WO2017051531A1 - 相変化冷却装置およびその制御方法 - Google Patents
相変化冷却装置およびその制御方法 Download PDFInfo
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- WO2017051531A1 WO2017051531A1 PCT/JP2016/004296 JP2016004296W WO2017051531A1 WO 2017051531 A1 WO2017051531 A1 WO 2017051531A1 JP 2016004296 W JP2016004296 W JP 2016004296W WO 2017051531 A1 WO2017051531 A1 WO 2017051531A1
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- refrigerant liquid
- refrigerant
- phase change
- cooling device
- change cooling
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or 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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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- 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
- H01L23/42—Fillings or auxiliary members in containers or encapsulations selected or arranged to facilitate heating or cooling
- H01L23/427—Cooling by change of state, e.g. use of heat pipes
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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
- H05K7/2029—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant with phase change in electronic enclosures
Definitions
- the present invention relates to a phase change cooling device used for cooling an electronic device or the like and a control method thereof, and more particularly to a phase change cooling device for circulating a refrigerant liquid using a drive source and a control method thereof.
- the cooling module for electronic devices described in Patent Document 1 is a pump circulation type phase change cooling device, and is a jacket (evaporator) that is thermally connected to a heating element to absorb heat, a radiator, and a gas-liquid separation function. And a coolant driving unit constituted by an electric pump.
- a pipe through which the refrigerant flows in a liquid state is provided at the inlet of the jacket, and a pipe through which the gas-liquid mixed liquid flows is provided at the outlet of the jacket.
- a coolant driving unit is attached in front of the inlet pipe of the jacket, and a tank also serving as a gas-liquid separating function is connected in the vicinity of the outlet of the jacket. The refrigerant vapor separated in this tank flows into the vapor pipe, and is then condensed by the radiator and returns to the coolant driving unit via the pipe to form a refrigerant closed loop.
- the tank that also functions as a gas-liquid separation function is partitioned by a porous body into a region in which refrigerant liquid is held and a gas-liquid mixing region in which a gas-liquid mixed refrigerant sucked from the jacket exists.
- the region where the refrigerant liquid is held is connected between the radiator and the coolant driving means by a bypass pipe.
- the related cooling module phase change cooling device
- JP 2008-130746 A paragraphs [0021] to [0036], FIG. 1) International Publication No. 2015/0775916
- FIG. 4A shows a general configuration example of a pump circulation type phase change cooling device that circulates a refrigerant liquid using a drive source such as a pump like the related phase change cooling device described above.
- 4A includes an evaporator 510 such as a radiator, a condenser 520 such as a heat exchanger or an outdoor unit, a drive source 530 such as a pump, a steam pipe 540, and a liquid pipe 550.
- the refrigerant liquid LR is supplied to the evaporator 510 by using the pump P or the like, and the evaporator 510 receives heat by latent heat when the refrigerant liquid LR evaporates and generates the refrigerant vapor VR.
- the refrigerant vapor VR flowing out of the evaporator 510 is condensed by radiating heat in the condenser 520 and returned to the refrigerant liquid LR, and sent to the drive source 530 such as the pump P through the liquid pipe 550.
- the refrigerant liquid in the pump circulation type phase change cooling device, when the pump is stopped, the refrigerant liquid also accumulates in the evaporator and the steam pipe by the action of gravity. After that, when the system is restarted, the evaporation of the refrigerant liquid in the evaporator is suppressed by the pressure of the liquid column of the refrigerant liquid accumulated in the steam pipe, so that the evaporator receives heat by the sensible heat of the refrigerant liquid.
- the refrigerant that has flowed into the condenser in the liquid phase is cooled by the condenser and returned to the evaporator.
- the evaporator performs cooling by sensible heat of the refrigerant liquid instead of latent heat by evaporation.
- heat reception by sensible heat is less efficient than heat reception by latent heat. In such a case, the cooling capacity of the pump circulation type phase change cooling device is significantly reduced.
- FIG. 4A schematically shows the distribution state of the refrigerant liquid LR and the refrigerant vapor VR during the normal operation of the above-described pump circulation type related phase change cooling device 500.
- the refrigerant liquid LR supplied to the evaporator 510 by the pump P is evaporated by the evaporator 510 to become the refrigerant vapor VR.
- the refrigerant vapor VR is transported to the condenser 520 through the vapor pipe 540, and is cooled and condensed in the condenser 520 to become the refrigerant liquid LR.
- the refrigerant liquid LR is supplied to the pump P again through the liquid pipe 550.
- the phase change cooling device 500 takes heat away by the evaporation of the refrigerant liquid LR in the evaporator 510, so that the cooling efficiency is high.
- the vapor pipe 540 is filled with the refrigerant vapor VR
- the liquid pipe 550 is filled with the refrigerant liquid LR.
- FIG. 4B schematically shows the distribution of the refrigerant when the pump P is stopped.
- the stopped state refers to a state where the pump P stops and the circulation of the refrigerant stops.
- the refrigerant liquid LR accumulates downward due to the action of gravity.
- the gas-liquid interface INT of the refrigerant is between the vertical direction of the evaporator 510 and the condenser 520, and the vapor pipe 540 and the liquid pipe 550 are filled with both the refrigerant liquid LR and the refrigerant vapor VR, respectively. Is shown.
- FIGS. 5A and 5B show a case where the amount of refrigerant is small, and FIG. 5B shows a case where the amount of refrigerant is large.
- the refrigerant liquid LR on the suction side of the pump P does not exist, and therefore the circulation of the refrigerant stops.
- the evaporator 510 absorbs heat due to the sensible heat of the refrigerant liquid LR.
- the temperature of the refrigerant liquid LR rises.
- the refrigerant liquid LR in the evaporator 510 has the temperature of the heating element that is the endothermic object before reaching the boiling point. It may become equal. As a result, the heat absorption in the evaporator 510 is stopped.
- the refrigerant liquid LR circulates through the condenser 520 as shown in FIG. 5B.
- the temperature of the refrigerant liquid does not rise to the boiling point in the evaporator 510, and evaporation does not occur. Therefore, the cooling efficiency is significantly reduced because the heat is received only by the sensible heat of the refrigerant liquid LR.
- the phase change cooling device that circulates the refrigerant liquid using the drive source has a problem that the cooling capacity is remarkably reduced immediately after the startup.
- the object of the present invention is the phase change cooling device that solves the problem that the cooling capacity of the phase change cooling device that circulates the refrigerant liquid by using the drive source is significantly reduced immediately after the start-up. It is to provide a control method.
- the phase change cooling device of the present invention includes an evaporator that stores a refrigerant liquid that receives heat from a heat generation source, a condenser that radiates the heat of the refrigerant vapor generated when the refrigerant liquid is vaporized in the evaporator, and generates a refrigerant liquid.
- the refrigerant liquid driving means for circulating the refrigerant liquid, the first pipe section connecting the evaporator and the condenser, the second pipe section connecting the condenser and the refrigerant liquid driving means, the refrigerant liquid driving means and the evaporation
- the first connection point is located below the position of the interface between the refrigerant liquid and the refrigerant vapor in the first pipe section when the refrigerant liquid driving means is activated.
- the control method of the phase change cooling device of the present invention includes an evaporator that stores a refrigerant liquid that receives heat from a heat source, and generates a refrigerant liquid by dissipating the heat of the refrigerant vapor that is generated when the refrigerant liquid is vaporized by the evaporator.
- phase change cooling device and its control method of the present invention it is possible to avoid a decrease in cooling capacity immediately after startup even in a configuration in which a refrigerant liquid is circulated using a drive source.
- phase change cooling device It is the schematic which shows typically the structure of the phase change cooling device which concerns on the 3rd Embodiment of this invention. It is a figure which shows typically the structure of a related phase change cooling device, and distribution of the refrigerant
- a related phase change cooling device it is a figure showing typically distribution of a refrigerant when starting a pump from a halt condition, and shows a case where there is little quantity of a refrigerant.
- a related phase change cooling device it is a figure showing typically distribution of a refrigerant when starting a pump from a stop state, and shows a case where there is much quantity of a refrigerant.
- FIG. 1A is a schematic diagram schematically showing the configuration of the phase change cooling device 100 according to the first embodiment of the present invention.
- FIG. 1B is a schematic diagram schematically showing the circulation state of the refrigerant in the phase change cooling device 100 according to the present embodiment.
- the phase change cooling device 100 includes an evaporator 110, a condenser 120, and a refrigerant liquid driving unit (refrigerant liquid driving means) 130 as shown in FIG. 1A.
- Phase change cooling device 100 further includes a first piping unit 140, a second piping unit 150, a third piping unit 160, and a fourth piping unit 170.
- the evaporator 110 accommodates the refrigerant liquid LR that receives heat from the heat source.
- the evaporator 110 is typically composed of a radiator or the like.
- the condenser 120 radiates the heat of the refrigerant vapor VR generated when the refrigerant liquid LR is vaporized in the evaporator 110 to generate the refrigerant liquid LR.
- the condenser 120 is typically configured by a heat exchanger, an outdoor unit, or the like.
- the refrigerant liquid driving unit 130 circulates the refrigerant liquid LR.
- the refrigerant liquid drive unit 130 is typically configured by a pump P or the like.
- the first piping unit 140 connects the evaporator 110 and the condenser 120.
- the second piping unit 150 connects the condenser 120 and the refrigerant liquid driving unit 130.
- the third piping unit 160 connects the refrigerant liquid driving unit 130 and the evaporator 110.
- the fourth piping unit 170 has one end connected to the first piping unit 140 at the first connection point 171 and the other end connected to the second piping unit 150 at the second connection point 172.
- the first connection point 171 is located below the interface position (INT1) between the refrigerant liquid LR and the refrigerant vapor VR in the first piping section 140 when the refrigerant liquid drive unit 130 is started. Yes.
- the 1st piping part 140, the 2nd piping part 150, the 3rd piping part 160, and the 4th piping part 170 are typically comprised by metal piping etc.
- 1B indicates the refrigerant liquid LR that circulates in the phase change cooling device 100 when the refrigerant liquid driving unit 130 is activated.
- the refrigerant liquid driving unit 130 is activated, the refrigerant liquid driving unit 130 is in an operating state, and the refrigerant liquid LR stored in the evaporator 110 is not receiving heat from the heat generation source.
- the phase change cooling device 100 is connected to the first piping unit 140 and the second piping unit 150 at the first connection point 171 and the second connection point 172, respectively.
- 4 piping parts 170 are provided.
- the first connection point 171 is configured to be positioned below the interface (INT1) between the refrigerant liquid LR and the refrigerant vapor VR in the first piping section 140 when the refrigerant liquid driving unit 130 is activated.
- the refrigerant liquid LR in the first pipe part 140 passes through the fourth pipe part 170 even when the amount of the refrigerant is small as shown in FIG. 5A. It is supplied to the drive unit 130. Therefore, since the circulation of the refrigerant liquid LR can be continued, it is possible to shift to a normal operation state.
- the refrigerant liquid LR can be circulated through the fourth piping section 170. Therefore, it is possible to avoid a state in which the refrigerant liquid LR circulates through the condenser 120, thereby cooling the refrigerant liquid LR and preventing the refrigerant liquid LR from evaporating in the evaporator 110. As a result, it is possible to shift to a normal operation state.
- the refrigerant liquid LR is supplied to the evaporator 110 by the refrigerant liquid driving unit 130, and the temperature of the refrigerant liquid LR rises to the boiling point by receiving heat from the heat generation source in the evaporator 110. Reach. At this time, heat is received from the heat generation source by latent heat when the refrigerant liquid LR evaporates to become the refrigerant vapor VR, so that efficient heat reception is possible.
- the refrigerant vapor VR generated in the evaporator 110 flows into the condenser 120 through the first piping part 140 and is condensed by being dissipated in the condenser 120 to become the refrigerant liquid LR.
- the refrigerant liquid LR condensed in the condenser 120 flows into the refrigerant liquid driving section 130 through the second piping section 150. That is, the refrigerant liquid LR flows through the second piping part 150 between the condenser 120 and the second connection point 172. Therefore, the amount of the refrigerant liquid LR in the first piping section 140 is reduced and the pressure due to the liquid column is lowered, so that the evaporation of the refrigerant liquid LR in the evaporator 110 is promoted. As a result, the phase change cooling device 100 can be easily shifted to a normal operation state.
- the condensed refrigerant liquid LR is supplied again to the evaporator 110 via the third pipe section 160 by the refrigerant liquid driving section 130. As a result, the phase change cooling cycle using the refrigerant is completed, and phase change cooling with a high cooling capacity is realized.
- the refrigerant liquid driving unit 130 is started from the stopped state regardless of the amount of the refrigerant, and the phase change cooling device is shifted to the normal operation state. It becomes possible. Therefore, even if it is the structure which circulates a refrigerant
- the refrigerant liquid LR present in the first piping part 140 during normal operation is returned to the second piping part 150 by the fourth piping part 170. be able to.
- the pressure loss of the first piping part 140 can be reduced, it is also possible to suppress a decrease in cooling capacity during normal operation.
- the second connection point 172 of the fourth piping unit 170 is activated at the interface between the refrigerant liquid LR and the refrigerant vapor VR held by the second piping unit 150.
- the position is lower than the position (INT2) at the time.
- the position (INT1, INT2) of the interface between the refrigerant liquid LR and the refrigerant vapor VR when the refrigerant liquid driving unit 130 is started can be configured to be lower than the condenser 120.
- the refrigerant liquid LR is cooled when passing through the condenser 120, the refrigerant liquid LR is prevented from rising to the boiling point in the evaporator 110.
- the gas-liquid interface INT between the refrigerant liquid LR and the refrigerant vapor VR only needs to be positioned above the refrigerant liquid driving unit 130 as shown in FIG. 1C.
- first connection point 171 of the fourth piping unit 170 may be positioned above the second connection point 172.
- the refrigerant liquid LR that has flowed into the fourth piping unit 170 from the first connection point 171 can flow to the second connection point 172 by the action of gravity. Therefore, the work amount of the refrigerant liquid driving unit 130 can be reduced.
- the condenser 120 can be configured to be positioned above the evaporator 110 and the refrigerant liquid driving unit 130. Thereby, since the natural circulation of the refrigerant
- the first connection point 171 where the fourth piping unit 170 is connected to the first piping unit 140 is a position close to the evaporator 110. This is because the pressure acting on the refrigerant liquid LR in the evaporator 110 by the liquid column of the refrigerant liquid LR accumulated in the first piping part 140 is proportional to the height from the upper end of the evaporator 110 at the first connection point 171. Because it does.
- the first connection point 171 close to the evaporator 110 the height of the first connection point 171 can be reduced, thereby suppressing the pressure increase due to the liquid column of the refrigerant liquid LR. Can do.
- phase change cooling device The configuration of the phase change cooling device is the same as that of the phase change cooling device 100 described above.
- position (INT1) of the interface between the refrigerant liquid LR and the refrigerant vapor VR held by the first pipe section 140 when the refrigerant liquid driving means 130 is activated is the first connection point 171. It controls so that it may be located above.
- phase change cooling device 100 By controlling the phase change cooling device 100 in this way, as described above, even if the refrigerant liquid is circulated using a driving source such as the refrigerant liquid driving means 130, the cooling capacity immediately after startup is improved. A decrease can be avoided.
- FIG. 2 the structure of the phase change cooling device 200 which concerns on the 2nd Embodiment of this invention is shown typically.
- the arrows in the figure indicate the refrigerant liquid LR that circulates in the phase change cooling device 200 when the refrigerant liquid driving unit 130 is activated.
- the phase change cooling device 200 includes an evaporator 110, a condenser 120, and a refrigerant liquid driving unit 130.
- Phase change cooling device 200 further includes a first piping unit 140, a second piping unit 150, a third piping unit 160, and a fourth piping unit 170.
- the configuration so far is the same as the configuration of the phase change cooling device 100 according to the first embodiment.
- the phase change cooling device 200 further includes a refrigerant storage unit (refrigerant storage unit) 210 that stores the refrigerant liquid LR in the flow path constituted by the second piping unit 150.
- the refrigerant storage unit 210 is typically configured by a metal container such as a tank.
- the refrigerant storage unit 210 can be configured to be positioned above the refrigerant liquid driving unit 130.
- the refrigerant reservoir 210 is arranged such that the interface between the refrigerant liquid LR and the refrigerant vapor VR when the refrigerant liquid drive unit 130 is stopped is located below the upper end of the refrigerant reservoir 210. be able to. That is, when the refrigerant liquid driving unit 130 is in a stopped state, the refrigerant storage unit 210 can be installed at a position where it is not filled with only the refrigerant liquid LR.
- the refrigerant reservoir 210 can be configured to be located below the first connection point 171. Thereby, it is possible to prevent the refrigerant liquid LR from flowing backward from the refrigerant storage unit 210 to the first piping unit 140.
- effects of the phase change cooling device 200 of the present embodiment will be described.
- phase change cooling device 200 of the present embodiment is configured to include the refrigerant reservoir 210, the amount of refrigerant liquid received is excessive because the amount of refrigerant liquid is excessive even when shifting to a normal operation state. Can be avoided. Moreover, the effect that the liquid column pressure for supplying a refrigerant
- phase change cooling device there is an appropriate amount of refrigerant that maximizes the amount of heat received in the evaporator in a normal operation state. This will be described below.
- the pressure of the refrigerant liquid increases.
- excess refrigerant liquid that does not evaporate and does not contribute to heat reception by latent heat accumulates in the vapor pipe, and the pressure of the refrigerant liquid increases by pressing the refrigerant liquid in the evaporator.
- the excess refrigerant liquid accumulates in the condenser, the heat exchange performance in the condenser may decrease, and the pressure in the steam pipe may increase.
- the evaporator cannot receive sufficient heat, so that the cooling performance is lowered. Therefore, in the phase change cooling device, there is an appropriate amount of refrigerant that maximizes the amount of heat received in the evaporator in a normal operation state.
- the amount of the refrigerant liquid necessary for shifting from the state where the refrigerant liquid driving unit is stopped to the normal operation state does not necessarily coincide with the amount of the refrigerant liquid for maximizing the amount of heat received in the normal operation state. That is, generally, the amount L1 of the refrigerant liquid necessary for shifting from the stopped state to the normal state is larger than the amount L2 of the refrigerant liquid for maximizing the amount of heat received in the normal operation state (L1> L2 ).
- the phase change cooling device 200 of the present embodiment is configured to include the refrigerant storage unit 210, excess refrigerant liquid can be stored in the refrigerant storage unit 210 in a normal operation state. it can. Specifically, for example, when L1> L2 described above, an amount of refrigerant liquid equal to or greater than L1 is introduced into the phase change cooling device 200. Thereby, the transition from the stop state of the refrigerant liquid drive unit to the normal operation state becomes possible. In addition, after the transition to the normal operation state, the surplus refrigerant liquid is stored in the refrigerant storage unit 210, so that excessive refrigerant liquid does not accumulate in the condenser 120 or the first piping unit 140. Therefore, it is possible to avoid an increase in the pressure of the refrigerant liquid in the evaporator 110, and it is possible to maximize the amount of heat received.
- phase change cooling device 200 of the present embodiment it is possible to avoid a decrease in the cooling capacity immediately after the start-up even if the refrigerant liquid is circulated using the drive source, and normal. It becomes possible to maximize the amount of heat received in the operating state.
- the refrigerant liquid exceeding the quantity of the refrigerant liquid that maximizes the amount of heat received during normal operation can be absorbed by the refrigerant reservoir 210, the tolerance of the quantity of the refrigerant liquid that is put into the phase change cooling device 200 is improved. Can be made.
- FIG. 3 the structure of the phase change cooling device 300 which concerns on the 3rd Embodiment of this invention is shown typically.
- the arrows in the figure indicate the refrigerant liquid LR that circulates in the phase change cooling device 300 when the refrigerant liquid driving unit 330 is activated.
- the phase change cooling device 300 includes a plurality of evaporators 310, a condenser 320, and a refrigerant liquid driving unit 330.
- Phase change cooling device 300 further includes a first piping unit 340, a second piping unit 350, a third piping unit 360, and a fourth piping unit 370.
- the first piping unit 340 connects the plurality of evaporators 310 and the condenser 320.
- the second piping unit 350 connects the condenser 320 and the refrigerant liquid driving unit 330.
- the third piping unit 360 connects the refrigerant liquid driving unit 330 and the plurality of evaporators 310.
- the fourth piping unit 370 has one end connected to the first piping unit 340 at the first connection point 371 and the other end connected to the second piping unit 350 at the second connection point 372.
- the first connection point 371 is located below the position of the interface between the refrigerant liquid LR and the refrigerant vapor VR held by the first piping part 340 when the refrigerant liquid driving unit 330 is activated.
- the first piping section 340 includes a common transport section (common transport means) 342 to which the plurality of evaporators 310 are commonly connected in a part between the plurality of evaporators 310 and the first connection point 371.
- the common transport section 342 is configured to be inclined in a state where the side close to the first connection point 371 is positioned below the side close to the evaporator 310. That is, the angle ⁇ formed by the axis passing through the common transport part 342 and the axis on the horizontal plane is greater than zero degrees.
- the first piping unit 340 is configured by a pipe having a large inner diameter in order to suppress the pressure loss of the refrigerant vapor VR flowing through the first piping unit 340.
- the refrigerant liquid driving unit 330 when the refrigerant liquid driving unit 330 is activated, the refrigerant liquid LR needs to reach the first connection point 371 in order to circulate the refrigerant liquid LR via the fourth piping unit 370. In this case, if a pipe with a large inner diameter is used as the first pipe portion 340, the amount of refrigerant liquid required increases.
- the common transport part 342 that constitutes a part of the first piping part 340 is inclined toward the first connection point 371 below. Therefore, the refrigerant liquid LR can flow in the common transport part 342 to the first connection point 371. As a result, it is possible to reduce the amount of refrigerant liquid necessary for shifting to the normal operation state.
- Phase change cooling device 110 310, 510 Evaporator 120, 320, 520 Condenser 130, 330 Refrigerant liquid drive unit 140, 340 First piping unit 150, 350 Second piping unit 160, 360 First 3 piping section 170, 370 4th piping section 171, 371 1st connection point 172, 372 2nd connection point 210 refrigerant storage section 342 common transport section 500 related phase change cooling device 530 drive source 540 steam pipe 550 Liquid pipe LR Refrigerant liquid VR Refrigerant vapor INT Gas-liquid interface INT1, INT2 interface
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Abstract
Description
図1Aは、本発明の第1の実施形態に係る相変化冷却装置100の構成を模式的に示す概略図である。また、図1Bは、本実施形態に係る相変化冷却装置100における冷媒の循環状態を模式的に示す概略図である。
次に、本発明の第2の実施形態について説明する。図2に、本発明の第2の実施形態に係る相変化冷却装置200の構成を模式的に示す。同図中の矢印は、冷媒液駆動部130の起動時において、相変化冷却装置200内を循環する冷媒液LRを示す。
次に、本実施形態の相変化冷却装置200による効果について説明する。
相変化冷却装置が正常運転している状態において、蒸発器における受熱量を増大させるためには、蒸発器における冷媒の圧力を低減する必要がある。これは、蒸発器における冷媒の圧力が増大すると冷媒の沸点TVが上昇するからである。すなわち、一般に、ある温度Theatの熱源からの熱を蒸発器において受熱する場合、熱源からの熱の温度と冷媒液の沸点との差Theat-TVが大きいほど、冷媒液の沸騰が促進されるので、蒸発器における受熱量は大きくなる。したがって、蒸発器における冷媒の圧力が増大し冷媒の沸点TVが上昇すると、Theat-TVが減少し受熱量が減少することになる。
逆に、冷媒液の量が過少である場合にも、蒸発器において充分に受熱することができないので、冷却性能は低下する。
したがって、相変化冷却装置においては、正常運転状態で蒸発器における受熱量が最大となる適正な冷媒量が存在することになる。
次に、本発明の第3の実施形態について説明する。図3に、本発明の第3の実施形態に係る相変化冷却装置300の構成を模式的に示す。同図中の矢印は、冷媒液駆動部330の起動時において、相変化冷却装置300内を循環する冷媒液LRを示す。
110、310、510 蒸発器
120、320、520 凝縮器
130、330 冷媒液駆動部
140、340 第1の配管部
150、350 第2の配管部
160、360 第3の配管部
170、370 第4の配管部
171、371 第1の接続点
172、372 第2の接続点
210 冷媒貯留部
342 共通輸送部
500 関連する相変化冷却装置
530 駆動源
540 蒸気管
550 液管
LR 冷媒液
VR 冷媒蒸気
INT 気液界面
INT1、INT2 界面
Claims (11)
- 発熱源から受熱する冷媒液を収容する蒸発手段と、
前記冷媒液が前記蒸発手段で気化することにより発生した冷媒蒸気の熱を放熱し冷媒液を生成する凝縮手段と、
前記冷媒液を循環させる冷媒液駆動手段と、
前記蒸発手段と前記凝縮手段を接続する第1の配管部と、
前記凝縮手段と前記冷媒液駆動手段を接続する第2の配管部と、
前記冷媒液駆動手段と前記蒸発手段を接続する第3の配管部と、
一端が第1の接続点において前記第1の配管部と接続し、他端が第2の接続点において前記第2の配管部と接続する第4の配管部、とを有し、
前記第1の接続点が、前記冷媒液駆動手段の起動時における、前記第1の配管部内の前記冷媒液と前記冷媒蒸気の界面の位置よりも下方に位置している
相変化冷却装置。 - 請求項1に記載した相変化冷却装置において、
前記第2の接続点が、前記第2の配管部によって保持されている前記冷媒液と前記冷媒蒸気の界面の、前記冷媒液駆動手段の起動時における位置よりも下方に位置している
相変化冷却装置。 - 請求項1または2に記載した相変化冷却装置において、
前記冷媒液と前記冷媒蒸気の界面の前記冷媒液駆動手段の起動時における位置が、前記凝縮手段よりも下方にある
相変化冷却装置。 - 請求項1から3のいずれか一項に記載した相変化冷却装置において、
前記第1の接続点は前記第2の接続点よりも上方に位置している
相変化冷却装置。 - 請求項1から4のいずれか一項に記載した相変化冷却装置において、
前記凝縮手段は前記蒸発手段および前記冷媒液駆動手段よりも上方に位置している
相変化冷却装置。 - 請求項1から5のいずれか一項に記載した相変化冷却装置において、
前記第2の配管部によって構成される流路内に、前記冷媒液をためる冷媒貯留手段をさらに有する
相変化冷却装置。 - 請求項5に記載した相変化冷却装置において、
前記冷媒貯留手段は、前記冷媒液駆動手段の停止時における前記冷媒液と前記冷媒蒸気の界面が、前記冷媒貯留手段の上端よりも下方に位置するように配置している
相変化冷却装置。 - 請求項5または6に記載した相変化冷却装置において、
前記冷媒貯留手段は、前記冷媒液駆動手段よりも上方に位置している
相変化冷却装置。 - 請求項5から7のいずれか一項に記載した相変化冷却装置において、
前記冷媒貯留手段は、前記第1の接続点よりも下方に位置している
相変化冷却装置。 - 請求項1から8のいずれか一項に記載した相変化冷却装置において、
複数の前記蒸発手段を備え、
前記第1の配管部は、前記蒸発手段と前記第1の接続点の間の一部に、前記複数の蒸発手段が共通に接続する共通輸送手段を備え、
前記共通輸送手段は、前記第1の接続点に近接する側が前記蒸発手段に近接する側よりも下方に位置する状態で傾斜している
相変化冷却装置。 - 発熱源から受熱する冷媒液を収容する蒸発手段と、
前記冷媒液が前記蒸発手段で気化することにより発生した冷媒蒸気の熱を放熱し冷媒液を生成する凝縮手段と、
前記冷媒液を循環させる冷媒液駆動手段と、
前記蒸発手段と前記凝縮手段を接続する第1の配管部と、
前記凝縮手段と前記冷媒液駆動手段を接続する第2の配管部と、
前記冷媒液駆動手段と前記蒸発手段を接続する第3の配管部と、
一端が第1の接続点において前記第1の配管部と接続し、他端が第2の接続点において前記第2の配管部と接続する第4の配管部、とを有する相変化冷却装置を、
前記第1の配管部によって保持されている前記冷媒液と前記冷媒蒸気の界面の、前記冷媒液駆動手段の起動時における位置が、前記第1の接続点よりも上方に位置するように制御する
相変化冷却装置の制御方法。
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US15/761,150 US20180266744A1 (en) | 2015-09-25 | 2016-09-21 | Phase-change cooling system and method for controlling the same |
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Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH04340077A (ja) * | 1991-05-15 | 1992-11-26 | Nec Corp | 液体冷媒循環システム |
JP2007513506A (ja) * | 2003-12-08 | 2007-05-24 | ノイズ リミット エーピーエス | バブルポンプを有する冷却システム |
JP2014052117A (ja) * | 2012-09-06 | 2014-03-20 | Panasonic Corp | 冷却装置およびこれを搭載した電気自動車および電子機器 |
JP2016164478A (ja) * | 2015-03-06 | 2016-09-08 | 株式会社東芝 | 冷却装置 |
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JP3272149B2 (ja) * | 1994-05-31 | 2002-04-08 | 三洋電機株式会社 | 冷媒加熱型暖房機 |
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2016
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- 2016-09-21 WO PCT/JP2016/004296 patent/WO2017051531A1/ja active Application Filing
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Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04340077A (ja) * | 1991-05-15 | 1992-11-26 | Nec Corp | 液体冷媒循環システム |
JP2007513506A (ja) * | 2003-12-08 | 2007-05-24 | ノイズ リミット エーピーエス | バブルポンプを有する冷却システム |
JP2014052117A (ja) * | 2012-09-06 | 2014-03-20 | Panasonic Corp | 冷却装置およびこれを搭載した電気自動車および電子機器 |
JP2016164478A (ja) * | 2015-03-06 | 2016-09-08 | 株式会社東芝 | 冷却装置 |
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US20200292221A1 (en) | 2020-09-17 |
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