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EP0073363A2 - Evaporator for a cooling apparatus with several temperatures - Google Patents

Evaporator for a cooling apparatus with several temperatures Download PDF

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Publication number
EP0073363A2
EP0073363A2 EP82107148A EP82107148A EP0073363A2 EP 0073363 A2 EP0073363 A2 EP 0073363A2 EP 82107148 A EP82107148 A EP 82107148A EP 82107148 A EP82107148 A EP 82107148A EP 0073363 A2 EP0073363 A2 EP 0073363A2
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EP
European Patent Office
Prior art keywords
evaporator
side wall
parallel
passage
compartment
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.)
Granted
Application number
EP82107148A
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German (de)
French (fr)
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EP0073363A3 (en
EP0073363B1 (en
Inventor
Georg Ing. Grad. Rannenberg
Gerd Dipl.-Ing. Vollhardt
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Licentia Patent Verwaltungs GmbH
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Licentia Patent Verwaltungs GmbH
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Publication of EP0073363A2 publication Critical patent/EP0073363A2/en
Publication of EP0073363A3 publication Critical patent/EP0073363A3/en
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Publication of EP0073363B1 publication Critical patent/EP0073363B1/en
Expired 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
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements

Definitions

  • the invention relates to an evaporator according to the preamble of the first claim.
  • the evaporator is part of an intermittently operated compression refrigerator, with the evaporator part assigned to the main refrigerator compartment being defrosted by frost and ice build-up during the downtime of the compression refrigerator.
  • This evaporator arrangement which is preferably used for the cooling device version described, has the disadvantage in the known designs that liquid refrigerant is transported from the evaporator assigned to the freezer compartment into the evaporator assigned to the main refrigerator compartment due to the pressure compensation in the refrigeration system during the downtime of the compression refrigerator.
  • This liquid refrigerant evaporates due to the higher heat load when entering the main refrigerator evaporator, primarily at the connection point of the freezer and the main refrigerator evaporator and prevents due to the resulting continuous cooling of this evaporator part, the required complete defrosting of the main cooling compartment evaporator.
  • additional measures for complete defrosting and avoidance of ice build-up are required in known cooling devices of this type.
  • the additional heating required for defrosting the surfaces cooled by flowing liquid during the downtime is achieved by taking advantage of the ambient heat by long downtimes or by arranging an electrical heating system on the evaporator. In the former case, this results in excessive temperature fluctuations in the refrigerated goods and in the second case an unnecessary increase in energy consumption due to the introduction of a heat source in the refrigerator compartment.
  • the invention has for its object to take measures in an evaporator according to the preamble of the first claim, by which icing on the main refrigerator evaporator in the area of the connection point between the freezer evaporator and the main refrigerator evaporator can be avoided with a simple construction, in particular by the fact that the afterflow of liquid Refrigerant is avoided in the main refrigerator compartment evaporator during the downtime of the compression refrigeration machine and thus the additional energy required: for defrosting can be significantly reduced or eliminated.
  • the refrigerant coming from the capillary tube acting as a throttling member is passed through the ceiling board over a short distance into the bottom board of the freezer evaporator, in which the tubing is large in volume with several parallel paths to reduce the flow velocity.
  • a parallel channel leads steeply upwards from the base plate to the ceiling plate, at least one transverse channel being provided in the side wall between the tubes of the parallel channel.
  • the tubing runs in several meandering turns.
  • the lower base plate acts as a kind of collecting vessel, in which there is an extensive separation of gaseous and liquid refrigerant when the compressor in the refrigerant circuit is switched off and the refrigerant is driven by pressure equalization in the refrigerant circuit.
  • the gas bubbles are separated again from liquid drops according to static laws, so that practically no liquid refrigerant is taken up from the bottom plate into the ceiling plate during downtimes of the compressor.
  • Small amounts of liquid entrained by the flow separate from the gas flow in the ceiling board and are returned to the floor board by the increasing arrangement of the ceiling board tubing.
  • a base plate 1 and a slightly inclined ceiling plate 2 together with a vertical side wall 3 form a one-piece freezer evaporator, to which a plate-shaped main refrigerator compartment evaporator 5 connects, which is approximately in the plane of the side wall 3.
  • the ceiling board 2 is inclined with respect to a horizontal plane from its connecting edge 6 with the side wall 3.
  • Dun g at connects skante 6 is inserted a throttle pipe 14 in the top board 2, by which the refrigerant in the refrigerant passage 7 is initiated.
  • the refrigerant channel 7 is led through the ceiling board 2 and the side wall 3 directly and without any turns into the floor board 1.
  • the refrigerant channel 7 branches into three sections connected in series with parallel pipes 8 which communicate in groups through a plurality of cross lines 9.
  • the parallel winding branches of the tubing in the base plate 1 enable, in particular, the gaseous components to have a separate flow path from the highly fluid-laden channel sections, so that the majority of the liquid components remain in the base plate 1.
  • the gaseous components flow through one of the last winding branch leading parallel duct 10 vertically through the side wall 3 upwards into the ceiling board 2.
  • At least one transverse duct 11 is provided in the parallel duct 10 for further separation of liquid and gaseous refrigerant according to static laws.
  • the tubing is uniformly distributed in turns over the surface, the outflow pipe 12 running through the side wall 3 continuously falling down to the connecting neck 4 and further to the turns of the main cooling compartment evaporator 5.
  • the ceiling board 2 which is inclined slightly upwards from the connecting edge 6, a further separation between gaseous and liquid refrigerant is achieved due to the slope, the liquid refrigerant being returned to the bottom board 1 of the freezer compartment evaporator.
  • connection neck 4 which tends to freeze during operation, is exposed to a significantly lower cold load during the defrosting phase, so that no more ripening or ice buildup on the main cooling compartment evaporator 5 is possible. There is therefore little or no heating of this connecting neck 4, which enables considerable energy savings.

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

Abstract

1. An evaporator for a multi-temperature refrigerating device having a main refrigerating compartment disposed below a deep-freezing compartment or freezer compartment, having an evaporator which is associated with the deep-freezing compartment or freezer compartment and which comprises piping for conveying coolant as a coolant passage (7) at least in a cover plate (2), in a side wall (3) and in a bottom plate (1), the injection of the expanded coolant into the coolant passage (7) being effected in the cover plate (2) which rises from its connecting edge (6) to the side wall (3) and the coolant passage (7) is taken from the cover plate (2), dropping steeply, into the side wall (3), directly to the piping (8, 9) of the bottom plate (1), the piping of which changes over, at the end at the flow outlet side, into a parallel passage (10) which extends in the side wall (3) and rises continuously steeply and which is connected directly to the piping of the cover plate (2) from which the end (12) of the piping at the flow outlet side is taken, dropping steadily, through the side wall (3) to the normal refrigerating compartment evaporator (5) connected thereto, in front of which the deep-freezing-compartment evaporator is connected in series in the coolant circuit, characterised in that the coolant passage (7) in the bottom plate (1) comprises series-connected portions with parallel pipelines (8) which are in communication in groups through a plurality of transverse pipelines (9), that the passage branches of the parallel passage (10) lead away from the last portion and are connected to one another via at least one transverse passage (11) in the side wall (3), that the coolant passage (7) is then taken, in a single duct, into the cover plate (2) in meandering turns distributed over the area, that the turns extend parallel to the connecting edge (6), that the parallel passage (10) is connected to the piping of the cover plate (2) close to the connecting edge (6) and that the end of the piping of the cover plate (2) at the flow outlet side passes through a point (13) which is situated higher than the other turns.

Description

Die Erfindung betrifft einen Verdampfer gemäß dem Oberbegriff des ersten Patentanspruches.The invention relates to an evaporator according to the preamble of the first claim.

Der Verdampfer ist Teil einer intermittierend betriebenen Kompressionskältemaschine,wobei der dem Hauptkühlfach zugeordnete Verdampferteil während der Stillstandszeit der Kompressionskältemaschine von Reif- und Eisansatz abgetaut wird. Diese für die beschriebene Kühlgeräteausführung bevorzugt angewandte Verdampferanordnung hat in den bekannten Ausführungen den Nachteil, daß während der Stillstandszeit der Kompressionskältemaschine bedingt durch den Druckausgleich in dem Kältesystem flüssiges Kältemittel von dem dem Tiefkühlfach zugeordneten Verdampfer in den dem Hauptkühlfach zugeordneten Verdampfer transportiert wird. Dieses flüssige Kältemittel verdampft durch die höhere Wärmebelastung beim Eintritt in den Hauptkühlfachverdampfer, vornehmlich an der Verbinüngsstelle des Tiefkühl- und des Hauptkihlfachverdampfers und verhindert durch die hieraus resultierende stetige Kühlung dieses Verdampferteiles die erforderliche vollständige Abtauung des Hauptkühlfachverdampfers. Um einen die Funktion des Hauptkühlfachverdampfers gefährdenden Eisaufbau zu vermeiden, werden bei bekannten Kühlgeräten dieser Bauart zusätzliche Maßnahmen zur vollständigen Abtauuhg und Vermeidung von Eisansatz erforderlich. Die zur Abtauung der in der Stillstandszeit durch nachströmende Flüssigkeit gekühlten Flächen erforderliche zusätzliche Erwärmung wird unter Ausnutzung der Umgebungswärme durch lange Stillstandszeiten oder durch Anordnung eines elektrischen Heizungssystemes am Verdampfer erreicht. Dies hat im ersteren Fall zu große Temperaturschwankungen im Kühlgut und im zweiten Fall eine unnötige Erhöhung des Energieverbrauches durch Einbringung einer Wärmequelle im Kühlfach zur Folge.The evaporator is part of an intermittently operated compression refrigerator, with the evaporator part assigned to the main refrigerator compartment being defrosted by frost and ice build-up during the downtime of the compression refrigerator. This evaporator arrangement, which is preferably used for the cooling device version described, has the disadvantage in the known designs that liquid refrigerant is transported from the evaporator assigned to the freezer compartment into the evaporator assigned to the main refrigerator compartment due to the pressure compensation in the refrigeration system during the downtime of the compression refrigerator. This liquid refrigerant evaporates due to the higher heat load when entering the main refrigerator evaporator, primarily at the connection point of the freezer and the main refrigerator evaporator and prevents due to the resulting continuous cooling of this evaporator part, the required complete defrosting of the main cooling compartment evaporator. In order to avoid an ice build-up endangering the function of the main cooling compartment evaporator, additional measures for complete defrosting and avoidance of ice build-up are required in known cooling devices of this type. The additional heating required for defrosting the surfaces cooled by flowing liquid during the downtime is achieved by taking advantage of the ambient heat by long downtimes or by arranging an electrical heating system on the evaporator. In the former case, this results in excessive temperature fluctuations in the refrigerated goods and in the second case an unnecessary increase in energy consumption due to the introduction of a heat source in the refrigerator compartment.

Der Erfindung liegt die Aufgabe zugrunde, bei einem Verdampfer gem-äß dem Oberbegriff des ersten Anspruches Maßnahmen zu treffen, durch die bei einfachem Aufbau Vereisungen am Hauptkühlfachverdampfer im Bereich der Verbindungsstelle von Tiefkühlfachverdampfer und Hauptkühlfachverdampfer vermieden werden können, insbesondere dadurch, daß das Nachströmen von flüssigem Kältemittel während der Stillstandszeit der Kompressionskältemaschine in den Hauptkühlfachverdampfer vermieden wird und damit die erforderliche zusätzliche Energie:zur Abtauung wesentlich reduziert werden oder entfallen kann.The invention has for its object to take measures in an evaporator according to the preamble of the first claim, by which icing on the main refrigerator evaporator in the area of the connection point between the freezer evaporator and the main refrigerator evaporator can be avoided with a simple construction, in particular by the fact that the afterflow of liquid Refrigerant is avoided in the main refrigerator compartment evaporator during the downtime of the compression refrigeration machine and thus the additional energy required: for defrosting can be significantly reduced or eliminated.

Die Lösung dieser Aufgabe erfolgt durch die kennzeichnenden Merkmale des ersten Anspruches.This problem is solved by the characterizing features of the first claim.

Durch eine Ausgestaltung gemäß der Erfindung wird das von dem als Drosselorgan wirkenden Kapillarrohr kommende Kältemittel durch die Deckenplatine auf kurzem Wege in die Bodenplatine des Tiefkühlfachverdampfers geleitet, in welcher die Berohrung großvolumig mit mehreren Parallelwegen zur Verminderung der Strömungsgeschwindigkeit geführt ist. Von der Bodenplatine führt ein Parallelkanal steil nach oben zur Deckenplatine, wobei in der Seitenwand wenigstens ein Querkanal zwischen den Rohren des Parallelkanals vorgesehen ist. In der Deckenplatine dagegen verläuft die Berohrung einzügig in mehreren mäanderförmigen Windungen. Bei dieser Kältemittelkanalanordnung wirkt die untere Bodenplatine als eine Art Sammelgefäß, in dem eine weitgehende Trennung von gasförmigen und flüssigem Kältemittel eintritt, wenn der Kompressor im Kältemittelkreislauf abgeschaltet ist und der Antrieb des Kältemittels durch den Druckausgleich im Kältemittelkreislauf erfolgt. Insbesondere werden durch den Parallelkanal und den Querkanal in der Seitenwand nochmals die Gasblasen von Flüssigkeitstropfen nach statischen Gesetzmäßigkeiten getrennt, so daß in den Stillstandszeiten des Kompressors aus der Bodenplatine praktisch kein flüssiges Kältemittel nach oben in die Deckenplatine mitgenommen wird. Durch die Strömung mitgerissene geringe Flüssigkeitsmengen trennen sich in der Deckenplatine vom Gasstromund werden durch die steigende Anordnung der Deckenplatinenberohrung in die Bodenplatine zurückgeführt. Durch diese Abtennung von flüssigem Kältemittel wird erreicht, daß nur gasförmiges Kältemittel zum Hauptkühlfachverdampfer strömt. Dadurch wird die Unterkühlung des Verbindungshalses der Verdampfer durch verdampfendes Kältemittel unterbunden und damit die Abtauung des Hauptkühlfachverdempfers auch in diesen kritischen Bereich sibhergestellt.Through an embodiment according to the invention, the refrigerant coming from the capillary tube acting as a throttling member is passed through the ceiling board over a short distance into the bottom board of the freezer evaporator, in which the tubing is large in volume with several parallel paths to reduce the flow velocity. A parallel channel leads steeply upwards from the base plate to the ceiling plate, at least one transverse channel being provided in the side wall between the tubes of the parallel channel. In the ceiling board, on the other hand, the tubing runs in several meandering turns. In this refrigerant channel arrangement, the lower base plate acts as a kind of collecting vessel, in which there is an extensive separation of gaseous and liquid refrigerant when the compressor in the refrigerant circuit is switched off and the refrigerant is driven by pressure equalization in the refrigerant circuit. In particular, through the parallel channel and the transverse channel in the side wall, the gas bubbles are separated again from liquid drops according to static laws, so that practically no liquid refrigerant is taken up from the bottom plate into the ceiling plate during downtimes of the compressor. Small amounts of liquid entrained by the flow separate from the gas flow in the ceiling board and are returned to the floor board by the increasing arrangement of the ceiling board tubing. This separation of liquid refrigerant ensures that only gaseous refrigerant flows to the main refrigerator compartment evaporator. As a result, the subcooling of the connecting neck of the evaporators by evaporating refrigerant is prevented, and thus the defrosting of the main refrigerator compartment evaporator is also achieved in this critical area.

Vorteilhafte Ausgestaltungen sind in den weiteren Ansprüchen angegeben.Advantageous refinements are specified in the further claims.

Die Erfindung ist nachfolgend anhand der Zeichnung eines Ausführungsbeispiels näher erläutert.'The invention is explained in more detail below with reference to the drawing of an exemplary embodiment.

Eine Bodenplatine 1 und eine demgegenüber leicht geneigte Deckenplatine 2 bilden zusammen mit einer senkrechten Seitenwand 3 einen einstückig hergestellten Tiefkühlfachverdampfer, an den sich über einen Verbindungshals 4 ein plattenförmiger Hauptkühlfachverdampfer 5 anschließt, welcher etwa in der Ebene der Seitenwand 3 steht. Die Deckenplatine 2 ist von ihrer Verbindungskante 6-mit der Seitenwand 3 aus ansteigend gegenüber einer waagerechten Ebene geneigt. An der Verbin- dungskante 6 ist in der Deckenplatine 2 ein Drosselrohr 14 eingeführt, durch die das Kältemittel in den Kältemittelkanal 7 eingeleitet wird. Der Kältemittelkanal 7 ist durch die Deckenplatine 2 und die Seitenwand 3 direkt und windungsfrei in die Bodenplatine 1 geführt. In der Bodenplatine 1 verzweigt sich der Kältemittelkanal 7 in drei hintereinander geschaltete Abschnitte mit parallelen Rohrleitungen 8, die gruppenweise durch mehrere Querleitungen 9 kommunizieren. Hierdurch wird nicht nur.ein großes Volumen für die Aufnahme von Kältemittel sondern aufgrund niedriger Strömungsgeschwindigkeiten in der Druckausgleichsphase des Kältesystems eine Trennung von flüssigem und gasförmigen Kältemittel erreicht. Die parallelen Windungsäste der Berohrung in der Bodenplatine 1 ermöglichen insbesondere den gasförmigen Anteilen einen getrennten Strömungsweg von den stark flüssigkeitsbehafteten Kanalabschnitten, so daß die flüssigen Anteile zum überwiegenden Teil in der Bodenplatine 1 verbleiben. Die gasförmigen Anteile strömen dagegen durch einen vom letzten Windungsast wegführenden Parallelkanal 10 senkrecht durch die Seitenwand 3 nach oben in die Deckenplatine 2. Dabei ist im Parallelkanal 10 zur weiteren Trennung von flüssigem und gasförmigen Kältemittel nach statischen Gesetzmäßigkeiten wenigstens ein Querkanal 11 vorgesehen. In der Deckenplatine 2 ist die Berohrung einzügig in Windungen über die Fläche verteilt, wobei das Abströmrohr 12 durch die Seitenwand 3 stetig fallend nach unten zum Verbindungshals 4 und weiter zu den Windungen des Hauptkühlfachverdampfers 5 verläuft. In der Deckenplatine 2, die von der Verbindungskante 6 an leicht nach oben geneigt ist, wird durch die Steigung eine weitere Trennung zwischen gasförmigem und flüssigem Kältemittel erreicht, wobei das flüssige Kältemittel in die Bodenplatine 1 des Tiefkühlfach- verdampfers zurückgeführt wird. Somit wird nach der Trennung der Gas- und Flüssigphasen von dem höchsten Punkt 13 durch das Abströmrohr 12 die für den Druckausgleich im Kältemittelsystem erforderliche Kältemittelmasse nur im Gaszustand mit geringer Enthalpie in den Hauptkühlfachverdampfer geleitet. In den Stillstandszeiten des Kompressors wird daher der Verbindungshals 4 nicht mehr mit verdampf= barem Kältemittel beaufschlagt, so daß keine nennenswerte Kälteleistung zum Hauptkühlfachverdampfer 5 gelangt. Dadurch ist der Verbindungshals 4, der im Betrieb erfahrungsgemäß zur Vereisung neigt, während der Abtauphase einer wesentlich geringeren Kältebelastung ausgesetzt, so daß an ihm kein stärkerer reif - bzw. Eisansatz als am Hauptkühlfachverdampfer 5 möglich ist. Es bedarf daher keiner oder nur geringer Beheizung dieses Verbundungshalses 4, wodurch eine erhebliche Energieeinsparung möglich ist.A base plate 1 and a slightly inclined ceiling plate 2 together with a vertical side wall 3 form a one-piece freezer evaporator, to which a plate-shaped main refrigerator compartment evaporator 5 connects, which is approximately in the plane of the side wall 3. The ceiling board 2 is inclined with respect to a horizontal plane from its connecting edge 6 with the side wall 3. Dun g at connects skante 6 is inserted a throttle pipe 14 in the top board 2, by which the refrigerant in the refrigerant passage 7 is initiated. The refrigerant channel 7 is led through the ceiling board 2 and the side wall 3 directly and without any turns into the floor board 1. In the base plate 1, the refrigerant channel 7 branches into three sections connected in series with parallel pipes 8 which communicate in groups through a plurality of cross lines 9. This not only achieves a large volume for the absorption of refrigerant, but also separates liquid and gaseous refrigerant due to low flow velocities in the pressure equalization phase of the refrigeration system. The parallel winding branches of the tubing in the base plate 1 enable, in particular, the gaseous components to have a separate flow path from the highly fluid-laden channel sections, so that the majority of the liquid components remain in the base plate 1. In contrast, the gaseous components flow through one of the last winding branch leading parallel duct 10 vertically through the side wall 3 upwards into the ceiling board 2. At least one transverse duct 11 is provided in the parallel duct 10 for further separation of liquid and gaseous refrigerant according to static laws. In the ceiling plate 2, the tubing is uniformly distributed in turns over the surface, the outflow pipe 12 running through the side wall 3 continuously falling down to the connecting neck 4 and further to the turns of the main cooling compartment evaporator 5. In the ceiling board 2, which is inclined slightly upwards from the connecting edge 6, a further separation between gaseous and liquid refrigerant is achieved due to the slope, the liquid refrigerant being returned to the bottom board 1 of the freezer compartment evaporator. Thus, after the separation of the gas and liquid phases from the highest point 13 through the outflow pipe 12, the refrigerant mass required for pressure compensation in the refrigerant system is passed into the main cooling compartment evaporator only in the gas state with low enthalpy. Therefore, the downtime of the compressor of the connection neck 4 is not acted upon with more vaporized = Barem refrigerant, so that no appreciable cooling capacity leads to the main refrigerating compartment evaporator. 5 As a result, the connecting neck 4, which tends to freeze during operation, is exposed to a significantly lower cold load during the defrosting phase, so that no more ripening or ice buildup on the main cooling compartment evaporator 5 is possible. There is therefore little or no heating of this connecting neck 4, which enables considerable energy savings.

Claims (4)

1. Verdampfer für ein Mehr- Temperaturen-Kühlgerät mit einem unterhalb eines Tiefkühlfaches oder Gefrierfaches angeordneten Hauptkühlfach, mit einem dem Tiefkühlfach oder Gefrierfach zugeordneten Verdampfer. der wenigstens in einer Deckenplatine- in einer Seitenwand und in einer Bodenplatine eine in Windungen geführte Berohrung zur Führung von Kältemittel aufweist, wobei die Einspritzung des expandierten Kältemittels in den Kältemittelkanal in der Deckenplatine erfolgt, und der Tiefkühlfachverdampfer in Reihe vor dem dem Normalkühlfach zugeordneten Verdampfer im Kältemittelkreislauf liegt. dadurch gekennzeichnet, daß der Kältemittelkanal (7) windungsfrei in der Deckenplatine (2) und steil abfallend in der Seitenwand (3) direkt zur Berohrung der Bodenplatine (1) geführt ist, daß die Berohrung der Bodenplatine (1) am strömungsseitigen Ende in einen stetig steil steigenden, in der Seitenwand (3) verlaufenden Parallelkanal (10) übergeht, daß die Kanalzweige des Parallelkanals (10) über mindestens einen Querkanal (11) miteinander verbunden sind. daß der Parallelkanal (10) unmittelbar an die Berohrung der Deckenplatine (2) angeschlossen ist. und daß der Kältemittelkanal von dem strömungsseitigen Ende (12) der Deckenplatinenberohrung stetig fallend durch die Seitenwand (3) zum damit verbundenen Hauptkühlfachverdampfer (5) geführt ist.1. Evaporator for a multi-temperature refrigerator with a main refrigerator compartment arranged below a freezer or freezer compartment, with an evaporator assigned to the freezer compartment or freezer compartment. which has at least in a ceiling board in a side wall and in a bottom board a winding tube for guiding refrigerant, the injection of the expanded refrigerant into the refrigerant channel takes place in the ceiling board, and the freezer evaporator in series in front of the evaporator assigned to the normal refrigerator in Refrigerant circuit. characterized in that the refrigerant channel (7) is led without windings in the ceiling plate (2) and falling steeply in the side wall (3) directly to the bottom plate (1), that the bottom plate (1) has a continuous flow at the flow end steeply rising parallel channel (10) running in the side wall (3) merges with the fact that the channel branches of the parallel channel (10) are connected to one another via at least one transverse channel (11). that the parallel channel (10) is connected directly to the tubing of the ceiling board (2). and that the refrigerant channel is continuously falling from the flow-side end (12) of the ceiling plate bore through the side wall (3) to the main cooling compartment evaporator (5) connected to it. 2. Verdampfer nach Anspruch 1. dadurch gekennzeichnet. daß die Windungsäste der Berohrung der Bodenplatine (1) jeweils parallel zueinander verlaufende Rohre (8) aufweisen. und daß die Rohre (8) jedes Windungsastes durch Querleitungen (9) miteinander verbunden sind.2. Evaporator according to claim 1. characterized. that the winding branches of the tubing of the base plate (1) each have tubes (8) running parallel to one another. and that the tubes (8) of each winding branch are connected to one another by cross lines (9). 3. Verdampfer nach Anspruch 1 oder 2. dadurch gekennzeichnet daß die Deckenplatine (2) gegenüber einer waagrechten Ebene geneigt ist derart, daß die Verbindungskante (6) mit der Seitenwand (3) tiefer liegt. daß die Windungen der Berohrung parallel zur Verbindungskante (6) verlaufen. daß der Parallelkanal (10) nahe der Verbindungskante (6) an die Berohrung angeschlossen ist und daß das strömungsseitige Ende der Berohrung der Deckenplatine durch einen Punkt (13) läuft der höher als die übrige mäanderförmige Berohrung der Deckenplatine (2) liegt.3. Evaporator according to claim 1 or 2. characterized in that the ceiling board (2) is inclined relative to a horizontal plane such that the connecting edge (6) with the side wall (3) is lower. that the turns of the pipe run parallel to the connecting edge (6). that the parallel channel (10) is connected to the tubing near the connecting edge (6) and that the flow-side end of the tubing of the ceiling p latine runs through a point (13) that is higher than the rest of the meandering tubing of the ceiling board (2). 4. Verdampfer nach Anspruch 1, 2 oder 3. dadurch,gekennzeichnet, daß der Kältemittelkanal von dem strömungsseitigen Ende der Berohrung der Deckenplatine auf einem nicht mit einer Seitenwand verbundenen stegartigen Verbindungsstück oder als Rohr zum Hauptkühlfachverdampfer (5) geführt ist.4. Evaporator according to claim 1, 2 or 3., characterized in that the refrigerant channel is guided from the flow-side end of the tubing to the ceiling plate on a web-like connecting piece not connected to a side wall or as a tube to the main cooling compartment evaporator (5).
EP19820107148 1981-08-29 1982-08-07 Evaporator for a cooling apparatus with several temperatures Expired EP0073363B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813134300 DE3134300A1 (en) 1981-08-29 1981-08-29 EVAPORATOR FOR A REFRIGERATOR
DE3134300 1981-08-29

Publications (3)

Publication Number Publication Date
EP0073363A2 true EP0073363A2 (en) 1983-03-09
EP0073363A3 EP0073363A3 (en) 1983-07-06
EP0073363B1 EP0073363B1 (en) 1985-06-26

Family

ID=6140473

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820107148 Expired EP0073363B1 (en) 1981-08-29 1982-08-07 Evaporator for a cooling apparatus with several temperatures

Country Status (2)

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EP (1) EP0073363B1 (en)
DE (1) DE3134300A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000014459A1 (en) * 1998-09-04 2000-03-16 BSH Bosch und Siemens Hausgeräte GmbH Evaporator arrangement

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3224452A1 (en) * 1982-06-30 1984-01-05 Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart Household refrigerator, especially two-temperature, single-circuit refrigerator
DE4141641A1 (en) * 1991-12-17 1993-06-24 Bosch Siemens Hausgeraete SECOND TEMPERATURE REFRIGERATOR

Citations (11)

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Publication number Priority date Publication date Assignee Title
DE1092939B (en) * 1957-07-09 1960-11-17 Gen Motors Corp Arrangement of refrigerant lines in refrigeration machines
US2986901A (en) * 1959-03-13 1961-06-06 Whirlpool Co Refrigerant evaporator
FR1434700A (en) * 1964-09-15 1966-04-08 Bosch Gmbh Robert evaporator for refrigerating machines, in particular for household refrigerators and machine equipped with said evaporator
DE1232598B (en) * 1964-07-10 1967-01-19 Danfoss As Cooling system with evaporator
DE1254650B (en) * 1964-12-01 1967-11-23 Danfoss As Cooling system with evaporator
DE6903900U (en) * 1969-01-31 1969-07-10 Bauknecht Gmbh G REFRIGERATED FURNITURE
DE1476962A1 (en) * 1964-12-14 1969-10-23 Electrolux Ab Refrigerator with two thermally insulated chambers and a compressor-operated cooling device
DE1476988A1 (en) * 1966-06-18 1970-03-19 Bosch Hausgeraete Gmbh Evaporator for refrigerators, especially for household refrigerators
GB1213644A (en) * 1967-03-03 1970-11-25 Alcoa Of Great Britain Ltd Improvements in or relating to heat exchangers
FR2134475A1 (en) * 1971-04-26 1972-12-08 Gen Motors Corp
FR2451559A1 (en) * 1979-03-12 1980-10-10 Schmoele Metall R & G Evaporator for compressor driven refrigerator - has connecting tongues punched out of metal plate with medium passages directed towards inside

Family Cites Families (2)

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Publication number Priority date Publication date Assignee Title
DE7431690U (en) * 1975-07-03 Bosch Siemens Hausgeraete Gmbh Evaporators for refrigerators, in particular two-temperature refrigerators
DE2231538A1 (en) * 1971-07-03 1973-01-11 Zanussi A Spa Industrie IMPROVEMENT TO REFRIGERATOR EVAPORATORS AND MANUFACTURING PROCESSES THEREFORE

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1092939B (en) * 1957-07-09 1960-11-17 Gen Motors Corp Arrangement of refrigerant lines in refrigeration machines
US2986901A (en) * 1959-03-13 1961-06-06 Whirlpool Co Refrigerant evaporator
DE1232598B (en) * 1964-07-10 1967-01-19 Danfoss As Cooling system with evaporator
FR1434700A (en) * 1964-09-15 1966-04-08 Bosch Gmbh Robert evaporator for refrigerating machines, in particular for household refrigerators and machine equipped with said evaporator
DE1254650B (en) * 1964-12-01 1967-11-23 Danfoss As Cooling system with evaporator
DE1476962A1 (en) * 1964-12-14 1969-10-23 Electrolux Ab Refrigerator with two thermally insulated chambers and a compressor-operated cooling device
DE1476988A1 (en) * 1966-06-18 1970-03-19 Bosch Hausgeraete Gmbh Evaporator for refrigerators, especially for household refrigerators
GB1213644A (en) * 1967-03-03 1970-11-25 Alcoa Of Great Britain Ltd Improvements in or relating to heat exchangers
DE6903900U (en) * 1969-01-31 1969-07-10 Bauknecht Gmbh G REFRIGERATED FURNITURE
FR2134475A1 (en) * 1971-04-26 1972-12-08 Gen Motors Corp
FR2451559A1 (en) * 1979-03-12 1980-10-10 Schmoele Metall R & G Evaporator for compressor driven refrigerator - has connecting tongues punched out of metal plate with medium passages directed towards inside

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000014459A1 (en) * 1998-09-04 2000-03-16 BSH Bosch und Siemens Hausgeräte GmbH Evaporator arrangement

Also Published As

Publication number Publication date
DE3134300A1 (en) 1983-03-10
EP0073363A3 (en) 1983-07-06
EP0073363B1 (en) 1985-06-26
DE3134300C2 (en) 1988-06-01

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