EP3982059B1 - Système de gestion de chaleur - Google Patents

Système de gestion de chaleur Download PDF

Info

Publication number
EP3982059B1
EP3982059B1 EP20871421.2A EP20871421A EP3982059B1 EP 3982059 B1 EP3982059 B1 EP 3982059B1 EP 20871421 A EP20871421 A EP 20871421A EP 3982059 B1 EP3982059 B1 EP 3982059B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
heat
exchange portion
heat exchange
communication
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20871421.2A
Other languages
German (de)
English (en)
Other versions
EP3982059A4 (fr
EP3982059A1 (fr
Inventor
Junqi DONG
Shiwei JIA
Yibiao WANG
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hangzhou Sanhua Research Institute Co Ltd
Original Assignee
Hangzhou Sanhua Research Institute Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hangzhou Sanhua Research Institute Co Ltd filed Critical Hangzhou Sanhua Research Institute Co Ltd
Publication of EP3982059A1 publication Critical patent/EP3982059A1/fr
Publication of EP3982059A4 publication Critical patent/EP3982059A4/fr
Application granted granted Critical
Publication of EP3982059B1 publication Critical patent/EP3982059B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • 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
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • F25B2313/0212—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during dehumidifying
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters

Definitions

  • the present invention relates to a field of air conditioning, and in particular to a thermal management system.
  • a thermal management system can realize cooling, heating, ventilation and air purification of indoor air, and provide a comfortable environment for indoor personnel. How to optimize the thermal management system to improve the performance thereof is a current focus.
  • a high-temperature and high-pressure refrigerant flows out of an outlet of the compressor and directly enters an outdoor heat exchanger.
  • the temperature of the refrigerant flowing out of the outlet of the compressor is relatively high.
  • the outdoor environment temperature is high, after the refrigerant exchanges heat with the external environment in the outdoor heat exchanger, the temperature of the refrigerant flowing out of the outdoor heat exchanger is still high, which results in poor cooling effect of the thermal management system.
  • US 2004/0134217 A1 discloses an air conditioning system.
  • refrigerant is circulated from a compressor to the compressor through a first exterior heat exchanger, a decompression device, an interior heat exchanger, an another decompression device, an inner heat exchanger and a second exterior heat exchanger, in this order.
  • a throttle opening degree of the another decompression device a refrigerant temperature in the interior heat exchanger can be set higher than that in the second exterior heat exchanger.
  • heat can be absorbed from outside air in the second exterior heat exchanger. Accordingly, when an outside air temperature is low, by setting the dehumidifying and heating operation, air to be blown into a compartment can be dehumidified while sufficiently increasing heating capacity.
  • US 2002/007943 A1 discloses a heat pump.
  • a first high-pressure side heat exchanger is disposed to perform a heat exchange between refrigerant discharged from a compressor and a first fluid
  • a second high-pressure side heat exchanger is disposed to perform a heat exchanger between refrigerant from the first high-pressure side heat exchanger and a second fluid having a temperature lower than that of the first fluid.
  • a heat quantity obtained from the heat pump cycle is the sum of a heat amount obtained from the first high-pressure side heat exchanger and a heat amount obtained from the second high-pressure side heat exchanger.
  • US 2014/069123 A1 discloses a heat pump system for a vehicle.
  • the heat pump system may include a cooling apparatus that supplies and circulates coolant to a motor and an electrical equipment through a cooling line, wherein the cooling apparatus includes a radiator, a cooling fan that ventilates wind to the radiator, and a water pump connected to the cooling line, and an air conditioner apparatus connected through a refrigerant line, wherein the air conditioner apparatus includes a water-cooled condenser connected to the cooling line to change a temperature of the coolant using a waste heat that has occurred in the motor and the electrical equipment according to each mode of the vehicle and that is connected to the refrigerant line to enable an injected refrigerant in the refrigerant line to exchange a heat with the coolant at the inside thereof, and an air-cooled condenser connected in series to the water-cooled condenser through the refrigerant line.
  • the present invention provides a thermal management system, as defined by appended independent claim 1, to improve the cooling effect of the thermal management system in a high-temperature environment.
  • first, second, third, etc. may be used in the present invention to describe various information, the information should not be limited to these terms. These terms are only used to distinguish the same type of information from each other.
  • a first information may also be referred to as a second information.
  • the second information may also be referred to as the first information.
  • the word “if' as used herein can be interpreted as "when” or “during” or “depending on”.
  • the term "communicated” used in the present invention is intended to indicate that a certain medium can circulate from one element to another element.
  • the term "connected” used in the present invention is intended to indicate a physical relationship, and does not necessarily mean that the components are communicated.
  • the thermal management system may include a compressor 1, a first heat exchanger 2, a first throttling device 3, a second heat exchanger 4, a third heat exchanger 6, a fourth heat exchanger 7, and an air-conditioning box 13.
  • the third heat exchanger 6 includes a first heat exchange portion 61 and a second heat exchange portion 62.
  • the first heat exchange portion 61 and the second heat exchange portion 62 can exchange heat with each other.
  • the first heat exchanger 2 and the fourth heat exchanger 7 in this embodiment are located outside the air-conditioning box 13.
  • the second heat exchanger 4 is located in an indoor air inlet passage.
  • the indoor air inlet passage is a passage of the air-conditioning box 13, that is, the second heat exchanger 4 is located in the air-conditioning box 13.
  • the thermal management system of this embodiment includes a cooling mode.
  • the thermal management system in the cooling mode, includes two loops, namely a first refrigerant loop and a coolant loop.
  • an outlet of the compressor 1, the first heat exchange portion 61, the first heat exchanger 2, the first throttling device 3, the second heat exchanger 4, and an inlet of the compressor 1 are in communication to form the first refrigerant loop.
  • the outlet of the compressor 1, the first heat exchange portion 61, the first heat exchanger 2, the first throttling device 3, the second heat exchanger 4, and the inlet of the compressor 1 are in communication in sequence to form the first refrigerant loop.
  • the second heat exchange portion 62 and the fourth heat exchanger 7 are in communication to form a coolant loop 5.
  • the second heat exchange portion 62 and the fourth heat exchanger 7 are sequentially communicated to form the coolant loop 5.
  • the above-mentioned structures in the coolant loop 5 can also be communicated in other arrangement sequences.
  • the sequential communication only describes the sequence relationship between the various components, and the various components may also include other components, such as a shut-off valve.
  • the type of the coolant disclosed in the present invention can be selected according to needs.
  • the coolant can be a heat exchange substance such as water and oil, or a mixture of water and ethylene glycol or other mixtures that can exchange heat.
  • the coolant in the second heat exchange portion 62 can cool down the temperature of the refrigerant in the first heat exchange portion 61.
  • the first heat exchanger 2 is used as a condenser
  • the second heat exchanger 4 is used as an evaporator.
  • the compressor 1 compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant.
  • the high-temperature and high-pressure gaseous refrigerant flows out of the outlet of the compressor 1 and enters the first heat exchange portion 61.
  • the refrigerant in the first heat exchange portion 61 exchanges heat with the coolant in the second heat exchange portion 62, and the refrigerant releases heat.
  • the released heat is carried by the coolant loop 5 to the fourth heat exchanger 7.
  • the heated coolant exchanges heat with the outdoor air flow in the fourth heat exchanger 7.
  • the coolant releases heat, and the released heat is carried by the air flow to the outdoor ambient air.
  • the low-temperature coolant continues to be recycled in the coolant loop 5.
  • the cooled refrigerant enters the first heat exchanger 2 and exchanges heat with the outdoor air flow in the first heat exchanger 2, and the refrigerant further releases heat.
  • the released heat is carried by the air flow to the outdoor ambient air, and the refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant.
  • the refrigerant flows out of the first heat exchanger 2, and is throttled and depressurized by the first throttling device 3 to become a low-temperature and low-pressure refrigerant.
  • the low-temperature and low-pressure refrigerant enters the second heat exchanger 4.
  • the low-temperature and low-pressure refrigerant absorbs the heat of the air around the second heat exchanger 4, so that the temperature of the air around the second heat exchanger 4 is lowered.
  • the cold air enters the passage of the air-conditioning box 13 and is sent into the cabin, thereby reducing the indoor temperature.
  • the refrigerant undergoes a phase change and partially or completely evaporates into a low-temperature and low-pressure gaseous refrigerant, which flows back into the compressor 1 to realize the recycling of the refrigerant.
  • a third heat exchanger 6 is provided at the outlet of the compressor 1.
  • the refrigerant in the first heat exchange portion 61 is cooled down by the coolant in the second heat exchange portion 62, which can reduce the temperature of the refrigerant in the outlet pipe of the compressor 1, for example, the temperature of the refrigerant decreases from 150°C to 80°C.
  • the cooled refrigerant then passes through the first heat exchanger 2 to exchange heat with the external environment so as to further reduce the temperature of the refrigerant, for example, the temperature of the refrigerant decreases from 80°C to 47°C.
  • the refrigerant flowing out of the first heat exchanger 2 sequentially flows through the first throttling device 3 to reduce pressure, flows through the second heat exchanger 4 to absorb heat and evaporate, and then flows back into the compressor 1 to realize the recycling of the refrigerant.
  • the third heat exchanger 6 is provided at the outlet of the compressor 1.
  • the refrigerant flowing out of the outlet of the compressor 1 will firstly pass through the third heat exchanger 6.
  • the refrigerant flows into the first heat exchanger 2 (i.e., the outdoor heat exchanger), takes the heat to the outside environment through the coolant loop 5, and undertakes part of the heat exchange of the outdoor heat exchanger pressure. This effectively solves the problem of insufficient outdoor heat exchanger capacity in high temperature environments (for example, between 35°C and 50°C), and improves the cooling capacity of the system.
  • the third heat exchanger 6 is a water-cooled heat exchanger.
  • the third heat exchanger 6 includes a first collecting member 15, a second collecting member 16 and a casing 19.
  • the casing 19 has two ends. The two ends of the casing 19 are sealed and connected to the first collecting member 15 and the second collecting member 16, respectively so as to enclose a heat exchange cavity 190.
  • a heat exchange tube 17 and a heat sink 18 are disposed in the third heat exchanger 6.
  • the heat exchange tube 17 and the heat sink 18 are alternately stacked in the heat exchange cavity 190 one by one.
  • the heat exchange tube 17 and the heat sink 18 are fixedly connected.
  • Two ends of the heat exchange tube 17 are fixedly connected to the first collecting member 15 and the second collecting member 16, respectively.
  • Each of the first collecting member 15 and the second collecting member 16 defines a collecting cavity.
  • the collecting cavity is in communication with a tube cavity of the heat exchange tube 17, so that the refrigerant can circulate between the first collecting member 15 and the second collecting member 16.
  • the two opposite sides of the casing 19 are also provided with an inlet pipe and an outlet pipe, so that the coolant can enter and exit the heat exchange cavity 190.
  • the coolant enters the heat exchange cavity 190 and exchanges heat with the refrigerant through the heat exchange tube 17.
  • the heat sink 18 may be corrugated fins for improving heat exchange efficiency.
  • the heat exchange tube 17 may be a microchannel flat tube.
  • Two connecting members are provided on the second current collecting member 16. The two connecting members are respectively used to connect the refrigerant pipeline, so that the refrigerant can enter and exit the second collecting member 16. It is understandable that those of ordinary skill in the art can select other types of heat exchangers as the first heat exchanger 2, the second heat exchanger 4, the third heat exchanger 6 and the fourth heat exchanger 7 according to specific scenarios, which is not limited here. According to the present invention, the corresponding type of refrigerant can also be selected and a suitable heat exchanger can be used according to the actual application.
  • the third heat exchanger 6 may adopt the structure shown in FIG. 5 , which has the characteristics of high pressure resistance and is suitable for using a medium with high pressure resistance requirements, such as carbon dioxide, as the refrigerant.
  • the thermal management system also includes a functional component.
  • the functional component can generate heat and needs to dissipate heat when the temperature exceeds a set value.
  • the coolant loop includes the above-mentioned functional component.
  • the coolant loop is used to dissipate heat from the functional component. Therefore, the coolant loop 5 in this embodiment can also undertake the heat dissipation of the functional component in the thermal management system to ensure the normal operation of the functional component, thereby effectively ensuring the stable operation of the thermal management system in the cooling mode.
  • the functional component may include a motor 51.
  • the coolant loop 5 can also undertake the heat dissipation of the motor 51 in the thermal management system to ensure the normal operation of the motor 51, thereby effectively ensuring the stable operation of the thermal management system in the cooling mode.
  • the functional components may also include other components capable of generating heat, such as a battery and so on.
  • the thermal management system can recycle the waste heat generated by the functional component. For example, in a heating mode in winter, the waste heat of functional component is used to improve the heating capacity of the thermal management system.
  • the coolant loop may also include a power device (for example, a pump device 52) for flowing the coolant. By providing the pump device 52, the circulating flow of the coolant in the coolant loop 5 can be driven.
  • the coolant flow path of the coolant loop 5 includes: the pump device 52 -> the motor 51 (or other functional component) -> the second heat exchange portion 62 -> the fourth heat exchanger 7.
  • the thermal management system may further include a first fan 9 located outside the air-conditioning box 13.
  • the first heat exchanger 2 and the fourth heat exchanger 7 are disposed along the air flow direction of the first fan 9. That is, the first heat exchanger 2 is located on an upwind side of the fourth heat exchanger 7.
  • the first heat exchanger 2 and the second heat exchanger 4 share the fan to dissipate heat from the first heat exchanger 2 and the second heat exchanger 4, and save installation space; on the other hand, in the cooling mode, since the temperature of the first heat exchanger 2 is usually higher than the temperature of the fourth heat exchanger 7, this arrangement allows the air to pass through the first heat exchanger 2 with a higher temperature first, and then pass through the fourth heat exchanger 7 with a lower temperature, thereby helping to improve the heat exchange effect and avoid affecting he heat dissipation of the first heat exchanger 2.
  • the first fan 9, the first heat exchanger 2 and the fourth heat exchanger 7 are disposed in a row or a column at intervals.
  • the fourth heat exchanger 7 is located between the first fan 9 and the first heat exchanger 2.
  • the air flow generated by the first fan 9 can more quickly take away the heat of the coolant in the fourth heat exchanger 7, speed up the cooling effect of the coolant loop 5, and reduce the temperature of the refrigerant in the second heat exchange portion 62 more quickly .
  • the inlet of the compressor 1 can also be connected with a gas-liquid separator 8 to perform gas-liquid separation of the refluxed refrigerant.
  • the liquid part of the refrigerant is stored in the gas-liquid separator 8, and the low-temperature and low-pressure gaseous refrigerant part enters the compressor 1 to be compressed again, so as to realize the recycling of the refrigerant.
  • the gas-liquid separator 8 may not be provided.
  • the thermal management system includes a fifth heat exchanger 10.
  • the fifth heat exchanger 10 includes a third heat exchange portion 11 and a fourth heat exchange portion 12.
  • the outlet of the compressor 1, the first heat exchange portion 61, the first heat exchanger 2, the third heat exchange portion 11, the first throttling device 3, the second heat exchanger 4, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form the first refrigerant loop.
  • the refrigerant flowing out of the first heat exchanger 2 passes through the third heat exchange portion 11 again.
  • the refrigerant in the third heat exchange portion 11 exchanges heat with the refrigerant in the fourth heat exchange portion 12 (a low-pressure side pipeline) to further reduce the refrigerant temperature in the third heat exchange portion 11 and further improve the cooling effect of the thermal management system.
  • the refrigerant flowing out of the third heat exchange portion 11 is throttled and depressurized by the first throttling device 3 to become a low-temperature and low-pressure refrigerant.
  • the low-temperature and low-pressure refrigerant enters the second heat exchanger 4.
  • the low-temperature and low-pressure refrigerant absorbs the heat of the air around the second heat exchanger 4, so that the temperature of the air around the second heat exchanger 4 is lowered.
  • the cold air enters the passage of the air-conditioning box 13 and is sent into the cabin, thereby reducing the indoor temperature.
  • the refrigerant undergoes a phase change and most of it evaporates into a low-temperature and low-pressure gas refrigerant, which flows into the gas-liquid separator 8.
  • the gas-liquid separator 8 separates the refluxed refrigerant, and stores the liquid part of it in the gas-liquid separator 8, while the low-temperature and low-pressure gaseous refrigerant part enters the compressor 1 through the fourth heat exchange portion 12 to be compressed again so as to realize the recycling of refrigerant.
  • the thermal management system includes a second throttling device 20 and a sixth heat exchanger 30.
  • the sixth heat exchanger 30 is located in the passage of the air-conditioning box 13.
  • the thermal management system of this embodiment also includes a heating mode. In the heating mode, the outlet of the compressor 1, the first heat exchange portion 61, the sixth heat exchanger 30, the second throttling device 20, the third heat exchange portion 11, the first heat exchanger 2, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form a second refrigerant loop. It is understandable to those skilled in the art that only one of the first refrigerant loop in the cooling mode and the second refrigerant loop in the heating mode can be selected in the same working mode.
  • the thermal management system also includes a damper 14 located in the air-conditioning box 13.
  • the damper 14 is located between the second heat exchanger 4 and the sixth heat exchanger 30.
  • the damper 14 is used to control whether the air passes through the sixth heat exchanger 30 or not. For example, in the cooling mode, the damper 14 is closed so that the air does not pass through the sixth heat exchanger 30. In the heating mode, the damper 14 is opened to allow air to pass through the sixth heat exchanger 30.
  • the first heat exchanger 2 is used as an evaporator
  • the sixth heat exchanger 30 is used as a condenser or an air cooler.
  • the damper 14 is opened so that air can flow through the sixth heat exchanger 30.
  • the damper 14 at the sixth heat exchanger 30 is closed, which reduces the influence of the sixth heat exchanger 30.
  • the compressor 1 compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant.
  • the high-temperature and high-pressure gaseous refrigerant flows out of the outlet of the compressor 1 and enters the sixth heat exchanger 30 through the first heat exchange portion 61.
  • the high-temperature and high-pressure refrigerant exchanges heat with the air flow in the sixth heat exchanger 30, and the refrigerant releases heat.
  • the hot air enters the passage of the air-conditioning box 13 and is sent into the cabin to increase the indoor temperature.
  • the refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant.
  • the refrigerant flows out of the sixth heat exchanger 30 and enters the second throttling device 20, where it is throttled and depressurized to become a low-temperature and low-pressure refrigerant.
  • the low-temperature and low-pressure refrigerant enters the first heat exchanger 2 through a third channel, absorbs the heat in the external air flow, and changes phase into a low-pressure gaseous refrigerant.
  • the low-pressure gas refrigerant enters the gas-liquid separator 8 after flowing out of the first heat exchanger 2.
  • the gas-liquid separator 8 separates the refluxed refrigerant, and stores the liquid part of it in the gas-liquid separator 8, while the low-temperature and low-pressure gaseous refrigerant part enters the compressor 1 through the fourth heat exchange portion 12 and is compressed again so as to realize the recycling of refrigerant.
  • the thermal management system of the present invention also includes a first branch.
  • the first branch is disposed in parallel with the third heat exchanger 6.
  • a control valve 80 is provided on the first branch.
  • the control valve 80 may be a water valve or other types of valves. Referring to FIG. 3 , the control valve 80 is connected to the first branch.
  • the control valve 80 is disposed in parallel with the third heat exchanger 6.
  • the control valve 80 may also be a three-way valve.
  • a first port of the three-way valve is connected to the motor 51 through a pipeline.
  • a second port of the three-way valve is connected to the second heat exchange portion 62 of the third heat exchanger 6 through a pipeline.
  • a third port of the three-way valve is connected to the first branch.
  • the coolant flow path of the coolant loop 5 includes: the pump device 52 -> the motor 51 (or other functional component) -> the control valve 80 -> the fourth heat exchanger 7. The waste heat generated by the motor is released to the external environment through the fourth heat exchanger 7.
  • the air flow generated by the first fan 9 can take away the heat of the coolant of the fourth heat exchanger 7 more quickly, and the air temperature rises at the same time.
  • the temperature of the surrounding environment of the first heat exchanger 2 rises, and the low-temperature refrigerant in the first heat exchanger 2 can absorb this part of the heat.
  • the control valve 80 can be opened to defrost the first heat exchanger 2.
  • the thermal management system also includes a heating and dehumidifying mode which can be executed when dehumidification is required in winter.
  • a heating and dehumidifying mode which can be executed when dehumidification is required in winter.
  • the outlet of the compressor 1, the first heat exchange portion 61, the sixth heat exchanger 30, the second throttling device 20, the third heat exchange portion 11, the first heat exchanger 2, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form the second refrigerant loop.
  • the outlet of the compressor 1, the first heat exchange portion 61, the sixth heat exchanger 30, the first throttling device 3, the second heat exchanger 4, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form a third refrigerant loop.
  • the second refrigerant loop is the second refrigerant loop in the heating mode in the above embodiment.
  • the third refrigerant loop is used to cool down the cabin.
  • the working process of the third refrigerant loop is as follows: the compressor 1 compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant; the high-temperature and high-pressure gaseous refrigerant flows out of the outlet of the compressor 1, enters the sixth heat exchanger 30 through the first heat exchange portion 61, and exchanges heat in the sixth heat exchanger 30; the refrigerant releases heat, the released heat is carried into the cabin by the air flow, and the refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant.
  • One path of the refrigerant flows out of the sixth heat exchanger 30 and enters the second throttling device 20 to realize the heating function of the second refrigerant loop.
  • the other path of the refrigerant enters the first throttling device 3 for expansion.
  • the refrigerant is throttled and depressurized to become a low-temperature and low-pressure refrigerant.
  • the low-temperature and low-pressure refrigerant enters the second heat exchanger 4.
  • the air circulation mode is an inner circulation, and the air with higher humidity flows through the second heat exchanger 4 with relatively lower temperature.
  • the moisture in the air flow condenses into water droplets to reduce the humidity of the air around the second heat exchanger 4.
  • the dehumidified air then flows through the sixth heat exchanger 30 for heating, so as to achieve the purpose of heating and dehumidifying.
  • the refrigerant undergoes a phase change and most of it evaporates into a low-temperature and low-pressure gas refrigerant, which flows into the gas-liquid separator 8.
  • the gas-liquid separator 8 separates the refluxed refrigerant, and stores the liquid part of it in the gas-liquid separator 8, while the low-temperature and low-pressure gaseous refrigerant enters the compressor 1 to be compressed again so as to realize the recycling of the refrigerant.
  • the thermal management system further includes a four-way valve 40.
  • the four-way valve 40 includes a first port 401, a second port 402, a third port 403 and a fourth port 404.
  • the first heat exchange portion 61 includes a first inlet 611 and a first outlet 612.
  • the first heat exchanger 2 includes a first connection port 21 and a second connection port 22.
  • the second heat exchanger 4 includes a third connection port 41 and a fourth connection port 42.
  • the sixth heat exchanger 30 includes a fifth connection port 301 and a sixth connection port 302.
  • the third heat exchange portion 11 includes a seventh connection port 111 and an eighth connection port 112.
  • the first inlet 611 is in communication with the outlet of the compressor 1.
  • the first outlet 612 is in communication with the fifth connection port 301.
  • the first port 401 is in communication with the sixth connection port 302.
  • the second port 402 is in communication with the first connection port 21.
  • the second connection port 22 is in communication with the seventh connection port 111.
  • the eighth connection port 112 is in communication with one end of the second throttling device 20.
  • the third port 403 is in communication with the other end of the second throttling device 20.
  • the third port 403 is also in communication with one end of the first throttling device 3.
  • the third connection port 41 is in communication with the other end of the first throttling device 3.
  • the fourth connection port 42 and the fourth port 404 are in communication with the inlet of the gas-liquid separator 8.
  • the fourth connection port 42 and the fourth port 404 are in communication with the inlet of the compressor 1 via the fourth heat exchange portion 12.
  • the first port 401 and the second port 402 are in communication, and the third port 403 and the fourth port 404 are not in communication.
  • the first port 401 is in communication with the third port 403, and the second port 402 is in communication with the fourth port 404.
  • the flow direction of the refrigerant can be switched, thereby realizing the switching of different modes.
  • a three-way valve or a shut-off valve can also be used to replace the four-way valve 40 to control the switching of the refrigerant flow direction and realize the switching of different modes.
  • the thermal management system may further include a shut-off valve 50.
  • One end of the shut-off valve 50 is in communication with the first outlet 612 and the fifth connection port 301, and the other end of the shut-off valve 50 is in communication with the first port 401 and the sixth connection port 302.
  • the shut-off valve 50 in the cooling mode, the shut-off valve 50 is opened. Due to the flow resistance, the sixth heat exchanger 30 can be bypassed through the branch where the shut-off valve 50 is located. Only a small amount or no refrigerant flows through the sixth heat exchanger 30, which reduces the influence of the sixth heat exchanger 30 on the refrigeration effect.
  • the shut-off valve 50 In the heating mode or the heating and dehumidifying mode, the shut-off valve 50 is closed. By controlling the shut-off valve 50, the on-off of the branch is realized. Applied to different modes, the shut-off valve 50 has a simple structure and reliable on-off control.
  • the thermal management system also includes a check valve 60.
  • the check valve 60 is disposed in parallel with the second throttling device 20. Among them, in the cooling mode, the check valve 60 is opened, and the second throttling device 20 is closed. In the heating mode or the heating and dehumidifying mode, the check valve 60 is closed, and the second throttling device 20 throttles. By controlling the check valve 60 and the second throttling device 20, the on-off of the branch is realized, which can be applied to different modes.
  • the first throttling device 3 and the second throttling device 20 can play the role of throttling and depressurizing, and blocking in the thermal management system, and may include a throttling valve, an ordinary thermal expansion valve or an electronic expansion valve etc.
  • the thermal management system may further include a second fan 70 located in the passage of the air-conditioning box 13.
  • the second heat exchanger 4 and the sixth heat exchanger 30 are disposed along the air flow direction of the second fan 70. With this arrangement, the second heat exchanger 4 and the sixth heat exchanger 30 share the fan, which saves installation space.
  • the second fan 70, the second heat exchanger 4 and the sixth heat exchanger 30 are disposed in a line or a row at intervals.
  • thermal management system of the present embodiments can be applied to houses, vehicles or other equipment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air-Conditioning For Vehicles (AREA)

Claims (13)

  1. Système de gestion thermique comprenant : un compresseur (1), un premier échangeur de chaleur (2), un premier dispositif d'étranglement (3), un deuxième échangeur de chaleur (4), un troisième échangeur de chaleur (6), un quatrième échangeur de chaleur (7) et un caisson de climatisation (13), le troisième échangeur de chaleur (6) comprenant une première portion d'échange de chaleur (61) pour faire circuler un fluide frigorigène et une deuxième portion d'échange de chaleur (62) pour faire circuler un liquide de refroidissement, le deuxième échangeur de chaleur (4) étant situé dans le caisson de climatisation (13) ;
    le système de gestion thermique étant configuré de telle sorte qu'il comprend un mode refroidissement ; dans le mode refroidissement,
    une sortie du compresseur (1), la première portion d'échange de chaleur (61), le premier échangeur de chaleur (2), le premier dispositif d'étranglement (3), le deuxième échangeur de chaleur (4) et une entrée du compresseur (1) sont en communication pour former une première boucle de fluide frigorigène ; la deuxième portion d'échange de chaleur (62) et le quatrième échangeur de chaleur (7) sont en communication pour former une boucle de liquide de refroidissement (5) ; et le liquide de refroidissement dans la deuxième portion d'échange de chaleur (62) est capable d'absorber la chaleur du fluide frigorigène dans la première portion d'échange de chaleur (61) ; et
    dans lequel le quatrième échangeur de chaleur (7) est situé à l'extérieur du caisson de climatisation (13) ;
    le système de gestion thermique comprend en outre un cinquième échangeur de chaleur (10), un second dispositif d'étranglement (20) et un sixième échangeur de chaleur (30), le cinquième échangeur de chaleur (10) comprend une troisième portion d'échange de chaleur (11) et une quatrième portion d'échange de chaleur (12) capable d'échanger de la chaleur avec la troisième portion d'échange de chaleur (11), le sixième échangeur de chaleur (30) est situé dans le caisson de climatisation (13) ;
    le système de gestion thermique étant configuré de telle sorte qu'il comprend en outre un mode chauffage et déshumidification ; et
    dans lequel, dans le mode chauffage et déshumidification, la sortie du compresseur (1), la première portion d'échange de chaleur (61), le sixième échangeur de chaleur (30), le second dispositif d'étranglement (20), la troisième portion d'échange de chaleur (11), le premier échangeur de chaleur (2), la quatrième portion d'échange de chaleur (12) et l'entrée du compresseur (1) sont en communication pour former la deuxième boucle de fluide frigorigène ; et la sortie du compresseur (1), la première portion d'échange de chaleur (61), le sixième échangeur de chaleur (30), le premier dispositif d'étranglement (3), le deuxième échangeur de chaleur (4), la quatrième portion d'échange de chaleur (12) et l'entrée du compresseur (1) sont en communication pour former une troisième boucle de fluide frigorigène ;
    caractérisé en ce que le système de gestion thermique comprend en outre une vanne à quatre voies (40), la vanne à quatre voies (40) ayant un premier orifice (401), un deuxième orifice (402), un troisième orifice (403) et un quatrième orifice (404) ;
    dans lequel la première portion d'échange de chaleur (61) comprend une première entrée (611) et une première sortie (612) ; le premier échangeur de chaleur (2) comprend un premier orifice de raccordement (21) et un deuxième orifice de raccordement (22) ; le deuxième échangeur de chaleur (4) comprend un troisième orifice de raccordement (41) et un quatrième orifice de raccordement (42) ; le sixième échangeur de chaleur (30) comprend un cinquième orifice de raccordement (301) et un sixième orifice de raccordement (302) ; la troisième portion d'échange de chaleur (11) comprend un septième orifice de raccordement (111) et un huitième orifice de raccordement (112) ; et
    dans lequel la première entrée (611) est en communication avec la sortie du compresseur (1) ; la première sortie (612) est en communication avec le cinquième orifice de raccordement (301) ; le premier orifice (401) est en communication avec le sixième orifice de raccordement (302) ; le deuxième orifice (402) est en communication avec le premier orifice de raccordement (21) ; le deuxième orifice de raccordement (22) est en communication avec le septième orifice de raccordement (111) ; le huitième orifice de raccordement (112) est en communication avec une extrémité du second dispositif d'étranglement (20) ; le troisième orifice (403) est en communication avec l'autre extrémité du second dispositif d'étranglement (20) et en communication avec une extrémité du premier dispositif d'étranglement (3) ; le troisième orifice de raccordement (41) est en communication avec l'autre extrémité du premier dispositif d'étranglement (3) ; et le quatrième orifice de raccordement (42) et le quatrième orifice (404) sont en communication avec l'entrée du compresseur (1) par l'intermédiaire de la quatrième portion d'échange de chaleur (12).
  2. Système de gestion thermique selon la revendication 1, comprenant en outre un premier ventilateur (9) situé à l'extérieur du caisson de climatisation (13), le premier échangeur de chaleur (2) et le quatrième échangeur de chaleur (7) partageant le premier ventilateur (9) pour la dissipation de chaleur.
  3. Système de gestion thermique selon la revendication 1, comprenant en outre un cinquième échangeur de chaleur (10), le cinquième échangeur de chaleur (10) comprenant une troisième portion d'échange de chaleur (11) et une quatrième portion d'échange de chaleur (12) capable d'échanger de la chaleur avec la troisième portion d'échange de chaleur (11) ; dans lequel
    le système est configuré de telle sorte que,
    dans le mode refroidissement, la sortie du compresseur (1), la première portion d'échange de chaleur (61), le premier échangeur de chaleur (2), la troisième portion d'échange de chaleur (11), le premier dispositif d'étranglement (3), le deuxième échangeur de chaleur (4), la quatrième portion d'échange de chaleur (12) et l'entrée du compresseur (1) sont en communication pour former la première boucle de fluide frigorigène.
  4. Système de gestion thermique selon la revendication 1, comprenant en outre un second dispositif d'étranglement (20) et un sixième échangeur de chaleur (30), le sixième échangeur de chaleur (30) étant situé dans le caisson de climatisation (13) ;
    le système de gestion thermique étant configuré de telle sorte qu'il comprend en outre un mode chauffage ; dans le mode chauffage, la sortie du compresseur (1), la première portion d'échange de chaleur (61), le sixième échangeur de chaleur (30), le second dispositif d'étranglement (20), le premier échangeur de chaleur (2) et l'entrée du compresseur (1) sont en communication pour former une deuxième boucle de fluide frigorigène.
  5. Système de gestion thermique selon la revendication 1, comprenant en outre une vanne d'arrêt (50), une extrémité de la vanne d'arrêt (50) étant en communication avec la première sortie (612) et étant en communication avec le cinquième orifice de raccordement (301), l'autre extrémité de la vanne d'arrêt (50) étant en communication avec le premier orifice (401) et étant en communication avec le sixième orifice de raccordement (302).
  6. Système de gestion thermique selon la revendication 5, le système étant configuré de telle sorte que dans le mode refroidissement, la vanne d'arrêt (50) est ouverte ; et dans le mode chauffage et déshumidification, la vanne d'arrêt (50) est fermée.
  7. Système de gestion thermique selon la revendication 1, comprenant en outre un séparateur gaz-liquide (8), le quatrième orifice de raccordement (42) et le quatrième orifice (404) étant en communication avec une entrée du séparateur gaz-liquide (8), une sortie du séparateur gaz-liquide (8) étant en communication avec la quatrième portion d'échange de chaleur (12).
  8. Système de gestion thermique selon la revendication 4, comprenant en outre un clapet antiretour (60), le clapet antiretour (60) étant disposé en parallèle avec le second dispositif d'étranglement (20).
  9. Système de gestion thermique selon la revendication 8, le système étant configuré de telle sorte que, dans le mode refroidissement, le clapet antiretour (60) est ouvert et le second dispositif d'étranglement (20) est fermé ; et dans le mode chauffage, le clapet antiretour (60) est fermé et le second dispositif d'étranglement (20) est ouvert.
  10. Système de gestion thermique selon l'une quelconque des revendications 1 à 9, comprenant en outre une première branche qui est disposée en parallèle avec le troisième échangeur de chaleur (6), la première branche étant raccordée à la boucle de liquide de refroidissement (5), la première branche étant pourvue d'une vanne de régulation (80) ; dans lequel dans le mode refroidissement, la vanne de régulation (80) est fermée.
  11. Système de gestion thermique selon l'une quelconque des revendications 1 à 9, comprenant en outre un dispositif de pompage (52) et un composant fonctionnel qui nécessite une dissipation de chaleur, le dispositif de pompage (52) et le composant fonctionnel étant disposés dans la boucle de liquide de refroidissement (5).
  12. Système de gestion thermique selon la revendication 1, comprenant en outre un dispositif d'alimentation en communication avec la boucle de liquide de refroidissement (5) pour entraîner l'écoulement du liquide de refroidissement ; le premier échangeur de chaleur (2) étant situé à l'extérieur du caisson de climatisation (13).
  13. Système de gestion thermique selon la revendication 1, dans lequel la boucle de liquide de refroidissement (5) comprend un composant fonctionnel qui nécessite une dissipation de chaleur, et le composant fonctionnel comprend un moteur (51) et/ou une batterie.
EP20871421.2A 2019-09-30 2020-09-25 Système de gestion de chaleur Active EP3982059B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201910945514.7A CN112577213A (zh) 2019-09-30 2019-09-30 热管理系统
PCT/CN2020/117923 WO2021063272A1 (fr) 2019-09-30 2020-09-25 Système de gestion de chaleur

Publications (3)

Publication Number Publication Date
EP3982059A1 EP3982059A1 (fr) 2022-04-13
EP3982059A4 EP3982059A4 (fr) 2022-08-17
EP3982059B1 true EP3982059B1 (fr) 2024-05-15

Family

ID=75116906

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20871421.2A Active EP3982059B1 (fr) 2019-09-30 2020-09-25 Système de gestion de chaleur

Country Status (4)

Country Link
US (1) US20220243961A1 (fr)
EP (1) EP3982059B1 (fr)
CN (1) CN112577213A (fr)
WO (1) WO2021063272A1 (fr)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4517529B2 (ja) * 2000-07-21 2010-08-04 株式会社日本自動車部品総合研究所 ヒートポンプサイクル、加熱装置、車両用暖房装置、暖房装置および蒸気圧縮式冷凍サイクル
JP2002195677A (ja) * 2000-10-20 2002-07-10 Denso Corp ヒートポンプサイクル
JP4151236B2 (ja) * 2001-06-07 2008-09-17 三菱電機株式会社 流量制御装置及び空気調和装置
DE10201741A1 (de) * 2002-01-18 2003-08-07 Daimler Chrysler Ag Fahrzeug mit einer Klimatisierung und einer Wärmequelle
JP4232463B2 (ja) * 2003-01-09 2009-03-04 株式会社デンソー 空調装置
WO2007031274A1 (fr) * 2005-09-12 2007-03-22 Behr Gmbh & Co. Kg Echangeur thermique, notamment refroidisseur d'air de suralimentation ou refroidisseur de gaz d'echappement pour un moteur a combustion interne d'un vehicule automobile
FR2971047B1 (fr) * 2011-02-01 2013-01-11 Peugeot Citroen Automobiles Sa Echangeur thermique reversible, procede de fonctionnement, utilisation et vehicule muni d'un tel echangeur.
KR101416357B1 (ko) * 2012-09-07 2014-07-08 현대자동차 주식회사 차량용 히트펌프 시스템 및 그 제어방법
CN109140815B (zh) * 2017-06-27 2020-09-25 杭州三花研究院有限公司 一种热管理系统及一种流量控制装置
CN109140816B (zh) * 2017-06-27 2020-07-17 杭州三花研究院有限公司 一种热管理系统
US11267315B2 (en) * 2017-10-02 2022-03-08 Marelli Cabin Comfort Japan Corporation Air-conditioning device
WO2019238129A1 (fr) * 2018-06-14 2019-12-19 杭州三花研究院有限公司 Système de pompe à chaleur

Also Published As

Publication number Publication date
EP3982059A4 (fr) 2022-08-17
WO2021063272A1 (fr) 2021-04-08
EP3982059A1 (fr) 2022-04-13
US20220243961A1 (en) 2022-08-04
CN112577213A (zh) 2021-03-30

Similar Documents

Publication Publication Date Title
CN112092566B (zh) 一种热管理系统
US11167620B2 (en) Thermal management system
US11912100B2 (en) Thermal conditioning circuit
JP7354580B2 (ja) 冷却水回路
CN104515323A (zh) 用于车辆的热泵系统
CN113173050B (zh) 热管理系统
CN112428767B (zh) 车辆热管理系统
CN111152622B (zh) 汽车空调系统
CN113173049B (zh) 热管理系统
US11358438B2 (en) Automotive air conditioning system
JP2005299935A (ja) 空気調和装置
JP4055739B2 (ja) 車両用空調装置
KR101172542B1 (ko) 차량 공조장치용 에어사이클
KR20210107361A (ko) 차량용 냉난방 시스템
CN210951942U (zh) 热管理系统
KR20220085243A (ko) 차량용 냉각 시스템
EP3982059B1 (fr) Système de gestion de chaleur
US20230356564A1 (en) Thermal management system with improved working efficiency of compressor
KR20090117055A (ko) 버스용 천정형 공기조화장치
KR20220033592A (ko) 차량용 히트펌프 시스템
CN109927509B (zh) 用于车辆的整车热管理系统及具有其的车辆
KR100613502B1 (ko) 히트 펌프식 공기조화기
US20240100909A1 (en) Thermal conditioning system
KR100624811B1 (ko) 리시버 냉매 순환 장치
CN118163567A (zh) 热管理系统

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20211220

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

A4 Supplementary search report drawn up and despatched

Effective date: 20220719

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 40/06 20060101ALI20220713BHEP

Ipc: B60H 1/00 20060101ALI20220713BHEP

Ipc: F24F 3/153 20060101ALI20220713BHEP

Ipc: F25B 5/02 20060101ALI20220713BHEP

Ipc: F25B 49/02 20060101ALI20220713BHEP

Ipc: F25B 41/26 20210101ALI20220713BHEP

Ipc: F25B 41/20 20210101ALI20220713BHEP

Ipc: F25B 40/04 20060101ALI20220713BHEP

Ipc: F25B 25/00 20060101ALI20220713BHEP

Ipc: F25B 6/04 20060101ALI20220713BHEP

Ipc: F25B 13/00 20060101AFI20220713BHEP

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 40/06 20060101ALI20231211BHEP

Ipc: B60H 1/00 20060101ALI20231211BHEP

Ipc: F24F 3/153 20060101ALI20231211BHEP

Ipc: F25B 5/02 20060101ALI20231211BHEP

Ipc: F25B 49/02 20060101ALI20231211BHEP

Ipc: F25B 41/26 20210101ALI20231211BHEP

Ipc: F25B 41/20 20210101ALI20231211BHEP

Ipc: F25B 40/04 20060101ALI20231211BHEP

Ipc: F25B 25/00 20060101ALI20231211BHEP

Ipc: F25B 6/04 20060101ALI20231211BHEP

Ipc: F25B 13/00 20060101AFI20231211BHEP

INTG Intention to grant announced

Effective date: 20240103

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602020031099

Country of ref document: DE