EP3344931B1 - Kältegerät mit mehreren lagerkammern - Google Patents

Kältegerät mit mehreren lagerkammern Download PDF

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Publication number
EP3344931B1
EP3344931B1 EP16751305.0A EP16751305A EP3344931B1 EP 3344931 B1 EP3344931 B1 EP 3344931B1 EP 16751305 A EP16751305 A EP 16751305A EP 3344931 B1 EP3344931 B1 EP 3344931B1
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EP
European Patent Office
Prior art keywords
evaporator
branch
choke point
refrigeration appliance
temperature
Prior art date
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Active
Application number
EP16751305.0A
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German (de)
English (en)
French (fr)
Other versions
EP3344931A1 (de
Inventor
Niels Liengaard
Vitali ULRICH
Alexander Foeldi
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.)
BSH Hausgeraete GmbH
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BSH Hausgeraete GmbH
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Publication date
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Publication of EP3344931A1 publication Critical patent/EP3344931A1/de
Application granted granted Critical
Publication of EP3344931B1 publication Critical patent/EP3344931B1/de
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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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • 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
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators

Definitions

  • the present invention relates to a refrigeration appliance, in particular a domestic refrigeration appliance, with at least two storage chambers that can be operated at different temperatures.
  • the operating temperatures of the storage compartments are roughly determined by the design of the refrigeration device and can only be adjusted in narrow, non-overlapping ranges, so that the possibility of using a compartment, for example as a refrigerator or freezer, can be determined by the user of the Refrigeration device is not changeable.
  • a refrigeration device in which the evaporators of two storage chambers are connected in series via a throttle point with an adjustable flow conductivity.
  • the throttling point makes it possible to vary the temperature of both storage chambers over a relatively wide range.
  • the operating temperature of one compartment also limits the setting range of the other. Since the pressure in the downstream evaporator can never be higher than that in the upstream, if the temperature of the compartment cooled by the upstream evaporator is given, the temperature of the other can only be set lower, or if the temperature of the compartment cooled by the downstream evaporator is given, that of the others only be set higher. This makes it difficult to adapt the refrigeration device to the changing needs of its users.
  • GB 2 017 890A discloses a refrigeration system with several parallel compressors and several parallel evaporators, which can be adjusted to different operating temperatures with the help of upstream and downstream expansion or pressure control valves.
  • the DE 10 2013 223737 A1 shows a refrigerator with two serially connected evaporators.
  • the U.S. 2010/218519 A1 discloses a refrigerator with an icemaker.
  • the object of the present invention is to improve the energy efficiency of a refrigeration device with multiple storage chambers.
  • the object is achieved by a refrigeration device having the features of claim 1.
  • the third evaporator also uses the cold that is generated when the refrigerant expands as it passes through the second throttle point to cool a third storage chamber.
  • the adjustable throttle points Due to the parallel connection of the branches, it is possible to use the adjustable throttle points to set a higher pressure in the first evaporator than in the second and thus a higher operating temperature in the first storage chamber than in the second, and vice versa.
  • Both the first and second and/or the third and fourth throttling point can be adjustable, so that in particular the pressure in the evaporator in between can be varied without affecting the total pressure drop or the refrigerant throughput of the relevant branch.
  • At least one capillary can comprise the first and third throttle points. Such a throttling point can nevertheless be adjustable if the capillary, which itself is not adjustable, is connected in series with an electronic expansion valve.
  • At least one, preferably exactly one, of the first and third throttle point has a fixed flow conductance and is in particular formed exclusively by a capillary.
  • Changes in the refrigerant throughput in a branch which can result from the fact that a change in the flow conductance in the second or fourth throttling point cannot be compensated for by an opposite adjustment in the first or third throttling point designed as a capillary, can be reduced by using a compressor with variable speed be avoided.
  • the compressor when the compressor is a variable speed compressor, its speed can be adjusted so that the compressor operates substantially uninterrupted. In this way, efficiency losses associated with the interim heating of parts of the refrigeration device when the compressor is at a standstill and these parts cooling down again after the compressor has started can be avoided.
  • a throttling point should be provided between the downstream evaporator of each branch and a confluence where the branches meet, in order to be able to set different pressures in the evaporators of the two branches located upstream of these throttling points.
  • the confluence is upstream of this third evaporator; in this case, the design of the refrigeration device is simpler and more energy-efficient operation is possible, in the third evaporator that part of the cooling capacity can still be used that is bound in the refrigerant that flows out of the second evaporator in an incompletely expanded state.
  • a suction tube heat exchanger may be arranged between the discharge port of the compressor and at least the first evaporator to pre-cool compressed refrigerant en route to the evaporator in thermal contact with refrigerant vapor drawn from the evaporators.
  • the intake manifold heat exchanger is arranged in the first branch, it only enables energy-efficient cooling there, but vice versa it can be compressed Refrigerants in the second branch reach the second evaporator without first being cooled in the draft tube heat exchanger.
  • the refrigerant can therefore reach the second evaporator at a higher temperature than the ambient temperature and, instead of being cooled, give up its heat to the second storage chamber.
  • the second evaporator can even function as a condenser be operated and in this way release a considerable heat output even with a small refrigerant flow rate.
  • the refrigeration device 1 comprises three storage chambers 1, 2, 3 which are arranged in a body above and/or next to each other and are thermally insulated from each other and from the environment.
  • Each storage chamber 1, 2, 3 is assigned an evaporator 4, 5 and 6, respectively.
  • the evaporators 4, 5, 6 are basically of any known design; as indicated in the figure, they can be plate evaporators, on the plate 7 of which a refrigerant line 8 runs in meanders and each of which runs within its storage chamber 1, 2, 3 or between an inner container of the storage chamber and a thermal insulation layer surrounding the inner container, but it can also be a wire tube or finned evaporator, possibly in combination with a fan driving the air circulation via the evaporator.
  • the evaporator 4 forms a first branch 11 of a refrigerant circuit together with an upstream throttling point 9 with an adjustable flow conductance, a downstream throttling point 10 with an adjustable flow conductance and a pipeline on which the components mentioned are lined up.
  • a second branch 12 parallel to the first branch 11 comprises the evaporator 5 together with an upstream adjustable throttle point 13 and a downstream adjustable throttle point 14.
  • the two branches 11, 12 join at a confluence 15, at which the evaporator is connected downstream in the direction of circulation of the refrigerant 6 connects.
  • the evaporator 6 is connected to a suction connection 17 of a compressor 18 via a suction line 16 .
  • the refrigerant circuit runs from a pressure connection 19 of the compressor 18 via a condenser 20 to a branch 21 from which the two branches 11, 12 originate.
  • part of branch 11 runs in close contact with, or even inside, the surface of suction line 16 to form a suction tube heat exchanger 22 in which the compressed refrigerant, after having passed through condenser 20 has been cooled to just above the ambient temperature, gives off further heat to refrigerant vapor in the suction pipe 16 in order to preheat it to such an extent that condensation of ambient moisture on parts of the suction pipe 16 which extend outside the thermal insulation layer is avoided.
  • the pressure that occurs in the evaporators 4, 5 and 6 during operation depends on the speed of the compressor 18 and on the flow conductance values of the throttle points 9, 10, 13, 14, which are determined by an electronic control unit 23 based on the measured values from in temperature sensors 24 arranged in the storage chambers 1, 2, 3 and operating temperatures selected by the user for the storage chambers 1, 2, 3.
  • the pressures in the evaporators 4 and 5 can be set to any values between the outlet pressure of the compressor 18 and the pressure of the evaporator 6 using the throttle points 9, 10 and 13, 14, respectively.
  • the pressure in the evaporator 4 can be varied without this having an effect on the amount of refrigerant that reaches the evaporator 6 per unit of time, and without consequently increasing the saturation temperature there influence.
  • the pressure in the evaporator 5 can be varied via the throttle points 13, 14 without this affecting the evaporator 6.
  • the throttling points 9, 10, 13, 14 can all be designed as electronic expansion valves, preferably of identical construction, the flow conductance of which can vary widely, preferably between a completely closed state and a wide open state in which the pressure drop at the throttling point is negligible. is adjustable. If, for example, the throttling point 10 is wide open and the pressure difference between the evaporators 4, 6 is therefore negligible, then the storage chamber 1 also works as a freezer compartment.
  • the throttle point is wide open, the refrigerant does not expand between the condenser 20 and the evaporator 4 and there is no evaporation in the evaporator 4, and the temperature at which the refrigerant enters the evaporator 4 essentially corresponds to that in the intake manifold heat exchanger accepted 22.
  • the range of temperatures to which the evaporator 4 can be set extends between the temperature reached in the intake manifold heat exchanger 22, which is slightly below the condensation temperature but can even be slightly higher than the ambient temperature, and the temperature of the evaporator 6.
  • a pressure drop in the throttle point 9 has no cooling effect on the storage chamber 1 as long as it is not sufficient to lower the boiling point of the refrigerant in the evaporator 4 below the temperature of the storage chamber 1 . It is therefore possible to implement the throttling point 9 as a series connection of an expansion valve and a capillary, the capillary being sized to create a pressure drop which lowers the pressure in the evaporator 4 to such an extent that the boiling temperature of the refrigerant therein corresponds to the ambient temperature.
  • This series connection allows a more precise control of the pressure in the evaporator 4 than only with an expansion valve.
  • the capillary expediently includes that part of the branch 11 which runs through the intake manifold heat exchanger 22 .
  • the pressure in the evaporator 5 can be set independently of that in the evaporator 4 and can assume both lower and higher values. If, for example, the storage chamber 3 is operated as a freezer compartment with a temperature of typically -17°C and the storage chamber 1 as a normal refrigeration compartment with a temperature of +4°C, for example, the saturation temperature in the evaporator 6 can be any value between -17°C and the condensation temperature prevailing in the condenser 20 can be set.
  • the evaporator 5 Since the evaporator 5 is connected to the condenser 20 bypassing the suction tube heat exchanger 22, when the refrigerant reaches the throttling point 13, it is generally at a temperature higher than the ambient temperature, so that when the throttling point 13 is wide open and the pressure drop across it is negligible, the storage chamber 3 can be heated by the refrigerant instead of being cooled. If the saturation temperature in the evaporator 5 is lower than that of the inflowing refrigerant, the liquefaction of the refrigerant can even continue in the evaporator 5 and the storage chamber 2 can be heated by released heat of condensation.
  • a temperature of +18°C which is appropriate for tempering red wine, can be achieved in storage chamber 3, even if the ambient temperature is lower.
  • the only limitation is that the temperature of the evaporator 5 cannot be lower than that of the downstream evaporator 6, but this in no way limits the possibilities of using the storage chamber 2, provided that the chamber 3 is operated as a freezer compartment and the temperature of its evaporator 6 is in any case the lowest temperature that can be practically achieved in the refrigerant circuit.
  • the throttle point 9 is formed exclusively by a capillary 25 as described above, without an expansion valve.
  • the throttling point 9 cannot then be adjusted, but the pressure in the evaporator 4 can still be adjusted by adjusting the flow conductance of the throttling point 10, can be set arbitrarily.
  • an adjustment of the throttling point 10 affects the total refrigerant throughput of the two branches 11, 12, this can be compensated for by adjusting the speed of the compressor 18 and the flow conductance values of the throttling points 13, 14.
  • the refrigerant circuit of a refrigeration device can also have more than the 1 shown two mutually parallel branches 11, 12 have.
  • such an additional parallel branch could also include two evaporators connected in series and only meet the suction line again downstream of the evaporator 6 .
  • either the pressure and temperature in the downstream evaporator of the additional branch would be the same as in the evaporator 6, or a throttling point would be required at the outlet of the two branches, which, if it causes a pressure drop, would also result in an unsuitably low temperature of the refrigerant causes in the suction line 16.
  • each branch comprises only one evaporator and their confluence 15 is always followed by a common evaporator 6 of a storage chamber 4 that can be used as a freezer compartment.
EP16751305.0A 2015-09-03 2016-08-16 Kältegerät mit mehreren lagerkammern Active EP3344931B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015216933.2A DE102015216933A1 (de) 2015-09-03 2015-09-03 Kältegerät mit mehreren Lagerkammern
PCT/EP2016/069371 WO2017036777A1 (de) 2015-09-03 2016-08-16 Kältegerät mit mehreren lagerkammern

Publications (2)

Publication Number Publication Date
EP3344931A1 EP3344931A1 (de) 2018-07-11
EP3344931B1 true EP3344931B1 (de) 2022-10-12

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Application Number Title Priority Date Filing Date
EP16751305.0A Active EP3344931B1 (de) 2015-09-03 2016-08-16 Kältegerät mit mehreren lagerkammern

Country Status (5)

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US (1) US10928102B2 (zh)
EP (1) EP3344931B1 (zh)
CN (1) CN107923667B (zh)
DE (1) DE102015216933A1 (zh)
WO (1) WO2017036777A1 (zh)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107356003B (zh) 2016-05-10 2021-04-20 比亚迪股份有限公司 热泵空调系统及电动汽车
CN107351624B (zh) * 2016-05-10 2020-08-25 比亚迪股份有限公司 热泵空调系统及电动汽车
DE102018206221A1 (de) 2018-04-23 2019-10-24 BSH Hausgeräte GmbH Kältegerät mit beheizbarem Innenraum
DE102019210539A1 (de) * 2019-07-17 2021-01-21 BSH Hausgeräte GmbH Haushaltskältegerätevorrichtung
DE102019213220A1 (de) * 2019-09-02 2021-03-04 BSH Hausgeräte GmbH Kältegerät mit heiz- und kühlbaren Fächern
DE102019216582A1 (de) * 2019-10-28 2021-04-29 BSH Hausgeräte GmbH Kältegerät mit heiz- und kühlbarem Fach
DE102019218352A1 (de) * 2019-11-27 2021-05-27 BSH Hausgeräte GmbH Kältegerät mit variabel nutzbarem Fach
US11885544B2 (en) * 2019-12-04 2024-01-30 Whirlpool Corporation Adjustable cooling system

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US20100218519A1 (en) * 2009-02-27 2010-09-02 Electrolux Home Products, Inc. Fresh food ice maker control
DE102013223737A1 (de) * 2013-11-20 2015-05-21 BSH Hausgeräte GmbH Einkreis-Kältegerät

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US20100218519A1 (en) * 2009-02-27 2010-09-02 Electrolux Home Products, Inc. Fresh food ice maker control
DE102013223737A1 (de) * 2013-11-20 2015-05-21 BSH Hausgeräte GmbH Einkreis-Kältegerät

Also Published As

Publication number Publication date
CN107923667A (zh) 2018-04-17
US20180231277A1 (en) 2018-08-16
WO2017036777A1 (de) 2017-03-09
DE102015216933A1 (de) 2017-03-09
EP3344931A1 (de) 2018-07-11
CN107923667B (zh) 2021-08-10
US10928102B2 (en) 2021-02-23

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