WO2015128164A1 - Appareil de froid - Google Patents

Appareil de froid Download PDF

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Publication number
WO2015128164A1
WO2015128164A1 PCT/EP2015/052373 EP2015052373W WO2015128164A1 WO 2015128164 A1 WO2015128164 A1 WO 2015128164A1 EP 2015052373 W EP2015052373 W EP 2015052373W WO 2015128164 A1 WO2015128164 A1 WO 2015128164A1
Authority
WO
WIPO (PCT)
Prior art keywords
evaporator
appliance according
refrigerating appliance
section
refrigerant
Prior art date
Application number
PCT/EP2015/052373
Other languages
German (de)
English (en)
Inventor
Andreas BABUCKE
Kudret Baysal
Original Assignee
BSH Hausgeräte 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
Application filed by BSH Hausgeräte GmbH filed Critical BSH Hausgeräte GmbH
Publication of WO2015128164A1 publication Critical patent/WO2015128164A1/fr

Links

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
    • F25D11/006—Self-contained movable devices, e.g. domestic refrigerators with cold storage accumulators
    • 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
    • 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 refrigerator, in particular a household refrigerator.
  • a combination refrigerator is described in the compressed refrigerant is first passed before reaching a freezer compartment evaporator through a arranged in a normal refrigeration compartment heat exchanger.
  • the heat exchanger acts temporarily as a condenser, via the heat released from the freezer compartment is discharged to the normal cooling compartment.
  • This heat is then removed from the normal refrigeration compartment again by the heat exchanger as an evaporator, in series with a heat to the environment donating condenser operated.
  • the condensing temperature is a few degrees higher than the ambient temperature when cooling the normal refrigeration compartment, it is correspondingly higher than the normal refrigeration compartment temperature when the freezer compartment is cooled.
  • the object of the invention is to provide a highly efficient refrigeration device with a simple refrigerant circuit.
  • the object is achieved by providing, in a refrigeration appliance, in particular a household refrigeration appliance, with a compressor, a condenser, a first evaporator, which cools a thermal buffer, a second evaporator, which cools a refrigerating compartment, a directional control valve, the flow in a first position of refrigerant through the Condenser and the first evaporator and in a second position, a flow of refrigerant through a running through the thermal buffer pressure line section and the second evaporator allowed, in the second position, the condenser upstream of the pressure line section and the second evaporator.
  • This structure allows, even if the second evaporator is supplied with refrigerant, to deliver heat via the condenser to the environment; At the same time, the cooling capacity of the second evaporator is increased by removing part of the required refrigeration from the thermal buffer.
  • This cooling can be provided with energy efficiency, since the first evaporator can operate at a higher evaporation temperature than the second evaporator in order to cool the thermal buffer. Since it is not necessary, as in DE10 2012 222 240.5, to temporarily reverse the flow direction of the refrigerant on a part of the refrigerant circuit to switch between cooling operation of the first and second evaporators, only a single simple directional control valve is needed to control the refrigerant flow.
  • a check valve should be provided to prevent, when refrigerant circulates through the first evaporator, refrigerant vapor in the second evaporator condensing out and thereby being withdrawn from the refrigerant circuit.
  • an evaporation pressure higher than the pressure in the second evaporator and enabling efficient refrigeration can be set therein.
  • the release of heat of condensation in the second evaporator is prevented, which would lead to an undesirable heating of the refrigerating compartment.
  • the pressure line section should be cut off from the flow of the refrigerant.
  • the pressure line section may extend on a plate of the first evaporator, in particular the pressure line section may be a tube which, like an evaporation tube, is soldered, glued or otherwise suitably fixed to a plate of the first evaporator or, in the case of one Lamella evaporator extends through the evaporator.
  • the first evaporator both in the release of heat extracted from the cooling compartment in the second Position of the directional control valve is used as well as for dissipating the heat in the first position of the directional control valve, the spread of heat in the thermal buffer can be minimized.
  • the pressure line section should be connected to the second evaporator via a first capillary section.
  • the pressure line section itself is formed as a capillary section. This allows in particular the use of an inexpensive directional control valve with a small line cross-section.
  • the first capillary section may be arranged in thermal contact with a suction line.
  • predominantly refrigerant vapor from the second evaporator circulates in this suction line, so that the thermal contact with this suction line allows further cooling of the circulating refrigerant in the first capillary section, even if this already during the passage through the second capillary section the temperature of the thermal Has reached buffer. Since the refrigerant circulating in the first capillary section is already pre-cooled at the first evaporator, the suction line can reach relatively low temperatures at the level of the first capillary section.
  • the suction line can be provided with a heat-insulating sheath at least at the level of the first capillary section.
  • the thermal buffer may comprise a latent heat storage.
  • the thermal buffer may comprise a further cooling compartment. The operating temperature of this cooling compartment is higher than that of the compartment cooled by the second evaporator, that is, it may be in the cooling compartment of the thermal buffer in particular to a normal refrigerated compartment and act at the cooled by the second evaporator compartment to a freezer.
  • the compartment cooled by the second evaporator form the only storage compartment of the refrigerator, and the thermal buffer includes only the latent heat storage.
  • the latent heat storage is expediently enclosed in a heat-insulating layer in this case.
  • the pressure line section may extend around the latent heat store, in particular around it, in order to exchange heat with the latent heat store over a large path length.
  • the heat released in the circulation of refrigerant through the pressure line section can be used to defrost the first evaporator.
  • means may be provided for detecting defrosting requirements existing at the first evaporator and for displacing the directional control valve into the second position and operating the compressor in the presence of defrosting requirements at the first evaporator.
  • FIG. 1 shows a schematic representation of the refrigerant circuit of a refrigerator according to a first embodiment of the invention
  • 2 shows a cross section through the housing of a refrigeration device according to the first
  • Fig. 3 is a schematic representation of the evaporator of the refrigerator; 4 shows a cross section through the housing of a refrigeration device according to a second embodiment;
  • FIG. 5 shows a schematic representation of the refrigerant circuit of a refrigeration device according to a third embodiment of the invention.
  • Fig. 6 is a longitudinal section through a latent heat storage of
  • Fig. 8 shows a cross section through the housing of a refrigerator according to the third
  • the refrigerant circuit shown in Fig. 1 comprises in a conventional manner a compressor 1 with a pressure port 2 and a suction port 3, one of the pressure port 2 outgoing pressure line 4, in series in succession, a condenser 5, a dryer 6 and a stop valve 7 are arranged , A directional valve 8 with two positions is shown here following the stop valve 7, but it is understood that both the stop valve 7 may be missing or the valves 7, 8 may be merged into a single valve with three positions, in which in one of his Positions the pressure line 4 is completely shut off.
  • the directional control valve 8 In its first position shown in FIG. 1, the directional control valve 8 directs a refrigerant flow driven by the compressor via a first capillary 9 to a first evaporator 10. An outlet of the evaporator 10 is connected to the suction port 3 via a suction line 11. In its second position, the directional control valve 8 directs the flow of the refrigerant via a second capillary 12 to a second evaporator 13. An outlet of the evaporator 13 is connected to the suction line 1 1 via a check valve 14.
  • the capillary 12 is here divided into an upstream capillary section 15 and a downstream capillary section 16.
  • the upstream capillary section 15 is in intimate thermal contact with the evaporator 10, e.g.
  • the evaporator 10 is a plate evaporator, it may extend on a plate of the evaporator 10 or, in the case of a fin evaporator, extend across the body of the fin evaporator.
  • the downstream capillary section 16 is guided in close thermal contact with a portion 17 of the suction duct 11, for example, glued within the section 17 or on its surface. This section 17 is symbolized by two rectangles in FIG. 2 for illustrative purposes, in order to express that the first capillary 9 also extends through this section 17.
  • the evaporators 10, 13 are each arranged on a compartment 18 and 19 of the refrigerator. They are embedded in a manner known per se between inner containers 26 of the compartments 18, 19 and one of the walls of a body 25 of the refrigerator filling thermal insulation layer 27.
  • the compartment 18 is referred to as a normal refrigeration compartment 18 and the compartment 19 as a freezer compartment 19, it being understood that the invention is also applicable to other types of compartment such as a fresh refrigerator or cellar compartment, provided that only the desired operating temperature of the compartment 19 is lower than that of the tray 18 is.
  • the check valve 14 would at most open when the evaporator 13 is warmer and the vapor pressure of the refrigerant contained therein higher than the pressure in the evaporator 10, but this case occurs during the cooling of the normal refrigeration compartment at best as a result of a disturbance.
  • the stop valve 7 is also closed in order to ensure that hot refrigerant flows from the condenser 5 into the evaporators 10, 13 To prevent and maintain a high pressure in the condenser 5 until the resumption of compressor operation.
  • the compressor 1 When in the second position of the directional control valve 8, the compressor 1 is in operation, the refrigerant after the directional control valve e first circulates through the capillary section 15 and cools down to normal refrigeration compartment temperature, where it gives off heat to the now functioning as a thermal buffer 33 normal cooling compartment 18.
  • FIG. 3 shows an exemplary arrangement of the evaporators 10, 13 in a schematic view.
  • the evaporators 10, 13 here each have a base plate 20, 21, on which an evaporation line 22, 23 extends in meanders.
  • the evaporators 10, 13 may be designed in particular as a tube on sheet or Rollbond evaporator.
  • the capillary 9 is guided on its way from the directional control valve 8 to the evaporator 10 on the portion 17 within the suction line 1 1.
  • the capillary 12 extends first, in its section 15, on the base plate 20 of the evaporator 10; here within an upstream loop of the evaporation line 22.
  • the capillary section 15 is preferably formed by a soldered or glued piping, even if the evaporation line 22 is not soldered, but molded by Rollbond technique. Only downstream of the section 15 enters the capillary 12 in its section 16 in the suction line 1 1 a.
  • the suction line 1 1 is here on almost its entire length, surrounded by its passage through an area surrounding the compartments 18, 19 insulating layer to the suction port 3, of a heat-insulating sheath 24.
  • a control circuit 29 controls a further embodiment of the invention according to the operation of the compressor 1 not only in a conventional manner based on the outputs of normal refrigerator compartment 18 and freezer 19 arranged temperature sensors 30, 31, but also on the basis of a Eissensors 32 on the evaporator 10. If this signaled in that the ice layer on the evaporator 10 has reached a critical strength and should be defrosted, this is done by cooling the freezer compartment 19.
  • the cooling of the freezer compartment 19 is particularly efficient in this case, since no latent heat storage must be thawed and then cooled again; the heat absorbed by the ice during defrosting must then not be withdrawn from the normal cooling compartment 18, since the water drains off and the absorbed heat is discharged from the normal cooling compartment 18.
  • the ice sensor 32 may also be substituted for other means of estimating the defrost requirement, e.g. a timer circuit which initiates a defrosting operation every a predetermined period of the cooling operation of the evaporator 10, or a counter initiating a defrosting operation after a predetermined number of door openings of the normal refrigeration compartment 18.
  • a timer circuit which initiates a defrosting operation every a predetermined period of the cooling operation of the evaporator 10, or a counter initiating a defrosting operation after a predetermined number of door openings of the normal refrigeration compartment 18.
  • FIG. 4 shows a schematic cross section through a body 25 of a refrigeration device according to a development of the present invention. While in the case of the freezer compartment 19, the thermal barrier coating rests directly on the outside of the evaporator 13, a latent heat accumulator 28 is arranged on the normal cooling compartment between the evaporator 10 and the thermal barrier coating 27 as a further constituent of the thermal buffer 33.
  • the latent heat storage 28 contains as a storage medium a material whose melting temperature corresponds to a typical operating temperature of the normal cooling compartment 18 or between the operating temperature of the normal cooling compartment 18 and the temperature setting of the evaporator 10 during cooling of the normal cooling compartment 18, so that it becomes solid during cooling of the normal cooling compartment 18 ,
  • this material absorbs heat that releases the evaporator 10 in the second position of the directional control valve 8
  • an undesirable heating of the normal cooling compartment 18 above the melting temperature of the material during cooling of the freezer compartment 19 can be avoided as long as the material is not completely melted. This allows long operating phases of the compressor 1 both when cooling the freezer compartment 19 and the normal refrigeration compartment 18 and so on contributes to the energy efficiency of the refrigerator.
  • the latent heat accumulator 28 may extend over the entire extent of the evaporator 10, as shown in FIG. In order to limit temperature fluctuations in the normal cooling compartment 18 during cooling of the freezer compartment 19, that part of the latent heat storage device 28 which is directly adjacent to the capillary section 15 is particularly effective. It is therefore also possible to attach the latent heat accumulator 28 to only a part of the evaporator 10, in contact with the capillary section 15, as indicated in FIG. 3 by a dashed outline.
  • FIG. 5 shows a further refrigerant circuit according to the invention in a representation analogous to FIG. 1.
  • Components that are already described with reference to FIG. 1 bear the same reference numerals and will not be explained again. Differences essentially relate to the construction of the evaporator 10. This here comprises a refrigerant line which is in close thermal contact with a latent heat storage 28 and the upstream capillary section 15, but no plates for heat exchange with a storage compartment.
  • FIG. 6 A suitable structure of the evaporator 10 for the refrigerant circuit of Fig. 5 is shown in Fig. 6 in a longitudinal section.
  • the capillary 9 opens into a spacious pipe or evaporation chamber 34, which is filled with a loose bed of latent heat storage 28 forming particles 35.
  • the particles 35 may be e.g. be formed as hollow spheres made of plastic, which are filled with the storage medium.
  • the refrigerant which has been expanded after emerging from the capillary 9, flows finely distributed through spaces between the particles 35 and in this way brings the storage medium to freeze in a short time.
  • the capillary section 15 is helically formed on the inside of a wall 36 of the evaporation chamber 34.
  • the capillary section 15 on a majority of its outer surface heat directly to the refrigerant and the particles 35 deliver.
  • the wall 36 itself is not involved in the heat exchange, it may consist of moderately good heat-conducting material, for example, the evaporation chamber of two thermoformed thermoformed or blown shells be composed between the welded together edges of the capillary section 15 in the evaporation chamber 34 on and exits from it.
  • the capillary section 15 does not intersect the wall 36 of the evaporation chamber 34, but is laid on the outside thereof. In order to ensure efficient heat exchange with the refrigerant and the latent heat accumulator 28, the capillary section 15 may be secured to the wall 36 by adhesive or solder 37.
  • the latent heat storage 28 may be formed by a bed of particles as shown in Figure 6;
  • the latent heat accumulator 28 is a hollow cylindrical or tubular body whose outer side is in close contact with the capillary section 15, while the refrigerant flows through the inner passage of the latent heat accumulator 28.
  • a laying of the capillary section 15 on the outside of the wall 36 is particularly useful when the evaporation chamber 34 is not cylindrical in cross-section perpendicular to the flow direction of the refrigerant.
  • FIG. 8 shows a section through the body 25 of a domestic refrigeration appliance equipped with the refrigerant circuit of FIG. 5 along a horizontal plane.
  • the evaporation chamber 34 is foamed in a rear wall of the body 25 in the thermal barrier coating 27. In order to efficiently use the space available in the rear wall, the evaporation chamber 34 has a flattened cross-section.
  • the vaporizing chamber may extend over the entire width of the rear wall, if not, a niche open to the environment for the condenser 5 may be kept next to it as shown.
  • the device does not include another storage compartment; Therefore, the evaporator 10 is used here exclusively for cooling the latent heat accumulator 28 and is thermally insulated from its environment by all-round embedding in the thermal barrier coating 27.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un appareil de froid, en particulier un appareil de froid ménager. Ledit appareil comprend un compresseur (1), un condenseur (5), un premier évaporateur (10), qui refroidit une solution tampon, un deuxième évaporateur (13), qui refroidit un compartiment frigorifique, un distributeur (8), qui, dans une première position, permet un écoulement de réfrigérant à travers le condenseur (5) et le premier évaporateur (10) et qui, dans une deuxième position, permet un écoulement de réfrigérant à travers une première partie de conduite de refoulement (15) s'étendant à travers la solution tampon thermique (18) et le deuxième évaporateur (13). Dans la deuxième position, le condenseur (5) est monté en amont de la première partie de conduite de refoulement (15) et du deuxième évaporateur (13).
PCT/EP2015/052373 2014-02-27 2015-02-05 Appareil de froid WO2015128164A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102014203615.1 2014-02-27
DE102014203615 2014-02-27
DE102014223460.3 2014-11-18
DE102014223460.3A DE102014223460A1 (de) 2014-02-27 2014-11-18 Kältegerät

Publications (1)

Publication Number Publication Date
WO2015128164A1 true WO2015128164A1 (fr) 2015-09-03

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PCT/EP2015/052373 WO2015128164A1 (fr) 2014-02-27 2015-02-05 Appareil de froid

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DE (1) DE102014223460A1 (fr)
WO (1) WO2015128164A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107975982A (zh) * 2016-10-24 2018-05-01 青岛海尔新能源电器有限公司 一种多流路热交换器、分流调节方法及冷媒循环系统
CN108700348A (zh) * 2016-03-09 2018-10-23 Bsh家用电器有限公司 具有冷冻格室和制冷剂循环系统的制冷器具以及用于运行制冷器具的方法
CN108700349A (zh) * 2016-02-19 2018-10-23 Bsh家用电器有限公司 包括多个储存室的制冷装置
CN108700346A (zh) * 2016-02-19 2018-10-23 Bsh家用电器有限公司 包括多个储存室的制冷装置
CN110657630A (zh) * 2019-10-25 2020-01-07 长虹美菱股份有限公司 一种用于冰箱的防凝露管

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998020291A1 (fr) * 1996-11-05 1998-05-14 James Timothy W Unite refrigerante a deux evaporateurs et unite de stockage d'energie thermique afferente
US20130098081A1 (en) * 2011-10-24 2013-04-25 Whirlpool Corporation Higher efficiency appliance employing thermal load shifting in refrigerators having horizontal mullion
DE102012222240A1 (de) 2012-12-04 2014-06-18 BSH Bosch und Siemens Hausgeräte GmbH Mehrzonen-Kältegerät

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998020291A1 (fr) * 1996-11-05 1998-05-14 James Timothy W Unite refrigerante a deux evaporateurs et unite de stockage d'energie thermique afferente
US20130098081A1 (en) * 2011-10-24 2013-04-25 Whirlpool Corporation Higher efficiency appliance employing thermal load shifting in refrigerators having horizontal mullion
DE102012222240A1 (de) 2012-12-04 2014-06-18 BSH Bosch und Siemens Hausgeräte GmbH Mehrzonen-Kältegerät

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108700349A (zh) * 2016-02-19 2018-10-23 Bsh家用电器有限公司 包括多个储存室的制冷装置
CN108700346A (zh) * 2016-02-19 2018-10-23 Bsh家用电器有限公司 包括多个储存室的制冷装置
CN108700348A (zh) * 2016-03-09 2018-10-23 Bsh家用电器有限公司 具有冷冻格室和制冷剂循环系统的制冷器具以及用于运行制冷器具的方法
CN107975982A (zh) * 2016-10-24 2018-05-01 青岛海尔新能源电器有限公司 一种多流路热交换器、分流调节方法及冷媒循环系统
CN107975982B (zh) * 2016-10-24 2021-03-09 青岛海尔新能源电器有限公司 一种多流路热交换器、分流调节方法及冷媒循环系统
CN110657630A (zh) * 2019-10-25 2020-01-07 长虹美菱股份有限公司 一种用于冰箱的防凝露管

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