WO2021048095A1 - Module compact de régulation de la température d'un véhicule motorisé - Google Patents

Module compact de régulation de la température d'un véhicule motorisé Download PDF

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Publication number
WO2021048095A1
WO2021048095A1 PCT/EP2020/075028 EP2020075028W WO2021048095A1 WO 2021048095 A1 WO2021048095 A1 WO 2021048095A1 EP 2020075028 W EP2020075028 W EP 2020075028W WO 2021048095 A1 WO2021048095 A1 WO 2021048095A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
coolant
compact module
channel plate
valve
Prior art date
Application number
PCT/EP2020/075028
Other languages
German (de)
English (en)
Inventor
Thomas Börnchen
Willi Parsch
Guido Koch
Original Assignee
Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg
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 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg filed Critical Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg
Priority to CN202080063550.1A priority Critical patent/CN114502396B/zh
Publication of WO2021048095A1 publication Critical patent/WO2021048095A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00357—Air-conditioning arrangements specially adapted for particular vehicles
    • B60H1/00385—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00485—Valves for air-conditioning devices, e.g. thermostatic valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00507—Details, e.g. mounting arrangements, desaeration devices
    • B60H1/00557—Details of ducts or cables
    • B60H1/00571—Details of ducts or cables of liquid ducts, e.g. for coolant liquids or refrigerants
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • B60H1/3217—Control means therefor for high pressure, inflamable or poisonous refrigerants causing danger in case of accidents
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3226—Self-contained devices, i.e. including own drive motor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32284—Cooling devices using compression characterised by refrigerant circuit configurations comprising two or more secondary circuits, e.g. at evaporator and condenser side
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3229—Cooling devices using compression characterised by constructional features, e.g. housings, mountings, conversion systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features

Definitions

  • the invention relates to a compact module for temperature control of a motor vehicle, having a refrigerant circuit for guiding a refrigerant, with an electric refrigerant compressor and with two heat exchangers as well as with an expansion valve.
  • Thermal management of a motor vehicle is understood here and below in particular to mean thermal management or conditioning, that is to say heating or cooling, of vehicle components and / or the passenger or vehicle interior.
  • a refrigerant circuit is often provided as the primary circuit for temperature control, in which a refrigerant is performed as a heat transfer medium (refrigerant tel Vietnameselauf).
  • the refrigerant for example R-134a (1, 1, 1, 2-tetrafluoroethane) or R-744 (carbon dioxide), is heated in a first heat exchanger (evaporator, chiller) and compressed by means of a (refrigerant) compressor, whereby the refrigerant then emits the absorbed heat again via a second heat exchanger (condenser, condenser) before it is again routed to the first heat exchanger via a throttle (expansion valve, expansion device).
  • R-134a 1, 1, 2-tetrafluoroethane
  • R-744 carbon dioxide
  • This refrigerant or primary circuit is regularly coupled with one or more secondary circuits, which are typically designed as coolant circuits.
  • a coolant for example water and glycol
  • the secondary circuits are, for example, coupled to the vehicle components and to a vehicle air conditioning system.
  • Electrically or electromotive driven or drivable motor vehicles such as for example electric or hybrid vehicles, usually comprise an electric motor as an electric drive system with which one or both vehicle axles can be driven.
  • the electric motor is typically coupled to an in-vehicle (high-voltage) battery as an electrical energy store.
  • a battery is to be understood here and in the following in particular as a rechargeable, electrochemical secondary battery, for example an accumulator.
  • Such electric motors as electric drive machines generate comparatively little waste heat during operation, which means that, compared to internal combustion engines, only a low cooling capacity is required for temperature control. However, only a small amount of heating power is available, which could be used to control the temperature of other components and / or the vehicle interior. This means, for example, that additional electrical heaters are required to ensure reliable temperature control of the motor vehicle.
  • Each vehicle component coupled to the secondary circuits can act as both a heat source and a heat sink, depending on the operating situation. As a result, by specifically influencing the heat carrier flows of the primary and secondary circuits, it is possible to reduce energy expenditure for the temperature control of the motor vehicle, which improves the range of the motor vehicle. For example, electrical components and the battery are cooled and this heat is used to warm the passenger compartment.
  • the primary circuit and at least sections of the secondary circuits can be designed, for example, as a so-called compact module.
  • compact modules of this type have numerous pipe and / or hose sections for coupling the components of the primary circuit, which results in a comparatively complex structure with high assembly costs.
  • the invention is based on the object of specifying a particularly suitable compact module for controlling the temperature of a motor vehicle.
  • the assembly effort in the primary circuit, in particular in the coupling between the primary and secondary circuit is to be reduced.
  • the compact module according to the invention is provided for temperature control of a motor vehicle, in particular an electrically driven or drivable motor vehicle, such as an electric or hybrid vehicle, and is suitable and set up for this.
  • the compact module has a refrigerant circuit as the primary circuit, in which a refrigerant is guided.
  • the refrigerant circuit which is as simple as possible, has an electric refrigerant compressor, for example a scroll compressor, and two heat exchangers and an expansion valve.
  • the heat exchangers are designed as plate heat exchangers, for example.
  • the simple structure of the primary circuit enables the refrigerant charge to be minimized for a given output.
  • the compact module has a duct plate and a modular valve unit coupled therewith.
  • the channel plate is designed as an approximately plattenförmi ges component with integrated channels or lines.
  • Käl teschkanäle of the refrigerant circuit and coolant channels for guiding a coolant are integrated in the channel plate.
  • the valve unit is designed as a connection area for coolant lines of the motor vehicle. A particularly suitable compact module is thereby formed.
  • the valve unit has an integrated secondary circuit topology, which means that the topology for a secondary circuit system is essentially completely integrated in the valve unit, so that only the coolant lines to and from the vehicle components need to be connected. This enables a simple and scalable structural implementation of the specified, scalable secondary circuit topology.
  • the refrigerant compressor and the heat exchanger as well as the expansion valve are arranged on or on the channel plate.This enables simple and compact placement on the one hand and a sealing connection of all media-carrying components of the primary circuit on the channel plate on the other.
  • the refrigerant compressor is preferably coupled to the channel plate as rigidly or rigidly as possible, so that due to the comparatively high structural weight, vibration damping is implemented to reduce or dampen vibrations or vibrations occurring during operation.
  • the compact module is preferably flexibly or elastically connected to a vehicle structure of the motor vehicle.
  • the channel plate is arranged on the front side of the refrigerant compressor.
  • the refrigerant compressor is preferably designed as an integrated compressor variant in which all media interfaces are arranged on the end face to the channel plate.
  • the refrigerant compressor and the heat exchangers are arranged on opposite flat sides of the channel plate.
  • the valve unit is preferably arranged on the side of the refrigerant compressor.
  • the refrigerant compressor and the valve unit are suitably arranged stacked along a flute direction on the channel plate.
  • at least one pump coupled to the coolant channels is provided for conveying the coolant in the secondary circulation system, which pump is arranged on the channel plate, preferably on the side of the heat exchanger.
  • the coolant channels and the refrigerant channels of the channel plate are guided in one plane without crossing. This means that the channels are run next to one another, with only the connection areas of the channels protruding from the plane. As a result, a channel plate that is particularly simple in terms of design and that is easy to manufacture is realized.
  • valve unit has a number of valve modules lined up at the end.
  • a valve module is preferably provided for each vehicle component to be connected.
  • a valve module is understood here to mean, in particular, a modular valve assembly.
  • the or each valve module has two 3-2-way valves, which are preferably switchable with two (single-acting) electromagnets.
  • the valve bodies of the two way valves are suitably coupled to one another. This means that the valve module is designed as a double 3-2-way switch valve.
  • the refrigerant compressor has jacket cooling (on the front / compressor head side), which is coupled to the channel plate.
  • the jacket cooling is thus in particular in a direct exchange with the channel plate.
  • the jacket cooling or cooling jacket of the refrigerant compressor is provided in particular for cooling or cooling power electronics and / or an electric motor and / or a compressor head of the refrigerant compressor, and is suitable and set up for this.
  • the refrigerant of the primary circuit is designed as a natural refrigerant, in particular as propane. Natural refrigerants have high thermodynamic properties and a low greenhouse potential. Natural refrigerants are still comparatively inexpensive, but they are also highly flammable and can form explosive mixtures with atmospheric oxygen.
  • the compact module has a tight, in particular fluid- or gas-tight, housing in which the refrigerant circuit and the channel plate as well as the valve unit are accommodated.
  • the compact module in particular the refrigerant or primary circuit, is hermetically or semi-hermetically sealed or encapsulated.
  • the housing is preferably not pressure-resistant, which means that the housing is made of a flexible or elastic material, for example.
  • the housing is designed in particular as a hood or membrane or fabric (fabric).
  • a shaped body or granulate is arranged as a space filler in the housing, whereby an explosive atmosphere in the housing is reduced in the event of a fault.
  • a ventilation opening is preferably provided on an upper side of the housing and a ventilation opening is provided on an opposite underside.
  • the underside faces a vehicle floor, with a channel preferably being provided through which an atmosphere in the housing can be safely discharged to the vehicle environment via the ventilation opening before an explosive or flammable mixture results inside the housing .
  • an additional blower or a fan is provided here, which, if necessary, generates an air flow from the ventilation opening to the ventilation opening. This makes it possible to “flush” the housing with air.
  • the fan is therefore intended for a controlled supply of fresh air, as well as being suitable and set up for it. This ensures a non-explosive atmosphere inside the housing.
  • a cold gas generator filled with inert gas can optionally be provided in the housing for accelerated dilution of the outflowing refrigerant and thus for an additional increase in safety.
  • FIG. 1 shows a schematic illustration of a cooling device of a motor vehicle
  • FIG. 2 shows a perspective illustration of a compact module of the cooling device in a first embodiment with a view of an upper side
  • FIG. 3 shows a perspective illustration of the compact module according to FIG. 2 with a view of an underside
  • Fig. 4 is a perspective view of the compact module in a second imple mentation form
  • Fig. 5 is a perspective view of a channel plate of the compact module
  • FIG. 6 shows a perspective view of a cover plate of the channel plate
  • FIG. 7 shows a perspective sectional illustration of the compact module according to FIG. 4
  • FIG. 8 shows a perspective illustration of a refrigerant compressor of the compact module with a view of an end face
  • FIG. 9 shows a section of a valve unit of the compact module in a perspective view
  • 10 shows a schematic representation of an explosion protection of the compact module in a first embodiment
  • FIG. 11 shows a schematic representation of the explosion protection of the compact module in a second embodiment.
  • the cooling device 2 is suitable and set up for vehicle temperature control, ie for temperature control or thermal management of at least one passenger compartment or vehicle interior 8 and vehicle assemblies / components 4, 6, 10 of the motor vehicle.
  • the cooling device 2 has an outside air duct 12 and a compact module 14 coupled to it.
  • the compact module 14 shown in FIG. 1 as a circulatory system has a primary circuit 16 and a secondary circuit system 18 coupled thereto.
  • the primary circuit 16 is designed as a refrigerant circuit for a refrigerant, in particular for a natural refrigerant such as propane.
  • the primary circuit 16 has an electronic expansion valve 20 and an electric refrigerant compressor 22 as well as two heat exchangers 24, 26.
  • the refrigerant compressor 22 is designed, for example, as a scroll compressor, and preferably has a cooling jacket as jacket cooling 28, which is coupled to the secondary circuit system 18.
  • the refrigerant in particular gaseous, is compressed (compressed) by the refrigerant compressor 22, the following (high-temperature) heat exchanger 24 acts as a condenser or liquefier, releasing heat from the refrigerant. Then the particularly liquid refrigerant is expanded via the expansion valve 20 due to the change in pressure. In the downstream (low-temperature) heat exchanger 26, which acts as a chiller or evaporator, the refrigerant evaporates while absorbing heat at a low temperature.
  • the heat exchangers 24, 26 form the interfaces with the secondary circuit system 16 designed as a coolant circuit.
  • the coolant of the secondary circuit system 16 is, for example, water and / or glycol.
  • the coolant lines of the heat exchanger 24 are routed to two heat exchangers 30, 32 of the outside air duct 12 designed as external heat exchangers.
  • the coolant is passed from the heat exchangers 30, 32 to an electronic flow control mixing valve 34.
  • the secondary circuit system 18 has two coolant or secondary circuits 18a, 18b, a high or medium temperature circuit 18a coupled to the heat exchanger 24 and a low temperature circuit 18b coupled to the heat exchanger 26.
  • the secondary circuit system 18 accordingly has two feed lines 36, 38 and two return lines 40, 42.
  • the flow 36 is a high or medium temperature flow, wherein the return 40 is the associated high or medium temperature return of theisserschulniklau fes 18a.
  • the flow 38 is correspondingly a low-temperature flow, the return 42 forming the associated low-temperature return of the coolant circuit 18b.
  • the coolant pump 44 is designed as an electric high- or medium-temperature coolant pump, which conveys the coolant from the return 40 to the heat exchanger 24.
  • the coolant pump 46 is designed accordingly as an electrical low-temperature coolant pump which conveys the coolant from the return 42 in the direction of the heat exchanger 26.
  • On the secondary circuit system 18, or on the supply and return lines 36, 38, 40, 42 are the units or components to be tempered 4,
  • a coolant heat storage device 10 as a thermal battery
  • a cooling heat exchanger 48 as well as a heating heat exchanger 50 and a surface temperature control element 52 designed as a headliner, for example, for controlling the temperature of the vehicle interior 8 are connected to the coolant circuit 18 in this exemplary embodiment.
  • the traction drive 4 has, for example, an electrical braking resistor, an inverter and a charging device.
  • the coolant heat storage 10, the battery 8 and the surface temperature control element 52 and the vehicle interior 8 preferably each have a high-quality thermal insulation.
  • the heat exchangers 48, 50 are coupled to a heating or air conditioning fan 54.
  • the heat exchangers 48, 50 and the air conditioning fan 54 are preferably part of an air conditioning device 56 of the motor vehicle.
  • switching valves 58 in particular electric double 3/2-way switching valves, are provided.
  • the heating heat exchanger 50 is coupled directly to the flow and return lines 36, 40.
  • An electronic flow control valve 60 is provided between the components 4, 10, 48, 52 and the reversing valve outlets guided to the return lines 40, 42, as well as at the outlet of the heating heat exchanger 50.
  • the switching valves 58 and the flow control valves 60 are provided with reference numerals in the figures merely by way of example.
  • the coolant lines of the battery 6 are coupled to the cooling jacket 28 of the refrigerant compressor 22 via an electronic flow regulating valve 62.
  • An electric coolant mixing pump 64 is arranged between the coolant lines leading to the heat exchanger 26, by means of which the coolant can be conveyed, in particular to the battery 6, in order to increase the cooling performance, for example in a charging or fast charging operation.
  • An electronic flow control valve 66 is provided between the flow 36 and the return 40.
  • the inlet and outlet coolant lines of the heat exchanger 24 are coupled or can be coupled by means of a controllable bypass line 68, which is arranged between the flow control mixing valve 34 and the outlet of the coolant pump 44.
  • the outside air duct 12 has, for example, two parallel air ducts 70, 72 which are each led from an inlet 70a, 72a to an outlet 70b, 72b, the inlets 68a, 70a can each be released as required by means of an actively controllable blind 74.
  • the heat exchanger 32 and an axial fan 76 arranged behind it are arranged in the air duct 70.
  • the air duct 72 has the heat exchanger 30 and a radial fan 78 arranged behind it.
  • the cooling device 2 and the compact module 14 are coupled to a controller (that is to say a control unit).
  • the controller is generally provided - in terms of program and / or circuitry - for performing thermal management, as well as being suitable and designed for it.
  • the controller controls and / or regulates the storage of thermal energy in the coolant heat storage 10, the cooling flow to all devices 4, 8, 10, 12, 14, 48, 50, 52 as well as the heat energy exchange to the environment and the waste heat management at a fast - or ultra-fast charging process of the battery 6.
  • the controller is at least essentially formed by a microcontroller with a processor and a data memory in which the functionality for performing thermal management is implemented in the form of operating software (firmware), so that the method - possibly in interaction with a device user - is carried out automatically when the operating software is executed in the microcontroller.
  • the controller can alternatively also be formed by a non-programmable electronic component, such as an application-specific integrated circuit (ASIC), in which the functionality for performing thermal management is implemented with circuitry.
  • ASIC application-specific integrated circuit
  • the controller exchanges information and data with a vehicle control of the motor vehicle with regard to the vehicle status (ambient temperature, position, ...), the status of the power units (battery, traction drive, air conditioning), and the operating mode (heating, cooling, charging,. ..) out.
  • the controller controls and / or regulates the outside air duct 12 by controlling and / or regulating the speed of the fans 76, 78 and the position of the blinds 74.
  • the controller also controls and / or regulates the operation of the compact module 14 and the connected components, for example by varying the speed of the refrigerant compressor 22 or the opening of the expansion valve 20.
  • the controller detects and monitors the pressures of the circuits 16, 18 and the operating temperature of the components, the coolant and the refrigerant.
  • the cooling device 2 can be operated in several operating modes. Eight different modes of operation of the cooling device 2 for controlling the temperature of the motor vehicle are explained in more detail below by way of example.
  • the first operating mode is suitable, for example, in summer at ambient temperatures of around 30 ° C when driving on the highway or uphill with air conditioning.
  • the coolant circuit 18a here comprises the heat exchanger 24, the heat exchangers 30, 32, the flow control mixing valve 34, the traction drive 4, the flow control valve 60 and the coolant pump 44.
  • coolant in the coolant circuit 18a is conveyed from the heat exchangers or external heat exchangers 30, 32 to the traction drive 4 .
  • the heat exchanger 32 here gives heat me from the traction drive 4, the heat exchanger 30 independently dissipating heat from the battery 6 and the vehicle interior 8.
  • the electric coolant pump 64 regulates the coolant flow temperature for the battery 6 and the jacket cooling 28 of the refrigerant compressor 22, for example to 20 ° C. to 30 ° C. (degrees Celsius).
  • the second operating mode is suitable, for example, in summer at ambient temperatures of around 30 ° C when driving downhill with an electric brake and thermal buffering as well as active air conditioning.
  • the heat exchanger 32 in turn emits heat from the traction drive 4, the heat exchanger 30 independently dissipating heat from the vehicle interior 8.
  • Thedemit teltude teltude 87 absorbs additional heat from the braking resistor of the traction drive 4 to buffer the thermal load peak. With reduced or stopped air conditioning (comfort) and limited heat output via the heat exchanger 32 (due to the limitation of the outlet air temperature, e.g. to 60 °
  • the heat absorption by the battery 6 can be increased (driving performance, safety), e.g. B. up to 95 ° C.
  • the third operating mode is suitable, for example, in summer at ambient temperatures of around 30 ° C with (ultra) fast charging with thermal buffering and air conditioning.
  • heat is given off from the battery 6 and the vehicle interior 8 via the heat exchanger 30.
  • the coolant heat store 10 also absorbs heat to buffer the thermal load peak.
  • the heat exchanger 30 (further) emits heat from the battery 6 and the vehicle interior 10, derating or reducing the charging current if necessary. If necessary, in the case of a cooled traction drive 4, this can also be loaded.
  • the fourth operating mode is suitable, for example, in winter at ambient temperatures of around -20 ° C when driving on the motorway / uphill with battery cooling and passenger compartment heating.
  • the coolant pump 46 feeds waste heat from the traction drive 4 via the inner heat exchanger 26 in the primary circuit 16.
  • the electric refrigerant compressor 22 generates additional heat, the total heat at a higher temperature level via the furnishedtau shear 24 is released again (heat pump function).
  • the coolant pump 44 supplies the vehicle interior 10 with a flow temperature of z. B. 60 ° C.
  • the battery 6 generates some heat loss and is slightly cooled; reheating is also possible.
  • the fifth operating mode is suitable, for example, in winter at ambient temperatures of around -20 ° C with (ultra) fast charging with thermal buffering and passenger compartment heating.
  • the temperature of the battery 6 is here on z. B. 30 ° C to 50 ° C increased.
  • the heat exchanger 30 emits heat from the battery 6, so that the flow temperature for the maintenance air conditioning is still 50 ° C., for example.
  • the cooling heat exchanger 48 can be connected in parallel as a second fleece heat exchanger 50 in order to enlarge the entire heat-exchanging network area in the air-conditioning unit 56.
  • the coolant heat accumulator 10 can also absorb heat loss from the battery 6, so that the charging phase is extended without power throttling. The heat stored in the coolant heat accumulator 10 can then be used for heating when the vehicle continues.
  • the sixth operating mode is suitable for example in spring or autumn with ambient temperatures of around 5 ° C with dehumidification and passenger compartment heating.
  • outside air and / or recirculated air from the vehicle interior 10 is cooled in the cooling heat exchanger 48 and part of the moisture is thereby withdrawn.
  • the heating heat exchanger 50 heats the air again to an inflow temperature of, for. B. 55 ° C.
  • the foundedntemperierele element 52 increases the heat flow into the cabin at the lowest possible and thus more efficient flow temperature.
  • An imbalance caused by the working point between the cooling and heating power requirements can be compensated for at times by the coolant heat accumulator 10.
  • the seventh operating mode is suitable, for example, in summer at ambient temperatures of about 30 ° C.
  • the coolant heat storage 10 and the vehicle interior 8 are preferably cooled relatively slowly (with an early start of the preconditioning). In particular, there is sequential cooling starting with the heat source with insulation of higher quality, i.e. first the coolant heat storage 10 and then the vehicle interior 8. A slight cooling jacket cooling of the refrigerant compressor 22 and the battery 6 is also possible here.
  • the coolant mixing pump 64 preferably circulates the coolant through the battery 6 for a very homogeneous cell temperature distribution.
  • the stored "cold" in the coolant heat storage 10 is used for air conditioning during the first z. B. usable 20 min / 20 km after driving off.
  • the eighth operating mode is suitable, for example, in winter at ambient temperatures of about -20 ° C. with preconditioning of the battery 6, the coolant heat accumulator 10 and the passenger compartment on the network.
  • the refrigerant compressor 22 and the primary circuit 16 are in triangular operation, this means that refrigerant is single-phase gaseous in operation, without condensation and evaporation.
  • the electrical input power of the refrigerant compressor is almost completely converted into heat flow and transferred into the coolant via the heat exchanger 24, which means the coefficient of performance (COP) is somewhat less than one.
  • the refrigerant compressor 22 can thus replace a separate auxiliary heater (e.g. HV-PTC heater).
  • sequential heating takes place, starting with the battery 6, until a charging temperature is reached and a charging process begins, then heat sources with insulation of higher quality, this means first the coolant heat accumulator 10 and then the vehicle interior 8.
  • the heat in the coolant heat accumulator 10 is for Heating during the first z. B. usable 20 min / 20 km after driving off.
  • the refrigerant or primary circuit 16 of the compact module 14 is designed as simple as possible, and essentially only has the refrigerant compressor 22 and the heat exchangers 24, 26 and the expansion valve 20 and these connect dende refrigerant channels.
  • the topology of the secondary circuit system 18 is here essentially integrated or mapped in a valve unit (coil hub) 80 of the compact module 14 designed as a control block, in particular in the valve unit 80 and a channel plate 82 coupled to it (FIG. 4).
  • the channel plate 82 of the compact module 14 is designed as an approximately plate-shaped component with integrated channels or lines.
  • refrigerant channels 84 of the refrigerant circuit 18 and coolant channels 86 for guiding the cooling medium are integrated into the channel plate 82.
  • FIGS. A first exemplary embodiment for the channel plate 82 of the compact module 14 is shown in FIGS.
  • the refrigerant compressor 22, the heat exchangers 24, 26 and the expansion valve 20 are arranged on a common plan side or top side of the channel plate 82.
  • the channel plate 82 designed as a die-cast part, for example, has channels 84, 86 designed as embossings or depressions on the underside facing away from the components 20, 22, 24, 26.
  • the channels 84, 86 are covered by means of a cover plate 88, shown semi-transparently in FIG. 3.
  • a second exemplary embodiment for the compact module 18 is explained in more detail below with reference to FIGS. 4 to 9.
  • the refrigerant compressor 22 shown in more detail in FIG. 4 and in FIG. 7 is designed as an electromotive scroll compressor.
  • the refrigerant compressor 22 has an electric (electromotive) drive 90 with a stator 92 and a rotor 94 and a compressor head 96 coupled to this.
  • a center plate 98 is provided as a bearing plate or mechanical interface, by means of which the Ver sealing head 96 is connected to the drive 90 in terms of drive technology.
  • the Centerpla te 98 forms an intermediate wall between a drive housing 100 and a Seal head housing 102.
  • a housing section of the drive housing 102 on the compressor head side is designed as a motor housing for receiving the electric motor formed by the stator 92 and the rotor 94.
  • an electronics housing with power electronics 104 controlling the electric motor is provided on the front side of the motor housing.
  • the drive housing 102 has a connection section 106 for making electrical contact between the power electronics 104 and an on-board network of the motor vehicle.
  • the refrigerant drive 22 has a (refrigerant) inlet or (refrigerant) inlet 108 for connection to the refrigerant circuit 16 and a (refrigerant) outlet 110.
  • the inlet 108 is integrally formed in a region of the motor housing facing the electronics housing, and is guided to the channel plate 82 by means of a low-pressure line 112.
  • the outlet 110 is integrally formed on a bottom of a compressor head housing 102, and is guided to the channel plate 82 with a high-pressure line 114.
  • the inlet 108 forms the low-pressure or suction side (suction gas side) and the outlet 110 the high-pressure or pump side (pump side) of the refrigerant compressor 22.
  • the refrigerant compressor 22 is designed as an integrated compressor variant in which all media interfaces are arranged on the end face of the channel plate 82. This means that the inlet 108 and the outlet 110 are arranged in the area of the compressor head 96.
  • the refrigerant compressor 22 has a common housing 116 for the compressor head 96 and the electric motor, which is encompassed by the jacket cooling 28.
  • the jacket cooling 28 is designed here as a cavity 117 through which the coolant flows and which surrounds the housing 116.
  • the jacket cooling is 28 or the cavity 117 is divided into a coolant flow 117a and a coolant return 117b.
  • the jacket cooling 28 of the refrigerant compressor 22 is provided in particular for cooling or cooling the power electronics 104 and / or the electric motor and / or the compressor head 96, as well as being suitable and set up for this.
  • the rotor 94 of the particularly brushless electric motor of the drive 90 is coupled in a rotationally fixed manner to a motor shaft 118.
  • the compressor head 96 has a movable scroll (scroll part), not shown in detail, which is coupled to the motor shaft 118 of the electric motor by means of an anti-rotation mechanism.
  • the movable scroll is driven orbiting during operation of the refrigerant compressor 22.
  • the compressor head 96 also has a rigid, that is to say fixed to the housing, stationary scroll (scroll part).
  • the two scrolls (scroll parts) interlock with their helical or spiral-shaped spiral walls (scroll walls, scroll spirals), which protrude axially from a respective base plate.
  • the stationary scroll also has a circumferential boundary wall forming the outer circumference.
  • the channel plate 82 in this embodiment of the compact module 14 is arranged on the front side of the refrigerant compressor 22.
  • the expansion valve 20, the refrigerant compressor 22, and the valve unit 82 are arranged one above the other or next to one another on a first flat side of the channel plate 82, hereinafter referred to as the top, with the heat exchangers 24, 26 and the pumps 44, 46 on the opposite side, as Designated underside, plan side of the channel plate 82 are arranged on.
  • the pumps 44, 46 are carried out, for example, as circulating pumps.
  • the underside of the channel plate 82 is essentially formed by the cover plate 88 shown individually in FIG. 6.
  • the channel plate 82 in this embodiment has seven integrated coolant channels 86a, 86b, 86c, 86d, 86e, 86f, 86h and four refrigerant channels 84a, 84b, 84c, 84d, which are guided in a plane without crossing.
  • the coolant channels 86a, 86b, 86c are assigned to the high or medium temperature circuit 18a and the coolant channels 86d, 86e, 86f are assigned to the low temperature circuit 18b of the secondary circuit system 18.
  • the coolant channel 86a is for the forward flow from the heat exchanger 24, wherein the coolant channel 86b carries the coolant to the pump 44, and the coolant channel 86c removes the coolant from the pump 44.
  • the coolant channel 86d is for the forward flow of the heat exchanger 26, the coolant channel 86e leading the coolant to the pump 46, and the coolant channel 86f leading the coolant away from the pump 46.
  • the coolant channel 86h is the return line to the heat exchanger 24.
  • the refrigerant duct 84a leads the refrigerant from the expansion valve 20 to the heat exchanger or evaporator 26.
  • the refrigerant duct 84b is arranged coaxially to this, which leads the refrigerant from the heat exchanger 24 to the expansion valve 20 after cooling.
  • the refrigerant duct 84c leads the refrigerant after the compression from the refrigerant compressor 22 to the heat exchanger or condenser 24, the refrigerant duct 84d leading the refrigerant from the heat exchanger 26 to the refrigerant compressor 22 after evaporation.
  • the channel plate 82 of the compact module 14 realizes an end-face flow and return for refrigerant and coolant.
  • the structure of the valve unit 80 is explained in more detail below with reference to FIGS. 4, 7 and 9.
  • the modular valve unit 80 is designed as a connection area for the coolant lines of the vehicle units and components 4, 6, 10, 48, 50, 52.
  • the valve unit 80 has four valve modules 120 lined up next to one another, the frontal outermost valve module 120 being shown partially opened or cut in the figures.
  • the individual valve modules 120 here form the double 3-2-way switchover valves 58.
  • a flow and a return connection are provided, which are controlled with the respectively assigned 3-2 -way valve.
  • the approximately qua der-shaped valve module 120 has two interacting electromagnetic coils 122 on the opposite end faces for adjusting a respectively assigned valve body 124.
  • valve bodies 124 are each carried on a valve rod 126, the valve rods 126 having a touch or pressure contact 128.
  • the valve rods 126 are ras tend in their end positions.
  • the valve modules 120 are penetrated in the row direction by four coolant channels, which form the flow and return lines 36, 38, 40, 42 of the secondary circuit system 18.
  • the flow cross-sections of the supply and return lines 36, 38, 40, 42 of the individual valve modules 120 are designed to be variable in steps with transitions.
  • the components 122, 124, 126, 128 of the valve modules 120 are provided with reference symbols in the figures merely by way of example.
  • the refrigerant of the refrigerant circuit 16 is propane. Since the primary circuit 16 of the compact module 14 thus carries a flammable refrigerant, the compact module 14 is preferably designed with explosion protection or explosion protection. Two explosion protection devices of the compact module 14 are explained in more detail below with the aid of the schematic and simplified representations of FIGS. 10 and 11.
  • the compact module 14 is hermetically or semi-hermetically encapsulated or closed by means of a housing 130.
  • the secondary circuit system 18 shown in simplified form is in a heat exchange with the supply air 132 conducted by the heating / air conditioning fan 54 through the air conditioning unit 56.
  • the supply air or the air flow 132 is indicated in FIGS. 10 and 11 with arrows.
  • the housing 130 designed for example as a hood, encloses the primary circuit system boundary of the compact module 14 in a gas- or fluid-tight manner, the housing 130 having a ventilation opening 134 on a (housing) top side and a ventilation opening 136 on a (housing) bottom side.
  • the interior of the primary circuit 16 is in a normal operating or idle state of the cooling device 2 and with a suitable design, especially the static seals, is not to be regarded as a zone in terms of explosion protection, since the refrigerant concentration is always above the upper explosion limit (UEL). lies.
  • Zone 2 A space 138 enclosed by the housing 130 is to be regarded as Zone 2 in terms of explosion protection, since the refrigerant concentration is generally between 0% and the LEL, and therefore it is not to be expected that an explosive atmosphere will occur. If such an explosive atmosphere does occur, it is most likely only rarely and for a short period of time.
  • a flame retardant screen 140 extends over the vent 134 at the top of the housing 130 and forms the boundary between the inner zone 2 and the atmosphere outside.
  • the ventilation opening 136 on the underside is open, and the zone boundary runs essentially conically to the floor or ground 142 of the motor vehicle.
  • An air guiding section 144 is provided between the flame protection screen 140 and the fan 54.
  • An operating behavior is provided in which the fan 54 is switched on first and then the refrigerant compressor 22 in the primary circuit 16 is switched on with a time interval.
  • the fan 54 thus exchanges the standing undefined atmosphere in room 138 for non-explosive outside air by means of forced ventilation as primary explosion protection before and during compressor operation in order to prevent or avoid the formation of an explosive atmosphere in the housing 130.
  • a separate fan 146 is provided as part of the compact module 14.
  • the advantages of this variant are an additional separation of the compact module 14 from the passenger compartment 8 and the need for an air duct to be connected to the compact module 14 when installing the vehicle.
  • the fan 7 can be used as an intrinsically safe, i.e. H. Ignition energy-free fan, be formed.
  • the upper zone boundary of room 138 can also be ensured by a flap 148 or a sufficient distance between the fan 146 and the housing 130 instead of the flame protection screen 140.
  • a passive relief 150 in the primary circuit 16 is provided, in particular in the form of a rupture disc. If the overpressure of the bursting disc 150 is exceeded and it is triggered, a pressure drop occurs that can be used to trigger an ignition spark in that a membrane acts on a spring-loaded bolt, which exerts an impulse on a piezo crystal and generates a short-term, spark-forming high voltage (piezo lighter principle ). The spark thus ignites the outflowing refrigerant immediately after the bursting disc 150 has been triggered.
  • This safety device is preferably arranged in a section of the primary circuit 16 in which the refrigerant is always in the gas phase, in particular before or after the refrigerant compressor 22, and spatially close to the un-nic vent opening 136.
  • the rupture disk 150 is shown behind in front of and behind the refrigerant compressor 22, the position in front of the refrigerant compressor 22 being shown in dashed lines.
  • a particularly umbrella-shaped, bell-shaped or tubular flow guide piece 152 around the outlet opening on the underground ensures that the resulting high energy flame is formed in a controlled manner in the direction of the floor 142 under the motor vehicle.
  • the flow guide has a minimum cross-section and sufficient pressure and temperature resistance, so that the flame is stable until the refrigerant charge is completely emptied and then goes out.
  • This controlled burning avoids uncontrolled leakage and the formation of a pool with an explosive atmosphere over it, whereby a tertiary explosion protection is realized with regard to a reduction of the effects and the severity of damage.
  • the particular advantage of this mechanism is that its function is independent of a supply of electrical energy.
  • the compact module 14 is preferably integrated in a collision-protected area of the motor vehicle, in particular adjacent to the passenger compartment or vehicle interior 8 and the air conditioner 56. This advantageously shortens the heat-exchanging lines.
  • the integrity and tightness of the primary circuit 16 should be preserved in the event of deformation of the surrounding structure in the event of an impact.
  • the housing 130 is designed to be flexible or elastic, for example, so that it absorbs some of the energy from the collision through deformation.
  • an actively acting relief 154 in the primary circuit 16 is provided.
  • the actively acting relief 154 is triggered by a signal from a control unit.
  • the outflowing refrigerant is ignited by an ignition spark or a glow element that is fed from the vehicle electrical system.
  • the control unit evaluates the risk of loss of integrity for the primary circuit 16 due to an impending or ongoing collision on the basis of sensor data from a vehicle environment monitoring system. If the severity of the collision can make it likely that refrigerant will escape and an explosive atmosphere is created, it triggers active relief 154 by means of a signal. The triggering time is in particular shortly before or during a collision. The advantage is that electrical ignition is possible even with a low pressure difference between the refrigeration circuit 16 and the atmosphere.
  • the housing 130 can be used in addition to the acoustic encapsulation of the compact module 14 by measures in the material, shape and connections.
  • Air conditioning unit 58 Changeover valve 60 Flow control valve 62 Flow control mixing valve 64 Coolant mixing pump 66 Flow control valve 68 Bypass line 70 Air duct a inlet b outlet

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un module compact (14) pour réguler la température d'un véhicule motorisé, comprenant un circuit de fluide frigorigène pour guider un fluide frigorigène, un compresseur de fluide frigorigène électrique (22) et deux échangeurs de chaleur (24, 26) ainsi qu'une soupape de détente (20), et une plaque de canal (82) dans laquelle des canaux de fluide frigorigène du circuit de fluide frigorigène (16) et des canaux de fluide frigorigène pour guider un fluide frigorigène sont intégrés, et comprenant une unité de vanne modulaire (80) en tant que région de raccordement pour des conduits de fluide frigorigène du véhicule motorisé.
PCT/EP2020/075028 2019-09-09 2020-09-08 Module compact de régulation de la température d'un véhicule motorisé WO2021048095A1 (fr)

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CN114861973A (zh) * 2022-03-24 2022-08-05 三峡大学 一种计及多源因素的风力发电系统风险评估方法
US20220332162A1 (en) * 2021-04-19 2022-10-20 Hyundai Motor Company Integrated thermal management module for vehicle
WO2022253480A1 (fr) * 2021-06-02 2022-12-08 Volkswagen Aktiengesellschaft Module de commande de gestion thermique doté d'un dispositif de commande intégré
WO2022266945A1 (fr) * 2021-06-24 2022-12-29 浙江吉利控股集团有限公司 Appareil d'intégration de conduites de refroidissement à canaux multiples, module d'intégration de gestion thermique et véhicule électrique
EP4083480A3 (fr) * 2021-04-08 2023-01-25 Veritas Ag Systeme de soupape de fluide
WO2023031177A1 (fr) * 2021-08-31 2023-03-09 Volkswagen Aktiengesellschaft Dispositif de distribution d'agent de refroidissement pour un véhicule automobile et véhicule automobile équipé d'un dispositif de distribution d'agent de refroidissement
WO2023045355A1 (fr) * 2021-09-27 2023-03-30 浙江吉利控股集团有限公司 Système de gestion thermique, véhicule et procédé de gestion thermique
WO2023171921A1 (fr) * 2022-03-10 2023-09-14 Hanon Systems Système de climatisation pour un véhicule
FR3133435A1 (fr) * 2022-03-08 2023-09-15 Valeo Systemes Thermiques Plaque commune d’un module thermique d’un circuit de fluide réfrigérant
FR3133432A1 (fr) * 2022-03-08 2023-09-15 Valeo Systemes Thermiques Plaque commune d’un module thermique d’un circuit de fluide réfrigérant
FR3133434A1 (fr) * 2022-03-08 2023-09-15 Valeo Systemes Thermiques Plaque commune d’un module thermique d’un circuit de fluide réfrigérant
DE102022108697A1 (de) 2022-04-11 2023-10-12 Audi Aktiengesellschaft Komponentenanordnung an einem Kühlpaket
WO2023217820A1 (fr) * 2022-05-10 2023-11-16 Valeo Systemes Thermiques Module de refroidissement, notamment pour un véhicule
WO2023217821A1 (fr) * 2022-05-10 2023-11-16 Valeo Systemes Thermiques Module multifonction fluidique, notamment pour un véhicule
FR3135422A1 (fr) * 2022-05-10 2023-11-17 Valeo Systemes Thermiques Système de conditionnement thermique comprenant un module de gestion des fluides pour un véhicule notamment automobile
WO2023237389A1 (fr) * 2022-06-09 2023-12-14 Valeo Systemes Thermiques Module de gestion de fluides, notamment pour un véhicule
WO2024017849A1 (fr) * 2022-07-22 2024-01-25 Valeo Systemes Thermiques Module de gestion de fluide pour véhicule
FR3138199A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
FR3138201A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
FR3138200A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
EP4317894A1 (fr) * 2022-08-01 2024-02-07 Valeo Systemes Thermiques Module réfrigérant pour système de gestion thermique
EP4317859A1 (fr) * 2022-08-01 2024-02-07 Valeo Systemes Thermiques Module réfrigérant pour système de gestion thermique
WO2024052382A1 (fr) * 2022-09-09 2024-03-14 Eto Magnetic Gmbh Dispositif de conduite de liquide, conduite de liquide et procédé de production d'une partie de coque pour le dispositif de conduite de liquide
WO2024078735A1 (fr) * 2022-10-10 2024-04-18 Voss Automotive Gmbh Module de gestion thermique et véhicule doté d'au moins un tel module
WO2024078800A1 (fr) * 2022-10-14 2024-04-18 Zf Friedrichshafen Ag Module de distribution pour un système de gestion thermique, système comprenant une pompe à chaleur contenant un module de distribution, et véhicule
DE102022211209A1 (de) 2022-10-21 2024-05-02 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Kältemittelbaugruppe für ein Kraftfahrzeug
WO2024135249A1 (fr) * 2022-12-21 2024-06-27 サンデン株式会社 Unité de fluide frigorigène

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Publication number Priority date Publication date Assignee Title
EP4083480A3 (fr) * 2021-04-08 2023-01-25 Veritas Ag Systeme de soupape de fluide
US20220332162A1 (en) * 2021-04-19 2022-10-20 Hyundai Motor Company Integrated thermal management module for vehicle
WO2022253480A1 (fr) * 2021-06-02 2022-12-08 Volkswagen Aktiengesellschaft Module de commande de gestion thermique doté d'un dispositif de commande intégré
WO2022266945A1 (fr) * 2021-06-24 2022-12-29 浙江吉利控股集团有限公司 Appareil d'intégration de conduites de refroidissement à canaux multiples, module d'intégration de gestion thermique et véhicule électrique
WO2023031177A1 (fr) * 2021-08-31 2023-03-09 Volkswagen Aktiengesellschaft Dispositif de distribution d'agent de refroidissement pour un véhicule automobile et véhicule automobile équipé d'un dispositif de distribution d'agent de refroidissement
WO2023045355A1 (fr) * 2021-09-27 2023-03-30 浙江吉利控股集团有限公司 Système de gestion thermique, véhicule et procédé de gestion thermique
FR3133435A1 (fr) * 2022-03-08 2023-09-15 Valeo Systemes Thermiques Plaque commune d’un module thermique d’un circuit de fluide réfrigérant
FR3133432A1 (fr) * 2022-03-08 2023-09-15 Valeo Systemes Thermiques Plaque commune d’un module thermique d’un circuit de fluide réfrigérant
FR3133434A1 (fr) * 2022-03-08 2023-09-15 Valeo Systemes Thermiques Plaque commune d’un module thermique d’un circuit de fluide réfrigérant
WO2023171921A1 (fr) * 2022-03-10 2023-09-14 Hanon Systems Système de climatisation pour un véhicule
CN114861973A (zh) * 2022-03-24 2022-08-05 三峡大学 一种计及多源因素的风力发电系统风险评估方法
DE102022108697A1 (de) 2022-04-11 2023-10-12 Audi Aktiengesellschaft Komponentenanordnung an einem Kühlpaket
FR3135421A1 (fr) * 2022-05-10 2023-11-17 Valeo Systemes Thermiques Module de refroidissement, notamment pour un véhicule
WO2023217821A1 (fr) * 2022-05-10 2023-11-16 Valeo Systemes Thermiques Module multifonction fluidique, notamment pour un véhicule
FR3135506A1 (fr) * 2022-05-10 2023-11-17 Valeo Systemes Thermiques Module multifonction fluidique, notamment pour un véhicule
FR3135422A1 (fr) * 2022-05-10 2023-11-17 Valeo Systemes Thermiques Système de conditionnement thermique comprenant un module de gestion des fluides pour un véhicule notamment automobile
WO2023217820A1 (fr) * 2022-05-10 2023-11-16 Valeo Systemes Thermiques Module de refroidissement, notamment pour un véhicule
WO2023237389A1 (fr) * 2022-06-09 2023-12-14 Valeo Systemes Thermiques Module de gestion de fluides, notamment pour un véhicule
FR3136402A1 (fr) * 2022-06-09 2023-12-15 Valeo Systemes Thermiques Module de gestion de fluides, notamment pour un véhicule
FR3138200A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
FR3138199A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
FR3138201A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
FR3138198A1 (fr) * 2022-07-22 2024-01-26 Valeo Systemes Thermiques Module de gestion de fluide destiné à un véhicule
WO2024017849A1 (fr) * 2022-07-22 2024-01-25 Valeo Systemes Thermiques Module de gestion de fluide pour véhicule
WO2024028065A1 (fr) * 2022-08-01 2024-02-08 Valeo Systemes Thermiques Module de fluide frigorigène pour système de gestion thermique
EP4317859A1 (fr) * 2022-08-01 2024-02-07 Valeo Systemes Thermiques Module réfrigérant pour système de gestion thermique
EP4317894A1 (fr) * 2022-08-01 2024-02-07 Valeo Systemes Thermiques Module réfrigérant pour système de gestion thermique
WO2024028059A1 (fr) * 2022-08-01 2024-02-08 Valeo Systemes Thermiques Module de fluide frigorigène pour système de gestion thermique
WO2024052382A1 (fr) * 2022-09-09 2024-03-14 Eto Magnetic Gmbh Dispositif de conduite de liquide, conduite de liquide et procédé de production d'une partie de coque pour le dispositif de conduite de liquide
WO2024078735A1 (fr) * 2022-10-10 2024-04-18 Voss Automotive Gmbh Module de gestion thermique et véhicule doté d'au moins un tel module
WO2024078800A1 (fr) * 2022-10-14 2024-04-18 Zf Friedrichshafen Ag Module de distribution pour un système de gestion thermique, système comprenant une pompe à chaleur contenant un module de distribution, et véhicule
DE102022210903A1 (de) 2022-10-14 2024-04-25 Zf Friedrichshafen Ag Verteilermodul für ein Thermomanagementsystem, System umfassend eine Wärme-pumpe mit einem Verteilermodul, und Fahrzeug
DE102022211209A1 (de) 2022-10-21 2024-05-02 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Kältemittelbaugruppe für ein Kraftfahrzeug
WO2024135249A1 (fr) * 2022-12-21 2024-06-27 サンデン株式会社 Unité de fluide frigorigène

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