EP3599434A1 - Appareil de refroidissement à circuit unique - Google Patents

Appareil de refroidissement à circuit unique Download PDF

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Publication number
EP3599434A1
EP3599434A1 EP19184581.7A EP19184581A EP3599434A1 EP 3599434 A1 EP3599434 A1 EP 3599434A1 EP 19184581 A EP19184581 A EP 19184581A EP 3599434 A1 EP3599434 A1 EP 3599434A1
Authority
EP
European Patent Office
Prior art keywords
condenser
thermal mass
refrigerator according
refrigerant
circuit
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.)
Withdrawn
Application number
EP19184581.7A
Other languages
German (de)
English (en)
Inventor
Lincoln Massashi Takemoto
Hans Ihle
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
Original Assignee
BSH Hausgeraete 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 Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Publication of EP3599434A1 publication Critical patent/EP3599434A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures

Definitions

  • the present invention relates to a single-circuit refrigerator with two storage zones to be kept at different operating temperatures, such as a normal refrigerator compartment and a freezer compartment.
  • evaporators of the two temperature zones are connected in series in a refrigerant circuit, so that the mass flow of the refrigerant through the two evaporators is the same.
  • different operating temperatures of the two storage compartments can result from different dimensions of the two evaporators and from the fact that only the refrigerant that has passed through the first evaporator in liquid form can evaporate in the second evaporator.
  • a known disadvantage of such single-circuit refrigeration devices is that the distribution of the available cooling capacity over the various storage zones can hardly be changed, but that the ratio of the cooling capacities that are required for maintaining the operating temperatures in the two storage zones depends on the ambient temperature. If this decreases, this affects the cooling capacity requirement of the warmer temperature zone more than that of the colder one, and there is a risk that if the refrigeration is regulated on the basis of the temperature of the warmer temperature zone, insufficient refrigeration will be generated to cool the colder one to keep the two temperature zones at their operating temperature.
  • a common approach to solving this problem is to install a heat source in the warmer temperature zone that can be operated at a low ambient temperature in order to ensure a longer compressor runtime, which is also sufficient for sufficient cooling of the colder storage compartment.
  • the operation of such a heat source inevitably affects the energy efficiency of the refrigerator.
  • a single-circuit refrigeration device in which a thermal mass is attached to the refrigerant line of a condenser in order to absorb heat that is released during the condensation of the refrigerant when the compressor is running and to release it to the environment during a standstill phase of the compressor. Furthermore, the free cross section of the refrigerant line is by deforming or inserting of a foreign body is narrowed to reduce the amount of liquid refrigerant stored in the condenser.
  • the object of the invention is to provide a single-circuit refrigeration device in which the heat source can be dispensed with or at least the frequency with which the heat source must be operated is reduced, or the range of the ambient temperature in which the refrigeration device can be operated without that the heat source is needed is enlarged.
  • the object is achieved in a single-circuit refrigeration device with a first and a second storage zone, in which a compressor follows one another along a refrigerant line between a pressure connection and a suction connection: a condenser, a throttle point, a first evaporator for cooling the first storage zone and a second evaporator for cooling the second storage zone, and with a thermal mass arranged in contact with the condenser, the thermal mass is predominantly arranged at a downstream region of the condenser.
  • the pressure in the condenser must be higher than the vapor pressure of the refrigerant at the temperature that the refrigerant has reached at the evaporator outlet. Consequently, the condensation of the refrigerant takes place predominantly in an upstream region of the condenser, while it cools down to the boiling temperature corresponding to the prevailing pressure; In comparison, in a downstream area of the condenser, through which the refrigerant then passes, only a little heat is released. At high ambient temperatures, the thermal mass has little influence on the liquid refrigerant, because the amount of liquid refrigerant that collects in the downstream area of the condenser and can give off heat to the thermal mass decreases on average with increasing ambient temperature.
  • a low ambient temperature means that the cooling capacity requirement in the warmer of the two storage zones decreases proportionally more than in the colder one. If the compressor is controlled by a temperature sensor located in the warmer of the two storage zones, this can result in the colder storage zone not being cooled sufficiently. However, if this is the first of the two storage zones, a reduced supply of the evaporator with liquid refrigerant at a low ambient temperature will result in enough liquid refrigerant only after an extended compressor runtime (or, in the case of a speed-controlled, continuously running compressor, at an increased delivery rate) reaches the second evaporator to keep the second storage zone at its operating temperature. This means that more liquid refrigerant is available for the first evaporator, and the interval of the ambient temperatures in which both temperature zones can be kept at their operating temperatures without heating of the second temperature zone being increased.
  • a refrigerant pipe that extends through the condenser from an inlet to an outlet must not be in contact with the thermal mass over its entire length, but should be in contact with the thermal mass over at least a quarter of its length in order to be able to form a sufficiently long supercooling zone.
  • the quarter can be distributed over several sections of the refrigerant pipe, between which the contact with the thermal mass is interrupted; Such an interruption can, as described in more detail below, be found in particular on the elbows of the refrigerant pipe.
  • a single section extends continuously over at least a quarter of the length of the refrigerant tube in contact with the thermal mass.
  • the refrigerant pipe should run at least a quarter of its length without contact with the thermal mass in order to allow the heat of condensation to be released directly to the environment.
  • This quarter is also here Length is preferably formed by a single section of the refrigerant tube which extends continuously without contact with the thermal mass.
  • the condenser is in the form of a plate and is installed in the refrigerator in a vertically elongated orientation, then in particular an upper half of the condenser should be free of the thermal mass in order to allow the heat of condensation to be released; the thermal mass, however, should be concentrated in a lower half of the condenser in order to absorb the supercooling heat of the liquid refrigerant collecting there.
  • a shut-off valve can be provided in the refrigerant line between the condenser and the first evaporator in order to prevent pressure equalization between the condenser and the evaporator during a standstill phase of the compressor. This prevents warm refrigerant from the condenser from reaching the first evaporator towards the end of a pressure equalization; on the other hand, the efficiency of refrigeration increases because the pressure difference between the condenser and evaporator does not have to be rebuilt each time the compressor is started.
  • the flow rate of the compressor can be adjusted to several non-vanishing values, i.e. especially if it is a speed-controlled compressor, the throughput of the compressor can be set so that the compressor does not come to a standstill as long as the refrigeration device is not completely switched off. In such a case, the shut-off valve is not required to maintain the pressure difference between the condenser and the compressor.
  • the thermal mass can comprise bitumen, possibly with fillers such as a mineral powder.
  • the thermal mass is plastic at elevated temperature, it can be attached to the condenser in a simple manner by pressing a refrigerant tube of the condenser into the heated thermal mass and allowing the thermal mass to cool.
  • the thermal mass can be in the form of a rectangular blank, at least one edge length of which is smaller than a corresponding edge length of the condenser, so that when the blank is placed on the plate-shaped condenser, the refrigerant tube of the condenser is only at a part of its length with the thermal Mass can come into contact.
  • a frame heater can be inserted in the refrigerant line between the condenser and the throttle point; This can also help to collect liquid refrigerant at low ambient temperatures and keep it away from the evaporators.
  • Fig. 1 shows a single-circuit household refrigeration device 10 with a first, colder storage zone 12, here a freezer compartment and a second, warmer storage zone 14, here a refrigerator compartment.
  • the refrigerator 10 has a heat-insulated housing 16 with housing walls 17 which, together with heat-insulated doors 18, delimit interior spaces 20 of the storage zones 12 and 14.
  • a refrigerant circuit 22 is arranged on the refrigeration device 10 for cooling the interior 20.
  • This refrigerant circuit 22 comprises a compressor 24 and, along a refrigerant line 27 extending from a pressure connection 26 to a suction connection 28 of the compressor 24, a condenser 30, a throttle point 32 designed as a capillary or as an expansion valve, a first evaporator 34 cooling the first storage zone 12 and a second evaporator 36 that cools the second storage zone 14.
  • An electronic control unit 38 is connected to a temperature sensor 40 arranged on the cooling compartment 14 in order to control the compressor 24 on the basis of the temperature prevailing in the cooling compartment 14.
  • the compressor 24 may be speed controlled, i.e. it can be operated at a plurality of non-disappearing speeds, and is preferably operated at a speed at which it covers the cooling requirement of the cooling compartment 14 exactly and can be operated non-stop with small fluctuations.
  • compressor 24 may be on / off controlled; in this case there is preferably an in between the condenser 30 and the first evaporator 34 Fig. 1 provided with 33 indicated shut-off valve, which is closed by the control unit 38 in a standstill phase of the compressor 24 in order to prevent pressure equalization between the condenser 30 and the evaporators 34, 36.
  • the throttle point 32 has a low throughput of 120 l / min N 2 gas at a pressure difference of 6 bar compared to conventional refrigeration devices of the same size.
  • This low throughput favors the build-up of liquid refrigerant in front of the throttle point 32 and at the same time leads to a shortage of the liquid refrigerant behind the throttle point 32.
  • This shortage is greater the lower the ambient temperature, and leads to the fact that liquid refrigerant is already at a low ambient temperature mostly evaporates in the evaporator 34, and the portion that reaches the evaporator 36 and cools the storage zone 14 becomes less and less as the ambient temperature decreases.
  • the result is that a long run time of the compressor 24 (or a high speed of the compressor) are required to achieve a ensure sufficient supply of the evaporator 36, and that in this way there is also sufficient cooling capacity for the colder storage zone 12.
  • the throttle point 32 can be connected to the condenser 30 or the shut-off valve 33 directly or, as in FIG Fig. 1 indicated by a dashed line, connected via a frame heater 31, in which the refrigerant line 27 extends within the insulating housing walls 17 in each case adjacent to the front edges facing the doors 18.
  • the condenser 30 is plate-shaped and deviates from the illustration in FIG Fig. 1 , mounted on a rear wall of the housing 16. It comprises a refrigerant tube 42, which is inserted, for example soldered, into the refrigerant line 27 at an inlet 42 and an outlet 44, extends in one piece between the inlet 43 and the outlet 44 and on which a plurality of straight horizontal tube segments 46 and the tube segments 46 extend alternate connecting arches 48.
  • the refrigerant tube 42 further comprises a riser tube 50, which connects the inlet 43 facing the compressor 24 housed in a machine room near the bottom of the housing 16 to an apex of the refrigerant tube 42, and the horizontal tube segments 46 and the bends 48 run from the apex to the outlet 44 descending.
  • the horizontal tube segments 46 are connected in a manner known per se through wires 52 arranged to cross them, in order to stiffen the condenser 30 and to enlarge its heat-emitting surface.
  • the ascending pipe 50 has an arc 54 extending laterally, to which some of the wires 52 are also fastened in order to fix the ascending pipe 50.
  • a rectangularly cut bitumen film or plate is pressed against the refrigerant pipe 42 in the heated state as a thermal mass 56, so that its lowermost horizontal pipe segments 46 and the bends 48 connecting them run in contact with the bitumen without interruption Form section 49.
  • These pipe segments 46 and elbows 48 take up about 30% of the effective length of the condenser (the riser 50 contributes to this Heat dissipation of the condenser 30 less than the proportion proportional to its length, since the crossing wires 52 are missing on a large part of its length). Since they are located in the lower half of the condenser 30, liquid refrigerant collects there from parts of the refrigerant tube 42 located further upstream and undercools there.
  • the bituminous sheet or plate which acts as thermal mass 56, extends over the entire width of the horizontal pipe segments 46 and arches 48. At the level of the bituminous sheet or plate there are two shortened horizontal segments 46 'and an inwardly offset sheet 48 to make room for the bend 54 of the ascending pipe 50. This also runs in contact with the bitumen film or plate here, but is too short to noticeably influence the condensation of the refrigerant.
  • the course of the refrigerant tube 42 and the arrangement of the wires 52 are the same as in FIG Fig. 2 ,
  • the width of the bitumen film or plate is reduced, so that the arch 54 of the riser 50 crosses and is attached to some of the wires 52, but does not contact the thermal mass 56.
  • the rectangular shape of the bitumen film or plate means that the arcs 48 facing the riser pipe 50 have no contact with the thermal mass 56 and the part of the refrigerant pipe 42 that is in contact with it disintegrates into several sections, each over one over the other Edge 48 of the thermal mass 56 projecting.
  • Fig. 4 shows a section through a horizontal pipe segment 46 in contact with the bitumen-extending section 49 of the liquefier 30.
  • the bitumen film or plate functioning as a thermal mass 56 is molded onto the raw segment 46 from a side opposite the wires 52 and lies on a part of the latter of its scope.
  • the bitumen film or plate is preferably molded onto the condenser 30 so closely that the bitumen also comes into contact with the wires 52 or even in Gaps between the wires 52 penetrate, so that heat that initially flows out of the refrigerant in the pipe segment 46 to a side facing away from the bitumen film or plate can also be introduced into the thermal mass 56 via the wires 52.

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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)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP19184581.7A 2018-07-23 2019-07-05 Appareil de refroidissement à circuit unique Withdrawn EP3599434A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102018212209.1A DE102018212209A1 (de) 2018-07-23 2018-07-23 Einkreis-Kältegerät

Publications (1)

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EP3599434A1 true EP3599434A1 (fr) 2020-01-29

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EP19184581.7A Withdrawn EP3599434A1 (fr) 2018-07-23 2019-07-05 Appareil de refroidissement à circuit unique

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EP (1) EP3599434A1 (fr)
DE (1) DE102018212209A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4265985A1 (fr) * 2022-04-20 2023-10-25 BSH Hausgeräte GmbH Appareil frigorifique ménager pourvu de deux évaporateurs

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19510268A1 (de) * 1995-03-21 1996-09-26 Liebherr Hausgeraete Kühlgerät mit einem Normalkühlraum und einem Tiefkühlfach
DE102010003825A1 (de) * 2010-04-09 2011-10-13 BSH Bosch und Siemens Hausgeräte GmbH Drahtrohrwärmetauscher, Verfahren zu dessen Herstellung und diesen verwendendes Kältegerät
EP2390602A2 (fr) * 2010-05-27 2011-11-30 Vestel Beyaz Esya Sanayi Ve Ticaret A.S. Unité de serpentin de condenseur pour dispositifs refroidisseurs
DE102011075207A1 (de) * 2011-05-04 2012-11-08 BSH Bosch und Siemens Hausgeräte GmbH Einkreis-Kältegerät
WO2013013997A1 (fr) 2011-07-25 2013-01-31 BSH Bosch und Siemens Hausgeräte GmbH Échangeur de chaleur pour un appareil frigorifique, procédé de fabrication d'un échangeur de chaleur ainsi qu'appareil frigorifique
DE102012020896A1 (de) * 2011-10-26 2013-05-02 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19510268A1 (de) * 1995-03-21 1996-09-26 Liebherr Hausgeraete Kühlgerät mit einem Normalkühlraum und einem Tiefkühlfach
DE102010003825A1 (de) * 2010-04-09 2011-10-13 BSH Bosch und Siemens Hausgeräte GmbH Drahtrohrwärmetauscher, Verfahren zu dessen Herstellung und diesen verwendendes Kältegerät
EP2390602A2 (fr) * 2010-05-27 2011-11-30 Vestel Beyaz Esya Sanayi Ve Ticaret A.S. Unité de serpentin de condenseur pour dispositifs refroidisseurs
DE102011075207A1 (de) * 2011-05-04 2012-11-08 BSH Bosch und Siemens Hausgeräte GmbH Einkreis-Kältegerät
WO2013013997A1 (fr) 2011-07-25 2013-01-31 BSH Bosch und Siemens Hausgeräte GmbH Échangeur de chaleur pour un appareil frigorifique, procédé de fabrication d'un échangeur de chaleur ainsi qu'appareil frigorifique
DE102012020896A1 (de) * 2011-10-26 2013-05-02 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4265985A1 (fr) * 2022-04-20 2023-10-25 BSH Hausgeräte GmbH Appareil frigorifique ménager pourvu de deux évaporateurs

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Publication number Publication date
DE102018212209A1 (de) 2020-01-23

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