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EP2487437B1 - Heat pump device - Google Patents

Heat pump device Download PDF

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Publication number
EP2487437B1
EP2487437B1 EP11001131.9A EP11001131A EP2487437B1 EP 2487437 B1 EP2487437 B1 EP 2487437B1 EP 11001131 A EP11001131 A EP 11001131A EP 2487437 B1 EP2487437 B1 EP 2487437B1
Authority
EP
European Patent Office
Prior art keywords
compressor
oil
heat pump
valve
operated
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.)
Active
Application number
EP11001131.9A
Other languages
German (de)
French (fr)
Other versions
EP2487437A1 (en
Inventor
Björn Holle
Steffen Smollich
Hartmut Kirchhoff
Michael Schaumlöffel
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.)
Stiebel Eltron GmbH and Co KG
Original Assignee
Stiebel Eltron GmbH and Co KG
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Publication date
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Priority to EP11001131.9A priority Critical patent/EP2487437B1/en
Publication of EP2487437A1 publication Critical patent/EP2487437A1/en
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Publication of EP2487437B1 publication Critical patent/EP2487437B1/en
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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25B2400/072—Intercoolers therefor
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle

Definitions

  • the present invention relates to a heat pump device.
  • chiller For some time, devices such as air conditioners, refrigerators and the like are known, which have a so-called chiller.
  • a chiller is used to generate refrigeration by implementing a thermodynamic cycle that absorbs heat below ambient temperature and releases it at a higher temperature.
  • heat pumps which absorbs thermal energy from a reservoir with lower temperature such as the environment, and transfers together with the drive energy as useful heat to a heated system with higher temperature, such as a space heater with the use of technical work.
  • chillers and heat pumps basically use the same principle, namely that the fluids used have different boiling or condensation temperatures at different pressures and that these fluids cool during the expansion (throttling).
  • heat pumps are usually operated with fluids that evaporate at low pressure with heat and after compression on condense a higher pressure with heat release again. The pressures are chosen so that the temperatures of the phase change have sufficient for the heat transfer distance to the temperatures of the heat source or heat sink.
  • the EP 2 221 559 A discloses a heat pump according to the preamble of claim 1.
  • the object of the present invention is to provide an improved heat pump device.
  • a heat pump apparatus having a refrigerant circuit, the refrigerant circuit having a first compressor and a second compressor connected in series through a line segment such that the compression is a two-stage compression if the first compressor and the second compressor are operated become.
  • the refrigerant circuit further includes a condenser, an evaporator, and an expansion valve disposed upstream of the evaporator in the flow direction.
  • the refrigerant circuit also includes a first oil separator disposed downstream of the first compressor and connected to the first compressor via a first oil line for returning separated oil to the first compressor and a second oil separator downstream of the second compressor is disposed and connected to the second compressor via a second oil line to return separated oil to the second compressor.
  • At least the first compressor or the second compressor can be operated independently.
  • the non-powered first compressor or the non-powered second compressor may be bypassed by a first bypass line or a second bypass line.
  • the second compressor is preceded by a shut-off valve in the flow direction, wherein the first and second bypass line respectively open into the line segment between the first oil separator and the shut-off valve.
  • this heat pump device with refrigeration circuit can be operated by means of a one-stage compression, if only one of the two compressors operated and the other is bridged, or by means a two-stage compression, if both compressors are operated together.
  • the shut-off valve is activated and thus opened, so that the second compressor can suck in the fluid during operation. If the second compressor is not operated, the shut-off valve remains closed, so that no fluid from the first compressor can be pressed into the second compressor.
  • the present invention relates to a townpumpenvonichtung with refrigeration circuit, preferably with a Kompressionslalte réelle.
  • a check valve downstream of the second compressor in the flow direction In this way it can be ensured that no fluid can reach the second compressor via the second environmental line.
  • the second bypass line of the second compressor is arranged such that the first oil separator and the second oil separator are connected in series, if the first compressor is operated.
  • the second oil separator becomes operative in the operation of one-stage compression, i. if only the first or the second compressor are operated, always flows through. As a result, no fluid can verlagem on the second bypass line in the second compressor.
  • the cooling circuit of the heat pump device has an injection line, which is arranged in the flow direction downstream of the shut-off valve. In this way, no fluid can accumulate in the economizer.
  • the refrigerant circuit of the heat pump device has an oil balance valve disposed between the first oil passage and the second oil passage.
  • the oil balance valve is open if the first compressor is operating.
  • the components economiser and second compressor of the refrigerator are provided at the suction pressure level of the first compressor.
  • opening the Oil balance valve ensures that an oil balance between the first and second compressor during operation of the first compressor can take place.
  • the first bypass line and / or the second bypass line to a check valve, which is provided obliquely so that condensed fluid can flow back into the perfused area.
  • the check valve is arranged obliquely, i. inclined to the horizontal, in order to ensure the backflow of the condensed fluid in the area flowed through. As a result, jamming or accumulation of condensed fluid can be avoided before the check valve.
  • a heat pump device with refrigeration circuit is the European Patent EP 2 088 388 A1 called.
  • This relates to a heat pump system with a condenser (also called condenser), an expansion valve (also called throttle), an evaporator and a compressor (also called compressor).
  • This heat pump system has two compressors C1 and C2, which can be operated either together in the so-called two-compressor operation (two-stage compression) or it can only one of the two compressors C1 or C2 in the so-called.
  • Einverêtr plante one-stage compression
  • Fig. 1 shows a block diagram of a heat pump device according to the prior art.
  • the refrigerant circuit of the heat pump device has a Refrigeration cycle with a condenser 2, an evaporator 3, an expansion valve 19, which is arranged upstream of the evaporator 3 in the flow direction and a compressor C1 and a second compressor C2, the first compressor C1 and the second compressor C2 are through a line segment 100 in Connected series.
  • a first oil separator 25 is disposed behind the first compressor C1 and connected to the first compressor C1 via a first oil pipe 101 to return separated oil to the first compressor C1.
  • a second oil separator 26 is disposed and connected to the second compressor C2 via a second oil passage 102 to return separated oil to the second compressor C2.
  • the first oil line 101 and the second oil line 102 are connected to each other via an oil compensation valve 24.
  • a collector 11 and a separator 20 is advantageously provided.
  • the refrigeration circuit can be operated in one-stage compression or in two-stage compression.
  • the first compressor C1 or the second compressor C2 can be operated independently of each other.
  • These bypass lines 122, 123 each have a check valve.
  • Fig. 2 shows a block diagram of a heat pump device according to the invention.
  • This heat pump device is based essentially on the heat pump device according to Fig. 1
  • a shut-off valve 27 is provided in the supply line 100 between the output of the first compressor C1 and the input of the second compressor C2, which is preferably designed as a servo-shut-off valve 27.
  • This Shut-off valve 27 is arranged in the supply line 100, that the shut-off valve 27 is bridged together with the second compressor C2 through the bypass line 123.
  • the second compressor C2 can be bypassed by closing the shut-off valve 27 for the operation of the refrigerator in the one-stage compression by means of the first compressor C1, without a part of the flowing out of the first compressor C1 fluid in the second compressor C2 is pressed.
  • the second oil separator 26 in contrast to the heat pump device according to the prior art, arranged so that the second bypass line 123 between the outlet of the second compressor C2 and the inlet of the second oil separator 26 opens. In this way, the second oil separator 26 is always traversed by the fluid both in the two-stage compression as well as in both modes of one-stage compression.
  • a check valve 28 is further provided between the junction of the second bypass line 123 and the output of the second compressor C2, to prevent backflow of fluid into the second compressor C2, if in the one-stage compression of the second compressor C2 is not operated ,
  • the oil balance valve 24 between the first oil pipe 101 and the second oil pipe 102 is opened in the one-stage compression by the first compressor C ⁇ b> 1 to allow oil equalization between the first compressor C ⁇ b> 1 and the second compressor C ⁇ b> 2. Further, in one embodiment, in the operation of the one-stage compression by the first compressor C1, by opening the oil balance valve 24, the bypass passage 124 having the compressor C2 and the injection passage 109 are brought to the suction pressure level via the intercooler 6 (economizer).
  • a flow 0 and a return 1 are connected to the capacitor 2. It is also advantageous to use a 4/2-way valve 4, which a first connection 4a, which is connected to a hot gas line 104. A second connection 4b is connected to an exit line 104b of the evaporator. A third connection 4c is connected to a connection line 104c, and a fourth connection 4d of the 412-way valve 4 is connected to a connection line 104d. Furthermore, a separator-collector 5 is provided. A Ableylange 7, to which a line segment 107 is connected, is advantageously mounted in front of the intercooler 6. Furthermore, an expansion valve 9, a filter drier 10 and a sight glass 12 are provided.
  • the flow direction check valves 15, 16, 17, 18 are mounted at different locations, which are mainly used for switching between heating and defrosting. Furthermore, an expansion valve 19 is provided, with which the state of the refrigerant is controlled in the evaporator.
  • the check valves 22 and 23 are provided in the bypass lines 106 and 110 for switching the flow direction.
  • a pressure equalization line 108 is connected behind the shut-off valve 27.
  • a line segment 103 is provided. To the line segment 103, the bypass lines 106 and 110 are connected.
  • the suction line 105 is advantageously performed by the separator-collector 5 to the compressor C1. Furthermore, the lines 108, 112, 115, 116, 117, 119, 121 and 122 are provided.
  • the invention relates to the idea that in the heat pump device of the European Patent EP 2 088 388 A1
  • problems may arise with regard to a refrigerant displacement.
  • the refrigerant ie the fluid
  • the heat pump system of EP 2 088 388 A1 run only in the compressor operation with the second compressor C2.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

Die vorliegende Erfindung betrifft eine Wärmepumpenvorrichtung.The present invention relates to a heat pump device.

Seit geraumer Zeit sind Vorrichtungen wie beispielsweise Klimaanlagen, Kühlschränke und dergleichen bekannt, die eine so genannte Kältemaschine aufweisen. Eine Kältemaschine dient der Kälteerzeugung, indem sie einen thermodynamischen Kreisprozess umsetzt, bei dem Wärme unterhalb der Umgebungstemperatur aufgenommen und bei höherer Temperatur abgegeben wird.For some time, devices such as air conditioners, refrigerators and the like are known, which have a so-called chiller. A chiller is used to generate refrigeration by implementing a thermodynamic cycle that absorbs heat below ambient temperature and releases it at a higher temperature.

In vergleichbarer Weise sind Wärmepumpen bekannt, die unter Aufwendung von technischer Arbeit thermische Energie aus einem Reservoir mit niedrigerer Temperatur wie beispielsweise der Umgebung aufnimmt und zusammen mit der Antriebsenergie als Nutzwärme auf ein zu beheizendes System mit höherer Temperatur wie beispielsweise eine Raumheizung überträgt.Similarly, heat pumps are known, which absorbs thermal energy from a reservoir with lower temperature such as the environment, and transfers together with the drive energy as useful heat to a heated system with higher temperature, such as a space heater with the use of technical work.

Sowohl Kältemaschinen als auch Wärmepumpen verwenden dabei grundsätzlich das gleiche Prinzip, nämlich dass die verwendeten Fluide bei unterschiedlichen Drücken unterschiedliche Siede- bzw. Kondensationstemperaturen aufweisen und dass sich diese Fluide bei der Entspannung (Drosselung) abkühlen. Beispielsweise werden Wärmepumpen in der Regel mit Fluiden betrieben, die bei niedrigem Druck unter Wärmezufuhr verdampfen und nach der Verdichtung auf einen höheren Druck unter Wärmeabgabe wieder kondensieren. Die Drücke werden so gewählt, dass die Temperaturen des Phasenwechsels einen für die Wärmeübertragung ausreichenden Abstand zu den Temperaturen der Wärmequelle bzw. Wärmesenke haben.Both chillers and heat pumps basically use the same principle, namely that the fluids used have different boiling or condensation temperatures at different pressures and that these fluids cool during the expansion (throttling). For example, heat pumps are usually operated with fluids that evaporate at low pressure with heat and after compression on condense a higher pressure with heat release again. The pressures are chosen so that the temperatures of the phase change have sufficient for the heat transfer distance to the temperatures of the heat source or heat sink.

Die EP 2 221 559 A offenbart eine Wärmepumpe gemäß dem Oberbegriff des Anspruchs 1.The EP 2 221 559 A discloses a heat pump according to the preamble of claim 1.

Aufgabe der vorliegenden Erfindung ist es, eine verbesserte Wärmepumpenvorrichtung vorzusehen.The object of the present invention is to provide an improved heat pump device.

Erfindungsgemäß wird die Aufgabe durch eine Wärmepumpenvorrichtung mit den Merkmalen nach Anspruch 1 gelöst. Vorteilhafte Weiterbildungen sind in den Unteransprüchen beschrieben.According to the invention the object is achieved by a heat pump device with the features of claim 1. Advantageous developments are described in the subclaims.

Somit wird eine Wärmepumpenvorrichtung mit einem Kältekreis vorgesehen, der Kältekreis mit einem ersten Kompressor und einem zweiten Kompressor, die durch ein Leitungssegment derart in Reihe verbunden sind, dass die Kompression eine Zwei-Stufen-Kompression ist, falls der erste Kompressor und der zweite Kompressor betrieben werden. Der Kältekreis weist ferner einen Kondensator, einen Verdampfer und ein Expansionsventil auf, das in der Strömungsrichtung vor dem Verdampfer angeordnet ist. Der Kältekreis weist auch einen ersten Ölabscheider, der in Strömungsrichtung hinter dem ersten Kompressor angeordnet und mit dem ersten Kompressor über eine erste Ölleitung verbunden ist, um abgeschiedenes Öl zu dem ersten Kompressor zurückzuführen, und einen zweiten Ölabscheider auf, der in Strömungsrichtung hinter dem zweiten Kompressor angeordnet und mit dem zweiten Kompressor über eine zweite Ölleitung verbunden ist, um abgeschiedenes Öl zu dem zweiten Kompressor zurückzuführen. Wenigstens der erste Kompressor oder der zweite Kompressor kann unabhängig betrieben werden. Der nicht betriebene erste Kompressor oder der nicht betriebene zweite Kompressor kann durch eine erste Umgehungsleitung oder eine zweite Umgehungsleitung überbrückt werden. Dem zweiten Kompressor ist ein Absperrventil in Strömungsrichtung vorgeschaltet, wobei die erste und zweite Umgehungsleitung jeweils zwischen dem ersten Ölabscheider und dem Absperrventil in das Leitungssegment münden.Thus, there is provided a heat pump apparatus having a refrigerant circuit, the refrigerant circuit having a first compressor and a second compressor connected in series through a line segment such that the compression is a two-stage compression if the first compressor and the second compressor are operated become. The refrigerant circuit further includes a condenser, an evaporator, and an expansion valve disposed upstream of the evaporator in the flow direction. The refrigerant circuit also includes a first oil separator disposed downstream of the first compressor and connected to the first compressor via a first oil line for returning separated oil to the first compressor and a second oil separator downstream of the second compressor is disposed and connected to the second compressor via a second oil line to return separated oil to the second compressor. At least the first compressor or the second compressor can be operated independently. The non-powered first compressor or the non-powered second compressor may be bypassed by a first bypass line or a second bypass line. The second compressor is preceded by a shut-off valve in the flow direction, wherein the first and second bypass line respectively open into the line segment between the first oil separator and the shut-off valve.

Vorteilhaft ist bei dieser Wärmepumpenvorrichtung mit Kältekreis, dass diese mittels einer Ein-Stufen-Kompression betrieben werden kann, falls lediglich einer der beiden Kompressoren betrieben und der andere überbrückt wird, oder mittels einer Zwei-Stufen-Kompression, falls beide Kompressoren gemeinsam betrieben werden. Dabei wird in dem Fall, dass der zweite Kompressor betrieben wird, das Absperrventil angesteuert und damit geöffnet, so dass der zweite Kompressor im Betrieb Fluid ansaugen kann. Wird der zweite Kompressor nicht betrieben, bleibt das Absperrventil geschlossen, sodass kein Fluid von dem ersten Kompressor in den zweiten Kompressor gedrückt werden kann.It is advantageous in this heat pump device with refrigeration circuit that it can be operated by means of a one-stage compression, if only one of the two compressors operated and the other is bridged, or by means a two-stage compression, if both compressors are operated together. In this case, in the event that the second compressor is operated, the shut-off valve is activated and thus opened, so that the second compressor can suck in the fluid during operation. If the second compressor is not operated, the shut-off valve remains closed, so that no fluid from the first compressor can be pressed into the second compressor.

Dabei betrifft die vorliegende Erfindung eine Wärmepumpenvonichtung mit Kältekreis, vorzugsweise mit einem Kompressionskältekreis.In this case, the present invention relates to a Wärmepumpenvonichtung with refrigeration circuit, preferably with a Kompressionskältekreis.

Gemäß einem Aspekt der Erfindung ist dem zweiten Kompressor ein Rückschlagventil in Strömungsrichtung nachgeschaltet. Hierdurch kann sichergestellt werden, dass kein Fluid über die zweite Umgebungsleitung in den zweiten Kompressor gelangen kann.According to one aspect of the invention, a check valve downstream of the second compressor in the flow direction. In this way it can be ensured that no fluid can reach the second compressor via the second environmental line.

Gemäß einem weiteren Aspekt der Erfindung ist die zweite Umgehungsleitung des zweiten Kompressors derart angeordnet, dass der erste Ölabscheider und der zweite Ölabscheider in Reihe geschaltet sind, falls der erste Kompressor betrieben wird. Auf diese Weise wird der zweite Ölabscheider im Betrieb der Ein-Stufen-Kompression, d.h. falls lediglich der erste oder der zweite Kompressor betrieben werden, immer durchströmt. Hierdurch kann sich kein Fluid über die zweite Umgehungsleitung in den zweiten Kompressor verlagem.According to another aspect of the invention, the second bypass line of the second compressor is arranged such that the first oil separator and the second oil separator are connected in series, if the first compressor is operated. In this way, the second oil separator becomes operative in the operation of one-stage compression, i. if only the first or the second compressor are operated, always flows through. As a result, no fluid can verlagem on the second bypass line in the second compressor.

Gemäß einem Aspekt der Erfindung weist der KälteKreis der Wärmepumpenvorrichtung eine Einspritzleitung auf, die in Strömungsrichtung nach dem Absperrventil angeordnet ist. Auf diese Weise kann sich kein Fluid im Economiser ansammeln.According to one aspect of the invention, the cooling circuit of the heat pump device has an injection line, which is arranged in the flow direction downstream of the shut-off valve. In this way, no fluid can accumulate in the economizer.

Gemäß einem weiteren Aspekt der Erfindung weist der Kältekreis der Wärmepumpenvorrichtung ein Ölausgleichsventil auf, welches zwischen der ersten Ölleitung und der zweiten Ölleitung angeordnet ist. Das Ölausgleichsventil ist geöffnet, falls der erste Kompressor betrieben wird. Somit sind die Komponenten Economiser und zweiter Kompressor der Kältemaschine auf dem Saugdruckniveau des ersten Kompressors vorgesehen. Ferner wird durch das Öffnen des Ölausgleichsventils sichergestellt, dass ein Ölausgleich zwischen dem ersten und zweiten Kompressor während des Betriebes des ersten Kompressors erfolgen kann.According to another aspect of the invention, the refrigerant circuit of the heat pump device has an oil balance valve disposed between the first oil passage and the second oil passage. The oil balance valve is open if the first compressor is operating. Thus, the components economiser and second compressor of the refrigerator are provided at the suction pressure level of the first compressor. Furthermore, by opening the Oil balance valve ensures that an oil balance between the first and second compressor during operation of the first compressor can take place.

Gemäß einem Aspekt der Erfindung weist die erste Umgehungsleitung und bzw. oder die zweite Umgehungsleitung ein Rückschlagventil auf, welches derart schräg vorgesehen ist, dass auskondensiertes Fluid wieder in den durchströmten Bereich zurückfließen kann. Dabei ist das Rückschlagventil schräg angeordnet, d.h. zur Horizontalen geneigt, um das Zurückfließen des auskondensierten Fluids in den durchströmten Bereich zu gewährleisten. Hierdurch kann ein Stauen oder Ansammeln von auskondensiertem Fluid vor dem Rückschlagventil vermieden werden.According to one aspect of the invention, the first bypass line and / or the second bypass line to a check valve, which is provided obliquely so that condensed fluid can flow back into the perfused area. In this case, the check valve is arranged obliquely, i. inclined to the horizontal, in order to ensure the backflow of the condensed fluid in the area flowed through. As a result, jamming or accumulation of condensed fluid can be avoided before the check valve.

Als Beispiel einer Wärmepumpenvorrichtung mit Kältekreis sei die Europäische Patentschrift EP 2 088 388 A1 genannt. Diese betrifft ein Wärmepumpensystem mit einem Kondensator (auch Verflüssiger genannt), einem Expansionsventil (auch Drossel genannt), einem Verdampfer und einem Kompressor (auch Verdichter genannt). Dieses Wärmepumpensystem weist dabei zwei Kompressoren C1 und C2 auf, die entweder gemeinsam im sog. Zweiverdichterbetrieb (Zwei-Stufen-Kompression) betrieben werden können oder es kann lediglich einer der beiden Kompressoren C1 oder C2 im sog. Einverdichterbetrieb (Ein-Stufen-Kompression) betrieben werden.As an example of a heat pump device with refrigeration circuit is the European Patent EP 2 088 388 A1 called. This relates to a heat pump system with a condenser (also called condenser), an expansion valve (also called throttle), an evaporator and a compressor (also called compressor). This heat pump system has two compressors C1 and C2, which can be operated either together in the so-called two-compressor operation (two-stage compression) or it can only one of the two compressors C1 or C2 in the so-called. Einverdichterbetrieb (one-stage compression) operate.

Ausführungsbeispiele und Vorteile der Erfindung werden nachstehend unter Bezugnahme auf folgende Figuren näher erläutert:

Fig. 1
zeigt ein Blockschaltbild einer Wärmepumpenvorrichtung gemäß dem Stand der Technik, und
Fig. 2
zeigt ein Blockschaltbild einer erfindungsgemäßen Wärmepumpenvorrichtung.
Exemplary embodiments and advantages of the invention are explained in more detail below with reference to the following figures:
Fig. 1
shows a block diagram of a heat pump device according to the prior art, and
Fig. 2
shows a block diagram of a heat pump device according to the invention.

Fig. 1 zeigt ein Blockschaltbild einer Wärmepumpenvorrichtung gemäß dem Stand der Technik. Der Kältekreis der Wärmepumpenvorrichtung weist einen Kältekreislauf mit einem Kondensator 2, einem Verdampfer 3, einem Expansionsventil 19, das in der Strömungsrichtung vor dem Verdampfer 3 angeordnet ist und einem Kompressor C1 und einem zweiten Kompressor C2 auf, Der erste Kompressor C1 und der zweite Kompressor C2 sind durch ein Leitungssegment 100 in Reihe verbunden. Fig. 1 shows a block diagram of a heat pump device according to the prior art. The refrigerant circuit of the heat pump device has a Refrigeration cycle with a condenser 2, an evaporator 3, an expansion valve 19, which is arranged upstream of the evaporator 3 in the flow direction and a compressor C1 and a second compressor C2, the first compressor C1 and the second compressor C2 are through a line segment 100 in Connected series.

In der Strömungsrichtung des Fluids ist hinter dem ersten Kompressor C1 ein erster Ölabscheider 25 angeordnet und mit dem ersten Kompressor C1 über eine erste Ölleitung 101 verbunden, um abgeschiedenes Öl zu dem ersten Kompressor C1 zurückzuführen. Ebenfalls ist in der Strömungsrichtung hinter dem zweiten Kompressor C2 ein zweiter Ölabscheider 26 angeordnet und mit dem zweiten Kompressor C2 über eine zweite Ölleitung 102 verbunden, um abgeschiedenes Öl zu dem zweiten Kompressor C2 zurückzuführen. Die erste Ölleitung 101 und die zweite Ölleitung 102 sind Ober ein Ölausgleichsventil 24 miteinander verbunden.In the flow direction of the fluid, a first oil separator 25 is disposed behind the first compressor C1 and connected to the first compressor C1 via a first oil pipe 101 to return separated oil to the first compressor C1. Also, in the flow direction behind the second compressor C2, a second oil separator 26 is disposed and connected to the second compressor C2 via a second oil passage 102 to return separated oil to the second compressor C2. The first oil line 101 and the second oil line 102 are connected to each other via an oil compensation valve 24.

Weiterhin ist vorteilhaft ein Sammler 11 und ein Abscheider 20 vorgesehen.Furthermore, a collector 11 and a separator 20 is advantageously provided.

Der Kältekreis kann in einer Ein-Stufen-Kompression oder in einer Zwei-Stufen-Kompression betrieben werden. Hierzu werden entweder die beiden Kompressoren C1 und C2 hintereinander vom Fluid durchströmt oder es wird lediglich einer der beiden Kompressoren C1 oder C2 durchströmt und der andere Kompressor C1 oder C2 wird mittels einer entsprechenden ersten Umgehungsleitung 122 bzw. zweiten Umgehungsleitung 123 überbrückt. Auf diese Weise können der erste Kompressor C1 oder der zweite Kompressor C2 unabhängig voneinander betrieben werden. Diese Umgehungsleitungen 122, 123 weisen jeweils ein Rückschlagventil auf.The refrigeration circuit can be operated in one-stage compression or in two-stage compression. For this purpose, either the two compressors C1 and C2 successively flowed through by the fluid or it is only one of the two compressors C1 or C2 flows through and the other compressor C1 or C2 is bridged by means of a corresponding first bypass line 122 and second bypass line 123. In this way, the first compressor C1 or the second compressor C2 can be operated independently of each other. These bypass lines 122, 123 each have a check valve.

Fig. 2 zeigt ein Blockschaltbild einer erfindungsgemäßen Wärmepumpenvorrichtung. Diese Wärmepumpenvorrichtung basiert im wesentlichen auf der Wärmepumpenvorrichtung gemäß Fig. 1. Erfindungsgemäß ist in dem Blockschaltbild der Fig. 2 ein Absperrventil 27 in der Zuleitung 100 zwischen dem Ausgang des ersten Kompressors C1 und dem Eingang des zweiten Kompressors C2 vorgesehen, welches bevorzugt als Servo-Absperrventil 27 ausgebildet ist. Dieses Absperrventil 27 ist so in der Zuleitung 100 angeordnet, dass das Absperrventil 27 gemeinsam mit dem zweiten Kompressor C2 durch die Umgehungsleitung 123 überbrückt wird. Auf diese Weise kann der zweite Kompressor C2 durch das Schließen des Absperrventils 27 für den Betrieb der Kältemaschine in der Ein-Stufen-Kompression mittels des ersten Kompressors C1 überbrückt werden, ohne dass ein Teil des aus dem ersten Kompressor C1 herausströmenden Fluids in den zweiten Kompressor C2 gedrückt wird. Fig. 2 shows a block diagram of a heat pump device according to the invention. This heat pump device is based essentially on the heat pump device according to Fig. 1 , According to the invention is in the block diagram of Fig. 2 a shut-off valve 27 is provided in the supply line 100 between the output of the first compressor C1 and the input of the second compressor C2, which is preferably designed as a servo-shut-off valve 27. This Shut-off valve 27 is arranged in the supply line 100, that the shut-off valve 27 is bridged together with the second compressor C2 through the bypass line 123. In this way, the second compressor C2 can be bypassed by closing the shut-off valve 27 for the operation of the refrigerator in the one-stage compression by means of the first compressor C1, without a part of the flowing out of the first compressor C1 fluid in the second compressor C2 is pressed.

Erfindungsgemäß ist ferner in dem Blockschaltbild der Fig. 2 der zweite Ölabscheider 26 - im Gegensatz zu der Wärmepumpenvorrichtung gemäß dem Stand der Technik - so angeordnet, dass die zweite Umgehungsleitung 123 zwischen dem Ausgang des zweiten Kompressors C2 und dem Eingang des zweiten Ölabscheiders 26 einmündet. Auf diese Weise wird der zweite Ölabscheider 26 sowohl bei der Zwei-Stufen-Kompression als auch bei beiden Betriebsweisen der Ein-Stufen-Kompression stets vom Fluid durchströmt.According to the invention is further in the block diagram of Fig. 2 the second oil separator 26, in contrast to the heat pump device according to the prior art, arranged so that the second bypass line 123 between the outlet of the second compressor C2 and the inlet of the second oil separator 26 opens. In this way, the second oil separator 26 is always traversed by the fluid both in the two-stage compression as well as in both modes of one-stage compression.

Erfindungsgemäß ist weiter zwischen der Einmündung der zweiten Umgehungsleitung 123 und dem Ausgang des zweiten Kompressors C2 ein Rückschlagventil 28 vorgesehen, um ein Rückströmen von Fluid in den zweiten Kompressor C2 zu verhindern, falls in der Ein-Stufen-Kompression der zweite Kompressor C2 nicht betrieben wird.According to the invention, a check valve 28 is further provided between the junction of the second bypass line 123 and the output of the second compressor C2, to prevent backflow of fluid into the second compressor C2, if in the one-stage compression of the second compressor C2 is not operated ,

Erfindungsgemäß wird auch das Ölausgleichsventil 24 zwischen der ersten Ölleitung 101 und der zweiten Ölleitung 102 in der Ein-Stufen-Kompression mittels des ersten Kompressors C1 geöffnet, um einen Ölausgleich zwischen dem ersten Kompressor C1 und dem zweiten Kompressor C2 zu ermöglichen. Ferner wird in einem Ausführungsbeispiel im Betrieb der Ein-Stufen-Kompression mittels des ersten Kompressors C1 durch das Öffnen des Ölausgleichsventil 24 die Umgehungsleitung 124 mit den Kompressor C2 und die Einspritzleitung 109 über den Zwischenkühler 6 (Economizer) auf Saugdruckniveau gebracht.Also, according to the invention, the oil balance valve 24 between the first oil pipe 101 and the second oil pipe 102 is opened in the one-stage compression by the first compressor C <b> 1 to allow oil equalization between the first compressor C <b> 1 and the second compressor C <b> 2. Further, in one embodiment, in the operation of the one-stage compression by the first compressor C1, by opening the oil balance valve 24, the bypass passage 124 having the compressor C2 and the injection passage 109 are brought to the suction pressure level via the intercooler 6 (economizer).

In einer vorteilhaften Ausgestaltung der Erfindung ist gemäß Fig. 2 weiterhin gezeigt, dass ein Vorlauf 0 und ein Rücklauf 1 am Kondensator 2 angeschlossen sind. Vorteilhaft ist weiterhin die Verwendung eines 4/2-Wegeventils 4, welches eine erste Verbindung 4a aufweist, die mit einer Heißgasleitung 104 verbunden ist. Eine zweite Verbindung 4b ist mit einer Austrittsleitung 104b des Verdampfers verbunden. Eine dritte Verbindung 4c ist mit einer Verbindungsleitung 104c verbunden, und eine vierte Verbindung 4d des 412-Wegeventils 4 ist mit einer Verbindungsleitung 104d verbunden. Weiterhin ist ein Abscheider-Sammler 5 vorgesehen. Eine Abtauschlange 7, an die auch ein Leitungssegment 107 angeschlossen ist, ist vorteilhaft vor dem Zwischenkühler 6 angebracht. Weiterhin ist ein Expansionsventil 9, ein Filtertrockner 10 und ein Schauglas 12 vorgesehen. Zur Schaltung der Strömungsrichtung sind an verschiedenen Stellen Rückschlagventile 15, 16, 17, 18 angebracht, die hauptsächlich für die Umschaltung zwischen Heizbetrieb und Abtaubetrieb verwendet werden. Weiterhin ist ein Expansionsventil 19 vorgesehen, mit welchem der Zustand des Kältemittels im Verdampfer geregelt wird. Die Rückschlagventile 22 und 23 sind in den Bypassleitungen 106 und 110 zur Schaltung der Strömungsrichtung vorgesehen. Mit dem Druckausgleichsventil 21 wird insbesondere der Druck in den beiden Ölsümpfen des Verdichters C1 und C2. Eine Druckausgleichsleitung 108 ist hinter dem Absperrventil 27 angeschlossen. Weiterhin ist ein Leitungssegment 103 vorgesehen. An das Leitungssegment 103 sind die Bypassleitungen 106 und 110 angeschlossen. Die Saugleitung 105 ist vorteilhaft vom Abscheider-Sammler 5 zum Verdichter C1 geführt. Des weiteren sind die Leitungen 108, 112, 115, 116, 117, 119, 121 und 122 vorgesehen.In an advantageous embodiment of the invention is according to Fig. 2 further shown that a flow 0 and a return 1 are connected to the capacitor 2. It is also advantageous to use a 4/2-way valve 4, which a first connection 4a, which is connected to a hot gas line 104. A second connection 4b is connected to an exit line 104b of the evaporator. A third connection 4c is connected to a connection line 104c, and a fourth connection 4d of the 412-way valve 4 is connected to a connection line 104d. Furthermore, a separator-collector 5 is provided. A Abtauschlange 7, to which a line segment 107 is connected, is advantageously mounted in front of the intercooler 6. Furthermore, an expansion valve 9, a filter drier 10 and a sight glass 12 are provided. For switching the flow direction check valves 15, 16, 17, 18 are mounted at different locations, which are mainly used for switching between heating and defrosting. Furthermore, an expansion valve 19 is provided, with which the state of the refrigerant is controlled in the evaporator. The check valves 22 and 23 are provided in the bypass lines 106 and 110 for switching the flow direction. With the pressure compensation valve 21 in particular the pressure in the two oil sumps of the compressor C1 and C2. A pressure equalization line 108 is connected behind the shut-off valve 27. Furthermore, a line segment 103 is provided. To the line segment 103, the bypass lines 106 and 110 are connected. The suction line 105 is advantageously performed by the separator-collector 5 to the compressor C1. Furthermore, the lines 108, 112, 115, 116, 117, 119, 121 and 122 are provided.

Die Erfindung betrifft den Gedanken, dass bei der Wärmepumpenvorrichtung der Europäischen Patentschrift EP 2 088 388 A1 in der Praxis Probleme hinsichtlich einer Kältemittelverlagerung auftreten können. Wird der erste Kompressor C1 gestartet, kann es vorkommen, dass sich das Kältemittel, d.h. das Fluid, in den zweiten Kompressor C2 bzw. in den Ölabscheider 26 verlagert. Daher kann es erforderlich sein, das Wärmepumpensystem der EP 2 088 388 A1 lediglich im Einverdichterbetrieb mit dem zweiten Kompressor C2 laufen zu lassen.The invention relates to the idea that in the heat pump device of the European Patent EP 2 088 388 A1 In practice, problems may arise with regard to a refrigerant displacement. When the first compressor C1 is started, it may happen that the refrigerant, ie the fluid, is displaced into the second compressor C2 or into the oil separator 26. Therefore, it may be necessary for the heat pump system of EP 2 088 388 A1 run only in the compressor operation with the second compressor C2.

Claims (8)

  1. Heat pump equipment with
    a refrigeration cycle,
    a first compressor (C1) and a second compressor (C2), which are connected by a pipeline segment (100) in series such that the compression is a two-stage compression, if the first compressor (C1) and the second compressor (C2) are operated,
    a condenser (2),
    an evaporator (3),
    an expansion valve (19), which is arranged before the evaporator (3) in the direction of flow,
    a first oil separator (25), which is arranged behind the first compressor (C1) in the direction of flow and connected with the first compressor (C1) over a first oil pipeline (101) in order to route oil which is separated out back to the first compressor (C1),
    a second oil separator (26), which is arranged behind the second compressor (C2) in the direction of flow and connected with the second compressor (C2) over a second oil pipeline (102) in order to route oil which is separated out back to the second compressor (C2),
    whereby at least the first compressor (C1) or the second compressor (C2) can be operated independently, and
    a first bypass line (122) for the bridging of the non-operated first compressor (C1) and a second bypass line (123) for the bridging of the non-operated second compressor (C2), and
    whereby a shut-off valve (27) is connected upstream of the second compressor (C2) in the direction of flow, identified in that
    the first and second bypass lines (122, 123) end in the pipeline segment (100) in each case between the first oil separator (25) and the shut-off valve (27).
  2. Heat pump equipment according to claim 1, whereby
    the second by-pass line (123) ends between the output of the second compressor (C2) and the second oil separator (26).
  3. Heat pump equipment according to claim 1 or 2,
    whereby a check valve (28) is provided between the connection of the second environment line (123) and the output of the second compressor (C2).
  4. Heat pump equipment according to claim 1, 2 or 3,
    whereby the second by-pass (123) of the second compressor (C2) is arranged in such a way that the first oil separator (25) and the second oil separator (26) are switched in series if the first compressor (C1) is operated.
  5. Heat pump equipment according to one of the previous claims, with
    an injecting line (109) which is arranged after the shut-off valve (27) in the direction of flow.
  6. Heat pump equipment according to one of the previous claims, with
    an oil-compensation valve (24) which is arranged between the first oil pipeline (101) and the second oil pipeline (102),
    whereby the oil-compensation valve (24) is opened if the first compressor (C1) is operated
  7. Heat pump equipment according to one of the claims 1-5, with an oil-compensation valve (24) which is arranged between the first oil pipeline (101) and the second oil pipeline (102), whereby in the operation of the one-stage compression, by means of the first compressor C1 through the opening of the oil-compensation valve 24, the bypass line 124, with the compressor C2 and the injecting line 109, are brought to suction pressure level over an economizer intermediate-cooler (6).
  8. Heat pump equipment according to one of the previous claims, whereby the first bypass line (122) and/or the second bypass line (123) indicate a check valve which is provided with a slope such that condensed-out fluid can flow back into the flow-through area again.
EP11001131.9A 2011-02-11 2011-02-11 Heat pump device Active EP2487437B1 (en)

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DE102013014543A1 (en) 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg heat pump device
DE102013014542A1 (en) 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg heat pump device
JP6301101B2 (en) * 2013-10-18 2018-03-28 三菱重工サーマルシステムズ株式会社 Two-stage compression cycle
US10317112B2 (en) 2014-04-04 2019-06-11 Johnson Controls Technology Company Heat pump system with multiple operating modes
CN104165478B (en) * 2014-08-01 2016-06-29 广东美芝制冷设备有限公司 multiple on-line system
US11874031B2 (en) 2018-12-19 2024-01-16 Copeland Lp Oil control for climate-control system
EP3899384A4 (en) * 2018-12-19 2022-09-28 Emerson Climate Technologies, Inc. Oil control for climate-control system
US11150001B2 (en) * 2019-12-17 2021-10-19 Heatcraft Refrigeration Products Llc Cooling system with compressor bypass

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EP2088388B1 (en) 2008-02-06 2019-10-02 STIEBEL ELTRON GmbH & Co. KG Heat pump system
EP2221559B1 (en) * 2009-02-19 2016-08-10 Systemair AC S.A.S Thermodynamic installation with improved lubrication.

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