EP4311989A1 - Circuit de fluide frigorigène - Google Patents

Circuit de fluide frigorigène Download PDF

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Publication number
EP4311989A1
EP4311989A1 EP23183718.8A EP23183718A EP4311989A1 EP 4311989 A1 EP4311989 A1 EP 4311989A1 EP 23183718 A EP23183718 A EP 23183718A EP 4311989 A1 EP4311989 A1 EP 4311989A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
ffm
heat exchanger
functional conveying
conveying agent
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.)
Pending
Application number
EP23183718.8A
Other languages
German (de)
English (en)
Inventor
Andreas Wagner
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.)
CTS Clima Temperatur Systeme GmbH
Original Assignee
CTS Clima Temperatur Systeme GmbH
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
Priority claimed from DE102022134604.8A external-priority patent/DE102022134604A1/de
Application filed by CTS Clima Temperatur Systeme GmbH filed Critical CTS Clima Temperatur Systeme GmbH
Publication of EP4311989A1 publication Critical patent/EP4311989A1/fr
Pending 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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/48—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow path resistance control on the downstream side of the diverging point, e.g. by an orifice
    • 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
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators

Definitions

  • the invention relates to a refrigerant circuit, comprising a refrigerant compressor, which compresses refrigerant to a high pressure level that is above the triple point of the refrigerant, and from which the compressed refrigerant is fed to a heat exchanger unit, which extracts heat from the refrigerant, an expansion element arranged downstream of the heat exchanger unit , which is followed by at least one heat exchanger channel, wherein the expansion element expands the compressed refrigerant in such a way that the triple point in the expansion element itself is not exceeded and that the refrigerant, after leaving the expansion element, falls below the triple point in the subsequent heat exchanger channel and sublimes, thereby generating heat from a receives a heat source surrounding the heat exchanger body having the heat exchanger channel, as well as a collecting line which receives the refrigerant after leaving the heat exchanger channel and supplies it to the refrigerant compressor.
  • the invention is therefore based on the object of improving the heat transfer from the heat exchanger body to the sublimating refrigerant flowing into the heat exchanger channel.
  • This object is achieved according to the invention in a refrigerant circuit of the type described above in that a mixture of refrigerant and a functional conveying medium flows through the heat exchanger channel During the sublimation of the refrigerant, the functional conveying agent is still present as a liquid functional conveying agent, which improves heat transfer in the heat exchanger channel between the sublimating refrigerant and the heat exchanger body having the heat transfer channel.
  • the advantage of the solution according to the invention can therefore be seen in the fact that the functional conveying agent, which is still liquid during the sublimation of the refrigerant, opens up the possibility of improving the heat transfer between them by wetting, on the one hand, the sublimating refrigerant and, on the other hand, walls of the heat exchanger body surrounding the heat exchanger channel, and thus in particular the To increase heat absorption by the sublimating refrigerant per unit of time.
  • a lubricant separator is arranged between the refrigerant compressor and the high-pressure side heat exchanger unit, which ensures that the lubricant from the refrigerant compressor does not circulate in undefined quantities in the refrigerant circuit, but after the refrigerant compressor in the refrigerant circuit is largely withdrawn again.
  • the lubricant separator is a coalescence separator, since with such a coalescence separator a very high separation rate of lubricant can be achieved in order to largely remove it from the refrigerant, which subsequently enters the heat exchanger channel, and thus problems due to blockages in the heat exchanger channel avoid.
  • the functional conveying agent should not change and/or impair the operating conditions of the refrigerant circuit with the refrigerant intended for sublimation without the addition of the functional conveying agent.
  • the functional conveying agent is selected such that the mixture of the refrigerant, in particular CO2, and the functional conveying agent is non-flammable, preferably also non-toxic, so that the addition of the functional conveying agent does not create any additional risk potential due to the refrigerant circuit arises.
  • non-flammable requirement requires that the mixture be classified as “1” or “A1” according to the ANSI/ASHRAE Standard 34 based on ASTM E681, where "1" is non-flammable and “A1” is non-toxic and not means flammable.
  • a further advantageous specification provides that the functional conveying agent is selected such that the mixture of the refrigerant and the functional conveying agent has a triple point that is lowered by a maximum of 5 K, preferably a maximum of 3 K, compared to the triple point of the pure refrigerant.
  • the functional conveying agent is selected such that the mixture of the refrigerant and the functional conveying agent has a temperature glide, that is to say a difference between the dew temperature and the boiling temperature, of a maximum of 5 K in the area between the triple point and the critical point , preferably a maximum of 3 K.
  • This measure ensures that no additional measures are required for optimal heat transfer when operating the refrigerant circuit, since the difference between the dew temperature and the boiling temperature of the mixture of refrigerant and functional fluid has no significant impact on the operating conditions.
  • a further advantageous condition provides that the functional conveying agent is selected such that the mixture of the refrigerant and the functional conveying agent has a global warming potential, hereinafter referred to as “global warming potential,” of less than 150.
  • This measure can ensure that the mixture of refrigerant and functional conveying agent has a minimal impact on the environmental compatibility of operating such a refrigerant circuit.
  • the proportion of the functional conveying agent in the mixture of refrigerant and functional conveying agent is selected such that no blockage occurs in the heat exchanger channel during the sublimation of the refrigerant.
  • This measure excludes functional conveying agents that separate out of the mixture in the heat exchanger channel and settle or become viscous in such a way that the flow conditions in the heat exchanger channel are significantly impaired.
  • the functional conveying agent in the refrigerant circuit has a circulating lubricant with a defined mass proportion of the total mass of the mixture of refrigerant and functional conveying agent.
  • the refrigerant circuit is supplied with metered lubricant from the lubricant separator as a functional conveying medium by means of a supply line and a metering unit assigned to it.
  • a further advantageous solution provides that a mixture of refrigerant and lubricant is fed to the refrigerant circuit as a functional conveying agent in a metered manner by means of a feed line branching off between the refrigerant compressor and the lubricant separator and a metering unit assigned to this.
  • This solution has the advantage that the lubricant is present in a reduced proportion in the refrigerant and the exact lubricant dosage can therefore be achieved even more easily by metering this combination of refrigerant and lubricant.
  • a condenser or gas cooler is preferably provided in the supply line, which makes it possible to cool the mixture of refrigerant and lubricant before it is fed back into the refrigerant circuit.
  • the refrigerant circuit in the area of the high-pressure side heat exchanger unit is supplied with metered lubricant as a functional conveyor so that the lubricant can mix well with the refrigerant before it enters the heat exchanger channel.
  • Another supplementary or alternative advantageous possibility of supplying lubricant as a functional conveying agent provides that lubricant is supplied in a metered manner as a functional conveying agent to the refrigerant circuit in the area of the expansion element.
  • the lubricant could be supplied to the refrigerant as a functional conveying agent upstream of the expansion element.
  • a particularly advantageous solution provides that lubricant is supplied in metered quantities as a functional conveying agent to the refrigerant circuit following the expansion element, in particular immediately following the expansion element.
  • the lubricant present in the mixture can be a lubricant for the refrigerant compressor, which, however, must be selected so that it does not settle in a viscous form in the heat exchanger channel and clog it.
  • the mass fraction of the lubricant present in the mixture in the heat exchanger channel is based on the mixture of refrigerant and functional promoting means is more than 0.02% by mass, preferably more than 0.04% by mass.
  • the mass fraction of the lubricant present in the mixture is a maximum of 1 mass%, better a maximum of 0.11 mass%, even better a maximum of 0.05 mass%.
  • an advantageous solution for a functional conveying agent according to the invention provides that the functional conveying agent comprises at least one additional refrigerant.
  • Such an additional refrigerant is a refrigerant which differs from the refrigerant, for example CO2, which is intended for the basic function of the refrigerant circuit and in particular sublimates in the heat exchanger channel.
  • the proportion of the additional refrigerant representing the functional conveying agent in the mixture of refrigerant and functional conveying agent is selected such that the mixture of refrigerant and functional conveying agent has a temperature glide that is smaller both in the area between the triple point and the critical point than 5 K, and, based on the pure refrigerant, has a triple point depression that is less than 5 K, and in particular is not combustible and in particular also has a “global warming potential” of less than 150.
  • the functional funding means contains one or more of the additional refrigerants (E)-1,3,3,3-tetrafluoropropene, 1,1,1,2-tetrafluoroethane, 1,1-difluoroethene, 2,3 ,3,3-Tetrafluoropropene, difluoromethane, ethane, ethene, ethyne, fluoroethene, fluoromethane, pentafluoroethane, propane, propene, xenon.
  • additional refrigerants E-1,3,3,3-tetrafluoropropene, 1,1,1,2-tetrafluoroethane, 1,1-difluoroethene, 2,3 ,3,3-Tetrafluoropropene, difluoromethane, ethane, ethene, ethyne, fluoroethene, fluoromethane, pentafluoroethane
  • the functional conveying agent can not only be formed from an additional refrigerant, but can also be a mixture of several such additional refrigerants, with the overall mixture of additional refrigerants formed as a functional conveying agent fulfilling in particular one or more or preferably all of the above-mentioned conditions.
  • the refrigerant in the refrigerant circuit according to the invention is COz.
  • COz When COz is used as a refrigerant, it is preferably provided that it has a mass proportion in the range of 80% by mass to 99% by mass based on the total mass of the mixture of the refrigerant COz and the functional conveying agent.
  • the refrigerant COz has a molar proportion in the range from 88 mol% to 99.6 mol% based on 100 mol% of the mixture of the refrigerant COz and the functional conveying agent.
  • FIG. 1 Illustrated embodiment of a refrigerant circuit designated as a whole by 10 comprises a refrigerant compressor 12, which compresses refrigerant supplied to a suction side 14 and discharges it to a high-pressure side 16, the refrigerant compressed to high pressure being supplied from the refrigerant circuit 10 to a high-pressure-side heat exchanger unit 18, which is in the position is to extract heat from the refrigerant that is compressed to high pressure.
  • the heat exchanger unit 18 comprises a desuperheater 19 and a condenser or gas cooler 20, each of which dissipates a heat flow 21 and 22, respectively.
  • the compressed refrigerant cooled by dissipating the heat flow 22 is fed to a control valve 24, which thus makes it possible to supply the refrigerant, which is still under pressure, to a heat exchanger designated as a whole by 30, in which, after expansion of the refrigerant, heat is absorbed Fig. 1 characterized as fluid stream 28, takes place.
  • the heat exchanger has a refrigerant distributor 32 connected to the control valve 24, to which the pressurized refrigerant is supplied and the refrigerant is subsequently supplied via nozzle channels 34 to the heat exchanger channels 36, in which the refrigerant expands while absorbing heat from the fluid stream 28 , which runs in particular transversely or perpendicular to the plane of the drawing.
  • the refrigerant After flowing through the heat exchanger channels 36, the refrigerant enters a refrigerant collector 38, which collects the refrigerant from all heat exchanger channels 36 and from which the refrigerant is then supplied to the suction side 14 of the refrigerant compressor 12.
  • the heat exchanger channels 36 are formed by heat exchanger bodies 40 running parallel to one another, which extend from the refrigerant distributor 32 to the refrigerant collector 38, the heat exchanger bodies 40 having a first end region 42 for connection to the Refrigerant distributor 32 and a second end region 44 for connection to the refrigerant collector.
  • a preferred design solution provides that the heat exchanger bodies 40 protrude with the first end region 42 into an interior 46 of the refrigerant distributor 32 and are also provided at the first end region 42 with the nozzle channel 34, which thus on the one hand receives refrigerant from the interior 46 of the refrigerant distributor 32 and delivers it to the heat exchanger channel 36, in which the refrigerant then expands and cools the heat exchanger body 40 so that it can absorb heat from the heat flow 28 from a heat flowing around the respective heat exchanger body.
  • the nozzle channels 34 in the end regions 42 are designed so that they limit a mass flow of refrigerant flowing from the interior 46 to the respective heat exchanger channel 36.
  • the nozzle channels 34 are designed with regard to their cross-sectional area in such a way that the refrigerant flows in them at the critical speed, that is, in this case, the speed of sound, and thus essentially an isenthalpic expansion of the refrigerant takes place in the nozzle channels 34.
  • the refrigerant is supplied in the refrigerant circuit 10 to the refrigerant distributor 32 at a pressure level which is above the triple point of COz, for example in the range between 10 bar and 160 bar, preferably in the range from 70 bar to about 140 bar and in particular in the range from 10 bar to about 70 bar.
  • the pressure is then reduced in the nozzle channel 34, but until the transition from the nozzle channel 34 into the heat exchanger channel 36 it is preferably still above the triple point of the refrigerant, in this case above the triple point of CO2, so that essentially sublimation occurs the nozzle channel 34 is prevented.
  • the pressure in the nozzle channel 34 and in particular up to the outlet of the nozzle channel 34 is preferably in the range of greater than 6 bar, for example in the range of approximately 6 bar to approximately 40 bar.
  • Gaseous refrigerant is preferably present at the second connection 44 of the heat exchanger body 40, which passes from the heat exchanger channel 36, in particular with its cross section, into an interior 48 of the refrigerant collector and is collected by it and fed to the suction side 14 of the refrigerant compressor 12 via the refrigerant circuit 10.
  • the nozzle channels 34 have, for example, a diameter of less than 0.55 mm, preferably less than 0.1 mm, and, for example, a length in the range of 0.05 mm to 5 mm
  • the refrigerant compressor 12 on the high pressure side 16 is followed by a lubricant separator 50, which consists of the compressed refrigerant, in particular CO2, lubricant, in particular oil, with the highest possible lubricant separation efficiency, for example larger 99%, in order to achieve a defined and as low as possible lubricant circulation rate in the refrigerant circuit.
  • a lubricant separator 50 which consists of the compressed refrigerant, in particular CO2, lubricant, in particular oil, with the highest possible lubricant separation efficiency, for example larger 99%, in order to achieve a defined and as low as possible lubricant circulation rate in the refrigerant circuit.
  • Such a lubricant separator 50 is preferably a coalescence separator with which a separation efficiency of more than 99.99% can be achieved.
  • a part, in particular a predominant part, of the lubricant collecting in the lubricant separator 50 in a lubricant bath 54 from the lubricant bath 54 is supplied to the refrigerant compressor 12 via a feed line 58 provided with a metering unit 56 Suction side 14 or directly to a lubricant sump of the refrigerant compressor 12.
  • the metering unit 56 is controlled according to the lubricant level of the lubricant bath 54.
  • a functional conveying agent FFM which increases the heat transfer between the sublimating refrigerant and the walls of the heat exchanger body 40 and is still liquid at the sublimation temperatures of the refrigerant, is preferably added to the refrigerant, in particular COz, in the heat exchanger channels 36 to form a mixture , which preferably performs an effective wetting function in the heat exchanger channels 36 between the sublimenting refrigerant, in particular refrigerant COz, and the walls of the heat exchanger body 40, in order to ensure that the solid state of the refrigerant changes more quickly into the gaseous state, so that the refrig
  • Such a functional conveying agent FFM is designed in particular in such a way that the triple point of the mixture of the refrigerant and the functional conveying agent FFM is only insignificantly lowered relative to the pure refrigerant, for example by less than 5 K.
  • a further requirement for such a functional conveying agent FFM is that the mixture of the refrigerant and the functional conveying agent FFM should be non-flammable, whereby the mixture according to ANSI/ASHRAE Standard 34, based on ASTM E681, is used for the “non-flammable” requirement must be classifiable as “1” or “A1”.
  • the requirement for such a functional conveying agent FFM is that the mixture of the refrigerant and the functional conveying agent FFM has a temperature glide TG in the area between the triple point and the critical point, that is, a difference between the dew temperature T "and the boiling temperature T ' which is smaller than 5 K.
  • the functional conveying agent FFM is selected such that the mixture of the refrigerant and the functional conveying agent FFM has a “global warming potential” GWP that is less than 150.
  • a further requirement for a functional conveying agent FFM according to the invention is that the mixture of the refrigerant and the functional conveying agent FFM is selected such that no blockage occurs during the sublimation of the refrigerant in the heat exchanger channel 36.
  • One possibility is to use a known refrigerant, referred to in this context as an additional refrigerant, as such a functional conveying agent FFM, whereby the mixture of the refrigerant and the additional refrigerant serving as a functional conveying agent FFM preferably not only has the triple point of the mixture relative to the triple point of the refrigerant by less than 5 K should be reduced, but also as low as possible “global warming potential” GWP should have, for example preferably a “global warming potential” GWP of less than 150.
  • Table 1 shows, on the one hand, the designation of additional refrigerants, the GWP and the ASHRAE designation of the same.
  • Table 1 shows how large the minimum mass proportion and proportion of the functional conveying agent FFM used should be in relation to the total mass of the mixture of refrigerant and functional conveying agent FFM, and how large the maximum mass proportion and quantitative proportion of this functional conveying agent FFM based on the total mass of the mixture of refrigerant and functional conveying agent should be, how large the GWP of the mixture of refrigerant and functional conveying agent FFM is at the maximum mass fraction of functional conveying agent, how large the temperature glide TG (T" - T) at minus 56 ° C of the mixture of refrigerant and functional conveying agent FFM at the maximum mass fraction of the Functional conveying agent FFM is and how large the maximum triple point reduction of the mixture of refrigerant and functional conveying agent FFM is at the maximum mass fraction based on the pure refrigerant.
  • the FFM functional conveying agent mixed with the refrigerant only causes a triple point reduction compared to the pure refrigerant of less than 3 K and the other specifications remain the same.
  • Tables 1 to 4 only list data for functional conveyors and lubricants are not taken into account as functional conveyors.
  • the lubricant itself is used as the functional conveying agent FFM, which can be added in doses at various points in the refrigerant circuit.
  • a lubricant supply line 62 is provided with a metering unit 64 arranged therein, which supplies the lubricant to the refrigerant circuit between the oil separator 50 and the desuperheater 19, so that a via the metering unit 64 precisely metered lubricant circulation rate can be specified.
  • the supply of lubricant from the lubricant bath 54 takes place via a supply line 72, in which a metering unit 74 is also provided, the supply line 72 opening into the refrigerant circuit between the desuperheater 19 and the condenser 20 and thus the refrigerant entering the condenser 20 then carries the exactly metered amount of lubricant in the refrigerant circuit, so that the lubricant then also can develop its wetting effect in the heat exchanger channels 36.
  • a supply line 82 is provided, in which a metering unit 84 is also provided, the supply line 82 supplying the lubricant to the refrigerant circuit between the condenser 20 and the control valve 24.
  • a supply line 92 is provided, which is also provided with a metering unit 94 and supplies lubricant from the lubricant bath 54 between the control valve 24 and the heat exchanger 30 or on the input side of the heat exchanger 30 to the refrigerant circuit, so that metering of the lubricant and lubricant is unaffected by the previous components
  • a very precise lubricant circulation rate in the heat exchanger 30 can be achieved and the wetting function of the lubricant serving as a function-promoting agent can be precisely specified.
  • the lubricant is supplied from a supply line 102 with a metering unit 104 from the lubricant bath 54 directly to the respective heat exchanger channel 36, for example an area 106 thereof, which is arranged close to the respective nozzle channel 34, preferably following it, so that the Lubricant can mix with the solid phase of the refrigerant that is forming or the refrigerant that is already sublimating and can then have a wetting effect.
  • the mass proportions of the lubricant in the heat exchanger channel 36 are at values of 0.11% by mass to 0.05% by mass of the mixture of refrigerant and lubricant entering the heat exchanger 30.
  • a supply line 112 with a metering unit 114 arranged therein is provided, which branches off the refrigerant compressed to high pressure with lubricant between the high-pressure side 16 of the refrigerant compressor 12 and the lubricant separator 50 from the refrigerant circuit and, bypassing the lubricant separator 50, supplies it to the refrigerant circuit between the lubricant separator 50 and the desuperheater 19, so that a lubricant circulation rate that can be precisely metered via the metering unit 114 can be specified.
  • the supply of refrigerant and lubricant branched off in the same way as in the seventh exemplary embodiment takes place via a supply line 122, in which a metering unit 124 is also provided, the supply line 122 opening into the refrigerant circuit between the desuperheater 19 and the condenser 20 and thus the in The refrigerant entering the condenser 20 then precisely metered amount of lubricant is carried in the refrigerant circuit, so that the lubricant can then also develop its wetting effect in the heat exchanger channels 36.
  • a supply line 132 is provided, in which a metering unit 134 is also provided, the supply line 132 supplying the refrigerant and lubricant branched off in the same way as in the seventh exemplary embodiment to the refrigerant circuit between the condenser 20 and the control valve 24, whereby an additional one is optionally used to cool it down Condenser or gas cooler 136 is provided in the supply line 132.
  • a supply line 142 is provided, which is also provided with a metering unit 144 and, in the same way as in the seventh exemplary embodiment, supplies diverted refrigerant and lubricant between the control valve 24 and the heat exchanger 30 or on the inlet side of the heat exchanger 30 to the refrigerant circuit, whereby an additional one is optionally used to cool it down Condenser or gas cooler 136 is provided in the supply line 142, so that a metering of the lubricant that is uninfluenced by the previous components and thus a very precise lubricant circulation rate in the heat exchanger 30 can be achieved and thus the wetting function of the lubricant serving as a function-promoting agent can be precisely specified.
  • the refrigerant and lubricant branched off in the same way as in the seventh exemplary embodiment is supplied from a supply line 152 with a metering unit 154 directly to the respective heat exchanger channel 36, for example an area 106 thereof, which is close to the respective nozzle channel 34, preferably following it, is arranged so that the lubricant mixes with the forming solid phase of the refrigerant or the already sublimating refrigerant and then has a wetting effect can be, whereby a condenser or gas cooler 136 is optionally provided in the supply line 152 to cool it down.
  • the mass proportions of the lubricant in the heat exchanger channel 36 are between 0.11% by mass and 0.05% by mass of the mixture of refrigerant and lubricant entering the heat exchanger 30.

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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)
  • Lubricants (AREA)
EP23183718.8A 2022-07-26 2023-07-05 Circuit de fluide frigorigène Pending EP4311989A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022118624 2022-07-26
DE102022134604.8A DE102022134604A1 (de) 2022-07-26 2022-12-22 Kältemittelkreislauf

Publications (1)

Publication Number Publication Date
EP4311989A1 true EP4311989A1 (fr) 2024-01-31

Family

ID=87158140

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23183718.8A Pending EP4311989A1 (fr) 2022-07-26 2023-07-05 Circuit de fluide frigorigène

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EP (1) EP4311989A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20200283665A1 (en) * 2019-03-06 2020-09-10 Weiss Umwelttechnik Gmbh Refrigerant
DE102020130063A1 (de) * 2020-11-13 2022-05-19 CTS Clima Temperatur Systeme GmbH Temperieranlage und Verfahren zum Betreiben einer Temperieranlage
DE102020130061A1 (de) * 2020-11-13 2022-05-19 CTS Clima Temperatur Systeme GmbH Wärmeübertrager und Kältemittelkreislauf

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20200283665A1 (en) * 2019-03-06 2020-09-10 Weiss Umwelttechnik Gmbh Refrigerant
DE102020130063A1 (de) * 2020-11-13 2022-05-19 CTS Clima Temperatur Systeme GmbH Temperieranlage und Verfahren zum Betreiben einer Temperieranlage
DE102020130061A1 (de) * 2020-11-13 2022-05-19 CTS Clima Temperatur Systeme GmbH Wärmeübertrager und Kältemittelkreislauf

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