EP0752563A2 - Evaporator arrangement for domestic refrigerators - Google Patents
Evaporator arrangement for domestic refrigerators Download PDFInfo
- Publication number
- EP0752563A2 EP0752563A2 EP96106978A EP96106978A EP0752563A2 EP 0752563 A2 EP0752563 A2 EP 0752563A2 EP 96106978 A EP96106978 A EP 96106978A EP 96106978 A EP96106978 A EP 96106978A EP 0752563 A2 EP0752563 A2 EP 0752563A2
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- EP
- European Patent Office
- Prior art keywords
- evaporator
- refrigerant
- capacity
- refrigeration
- arrangement
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- 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.)
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Classifications
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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
- 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
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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
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
- F25B39/024—Evaporators with plate-like or laminated elements with elements constructed in the shape of a hollow panel
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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
- 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
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
- F25D2400/04—Refrigerators with a horizontal mullion
Definitions
- the invention relates to an evaporator arrangement for household refrigeration devices with at least two evaporators, which are located in a closed refrigeration circuit with a refrigerant compressor and have a different refrigeration capacity, the refrigerant channel arrangements of which are connected in series in terms of flow technology, the refrigerant channel arrangement of the evaporator of lower refrigeration capacity being a collector for has liquid refrigerant.
- a two-temperature refrigerator which is equipped with a plate evaporator for cooling its thermally separated compartments.
- This has two evaporator sections, which are equipped with a different cooling capacity and are arranged in series in terms of flow technology, which are mechanically connected to one another via a connecting web and which can be acted upon with refrigerant via an injection point arranged on the evaporator section with a lower cooling capacity.
- the plate evaporator is designed that the refrigerant first flows through the evaporator section of lower refrigeration capacity from the injection point in a refrigerant channel laid in turns and is then fed to the evaporator section of higher refrigeration capacity and from there is returned to the evaporator section of lower refrigeration capacity.
- it is fed to a sack-like collector for its phase separation, which is connected upstream of an intake manifold connection in the flow direction of the refrigerant.
- the invention has for its object to improve an evaporator arrangement according to the preamble of claim 1 with respect to the disadvantages of the prior art.
- the evaporator of lower cooling capacity is downstream of the evaporator of higher cooling capacity in terms of flow technology and the portion of its refrigerant channel arrangement located in the flow direction of the refrigerant driven by the compressor is designed to be volume-optimized.
- the solution according to the invention is characterized in particular by the fact that the quantity of refrigerant required for performance-optimized operation of the refrigeration device is insensitive to quantity tolerance, so that the refrigeration circuit can be operated even with large fluctuations in the quantity without noticeable loss of performance. Furthermore, it is prevented by the evaporator arrangement according to the invention that liquid refrigerant can get into the intake manifold during the running time of the compressor, where there can then be noise on the one hand and cooling and thus condensation water formation and, as a result, corrosion problems on the intake manifold.
- the storage compartment cooled by the evaporator with a higher cooling capacity has a significantly more precisely maintained storage temperature if, as is customary with single-circuit cooling systems of this type, indirect temperature control of the colder compartment via the warmer storage compartment is used.
- Volume-optimized is to be understood here as the production-technically controllable design of the channel cross section of the refrigerant channels or their length-maximized arrangement on a certain evaporator board surface.
- the volume optimization of the section of the refrigerant channel arrangement of the evaporator of lower evaporating capacity located in front of the collector is generated by the length of the refrigerant channels forming the refrigerant channel arrangement.
- Such a design of the evaporator with lower cooling capacity creates a particularly simple additional volume for liquid refrigerant, which additionally prevents liquid refrigerant from getting into the intake manifold of the refrigeration circuit during the running time of the compressor and cooling it down, even if a refrigeration circuit of this type is filled with refrigerant up to the upper filling limit.
- the refrigerant return from the evaporator of lower cooling capacity to the suction side of the compressor is at least largely decoupled thermally from the evaporator of higher cooling capacity.
- the evaporators are different Cooling capacity are designed as independent, only fluidly interconnected units, the evaporator of lower cooling capacity is arranged in the installed position of the evaporator arrangement above and the inflow of its refrigerant channel arrangement is lower than its outflow.
- Such a structure of an evaporator arrangement ensures that the liquid refrigerant can pass from the evaporator of lower refrigeration capacity into the evaporator of higher refrigeration capacity when the refrigerant compressor is at a standstill, since, due to the design, no siphon-like refrigerant channel arrangements are necessary in the evaporator of lower refrigeration capacity, so that on the one hand so-called glugging noises rising vapor bubbles that penetrate the liquid refrigerant residues are prevented. On the other hand, so-called re-evaporation of liquid refrigerant residues in the evaporator of lower refrigeration capacity is avoided, so that it can be defrosted more specifically and thus more quickly while the refrigerant compressor is at a standstill.
- a household refrigeration appliance 10 shown in FIG. 1 is equipped with a heat-insulating housing 12 which can be closed by a door 11 and in which two storage compartments of different temperatures which are thermally separated from one another by a heat-insulating partition plate 13 are arranged.
- the storage compartment above the partition plate 13 is designed as a normal cooling compartment 14 with intermediate shelves 15 serving as shelves, while the storage compartment arranged below the partition plate 13 serves as a cold storage compartment 16.
- This is equipped with a plurality of closed-walled containers 17 arranged one above the other, some of which are designed as pull-outs, whose container walls facing the inside of the compartment serve together with these as air guiding devices for the cooling air circulated within the cold storage compartment 16 by a fan (not shown).
- the cold storage compartment 16 has on its rear side a step-like projection 18, through which a recess 19 accessible from the outside for accommodating a refrigerant compressor 20 is saved in the heat-insulated housing 12.
- This is used for the forced circulation of refrigerant in a closed refrigeration circuit with two board-like evaporators, which have different cooling capacities and are designed as so-called cold wall evaporators.
- the evaporator of higher refrigeration capacity 21 is arranged in the cold storage compartment 16 and is equipped with a refrigerant injection point 22, which serves to lower the pressure of the refrigerant flowing to the evaporator 21 from a condenser (not shown) in the refrigeration cycle.
- the evaporator of higher cooling capacity 21 is designed as a refrigerant channel arrangement 23 serving refrigerant channel arranged in turns on the evaporator board, the outlet end of which is in the installed position of the evaporator arrangement in the refrigeration device 10 above the refrigerant injection point 22 and is connected to a refrigerant line 24.
- This serves for the fluidic connection of the evaporator of higher refrigeration capacity 21 to the board-like evaporator 25, which, in comparison, is equipped with a lower refrigeration capacity and is arranged in the normal cooling compartment 14 and is connected to the evaporator 21 only via the refrigerant line 24.
- the evaporator with a lower refrigeration capacity 25 is provided with a refrigerant channel serving as a refrigerant channel arrangement 26, which has one of its inflow openings 27 connected to the refrigerant line 24 and is arranged in closely aligned windings above the height of the evaporator board.
- the outlet-side end of the refrigerant channel is provided with a horizontal connection piece, bag-shaped refrigerant collector 28, before it opens into a drain opening 29 located higher in the installed position of the evaporator 25, which serves for connection to a suction line, not shown, in the refrigeration circuit.
- the liquid refrigerant conveyed by it only becomes the evaporator of higher refrigeration capacity arranged first in the series connection of the two evaporators 21 and 25 21 supplied so that it is cooled first. Subsequently, the liquid refrigerant is supplied in series connection to evaporators with a lower cooling capacity 25, so that the latter cools down.
- the evaporator of lower refrigeration capacity 25 serving to cool the normal refrigeration compartment 14 heats up much faster than the evaporator of higher refrigeration capacity 21 located in the cold storage compartment 16, as a result of which the liquid refrigerant accumulated in the refrigerant collector 28 evaporates very quickly and partly in the evaporator of higher refrigeration capacity 21 condensed.
- the refrigerant located in the refrigerant channel arrangement 26 of the evaporator 25 after the refrigerant compressor 20 has been switched off is fed by the action of gravity on the refrigerant to the evaporator of higher refrigeration capacity arranged underneath in the installed position of the evaporator arrangement.
- the invention can also be applied to an evaporator board in which an evaporator section of higher refrigeration capacity is connected via a connecting web to an evaporator section of lower refrigeration capacity, the return of the refrigerant from the evaporator section of lower refrigeration capacity not via the evaporator section of higher refrigeration capacity.
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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)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
Die Erfindung betrifft eine Verdampferanordnung für Haushalts-Kältegeräte mit wenistens zwei in einem geschlossenen Kältekreis mit einem Kältemittelverdichter liegenden, eine unterschiedliche Kälteleistung aufweisenden Verdampfern, deren Kältemittel-Kanalanordnungen strömungstechnisch in Reihenschaltung miteinander verbunden sind, wobei die Kältemittel-Kanalanordnung des Verdampfers geringerer Kälteleistung einen Sammler für flüssiges Kältemittel aufweist.The invention relates to an evaporator arrangement for household refrigeration devices with at least two evaporators, which are located in a closed refrigeration circuit with a refrigerant compressor and have a different refrigeration capacity, the refrigerant channel arrangements of which are connected in series in terms of flow technology, the refrigerant channel arrangement of the evaporator of lower refrigeration capacity being a collector for has liquid refrigerant.
Aus dem DE-GM 90 06 386 ist ein Zweitemperaturen-Kältegerät bekannt, welches zur Kühlung seiner thermisch voneinander getrennten Fächer mit einem Plattenverdampfer ausgestattet ist. Dieser weist zwei mit einer unterschiedlichen Kälteleistung ausgestatteten, strömungstechnisch in Reihenschaltung angeordnete Verdampferabschnitte auf, welche über einen Verbindungssteg mechanisch miteinander verbunden sind und welche über eine am Verdampferabschnitt geringerer Kälteleistung angeordnete Einspritzstelle mit Kältemittel beaufschlagbar sind. Der Plattenverdampfer ist dabei so konzipiert, daß das Kältemittel von der Einspritzstelle aus in einem in Windungen verlegten Kältemittelkanal Zuerst den Verdampferabschnitt geringerer Kälteleistung durchströmt und anschließend dem Verdampferabschnitt höherer Kälteleistung zugeführt ist und von diesem aus wieder auf den Verdampferabschnitt geringerer Kälteleistung zurückgeleitet ist. Hier ist es zu seiner Phasentrennung einem sackartigen Sammler zugeführt, welcher in Strömungsrichtung des Kältemittels einem Saugrohranschluß vorgeschaltet ist.From DE-GM 90 06 386 a two-temperature refrigerator is known, which is equipped with a plate evaporator for cooling its thermally separated compartments. This has two evaporator sections, which are equipped with a different cooling capacity and are arranged in series in terms of flow technology, which are mechanically connected to one another via a connecting web and which can be acted upon with refrigerant via an injection point arranged on the evaporator section with a lower cooling capacity. The plate evaporator is designed that the refrigerant first flows through the evaporator section of lower refrigeration capacity from the injection point in a refrigerant channel laid in turns and is then fed to the evaporator section of higher refrigeration capacity and from there is returned to the evaporator section of lower refrigeration capacity. Here it is fed to a sack-like collector for its phase separation, which is connected upstream of an intake manifold connection in the flow direction of the refrigerant.
Infolge der kältetechnischen Schaltung der beiden Verdampferabschnitte, wonach der Verdampferabschnitt höherer Kälteleistung dem Verdampferabschnitt geringerer Kälteleistung strömungstechnisch nachgeschaltet ist, ist bedingt, daß letzterer zuerst und im Anschluß daran erst der Verdampferabschnitt höherer Kälteleistung mit flüssigen Kältemittel beaufschlagt und damit gekühlt ist. Dies wiederum zieht nach sich, daß nach einer gewissen Laufzeit des Kältemittelverdichters flüssiges Kältemittel vom nachgeschalteten Verdampferabschnitt höherer Kälteleistung in den Verdampferabschnitt geringerer Kälteleistung übertritt, dort aber aufgrund der bereits erfolgten Kühlung dieses Verdampferabschnitts nicht verdampfen kann und sich im Sammler absetzt. Dieser kann aufgrund seiner geometrischen Form jedoch nur eine gewisse Menge flüssigen Kältemittels aufnehmen, so daß die Gefahr besteht, daß dieses in das Saugrohr und unter Umständen sogar zum Verdichter gelangen kann und diesen beschädigt. Um dem vorzubeugen, ist es unumgänglich, die Füllmenge des Kältemittels im Kältekreislauf zu reduzieren, so daß es zu Unterfüllungserscheinungen und somit zu Leistungseinbußen im Kältekreislauf kommen kann.As a result of the refrigeration circuit of the two evaporator sections, according to which the evaporator section of higher refrigeration capacity is connected downstream in terms of flow technology to the evaporator section of lower refrigeration capacity, it is necessary that the latter first and subsequently the evaporator section of higher refrigeration capacity be acted upon with liquid refrigerant and thus cooled. This in turn means that after a certain running time of the refrigerant compressor, liquid refrigerant passes from the downstream evaporator section of higher refrigeration capacity into the evaporator section of lower refrigeration capacity, but cannot evaporate there due to the cooling of this evaporator section and settles in the collector. However, due to its geometric shape, this can only absorb a certain amount of liquid refrigerant, so that there is a risk that it can get into the intake manifold and possibly even to the compressor and damage it. To prevent this, it is essential to reduce the amount of refrigerant in the refrigeration cycle so that there may be signs of underfilling and thus reduced performance in the refrigeration cycle.
Der Erfindung liegt die Aufgabe zugrunde, eine Verdampferanordnung gemäß dem Oberbegriff des Anspruches 1 hinsichtlich der Nachteile des Standes der Technik zu verbessern.The invention has for its object to improve an evaporator arrangement according to the preamble of claim 1 with respect to the disadvantages of the prior art.
Diese Aufgabe wird gemäß der Erfindung dadurch gelöst, daß der Verdampfer geringerer Kälteleistung dem Verdampfer höherer Kälteleistung strömungstechnisch nachgeschaltet ist und der in Strömungsrichtung des vom Verdichter angetriebenen Kältemittels vor dem Sammler liegende Abschnitt seiner Kältemittel-Kanalanordnung volumenoptimiert ausgebildet ist.This object is achieved according to the invention in that the evaporator of lower cooling capacity is downstream of the evaporator of higher cooling capacity in terms of flow technology and the portion of its refrigerant channel arrangement located in the flow direction of the refrigerant driven by the compressor is designed to be volume-optimized.
Die erfindungsgemäße Lösung zeichnet sich vor allem dadurch aus, daß die für einen leistungsoptimierten Betrieb des Kältegerätes notwendige Kältemittelmenge mengentoleranz-unempfindlich ist, so daß der Kältekreis ohne merkliche Leistungseinbuße auch bei größeren Füllmengenschwankungen betreibbar ist. Ferner ist durch die erfindungsgemäße Verdampferanordnung verhindert, daß flüssiges Kältemittel während der Laufzeit des Verdichters in das Saugrohr gelangen kann, wo es dann einerseits zur Geräuschbildung und andererseits zur Abkühlung und somit zur Schwitzwasserbildung und daraus resultierend zu Korrosionsproblemen am Saugrohr kommen kann. Außerdem ergibt sich für das vom Verdampfer höherer Kälteleistung gekühlte Lagerfach eine deutlich präziser eingehaltene Lagertemperatur, wenn wie bei derartigen Einkreis-Kühlsystemen üblich, eine indirekte Temperaturregelung des kälteren Faches über das wärmere Lagerfach Anwendung findet.The solution according to the invention is characterized in particular by the fact that the quantity of refrigerant required for performance-optimized operation of the refrigeration device is insensitive to quantity tolerance, so that the refrigeration circuit can be operated even with large fluctuations in the quantity without noticeable loss of performance. Furthermore, it is prevented by the evaporator arrangement according to the invention that liquid refrigerant can get into the intake manifold during the running time of the compressor, where there can then be noise on the one hand and cooling and thus condensation water formation and, as a result, corrosion problems on the intake manifold. In addition, the storage compartment cooled by the evaporator with a higher cooling capacity has a significantly more precisely maintained storage temperature if, as is customary with single-circuit cooling systems of this type, indirect temperature control of the colder compartment via the warmer storage compartment is used.
Unter volumenoptimiert ist hier die fertigungstechnisch beherrschbare Ausbildung des Kanalquerschnitts der Kältemittelkanäle oder deren längenmäßig maximierte Anordnung auf einer bestimmten Verdampferplatinenfläche zu verstehen.Volume-optimized is to be understood here as the production-technically controllable design of the channel cross section of the refrigerant channels or their length-maximized arrangement on a certain evaporator board surface.
Nach einer bevorzugten Ausführungsform des Gegenstandes der Erfindung ist vorgesehen, daß die Volumenoptimierung des vor dem Sammler liegenden Abschnitts der Kältemittel-Kanalanordnung des Verdampfers geringerer Kälteleistung durch die Länge der die Kältemittel-Kanalanordnung bildenden Kältemittelkanäle erzeugt ist.According to a preferred embodiment of the subject matter of the invention, it is provided that the volume optimization of the section of the refrigerant channel arrangement of the evaporator of lower evaporating capacity located in front of the collector is generated by the length of the refrigerant channels forming the refrigerant channel arrangement.
Durch eine derartige Ausbildung des Verdampfers geringerer Kälteleistung ist in diesem ein auf besonders einfache Weise zusätzliches Aufnahmevolumen für flüssiges Kältemittel geschaffen, wodurch zusätzlich verhindert ist, daß flüssiges Kältemittel während der Laufzeit des Verdichters in das Saugrohr des Kältekreises gelangt und dieses unzulässig abkühlt, auch wenn ein derartiger Kältekreis bis an die obere Füllgrenze mit Kältemittel gefüllt ist.Such a design of the evaporator with lower cooling capacity creates a particularly simple additional volume for liquid refrigerant, which additionally prevents liquid refrigerant from getting into the intake manifold of the refrigeration circuit during the running time of the compressor and cooling it down, even if a refrigeration circuit of this type is filled with refrigerant up to the upper filling limit.
Entsprechend einer weiteren bevorzugten Ausführungsform des Gegenstandes der Erfindung ist vorgesehen, daß die Kaltemittelrückführung vom Verdampfer geringerer Kälteleistung zur Saugseite des Verdichters thermisch vom Verdampfer höherer Kälteleistung zumindest weitestgehend entkoppelt ist.According to a further preferred embodiment of the object of the invention, it is provided that the refrigerant return from the evaporator of lower cooling capacity to the suction side of the compressor is at least largely decoupled thermally from the evaporator of higher cooling capacity.
Durch eine solche Lösung ist gewährleistet, daß sich der Verdampfer höherer Kälteleistung und somit das von ihm gekühlte Lagerfach nicht unnötiger Weise durch den relativ warmen Kältemitteldampf aus dem Verdampfer geringerer Kälteleistung erwärmt und somit zusätzliche Energie notwendig ist um die bestimmungsgemäße Temperatur wieder herzustellen.Such a solution ensures that the evaporator of higher refrigeration capacity and thus the storage compartment cooled by it is not unnecessarily heated by the relatively warm refrigerant vapor from the evaporator of lower refrigeration capacity and additional energy is therefore necessary to restore the intended temperature.
Gemäß einer letzten bevorzugten Ausführungsform des Gegenstandes der Erfindung ist vorgesehen, daß die Verdampfer unterschiedlicher Kälteleistung als eigenständige, lediglich strömungstechnisch miteinander verbundene Baueinheiten ausgebildet sind, wobei der Verdampfer geringerer Kälteleistung in Einbaulage der Verdampferanordnung obenliegend angeordnet ist und der Zufluß seiner Kältemittel-Kanalanordnung tiefer als deren Abfluß liegt.According to a last preferred embodiment of the object of the invention it is provided that the evaporators are different Cooling capacity are designed as independent, only fluidly interconnected units, the evaporator of lower cooling capacity is arranged in the installed position of the evaporator arrangement above and the inflow of its refrigerant channel arrangement is lower than its outflow.
Durch einen derartigen Aufbau einer Verdampferanordnung ist gewährleistet, daß das flüssige Kältemittel im Stillstand des Kältemittelverdichters aus dem Verdampfer geringerer Kälteleistung in den Verdampfer höherer Kälteleistung übertreten kann, da konstruktionsbedingt keine siphonartigen Kältemittel-Kanalanordnungen im Verdampfer geringerer Kälteleistung notwendig werden, so daß einerseits sogenannte Gluckergeräusche durch aufsteigende, die flüssigen Kältemittelrückstände durchdringenden Dampfblasen verhindert sind. Andererseits ist auch ein sogenanntes Nachverdampfen flüssiger Kältemittelrückstände im Verdampfer geringerer Kälteleistung vermieden, so daß dieser zielgerichteter und somit schneller während des Stillstandes des Kältemittelverdichters abgetaut werden kann.Such a structure of an evaporator arrangement ensures that the liquid refrigerant can pass from the evaporator of lower refrigeration capacity into the evaporator of higher refrigeration capacity when the refrigerant compressor is at a standstill, since, due to the design, no siphon-like refrigerant channel arrangements are necessary in the evaporator of lower refrigeration capacity, so that on the one hand so-called glugging noises rising vapor bubbles that penetrate the liquid refrigerant residues are prevented. On the other hand, so-called re-evaporation of liquid refrigerant residues in the evaporator of lower refrigeration capacity is avoided, so that it can be defrosted more specifically and thus more quickly while the refrigerant compressor is at a standstill.
Die Erfindung ist in der nachfolgenden Beschreibung anhand eines in der beigefügten Zeichnung vereinfacht dargestellten Ausführungsbeispieles erläutert. Es zeigen:
- Fig. 1
- ein Einbau-Haushaltskältegerät mit zwei übereinander angeordneten, eine unterschiedliche Lagertemperatur aufweisenden Lagerfächer, welche durch je einen Verdampfer gekühlt sind, von der Seite gesehen in Schnittdarstellung und
- Fig. 2
- schematisch die zur Kühlung der Lagerfächer dienenden Verdampfer in ihrer kältetechnischen Schaltungsanordnung.
- Fig. 1
- a built-in household refrigerator with two stacked compartments, which have a different storage temperature and are cooled by an evaporator, viewed from the side in a sectional view and
- Fig. 2
- schematically the evaporators used to cool the storage compartments in their refrigeration circuitry.
Ein in Fig. 1 gezeigtes Haushalts-Kältegerät 10 ist mit einem durch eine Tür 11 verschließbaren, warmeisolierenden Gehäuse 12 ausgestattet, in welchem zwei durch eine wärmeisolierende Trennplatte 13 thermisch voneinander getrennte Lagerfächer unterschiedlicher Temperatur angeordnet sind. Hierbei ist das Lagerfach oberhalb der Trennplatte 13 als Normalkühlfach 14 mit als Ablagen dienenden Zwischenböden 15 ausgebildet, während das unterhalb der Trennplatte 13 angeordnete Lagerfach als Kaltlagerfach 16 dient. Dieses ist mit mehreren übereinander angeordneten, teils als Auszüge ausgebildeten geschlossenwandigen Behältern 17 ausgestattet, deren den Fachinnenseiten zugekehrte Behälterwände zusammen mit diesen als Luftleitvorrichtungen für die innerhalb des Kaltlagerfaches 16 von einem nicht dargestellten Ventilator umgewälzte Kühlluft dienen. Das Kaltlagerfach 16 weist auf seiner Rückseite einen stufenartigen Vorsprung 18 auf, durch welchen im wärmeisolierten Gehäuse 12 eine von außen zugängliche Nische 19 zur Aufnahme eines Kältemittelverdichters 20 freigespart ist. Dieser dient zur zwangsweisen Umwälzung von Kältemittel in einem geschlossenen Kältekreis mit zwei eine unterschiedliche Kälteleistung aufweisenden, als sogenannte Coldwall-Verdampfer ausgebildete platinenartige Verdampfer. Von diesen ist der Verdampfer höherer Kälteleistung 21 im Kaltlagerfach 16 angeordnet und mit einer Kältemittel-Einspritzstelle 22 ausgestattet, welche zur Druckabsenkung des von einem nicht dargestellten Verflüssiger im Kältekreislauf auf den Verdampfer 21 zuströmenden Kältemittels dient. Der Verdampfer höhrer Kälteleistung 21 ist mit einem als Kältemittel-Kanalanordnung 23 dienenden, in Windungen auf der Verdampferplatine angeordneten Kältemittelkanal ausgestattet, dessen auslaufseitiges Ende in Einbaulage der Verdampferanordnung im Kältegerät 10 über der Kältemittel-Einspritzstelle 22 liegt und an eine Kältemittelleitung 24 angeschlossen ist. Diese dient zur strömungstechnischen Anbindung des Verdampfers höherer Kälteleistung 21 an den im Vergleich dazu mit einer geringeren Kälteleistung ausgestatteten, im Normalkühlfach 14 angeordneten platinenartigen Verdampfers 25, welcher mit dem Verdampfer 21 lediglich über die Kältemittelleitung 24 verbunden ist. Der Verdampfer geringerer Kälteleistung 25 ist mit einem als Kältemittel-Kanalanordnung 26 dienenden Kältemittelkanal versehen, welcher eine seiner mit der Kältemittelleitung 24 verbundenen Zuflußöffnung 27 aufweist und in eng aneinandergereihten Windungen über die Höhe der Verdampferplatine angeordnet ist. Das auslaufseitige Ende des Kältemittelkanals ist mit einem horizontale Anschlußstutzen aufweisenden, sackartig ausgebildeten Kältemittelsammler 28 versehen, bevor er in eine in Einbaulage des Verdampfers 25 höherliegend angeordnete Abflußöffnung 29 mündet, welche zum Anschluß an eine nicht dargestellte Saugleitung im Kältekreislauf dient. Durch die räumlich getrennte Anordnung der Saugleitung von der Kältemittel-Einspritzstelle 22 wird eine zur unnötigen Erwärmung des Verdampfers 21 beitragende Rückführleitung zur Einspritzstelle 22 vermieden, so daß die beiden Verdampfer 21 und 25 thermisch weitestgehend entkoppelt sind.A
Bei im Regelbetrieb befindlichem Kältemittelverdichter 20 wird das von diesem geförderte flüssige Kältemittel erst dem in der Reihenschaltung der beiden Verdampfer 21 und 25 an erster Stelle angeordneten Verdampfer höherer Kälteleistung 21 zugeführt, so daß dieser als erster gekühlt wird. Im Anschluß daran wird das flüssige Kältemittel in Reihenschaltung an zweiter Stelle befindlichen Verdampfer geringerer Kälteleistung 25 zugeführt, so daß sich dieser abkühlt. Mit zunehmender Laufzeit des Kältemittelverdichters 20 erhöht sich die Menge des flüssigen Kältemittels im Verdampfer geringerer Kälteleistung 25, wobei sich das in Laufe der Zeit überschüssige Kältemittel langsam im Kältemittelsammler 28 ansammelt, wodurch in Kombination mit den Strömungsrichtungen des Kältemittels vor dem Kältemittelsammler 28 durch die große Kanallänge erzeugten, volumenopitimierten Abschnitt der Kältemittel-Kanalanordnung 26 verhindert ist, daß flüssiges Kältemittel in das durch den abgesaugten Kältemitteldampf erwärmte Saugrohr gelangen kann. Nach dem Abschalten des Kältemittelverdichters 20 erwärmt sich der zur Kühlung des Normalkühlfaches 14 dienende Verdampfer geringerer Kälteleistung 25 wesentlich schneller als der im Kaltlagerfach 16 befindliche Verdampfer höherer Kälteleistung 21, wodurch das sich im Kältemittelsammler 28 angesammelte flüssige Kältemittel sehr rasch verdampft und teilweise im Verdampfer höherer Kälteleistung 21 kondensiert. Das nach dem Abschalten des Kältemittelverdichters 20 sich in der Kältemittel-Kanalanordnung 26 des Verdampfers 25 befindliche Kältemittel wird durch die Einwirkung der Schwerkraft auf das Kältemittel dem in Einbaulage der Verdampferanordnung darunter angeordneten Verdampfer höherer Kälteleistung zugeführt.When the
Es versteht sich, daß die Erfindung auch auf eine Verdampferplatine anwendbar ist, bei welcher ein Verdampferabschnitt höherer Kälteleistung über einen Verbindungssteg mit einem Verdampferabschnitt geringerer Kälteleistung verbunden ist, wobei die Rückführung des Kältemittels aus dem Verdampferabschnitt geringerer Kälteleistung nicht über den Verdampferabschnitt höherer Kälteleistung erfolgt.It goes without saying that the invention can also be applied to an evaporator board in which an evaporator section of higher refrigeration capacity is connected via a connecting web to an evaporator section of lower refrigeration capacity, the return of the refrigerant from the evaporator section of lower refrigeration capacity not via the evaporator section of higher refrigeration capacity.
Claims (4)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE1995124840 DE19524840A1 (en) | 1995-07-07 | 1995-07-07 | Evaporator arrangement for household refrigeration devices |
| DE29524840U | 1995-07-07 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP0752563A2 true EP0752563A2 (en) | 1997-01-08 |
| EP0752563A3 EP0752563A3 (en) | 1999-10-20 |
| EP0752563B1 EP0752563B1 (en) | 2003-12-03 |
Family
ID=7766301
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP19960106978 Expired - Lifetime EP0752563B1 (en) | 1995-07-07 | 1996-05-03 | Evaporator arrangement for domestic refrigerators |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0752563B1 (en) |
| DE (2) | DE19524840A1 (en) |
| ES (1) | ES2211922T3 (en) |
| TR (1) | TR199600556A2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000014459A1 (en) * | 1998-09-04 | 2000-03-16 | BSH Bosch und Siemens Hausgeräte GmbH | Evaporator arrangement |
| WO2001040721A1 (en) * | 1999-11-30 | 2001-06-07 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeration device |
| WO2002035162A1 (en) * | 2000-10-27 | 2002-05-02 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeratory and refrigerating device for a zeotropic refrigerating agent mixture |
| KR100463511B1 (en) * | 1998-01-14 | 2005-04-06 | 엘지전자 주식회사 | Refrigerator with two evaporators |
| CN104654646A (en) * | 2015-01-23 | 2015-05-27 | 青岛海尔股份有限公司 | Reversible direct cooling system, refrigerator and refrigeration control method |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2769319A (en) * | 1952-02-18 | 1956-11-06 | Whirlpool Seeger Corp | Two temperature household refrigerators |
| US2807149A (en) * | 1955-07-15 | 1957-09-24 | Whirlpool Seeger Corp | Cycle defrost type refrigerators |
| US3009338A (en) * | 1959-10-01 | 1961-11-21 | Westinghouse Electric Corp | Refrigeration apparatus |
| DE2039246A1 (en) * | 1970-08-07 | 1972-02-10 | Bosch Hausgeraete Gmbh | Refrigerator, especially two-temperature refrigerator |
| EP0178226A1 (en) * | 1984-10-05 | 1986-04-16 | Societe D'electromenager Du Nord Selnor | Two-compartment refrigerated cabinet |
| DE3703902A1 (en) * | 1987-02-09 | 1988-08-18 | Liebherr Hausgeraete | Plate evaporator for refrigerators and freezers |
-
1995
- 1995-07-07 DE DE1995124840 patent/DE19524840A1/en not_active Ceased
-
1996
- 1996-05-03 DE DE59610842T patent/DE59610842D1/en not_active Expired - Lifetime
- 1996-05-03 EP EP19960106978 patent/EP0752563B1/en not_active Expired - Lifetime
- 1996-05-03 ES ES96106978T patent/ES2211922T3/en not_active Expired - Lifetime
- 1996-07-03 TR TR96/00556A patent/TR199600556A2/en unknown
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2769319A (en) * | 1952-02-18 | 1956-11-06 | Whirlpool Seeger Corp | Two temperature household refrigerators |
| US2807149A (en) * | 1955-07-15 | 1957-09-24 | Whirlpool Seeger Corp | Cycle defrost type refrigerators |
| US3009338A (en) * | 1959-10-01 | 1961-11-21 | Westinghouse Electric Corp | Refrigeration apparatus |
| DE2039246A1 (en) * | 1970-08-07 | 1972-02-10 | Bosch Hausgeraete Gmbh | Refrigerator, especially two-temperature refrigerator |
| EP0178226A1 (en) * | 1984-10-05 | 1986-04-16 | Societe D'electromenager Du Nord Selnor | Two-compartment refrigerated cabinet |
| DE3703902A1 (en) * | 1987-02-09 | 1988-08-18 | Liebherr Hausgeraete | Plate evaporator for refrigerators and freezers |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100463511B1 (en) * | 1998-01-14 | 2005-04-06 | 엘지전자 주식회사 | Refrigerator with two evaporators |
| WO2000014459A1 (en) * | 1998-09-04 | 2000-03-16 | BSH Bosch und Siemens Hausgeräte GmbH | Evaporator arrangement |
| WO2001040721A1 (en) * | 1999-11-30 | 2001-06-07 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeration device |
| WO2002035162A1 (en) * | 2000-10-27 | 2002-05-02 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeratory and refrigerating device for a zeotropic refrigerating agent mixture |
| CN104654646A (en) * | 2015-01-23 | 2015-05-27 | 青岛海尔股份有限公司 | Reversible direct cooling system, refrigerator and refrigeration control method |
| CN104654646B (en) * | 2015-01-23 | 2017-04-05 | 青岛海尔股份有限公司 | The refrigeration control method of reversible direct-cooled system |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0752563B1 (en) | 2003-12-03 |
| EP0752563A3 (en) | 1999-10-20 |
| DE59610842D1 (en) | 2004-01-15 |
| ES2211922T3 (en) | 2004-07-16 |
| TR199600556A2 (en) | 1997-01-21 |
| DE19524840A1 (en) | 1997-01-09 |
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