant is supplied to each heat receiver through a pipe provided in the lower part.
- the inside of the refrigerant distributor overflows, passes through a pipe that flows through the lower liquid phase pipe provided on the side surface, and goes to the refrigerant distributor that supplies the refrigerant to the next heat receiver.
- Patent Document 1 As the refrigerant level in the tank rises, the float member disposed in the tank also rises as the level of the refrigerant liquid in the tank rises, and the valve mechanism in the pipe closes, thereby reducing the liquid level.
- An adjusting refrigerant distribution device is disclosed. Since it is necessary to install the float member, the refrigerant distributor becomes large, the heat receiver becomes small, and a sufficient heat receiving area cannot be obtained, so that sufficient heat absorption performance cannot be ensured.
- Patent Document 2 if a downstream liquid phase pipe that flows to the lower refrigerant distributor is provided on the side surface of the refrigerant distributor, a bent portion of the pipe must be provided. Therefore, the ratio of the piping to the lateral width increases, and the heat receiver cannot have a sufficient heat receiving area, and sufficient heat absorption performance cannot be ensured. Even if the heat receiving area is increased by arranging the downstream liquid phase pipe and the upstream liquid phase pipe in a straight line in order to reduce the piping space, Since it flows into the liquid phase tube, the liquid phase refrigerant cannot be sufficiently supplied to the heat receiver, and sufficient heat absorption performance cannot be obtained.
- An object of the present invention is to provide a refrigerant distribution device and a cooling device that supply space evenly to a multi-stage heat receiver and save space.
- a refrigerant distribution device for distributing refrigerant supplied from upstream, wherein the refrigerant distribution device is provided on the upper surface portion so as to communicate with a main body portion having a side wall portion, an upper surface portion and a lower surface portion, and the inside of the main body portion.
- An upstream pipe, a downstream pipe provided in a state where a part thereof is inserted into the main body through a lower surface hole provided in the lower surface, and the side wall or the lower surface so as to communicate with the inside of the main body.
- a branch flow pipe provided in the section, and a refrigerant turning means provided between the upstream pipe and the downstream pipe.
- FIG. 3 shows an overall view of a cooling device including the refrigerant distribution device of the present embodiment.
- a heat receiver 1 is disposed on a side surface (exhaust side) of a storage body in which a large number of electronic devices such as a server that emit a large amount of heat are disposed, and the heat receiver 1 is connected to the heat receiver 1 by piping. 2 is placed on top of it.
- the housing and the heat receiver 1 are installed in a building, the radiator 2 is installed outside the building, and the heat receiver 1 and the radiator 2 communicate with each other by two pipes. This is the configuration.
- the storage body in which the electronic device assumed in the present embodiment is arranged is assumed to be a 19-inch rack used for storing many electronic devices such as servers and network devices.
- the 19-inch rack may be a JIS standard (Japanese Industrial Standard) or an EIA standard (American Electronic Industries Association standard).
- a 19-inch rack is assumed, but it is not limited to this as long as it is similar.
- the heat receivers 1 installed on the exhaust side are provided in a plurality (in multiple stages) and are arranged in the height direction of the rack.
- the heat receiver 1 absorbs the exhaust heat of the electronic device by boiling the internal liquid-phase refrigerant and changing the phase to a gas-phase refrigerant.
- Each heat receiver 1 includes a hollow tube and fins 9 arranged in a tube tube and headers 7 and 8 arranged above and below them.
- the heat receiver 1 communicates with a gas-phase branch pipe 11 that communicates with the gas-phase pipe 3 through which the gas-phase refrigerant passes on the side surface of the upper header 7.
- the gas phase pipe 3 communicates with each heat receiver 1 via each gas phase branch pipe 11 that communicates with each heat receiver 1.
- the heat receiver 1 communicates with the liquid-phase branch pipe 12 that communicates with the branch port of the refrigerant distributor 10 on the side surface of the lower header 8 and is supplied with the liquid-phase refrigerant.
- the vapor phase pipe 3 has a manifold shape in which the vapor phase refrigerant flowing out from each heat receiver 1 through the gas phase branch pipe 11 joins.
- the gas phase tube 3 extends to the radiator 2 installed on the upper part of the heat receiver 1 and communicates with the radiator 2.
- the gas phase tube 3 has a volume that is several hundred times as large as that of the liquid phase refrigerant.
- a pipe from each gas-phase branch pipe 11 communicating with each heat receiver 1 to the gas-phase pipe 3 communicating with the radiator 2 may be a first pipe. In this case, the first pipe is branched at a plurality of locations and communicates with each heat receiver 1.
- the heat radiator 2 radiates heat transported by the gas-phase refrigerant.
- heat may be dissipated by exchanging heat between the gas-phase refrigerant and water, or heat may be dissipated by exchanging heat between the air-phase and gas-phase refrigerant.
- the warmed water is cooled by a chiller or a cooling tower and circulated by a pump or the like.
- heat is exchanged with air, the warmed air is sent to the radiator 2 by a fan or the like, and the air exchanged with the gas phase refrigerant is discharged into a space separated from the space where the rack is installed.
- the cooled gas phase refrigerant condenses and changes into a liquid phase refrigerant.
- the liquid phase pipe 4 through which the liquid phase refrigerant circulates is installed on the side opposite to the gas phase pipe 3 on the rack exhaust side, and the refrigerant distributor 10 is provided at a location where the liquid phase pipe 4 branches to each heat receiver 1. Is provided, and an appropriate amount of liquid phase refrigerant is supplied to each heat receiver 1 via the liquid phase branch pipe 12.
- the plurality of refrigerant distributors 10 are connected in series via the liquid phase pipe 4 in the vertical direction.
- Each refrigerant distributor 10 communicates with each heat receiver 1 via a liquid-phase branch pipe 12 that communicates with each heat receiver 1.
- the refrigerant distributor 10 at the lower end of the liquid phase pipe 4 supplies the liquid phase refrigerant to the heat receiver 1 at the lower end without flowing downward.
- a pipe from the liquid phase pipe 4 communicating with the radiator 2 to the liquid phase branch pipe 12 communicating with each heat receiver 1 may be used as the second pipe.
- the second pipe is branched at a plurality of locations and communicates with each of the heat receivers 1, and the refrigerant distributor 10 is provided at each of the branch locations.
- These devices are sealed by reducing the pressure by vacuuming or the like after filling the refrigerant.
- Refrigerant is an insulating refrigerant for use in electronic equipment.
- HFC hydrofluorocarbon
- HFE hydrofluoroether
- FIGS. 4 is a cross-sectional view of the refrigerant distributor 10
- FIG. 5 is a cross-sectional view seen from the point A shown in FIG.
- the refrigerant distribution device 10 forms a main body portion by a side wall portion by the branch outer wall 14 and an upper surface portion and a lower surface portion.
- An upper surface hole portion 21 is provided in the upper surface portion, and is joined to the upstream liquid phase pipe port 17 of the upstream liquid phase pipe 4 which is an upstream pipe extending in the upstream direction.
- the upstream liquid phase tube 4 may be integrally formed with the upper surface portion.
- a part of the refrigerant lead-in pipe 13 which is a downstream pipe is inserted into the main body portion and is formed to extend in the downstream direction through a lower surface hole portion 22 provided in the lower surface portion.
- the refrigerant drawing pipe 13 is provided with a refrigerant drawing pipe port 18a at the end.
- the liquid phase branch pipe 12 is joined to a side wall hole 23 provided in the side wall. Further, the liquid phase branch pipe 12 may be integrated with the side wall portion. Since the liquid-phase branch pipe 12 only needs to be provided at a position lower than the height of the refrigerant inlet pipe port 18a, it may be joined to the lower surface portion.
- a direction changing plate 15 a serving as a refrigerant direction changing means is provided between the refrigerant inlet pipe port 18 a and the upstream liquid phase pipe port 17.
- the refrigerant distributor 10 of the present embodiment communicates with the upstream liquid phase pipe 4 and communicates with the downstream liquid phase pipe 4 through an internal refrigerant drawing pipe 13. Further, the liquid-phase branch pipes 12 connected to the respective heat receivers 1 communicate with the storage section 16 below the branch outer wall 14. Inside, there is a deflecting plate 15 a that functions as a refrigerant redirecting means for redirecting the flow of the liquid-phase refrigerant descending from the upstream liquid-phase pipe 4 toward the branch outer wall 14, and the upstream liquid-phase pipe 4 and the refrigerant intake pipe 13. It is provided between.
- the branch outer wall 14 which is the outer wall of the refrigerant distributor 10 has a size larger than the diameter of the liquid phase tube 4.
- the shape may be a cylinder or a rectangular parallelepiped, but a cylinder is desirable in view of the manufacturing surface. If the branch outer wall 14 is too small, the refrigerant intake pipe 13 and the storage part 16 on the branch outer wall 14 become small, and when a large flow rate falls from the upstream, it immediately overflows and the refrigerant is appropriately received by the heat receiver. 1 can not be supplied. In addition, the pressure loss of the liquid-phase refrigerant passing through the storage unit 16 increases, and the amount of refrigerant supplied to the heat receiver 1 decreases.
- the branched outer wall 14 is too large, it takes time for the liquid refrigerant to overflow, and the liquid refrigerant cannot be supplied to the lower heat receiver 1 at an appropriate timing. Furthermore, if the branch outer wall 14 is too large, it takes up space. Therefore, when the cooling device of the present embodiment is installed in a rack or the like, the heat receiver 1 must be made small, and the heat absorption performance is degraded.
- the diameter of the branch outer wall 14 is desirably small as long as the flow to the liquid-phase branch pipe 12 is not hindered. Specifically, the size of 1.2 to 5 times the diameter of the liquid phase tube 4 is desirable. That is, the cross-sectional area of the main body may be smaller than the sum of the cross-sectional area of the liquid phase tube 4 and the cross-sectional area of the refrigerant drawing tube 13.
- the length of the branched outer wall 14 in the liquid-phase refrigerant descending direction is set so that the refrigerant suction pipe 13 can be accommodated and the gap between the direction change plate 15a, the upstream liquid-phase pipe port, and the refrigerant suction pipe port 18a is appropriately maintained.
- a refrigerant drawing pipe 13 protruding in the center is arranged so as to be linear with the upstream liquid phase pipe 4.
- the diameter of the refrigerant drawing pipe 13 is preferably equal to the diameter of the liquid phase pipe 4 in consideration of connection with the liquid phase pipe 4. If the position of the refrigerant inlet pipe port 18a is too high, the liquid level of the liquid phase refrigerant stored in the storage unit 16 becomes the position of the gas phase branch pipe 11 of the heat receiver 1. In this state, the liquid-phase refrigerant flows into the gas-phase pipe 3 from the gas-phase branch pipe 11 of the heat receiver 1, obstructs the rising flow of the gas-phase refrigerant, and reduces the heat absorption performance.
- the position of the refrigerant inlet pipe port 18a is fixed at a position where the liquid phase refrigerant does not flow into the gas phase pipe and a sufficiently high liquid phase refrigerant can be stored in the storage unit 16.
- the position of the refrigerant inlet pipe port 18a is preferably above the upper surface of the liquid phase branch pipe 12 and below the lower surface of the gas phase branch pipe 11 of the heat receiver 1 connected to the refrigerant distributor 10.
- the deflecting plate 15a is installed at such a position and size that the liquid refrigerant descending from the upstream liquid phase pipe 4 does not directly flow into the refrigerant draw pipe 13 from the refrigerant draw pipe port 18a.
- the direction change plate 15a is installed between the upstream liquid phase inlet 17 and the refrigerant inlet pipe 18a so as to have the same size as the diameter of the refrigerant inlet pipe 13.
- the shape of the deflecting plate 15a may be circular or rectangular. If the position of the deflecting plate 15a is too close to the upstream liquid phase tube 4 side, the flow of the liquid phase refrigerant descending from the upstream liquid phase tube 4 is changed to obstruct the circulation, and the endothermic performance is deteriorated.
- the direction change plate 15a is provided at a position where the flow of the liquid phase refrigerant descending from the upstream liquid phase tube 4 and the flow from the storage unit 16 to the refrigerant drawing tube 13 are not hindered. Specifically, it is desirable that the height between the direction change plate 15 a and the upstream pipe port and the area around the direction change plate 15 a be equal to or larger than the cross-sectional area of the liquid phase tube 4. Similarly, it is desirable that the height between the direction change plate 15a and the refrigerant intake pipe port 18a and the area around the direction change plate 15a be equal to or larger than the cross-sectional area of the refrigerant intake pipe 13.
- the fixing plate 15a is fixed by bringing a part of the changing plate 15a into contact with the branch outer wall 14 and fixing it with the branch outer wall 14 by welding or brazing. At this time, a hole may be provided in a portion extending from the deflecting plate 15a to the branch outer wall 14 and fixed by a screw or the like. Further, the deflecting plate 15a may be integrated with the main body.
- the reservoir 16 accumulates and the height increases, so that the force for pushing out the refrigerant to the liquid phase branch pipe 12 is increased, and a large amount of liquid phase refrigerant can be supplied to the heat receiver 1. .
- the branch outer wall 14, the upstream liquid phase pipe 4, and the refrigerant lead-in pipe 13 can be made of metal such as aluminum or stainless steel.
- the direction plate 15a is not particularly limited as long as it has predetermined heat resistance.
- the refrigerant distributor 10 distributes an appropriate amount of liquid phase refrigerant to the heat receiver 1 connected to the refrigerant distributor 10 while lowering the liquid refrigerant to the lower refrigerant distributor 10 by its internal structure.
- the liquid-phase refrigerant refluxed to each heat receiver 1 receives the exhaust heat of the electronic device again, boils and absorbs heat by becoming a gas-phase refrigerant, and heat-transports to the radiator 2 by moving the gas-phase refrigerant. .
- the liquid phase refrigerant that has descended from the upstream liquid phase pipe 4 is first changed in the direction of descending by hitting the direction change plate 15 a, and does not directly enter the refrigerant drawing pipe 13, but the surrounding storage unit 16.
- the liquid phase branch pipe 12 communicates with the storage unit 16, and the liquid phase refrigerant in the storage unit 16 is returned to the heat receiver 1 through the liquid phase refrigerant distributor 10.
- the liquid phase refrigerant stored in the storage unit 16 always comes into contact with the refrigerant drawing tube 13 and brings the refrigerant drawing tube 13 to substantially the same temperature as the liquid phase refrigerant.
- the liquid-phase refrigerant in the storage unit 16 overflows and flows into the refrigerant draw-in pipe 13 from the refrigerant draw-in pipe port 18a.
- the refrigerant inlet pipe 13 is always at the same temperature as the liquid phase refrigerant due to the liquid phase refrigerant in the storage unit 16, the refrigerant will boil even if the temperature is higher than the exhaust heat from the electronic device. However, it does not interfere with the flow of the liquid refrigerant that overflows and flows in.
- the liquid phase tube 4 connected to the refrigerant drawing tube 13 may be at a high temperature because it touches the outside air. However, since the liquid phase tube 4 has a certain flow velocity while descending the refrigerant drawing tube 13, the high temperature is high. Even if the liquid phase tube 4 is touched or boiled there, the liquid phase refrigerant has a certain flow velocity, so that it can overcome and descend.
- the refrigerant that has descended from the refrigerant inlet pipe 13 passes through the liquid phase pipe 4 and supplies the liquid refrigerant to the next heat receiver 1 at the next refrigerant distributor 10 or at the end.
- the deflecting plate 15 a is provided between the upstream liquid phase pipe 4 and the refrigerant drawing pipe 13, so that the liquid phase is transferred to the heat receiver 1 through the liquid phase branch pipe 12 communicating with the storage unit 16.
- the liquid phase refrigerant can be distributed to the lower refrigerant distribution device 10 while supplying the refrigerant.
- the upstream liquid phase pipe 4 and the refrigerant drawing pipe 13 can be arranged linearly, the installation space can be greatly reduced. Thereby, when installing in a rack or the like where the installation space is limited, the area of the heat receiver 1 can be maximized, so that the heat absorption performance can be improved.
- the liquid-phase refrigerant stored in the storage unit 16 of the refrigerant distributor 10 since the refrigerant intake pipe 13 is partially inserted into the main body, the liquid-phase refrigerant stored in the storage unit 16 of the refrigerant distributor 10 always comes into contact with the refrigerant intake pipe 13.
- the temperature of the refrigerant drawing pipe 13 can be kept the same as the liquid phase refrigerant temperature. Therefore, when the liquid-phase refrigerant stored in the storage unit 16 overflows and the liquid-phase refrigerant flows into the refrigerant drawing pipe 13, the liquid-phase refrigerant boils and may obstruct the flow of the inflowing liquid-phase refrigerant. Absent. Accordingly, the refrigerant can be efficiently distributed to each heat receiver 1 and circulated, so that the heat absorption performance is not deteriorated.
- FIG. 7 is a cross-sectional view of the refrigerant distribution device 10 of the present embodiment
- FIG. 8 is a cross-sectional view from the point shown in FIG.
- cooling device of the present embodiment is different only in the configuration of the refrigerant distribution device 10 described in the first embodiment, description of other parts is omitted.
- the difference between this embodiment and the first embodiment is the structure of the deflecting plate 15b.
- the deflecting plate 15 b is arranged so as to be inclined with respect to the flow direction of the upstream liquid phase tube 4 and the refrigerant drawing tube 13 so that the liquid phase refrigerant from the upstream flows into the storage unit 16.
- the direction change plate 15b and the refrigerant It is necessary to incline the diverting plate 15b so that the closest distance of the lead-in port 18a and the farthest distance are sufficiently large.
- the angle at which the direction change plate 15 b is inclined is preferably about 30 ° to 85 ° with respect to the flow direction of the upstream liquid phase pipe 4 and the refrigerant drawing pipe 13.
- the angle at which the direction change plate 15b is inclined does not have to be fixed, and may be a variable structure. At this time, the angle may be changed manually or the angle may be changed by automatic control.
- the liquid phase refrigerant descending from the upstream strikes the direction change plate 15b, and when the direction of the flow is changed, the direction change plate 15b is inclined in a direction to be guided to the storage unit 16, so that the flow is changed.
- FIG. 9 is a cross-sectional view of the refrigerant distributor
- FIG. 10 is a cross-sectional view seen from the point C shown in FIG.
- cooling device of the present embodiment is different only in the configuration of the refrigerant distribution device 10 described in the first embodiment, description of other parts is omitted.
- the difference between the present embodiment and the first embodiment is the structure of the deflection plate 15c.
- a deflecting plate 15c having substantially the same shape (substantially the same shape) as the cross-sectional shape of the refrigerant inlet tube 13 is directly provided on the upper end of the refrigerant inlet tube 13 to form an integral shape.
- the refrigerant inlet pipe port 18a provided at the upper end of the refrigerant inlet pipe 13 of the first embodiment is configured to be closed by the deflecting plate 15c.
- an opening 18b through which the overflowing liquid phase refrigerant flows is provided on the upper side surface of the refrigerant drawing pipe 13.
- the direction change plate 15c is manufactured so as to have an integrated shape so as to close the upper end of the refrigerant intake pipe as in the present embodiment, the direction change plate 15c and the refrigerant intake pipe 13 can be handled as one part, The assemblability of the refrigerant distributor 10 is dramatically improved.
- FIG. 11 is a cross-sectional view of the refrigerant distributor
- FIG. 12 is a cross-sectional view seen from the point D shown in FIG.
- cooling device of the present embodiment is different only in the configuration of the refrigerant distribution device 10 described in the first embodiment, description of other parts is omitted.
- the difference between this embodiment and the first embodiment is the structure of the deflecting plate 15d.
- the direction change plate 15d is provided with a small opening 19 at the center, and a refrigerant intake pipe is provided without changing the flow of a part of the liquid-phase refrigerant that descends from the upstream side by the direction change plate 15d.
- Lower to 13 If this opening 19 is large, most of the liquid-phase refrigerant descending from the upstream flows into the refrigerant drawing pipe 13, so that sufficient liquid-phase refrigerant cannot be stored in the storage unit 16, and sufficient refrigerant is not supplied to the connected heat receiver 1. Cannot supply. For this reason, it is desirable that the size of the diameter of the refrigerant drawing pipe 13 is about 5% to 50%.
- the liquid-phase refrigerant that has descended from the upstream liquid-phase pipe 4 is changed in the flow direction by contacting the direction change plate 15 d and flows into the storage unit 16.
- the cooling device of the present invention wants to absorb the exhaust heat of the electronic equipment below the rack immediately after the operation starts.
- FIG. 13 is a cross-sectional view of the refrigerant distributor
- FIG. 14 is a cross-sectional view seen from the point E shown in FIG.
- cooling device of the present embodiment is different only in the configuration of the refrigerant distribution device 10 described in the first embodiment, description of other parts is omitted.
- the difference between this embodiment and the first embodiment is the structure of the deflecting plate 15e.
- the deflecting plate 15 e has the same shape as the internal cross-sectional shape of the main body formed by the branch outer wall 14. That is, in this embodiment, since the main body has a circular cross-sectional shape due to the branch outer wall 14, the direction change plate 15e has the same shape, that is, a disk shape.
- the direction change plate 15e is arranged in such a state that the inner wall of the branch outer wall 14 and the peripheral part of the direction change plate 15e are all in contact.
- the direction change plate 15e is provided between the upstream liquid phase pipe port 17 and the refrigerant drawing pipe port 18a as in the first embodiment.
- the turning plate 15e has a structure in which a plurality of small openings 20 are provided at the periphery, and the flow of the liquid-phase refrigerant descending from the upstream is changed and lowered.
- the shape of the direction change plate 15e is a disc shape, but the shape of the direction change plate 15e is a shape such as a rectangle corresponding to the cross-sectional shape of the main body formed by the branch outer wall 14.
- FIG. 15 is a cross-sectional view of the refrigerant distributor.
- cooling device of this embodiment is different only in the configuration of the refrigerant distribution device 10 described in the fifth embodiment, the description of other parts is omitted.
- the difference between the present embodiment and the fifth embodiment is the installation position of the deflection plate 15e.
- the structure of the deflecting plate 15e alone is the same as that of the fifth embodiment.
- direction change plate 15e closes the upper end of the refrigerant suction pipe 13, and an opening 18b through which an overflowing liquid phase refrigerant flows is provided on the upper side surface of the refrigerant suction pipe 13.
- the direction change plate 15e can be easily fixed as in the fifth embodiment, and the assemblability of the refrigerant distributor 10 can be dramatically improved.
- the direction change plate has been described as an example of the refrigerant direction change unit, but the refrigerant direction change unit is not limited to a plate shape.
- the refrigerant redirecting means may have other shapes such as a semi-spherical shape, a roof shape, and a net shape around the periphery. Specifically, in the case of a hemispherical shape and a roof shape, a shape that protrudes upward is desirable.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Computer Hardware Design (AREA)
- Microelectronics & Electronic Packaging (AREA)
- Cooling Or The Like Of Electrical Apparatus (AREA)
- Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
Abstract
Description
(第1の実施形態)
本実施形態について詳細に説明する。図3に本実施形態の冷媒分配装置を含んだ冷却装置の全体図を示している。
(第2の実施形態)
第2の実施形態について図7及び図8を参照して説明する。図7は、本形態の冷媒分配装置10の断面図であり、図8は図7に示す点からの断面図である。
(第3の実施形態)
第3の実施形態について図9及び図10を参照して説明する。図9は冷媒分配装置の断面図で、図10は、図9の示すC点から見た断面図である。
(第4の実施形態)
第4の実施形態について図11及び図12を参照して説明する。図11は冷媒分配装置の断面図で、図12は、図11の示すD点から見た断面図である。
(第5の実施形態)
第5の実施形態について図13及び図14を参照して説明する。図13は冷媒分配装置の断面図で、図14は、図13の示すE点から見た断面図である。
(第6の実施形態)
第6の実施形態について図15を参照して説明する。図15は冷媒分配装置の断面図である。
2 放熱器
3 気相管
4 液相管
5 ラック
6 電子機器
10 冷媒分配装置
11 気相支流管
12 液相支流管
13 冷媒引き込み管
14 分岐外壁
15 変向板
16 貯蔵部
17 上流液相管口
18 冷媒引き込み管口
19、20 変向板の一部に設けた開口
Claims (10)
- 上流から供給される冷媒を分配する冷媒分配装置であって、
前記冷媒分配装置は側壁部、上面部および下面部を有する本体部と、
前記本体部の内部と連通するよう前記上面部に設けられる上流配管と、
前記下面部に設けられた下面孔部を介して前記本体部の内部に一部が挿入された状態で設けられる下流配管と、
前記本体内部と連通するよう前記側壁部または下面部に設けられる支流配管と、
前記上流配管と前記下流配管との間に設けられた冷媒変向手段とを有する冷媒分配装置。 - 前記冷媒変向手段は、前記上流配管から前記本体部の内部に降下する冷媒を、前記下流配管とは異なる領域に流入させるよう設けられる請求項1に記載の冷媒分配装置。
- 前記冷媒変向手段は、前記本体部の内部に降下する前記冷媒の流れを変向する変向板であることを特徴とする請求項1または請求項2記載の冷媒分配装置。
- 前記変向板が前記下流配管の上端に設けられ、前記下流配管の側面に冷媒流入口を設けたことを特徴とする請求項3記載の冷媒分配装置。
- 前記変向板の形状が前記下流配管の断面形状と実質的に同一の形状または前記下流配管の断面形状よりも大きく前記本体部の内部断面形状よりも小さい形状であることを特徴とする請求項3または請求項4記載の冷媒分配装置。
- 前記変向板の一部に開口部を設けたことを特徴とする請求項3記載の冷媒分配装置。
- 前記開口部を前記変向板の中央部に設けたことを特徴とする請求項6記載の冷媒分配装置。
- 前記変向板の形状が前記本体部の内部断面形状と実質的に同一の形状で、前記開口部を前記変向板の周辺部に複数設けたことを特徴とする請求項6記載の冷媒分配装置。
- 電子機器が収納された収納体の側面に設けられた複数の受熱器と、
前記収納体外に設置された放熱器と、
前記複数の受熱器と前記放熱器とを連通する第1の配管と、
前記放熱器と前記複数の受熱器とを連通する第2の配管と、
前記第2の配管の前記複数の受熱器への分岐部にそれぞれ設置される請求項1から8のいずれか1項に記載の冷媒分配装置と、を備える冷却装置。 - 前記複数の冷媒分配装置は、上下方向に直列に接続され、上方の前記冷媒分配装置から供給された前記冷媒を、前記冷媒分配装置と接続される前記受熱器と下方の前記冷媒分配装置とに冷媒を供給することを特徴とする請求項9記載の冷却装置。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
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EP14869837.6A EP3091321B1 (en) | 2013-12-13 | 2014-12-05 | Refrigerant distribution device and cooling device |
CN201480068292.0A CN105829822B (zh) | 2013-12-13 | 2014-12-05 | 制冷剂分配装置和冷却设备 |
JP2015552330A JPWO2015087530A1 (ja) | 2013-12-13 | 2014-12-05 | 冷媒分配装置および冷却装置 |
KR1020167015356A KR101917013B1 (ko) | 2013-12-13 | 2014-12-05 | 냉매 분배 장치 및 냉각 장치 |
US15/036,464 US10215456B2 (en) | 2013-12-13 | 2014-12-05 | Refrigerant distribution device and cooling apparatus |
SG11201604782PA SG11201604782PA (en) | 2013-12-13 | 2014-12-05 | Refrigerant distribution device and cooling apparatus |
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JP2013-257936 | 2013-12-13 | ||
JP2013257936 | 2013-12-13 |
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US (1) | US10215456B2 (ja) |
EP (1) | EP3091321B1 (ja) |
JP (1) | JPWO2015087530A1 (ja) |
KR (1) | KR101917013B1 (ja) |
CN (1) | CN105829822B (ja) |
SG (1) | SG11201604782PA (ja) |
WO (1) | WO2015087530A1 (ja) |
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JP2018013259A (ja) * | 2016-07-19 | 2018-01-25 | パナソニックIpマネジメント株式会社 | 冷媒分流器およびそれを用いた冷凍システム |
JP6304420B1 (ja) * | 2017-03-23 | 2018-04-04 | 日本電気株式会社 | 冷媒分配装置、冷却装置及び冷媒分配装置における冷媒分配方法 |
WO2018179198A1 (ja) * | 2017-03-30 | 2018-10-04 | 日本電気株式会社 | 熱交換器、熱交換システム、および熱交換方法 |
CN108759186A (zh) * | 2018-04-13 | 2018-11-06 | 宁波得晴电器科技有限公司 | 制冷剂分配装置 |
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Also Published As
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CN105829822A (zh) | 2016-08-03 |
KR101917013B1 (ko) | 2018-11-08 |
CN105829822B (zh) | 2020-04-03 |
JPWO2015087530A1 (ja) | 2017-03-16 |
EP3091321B1 (en) | 2019-07-17 |
EP3091321A1 (en) | 2016-11-09 |
KR20160084857A (ko) | 2016-07-14 |
US10215456B2 (en) | 2019-02-26 |
US20160282023A1 (en) | 2016-09-29 |
SG11201604782PA (en) | 2016-07-28 |
EP3091321A4 (en) | 2017-10-11 |
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