EP0180904A2 - Cooling device - Google Patents

Cooling device Download PDF

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Publication number
EP0180904A2
EP0180904A2 EP85113773A EP85113773A EP0180904A2 EP 0180904 A2 EP0180904 A2 EP 0180904A2 EP 85113773 A EP85113773 A EP 85113773A EP 85113773 A EP85113773 A EP 85113773A EP 0180904 A2 EP0180904 A2 EP 0180904A2
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EP
European Patent Office
Prior art keywords
cooling device
suction
subcooler
line
refrigerant
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
EP85113773A
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German (de)
French (fr)
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EP0180904B1 (en
EP0180904A3 (en
Inventor
Hermann Renz
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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Publication date
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to AT85113773T priority Critical patent/ATE46026T1/en
Publication of EP0180904A2 publication Critical patent/EP0180904A2/en
Publication of EP0180904A3 publication Critical patent/EP0180904A3/en
Application granted granted Critical
Publication of EP0180904B1 publication Critical patent/EP0180904B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • the invention relates to a cooling device with a piston compressor having a plurality of cylinders, a condenser, an expansion element and an evaporator, with a line connecting the piston compressor, the condenser, the expansion element and the evaporator to one another for an evaporable refrigerant liquid, and with an in the line between the condenser and expansion element, provided with a vaporizable coolant subcooler for the refrigerant.
  • the object is achieved in that part of the refrigerant is used as the coolant for the subcooler, and an outlet opening of the subcooler for evaporated coolant is connected via an additional suction line to the suction side of part of the cylinders of the piston compressor.
  • a multi-cylinder, motor-driven compressor 1 sucks vapor Refrigerant via a so-called suction line 2 from an evaporator 3 at a relatively low pressure and compresses the steam to a relatively high pressure in order to convey it via a so-called compressed gas line 4 into a condenser 5.
  • a heat transfer medium for example air, water or the like
  • the liquefied (and slightly subcooled) refrigerant is passed via a liquid line 6 to an expansion device 7, the function of which is to feed an amount of refrigerant liquid adapted to the respective operating conditions into the evaporator 3.
  • the expansion element 7 is also a throttling point between high and low pressure.
  • the liquid refrigerant fed into the evaporator 3 and kept at low pressure evaporates by supplying heat and is then sucked off again by the compressor 1 via the suction line 2, either dry saturated or slightly overheated.
  • cooling capacity the amount of heat absorbed in the evaporator 3
  • the subcooler 8 has its own coolant circuit with compressor 11, suction line 12, pressure line 14,
  • the circuit of the subcooler 8 also contains a solenoid valve 19.
  • the refrigerant circuit connected to the compressor 1 is also referred to as the main circuit, the coolant circuit connected to the compressor 11 as a secondary circuit. Both circuits work physically in the same way.
  • the delivery volume of the compressor 11 required for the secondary or subcooling circuit need only be approximately 10 to 25% of the delivery volume of the compressor 1 in order to achieve the desired liquid subcooling.
  • the core of which is a compressor which combines the functions of the compressors 1 and 11.
  • the common piston compressor 21 has six cylinders. Of these six cylinders, only a few (e.g. five cylinders) draw vaporous refrigerant via the suction line 22 from the evaporator 23 and, in the same way as previously described with reference to the main circuit of FIG. 1, convey via the compressed gas line 24 into the common condenser 25. After leaving the condenser 25, the liquefied refrigerant is passed directly through the subcooler 28 to the expansion element 27 via a first line A of the liquid line 26 and is fed by the latter into the evaporator 23 in a controlled manner and, after evaporation, is sucked off again by the piston compressor 21.
  • a few e.g. five cylinders
  • a partial flow of the liquefied refrigerant is fed into the subcooler 28 in a controlled manner via a further line B of the liquid line 26 via a remotely controlled solenoid valve 29 and through a further expansion element 30.
  • the refrigerant evaporates due to this partial stream of the heat supply by the relatively warmer K älteschierikeit of the strand A and is then used as an additional suction vapor, with an outlet opening 31 of the subcooler 28 pumped connected suction line 32.
  • This pumping takes place according to the invention via the cylinder or cylinders of the piston compressor 21-, the suction chambers of which are not connected to the line 22 but to the line 32. From the suction side of this or these cylinders, the suction steam is then conveyed to a common pressure chamber of the piston compressor 21 and mixed there with the steam of the main compressor part (originating from the suction line 22). This process causes the refrigerant liquid to be subcooled in the subcooler 8 with the aforementioned increase in performance resulting therefrom.
  • FIG. 3 shows a modified arrangement in which the subcooler 38 is designed as an "open liquid collector", ie does not act as a heat exchanger like the subcooler 28 in the case of FIG. 2. Corresponding parts are provided with the same reference numerals in FIGS. 2 and 3.
  • the principle of operation of the "open" subcooler 38 is based on the fact that part of the liquid refrigerant contained therein is sucked off in vapor form by the relevant part of the compressor 21 via the additional suction line 32.
  • the K included in the sub-cooler 38 älteffentechnik is subcooled thereby.
  • the solenoid valve 29 has the task of interrupting the refrigerant flow during the standstill periods and is opened with a certain delay after the start.
  • a regulator 39 in the additional suction line 32 controls the pressure and the flowing amount of refrigerant.
  • a pressure regulator 4o is provided in the system according to FIG. 3, which is required to maintain a certain condensing pressure.
  • FIG. 4 shows one of the twin cylinder heads.
  • the other cylinder heads of the compressor are designed in the usual way.
  • the suction chamber of the cylinder head shown in FIG. 4 is divided into two suction chambers 42 and 43 by a partition 41.
  • the chamber 42 is connected to the subcooler via the additional suction line 32 in the manner described.
  • the suction chamber 43 like the suction chambers of the other cylinders, is connected to the evaporator 23 via the suction line 22.
  • One of the pistons 44 of the compressor is visible in FIG. 3. All cylinders of the arrangement are connected to a common pressure chamber (not shown) in the usual way.
  • a valve device 45 is arranged in the partition 41, which is designed either (as shown) as a check valve 46 or as a solenoid valve can be.
  • the compressor compressor 21
  • the subcooler is first pumped down to a suction pressure that corresponds to that of the other cylinders.
  • the check valve opens automatically, the cylinder in question then works in parallel with the other compressor part.
  • valve device 41 as a solenoid valve, this must already be opened when the solenoid valve 29 closes.
  • the cooling device described offers the following advantages: at the start, the system can initially stabilize by delayed opening of the solenoid valve 29. The risk of refrigerant transfer from the subcooler to the compressor during the Start-up phase is avoided by the aforementioned empty pumping. By switching the supercooling circuit on and off, power control is possible without affecting the application limits. By combining the main circuit with its secondary circuit, there is no need for second compressors and condensers with accessories. This also results in a simplified line assembly. A subsequent retrofitting of the compressor to the embodiment according to FIG. 4 is possible.

Abstract

1. A cooling device comprising a multi-cylinder reciprocating compressor (21), a liquefier (25), an expansion unit (27) an evaporator (23), and pipes (22, 24, 26) to contain a cooling liquid which can be vaporized, which pipes connect the reciprocating compressor, the liquefier, the expansion unit and the evaporator to one another, and with a supercooler (28, 38) for the cooling liquid, which supercooler operates with a cooling medium which can be vaporized and is situated in the pipe (26) between the liquefier and the expansion unit, wherein a part of the cooling liquid is used as cooling medium for the supercooler, and wherein the outlet opening (31) of the supercooler is connected by means of an auxiliary suction pipe (32) to the suction side of a portion of the cylinders of the reciprocating compressor, and wherein, moreover, either a part of the cooling liquid which is diverted after the liquefier is led through an additional expansion unit (30), and then through the supercooler which is then constructed as a heat exchanger (28) and from here to the auxiliary suction pipe, or the supercooler is constructed as a gas-liquid-separating vessel (38) connected to the auxiliary suction pipe, in which part of the diverted cooling liquid is vaporized by pressure reduction and consequently the remaining liquid portion is cooled, characterized in that a suction chamber (42), which is connected to the auxiliary suction pipe (32), of at least one cylinder of the reciprocating compressor (21) is separated by a separating wall (41) from the suction chambers (43) of the other cylinders, and a valve device (45) is arranged in the separating wall, and in that this valve device closes when the pressure in the suction chamber (42) connected to the auxiliary suction pipe exceeds that in the other suction chambers (43).

Description

Die Erfindung betrifft eine Kühlvorrichtung mit einem mehrere Zylinder aufweisenden Kolbenverdichter, einem Verflüssiger, einem Expansionsorgan und einem Ver- da.mpfer, mit einer den Kolbenverdichter, den Verflüssiger, das Expansionsorgan und den Verdampfer miteinander verbindenden Leitung für eine verdampfbare Kälteflüssigkeit, und mit einem in der Leitung zwischen Verflüssiger und Expansionsorgan vorgesehenem, mit einem verdampfbaren Kühlmittel arbeitenden Unterkühler für die Kälteflüssigkeit.The invention relates to a cooling device with a piston compressor having a plurality of cylinders, a condenser, an expansion element and an evaporator, with a line connecting the piston compressor, the condenser, the expansion element and the evaporator to one another for an evaporable refrigerant liquid, and with an in the line between the condenser and expansion element, provided with a vaporizable coolant subcooler for the refrigerant.

Bei bekannten Kühlvorrichtungen oder Kälteanlagen dieser Art werden Leistung und Wirkungsgrad manchmal durch einen zusätzlichen Unterkühlungskreislauf gesteigert, insbesondere bei Systemen mit relativ großer Differenz zwischen kalter und warmer Seite.In known cooling devices or refrigeration systems of this type, performance and efficiency are sometimes increased by an additional supercooling circuit, in particular in systems with a relatively large difference between the cold and the warm side.

Hierzu wird neben dem Hauptkreislauf der Kälteflüssigkeit ein Nebenkreislauf für das Kühlmittel des Unterkühlers mit eigenem Verdichter, Verflüssiger und Expansionsorgan benötigt, wobei der Unterkühler dann als Verdampfer wirkt.For this purpose, a secondary circuit for the coolant of the subcooler with its own compressor, condenser and Expansion device needed, the subcooler then acts as an evaporator.

Diese Kühlvorrichtungen mit Unterkühlung der Kälteflüssigkeit haben sich wegen des erforderlichen hohen Aufwandes bisher noch nicht durchgesetzt. Abgesehen von dem hohen Aufwand ist der Verdichter des den Unterkühler enthaltenden Nebenkreislaufes auch einer erhöhten Gefahr von Kälteflüssigkeitsverlagerung ins Schmieröl während der Stillstandsphasen ausgesetzt. Der Grund dafür liegt darin, daß der Nebenkreislauf etwas zeitverzögert .zum Hauptkreislauf in Betrieb gesetzt wird. Bei der Inbetriebnahme des Hauptkreislaufes erwärmen sich dessen Kälteflüssigkeitsleitung und der Unterkühler, wodurch eine Kühlmittelverlagerung in Saugleitung und Verdichter des Nebenkreislaufes hervorgerufen werden. Als Folge hiervon können mangelhafte Schmierung sowie öl- und Flüssigkeitsschläge beim Start auftreten.These cooling devices with subcooling of the cooling liquid have not yet become established because of the high outlay required. Apart from the high cost of the compressor is exposed to the subcooler containing by-cycle also an increased danger of refrigerant liquid shift to the lubricating oil during lactation Stan d sphasen. The reason for this is that the secondary circuit is started with a slight delay to the main circuit. When the main circuit is started up, its refrigerant line and the subcooler heat up, causing a coolant shift in the suction line and compressor of the secondary circuit. As a result, poor lubrication as well as oil and liquid slugs can occur at the start.

Es ist daher Aufgabe der Erfindung, eine gattungsgemäße Kühlvorrichtung mit Unterkühlung der Kälteflüssigkeit derart zu verbessern, daß unter Beibehaltung ihrer Vorteile der zu treffende Aufwand gegenüber bekannten Vorrichtungen erheblich reduziert ist und Betriebsstörungen der genannten Art (mangelhafte Schmierung sowie öl- und Flüssigkeitsschläge beim Start) ausgeschaltet sind.It is therefore an object of the invention to improve a generic cooling device with subcooling of the refrigerant in such a way that, while maintaining its advantages, the effort to be taken is considerably reduced compared to known devices and operational malfunctions of the type mentioned (inadequate lubrication and oil and liquid strikes at start) are eliminated are.

Die Aufgabe wird erfindungsgemäß dadurch gelöst, daß als Kühlmittel für den Unterkühler ein Teil der Kälteflüssigkeit verwendet ist, und eine Auslaßöffnung des Unterkühlers für verdampftes Kühlmittel über eine zusätzliche Saugleitung mit der Saugseite eines Teiles der Zylinder des Kolbenverdichters verbunden ist.The object is achieved in that part of the refrigerant is used as the coolant for the subcooler, and an outlet opening of the subcooler for evaporated coolant is connected via an additional suction line to the suction side of part of the cylinders of the piston compressor.

Die nachstehende Beschreibung bevorzugter Ausführungsformen der Erfindung dient im Zusammenhang mit beiliegender Zeichnung der weiteren Erläuterung. Es zeigen:

  • Fig. 1 eine herkömmliche Kühlvorrichtung mit Unterkühlung der Kälteflüssigkeit;
  • Fig. 2 eine erste Ausführungsform einer Kühlvorrichtung mit verbesserter Unterkühlung der Kälteflüssigkeit;
  • Fig. 3 eine zweite Ausführungsform einer Kühlvorrichtung mit verbesserter Unterkühlung der Kälteflüssigkeit und
  • Fig. 4 eine Ventilanordnung an der Saugseite zweier Zylinder eines Kolbenverdichters.
The following description of preferred embodiments of the invention serves in conjunction with the accompanying drawings for further explanation. Show it:
  • 1 shows a conventional cooling device with subcooling of the refrigerant.
  • 2 shows a first embodiment of a cooling device with improved subcooling of the refrigerant liquid;
  • Fig. 3 shows a second embodiment of a cooling device with improved sub-cooling of the refrigerant and
  • Fig. 4, a valve assembly on the suction side of two cylinders of a K olbenverdichters.

Bei der in Fig. 1 dargestellten herkömmlichen Kühlvorrichtung saugt ein mehrere Zylinder aufweisender, motorisch angetriebener Verdichter 1 dampfförmiges Kältemittel über eine sogenannte Saugleitung 2 aus einem Verdampfer 3 bei relativ niedrigem Druck ab und komprimiert den Dampf auf einen realtiv hohen Druck, um ihn über eine sogenannte Druckgasleitung 4 in einen Verflüssiger 5 zu fördern. Im Verflüssiger 5 wird über ein Wärmeträgermedium (z. B. Luft, Wasser od. dgl.) Wärme abgeführt, so daß der unter hohem Druck stehende Dampf kondensiert. über eine Flüssigkeitsleitung 6 wird das verflüssigte (und geringfügig unterkühlte) Kältemittel zu einem Expansionsorgan 7 geleitet, dessen Aufgabe darin besteht, eine den jeweiligen Betriebsbedingungen angepaßte Menge an Kältemittelflüssigkeit in den Verdampfer 3 einzuspeisen. Das Expansionsorgan 7 ist zugleich Drosselstelle zwischen Hoch- und Niederdruck. Das in den Verdampfer 3 eingespeiste, auf niedrigem Druck gehaltene, flüssige Kältemittel verdampft durch Wärmezufuhr und wird anschließend wieder über die Saugleitung 2 - entweder trocken gesättigt oder geringfügig überhitzt - vom Verdichter 1 abgesaugt.In the conventional cooling device shown in FIG. 1, a multi-cylinder, motor-driven compressor 1 sucks vapor Refrigerant via a so-called suction line 2 from an evaporator 3 at a relatively low pressure and compresses the steam to a relatively high pressure in order to convey it via a so-called compressed gas line 4 into a condenser 5. In the condenser 5, heat is removed via a heat transfer medium (for example air, water or the like), so that the steam, which is under high pressure, condenses. The liquefied (and slightly subcooled) refrigerant is passed via a liquid line 6 to an expansion device 7, the function of which is to feed an amount of refrigerant liquid adapted to the respective operating conditions into the evaporator 3. The expansion element 7 is also a throttling point between high and low pressure. The liquid refrigerant fed into the evaporator 3 and kept at low pressure evaporates by supplying heat and is then sucked off again by the compressor 1 via the suction line 2, either dry saturated or slightly overheated.

Es läßt sich zeigen, daß die im Verdampfer 3 aufgenommene Wärmemenge ("Kälteleistung") um so größer ist, je tiefer die Temperatur des Kältemittels vor dem Expansionsorgan 7 liegt. Daher ist es bekannt, in der Flüssigkeitsleitung 6 einen sogenannten Unterkühler 8 vorzusehen, der das flüssige Kältemittel abkühlt. Dem Unterkühler 8 ist ein eigener Kühlmittelkreislauf mit Verdichter 11, Saugleitung 12, Druckleitung 14,It can be shown that the amount of heat absorbed in the evaporator 3 (“cooling capacity”) is greater the lower the temperature of the refrigerant in front of the expansion element 7. It is therefore known to provide a so-called subcooler 8 in the liquid line 6, which cools the liquid refrigerant. The subcooler 8 has its own coolant circuit with compressor 11, suction line 12, pressure line 14,

Verflüssiger 15, Flüssigkeitsleitung 16 und Expansionsorgan 17 zugeordnet, wobei der Unterkühler 8 als "Verdampfer" wirkt und das Kältemittel in der Leitung 6 kühlt. Der Kreislauf des Unterkühlers 8 enthält weiterhin ein Magnetventil 19. Der an den Verdichter 1 angeschlossene Kältemittelkreislauf wird auch als Hauptkreislauf, der an den Verdichter 11 angeschlossene Kühlmittelkreislauf als Nebenkreislauf bezeichnet. Beide Kreisläufe wirken physikalisch in der gleichen Weise.Condenser 15, liquid line 16 and expansion element 17 assigned, the subcooler 8 acting as an "evaporator" and cooling the refrigerant in the line 6. The circuit of the subcooler 8 also contains a solenoid valve 19. The refrigerant circuit connected to the compressor 1 is also referred to as the main circuit, the coolant circuit connected to the compressor 11 as a secondary circuit. Both circuits work physically in the same way.

Da der Verdampfungsvorgang im Unterkühler 8 aufgrund der relativ hohen Flüssigkeitstemperatur des Hauptkreislaufes bei einem deutlich höheren Temperaturniveau erfolgen kann als der Verdampfungsvorgang im Verdampfer 3, liegen sowohl der relative Massenstrom wie auch der Wirkungsgrad des Nebenkreislaufes höher als im Hauptkreislauf. Daraus resultiert, daß das für den Neben- oder Unterkühlungskreislauf erforderliche Fördervolumen des Verdichters 11 lediglich etwa 10 bis 25 % des Fördervolumens des Verdichters 1 betragen muß, um die gewünschte Flüssigkeitsunterkühlung zu erzielen. Dies ist Ansatzpunkt der Erfindung, deren Kernstück ein Verdichter ist, der die Funktionen der Verdichter 1 und 11 in sich vereinigt. Nachdem ein solcher einziger Verdichter, wie noch beschrieben werden wird, nur in seinem Zylinderbereich, und zwar saugseitig, unterteilt ist, jedoch einen gemeinsamen Antrieb (Kurbeltrieb) und eine gemeinsame Druckkammer besitzt, kann ohne Nachteile auf die Betriebssicherheit auch ein gemeinsamer, einziger Verflüssiger statt der Verflüssiger 5 und 15 verwendet werden.Since the evaporation process in the subcooler 8 can take place at a significantly higher temperature level than the evaporation process in the evaporator 3 due to the relatively high liquid temperature of the main circuit, both the relative mass flow and the efficiency of the secondary circuit are higher than in the main circuit. The result of this is that the delivery volume of the compressor 11 required for the secondary or subcooling circuit need only be approximately 10 to 25% of the delivery volume of the compressor 1 in order to achieve the desired liquid subcooling. This is the starting point of the invention, the core of which is a compressor which combines the functions of the compressors 1 and 11. After such a single compressor, as will be described later, is divided only in its cylinder area, specifically on the suction side, but with a common drive (crank drive) and a common pressure chamber owns, a common, single condenser can be used instead of the condensers 5 and 15 without disadvantages to the operational safety.

Die Erfindung wird nachstehend anhand zweier Ausführungsbeispiele gemäß Fig. 2 und 3 weiter erläutert.The invention is further explained below using two exemplary embodiments according to FIGS. 2 and 3.

In Fig. 2 hat der gemeinsame Kolbenverdichter 21 sechs Zylinder. Von diesen sechs Zylindern saugen lediglich einige (z. B. fünf Zylinder) dampfförmiges Kältemittel über die Saugleitung 22 aus dem Verdampfer 23 und fördern in gleicher Weise, wie zuvor anhand des Hauptkreislaufes der Fig. 1 beschrieben, über die Druckgasleitung 24 in den gemeinsamen Verflüssiger 25. Das verflüssigte Kältemittel wird nach dem Austritt aus dem Verflüssiger 25 über einen ersten Strang A der Flüssigkeitsleitung 26 direkt durch den Unterkühler 28 zum Expansionsorgan 27 geführt und von diesem geregelt in den Verdampfer 23 eingespeist sowie nach der Verdampfung vom Kolbenverdichter 21 wieder abgesaugt. Ein Teilstrom des verflüssigten Kältemittels wird über einen weiteren Strang B der Flüssigkeitsleitung 26 über ein ferngesteuertes Magnetventil 29 und durch ein weiteres Expansionsorgan 3o geregelt in den Unterkühler 28 eingespeist. Das Kältemittel dieses Teilstroms verdampft aufgrund der Wärmezufuhr durch die relativ wärmere Kältemittelflüssigkeit des Stranges A und wird dann als Saugdampf über eine zusätzliche, mit einer Auslaßöffnung 31 des Unterkühlers 28 verbundenen Saugleitung 32 abgepumpt.In Fig. 2 the common piston compressor 21 has six cylinders. Of these six cylinders, only a few (e.g. five cylinders) draw vaporous refrigerant via the suction line 22 from the evaporator 23 and, in the same way as previously described with reference to the main circuit of FIG. 1, convey via the compressed gas line 24 into the common condenser 25. After leaving the condenser 25, the liquefied refrigerant is passed directly through the subcooler 28 to the expansion element 27 via a first line A of the liquid line 26 and is fed by the latter into the evaporator 23 in a controlled manner and, after evaporation, is sucked off again by the piston compressor 21. A partial flow of the liquefied refrigerant is fed into the subcooler 28 in a controlled manner via a further line B of the liquid line 26 via a remotely controlled solenoid valve 29 and through a further expansion element 30. The refrigerant evaporates due to this partial stream of the heat supply by the relatively warmer K ältemittelflüssigkeit of the strand A and is then used as an additional suction vapor, with an outlet opening 31 of the subcooler 28 pumped connected suction line 32.

Dieses Abpumpen erfolgt erfindungsgemäß über den oder die Zylinder des Kolbenverdichters 21-, deren Saugkammern nicht mit der Leitung 22, sondern an die Leitung 32 angeschlossen sind. Von der Saugseite dieses oder dieser Zylinder wird der Saugdampf dann zu einer gemeinsamen Druckkammer des Kolbenverdichters 21 gefördert und dort mit dem Dampf des Hauptverdichterteils (aus der Saugleitung 22 stammend) vermischt. Dieser Vorgang bewirkt eine Unterkühlung der Kältemittelflüssigkeit im Unterkühler 8 mit der bereits erwähnten, hieraus resultierenden Leistungserhöhung.This pumping takes place according to the invention via the cylinder or cylinders of the piston compressor 21-, the suction chambers of which are not connected to the line 22 but to the line 32. From the suction side of this or these cylinders, the suction steam is then conveyed to a common pressure chamber of the piston compressor 21 and mixed there with the steam of the main compressor part (originating from the suction line 22). This process causes the refrigerant liquid to be subcooled in the subcooler 8 with the aforementioned increase in performance resulting therefrom.

Die Fig. 3 zeigt eine abgewandelte Anordnung, bei welcher der Unterkühler 38 als "offener Flüssigkeitssammler" ausgebildet ist, also nicht als Wärmetauscher wie der Unterkühler 28 im Falle der Fig. 2 wirkt. Einander entsprechende Teile sind in Fig. 2 und 3 mit den gleichen Bezugszeichen versehen.FIG. 3 shows a modified arrangement in which the subcooler 38 is designed as an "open liquid collector", ie does not act as a heat exchanger like the subcooler 28 in the case of FIG. 2. Corresponding parts are provided with the same reference numerals in FIGS. 2 and 3.

Das Wirkungsprinzip des "offenen" Unterkühlers 38 beruht darauf, daß ein Teil des darin befindlichen flüssigen Kältemittels vom betreffenden Teil des Verdichters 21 über die zusätzliche Saugleitung 32 dampfförmig abgesaugt wird. Die im Unterkühler 38 enthaltene Kältemittelflüssigkeit wird dadurch unterkühlt.The principle of operation of the "open" subcooler 38 is based on the fact that part of the liquid refrigerant contained therein is sucked off in vapor form by the relevant part of the compressor 21 via the additional suction line 32. The K included in the sub-cooler 38 ältemittelflüssigkeit is subcooled thereby.

Das Magnetventil 29 hat die Aufgabe, den Kältemittelfluß während der Stillstandsperioden zu unterbrechen und wird mit einer gewissen Verzögerung nach dem Start geöffnet. Ein Regler 39 in der zusätzlichen Saugleitung 32 kontrolliert den Druck und die strömende Kältemittelmenge. Zusätzlich ist im System gemäß Fig. 3 ein Druckregler 4o vorgesehen, der zur Aufrechterhaltung eines bestimmten Verflüssigungsdruckes benötigt wird.The solenoid valve 29 has the task of interrupting the refrigerant flow during the standstill periods and is opened with a certain delay after the start. A regulator 39 in the additional suction line 32 controls the pressure and the flowing amount of refrigerant. In addition, a pressure regulator 4o is provided in the system according to FIG. 3, which is required to maintain a certain condensing pressure.

Die Fig. 4 zeigt einen der Twin-Zylinderköpfe eines . Vier-, Sechs- oder Acht-Zylinderkompressors in V-, W- oder WW-Ausführung. Die anderen Zylinderköpfe des Kompressors sind in üblicher Weise ausgeführt. Die Saugkammer des in Fig. 4 dargestellten Zylinderkopfes ist durch eine Trennwand 41 in zwei Saugkammern 42 und 43 unterteilt. Die Kammer 42 steht über die zusätzliche Saugleitung 32 in der beschriebenen Weise mit dem Unterkühler in Verbindung. Die Saugkammer 43 ist ebenso wie die Saugkammern der übrigen Zylinder über die Saugleitung 22 an den Verdampfer 23 angeschlossen. Einer der Kolben 44 des Kompressors ist in Fig. 3 sichtbar. Sämtliche Zylinder der Anordnung stehen mit einer gemeinsamen Druckkammer (nicht dargestellt) in der üblichen Weise in Verbindung.4 shows one of the twin cylinder heads. Four, six or eight cylinder compressors in V, W or WW design. The other cylinder heads of the compressor are designed in the usual way. The suction chamber of the cylinder head shown in FIG. 4 is divided into two suction chambers 42 and 43 by a partition 41. The chamber 42 is connected to the subcooler via the additional suction line 32 in the manner described. The suction chamber 43, like the suction chambers of the other cylinders, is connected to the evaporator 23 via the suction line 22. One of the pistons 44 of the compressor is visible in FIG. 3. All cylinders of the arrangement are connected to a common pressure chamber (not shown) in the usual way.

In der Trennwand 41 ist eine Ventileinrichtung 45 angeordnet, die entweder (wie dargestellt) als Rückschlagventil 46 oder auch als Magnetventil ausgeführt sein kann. Durch diese Ventileinrichtung ist der Kompressor (Verdichter 21) in der Lage, mit seinen sämtlichen Zylindern auch direkt auf den Verdampfer 23 zu arbeiten, solange das Ventil 29 geschlossen bleibt. In diesem Fall wird der Unterkühler zunächst bis zu einem Saugdruck leergepumpt, der demjenigen der anderen Zylinder entspricht. Das Rückschlagventil öffnet automatisch, der betreffende Zylinder arbeitet dann parallel zum anderen Verdichterteil.A valve device 45 is arranged in the partition 41, which is designed either (as shown) as a check valve 46 or as a solenoid valve can be. By means of this valve device, the compressor (compressor 21) is able to work with all of its cylinders directly on the evaporator 23 as long as the valve 29 remains closed. In this case, the subcooler is first pumped down to a suction pressure that corresponds to that of the other cylinders. The check valve opens automatically, the cylinder in question then works in parallel with the other compressor part.

Wenn andererseits nach einer gewissen Stabilisierungsphase das Magnetventil 29 geöffnet wird, verdampft ein Teil des flüssigen Kältemittels im Unterkühler. Der Unterkühlungskreislauf arbeitet bei höherem Saugdruck (höhere Kälteleistung und Leistungszahl), so daß das Rückschlagventil im Zylinderkopf automatisch geschlossen bleibt. Der betreffende Zylinder hat dann keine Verbindung mehr zum Nachbarzylinder und bedient nur noch den Unterkühlungskreislauf.On the other hand, if the solenoid valve 29 is opened after a certain stabilization phase, some of the liquid refrigerant evaporates in the subcooler. The supercooling circuit works at a higher suction pressure (higher cooling capacity and coefficient of performance), so that the check valve in the cylinder head remains automatically closed. The cylinder in question then no longer has a connection to the neighboring cylinder and only serves the supercooling circuit.

Bei alternativer Ausbildung der Ventileinrichtung 41 als Magnetventil muß dieses beim Schließen des Magnetventils 29 bereits geöffnet werden.In an alternative embodiment of the valve device 41 as a solenoid valve, this must already be opened when the solenoid valve 29 closes.

Die beschriebene Kühlvorrichtung bietet folgende Vorteile: beim Start kann sich das System durch verzögertes öffnen des Magnetventils 29 zunächst einmal stabilisieren. Die Gefahr einer Kältemittelverlagerung aus dem Unterkühler in den Verdichter während der Anlaufphase wird durch das vorerwähnte Leerpumpen vermieden. Durch Zu- und Abschalten des Unterkühlungskreislaufes ist eine Leistungsregelung ohne Beeinträchtigung der Anwendungsgrenzen möglich. Durch die Kombination des Haupt- mit seinem Nebenkreislauf können zweite Verdichter und Verflüssiger mit Zubehör entfallen. Es ergibt sich somit auch eine vereinfachte Leitungsmontage. Ein nachträgliches Umrüsten des Verdichters auf die Ausführungsform gemäß Fig. 4 ist möglich.The cooling device described offers the following advantages: at the start, the system can initially stabilize by delayed opening of the solenoid valve 29. The risk of refrigerant transfer from the subcooler to the compressor during the Start-up phase is avoided by the aforementioned empty pumping. By switching the supercooling circuit on and off, power control is possible without affecting the application limits. By combining the main circuit with its secondary circuit, there is no need for second compressors and condensers with accessories. This also results in a simplified line assembly. A subsequent retrofitting of the compressor to the embodiment according to FIG. 4 is possible.

Claims (10)

1. Kühlvorrichtung mit einem mehrere Zylinder aufweisenden Kolbenverdichter, einem Verflüssiger, einem Expansionsorgan und einem Verdampfer, mit einer den Kolbenverdichter, den Verflüssiger, das Expansionsorgan und den Verdampfer miteinander verbindenden Leitung für eine verdampfbare Kälteflüssigkeit und mit einem in der Leitung zwischen Verflüssiger und Expansionsorgan vorgesehenem, mit einem verdampfbaren Kühlmittel arbeitenden Unterkühler für die Kälteflüssigkeit, dadurch gekennzeichnet , daß als Kühlmittel für den Unterkühler (28,38) ein Teil der Kälteflüssigkeit verwendet ist, und die Auslaßöffnung (31) des Unterkühlers für verdampftes Kühlmittel über eine zusätzliche Saugleitung (32) mit der Saugseite eines Teiles der Zylinder des Kolbenverdichters (21) verbunden ist.1. Cooling device with a piston compressor having a plurality of cylinders, a condenser, an expansion element and an evaporator, with a line connecting the piston compressor, the condenser, the expansion element and the evaporator for an evaporable refrigerant liquid and with a line provided in the line between the condenser and the expansion element , with a vaporizable coolant subcooler for the refrigerant, characterized in that part of the refrigerant is used as the coolant for the subcooler (28, 38), and the outlet opening (31) of the subcooler for vaporized coolant via an additional suction line (32) is connected to the suction side of a part of the cylinder of the piston compressor (21). 2. Kühlvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß ein hinter dem Verflüssiger (25) abgezweigter Teil der Kälteflüssigkeit durch ein zusätzliches Expansionsorgan (3o), anschließend durch den als Wärmetauscher ausgebildeten Unterkühler (28) und hierauf zu der zusätzlichen Saugleitung (32) geführt ist.2. Cooling device according to claim 1, characterized in that a branched off downstream of the condenser (25) part of the K älteflüssigkeit by an additional expansion element (3o), then formed by a heat exchanger Subcooler (28) and then to the additional suction line (32). 3. Kühlvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Unterkühler (38) als offener Flüssigkeitssammler ausgebildet und mit der zusätzlichen Saugleitung (32) verbunden ist.3. Cooling device according to claim 1, characterized in that the subcooler (38) is designed as an open liquid collector and is connected to the additional suction line (32). 4. Kühlvorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß lediglich die Saugseite (Saugkammer 42) eines einzigen Zylinders des Kolbenverdichters (21) an die zusätzliche Saugleitung (32) angeschlossen ist.4. Cooling device according to one of claims 1 to 3, characterized in that only the suction side (suction chamber 42) of a single cylinder of the piston compressor (21) is connected to the additional suction line (32). 5. Kühlvorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß eine mit der zusätzlichen Saugleitung (32) verbundene Saugkammer (42) wenigstens eines Zylinders des Kolbenverdichters (21) durch eine Trennwand (41) von den Saugkammern (43) der übrigen Zylinder abgetrennt und in der Trennwand eine Ventileinrichtung (45) angeordnet ist.5. Cooling device according to one of claims 1 to 4, characterized in that a suction chamber (42) connected to the additional suction line (32) at least one cylinder of the piston compressor (21) through a partition (41) from the suction chambers (43) of the rest Separated cylinder and a valve device (45) is arranged in the partition. 6. Kühlvorrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die Ventileinrichtung (45) ein Rückschlagventil (46) ist, welches schließt, sobald der Druck in der mit der zusätzlichen Saugleitung (32) verbundenen Saugkammer (42) höher als in den übrigen Saugkammern (43) ist.6. Cooling device according to claim 5, characterized in that the valve device (45) is a check valve (46) which closes as soon as the pressure in the suction chamber (42) connected to the additional suction line (32) is higher than in the other suction chambers ( 43) is. 7. Kühlvorrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die Ventileinrichtung (45) ein Magnetventil ist.7. Cooling device according to claim 5, characterized in that the valve device (45) is a solenoid valve. 8. Kühlvorrichtung nach einem der Ansprüche 2 und 4 bis 7, dadurch gekennzeichnet, daß dem zusätzlichen Expansionsorgan (3o) ein Magnetventil (29) vorgeschaltet ist.8. Cooling device according to one of claims 2 and 4 to 7, characterized in that the additional expansion member (3o) is connected upstream of a solenoid valve (29). 9. Kühlvorrichtung nach einem der Ansprüche 3 bis 7, dadurch gekennzeichnet, daß in der zusätzlichen Saugleitung (32) ein Magnetventil (29) angeordnet ist.9. Cooling device according to one of claims 3 to 7, characterized in that a solenoid valve (29) is arranged in the additional suction line (32). 10. Kühlvorrichtung nach einem der Ansprüche 3 bis 7 und 9, dadurch gekennzeichnet, daß zwischen dem Verflüssiger (25) und dem Unterkühler (38) ein Druckregler (4o) vorgesehen ist.1 0 . Cooling device according to one of claims 3 to 7 and 9, characterized in that a pressure regulator (4o) is provided between the condenser (25) and the subcooler (38).
EP85113773A 1984-11-03 1985-10-29 Cooling device Expired EP0180904B1 (en)

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AT85113773T ATE46026T1 (en) 1984-11-03 1985-10-29 COOLING DEVICE.

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DE19843440253 DE3440253A1 (en) 1984-11-03 1984-11-03 COOLING DEVICE

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2092424A1 (en) * 1992-09-16 1996-11-16 Ornaque Carlos Gutierrez Mixed-unit safety cooling system
EP0898128A2 (en) * 1997-08-22 1999-02-24 Carrier Corporation Variariable refrigerant, intrastage compression heat pump
EP0837291A3 (en) * 1996-08-22 2000-10-04 Denso Corporation Vapor compression type refrigerating system
EP1139039A1 (en) * 2000-03-27 2001-10-04 Carrier Corporation Economizer circuit enhancement
EP1498667A2 (en) * 2003-07-18 2005-01-19 Star Refrigeration Ltd. Improved transcritical refrigeration cycle
WO2005008148A1 (en) * 2003-07-14 2005-01-27 Carrier Corporation Refrigerant compression system with selective subcooling
WO2006015741A1 (en) * 2004-08-09 2006-02-16 Linde Kältetechnik Gmbh Refrigeration circuit and method for operating a refrigeration circuit
DE102005009173A1 (en) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh refrigeration plant
US8113008B2 (en) 2004-08-09 2012-02-14 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4702086A (en) * 1986-06-11 1987-10-27 Turbo Coils Inc. Refrigeration system with hot gas pre-cooler
US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
DE19826291A1 (en) * 1998-06-12 1999-12-16 Linde Ag Process for operating a pump to convey boiling refrigerants or refrigerants
US10253766B2 (en) 2015-05-13 2019-04-09 Carrier Corporation Economized reciprocating compressor

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH101888A (en) * 1922-06-26 1923-10-16 Sulzer Ag Compression refrigeration machine.
US2320097A (en) * 1941-08-20 1943-05-25 Servel Inc Refrigeration
FR2287666A1 (en) * 1974-10-11 1976-05-07 Primore Sales Inc AUTOMATIC VALVE EQUIPPED WITH A REFRIGERANT COMPRESSOR
FR2304041A1 (en) * 1975-03-11 1976-10-08 Kvaerner Brug Kjoleavdelning Gas liquefaction machine for refrigeration plant - has compact intercooler which encloses liquefied gas separator for shortening pipework
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
US4230470A (en) * 1977-01-21 1980-10-28 Hitachi, Ltd. Air conditioning system
FR2503841A1 (en) * 1981-04-09 1982-10-15 Guillemin Georges Heat extraction pump for heating buildings - has reservoir to compressor connection allowing lower exit temperatures from condenser
DE3301304A1 (en) * 1982-02-26 1983-09-15 Hitachi, Ltd., Tokyo COOLING SYSTEM WITH A COMPRESSOR IN SPIRAL DESIGN

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH101888A (en) * 1922-06-26 1923-10-16 Sulzer Ag Compression refrigeration machine.
US2320097A (en) * 1941-08-20 1943-05-25 Servel Inc Refrigeration
FR2287666A1 (en) * 1974-10-11 1976-05-07 Primore Sales Inc AUTOMATIC VALVE EQUIPPED WITH A REFRIGERANT COMPRESSOR
FR2304041A1 (en) * 1975-03-11 1976-10-08 Kvaerner Brug Kjoleavdelning Gas liquefaction machine for refrigeration plant - has compact intercooler which encloses liquefied gas separator for shortening pipework
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
US4230470A (en) * 1977-01-21 1980-10-28 Hitachi, Ltd. Air conditioning system
FR2503841A1 (en) * 1981-04-09 1982-10-15 Guillemin Georges Heat extraction pump for heating buildings - has reservoir to compressor connection allowing lower exit temperatures from condenser
DE3301304A1 (en) * 1982-02-26 1983-09-15 Hitachi, Ltd., Tokyo COOLING SYSTEM WITH A COMPRESSOR IN SPIRAL DESIGN

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2092424A1 (en) * 1992-09-16 1996-11-16 Ornaque Carlos Gutierrez Mixed-unit safety cooling system
EP0837291A3 (en) * 1996-08-22 2000-10-04 Denso Corporation Vapor compression type refrigerating system
EP0898128A2 (en) * 1997-08-22 1999-02-24 Carrier Corporation Variariable refrigerant, intrastage compression heat pump
EP0898128A3 (en) * 1997-08-22 2001-09-05 Carrier Corporation Variariable refrigerant, intrastage compression heat pump
EP1139039A1 (en) * 2000-03-27 2001-10-04 Carrier Corporation Economizer circuit enhancement
WO2005008148A1 (en) * 2003-07-14 2005-01-27 Carrier Corporation Refrigerant compression system with selective subcooling
EP1498667A3 (en) * 2003-07-18 2006-05-17 Star Refrigeration Ltd. Improved transcritical refrigeration cycle
EP1498667A2 (en) * 2003-07-18 2005-01-19 Star Refrigeration Ltd. Improved transcritical refrigeration cycle
US7845190B2 (en) 2003-07-18 2010-12-07 Star Refrigeration Limited Transcritical refrigeration cycle
WO2006015741A1 (en) * 2004-08-09 2006-02-16 Linde Kältetechnik Gmbh Refrigeration circuit and method for operating a refrigeration circuit
US8113008B2 (en) 2004-08-09 2012-02-14 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US8844303B2 (en) 2004-08-09 2014-09-30 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US9476614B2 (en) 2004-08-09 2016-10-25 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US9494345B2 (en) 2004-08-09 2016-11-15 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
DE102005009173A1 (en) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh refrigeration plant
WO2006087075A1 (en) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Refrigeration plant
US7451617B2 (en) 2005-02-17 2008-11-18 Bitzer Kuhlmaschinenbau Gmbh Refrigeration system

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ATE46026T1 (en) 1989-09-15
DE3440253A1 (en) 1986-05-15
EP0180904B1 (en) 1989-08-30
DE3572721D1 (en) 1989-10-05
EP0180904A3 (en) 1986-10-08

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