US20170138651A1 - Branching means for a refrigerant flow of a refrigerant circuit - Google Patents

Branching means for a refrigerant flow of a refrigerant circuit Download PDF

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Publication number
US20170138651A1
US20170138651A1 US15/317,528 US201515317528A US2017138651A1 US 20170138651 A1 US20170138651 A1 US 20170138651A1 US 201515317528 A US201515317528 A US 201515317528A US 2017138651 A1 US2017138651 A1 US 2017138651A1
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United States
Prior art keywords
branching means
refrigerant
point
throttle
branching
Prior art date
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Abandoned
Application number
US15/317,528
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English (en)
Inventor
Roland Haussmann
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.)
Valeo Klimasysteme GmbH
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Valeo Klimasysteme GmbH
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Assigned to VALEO KLIMASYSTEME GMBH reassignment VALEO KLIMASYSTEME GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAUSSMANN, ROLAND
Publication of US20170138651A1 publication Critical patent/US20170138651A1/en
Abandoned legal-status Critical Current

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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
    • F25B39/00—Evaporators; Condensers
    • 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
    • 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
    • F25B40/02—Subcoolers
    • 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
    • F25B41/062—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/003—Filters
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means

Definitions

  • the invention relates to a branching means for a refrigerant flow of a refrigerant circuit, in particular of a battery cooler circuit.
  • the battery modules In electrically operated vehicles or in hybrid vehicles, the battery modules generate heat during operation, which heat is often dissipated by way of a cooling circuit.
  • a cooling sub-circuit of a vehicle air-conditioning system that is already provided in the vehicle.
  • the battery cooler circuit is often split into multiple cooling branches which are assigned to in each case one or more of the battery modules. In this case, it is the intention for the cooling branches to be flowed through in parallel by the refrigerant.
  • the battery cooler circuit is assigned a dedicated expansion device which is provided between an outlet of the gas cooler and an inlet into a branching means which splits the refrigerant into the individual cooling branches.
  • an expansion device use is made of a known thermostatic expansion valve (TXV) which controls the refrigerant throughflow in accordance with the conditions in the battery cooler circuit.
  • TXV thermostatic expansion valve
  • the pressure drop in the thermostatic expansion valve accounts for approximately 60 to 95% of the total pressure difference, whereas the pressure drop in the branching means amounts to merely 3 to 10%.
  • a reason for this is that the pressure difference between the high-pressure branch and the low-pressure branch of the vehicle air conditioning system is considerably greater in the presence of high ambient temperatures than in the presence of low temperatures.
  • thermostatic expansion valve must however supply an adequate amount of refrigerant, that is to say an adequate refrigerant flow, to the evaporator even in the presence of the minimum operating temperature and thus a minimal pressure difference; this is possible only if the pressure drop in the branching means is small. Therefore, known branching means are configured for a small pressure drop.
  • the known branching means Owing to the phase mixture in the branching means, it is also necessary for the known branching means to be installed in an exactly vertical orientation in order, even in the presence of a small throughflow, to realize as homogenous as possible a distribution of the two-phase mixture to the various outlet lines.
  • a cooling arrangement must function even in the presence of low ambient temperatures of, for example, down to ⁇ 10° C. or below, by contrast to a passenger compartment cooling arrangement, which is normally deactivated in the presence of such temperatures.
  • the fraction of liquid refrigerant upstream of the branching means is substantially 100%, for which the known branching means are not configured.
  • a branching means for a refrigerant flow of a refrigerant circuit in particular of a battery cooler circuit, having an inlet and having at least two outlet lines which lead to two cooling branches, wherein at least one throttle stage is integrated into the branching means.
  • the throttle stage is arranged upstream of a branching point to the individual outlet lines, wherein the throttle stage is in particular situated directly upstream of the branching point. Owing to the spatial proximity of the throttle point to the splitting of the refrigerant flow to the individual outlet lines, the liquid phase and the gas phase in the refrigerant flow remain fully mixed downstream of the throttle point, thus ensuring a homogenous distribution of the refrigerant, including the liquid fractions of the refrigerant, to the individual outlet lines. Since the cooling performance is primarily linked to the evaporation of the liquid phase of the refrigerant, it is thus possible to attain highly homogenous cooling performance in both cooling branches.
  • the throttle stage preferably has a throttle point, that is to say a constriction of the flow cross section, each of the outlet lines, said throttle points being in particular of identical form such that the same conditions prevail in all of the outlet lines and in all of the cooling branches supplied from said outlet lines.
  • the calibrated bore may be formed so as to directly adjoin the branching point of the main line, in order to keep the structural length of the branching means small.
  • the pipe may for example be inserted into a threaded sleeve which is screwed into the body of the branching means.
  • a threaded sleeve which is screwed into the body of the branching means.
  • Suitable internal diameters for the throttle point both for a calibrated bore and for a pipe with calibrated internal diameter, for example between 0.2 and 1.0 mm, and a suitable length lies between 10 and 40 mm.
  • the desired pressure drop across the branching means is set by way of the design of the throttle points, specifically the arrangement, cross section and length thereof.
  • the refrigerant In the presence of ambient temperatures of approximately between 20 and 40° C., that is to say under summer conditions, the refrigerant is preferably still substantially in the supercritical or liquid state, with only a single phase, at the inlet of the branching means.
  • the refrigerant flow does not, in any operating state, have clearly separated phases downstream of the branching point, such that a homogenous distribution of the refrigerant flow to the two outlet lines is always realized.
  • uniform cooling of the battery modules in the two cooling branches is always ensured.
  • the sensitivity with respect to a deviation from a vertical installation position is greatly reduced.
  • FIG. 6 is a diagrammatic illustration of the maximum pressure difference at the pressure reducer of the battery cooler system as a function of the ambient temperature
  • the pressure reduction from the high-pressure side to the low-pressure side is realized here by way of a fixedly predefined cross-sectional constriction, such as is known for R744 refrigerant circuits.
  • the diameter of said throttle point is selected inter alia in a manner dependent on the required performance of the evaporator.
  • the first cooling sub-circuit 18 opens into the return suction line 38 .
  • shut-off valve 42 and the branching means 44 are combined in a single component. They may however also be formed as separate components. It would also be possible to dispense with the shut-off valve 42 and to realize the pressure reduction entirely by way of the branching means 44 .
  • the shut-off valve 42 is connected to a controller 46 which can define the opening state of the shut-off valve 42 .
  • the shut-off valve 42 can assume only the two control states “open” and “closed”.
  • the calibrated bore 62 has for example a diameter of 0.2-1.0 mm and a length of 10-40 mm, wherein, with increasing length of the throttle point, the flow becomes more stable, and the tendency for the generation of vibrations in the flow is also reduced.
  • FIG. 3 shows an embodiment of a branching means 44 in which the throttle stage is provided in the region of the main line 54 . In this case, the pressure reduction takes place already upstream of the branching point 56 .
  • the pipe 70 is covered by a filter 64 which prevents contamination of the branching means 44 .
  • the calibrated internal diameter of the inserted type 70 can be produced with high precision as a bore.
  • FIG. 4 shows a pressure reducer 40 which has two throttle stages in series in terms of flow.
  • a first throttle stage is realized, in this case by way of a calibrated bore 82 , which constitutes a constriction of the throughflow cross section for the refrigerant.
  • the cross section of the calibrated bore 82 is narrowed in relation to the cross section of the inlet 78 and also in relation to the cross section of the adjoining inlet 52 of the branching means 44 . In this way, a first expansion of the refrigerant, and a first pressure reduction, is effected in the calibrated bore 82 .
  • shut-off valve 42 instead of the calibrated bore 82 in the body of the shut-off valve 42 , it would also be possible for a calibrated bore or a pipe 70 with calibrated internal diameter to be provided in the inlet 52 of the branching means 44 . In this way, the construction of the shut-off valve 42 can be further simplified.
  • the refrigerant flows into the two cooling branches 34 , 36 of the battery cooler circuit 30 .
  • the battery cooler system 32 is configured such that, in the presence of low ambient temperatures under “winter conditions”, that is to say in the presence of temperatures between approximately ⁇ 10 and 0° C., a pressure difference of approximately 10 bar and an enthalpy difference of approximately 240 kJ/kg are attained across the pressure reducer.
  • the pressure difference may also be configured with regard to a pressure difference between the high-pressure side and the low-pressure side of the overall refrigerant circuit 10 .
  • the solid curve indicates that, in the presence of high ambient temperatures, the shut-off valve 42 is, by way of the controller 46 , operated with pulse width modulation in such a way that the cooling performance is optimized.
  • the opening duration of the shut-off valve 42 is calculated by the controller 46 from the values signaled by the temperature sensor T 1 and T 2 , that is to say from the refrigerant temperature at the inlet 52 of the branching means 44 and the refrigerant temperature after said refrigerant has passed through the cooling branches 34 , 36 of the battery cooler circuit 30 .
  • shut-off valve 42 In winter, that is to say in the presence of low ambient temperatures and a small pressure difference, it is by contrast the case that the shut-off valve 42 is continuously open (see dashed line in FIG. 5 ).
  • FIGS. 6 and 7 show the pressures prevailing on the high-pressure side of the refrigerant circuit 10 and on the low-pressure side thereof as a function of the ambient temperature.
  • the pressure profile of the high-pressure side is denoted by rhombuses, whereas the pressure profile on the low-pressure side is denoted by squares.
  • FIG. 6 It can be read from FIG. 6 that, in the presence of winter conditions between ⁇ 10 and 0° C., a pressure difference of between 7 and 9 bar (0.7 to 0.9 MPa) is to be expected, whereas, in the presence of summer conditions between 25 and 40° C. ambient temperature, considerably higher pressure differences prevail, for example 35 to 65 bar (3.5 to 6.5 MPa), wherein a pressure difference of even 90 bar may prevail.
  • the pressure difference between the high-pressure side and low-pressure side greatly increases with rising ambient temperature. Since the mass flow that is generated changes approximately with the square root of the pressure difference, it is the case for example that, for an ambient temperature of ⁇ 10° C., the possible cooling performance of the battery cooler circuit 30 is reduced by approximately 40% in relation to an ambient temperature of +40° C. If the battery cooler system 32 and in particular the pressure reducer 40 are optimized for operation in the presence of low ambient temperatures, this has the effect that, during operation in the presence of high ambient temperatures, the shut-off valve 42 should be closed for approximately 30-90% of the time.
  • the configuration of the rest of the refrigerant circuit 10 , in particular of the cooling sub-circuit 18 , which serves for the vehicle air-conditioning system evaporator 20 , are not affected by these considerations, as only the pressure reducer 40 in the battery cooler circuit 30 has to be configured correspondingly.
  • FIG. 8 shows, on the basis of a Mollier diagram, the cycles that are passed through for operation of the refrigerant circuit 10 under some conditions (high ambient temperatures) and winter conditions (low ambient temperatures).
  • the upper cycle in the graph, with the points A to G, describes the operation in the presence of high ambient temperatures.
  • the high-pressure side which in this case is preferably at between 80 and 120 bar, is operated in the supercritical range.
  • point A to point B the compression of the refrigerant in the compressor 12 takes place.
  • point B to point C the supercritical refrigerant is cooled in the gas cooler 14 .
  • point C to point D further cooling on the high-pressure side of the refrigerant circuit 10 is realized by way of the inner heat exchanger 16 .
  • point D to point E a pressure reduction takes place in the first throttle stage of the pressure reducer 40 , wherein the pressure reduction takes place at most as far as the liquid boundary, such that the refrigerant remains in only single-phase form, or is in the supercritical state, when it enters the branching means 44 .
  • the refrigerant is however still in only single-phase form when it the branching means 44 .
  • a homogenous distribution to the two cooling branches 34 , 36 is possible more easily than in the presence of a phase mixture.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Secondary Cells (AREA)
US15/317,528 2014-06-26 2015-06-23 Branching means for a refrigerant flow of a refrigerant circuit Abandoned US20170138651A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102014108989.8A DE102014108989A1 (de) 2014-06-26 2014-06-26 Verzweiger für einen Kältemittelstrom eines Kältemittelkreislaufs
DE102014108989.8 2014-06-26
PCT/EP2015/064105 WO2015197612A1 (en) 2014-06-26 2015-06-23 Branching means for a refrigerant flow of a refrigerant circuit

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US20170138651A1 true US20170138651A1 (en) 2017-05-18

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ID=53476896

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US15/317,528 Abandoned US20170138651A1 (en) 2014-06-26 2015-06-23 Branching means for a refrigerant flow of a refrigerant circuit

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US (1) US20170138651A1 (de)
EP (1) EP3161393A1 (de)
JP (1) JP2017523371A (de)
CN (1) CN106662380A (de)
DE (1) DE102014108989A1 (de)
WO (1) WO2015197612A1 (de)

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US20160223239A1 (en) * 2015-01-31 2016-08-04 Trane International Inc. Indoor Liquid/Suction Heat Exchanger
US11339691B2 (en) * 2017-11-03 2022-05-24 Dana Heavy Vehicle Systems Group, Llc Heat transfer system
FR3116598A1 (fr) * 2020-11-24 2022-05-27 Valeo Systemes Thermiques Circuit de fluide réfrigérant comprenant un filtre à particules
EP4068470A1 (de) * 2021-03-29 2022-10-05 Castrol Limited Wärmetransfersystem mit wärmeträgerfluid einschliesslich flüssigkeits- und gaskomponenten
EP4068472A1 (de) * 2021-03-29 2022-10-05 Castrol Limited Wärmetransfersystem mit wärmeträgerfluid einschliesslich flüssigkeits- und gaskomponenten
EP4068471A1 (de) * 2021-03-29 2022-10-05 Castrol Limited Wärmetransfersystem mit wärmeträgerfluid einschliesslich flüssigkeits- und gaskomponenten

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CN107403975B (zh) * 2017-07-21 2019-09-27 精进电动科技股份有限公司 一种储能电池液冷***均流装置和方法
FR3077376A1 (fr) * 2018-01-31 2019-08-02 Valeo Systemes Thermiques Circuit de fluide refrigerant pour vehicule a performances ameliorees
DE102019208976A1 (de) 2019-06-19 2020-12-24 Volkswagen Aktiengesellschaft Abzweigstück für eine Fluidleitung
DE102021204489A1 (de) * 2021-05-04 2022-11-10 BSH Hausgeräte GmbH Trocknerloser Kältemittelkreislauf, Verfahren zur Montage eines Kältemittelkreislaufs und Kältegerät

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US20130087204A1 (en) * 2011-10-07 2013-04-11 Trane International Inc. Pressure Correcting Distributor For Heating and Cooling Systems

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160223239A1 (en) * 2015-01-31 2016-08-04 Trane International Inc. Indoor Liquid/Suction Heat Exchanger
US11339691B2 (en) * 2017-11-03 2022-05-24 Dana Heavy Vehicle Systems Group, Llc Heat transfer system
FR3116598A1 (fr) * 2020-11-24 2022-05-27 Valeo Systemes Thermiques Circuit de fluide réfrigérant comprenant un filtre à particules
EP4068470A1 (de) * 2021-03-29 2022-10-05 Castrol Limited Wärmetransfersystem mit wärmeträgerfluid einschliesslich flüssigkeits- und gaskomponenten
EP4068472A1 (de) * 2021-03-29 2022-10-05 Castrol Limited Wärmetransfersystem mit wärmeträgerfluid einschliesslich flüssigkeits- und gaskomponenten
EP4068471A1 (de) * 2021-03-29 2022-10-05 Castrol Limited Wärmetransfersystem mit wärmeträgerfluid einschliesslich flüssigkeits- und gaskomponenten
WO2022208268A1 (en) * 2021-03-29 2022-10-06 Castrol Limited Heat transfer system with heat transfer fluid including liquid and gas components
WO2022208266A1 (en) * 2021-03-29 2022-10-06 Castrol Limited Heat transfer system with heat transfer fluid including liquid and gas components
WO2022208267A1 (en) * 2021-03-29 2022-10-06 Castrol Limited Heat transfer system with heat transfer fluid including liquid and gas components

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WO2015197612A1 (en) 2015-12-30
DE102014108989A1 (de) 2015-12-31
JP2017523371A (ja) 2017-08-17
CN106662380A (zh) 2017-05-10
EP3161393A1 (de) 2017-05-03

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