US20200309467A1 - Two phase oil cooling system - Google Patents
Two phase oil cooling system Download PDFInfo
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- US20200309467A1 US20200309467A1 US16/367,551 US201916367551A US2020309467A1 US 20200309467 A1 US20200309467 A1 US 20200309467A1 US 201916367551 A US201916367551 A US 201916367551A US 2020309467 A1 US2020309467 A1 US 2020309467A1
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- refrigerant
- evaporator
- condenser
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- oil
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D31/00—Other cooling or freezing apparatus
- F25D31/002—Liquid coolers, e.g. beverage cooler
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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
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/04—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the fluid being in different phases, e.g. foamed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D29/00—Arrangement or mounting of control or safety devices
- F25D29/001—Arrangement or mounting of control or safety devices for cryogenic fluid systems
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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
- F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
-
- 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
- F28D2015/0291—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 comprising internal rotor means, e.g. turbine driven by the working fluid
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0089—Oil coolers
Definitions
- the present disclosure relates generally to a cooling system applied to a work vehicle.
- the off-highway industry uses a variety of rotating components: transmissions, axles, e-machines, hydraulic pumps and motors, etc. These components may use oil as a working fluid and/or for lubrication and cooling.
- a rotating component of a work vehicle such as axle or transmission, generates heat while in operation.
- the heat is partially removed by a cooling system/circuit, including a radiator coupled to the work vehicle, a cooling fan, and an oil path.
- a hot cooling oil from the rotating component flows into the radiator and is cooled by the radiator due to the cooling fan providing an air flow passing through a series of heat dissipation components of the radiator.
- the cooled cooling oil later flow back to the rotating component.
- this cooling circuit is prone to leaks, contamination, pumping losses and has a low heat transfer coefficient.
- the present disclosure includes a two phase oil cooling system that leverages the advantages of two-phase refrigerant applied on oil cooling which has significantly higher heat transfer coefficient.
- the present disclosure has the advantage of distributed heat loads from several components and does not require that oil be pumped to a remote cooling system.
- a two phase oil cooling system for a work vehicle.
- the two phase oil cooling system includes a condenser, an evaporator, a refrigerant path, and a pump.
- the condenser cools a refrigerant from vapor form to liquid form.
- the evaporator exchanges heat between a first fluid of the work vehicle and the refrigerant, thereby heating the refrigerant from liquid form to vapor form.
- the refrigerant path comprises a first refrigerant path thermally coupling the condenser to the evaporator and a second refrigerant path thermally coupling the evaporator to the condenser.
- the refrigerant flows through the refrigerant path.
- the pump is positioned in the first refrigerant path for pumping the refrigerant from the condenser to the evaporator, such that the evaporator is downstream of the pump and the condenser is downstream of the evaporator.
- a two phase oil cooling system for a work vehicle.
- the two phase oil cooling system includes a condenser, an evaporator, and a refrigerant path.
- the condenser cools a refrigerant from vapor form to liquid form.
- the evaporator is positioned below the condenser and exchanges heat between an oil of a rotating component of the work vehicle and the refrigerant, thereby heating the refrigerant from liquid form to vapor form.
- the refrigerant path thermally couples the condenser to the evaporator.
- the refrigerant flows in bi-directions in the refrigerant path, driven by difference of densities of the refrigerant responsive to temperatures of the refrigerant within the refrigerant path, within the condenser, and within the evaporator.
- the present disclosure also provides a method for cooling a rotating component.
- the method includes: pumping a refrigerant at least partial in liquid form to an evaporator and moving the refrigerant at least partial in vapor form to a condenser via the pumping such that a pressure of the refrigerant flowing into the evaporator is higher than another pressure of the refrigerant flowing into the condenser; absorbing a heat from an oil in the rotating component by the evaporator to evaporate the refrigerant from liquid form to vapor form; and cooling the refrigerant at least partial in vapor form via the condenser.
- FIG. 1 is a block diagram for a conventional cooling system applied on an air conditioner
- FIG. 2 is a simplified block diagram for a two phase oil cooling system applied on a work vehicle
- FIG. 3 is a block diagram of the first embodiment of FIG. 2 having multiple evaporators
- FIG. 4 is a block diagram of the second embodiment of FIG. 2 having a pump-condenser fan control logic
- FIG. 5 is a block diagram of the third embodiment of FIG. 2 having a separator separating a refrigerant in vapor form from the refrigerant in liquid form;
- FIG. 6 is a block diagram of the fourth embodiment of FIG. 2 having a separator separating a refrigerant in vapor form from the refrigerant in liquid form, and the refrigerant in vapor form is processed in a compressor;
- FIG. 7 is a block diagram of the fifth embodiment of FIG. 2 , showing an evaporator is positioned within a rotating component;
- FIG. 8A is a block diagram of the sixth embodiment of FIG. 2 , showing an evaporator is positioned outside a rotating component;
- FIG. 8B is a perspective view of the evaporator in FIG. 8A ;
- FIG. 9A is a block diagram of an embodiment of the two phase oil cooling system that utilizes antifreeze flowing through the evaporator and the heat exchangers positioned within the rotating components;
- FIG. 9B is a block diagram of an embodiment of the two phase oil cooling system that utilizes antifreeze flowing through the evaporator and the heat exchangers positioned outside rotating components;
- FIG. 10 is a block diagram of an embodiment of the two phase oil cooling system, where the rotating components are in partial parallel connection;
- FIG. 11 is a block diagram of the seventh embodiment of FIG. 2 , demonstrating the fan driven by the refrigerant.
- FIG. 12 is a block diagram of an embodiment of the two phase oil cooling system that utilizes buoyancy to drive the refrigerant flow.
- a conventional cooling system applied on an air conditioner includes an evaporator 14 ′, a compressor 24 ′, a condenser 12 ′, and a thermal expansion valve (TXV), where refrigerant flows through in liquid and/or in vapor form at different pressure.
- the air conditioner normally is fixed on a wall of a house and some elements of the air condition are indoor and some are outdoor.
- the compressor 24 ′ and the condenser 12 ′ of the air conditioner are positioned in the outdoor environment; the thermal expansion valve (TXV) and the evaporator 14 ′ are positioned indoor environment.
- the evaporator 14 ′ is located in the low pressure side (compressor suction side) and the condenser 12 ′ is used in the high pressure side.
- the thermal expansion valve (TXV) is used between the condenser 12 ′ and the evaporator 14 ′ to reduce pressure.
- the refrigerant In a path (suction line) between the evaporator 14 ′ and the compressor 24 ′, the refrigerant is at a low pressure and low temperature. In order to run the compressor 24 ′ properly, the refrigerant is in vapor form (gas or superheat gas). When the refrigerant reaches the compressor 24 ′, the compressor 24 ′ compresses the refrigerant in vapor form, such that the refrigerant in a path between the compressor 24 ′ and the condenser 12 ′ is at a high pressure (P H ) and high temperature (may be superheat).
- P H high pressure
- high temperature may be superheat
- the condenser 12 ′ cools the temperature of the refrigerant and change it into liquid form via a fan (not shown).
- the fan provides a first air flow AF 1′ passing through a heat dissipation element of the condenser 12 ′ to remove the heat from the condenser 12 ′.
- Refrigerant at the exit of the condenser 12 ′ must be saturated or subcooled liquid for smooth operation of thermal expansion valve (TXV). In a path between the condenser 12 ′ and the thermal expansion valve (TXV), the refrigerant is still at the high pressure.
- TXV thermal expansion valve
- the thermal expansion valve (TXV) later collects the refrigerant from the condenser 12 ′.
- the pressure of the refrigerant drastically decreases.
- the temperature of the refrigerant may also drop. Therefore, in a path between the thermal expansion valve (TXV) and the evaporator 14 ′, the refrigerant is at a low pressure (P L ).
- the low pressure refrigerant flows into the evaporator 14 ′.
- Another fan (not shown) adjacent to the evaporator 14 ′ provides a second air flow AF 2′ (indoor) passing through a heat exchange element of the evaporator 14 ′.
- the heat of the second air flow AF 2′ is absorbed by the refrigerant, because refrigerant in liquid form changing into vapor form requires latent heat (energy potential). Again, the refrigerant is discharged by the evaporator 14 ′ and flows into the compressor 24 ′.
- FIG. 2 illustrates a simplified block diagram of a two phase oil cooling system 10 for a work vehicle.
- the two phase oil cooling system 10 is applied on at least one rotating component of the work vehicle, including transmissions, axles, e-machines, hydraulic pumps and motors.
- the two phase oil cooling system 10 comprises a condenser 12 , an evaporator 14 , and a pump 20 .
- the condenser 12 is used to cool a refrigerant from vapor form to liquid form.
- the evaporator 14 is used to exchange heat between an oil of a rotating component of the work vehicle and the refrigerant.
- the two phase oil cooling system 10 also includes a refrigerant path 16 which has a first and second refrigerant paths 162 , 164 .
- the first refrigerant path 162 thermally couples the condenser 12 to the evaporator 14
- the second refrigerant path 164 thermally couples the evaporator 14 to the condenser 12
- the refrigerant flows through the refrigerant path 16 .
- the pump 20 is positioned in the first refrigerant path 162 for pumping the refrigerant from the condenser 12 to the evaporator 14 , such that the evaporator 14 is downstream of the pump 20 and the condenser 12 is downstream of the evaporator 14 .
- the pressure of the refrigerant in between the pump 20 and the evaporator 14 of the first refrigerant path 162 is high pressure P H ; the pressure of the refrigerant in the second refrigerant path 164 is low pressure P L .
- the evaporator 14 is located in the high pressure side and the condenser 12 is located in the low pressure side.
- the reservoir, if any, is omitted in FIG. 2 .
- a first air flow AF 1 is driven by a condenser fan 80 to cool the condenser 12 , such that the refrigerant in vapor form flowing from the second refrigerant path 164 can be transformed into liquid form.
- the pump 20 pumps the refrigerant into the evaporator 14 .
- a first oil flow OF 1 flowing from or in the rotating component transfers the heat to the refrigerant within the evaporator 14 . With the vaporization of the refrigerant, the first oil flow OF 1 is therefore cooled.
- the heated refrigerant later exits from the evaporator 14 and enters to the condenser 12 to be liquidized.
- the pump 20 can be a two-phase flow pump, a positive displacement liquid pump, or can be combined with a compressor.
- the number of the evaporator 14 can be one or more than one.
- the multiple evaporators 14 can be applied on one or more rotating component.
- the position of the evaporator 14 can be inside or outside of the rotating component for exchanging the heat between the refrigerant and the oil.
- the pump 20 is a two-phase flow pump, which has capability to pump the refrigerant in both vapor and liquid forms. Because pump 20 in this embodiment is compatible to the two forms of the refrigerant, it can avoid the cavitation that occurs when some the refrigerant in vapor form in a liquid pump. Therefore, even when the condenser 12 in this embodiment cannot completely transform the refrigerant in vapor form to liquid form, the pump 20 can still work smoothly to pump the refrigerant into the evaporators 14 . There are multiple evaporators 14 , each of which is applied on a respective one of rotating component (not shown in FIG. 3 ).
- the first refrigerant path 162 divides a plurality of sub-first refrigerant paths 1622 and the second refrigerant path 164 divides a plurality of sub-second refrigerant paths 1642 .
- Each of the evaporators 14 is coupled to one of the sub-first refrigerant paths 1622 and to one of the sub-second refrigerant paths 1642 .
- Each of the sub-first refrigerant path 1622 is positioned a flow control valve 40 to control the flow in the respective one of the evaporators 14 .
- the four evaporators 14 may have different flows of the refrigerant and therefore the efficiency of the heat exchange in the evaporators 14 are different.
- Utilizing the flow control valves 40 can distribute appropriate amount of refrigerant in the evaporators 14 .
- the control of the flow control valves 40 relates to the extent of necessity for the rotating components where the evaporators 14 are coupled. For one example, if one of the rotating components is a front axle and another one of rotating components is a rear axle, and if there is a mode change in the work vehicle, from four-wheel drive to front wheel drive, the flow control valve 40 applied on the front axle will increase the flow of the refrigerant, and the flow control valve 40 applied on the rear axle will decrease the flow of the refrigerant.
- the flow control valves 40 is operated via the command of a controller (not shown) which adjust the multiple flow control valves 40 based on the loading of the rotating components.
- the flow control valve 40 allows larger flow of the refrigerant than another flow control valve 40 of another rotating component does. It can be performed when the flow control valves 40 are temperature control valves, or the flow control valves 40 coupled to thermometers and/or flow pressor sensor, in corporation with a controller (not shown) controlling the flow based on preset multiple criteria, including temperature, flow pressure, durability of the rotating components, etc. Alternatively, the multiple evaporators 14 can be applied on a single rotating component to cool different portions of the rotating component.
- FIG. 4 it is the second embodiment of FIG. 2 .
- the feature in this embodiment is similar to FIG. 3 except the pump 20 is a positive displacement liquid pump, and the two phase oil cooling system 10 also includes a controller 70 which has a pump-condenser fan control logic 72 .
- the pump-condenser fan control logic 72 is connected to the pump 20 and condenser fan 80 .
- the pump-condenser fan control logic 72 regulates the condenser 12 to cool the refrigerant before the pump 20 pumping the refrigerant.
- the condenser 12 makes the refrigerant subcooled or saturated before the refrigerant reaches the pump 20 .
- the pump 20 in this embodiment is a positive displacement liquid pump.
- the two phase oil cooling system 10 also includes a separator 22 , a reverse refrigerant path 166 , and a reverse flow control valve 42 positioned in the reverse refrigerant path 166 .
- the separator 22 is positioned in the first refrigerant path 162 between the condenser 12 and the pump 20 , and is configured to separate the refrigerant in vapor form from the refrigerant in liquid form and to permit the refrigerant in liquid form to flow through the pump 20 .
- the reverse flow control valve 42 controls the flow of the refrigerant in vapor form in the reverse refrigerant path 166 .
- the reverse flow control valve 42 /check valve may be used to reduce the pressure in the separator 22 in case excessive refrigerant in vapor form build up.
- the refrigerant returns the second refrigerant path 164 will be cooled in the condenser 12 again.
- the reverse flow control valve 42 may be optional if the pump-condenser fan control logic 72 in the second embodiment applied to this embodiment.
- the reverse flow control valve 42 may be optional if the size of the condenser 12 is large enough.
- the pump-condenser fan control logic 72 is connected to the pump 20 and condenser fan 80 .
- the pump-condenser fan control logic 72 regulates the condenser 12 to cool the refrigerant before the pump 20 pumping the refrigerant.
- the condenser 12 can cool the refrigerant before the refrigerant reaches the pump 20 . Even if there is still a refrigerant in vapor form after the operation of the condenser 12 , the refrigerant in vapor form will be separated by the separator 22 and returns the second refrigerant path 164 as described previously.
- the combination further prevents the pump 20 from cavitation when the pump 20 is a liquid pump.
- the pump 20 in this embodiment is a positive displacement liquid pump.
- the two phase oil cooling system 10 also includes a separator 22 , a compressor path 1624 coupling the separator 22 to the first refrigerant path 162 , and a compressor 24 positioned in the compressor path 1624 .
- the compressor 24 compresses the refrigerant that is vapor form flowing from the separator 22 through the compressor path 1624 to the evaporators 14 .
- the pump 20 pumps the refrigerant that is liquid form flowing from the separator 22 through the first refrigerant path 162 to the evaporators 14 .
- the compressor path 1624 later merges to the first refrigerant path 162 , mixing the refrigerant in vapor and liquid forms.
- the compressor path 1624 is parallel to the first refrigerant path 162 from the separator 22 to the pump 20 such that the refrigerant in vapor form separated by the separator 22 does not flow into the pump 20 which is a liquid pump.
- the refrigerant in vapor form can be guided to the compressor path 1624 without damage the pump 20 .
- the refrigerant flows from the evaporator 14 ′, through the compressor 24 ′, to the condenser 12 ′
- the refrigerant flows opposite direction, from the condenser 12 , through the compressor 24 , to the evaporator 14 .
- the two phase oil cooling system 10 includes an energy recycling unit 30 positioned in the second refrigerant path 164 .
- the energy recycling unit 30 is installed between the evaporators 14 and the condenser 12 .
- the energy recycling unit 30 includes a turbine 32 driven by the refrigerant.
- the turbine 32 in this embodiment is a two phase flow turbine compatible to work with the refrigerant in vapor and liquid forms.
- the energy recycling unit 30 may include at least one of a secondary pump 34 and a generator 36 coupled to the turbine 32 .
- the turbine 32 absorbs partial energy from the refrigerant and drives the secondary pump 34 and the generator 36 .
- the turbine 32 can translate energy potential in the refrigerant that is vapor form into shaft power.
- the shaft power is used to turn the secondary pump 34 and the generator 36 .
- the turbine 32 can also utilize the flow of the refrigerant, in liquid or vapor form, caused by the pump 20 to increase the shaft power.
- the energy recycling unit 30 not only reuse excessive energy of the refrigerant but also share the task of the condenser 12 because a portion of the energy is removed. Therefore, more percentage of the refrigerant in liquid form is transformed into liquid form.
- TXV thermal expansion valve
- the second refrigerant path 164 coupled to the condenser 12 and the evaporators 14 does not have to have the thermal expansion valve (TXV).
- the secondary pump 34 may pump another liquid to obtain additional functions.
- the secondary pump 34 can be an oil pump 66 as shown in FIG. 8A .
- the secondary pump 34 /oil pump 66 therefore can pump an oil from the rotating component 60 , which will be introduced in detail later.
- the generator 36 may be further coupled to a battery or other electrical components (not shown).
- the energy recycling unit 30 can also be applied to the second refrigerant path 164 in the configuration of FIGS. 3-5 or other variations of FIG. 2 .
- FIG. 7 it is the fifth embodiment of FIG. 2 .
- a rotating component 60 is used for illustration in this embodiment; however, the two phase oil cooling system 10 may have more than one rotating components 60 .
- the evaporator 14 is at least partially submerged in the oil 62 within the rotating component 60 of the work vehicle. When the rotating component 60 operates, the oil 62 is driven to flow along at least one surface of the evaporator 14 to increase heat exchange rate.
- the rotating component 60 is a front axle where a gear sets, a differential, a shaft, etc. are rotating and driving the oil 62 flowing quickly within the rotating component 60 and therefore such configuration improves the heat exchange between the refrigerant in the evaporator 14 and the oil 62 in the rotating component 60 .
- the relative position between the evaporator 14 and the rotating component 60 can be applied to other variations of FIG. 2 .
- FIG. 8A it is the sixth embodiment of FIG. 2 .
- a rotating component 60 is used for illustration in this embodiment; however, the two phase oil cooling system 10 may have more than one rotating components 60 .
- FIG. 8A merely demonstrates one evaporator 14 but the number of the evaporator 14 , depending on practical design, can be numerous applied on single or multiple rotating components 60 .
- the evaporator 14 is positioned outside the rotating component 60 .
- the two phase oil cooling system 10 further includes the oil pump 66 , first oil path 642 , and second oil path 644 .
- the oil (will be shown in FIG.
- the rotating component 60 is in fluid communication with the rotating component 60 and the evaporator 14 via the first oil path 642 and the second oil path 644 which couple the rotating component 60 to the evaporator 14 .
- the oil pump 66 is positioned in the first oil path 642 , and the oil pump 66 pumping the oil from the rotating component 60 to the evaporator 14 .
- the two phase oil cooling system 10 may further include an oil filter 68 which can be positioned in either one of the first oil path 642 and second oil path 644 . In this embodiment, the oil filter 68 is positioned in the second oil path 644 .
- the flow of oil not only is not only cooled during the heat exchange in the evaporator 14 , but is also cleaned during the filtration in the oil filter 68 . Therefore, the oil exiting from the evaporator 14 is hot with impurity but when it flows back to the evaporator 14 , it is cooled and clean.
- the evaporator 14 is positioned outside the rotating component 60 makes an operator to maintain easily.
- the filtration process also extends the life of the rotating component 60 .
- the sixth embodiment of the two phase oil cooling system 10 may be used in a work vehicle that normally has a severe duty application.
- FIG. 8B it illustrations a perspective view of the evaporator 14 , with the refrigerant designated as 15 and the oil designated as 62 .
- the evaporator 14 includes a refrigerant passage 142 through which flows the refrigerant 15 .
- the refrigerant passage 142 thermally couples the first refrigerant path 162 to the second refrigerant path 164 .
- the evaporator 14 also includes an oil passage 144 through which flows the oil 62 .
- the oil passage 144 thermally couples the first oil path 642 to the second oil path 644 .
- the refrigerant passage 142 and the oil passage 144 are at least in proximity to or engaged with one another to exchange heat. It is also noted that in at least a portion of the refrigerant passage 142 and in at least a portion of the oil passage 144 , the refrigerant 15 and the oil 62 run in opposite directions.
- FIG. 9A it shows another embodiment of the two phase oil cooling system 10 .
- the two phase oil cooling system 10 may include one or more fluid (circuits) to absorb heat from the oil and to be cooled by the refrigerant 15 .
- the condenser 12 , the separator 22 , the pump 20 , the evaporator 14 , and the refrigerant 15 may be similar to those as shown in FIG. 8 .
- the rotating component in this embodiment includes a first rotating component 602 , a second rotating component 604 , and a third rotating component 606 .
- the two phase oil cooling system 10 include a first heat exchanger 902 , a second heat exchanger 904 , and a third heat exchanger 906 respectively submerged in the oil of the first rotating component 602 , the second rotating component 604 , and the third rotating component 606 .
- the two phase oil cooling system may also include an antifreeze path 94 which couples the evaporator 14 to the first, second and third heat exchangers 902 , 904 , 906 .
- An antifreeze 92 is in fluid communication with the evaporator 14 and the first, second and third heat exchangers 902 , 904 , 906 via the antifreeze path 94 .
- an antifreeze pump 96 is positioned in the antifreeze paths 94 and is configured to pump the antifreeze 92 to the evaporator 14 .
- the antifreeze 92 in this embodiment is glycol.
- the antifreeze 92 absorbs heat in the first, second, third heat exchangers 902 , 904 , 906 from the oil of the first, second, and third rotating components 602 , 604 , 606 .
- the heated antifreeze 92 then flows to the evaporator 14 to heat the refrigerant from liquid form to vapor form such that the cooled antifreeze 92 can flow to the heat exchangers 902 , 904 , 906 again to cool the oil in the first, second, third rotating components 602 , 604 , 606 .
- the first, second, third heat exchangers 902 , 904 , 906 are positioned outside the first, second, third rotating components 602 , 604 , 606 .
- the oil is in fluid communication with the first, second, third heat exchangers 902 , 904 , 906 and the first, second, third rotating components 602 , 604 , 606 .
- the oil pump can pump the oil from the rotating component.
- the oil is cooled in the heat exchangers 902 , 904 , 906 via the antifreeze 92 .
- the rotating components 602 , 604 , 606 are in series connection.
- the temperature of the antifreeze 92 increases when it flows from the first rotating component 602 to the third rotating component 606 .
- Such arrangement may be based on heat transfer requirements and the maximum oil temperature requirements.
- the first rotating component 602 may need to dissipate the heat quicker than the second and third rotating components 604 , 606 .
- the third rotating component 606 may require the cooling fluid (i.e. antifreeze) above certain temperature to ensure the temperature of the oil is above certain temperature.
- the rotating components 602 , 604 , 606 can be in parallel or partially parallel, as shown in FIG. 10 .
- the condenser fan 80 may be coupled to the refrigerant path 16 .
- the condenser fan 80 is positioned in the second refrigerant path 164 .
- the condenser fan 80 is downstream of the evaporator 14 but upstream of the condenser 12 .
- the volumetric expansion of the refrigerant may be used to spin the condenser fan 80 .
- the fan 80 may spin without power from other sources or with relative lower power from other sources (not shown). This configuration may be applied to various embodiments having a path between an evaporator and a condenser.
- FIG. 12 it illustrates another embodiment of the two phase oil cooling system 10 that utilizes buoyancy to drive refrigerant.
- the condenser 12 is positioned higher than the evaporators 14 .
- the two phase oil cooling system 10 comprises the condenser 12 , the evaporators 14 , the refrigerant path 16 , the controller 70 , and the condenser fan 80 .
- the refrigerant path 16 thermally couples the condenser 12 to the evaporators 14 .
- the refrigerant passing through or in proximity to the condenser 12 moves downward and the refrigerant passing though or in proximity to the evaporators 14 moves upward.
- the refrigerant is able to flow bi-directions in the refrigerant path 16 .
- the refrigerant is driven by difference of densities of the refrigerant responsive to the temperatures of the refrigerant within the refrigerant path 16 , within the condenser 12 , and within the evaporators 14 .
- the two phase oil cooling system 10 further includes a temperature sensor 122 to measure the temperature of the refrigerant in at least one of the condenser 12 , the evaporators 14 , and the refrigerant path 16 .
- the temperature sensor 122 is positioned in the condenser 12 to measure the temperature of the refrigerant and to be electrically connected to the controller 70 .
- the controller 70 based on the temperature of the refrigerant in the condenser 12 , adjusts the condenser fan 80 operation speed.
- the refrigerant exiting from the evaporators 14 may bring more heat, and the condenser fan 80 thus speeds up to provide the stronger first air flow AF 1 to ensure there is a substantial difference in density of the refrigerant between the condenser 12 and evaporators 14 .
- the circulation of the refrigerant is ensured in this embodiment.
- the present disclosure also provides a method for cooling a rotating component:
- Step 1 pumping a refrigerant at least partial in liquid form to an evaporator and further to a condenser via a pump such that a pressure of the refrigerant flowing into the evaporator is higher than another pressure of the refrigerant flowing into the condenser.
- step 1 also includes separating the refrigerant in vapor form from the refrigerant in liquid form to permit the refrigerant in liquid form to flow through the pump.
- the refrigerant in vapor form is disposed in two ways:
- Step 2 absorbing a heat from an oil of the rotating component by the evaporator to evaporate the refrigerant from liquid form to vapor form.
- Step 2 also includes submerging the evaporator in the oil within the rotating component.
- the oil is driven to flow along at least one surface of the evaporator to increase heat exchange rate.
- step 2 includes pumping the oil by an oil pump from the rotating component to the evaporator to exchange the heat between the oil and the refrigerant.
- This step also includes filtering the oil via an oil filter utilizing the oil pressure created by the oil pump.
- Step 2 may also include recycling energy from the refrigerant that exits from the evaporator.
- the turbine is driven by the refrigerant.
- Step 3 cooling the refrigerant at least partial in vapor form via the condenser.
- a technical effect of one or more of the example embodiments disclosed herein is to cool the oil in the rotating component with higher heat transfer coefficient refrigerant to reach better cooling performance. Another technical effect of one or more of the example embodiments disclosed herein is to distribute the heat loads from one or more rotating components without the oil being pumped to a remote distance of the work vehicle. Another technical effect of one or more of the example embodiments disclosed herein is to decrease the chance of oil leakage.
- lists with elements that are separated by conjunctive terms (e.g., “and”) and that are also preceded by the phrase “at least one of” or “one or more of” indicate configurations or arrangements that potentially include individual elements of the list, or any combination thereof.
- “at least one of A, B, and C” or “one or more of A, B, and C” indicates the possibilities of only A, only B, only C, or any combination of two or more of A, B, and C (e.g., A and B; B and C; A and C; or A, B, and C)
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Abstract
Description
- N/A
- The present disclosure relates generally to a cooling system applied to a work vehicle.
- The off-highway industry uses a variety of rotating components: transmissions, axles, e-machines, hydraulic pumps and motors, etc. These components may use oil as a working fluid and/or for lubrication and cooling. A rotating component of a work vehicle, such as axle or transmission, generates heat while in operation. Conventionally, the heat is partially removed by a cooling system/circuit, including a radiator coupled to the work vehicle, a cooling fan, and an oil path. A hot cooling oil from the rotating component flows into the radiator and is cooled by the radiator due to the cooling fan providing an air flow passing through a series of heat dissipation components of the radiator. The cooled cooling oil later flow back to the rotating component. However, since the oil is typically pumped outside the rotating component to the remote single phase oil-to-air heat exchanger for cooling, this cooling circuit is prone to leaks, contamination, pumping losses and has a low heat transfer coefficient.
- The present disclosure includes a two phase oil cooling system that leverages the advantages of two-phase refrigerant applied on oil cooling which has significantly higher heat transfer coefficient. In addition, the present disclosure has the advantage of distributed heat loads from several components and does not require that oil be pumped to a remote cooling system.
- According to an aspect of the present disclosure, a two phase oil cooling system is provided for a work vehicle. The two phase oil cooling system includes a condenser, an evaporator, a refrigerant path, and a pump. The condenser cools a refrigerant from vapor form to liquid form. The evaporator exchanges heat between a first fluid of the work vehicle and the refrigerant, thereby heating the refrigerant from liquid form to vapor form. The refrigerant path comprises a first refrigerant path thermally coupling the condenser to the evaporator and a second refrigerant path thermally coupling the evaporator to the condenser. The refrigerant flows through the refrigerant path. The pump is positioned in the first refrigerant path for pumping the refrigerant from the condenser to the evaporator, such that the evaporator is downstream of the pump and the condenser is downstream of the evaporator.
- According to another aspect of the present disclosure, a two phase oil cooling system is provided for a work vehicle. The two phase oil cooling system includes a condenser, an evaporator, and a refrigerant path. The condenser cools a refrigerant from vapor form to liquid form. The evaporator is positioned below the condenser and exchanges heat between an oil of a rotating component of the work vehicle and the refrigerant, thereby heating the refrigerant from liquid form to vapor form. The refrigerant path thermally couples the condenser to the evaporator. The refrigerant flows in bi-directions in the refrigerant path, driven by difference of densities of the refrigerant responsive to temperatures of the refrigerant within the refrigerant path, within the condenser, and within the evaporator.
- The present disclosure also provides a method for cooling a rotating component. The method includes: pumping a refrigerant at least partial in liquid form to an evaporator and moving the refrigerant at least partial in vapor form to a condenser via the pumping such that a pressure of the refrigerant flowing into the evaporator is higher than another pressure of the refrigerant flowing into the condenser; absorbing a heat from an oil in the rotating component by the evaporator to evaporate the refrigerant from liquid form to vapor form; and cooling the refrigerant at least partial in vapor form via the condenser.
- Other features and aspects will become apparent by consideration of the detailed description and accompanying drawings.
- The detailed description of the drawings refers to the accompanying figures in which:
-
FIG. 1 is a block diagram for a conventional cooling system applied on an air conditioner; -
FIG. 2 is a simplified block diagram for a two phase oil cooling system applied on a work vehicle; -
FIG. 3 is a block diagram of the first embodiment ofFIG. 2 having multiple evaporators; -
FIG. 4 is a block diagram of the second embodiment ofFIG. 2 having a pump-condenser fan control logic; -
FIG. 5 is a block diagram of the third embodiment ofFIG. 2 having a separator separating a refrigerant in vapor form from the refrigerant in liquid form; -
FIG. 6 is a block diagram of the fourth embodiment ofFIG. 2 having a separator separating a refrigerant in vapor form from the refrigerant in liquid form, and the refrigerant in vapor form is processed in a compressor; -
FIG. 7 is a block diagram of the fifth embodiment ofFIG. 2 , showing an evaporator is positioned within a rotating component; -
FIG. 8A is a block diagram of the sixth embodiment ofFIG. 2 , showing an evaporator is positioned outside a rotating component; -
FIG. 8B is a perspective view of the evaporator inFIG. 8A ; -
FIG. 9A is a block diagram of an embodiment of the two phase oil cooling system that utilizes antifreeze flowing through the evaporator and the heat exchangers positioned within the rotating components; -
FIG. 9B is a block diagram of an embodiment of the two phase oil cooling system that utilizes antifreeze flowing through the evaporator and the heat exchangers positioned outside rotating components; -
FIG. 10 is a block diagram of an embodiment of the two phase oil cooling system, where the rotating components are in partial parallel connection; -
FIG. 11 is a block diagram of the seventh embodiment ofFIG. 2 , demonstrating the fan driven by the refrigerant; and -
FIG. 12 is a block diagram of an embodiment of the two phase oil cooling system that utilizes buoyancy to drive the refrigerant flow. - Referring to
FIG. 1 , a conventional cooling system applied on an air conditioner includes anevaporator 14′, acompressor 24′, acondenser 12′, and a thermal expansion valve (TXV), where refrigerant flows through in liquid and/or in vapor form at different pressure. The air conditioner normally is fixed on a wall of a house and some elements of the air condition are indoor and some are outdoor. In general, thecompressor 24′ and thecondenser 12′ of the air conditioner are positioned in the outdoor environment; the thermal expansion valve (TXV) and theevaporator 14′ are positioned indoor environment. Theevaporator 14′ is located in the low pressure side (compressor suction side) and thecondenser 12′ is used in the high pressure side. The thermal expansion valve (TXV) is used between thecondenser 12′ and theevaporator 14′ to reduce pressure. - In a path (suction line) between the
evaporator 14′ and thecompressor 24′, the refrigerant is at a low pressure and low temperature. In order to run thecompressor 24′ properly, the refrigerant is in vapor form (gas or superheat gas). When the refrigerant reaches thecompressor 24′, thecompressor 24′ compresses the refrigerant in vapor form, such that the refrigerant in a path between thecompressor 24′ and thecondenser 12′ is at a high pressure (PH) and high temperature (may be superheat). When the refrigerant reachescondenser 12′, thecondenser 12′ cools the temperature of the refrigerant and change it into liquid form via a fan (not shown). The fan provides a first air flow AF1′ passing through a heat dissipation element of thecondenser 12′ to remove the heat from thecondenser 12′. Refrigerant at the exit of thecondenser 12′ must be saturated or subcooled liquid for smooth operation of thermal expansion valve (TXV). In a path between thecondenser 12′ and the thermal expansion valve (TXV), the refrigerant is still at the high pressure. - The thermal expansion valve (TXV) later collects the refrigerant from the
condenser 12′. In the thermal expansion valve (TXV), the pressure of the refrigerant drastically decreases. The temperature of the refrigerant may also drop. Therefore, in a path between the thermal expansion valve (TXV) and theevaporator 14′, the refrigerant is at a low pressure (PL). The low pressure refrigerant flows into theevaporator 14′. Another fan (not shown) adjacent to theevaporator 14′ provides a second air flow AF2′ (indoor) passing through a heat exchange element of the evaporator 14′. The heat of the second air flow AF2′ is absorbed by the refrigerant, because refrigerant in liquid form changing into vapor form requires latent heat (energy potential). Again, the refrigerant is discharged by theevaporator 14′ and flows into thecompressor 24′. -
FIG. 2 illustrates a simplified block diagram of a two phaseoil cooling system 10 for a work vehicle. In particular, the two phaseoil cooling system 10 is applied on at least one rotating component of the work vehicle, including transmissions, axles, e-machines, hydraulic pumps and motors. The two phaseoil cooling system 10 comprises acondenser 12, anevaporator 14, and apump 20. Thecondenser 12 is used to cool a refrigerant from vapor form to liquid form. Theevaporator 14 is used to exchange heat between an oil of a rotating component of the work vehicle and the refrigerant. The two phaseoil cooling system 10 also includes arefrigerant path 16 which has a first and secondrefrigerant paths refrigerant path 162 thermally couples thecondenser 12 to theevaporator 14, and the secondrefrigerant path 164 thermally couples theevaporator 14 to thecondenser 12. The refrigerant flows through therefrigerant path 16. Thepump 20 is positioned in the firstrefrigerant path 162 for pumping the refrigerant from thecondenser 12 to theevaporator 14, such that theevaporator 14 is downstream of thepump 20 and thecondenser 12 is downstream of theevaporator 14. In other word, the pressure of the refrigerant in between thepump 20 and theevaporator 14 of the firstrefrigerant path 162 is high pressure PH; the pressure of the refrigerant in the secondrefrigerant path 164 is low pressure PL. Theevaporator 14 is located in the high pressure side and thecondenser 12 is located in the low pressure side. The reservoir, if any, is omitted inFIG. 2 . - A first air flow AF1 is driven by a
condenser fan 80 to cool thecondenser 12, such that the refrigerant in vapor form flowing from the secondrefrigerant path 164 can be transformed into liquid form. Thepump 20 pumps the refrigerant into theevaporator 14. A first oil flow OF1 flowing from or in the rotating component, transfers the heat to the refrigerant within theevaporator 14. With the vaporization of the refrigerant, the first oil flow OF1 is therefore cooled. The heated refrigerant later exits from theevaporator 14 and enters to thecondenser 12 to be liquidized. - The following embodiments include multiple variations derivative from
FIG. 2 . The embodiments of present disclosure can be modified and/or combined with at least one another to construe different configurations. The variations and the combinations will not depart from the spirit and scope of the present disclosure. For example, thepump 20 can be a two-phase flow pump, a positive displacement liquid pump, or can be combined with a compressor. The number of theevaporator 14 can be one or more than one. Themultiple evaporators 14 can be applied on one or more rotating component. The position of theevaporator 14 can be inside or outside of the rotating component for exchanging the heat between the refrigerant and the oil. - Referring to
FIG. 3 , in the first embodiment of the present disclosure, thepump 20 is a two-phase flow pump, which has capability to pump the refrigerant in both vapor and liquid forms. Becausepump 20 in this embodiment is compatible to the two forms of the refrigerant, it can avoid the cavitation that occurs when some the refrigerant in vapor form in a liquid pump. Therefore, even when thecondenser 12 in this embodiment cannot completely transform the refrigerant in vapor form to liquid form, thepump 20 can still work smoothly to pump the refrigerant into theevaporators 14. There aremultiple evaporators 14, each of which is applied on a respective one of rotating component (not shown inFIG. 3 ). In addition, in this embodiment, the firstrefrigerant path 162 divides a plurality of sub-firstrefrigerant paths 1622 and the secondrefrigerant path 164 divides a plurality of sub-secondrefrigerant paths 1642. Each of theevaporators 14 is coupled to one of the sub-firstrefrigerant paths 1622 and to one of thesub-second refrigerant paths 1642. Each of the sub-firstrefrigerant path 1622 is positioned aflow control valve 40 to control the flow in the respective one of theevaporators 14. In this regard, the fourevaporators 14 may have different flows of the refrigerant and therefore the efficiency of the heat exchange in theevaporators 14 are different. Utilizing theflow control valves 40 can distribute appropriate amount of refrigerant in theevaporators 14. The control of theflow control valves 40 relates to the extent of necessity for the rotating components where theevaporators 14 are coupled. For one example, if one of the rotating components is a front axle and another one of rotating components is a rear axle, and if there is a mode change in the work vehicle, from four-wheel drive to front wheel drive, theflow control valve 40 applied on the front axle will increase the flow of the refrigerant, and theflow control valve 40 applied on the rear axle will decrease the flow of the refrigerant. Theflow control valves 40 is operated via the command of a controller (not shown) which adjust the multipleflow control valves 40 based on the loading of the rotating components. For another example, if the temperature of one rotating component is higher than that of another, theflow control valve 40 allows larger flow of the refrigerant than anotherflow control valve 40 of another rotating component does. It can be performed when theflow control valves 40 are temperature control valves, or theflow control valves 40 coupled to thermometers and/or flow pressor sensor, in corporation with a controller (not shown) controlling the flow based on preset multiple criteria, including temperature, flow pressure, durability of the rotating components, etc. Alternatively, themultiple evaporators 14 can be applied on a single rotating component to cool different portions of the rotating component. - Referring to
FIG. 4 , it is the second embodiment ofFIG. 2 . The feature in this embodiment is similar toFIG. 3 except thepump 20 is a positive displacement liquid pump, and the two phaseoil cooling system 10 also includes acontroller 70 which has a pump-condenserfan control logic 72. The pump-condenserfan control logic 72 is connected to thepump 20 andcondenser fan 80. To ensure most of the refrigerant exiting from thecondenser 12 has been transformed into liquid form to prevent the cavitation occurred in thepump 20, the pump-condenserfan control logic 72 regulates thecondenser 12 to cool the refrigerant before thepump 20 pumping the refrigerant. In this regard, thecondenser 12 makes the refrigerant subcooled or saturated before the refrigerant reaches thepump 20. - Referring to
FIG. 5 , it is the third embodiment ofFIG. 2 . Thepump 20 in this embodiment is a positive displacement liquid pump. The two phaseoil cooling system 10 also includes aseparator 22, a reverserefrigerant path 166, and a reverseflow control valve 42 positioned in the reverserefrigerant path 166. Theseparator 22 is positioned in the firstrefrigerant path 162 between thecondenser 12 and thepump 20, and is configured to separate the refrigerant in vapor form from the refrigerant in liquid form and to permit the refrigerant in liquid form to flow through thepump 20. The remaining part of the refrigerant in vapor form flows through the reverserefrigerant path 166 from theseparator 22 to the secondrefrigerant path 164. The reverseflow control valve 42, for example, a check valve, controls the flow of the refrigerant in vapor form in the reverserefrigerant path 166. The reverseflow control valve 42/check valve may be used to reduce the pressure in theseparator 22 in case excessive refrigerant in vapor form build up. The refrigerant returns the secondrefrigerant path 164 will be cooled in thecondenser 12 again. The reverseflow control valve 42 may be optional if the pump-condenserfan control logic 72 in the second embodiment applied to this embodiment. The reverseflow control valve 42 may be optional if the size of thecondenser 12 is large enough. - It is noted that the features in the second and third embodiments can be combined (referring to
FIGS. 4 and 5 ). The pump-condenserfan control logic 72 is connected to thepump 20 andcondenser fan 80. The pump-condenserfan control logic 72 regulates thecondenser 12 to cool the refrigerant before thepump 20 pumping the refrigerant. In this regard, thecondenser 12 can cool the refrigerant before the refrigerant reaches thepump 20. Even if there is still a refrigerant in vapor form after the operation of thecondenser 12, the refrigerant in vapor form will be separated by theseparator 22 and returns the secondrefrigerant path 164 as described previously. The combination further prevents thepump 20 from cavitation when thepump 20 is a liquid pump. - Referring to
FIG. 6 , it is the fourth embodiment ofFIG. 2 . Thepump 20 in this embodiment is a positive displacement liquid pump. The two phaseoil cooling system 10 also includes aseparator 22, acompressor path 1624 coupling theseparator 22 to the firstrefrigerant path 162, and acompressor 24 positioned in thecompressor path 1624. Thecompressor 24 compresses the refrigerant that is vapor form flowing from theseparator 22 through thecompressor path 1624 to theevaporators 14. Thepump 20 pumps the refrigerant that is liquid form flowing from theseparator 22 through the firstrefrigerant path 162 to theevaporators 14. In this embodiment, thecompressor path 1624 later merges to the firstrefrigerant path 162, mixing the refrigerant in vapor and liquid forms. Thecompressor path 1624 is parallel to the firstrefrigerant path 162 from theseparator 22 to thepump 20 such that the refrigerant in vapor form separated by theseparator 22 does not flow into thepump 20 which is a liquid pump. In this regard, even if the rotating component is in high heat load and thecondenser 12 cannot condense all the refrigerant into liquid form with the energy consumed by another component (i.g. energy recycling unit, introduced in next paragraph), the refrigerant in vapor form can be guided to thecompressor path 1624 without damage thepump 20. Unlike the conventional cooling system as described inFIG. 1 , where the refrigerant flows from theevaporator 14′, through thecompressor 24′, to thecondenser 12′, in this embodiment, the refrigerant (in vapor form) flows opposite direction, from thecondenser 12, through thecompressor 24, to theevaporator 14. - Referring again to
FIG. 6 , the two phaseoil cooling system 10 includes anenergy recycling unit 30 positioned in the secondrefrigerant path 164. In this embodiment, theenergy recycling unit 30 is installed between theevaporators 14 and thecondenser 12. Theenergy recycling unit 30 includes aturbine 32 driven by the refrigerant. Theturbine 32 in this embodiment is a two phase flow turbine compatible to work with the refrigerant in vapor and liquid forms. Theenergy recycling unit 30 may include at least one of asecondary pump 34 and agenerator 36 coupled to theturbine 32. Theturbine 32 absorbs partial energy from the refrigerant and drives thesecondary pump 34 and thegenerator 36. In one aspect, theturbine 32 can translate energy potential in the refrigerant that is vapor form into shaft power. The shaft power is used to turn thesecondary pump 34 and thegenerator 36. In another aspect, theturbine 32 can also utilize the flow of the refrigerant, in liquid or vapor form, caused by thepump 20 to increase the shaft power. As such, theenergy recycling unit 30 not only reuse excessive energy of the refrigerant but also share the task of thecondenser 12 because a portion of the energy is removed. Therefore, more percentage of the refrigerant in liquid form is transformed into liquid form. Unlike the conventional cooling system as described inFIG. 1 having a thermal expansion valve (TXV) which may decrease the refrigerant flowing speed, the secondrefrigerant path 164 coupled to thecondenser 12 and theevaporators 14 does not have to have the thermal expansion valve (TXV). - When the
energy recycling unit 30 includes thesecondary pump 34, thesecondary pump 34 may pump another liquid to obtain additional functions. For example, thesecondary pump 34 can be anoil pump 66 as shown inFIG. 8A . Thesecondary pump 34/oil pump 66 therefore can pump an oil from the rotatingcomponent 60, which will be introduced in detail later. Referring toFIG. 6 , when theenergy recycling unit 30 includes thegenerator 36, thegenerator 36 may be further coupled to a battery or other electrical components (not shown). - It is noted that, the
energy recycling unit 30 can also be applied to the secondrefrigerant path 164 in the configuration ofFIGS. 3-5 or other variations ofFIG. 2 . - With reference to
FIG. 7 , it is the fifth embodiment ofFIG. 2 . A rotatingcomponent 60 is used for illustration in this embodiment; however, the two phaseoil cooling system 10 may have more than onerotating components 60. Theevaporator 14 is at least partially submerged in theoil 62 within the rotatingcomponent 60 of the work vehicle. When therotating component 60 operates, theoil 62 is driven to flow along at least one surface of theevaporator 14 to increase heat exchange rate. For example, the rotatingcomponent 60 is a front axle where a gear sets, a differential, a shaft, etc. are rotating and driving theoil 62 flowing quickly within the rotatingcomponent 60 and therefore such configuration improves the heat exchange between the refrigerant in theevaporator 14 and theoil 62 in the rotatingcomponent 60. The relative position between the evaporator 14 and therotating component 60 can be applied to other variations ofFIG. 2 . - Referring to
FIG. 8A , it is the sixth embodiment ofFIG. 2 . A rotatingcomponent 60 is used for illustration in this embodiment; however, the two phaseoil cooling system 10 may have more than onerotating components 60.FIG. 8A merely demonstrates oneevaporator 14 but the number of theevaporator 14, depending on practical design, can be numerous applied on single or multiplerotating components 60. In this embodiment, theevaporator 14 is positioned outside the rotatingcomponent 60. The two phaseoil cooling system 10 further includes theoil pump 66,first oil path 642, andsecond oil path 644. The oil (will be shown inFIG. 8B ) of therotating component 60 is in fluid communication with the rotatingcomponent 60 and theevaporator 14 via thefirst oil path 642 and thesecond oil path 644 which couple therotating component 60 to theevaporator 14. Theoil pump 66 is positioned in thefirst oil path 642, and theoil pump 66 pumping the oil from the rotatingcomponent 60 to theevaporator 14. The two phaseoil cooling system 10 may further include anoil filter 68 which can be positioned in either one of thefirst oil path 642 andsecond oil path 644. In this embodiment, theoil filter 68 is positioned in thesecond oil path 644. In this configuration, the flow of oil not only is not only cooled during the heat exchange in theevaporator 14, but is also cleaned during the filtration in theoil filter 68. Therefore, the oil exiting from theevaporator 14 is hot with impurity but when it flows back to theevaporator 14, it is cooled and clean. - The
evaporator 14 is positioned outside the rotatingcomponent 60 makes an operator to maintain easily. The filtration process also extends the life of therotating component 60. The sixth embodiment of the two phaseoil cooling system 10 may be used in a work vehicle that normally has a severe duty application. - Referring to
FIG. 8B , it illustrations a perspective view of theevaporator 14, with the refrigerant designated as 15 and the oil designated as 62. Theevaporator 14 includes arefrigerant passage 142 through which flows the refrigerant 15. Therefrigerant passage 142 thermally couples the firstrefrigerant path 162 to the secondrefrigerant path 164. Theevaporator 14 also includes anoil passage 144 through which flows theoil 62. Theoil passage 144 thermally couples thefirst oil path 642 to thesecond oil path 644. Therefrigerant passage 142 and theoil passage 144 are at least in proximity to or engaged with one another to exchange heat. It is also noted that in at least a portion of therefrigerant passage 142 and in at least a portion of theoil passage 144, the refrigerant 15 and theoil 62 run in opposite directions. - Referring to
FIG. 9A , it shows another embodiment of the two phaseoil cooling system 10. Instead of circulating the refrigerant 15 around the work vehicle and exchanging heat directly withoil 62 at theevaporator 14, the two phaseoil cooling system 10 may include one or more fluid (circuits) to absorb heat from the oil and to be cooled by the refrigerant 15. Thecondenser 12, theseparator 22, thepump 20, theevaporator 14, and the refrigerant 15 may be similar to those as shown inFIG. 8 . The rotating component in this embodiment includes a firstrotating component 602, a secondrotating component 604, and a thirdrotating component 606. The two phaseoil cooling system 10 include afirst heat exchanger 902, asecond heat exchanger 904, and athird heat exchanger 906 respectively submerged in the oil of the firstrotating component 602, the secondrotating component 604, and the thirdrotating component 606. The two phase oil cooling system may also include anantifreeze path 94 which couples theevaporator 14 to the first, second andthird heat exchangers antifreeze 92 is in fluid communication with theevaporator 14 and the first, second andthird heat exchangers antifreeze path 94. In addition, anantifreeze pump 96 is positioned in theantifreeze paths 94 and is configured to pump theantifreeze 92 to theevaporator 14. - The
antifreeze 92 in this embodiment is glycol. Theantifreeze 92 absorbs heat in the first, second,third heat exchangers rotating components heated antifreeze 92 then flows to theevaporator 14 to heat the refrigerant from liquid form to vapor form such that the cooledantifreeze 92 can flow to theheat exchangers rotating components - Alternatively, referring to
FIG. 9B , the first, second,third heat exchangers rotating components third heat exchangers rotating components third heat exchangers rotating components heat exchangers antifreeze 92. - In
FIGS. 9A and 9B , the rotatingcomponents antifreeze 92 increases when it flows from the firstrotating component 602 to the thirdrotating component 606. Such arrangement may be based on heat transfer requirements and the maximum oil temperature requirements. For example, the firstrotating component 602 may need to dissipate the heat quicker than the second and thirdrotating components rotating component 606 may require the cooling fluid (i.e. antifreeze) above certain temperature to ensure the temperature of the oil is above certain temperature. Alternatively, based on the need, the rotatingcomponents FIG. 10 . - Referring to
FIG. 11 , it is noted that thecondenser fan 80 may be coupled to therefrigerant path 16. Thecondenser fan 80 is positioned in the secondrefrigerant path 164. In other words, thecondenser fan 80 is downstream of theevaporator 14 but upstream of thecondenser 12. Because the refrigerant, as described previously, is at least partially transformed to vapor form, the volumetric expansion of the refrigerant may be used to spin thecondenser fan 80. In this regard, thefan 80 may spin without power from other sources or with relative lower power from other sources (not shown). This configuration may be applied to various embodiments having a path between an evaporator and a condenser. - Referring to
FIG. 12 , it illustrates another embodiment of the two phaseoil cooling system 10 that utilizes buoyancy to drive refrigerant. In this embodiment, nopump 20 is required. Unlike previous embodiments that havepump 20 and the relative positions in height between thecondenser 12 andevaporators 14 are flexible, in this embodiment thecondenser 12 is positioned higher than theevaporators 14. In this embodiment, the two phaseoil cooling system 10 comprises thecondenser 12, theevaporators 14, therefrigerant path 16, thecontroller 70, and thecondenser fan 80. Therefrigerant path 16 thermally couples thecondenser 12 to theevaporators 14. Because the temperature the refrigerant passing through or in proximity to thecondenser 12 is lower than that of the refrigerant passing through or in proximity to theevaporators 14, the refrigerant passing through or in proximity to thecondenser 12 moves downward and the refrigerant passing though or in proximity to theevaporators 14 moves upward. In this regard, the refrigerant is able to flow bi-directions in therefrigerant path 16. The refrigerant is driven by difference of densities of the refrigerant responsive to the temperatures of the refrigerant within therefrigerant path 16, within thecondenser 12, and within theevaporators 14. - The two phase
oil cooling system 10 further includes atemperature sensor 122 to measure the temperature of the refrigerant in at least one of thecondenser 12, theevaporators 14, and therefrigerant path 16. In the embodiment as shown inFIG. 12 , thetemperature sensor 122 is positioned in thecondenser 12 to measure the temperature of the refrigerant and to be electrically connected to thecontroller 70. Thecontroller 70, based on the temperature of the refrigerant in thecondenser 12, adjusts thecondenser fan 80 operation speed. If the temperature of the refrigerant in thecondenser 12 is relatively higher than its normal operation, the refrigerant exiting from theevaporators 14 may bring more heat, and thecondenser fan 80 thus speeds up to provide the stronger first air flow AF1 to ensure there is a substantial difference in density of the refrigerant between thecondenser 12 andevaporators 14. In this regard, even without the pump as shown in the previous embodiment, the circulation of the refrigerant is ensured in this embodiment. - The present disclosure also provides a method for cooling a rotating component:
- Step 1: pumping a refrigerant at least partial in liquid form to an evaporator and further to a condenser via a pump such that a pressure of the refrigerant flowing into the evaporator is higher than another pressure of the refrigerant flowing into the condenser.
- When the pump is a liquid pump,
step 1 also includes separating the refrigerant in vapor form from the refrigerant in liquid form to permit the refrigerant in liquid form to flow through the pump. The refrigerant in vapor form is disposed in two ways: - (1) diverting the refrigerant in vapor form back to the condenser through a reverse refrigerant path; or
- (2) compressing the refrigerant in vapor form to the evaporator via a compressor.
- Step 2: absorbing a heat from an oil of the rotating component by the evaporator to evaporate the refrigerant from liquid form to vapor form.
- Step 2 also includes submerging the evaporator in the oil within the rotating component. In the operation of the rotating component, the oil is driven to flow along at least one surface of the evaporator to increase heat exchange rate.
- Alternatively, step 2 includes pumping the oil by an oil pump from the rotating component to the evaporator to exchange the heat between the oil and the refrigerant. This step also includes filtering the oil via an oil filter utilizing the oil pressure created by the oil pump.
- Step 2 may also include recycling energy from the refrigerant that exits from the evaporator. The turbine is driven by the refrigerant.
- Step 3: cooling the refrigerant at least partial in vapor form via the condenser.
- The steps mentioned above will repeat to cool the oil in the rotating component.
- Without in any way limiting the scope, interpretation, or application of the claims appearing below, a technical effect of one or more of the example embodiments disclosed herein is to cool the oil in the rotating component with higher heat transfer coefficient refrigerant to reach better cooling performance. Another technical effect of one or more of the example embodiments disclosed herein is to distribute the heat loads from one or more rotating components without the oil being pumped to a remote distance of the work vehicle. Another technical effect of one or more of the example embodiments disclosed herein is to decrease the chance of oil leakage.
- As used herein, unless otherwise limited or modified, lists with elements that are separated by conjunctive terms (e.g., “and”) and that are also preceded by the phrase “at least one of” or “one or more of” indicate configurations or arrangements that potentially include individual elements of the list, or any combination thereof. For example, “at least one of A, B, and C” or “one or more of A, B, and C” indicates the possibilities of only A, only B, only C, or any combination of two or more of A, B, and C (e.g., A and B; B and C; A and C; or A, B, and C)
- While the above describes example embodiments of the present disclosure, these descriptions should not be viewed in a limiting sense. Rather, other variations and modifications may be made without departing from the scope and spirit of the present disclosure as defined in the appended claims.
Claims (26)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/367,551 US20200309467A1 (en) | 2019-03-28 | 2019-03-28 | Two phase oil cooling system |
BR102020006222-0A BR102020006222A2 (en) | 2019-03-28 | 2020-03-27 | BIPhasic OIL COOLING SYSTEMS FOR A WORKING VEHICLE, AND, METHOD FOR COOLING A ROTATING COMPONENT |
CN202010240344.5A CN111750609A (en) | 2019-03-28 | 2020-03-30 | Two-phase oil cooling system |
DE102020204117.2A DE102020204117A1 (en) | 2019-03-28 | 2020-03-30 | TWO-PHASE OIL COOLING SYSTEM |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US16/367,551 US20200309467A1 (en) | 2019-03-28 | 2019-03-28 | Two phase oil cooling system |
Publications (1)
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US20200309467A1 true US20200309467A1 (en) | 2020-10-01 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US16/367,551 Abandoned US20200309467A1 (en) | 2019-03-28 | 2019-03-28 | Two phase oil cooling system |
Country Status (4)
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US (1) | US20200309467A1 (en) |
CN (1) | CN111750609A (en) |
BR (1) | BR102020006222A2 (en) |
DE (1) | DE102020204117A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11592221B2 (en) | 2020-12-22 | 2023-02-28 | Deere & Company | Two-phase cooling system |
US11739756B2 (en) | 2020-11-30 | 2023-08-29 | Deere & Company | Multi-pump apparatus of cooling system |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN114459266A (en) * | 2022-04-14 | 2022-05-10 | 北京中矿赛力贝特节能科技有限公司 | Gas-liquid two-phase power type separated heat pipe device |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0538400U (en) * | 1991-10-29 | 1993-05-25 | 三菱重工業株式会社 | Gas-liquid two-phase pump |
KR20040042090A (en) * | 2002-11-13 | 2004-05-20 | 위니아만도 주식회사 | refrigerating system using expansion work of refrigerant |
JP2009097434A (en) * | 2007-10-17 | 2009-05-07 | Sanden Corp | Waste heat utilization device for internal combustion engine |
CN102207020A (en) * | 2011-04-22 | 2011-10-05 | 宁波鲍斯能源装备股份有限公司 | Internal combustion engine cooling circulation system |
EP2520771B1 (en) * | 2011-05-03 | 2016-08-10 | Orcan Energy AG | Method and device for quick oil heating for oil-lubricated expansion machines |
CN103089759B (en) * | 2013-01-30 | 2016-01-20 | 三一重机有限公司 | A kind of engineering machinery and hydraulic oil cooling control system thereof |
CN203499851U (en) * | 2013-09-23 | 2014-03-26 | 天津爱奥路斯汽车技术有限公司 | Rankine power generation device for oil-powered automobile |
WO2016040408A1 (en) * | 2014-09-09 | 2016-03-17 | Carrier Corporation | Chiller compressor oil conditioning |
CN106016848A (en) * | 2016-07-07 | 2016-10-12 | 南京佳力图机房环境技术股份有限公司 | Separation type heat pipe air conditioner unit |
US10295271B2 (en) * | 2017-02-10 | 2019-05-21 | Hamilton Sundstrand Corporation | Two-phase thermal loop with rotary separation |
CN109186143B (en) * | 2018-09-29 | 2023-11-28 | 珠海格力电器股份有限公司 | Oil cooling device and control method thereof |
-
2019
- 2019-03-28 US US16/367,551 patent/US20200309467A1/en not_active Abandoned
-
2020
- 2020-03-27 BR BR102020006222-0A patent/BR102020006222A2/en not_active Application Discontinuation
- 2020-03-30 CN CN202010240344.5A patent/CN111750609A/en active Pending
- 2020-03-30 DE DE102020204117.2A patent/DE102020204117A1/en not_active Withdrawn
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11739756B2 (en) | 2020-11-30 | 2023-08-29 | Deere & Company | Multi-pump apparatus of cooling system |
US11592221B2 (en) | 2020-12-22 | 2023-02-28 | Deere & Company | Two-phase cooling system |
Also Published As
Publication number | Publication date |
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DE102020204117A1 (en) | 2020-10-01 |
CN111750609A (en) | 2020-10-09 |
BR102020006222A2 (en) | 2020-12-01 |
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