EP0563718A1 - Dispositif frigorifique pour réfrigérateurs - Google Patents

Dispositif frigorifique pour réfrigérateurs Download PDF

Info

Publication number
EP0563718A1
EP0563718A1 EP93104613A EP93104613A EP0563718A1 EP 0563718 A1 EP0563718 A1 EP 0563718A1 EP 93104613 A EP93104613 A EP 93104613A EP 93104613 A EP93104613 A EP 93104613A EP 0563718 A1 EP0563718 A1 EP 0563718A1
Authority
EP
European Patent Office
Prior art keywords
section
capillary throttle
throttle tube
capillary
length
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Withdrawn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
EP93104613A
Other languages
German (de)
English (en)
Inventor
Bruno Ebel
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.)
KM Schmoele GmbH
Original Assignee
KM Schmoele 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 KM Schmoele GmbH filed Critical KM Schmoele GmbH
Publication of EP0563718A1 publication Critical patent/EP0563718A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2500/12—Sound
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters

Definitions

  • the invention relates to a refrigeration device for refrigerators or the like with a suction line for the conveyance of a vaporous refrigerant from an evaporator to a compressor and a capillary throttle tube arranged partially within the suction line for the expansion of the liquid refrigerant and its feed line to the evaporator.
  • a generic refrigeration device for refrigerators essentially comprises a plate evaporator consisting of interconnected sheets, a suction line for discharging the evaporated refrigerant, a compressor for drawing in and compressing the refrigerant, a condenser and a capillary throttle tube for expanding the liquefied refrigerant and its feed line to the evaporator.
  • Such refrigeration devices have long been used in refrigerators to extract heat from their contents and thus reduce the temperature prevailing in the refrigerator.
  • the low-pressure refrigerant is evaporated in the evaporator. Evaporation reduces the temperature in the cold room.
  • the compressor sucks in the steam and compresses it to a higher pressure.
  • the steam releases its heat to the outside in the downstream condenser.
  • the refrigerant is liquefied by the interaction of increased pressure and heat emission.
  • the liquid refrigerant in the capillary throttle tube is expanded to the lower pressure and gets back into the evaporator.
  • capillary throttle tubes with a very small inside diameter. This had the advantage that the capillary throttle tube could be made short, which ensured good handling and inexpensive execution.
  • the noises had a disadvantageous effect when the refrigerant was injected from the capillary throttle tube into the evaporator.
  • the noise emission was then remedied by increasing the inside diameter of the capillary throttle tubes.
  • this was associated with the disadvantageous consequence that the capillary throttle tubes had to be made very long for the same flow rate of the refrigerant.
  • the capillary throttle tube with an inner diameter D i of 0.6 mm had to have a length L K of 2000 mm.
  • the capillary throttle tubes had to be 5500 mm long under otherwise identical conditions.
  • the invention is based on the object of improving such a refrigeration device in such a way that the material used for the capillary throttle tube can be markedly reduced while reducing the injection noise.
  • the end of the capillary throttle tube on the evaporator side is now provided with a length section which is designed as a calming section.
  • the calming section has a larger inner diameter compared to the constant inner diameter of the previous length of the capillary throttle tube.
  • the length of the calming section is adjusted in such a way that the turbulence occurring during the transition from the smaller inside diameter to the larger inside diameter changes into an essentially calmed laminar flow.
  • the injection noise can be reduced to the same values as would otherwise only be achievable over the entire length if the capillary throttle tube was designed with a larger diameter.
  • the capillary throttle tubes can be made much shorter than usual, which also improves their manageability.
  • the material savings mean that the capillary throttle tubes are also available at a significantly lower cost than in the prior art. Since the capillary throttle tubes are mass products, this advantage is particularly noticeable from an economic point of view.
  • the enlargement of the inner diameter in the area of the calming section can be carried out with different manufacturing processes. For example, drawing, pressing, punching, rolling or rolling are conceivable.
  • a capillary throttle tube with a larger inner diameter can also be used and this can subsequently be narrowed to the area outside the calming section.
  • the length section of the capillary throttle tube having the calming section can be designed such that it continuously increases from the smaller inner diameter to the larger inner diameter. A laminar flow pattern is thereby achieved.
  • the transition from the length section of the capillary throttle tube with the smaller inside diameter to the calming section can be step-shaped with sharp-edged or rounded edges or else conical.
  • the capillary throttle tube is rolled up helically. This leads to a space-saving, flexible design.
  • this has a capillary throttle tube insertion section according to the features of claim 6.
  • the outer diameter of the suction line in the area of the capillary throttle tube insertion section is increased by approximately the outer diameter of the capillary throttle tube.
  • the capillary throttle tube is guided at least once helically around the suction line in front of the capillary throttle tube insertion section in accordance with the features of claim 8. Damage to the installation of the cooling device in the cooling units is also prevented in this way.
  • a further possibility of fixing the capillary throttle tube to the suction line before it is introduced into the suction line consists, according to the features of claim 9, in a connection which is produced from plastic by means of a shrink tube.
  • the shrink tube is pulled over the capillary throttle tube and the suction line and shrunk by heating, which creates the positionally stable connection.
  • the plate evaporator 1 shows a plate evaporator, in particular for refrigerators.
  • the plate evaporator 1 consists of two sheets 2, which are connected to one another in a known manner. At least one of the sheets 2 is provided with internal features 3, which form 2 channels 4 in the plate evaporator 1 after the sheets have been connected.
  • the plate evaporator 1 has a connection opening 5 through which both a suction line 6 leading to the compressor (not shown) for the vaporous refrigerant and a capillary throttle tube 7 for conveying the liquid refrigerant enter the plate evaporator 1.
  • a tubular suction channel 8 for the vaporous refrigerant at.
  • the suction channel 8 narrows at a sealing section 9 to the outer diameter D a of the capillary throttle tube 7. Behind the sealing section 9, the suction channel 8 widens to the evaporator channel 4a, into which the capillary throttle tube 7 opens with an end section 10.
  • the evaporator-side end section 10 of the capillary throttle tube 7 has a length section L B designed as a calming section (FIG. 2).
  • the capillary throttle tube 7 In the entire length section L of the capillary throttle tube 7 before the calming section, the capillary throttle tube 7 has a constant diameter D i .
  • the capillary throttle tube 7 in the length section L B has an internal diameter D i, g that is larger than the constant diameter D i of the preceding length section L.
  • the suction channel 8 and the capillary throttle tube 7 are connected in a refrigerant-tight manner on the sealing section 9.
  • the suction line 6 has a capillary throttle tube insertion section 11.
  • the suction line 6 is provided with a clear cross-section D k which is larger by the outer diameter D a of the capillary throttle tube 7 than its remaining length range L S.
  • the capillary throttle tube 7 is guided into the suction line 6.
  • the capillary throttle tube 7 is laid on a length section E parallel to the suction line 6.
  • the capillary throttle tube 7 has three helical windings 13 around the suction line 6.
  • the capillary throttle tube 7 is again provided on a section T with helical turns 14. This ensures a space-saving way of laying the capillary throttle tube 7.
  • FIG. 3 shows an embodiment of a length section L B1 with an evaporator-side end section 10a of a capillary throttle tube 7 with a transition 15, which takes place in steps with sharp-edged corners.
  • the inner diameter D i of the capillary throttle tube 7 widens to the larger inner diameter D i, g of the length section L B1 .
  • FIG. 4 of the length section L B comprising a calming section corresponds to that in FIG. 2.
  • the end section 10 of a capillary throttle tube 7 is shown with a transition 16 which tapers from the inside diameter D i of the capillary throttle tube 7 to the larger inside diameter D i, g expanded.
  • the transition 16 takes place on a short length L E.
  • FIG. 5 discloses a length section L B2 having a calming section with an end section 10b of a capillary throttle tube 7, in which the inside diameter D i continuously expands to the larger inside diameter D i, g .
  • the course of the calming section is optimized in terms of flow technology and has an inner contour adapted to the characteristics of the refrigerant with regard to at least the pressure and speed conditions.
  • FIG. 6 shows a length section L B3 designed as a calming section with an end section 10c of a capillary throttle tube 7 with a transition 17 which takes place in two stages 18, 19.
  • the length section L B3 is divided into the length sections L1 and L2.
  • the inside diameter D i of the capillary throttle tube 7 initially widens to a larger inside diameter D i, 1 in the length section L 1 .
  • the inner diameter D i, 1 expands to the inner diameter D i, g .

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP93104613A 1992-03-30 1993-03-20 Dispositif frigorifique pour réfrigérateurs Withdrawn EP0563718A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4210350 1992-03-30
DE4210350 1992-03-30

Publications (1)

Publication Number Publication Date
EP0563718A1 true EP0563718A1 (fr) 1993-10-06

Family

ID=6455399

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93104613A Withdrawn EP0563718A1 (fr) 1992-03-30 1993-03-20 Dispositif frigorifique pour réfrigérateurs

Country Status (1)

Country Link
EP (1) EP0563718A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0779482B2 (fr) † 1995-12-11 2007-12-19 Matsushita Electric Industrial Co., Ltd. Circuit frigorifique
EP1843110A3 (fr) * 2006-04-05 2012-05-30 BSH Bosch und Siemens Hausgeräte GmbH Appareil frigorifique
DE102012205058A1 (de) 2012-03-29 2013-10-02 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät
EP3045842A1 (fr) * 2015-01-14 2016-07-20 Liebherr-Hausgeräte Ochsenhausen GmbH Appareil de réfrigération et/ou de congélation

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB507150A (en) * 1937-01-29 1939-06-09 Westinghouse Electric & Mfg Co Improvements in or relating to methods of and apparatus for controlling the flow of refrigerant in refrigerating systems
US2674105A (en) * 1950-10-07 1954-04-06 Int Harvester Co Tube joint in refrigeration system
US2933905A (en) * 1957-07-09 1960-04-26 Gen Motors Corp Refrigerating apparatus
DE1116247B (de) * 1957-01-26 1961-11-02 Schmoele Metall R & G Rohrelement fuer Waermeaustauscher, bei dem ein Mantel ein Kernrohr und mindestens ein an dessen Umfang anliegendes Aussenrohr kleineren Querschnittes umschliesst
DE1242646B (de) * 1961-02-08 1967-06-22 Schmoele Metall R & G Kaelteeinrichtung fuer Kuehlschraenke
FR1516944A (fr) * 1967-01-20 1968-02-05 Siemens Elektrogeraete Gmbh Machine frigorifique à compresseur incorporée à un réfrigérateur à isolement par mousse plastique
US3531947A (en) * 1968-10-29 1970-10-06 Gen Electric Refrigeration system including refrigerant noise suppression
FR2280303A7 (fr) * 1974-07-27 1976-02-20 Bosch Siemens Hausgeraete Evaporateur, en particulier evaporateur soude par cylindrage
US4445343A (en) * 1983-02-04 1984-05-01 General Electric Company Sonic restrictor means for a heat pump system
US4793150A (en) * 1988-05-13 1988-12-27 General Electric Company Refrigeration system including refrigerant noise suppression
DE9217405U1 (de) * 1992-03-30 1993-02-18 KM-Schmöle GmbH, 5750 Menden Kälteeinrichtung für Kühlschränke

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB507150A (en) * 1937-01-29 1939-06-09 Westinghouse Electric & Mfg Co Improvements in or relating to methods of and apparatus for controlling the flow of refrigerant in refrigerating systems
US2674105A (en) * 1950-10-07 1954-04-06 Int Harvester Co Tube joint in refrigeration system
DE1116247B (de) * 1957-01-26 1961-11-02 Schmoele Metall R & G Rohrelement fuer Waermeaustauscher, bei dem ein Mantel ein Kernrohr und mindestens ein an dessen Umfang anliegendes Aussenrohr kleineren Querschnittes umschliesst
US2933905A (en) * 1957-07-09 1960-04-26 Gen Motors Corp Refrigerating apparatus
DE1242646B (de) * 1961-02-08 1967-06-22 Schmoele Metall R & G Kaelteeinrichtung fuer Kuehlschraenke
FR1516944A (fr) * 1967-01-20 1968-02-05 Siemens Elektrogeraete Gmbh Machine frigorifique à compresseur incorporée à un réfrigérateur à isolement par mousse plastique
US3531947A (en) * 1968-10-29 1970-10-06 Gen Electric Refrigeration system including refrigerant noise suppression
FR2280303A7 (fr) * 1974-07-27 1976-02-20 Bosch Siemens Hausgeraete Evaporateur, en particulier evaporateur soude par cylindrage
US4445343A (en) * 1983-02-04 1984-05-01 General Electric Company Sonic restrictor means for a heat pump system
US4793150A (en) * 1988-05-13 1988-12-27 General Electric Company Refrigeration system including refrigerant noise suppression
DE9217405U1 (de) * 1992-03-30 1993-02-18 KM-Schmöle GmbH, 5750 Menden Kälteeinrichtung für Kühlschränke

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0779482B2 (fr) † 1995-12-11 2007-12-19 Matsushita Electric Industrial Co., Ltd. Circuit frigorifique
EP1843110A3 (fr) * 2006-04-05 2012-05-30 BSH Bosch und Siemens Hausgeräte GmbH Appareil frigorifique
DE102012205058A1 (de) 2012-03-29 2013-10-02 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät
EP3045842A1 (fr) * 2015-01-14 2016-07-20 Liebherr-Hausgeräte Ochsenhausen GmbH Appareil de réfrigération et/ou de congélation

Similar Documents

Publication Publication Date Title
EP0132620A2 (fr) Evaporateur
EP0629824B1 (fr) Evaporateur pour un appareil frigorifique à compresseur
DE69203388T2 (de) Verfahren zur Herstellung eines Rohrbündelwärmetauschers.
DE2226745A1 (de) Strahlgeblaese, sogenannter ejektor
EP1567770B1 (fr) Compresseur a vis
WO2014166805A1 (fr) Appareil frigorifique muni d'un évaporateur
EP1921401A2 (fr) Procédé de récuperation de chaleur
EP0563718A1 (fr) Dispositif frigorifique pour réfrigérateurs
DE9217405U1 (de) Kälteeinrichtung für Kühlschränke
DE4330214A1 (de) Wärmetauscher
DE3613395C1 (en) Compression refrigerating machine
DE10258145A1 (de) Schraubenverdichter
EP1721763B1 (fr) Canalisation de liquide réfrigérant pour climatisation
DE973828C (de) Kaelteeinrichtung fuer Kuehlschraenke
DE4442817C2 (de) Verdampfer für ein Kompressorkühlgerät
EP0698771B1 (fr) Congélateur
DE7431690U (de) Verdampfer für Kühlgeräte, Insbesondere Zweitemperaturen-Kühlschränke
DE19900701A1 (de) Kapillar-Saugrohrsystem für Verdampfersysteme bzw. Kältekreislaufsysteme
DE2525889A1 (de) Klimaanlage, insbesondere fuer kraftfahrzeuge
DE4319192A1 (de) Verfahren zur Herstellung von Kältemittelverteilern, insbesondere für Verdampfer einer Klimaanlage eines Kraftfahrzeuges
DE1451039A1 (de) Rohrschlangen-Waermeaustauscher
DE102009041916A1 (de) Kühl- und/oder Gefriergerät
DE102007048386A1 (de) Kühl- und/oder Gefriergerät
DE202007014077U1 (de) Kühl- und/oder Gefriergerät
EP1540223A1 (fr) Echangeur de chaleur, procede pour produire un echangeur de chaleur, et profile composite extrude utilise dans un tel procede

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE DK ES FR IT SE

17P Request for examination filed

Effective date: 19940311

17Q First examination report despatched

Effective date: 19950213

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19950624