EP2005077A2 - Appareil frigorifique à évaporateur tubulaire - Google Patents

Appareil frigorifique à évaporateur tubulaire

Info

Publication number
EP2005077A2
EP2005077A2 EP07712510A EP07712510A EP2005077A2 EP 2005077 A2 EP2005077 A2 EP 2005077A2 EP 07712510 A EP07712510 A EP 07712510A EP 07712510 A EP07712510 A EP 07712510A EP 2005077 A2 EP2005077 A2 EP 2005077A2
Authority
EP
European Patent Office
Prior art keywords
pipe
refrigerant
loops
refrigerating appliance
appliance according
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Withdrawn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
EP07712510A
Other languages
German (de)
English (en)
Inventor
Wolfgang Nuiding
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 Bosch und Siemens 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 Bosch und Siemens Hausgeraete GmbH filed Critical BSH Bosch und Siemens Hausgeraete GmbH
Publication of EP2005077A2 publication Critical patent/EP2005077A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/023—Evaporators consisting of one or several sheets on one face of which is fixed a refrigerant carrying coil
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/006—General constructional features for mounting refrigerating machinery components

Definitions

  • the present invention relates to a refrigerator in which an internal cooling space is cooled by a tube evaporator through which refrigerant circulated by a compressor flows and which has a carrier board and a pipe arranged thereon in heat-conductive contact.
  • the tube evaporator in close thermal contact with the internal cooling space is thermally shielded from the environment by an insulating layer.
  • the compressor is located outside the insulating layer and supplies the evaporator with compressed refrigerant at ambient temperature.
  • the refrigerant is depressurized as it passes through a vaporizer's evaporator, reducing the boiling point of the refrigerant to a level well below ambient.
  • the resulting evaporation of the refrigerant causes the cooling of the interior. Gaseous refrigerant is sucked from the compressor via a suction line.
  • Rollbond evaporators generally composed of two sheets, one of which has a meandering refrigerant line stamped therein, generally have a collector formed adjacent the downstream end of the refrigerant line, which collects un-vaporized refrigerant during a standstill phase of the compressor and thereby prevents it from being forced out of the evaporator and into the suction line by refrigerant evaporating further upstream in the line.
  • a collector formed adjacent the downstream end of the refrigerant line, which collects un-vaporized refrigerant during a standstill phase of the compressor and thereby prevents it from being forced out of the evaporator and into the suction line by refrigerant evaporating further upstream in the line.
  • To provide such a collector even with a tube evaporator is complicated and expensive, since it is necessary for this, several tube sections with different clear widths close together. Instead, in conventional tube evaporators, a rising outlet tube is often located immediately upstream of the suction tube.
  • Object of the present invention is to provide a refrigeration device with a tube evaporator, in which, despite generous filling with refrigerant, the risk of overflow of the outlet pipe is avoided.
  • the invention achieves this object by providing in a refrigerator with a tube evaporator connected to a compressor via a suction line and in which a refrigerant tube connects a plurality of tube loops connected in series and one of the most downstream of the tube loops to the suction line, rising outlet pipe forms, instead of a conventional horizontal course of straight pipe sections of the individual pipe loops on a predetermined length a rising in the flow direction of the refrigerant flow course of the pipe loops is provided, wherein the predetermined length of the pipe loop in combination with its flow-through cross-section forms a buffer volume, whereby an overflow of liquid refrigerant is prevented in the outlet pipe.
  • Each rising-loop pipe loop portion is capable of storing liquid refrigerant and simultaneously sweeping or displacing supple gaseous refrigerant over the liquid so as to trap the liquid refrigerant in the descending portion and not reach the exit pipe.
  • the storage capacity of the tube evaporator for liquid refrigerant is considerably increased, and the risk of expelling liquid refrigerant into the suction line is reduced accordingly.
  • each pipe loop in a conventional manner comprises two straight pipe sections connected by a curved section, it may be provided according to a first embodiment that the straight sections of a furthest downstream group of the pipe loops are parallel oblique.
  • the straight sections of a furthest downstream group of the pipe loops are parallel oblique.
  • the one further downstream has the course rising in the flow direction of the refrigerant.
  • both straight pipe sections increase in the flow direction of the refrigerant.
  • any straight pipe section is able to catch liquid refrigerant, and the amount attributable to a single section is small. The smaller this amount is, the stronger the flow of gaseous refrigerant that can flow through the pipe section without expelling the liquid refrigerant.
  • the group should comprise a plurality of pipe loops formed as described above; Preferably, the group includes all tube loops of the evaporator.
  • each straight pipe section preferably corresponds to at most half its mean distance to adjacent straight pipe sections.
  • Fig. 1 is a schematic view of a refrigerator according to the invention.
  • FIG. 2 shows a section through a tube evaporator according to a first embodiment of the invention.
  • Fig. 3 is a similar to Fig. 2, fragmentary section through a tube evaporator according to a second embodiment of the invention.
  • Fig. 1 shows a schematic view of a refrigerating appliance, seen from the back, wherein the rear wall and insulating layer of a body 1 of the device omitted and the remaining outer surfaces of the body 1 are shown transparent to an inner container 2 and attached to the rear wall of the inner container tube evaporator 3 to show.
  • a niche is recessed to form a machine room, which receives a compressor 4 and a condenser 5.
  • the compressor 4, the condenser 5 and the tube evaporator 3 are interconnected to a refrigerant circuit.
  • a suction line 6 extends substantially vertically downwards from the compressor 4 between a right upper corner of the tube evaporator 3.
  • a pressure line 7 emerges from the condenser 5 and runs along a large part of its length within the suction line 6 to the upper right corner of the evaporator 3 where it exits the suction line 6 again and opens via a throttle point 8 in a refrigerant pipe of the evaporator 3.
  • the refrigerant tube forms a plurality of vertically staggered serially connected tube loops 9 each having two rectilinear tube sections connected by a tube bend 10 and connected in opposite directions.
  • the upstream pipe section of each loop 9 is denoted by 1 1, the downstream by 12.
  • the lowermost tube section 12 is connected by a substantially vertical outlet tube to the suction line 6 at the upper right corner of the evaporator.
  • the puddles 14 have a perfectly flat liquid level, it is easy to see that the amount of liquid that each pipe section 12 can accommodate, without the liquid completely blocking its cross-section, must be greatest when the height difference between the two ends of the section is just smaller than the diameter of the pipe section 1 1. Then the puddle 14 can extend over the entire length of the pipe section 12 and fill its volume just in half. Therefore, if the influence of the surface tension on the shape of the liquid level is negligible, be it due to a low surface tension of the refrigerant or a large diameter of the refrigerant pipe, it may be appropriate to select the height difference between the ends of each pipe portion.
  • the liquid refrigerant tends to obstruct the free pipe cross-section due to surface tension, it will be reasonable to make the slope of the sections 11, 12 slightly larger to ensure that the liquid refrigerant is a puddle 14 that is separated from the deepest by inflowing gas Place was displaced, this strives sufficiently strong again, so that in the course of the pipe section 12, the gas can pass through the liquid without displacing it downstream.
  • the height difference can amount to a few multiples of the pipe diameter here.
  • the pipe loops can store a considerable amount of liquid refrigerant before there is a risk that it will be pushed downstream in a stagnant phase of the compressor by further upstream vaporizing refrigerant. Therefore, a large amount of refrigerant may be filled in the refrigerant cycle without liquid refrigerant in such an amount can fill the downstream pipe loops 9, filling the entire discharge pipe 13 connecting the lowermost pipe loop 9 with the suction pipe and into the suction pipe 6 could arrive.
  • Fig. 3 shows a tube evaporator 3 according to a second embodiment of the invention.
  • the suction line 6, the pressure line 7 and its course to the throttle point 8 are the same as in the first embodiment and therefore need not be described again.
  • the two rectilinear pipe sections 1 1, 12 of the pipe loops 9 are not parallel here, but both extend in each case in the flow direction of the refrigerant increasing, in the figure, the slope of the clearer representation is exaggerated because of. This allows both pipe sections 1 1, 12 of each pipe loop 9 to store liquid refrigerant, so that the amount of liquid refrigerant allocated to each pipe section is small and the risk of the liquid refrigerant being displaced downstream by further upstream evaporation still exists is further reduced.
  • pipe loops can also be combined with conventional horizontal pipe sections and those with rising pipe sections in an evaporator, in which case the pipe loops should be provided with rising pipe sections in the downstream part of the evaporator to trap and store liquid refrigerant draining from upstream horizontal pipe sections can.

Abstract

L'invention concerne un appareil frigorifique dans lequel un évaporateur tubulaire (3) est relié à un compresseur (4) par l'intermédiaire d'une conduite d'aspiration (6). Un tube frigorifique de l'évaporateur tubulaire est constitué d'une pluralité de coudes (9) reliés en série et d'un tube de sortie montant (13) reliant le coude (9) situé le plus en aval à la conduite d'aspiration (6). Ces coudes (9) présentent une allure montante dans le sens de passage du fluide frigorigène sur une longueur correspondant au moins à la longueur du tube de sortie (13).
EP07712510A 2006-04-05 2007-03-12 Appareil frigorifique à évaporateur tubulaire Withdrawn EP2005077A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202006005551U DE202006005551U1 (de) 2006-04-05 2006-04-05 Kältegerät mit Rohrverdampfer
PCT/EP2007/052291 WO2007115877A2 (fr) 2006-04-05 2007-03-12 Appareil frigorifique à évaporateur tubulaire

Publications (1)

Publication Number Publication Date
EP2005077A2 true EP2005077A2 (fr) 2008-12-24

Family

ID=36710192

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07712510A Withdrawn EP2005077A2 (fr) 2006-04-05 2007-03-12 Appareil frigorifique à évaporateur tubulaire

Country Status (6)

Country Link
US (1) US8122737B2 (fr)
EP (1) EP2005077A2 (fr)
CN (1) CN101410679A (fr)
DE (1) DE202006005551U1 (fr)
RU (1) RU2426038C2 (fr)
WO (1) WO2007115877A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008024325A1 (de) * 2008-05-20 2009-11-26 BSH Bosch und Siemens Hausgeräte GmbH Kühlgerät mit Kühlmittelspeicherung im Verflüssiger und entsprechendes Verfahren
DE102016123512A1 (de) 2016-12-06 2018-06-07 Coolar UG (haftungsbeschränkt) Verdampfervorrichtung
JP2019207068A (ja) * 2018-05-29 2019-12-05 株式会社ノーリツ 熱交換器およびこれを備えた温水装置
CN115479427B (zh) * 2021-06-16 2023-08-15 青岛海尔电冰箱有限公司 冰箱

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US2371215A (en) * 1945-03-13 Refrigerating apparatus
US1995167A (en) 1933-01-14 1935-03-19 Ingersoll Steel And Dise Co Evaporator
US2118637A (en) 1936-03-05 1938-05-24 Gen Electric Evaporator for refrigerating machines
US2292803A (en) 1937-04-17 1942-08-11 Gen Electric Evaporator for refrigerating machines
US2730872A (en) 1954-05-25 1956-01-17 Reynolds Metals Co Evaporator incorporating accumulator wells and feed grid
US2827774A (en) * 1955-03-10 1958-03-25 Avco Mfg Corp Integral evaporator and accumulator and method of operating the same
DE1299007B (de) 1964-09-18 1969-07-10 Danfoss As Kaelteanlage mit Kuehlfach-Verdampfer und vorgeschaltetem Gefrierfach-Verdampfer
US4171622A (en) * 1976-07-29 1979-10-23 Matsushita Electric Industrial Co., Limited Heat pump including auxiliary outdoor heat exchanger acting as defroster and sub-cooler
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US4291546A (en) * 1979-06-11 1981-09-29 Alco Foodservice Equipment Company Cold plate heat exchanger
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US4823561A (en) * 1988-03-18 1989-04-25 Medlock Danny H Refrigeration apparatus having a heat exchanger pre-cooling element
KR910002810Y1 (ko) * 1988-10-06 1991-05-02 삼성전자 주식회사 제빙기의 증발기 구조
KR910003551Y1 (ko) * 1989-03-03 1991-05-31 삼성전자 주식회사 제빙기의 증발기 구조
DE3921485A1 (de) * 1989-06-30 1991-01-10 Erno Raumfahrttechnik Gmbh Verdampfungswaermetauscher
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SU1740916A1 (ru) 1990-06-14 1992-06-15 Московский автомобильный завод им.И.А.Лихачева Испаритель
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US6370901B1 (en) * 2000-07-26 2002-04-16 Ming-Li Tso Compound evaporation system and device thereof
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FR2867843B1 (fr) * 2004-03-22 2006-04-28 Pechiney Rhenalu Panneau de refroidissement pour refrigerateur ou congelateur

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Also Published As

Publication number Publication date
US20090120125A1 (en) 2009-05-14
WO2007115877A3 (fr) 2007-11-29
US8122737B2 (en) 2012-02-28
RU2426038C2 (ru) 2011-08-10
CN101410679A (zh) 2009-04-15
RU2008142982A (ru) 2010-05-10
DE202006005551U1 (de) 2006-07-06
WO2007115877A2 (fr) 2007-10-18

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