EP3604988A1 - Appareil de réfrigération avec une pluralité de zones de température - Google Patents

Appareil de réfrigération avec une pluralité de zones de température Download PDF

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Publication number
EP3604988A1
EP3604988A1 EP19180899.7A EP19180899A EP3604988A1 EP 3604988 A1 EP3604988 A1 EP 3604988A1 EP 19180899 A EP19180899 A EP 19180899A EP 3604988 A1 EP3604988 A1 EP 3604988A1
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EP
European Patent Office
Prior art keywords
evaporator
temperature
cooling
blow
openings
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.)
Granted
Application number
EP19180899.7A
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German (de)
English (en)
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EP3604988B1 (fr
Inventor
Emanuele Diana
Christian Schropp
Adrian Bachmann
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V-Zug AG
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V-Zug AG
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Publication date
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Publication of EP3604988A1 publication Critical patent/EP3604988A1/fr
Application granted granted Critical
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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
    • F25D17/065—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators with compartments at different 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/062—Capillary expansion 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
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting 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
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/067—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by air ducts
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/12—Sensors measuring the inside temperature
    • F25D2700/123—Sensors measuring the inside temperature more than one sensor measuring the inside temperature in a compartment

Definitions

  • the invention relates to a cooling device with several temperature zones and a method for its operation according to the preamble of the main claims.
  • US 2009/0188262 describes a cooling device whose cooling space is divided into several temperature zones with different target temperatures.
  • a cooling air duct is provided, in which air is drawn in from the uppermost temperature zone. The air is guided along the evaporator and led back into the temperature zones via several connection openings.
  • To the Air flaps are provided for connection openings, which are individually controlled. The temperature in the temperature zones is regulated by suitable control of these air flaps.
  • the object is to provide a cooling device of this type or a method for controlling it with improved temperature control.
  • the compressor is also designed to convey the cooling medium from bottom to top through the first evaporator. With this flow direction of the cooling medium, there is significantly more liquid cooling medium in a lower region of the first evaporator than in the upper region. Since the liquid cooling medium draws more heat from its surroundings when it evaporates than the medium that has already evaporated, this leads to a relatively strong, vertical temperature gradient in the first evaporator. Accordingly, the air that flows through the various blow-back openings is cooled to different degrees.
  • the control of the device is designed to control the amount of liquid medium in the first evaporator depending on the target temperatures and the actual temperatures in the temperature zones.
  • control can be designed to set the upper limit of the liquid cooling medium in the first evaporator depending on the target temperatures and the actual temperatures in the temperature zones above or below at least one first blow-back opening. If this upper limit lies below this first blow-back opening, the air conveyed through this first blow-back opening is cooled less than if the upper limit lies above the first blow-back opening.
  • At least one second blow-back opening is advantageously provided below (i.e. lower than) the first blow-back opening.
  • the cooling capacity between the first and the second blow-back opening which can be used for individual regulation of the cooling capacity in the region of the two blow-back openings.
  • a particularly good regulation can be achieved if the control also controls the delivery capacity of the fan depending on the target temperatures and the actual temperatures.
  • the outlet temperature can be increased at the blow-back openings, in particular at the blow-back openings which are lower than the upper limit of the liquid cooling medium.
  • the delivery capacity of the compressor is also a good control parameter. Accordingly, the control can be configured to control the delivery capacity of the compressor depending on the target temperatures and the actual temperatures in the temperature zones.
  • the present technique it is possible to control the temperatures at the blowback openings without the closure means controlled at the blowback openings, e.g. Air flaps are arranged.
  • the invention can also be used in combination with such controlled closure means in the blow-back openings, in which case the temperatures can be regulated even better and / or with greater efficiency.
  • At least two throttles can be arranged between the condenser and the first evaporator, and a changeover valve can be provided in order to vary the flow ratio of cooling medium between the two throttles.
  • the ratio of the flows through the two chokes with the Changeover valve can be varied.
  • the changeover valve can either guide the cooling medium through one or the other throttle, or the ratio can also be set variably.
  • the control can be configured to control the amount of liquid medium in the first evaporator at least via the changeover valve.
  • At least one second evaporator in addition to the first evaporator, at least one second evaporator can be provided.
  • the first of the throttles leads cooling medium from the compressor past the second evaporator to the first evaporator.
  • the second of the throttles leads cooling medium from the compressor to the second evaporator.
  • more or less cooling medium can be passed through the second evaporator via the changeover valve, as a result of which the amount of liquid cooling medium and the evaporation temperature in the first evaporator can be varied.
  • a higher resulting air temperature can result from overheating of the refrigerant in the first evaporator.
  • the invention also relates to a method for operating such a cooling device.
  • the amount of liquid cooling medium in the first evaporator is controlled depending on the target temperatures and the actual temperatures in the temperature zones.
  • the delivery rate of the compressor and / or the delivery rate of the fan can also be controlled depending on the target temperatures and the actual temperatures in the temperature zones.
  • the cooling device is advantageously a refrigerator and / or a freezer, in particular a household appliance. However, it can also be a refrigerator for other applications, e.g. a cooling device for medication or other refrigerated goods.
  • top, bottom, horizontal and vertical refer to the intended orientation of the device, in which the door runs vertically.
  • An “insulation material” is a body with a thermal conductivity of less than 0.1 W / mK, in particular less than 0.05 W / mK. With vacuum insulation panels, the value can even be below 0.01 W / mK, e.g. at 0.003 - 0.006 W / mK.
  • the refrigerator has a housing 1, in the interior of which a useful space 2 is arranged for receiving food to be stored.
  • the usable space 2 In a section in the vertical direction, the usable space 2 has an approximately rectangular cross section.
  • a rear wall element 3 is arranged on the rear wall 2a of the usable space Fig. 2 is highlighted in bold outline.
  • the usable space is divided into two temperature zones 2a, 2b.
  • An intermediate wall 11 is arranged between the two temperature zones 2a, 2b, which e.g. can have the shape of a shelf or drawer lid.
  • the intermediate wall 11 is designed in such a way that it allows an air exchange between the two temperature zones 2a, 2b.
  • the intermediate wall can have an insulation material.
  • Different target temperatures are assigned to the temperature zones 2a, 2b.
  • the target temperatures advantageously increase from bottom to top, i.e. the lowest target temperature is assigned to the lowest temperature zone 2a.
  • the rear wall element 3 is in 3 - 7 from the front and back and in Fig. 8 shown in a vertical section.
  • It has an essentially rectangular outline and is plate-shaped. It has a molded body 4 made of an insulating material, e.g. made of expanded polystyrene.
  • a cover plate 5 is attached on the front of the molded body 4. It consists of a material of higher strength than the molded body 4. It is preferably made of plastic.
  • the cover plate 5 preferably extends on the front over the entire wall element 3 or at least over the entire molded body 4.
  • the rear wall element 3 preferably has a first section 3a (cf. Fig. 7 . 8th ) and a second section 3b.
  • the fan 10 is arranged in section 3a.
  • the rear wall element 3 is thicker in the direction from the front to the rear than in the second section 3b. This takes into account the fact that the two parts 6a, 6b of the cooling air duct overlap in section 3a, while this is not the case in section 3b. With this configuration, the rear wall element 3 takes up less volume.
  • rear wall element 3 is, however, of minor importance in the present case.
  • it can also have a simpler plate shape.
  • Cooling air duct
  • a cooling air duct 6 can be formed in or on the rear wall element 3 (or elsewhere in the device). It is used to guide cooling air past an evaporator. An exemplary structure of the cooling air duct is described in more detail below.
  • a first part 6a of the cooling air duct is configured on the front of the molded body 4, namely between the molded body 4 and the cover plate 5.
  • This first part is best made of Fig. 4 and 10 seen.
  • the cooling air duct has a plurality of intake openings 7a-7i.
  • intake openings 7a-7i e.g. four suction openings 7a - 7d on the lateral edges 8a, 8b of the rear wall element 3, in particular in the upper quarter of the lateral edges 8a, 8b, and the rest on the upper edge 8c.
  • the suction openings 7a-7i form channel sections which are formed between depressions 9a, 9b, 9c ... in the molded body 3 and the cover plate 5 and which lead to a fan 10.
  • the fan 10 is arranged in the present example with an opening 12 extending from the front to the rear through the molded body and in Fig. 9 presented in detail.
  • the fan 10 shown has a rigid frame 14 in which a fan wheel 15 and its drive are arranged.
  • the frame 14 can be fastened to the molded body 4 via a damping element 16.
  • the damping element 16 can in turn be attached to the molded body 4 in a suitable manner. This is how best to look at 6, 7 and 9 can be seen, a holding frame 18 is provided in the present embodiment. The damping element 16 is clamped between a shoulder 20 of the molded body 4 and the holding frame 18.
  • the holding frame 18 is inserted in a recess of the molded body 4 and is preferably snapped there into undercuts 24, so that it can only be removed with deformation.
  • the holding frame 18 has projections 26 projecting to the rear, which are supported against the front of the rear wall 30, which is located behind the rear wall element 3 and forms a counter bearing 32, when the rear wall element 3 is installed as intended.
  • the second part 6b of the cooling air duct adjoins the opening 10, cf. Fig. 6 . 9 . 10 ,
  • the molded body 4 has on its rear side one or more recesses 34 which form or form the front area of part 6b of the cooling air duct.
  • the recess 34 extends from the area of the fan 10 towards the bottom, to the lower end of the molded body 4.
  • the molded body 4 can form at least two lateral boundaries 36 for the recess 34, which touch the rear wall 30 in the assembled state of the wall element 3 and thus laterally limit the cooling air duct.
  • One or preferably both of these boundaries 36 has or have recessed areas which do not touch the rear wall and which form a plurality of laterally arranged first blowback openings 38a-38m of the cooling air duct on the side edges 8a, 8b of the rear wall element 3.
  • the first blow-back openings 38a-38m lead into the first temperature zone 2a.
  • the rear wall also forms laterally arranged second blowback openings 38n. These lead to the second temperature zone 2b.
  • the shaped body 4 shown forms an upper boundary 39a of the recess 34, which contacts the rear wall 30 in the assembled state of the wall element 3. This advantageously closes off the second part 6b of the cooling air duct at the top.
  • the shaped body 4 shown forms a lower boundary 39b of the recess 34.
  • the lower boundary 39b has one or more recessed areas which do not touch the rear wall 30 and thus one or more lower, second blow-back openings 43 for forms the cooling air duct on the lower edge 8d of the rear wall element 3.
  • the lower second blow-back openings 43 also lead into the second temperature zone 2b.
  • the molded body 4 can form spacers 37 which support the recess 34 against the rear wall.
  • spacers 37 can also be used as air guiding elements.
  • the recess 34 is advantageously not the same depth everywhere.
  • it has an upper, lower region 34a and a lower, less deep region 34b. This configuration allows the air flow in the cooling air duct to be brought into a desired ratio in accordance with the requirements.
  • the evaporator 40 of a heat pump is arranged in the rear wall 30 of the cooling device. It is thermally connected to a wall plate 42, which forms the inside of the rear wall 30, that is to say the side facing the useful space 2.
  • the present embodiment of the cooling device has two evaporators, which is why the evaporator 40 is sometimes referred to below as the "first evaporator 40".
  • the terms “first” and “second” evaporator are used only for Enumeration does not use and do not describe the flow order of the evaporators.
  • the refrigerant preferably flows first through the second and then through the first evaporator.
  • an insulation element 44 in particular a vacuum insulation panel, is arranged.
  • the area of the cooling air duct 6a, 6b which is in contact with the evaporator 40 is referred to as the cooling section 13.
  • blow-back openings 38a-38n and 43 are arranged along the cooling section 13 at different, vertically spaced positions.
  • the fan 10 conveys the air from front to back, i.e. it sucks in the air through the suction openings 7a - 7i, conveys it through the first part 6a of the cooling air duct, through the opening 12, through the second part 6b of the cooling air duct and to the blowback openings 38a - 38n and 43.
  • the air is cooled by the evaporator 40 as it passes through the second part 6b of the cooling air duct.
  • the air essentially runs from top to bottom through the cooling air duct and sweeps past the cooling element or evaporator 40 from top to bottom.
  • the cooling element i.e. the evaporator 40
  • the wall plate 42 can also be arranged in the cooling air duct itself and e.g. be surrounded by cooling air on both sides.
  • the evaporator is of secondary importance in the present context.
  • it can be foamed in or arranged freely in the air flow.
  • it can be a Trade tube, roll bond or a finned heat exchanger.
  • the cooling device has a heat pump with a compressor 50, a condenser 52, a changeover valve 54, a plurality of throttles 56a, 56b (which in the present case are configured as capillaries), the first evaporator 40 and a second evaporator 58.
  • the components of the cooling device are controlled by a controller 60. This can also communicate with sensors that measure the current state of the device, e.g. a first temperature sensor 62a for measuring the temperature in the first temperature zone 2a and a second temperature sensor 62b for measuring the temperature in the second temperature zone 2b.
  • sensors that measure the current state of the device, e.g. a first temperature sensor 62a for measuring the temperature in the first temperature zone 2a and a second temperature sensor 62b for measuring the temperature in the second temperature zone 2b.
  • the compressor 50 has a variable speed, i.e. it can be operated by the controller 60 at several different speeds> 0.
  • the switching valve 54 is controlled by the controller 60. In the present embodiment, the flow of the cooling liquid between the throttles or capillaries 56a, 56b can thus be switched.
  • the first capillary 56a leads from the changeover valve 54 to the input of the first evaporator 40 already described.
  • the second capillary 56b leads from the changeover valve 54 to the input of the second evaporator 58.
  • the second evaporator 58 is assigned to a freezer compartment 64. This is thermally separated from the utility room 2 and it is usually operated at a lower temperature than the utility room 2, e.g. at a target temperature of -25 ° C to - 10 ° C.
  • the cooling device can be operated in at least two operating modes.
  • the changeover valve 54 is set such that the cooling medium flows through the second capillary 56b. Thus, it first passes through the second evaporator 58, where it can (depending on the temperature conditions) at least partially evaporate. Then it reaches the first evaporator 40 via a connecting line 66.
  • the changeover valve 54 is set such that the cooling medium flows through the first capillary 56a. It thus bypasses the second evaporator 58 and enters the first evaporator 40 directly.
  • the cooling medium enters the second evaporator 40 from below.
  • the liquid phase of the cooling medium will thus accumulate in the lowest area of the evaporator 40.
  • the upper limit of the liquid cooling medium is in Fig. 11 for example, drawn in under reference number 68.
  • the cooling effect of the first evaporator 40 is stronger below this upper limit 68 than above.
  • the cooling medium returns to the compressor 50 via a return line 70.
  • the return line 70 can be coupled to the throttles or capillaries 56a, 56b via a heat exchanger 72. This improves the efficiency of the device.
  • the cooling air duct is generally designated by reference number 6.
  • the fan is not shown.
  • the cooling air which flows through the intake openings into the cooling air duct 6a, 6b and from there through the blow-back openings 37a-38n, 43 back into the useful space 2, is illustrated with arrows.
  • the cooling air is drawn in from the first temperature zone 2a (arrows 72a). It flows down through the cooling air duct 6. In particular, it runs from top to bottom through the cooling section 13 along the first evaporator 40.
  • the cooling air enters the blow-back openings 38a-38n, 43 at various vertical positions.
  • blow-back openings 38a-38m in the example above, arrows 72b If it passes through one of the upper blow-back openings (blow-back openings 38a-38m in the example above, arrows 72b), it flows into the first temperature zone 2a. If it passes through one of the lower blowback openings (blowback openings 38n and 43, arrows 72c), it enters the second temperature zone 2b.
  • the air is conveyed upward from the second temperature zone 2b through one or more gaps or openings 74 in the region of the intermediate wall 11 into the first temperature zone 2a.
  • the cooling effect of the first evaporator 40 depends on where the upper limit 68 of the liquid cooling medium lies.
  • this upper limit 68 is relatively high (as in Fig. 12 68a), at least a portion of the cooling air is cooled before flowing back through the upper ("first") blow-back openings 38a-38m into the first temperature zone 2a. A relatively strong cooling of the first temperature zone 2a can thus be achieved.
  • Another important operating parameter of the cooling device is the delivery rate of the fan 10.
  • the air stays longer in the cooling section 13 and is noticeably cooled by the evaporator 40.
  • the lower or both temperature zones 2a, 2b can thereby be cooled.
  • T1 and T2 denote the instantaneous temperatures in the first and second temperature zones 2a, 2b and Tlsoll and T2soll their target temperatures.
  • high liquid level in the evaporator 40 is a state in which the upper limit 68 of the liquid cooling medium in the evaporator 40 lies above at least the lowest first blow-back opening 38m, preferably above at least half of the first blow-off openings 38a-38n, in particular above all of the first blow-back openings 38a-38n.
  • a “low liquid level” in the evaporator 40 is a state in which the upper limit 68 of the liquid cooling medium in the evaporator 40 is below the lowest first blow-back opening 38m, but in particular above a part, preferably all, of the second blow-back openings 38n, 43. Possible measures for influencing this the upper limit 68 are described above.
  • the controller 60 controls the device in such a way that the deepest liquid level in the evaporator 40 is at most, by which Reduce cooling capacity.
  • the upper limit 68 is advantageously set so low that at least some of the second blow-back openings 38n, 43 lie above the upper limit 68.
  • the controller 60 can at least temporarily increase the delivery capacity of the fan 10. Both measures reduce the cooling of the air in the cooling air duct 6.
  • T1 ⁇ T1soll and T2> T2soll The controller 60 controls the device in such a way that the deep liquid level is established in the evaporator 40, so that primarily only the air flowing into the second temperature zone 2b is cooled. At the same time, the delivery rate of the fan can, if necessary, be reduced at least temporarily in order to greatly cool the air that enters the second temperature zone 2b.
  • T1> T1soll and T2 ⁇ T2soll The controller 60 controls the device so that the high liquid level is established in the evaporator 40, so that the air flowing into the first temperature zone 2a is also cooled.
  • the delivery rate of the fan is preferably chosen to be at least temporarily so great that the air in the air duct 6a, 6b has no time to cool down significantly, so that its temperature when it passes through the second blow-back openings 38n, 43 has a temperature greater than T2soll.
  • T1> T1soll and T2> T2soll The controller 60 controls the device in such a way that the high liquid level is set in the evaporator 40, so that the air flowing into the first temperature zone 2a is also cooled.
  • the delivery rate of the fan is selected at least temporarily so low that the air in the air duct has enough time to cool down so much that its temperature when passing through the second blow-back openings 38n, 43 is less than T2soll, and that its temperature when passing through through at least part of the first blow-back openings 38a-38m has a temperature lower than T1soll.
  • a further manipulated variable is the speed or delivery capacity of the compressor 50.
  • the cooling capacity can be increased and at the same time the evaporation temperature can be reduced.
  • the cooling capacity can be reduced and the evaporation temperature increased by reducing the speed.
  • the first temperature zone 2a is advantageously a cooling compartment with a target temperature Tlsoll between 0 ° and 10 ° C, in particular between 2 and 7 ° C.
  • the second temperature zone 2b is a cold storage compartment with a target temperature T2set between -2 ° and 3 ° C, in particular between 0 ° and 3 ° C.
  • the difference T1soll - T2soll is advantageously at most 10 ° C, in particular at most 5 ° C, e.g. to keep the condensation in the cold areas low.
  • the delivery rate of the fan 10 should be controllable in a range sufficient to carry out the above measures.
  • a delivery rate in the range of 10 to 30 m 3 / h has proven to be useful, for example.
  • Other funding options are conceivable. They depend, among other things, on the size of usable space 2 and the operating parameters of the heat pump and can be determined experimentally or mathematically.
  • two temperature zones 2a, 2b are provided. However, more than two temperature zones can also be provided.
  • the temperature zones are advantageously arranged one above the other and / or separated from one another by horizontal partition walls 11.
  • the at least one suction opening 7a-7i is arranged higher than the blow-back openings 38a-38n, 43, or with the fan 10, the air is guided from top to bottom through the cooling section 13, so that the strong temperature gradient in the evaporator 40 is efficient Control of temperatures can be used.
  • At least one of the suction openings 7a-7i opens into the first temperature zone 2a. All the suction openings 7a-7i advantageously open into the first temperature zone. However, it is conceivable that at least one suction opening also opens into the second temperature zone 2b.
  • the fan 10 advantageously conveys the air from bottom to top, i.e. the air passes from the lower, second temperature zone 2b into the upper, first temperature zone 2a.
  • a refrigerator is shown in the above examples.
  • the refrigerator can e.g. can also be designed as a freezer or wine cooler or for other refrigerated goods, and / or it can be a combination device with several cooling zones for different temperatures.
  • the cooling air duct can also be arranged at least partially or completely elsewhere in the device, e.g. in a side wall.
  • freezer compartment 64 is optional.

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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)
  • Combustion & Propulsion (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP19180899.7A 2018-08-02 2019-06-18 Appareil de réfrigération avec une pluralité de zones de température Active EP3604988B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH00948/18A CH715229A1 (de) 2018-08-02 2018-08-02 Kühlgerät mit mehreren Temperaturzonen.

Publications (2)

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EP3604988A1 true EP3604988A1 (fr) 2020-02-05
EP3604988B1 EP3604988B1 (fr) 2024-03-27

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CH (1) CH715229A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021259630A1 (fr) * 2020-06-22 2021-12-30 BSH Hausgeräte GmbH Dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration et procédé d'actionnement d'un dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration

Citations (5)

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Publication number Priority date Publication date Assignee Title
US1642015A (en) * 1921-06-04 1927-09-13 Delco Light Co Refrigerating apparatus
WO1995010742A1 (fr) * 1993-10-12 1995-04-20 Hyde Robert E Deshumidification de l'air dans un environnement climatise
WO2006049354A1 (fr) * 2004-11-02 2006-05-11 Lg Electronics, Inc. Refrigerateur
US20090188262A1 (en) 2008-01-30 2009-07-30 Libeherr-Hausgeraete Ochsenhausen Gmbh Method of Operating a Refrigerator Unit and/or Freezer Unit as well as a Refrigerator Unit and/or Freezer Unit Operated Using Such a Method
EP2988077A1 (fr) * 2014-08-18 2016-02-24 Paul Mueller Company Systèmes et procédés pour faire fonctionner un système de réfrigération

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Publication number Priority date Publication date Assignee Title
US5711159A (en) * 1994-09-07 1998-01-27 General Electric Company Energy-efficient refrigerator control system
US6931870B2 (en) * 2002-12-04 2005-08-23 Samsung Electronics Co., Ltd. Time division multi-cycle type cooling apparatus and method for controlling the same
JP4303062B2 (ja) * 2003-08-29 2009-07-29 日立アプライアンス株式会社 冷蔵庫
US8056360B2 (en) * 2006-11-22 2011-11-15 Paul Neilson Unmack Absorption refrigeration protective controller
CH709751B1 (de) * 2015-11-09 2019-06-28 V Zug Ag Kühlgerät mit einem Nutzraum mit mehreren Temperaturzonen.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1642015A (en) * 1921-06-04 1927-09-13 Delco Light Co Refrigerating apparatus
WO1995010742A1 (fr) * 1993-10-12 1995-04-20 Hyde Robert E Deshumidification de l'air dans un environnement climatise
WO2006049354A1 (fr) * 2004-11-02 2006-05-11 Lg Electronics, Inc. Refrigerateur
US20090188262A1 (en) 2008-01-30 2009-07-30 Libeherr-Hausgeraete Ochsenhausen Gmbh Method of Operating a Refrigerator Unit and/or Freezer Unit as well as a Refrigerator Unit and/or Freezer Unit Operated Using Such a Method
EP2988077A1 (fr) * 2014-08-18 2016-02-24 Paul Mueller Company Systèmes et procédés pour faire fonctionner un système de réfrigération

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021259630A1 (fr) * 2020-06-22 2021-12-30 BSH Hausgeräte GmbH Dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration et procédé d'actionnement d'un dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration

Also Published As

Publication number Publication date
CH715229A1 (de) 2020-02-14
EP3604988B1 (fr) 2024-03-27

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