EP2221559B1 - Thermodynamische Anlage mit verbesserter Schmierung - Google Patents

Thermodynamische Anlage mit verbesserter Schmierung Download PDF

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Publication number
EP2221559B1
EP2221559B1 EP09153255.6A EP09153255A EP2221559B1 EP 2221559 B1 EP2221559 B1 EP 2221559B1 EP 09153255 A EP09153255 A EP 09153255A EP 2221559 B1 EP2221559 B1 EP 2221559B1
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EP
European Patent Office
Prior art keywords
compressor
lubricant
compressors
hose
refrigerant fluid
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
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EP09153255.6A
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English (en)
French (fr)
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EP2221559A1 (de
Inventor
Mario Borras
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Systemair Ac SAS
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Systemair Ac SAS
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Priority to EP09153255.6A priority Critical patent/EP2221559B1/de
Priority to ES09153255.6T priority patent/ES2600474T3/es
Publication of EP2221559A1 publication Critical patent/EP2221559A1/de
Application granted granted Critical
Publication of EP2221559B1 publication Critical patent/EP2221559B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication

Definitions

  • the present invention relates to a thermodynamic refrigerant plant and its method of operation.
  • lubricant such as lubricating oil
  • refrigerant for the compressors is often driven by the refrigerant.
  • An object of the invention is to avoid this. This object is obtained with an installation having the features of claim 1 and a method according to claim 8.
  • a corollary problem also arises as to how to ensure the type of valve means to be used so that the lubricant balancing can be achieved effectively and simply at least in the second and third aforementioned configurations.
  • the architecture of the system will preferably make it possible to use a simple 4-way valve (favorably with a non-return valve) to go from the two-stage operation cycle to the single-stage cycle, depending on the needs of the system. building heating in such an application.
  • the fat indicates a circulation of the refrigerant in the blackened pipe.
  • the figure 1 shows such a two-stage operation.
  • the low pressure (LP) compressor 1 draws in the refrigerant which has evaporated in the evaporator 9 thus recovering the heat generally from the outside air.
  • the cold source may be soil or water. However, it is best to use outside air.
  • the compressor 1 compresses the refrigerant, for example a mixture of HFCs such as R-407C, at the medium pressure of the system which is fixed by the high pressure compressor (HP) 2.
  • This intermediate pressure is set by the ratio of the volumes swept compressors 1 and 2.
  • the four-way valve 3 then relates its input 31 to its output 34, as figure 2 . It will be understood that this valve is mounted to operate the installation according to one of said three possible configurations, being arranged between the two compressors 1, 2 when they operate in series. In this way, the low-pressure delivery pipe 5 is in direct connection with the suction pipe 6 of the compressor 2.
  • the non-return valve 4 prevents the high-pressure refrigerant leaving the compressor 2 by the pipe 21 to iron at low system pressure by the pipes 8 and 7.
  • the water of the heating circuit of the habitat here to be heated is heated by the refrigerant which gives in heat there.
  • the water enters the condenser 10 after cooling in the heating system (radiators, convectors ...) by the pipe 19 and out, at a temperature typically higher than 4 to 5 ° C, through the pipe 20.
  • the tapping 17 on the high-pressure pipe 18 of the condenser outlet makes it possible to take a certain flow rate d3 of fluid which is evaporated in the subcooling exchanger 11, after expansion by the expander 12, in order to sub-cool the flow rate d2.
  • the flow d2 is equal to d1 - d3.
  • the flow d1 is then the total flow compressed by the compressor 2 and condensed in the condenser 10.
  • the flow d3 is much lower than d2.
  • the point 25 is the outlet point of the flow d2 of the subcooling exchanger 11.
  • the enthalpies at the respective points 13, 17 and 25 are shown in FIG. figure 4 on a so-called Mollier diagram, pressure - enthalpy, where is represented the two-stage cycle corresponding to the functioning presented figure 1 .
  • the quilting 16 of the pipework 26 on the pipe 6 allows the high-pressure compressor 2 to suck also the flow rate d3 evaporated in the subcooling heat exchanger 11.
  • the flow d2 is then brought by the pipe 14 to the evaporator 9, the refrigerant being expanded in the expander 15.
  • the four-way valve 3, according to its position, then allows either the first compressor 1 to operate alone, or the second compressor 2 to operate alone.
  • the operation of one or the other of the compressors depends on the heat output required, since the first compressor 1 has a swept volume greater than the HP compressor 2 and therefore a higher power, given their size for the two-stage operation.
  • the figure 2 presents the operation with the first compressor 1 in operation and the second compressor 2 stopped.
  • the inlet 31 of the four-way valve 3 is in connection with the outlet 32, thereby directly connecting the discharge pipe 5 of the first compressor 1 with the pipe 8 which bypasses the second compressor 2 and joins the ducting 21 before entering the condenser 10 via the quilting 22.
  • the figure 3 shows the operation of the second compressor 2 alone, the first compressor 1 being stopped.
  • the second compressor 2 sucks up the refrigerant which has evaporated in the evaporator 9 via the piping 7 and the tap 23 of the outlet pipe 24 of the evaporator 9.
  • the four-way valve 3 then communicates this piping. 7 with the suction pipe 6 of the second compressor 2 via the second inlet 33 and the first outlet 34 of the four-way valve 3.
  • the rest of the circulation of the refrigerant is identical. Again the sub-cooling exchanger 11 is not in operation. It is therefore crossed by the total flow d1.
  • the four-way valve 3 is electrically controlled to move an inner piston, thereby communicating the first input 31 with either the first output 34 or the second output 32. In the latter case, the four-way valve 3 in communication the second input 33 with the first output 34.
  • This single four-way valve 3 associated favorably with the non-return valve 4 then allows to develop a simple regulation according to the external temperature of the environment.
  • the regulator 40 of the installation which controls its configuration receives, via the input channel 41, an electrical signal corresponding to the analog value of the outside temperature, measured for example by a probe, shown schematically in FIG. figure 5 .
  • this outside temperature is below a threshold temperature T1, for example 0 ° C.
  • T1 a threshold temperature
  • the four-way valve 3 is in position 1 of Table A below corresponding to the operation presented.
  • FIG 1 where the tubing 5 is in communication with the tubing 6, via the first inlet 31 and the first output 34 of the four-way valve.
  • the regulator 40 then sends an electrical signal via the channel 42 to put the four-way valve 3 in position 1.
  • the controller has also operated the compressors 1 and 2 via the channels 44 and 45 of the regulator 40.
  • the heating capacity of the heat pump is set by two thresholds, low and high, from the water inlet temperature to the condenser.
  • This water temperature is measured on the pipe 19 by a probe, schematized at 47, and its value is received analogically by the regulator 40, via the channel 43.
  • the regulator 40 puts into operation either the compressors 1 and 2 together in two-stage operation, or the one of the compressors 1, 2, this as a function of the outside temperature, as indicated below in Table A.
  • the regulator 40 sends, via the channel 42, the setpoint position 2 to the four-way valve 3 as defined in the table below.
  • the regulator 40 controls in parallel the operation of the first compressor 1 alone, as shown figure 2 .
  • the first input 31 is then put into communication with the second output 32.
  • the regulator 40 sends, via the channel 42, the instruction of the same position 2 to the four-way valve 3, as again defined in the table below.
  • the regulator 40 controls the operation of the second compressor 2 alone, as shown figure 3 .
  • the second input 33 is thus placed in communication with the first output 34.
  • the four-way valve 3 is in its position 2 unchanged. It is the compressor, 1 or 2, in operation that circulates the refrigerant as indicated in FIG. figure 2 or 3 corresponding.
  • the second regulator 12 may conventionally be a capillary tube. In this case, it is necessary to provide on the bypass circuit 26 a solenoid valve, shown diagrammatically in Figures 1 to 3 , to close the circuit 26, in particular in the operating mode shown schematically in FIG. figure 3 .
  • the capillary tube could be replaced by another type of regulator.
  • the four-way valve 3 could be replaced by equivalent means fulfilling the same functions (selection means).
  • the first valve 50 is mounted, upstream of the tapping 16, between the pipes 5 and 6 connected together.
  • the second valve 51 is mounted on the second bypass 8 then connected between the tapping 54 situated upstream of the first valve inlet 50 and the tapping 22.
  • the third valve 52 is mounted on first bypass 7 then connected between the tap 23 located upstream of the inlet of the compressor BP 1 and the tap 53 connected between the tap 16 and the inlet of the compressor HP 2.
  • the figure 6 shows the two-stage configuration, with the two compressors in series.
  • the valves 51, 52 are closed, the one 50 is open.
  • the figure 7 shows the single-stage configuration with the HP 2 compressor running, while the other 1 is stopped.
  • the valves 50, 51 are closed, that 52 is open.
  • the figure 8 shows the other single-stage configuration with the BP 1 compressor in operation, the other 2 being stopped.
  • the valves 50, 52 are closed, the 51 is open.
  • the selective circulation means comprise a dedicated conduit 56 with two pipes 57, 59 interconnecting the lubricant receptacles of the compressors, and a valve means 55 interposed at a location of this selectively to open and close the circulation of the lubricant between the compressors.
  • Figure 9 on each of the two compressors, the tubing concerned is connected to the casing at the level of the oil level (used here as a lubricating fluid), thus in connection with the lubricant receptacles 100, 200.
  • valve means 55 that is recommended to use is of the two-way solenoid valve type which, when under direct control (“directly actuated"), operates in such a way that the magnetic field of the solenoid then forces a movement of the plunger and thus causes the opening of the valve means 550 that it contains, this without requiring any pressure difference.
  • this preferred valve means will be adapted to open on command (direct) and remain open regardless of the difference in lubricant pressures established between the compressors 1, 2.
  • valve means 55 This will impose a mounting direction of the valve means 55, as shown more clearly figure 9 where the arrow 551, directed from the compressor HP 2 to the compressor BP 1, therefore indicates this closing tightness all the stronger the valve 550 that P2 will be higher compared to P1.
  • a two-way valve solenoid valve from "ALCO CONTROLS" type 110RB, without pressure differential, will be suitable.
  • the operation of the installation in connection with the pressure equalization sought may be the following, in the operating hypotheses corresponding to the figures 1 and 3 (information will easily be adapted to cases of Figures 6, 7 corresponding):
  • the start of the installation is carried out here from the compressor 2 (C2) with the four-way valve 3 in single-stage configuration ( figure 3 ).
  • the suction pressure of the C2 (C2 housing pressure) is equal to the suction pressure of the compressor 1 (C1) minus the pressure drop of the valve 3.
  • the management of the opening time of the valve 55 and the frequency of this operation are defined by the regulator 40.
  • the regulator 40 will intervene so that a correct amount of oil is stored in each compressor for reliable operation.
  • valve 3 could be replaced by that of the valves 50 or 52, for the pressure drop, and that of the three valves 50, 51, 52 for the circulation of the refrigerant.
  • the duration of the balancing may be a few seconds.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (9)

  1. Thermodynamische Anlage, umfassend einen ersten Kompressor (1, C1), einen zweiten Kompressor (2, C2), einen Kreislauf mit mehreren Zirkulationswegen eines Kühlfluids, der sie verbindet, Schmierstoffbehälter (100, 200), die vorgesehen sind, um ein Schmierfluid der Kompressoren aufzunehmen, Selektionsmittel (3; 50, 51, 52), die einen Betrieb der Anlage gemäß bestimmten mindestens der drei folgenden Konfigurationen ermöglichen:
    - a) mit dem Kühlfluid, das durch den ersten Kompressor verläuft, ohne durch den zweiten Kompressor zu verlaufen,
    - b) mit dem Kühlfluid, das durch den zweiten Kompressor verläuft, ohne durch den ersten Kompressor zu verlaufen,
    - c) mit den zwei Kompressoren, die in Reihe geschaltet funktionieren, wobei der zweite Kompressor dann nachgelagert vom ersten Kompressor gemäß der Zirkulationsrichtung des Kühlfluids angebracht ist, wobei die oder bestimmte der Selektionsmittel, die ausgelegt sind, um einen Druckverlust zu erzeugen, auf dem Kreislauf des Kühlfluids wie folgt angebracht sind:
    -- vorgelagert vom zweiten Kompressor in der Konfiguration, in der das Kühlfluid durch ihn verläuft, ohne durch den zweiten Kompressor zu verlaufen,
    -- und zwischen dem ersten und dem zweiten Kompressor, wenn sie in Reihe geschaltet funktionieren, dadurch gekennzeichnet, dass sie Mittel (40, 55, 56, 57, 59) zur selektiven Zirkulation des Schmierstoffs umfasst, umfassend eine Leitung, die die Behälter verbindet und/oder ein Schiebermittel (55), das durch einen Regler gesteuert (40) wird, um selektiv die Zirkulation des Schmierstoffs zwischen den Kompressoren zu öffnen und zu schließen und um eine Zirkulation des Schmierstoffs des Behälters (100) des ersten Kompressors hin zu demjenigen (200) des zweiten in einer Situation zu ermöglichen, in der, wobei die Anlage gemäß der Konfiguration b) funktioniert, der Druckverlust der Selektionsmittel (3; 50; 51, 52) eine Druckdifferenz zwischen den Schmierstoffbehältern erzeugt.
  2. Anlage nach Anspruch 1, dadurch gekennzeichnet, dass das Schiebermittel ein Ventilmittel (550) umfasst, das ausgelegt ist, um:
    - in einem geschlossenen Zustand eine Schließdichtigkeit zu schaffen, die der Zirkulation des Schmiermittels umso stärker entgegensteht, als der Druck des Schmiermittels im zweiten Kompressor mit Bezug auf denjenigen im ersten Kompressor erhöht ist; und
    - sich auf Befehl zu öffnen und offen zu bleiben, unabhängig von der Druckdifferenz des Schmierstoffs, der zwischen den Kompressoren festgesetzt ist.
  3. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Schiebermittel (55, 550) ein Zweiwege-Magnetschieber ohne Druckausgleich ist.
  4. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Selektionsmittel (3; 50, 51, 52) einen Vierwegeschieber (3) umfassen, der montiert ist, um die Anlage gemäß einer der drei möglichen Konfigurationen funktionieren zu lassen, indem er zwischen den zwei Kompressoren (1, 2) angeordnet ist, wenn sie in Reihe geschaltet funktionieren.
  5. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie am Ausgang jedes des ersten und des zweiten Kompressors (1, 2) eine passive Trennvorrichtung (62, 64) zwischen dem angetriebenen Schmierstoff und dem komprimierten Kältefluid umfasst, um den Schmierstoff wiederzugewinnen und ihn am Eingang des betreffenden Kompressors über eine Leitung zur Wiedereinspritzung von Schmierstoff wieder einzuspritzen.
  6. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass
    - der Kreislauf mit mehreren Zirkulationswegen des Kühlfluids einen ersten Rohransatz (5) am Ausgang des ersten Kompressors (1), einen zweiten Rohransatz (6) am Eingang des zweiten Kompressors (2), einen dritten Rohransatz (21) am Ausgang des zweiten Kompressors (2) umfasst, der sich bis zum Eingang eines Kondensators (10) erstreckt, einen vierten Rohransatz (18, 14), der den Ausgang des Kondensators (10) mit dem Eingang eines Druckminderers (12, 15) verbindet, der vorgelagert vom Verdampfer (9) angeordnet ist, einen fünften Rohransatz (24), der den Ausgang eines Verdampfers (9) mit dem Eingang des ersten Kompressors (1) verbindet, einen ersten Bypass (7) des ersten Kompressors (1), der sich vom Eingang des ersten Kompressors (1) in Richtung des zweiten Rohransatzes (6) erstreckt, einen zweiten Bypass (8) des zweiten Kompressors (2), der sich vom dritten Rohransatz (21) in Richtung des ersten Rohransatzes (5) erstreckt, und mit einem Rückschlagventil (4) ausgestattet ist,
    - und die Selektionsmittel (3; 50, 51, 52) ausgelegt sind um Folgendes zu verbinden:
    -- in der Konfiguration, in der die zwei Kompressoren (1, 2) in Reihe geschaltet arbeiten, den ersten Rohransatz (5) mit dem zweiten Rohransatz (6) und den ersten Bypass (7) mit dem Rückschlagventil (4) des zweiten Bypasses (8), und,
    -- in der Konfiguration, in der das Kühlfluid durch den ersten Kompressor (1) verläuft, ohne durch den zweiten Kompressor (2) zu verlaufen, den ersten Rohransatz (5) mit dem dritten Rohransatz (21) und den ersten Bypass (7) mit dem zweiten Rohransatz (6).
  7. Anlage nach den Ansprüchen 4 und 6, dadurch gekennzeichnet, dass der Vierwegeschieber (3) einen ersten Eingang (31) aufweist, der mit dem ersten Rohransatz (5) verbunden ist, einem ersten Ausgang (34), der mit dem zweiten Rohransatz (6) verbunden ist, einen zweiten Eingang (33), der mit dem ersten Bypass (7) verbunden ist, einen zweiten Ausgang (32), der mit dem Rückschlagventil (4) des zweiten Bypasses (8) verbunden ist, und ein bewegliches Mittel (35), das ausgelegt ist, um, in einer ersten Konfiguration, den ersten Eingang (31) mit dem ersten Ausgang (34) und den zweiten Eingang (33) mit dem zweiten Ausgang (32), und, in einer zweiten Konfiguration, den ersten Eingang (31) mit dem zweiten Ausgang (32) und den zweiten Eingang (33) mit dem ersten Ausgang (34) zu verbinden.
  8. Verfahren, um die Zirkulation von Schmierstoff zwischen dem ersten und dem zweiten Kompressor (C1, 1, C2, 2) einer thermodynamischen Anlage zu fördern, umfassend einen Kreislauf aus mehreren Zirkulationswegen eines Kühlfluids, Schmierstoffbehälter (100, 200), um ein Schmierfluid der Kompressoren aufzunehmen, und Selektionsmittel (3; 50, 51, 52), die einen Betrieb der Anlage gemäß den folgenden Konfigurationen ermöglichen:
    - a) mit dem Kühlfluid, das durch den ersten Kompressor verläuft, ohne durch den zweiten Kompressor zu verlaufen,
    - b) mit dem Kühlfluid, das durch den zweiten Kompressor verläuft, ohne durch den ersten Kompressor zu verlaufen,
    - c) mit den zwei Kompressoren, die in Reihe geschaltet funktionieren, wobei der zweite Kompressor dann nachgelagert vom ersten Kompressor gemäß der Zirkulationsrichtung des Kühlfluids angebracht ist, wobei in dem Verfahren ein Druckverlust auf dem Kreislauf des Kühlfluids mit Hilfe der oder von bestimmten der Selektionsmittel erzeugt wird,
    dadurch gekennzeichnet, dass der Druckverlust verwendet wird, um eine Druckdifferenz zwischen den Schmierstoffbehältern (100, 200) zu erzeugen und so, außerhalb des Kreislaufs des Kühlfluids (dedizierte Leitung 56), eine Ausgleichszirkulation des Schmierfluids zwischen den Behältern zu bewirken, dies ausschließlich von demjenigen (100) des ersten Kompressors hin zu demjenigen (200) des zweiten im Fall eines Starts der Anlage, bei der das Kühlfluid durch den zweiten Kompressor (C2, 2) verläuft, ohne durch den ersten Kompressor (C1, 1) zu verlaufen.
  9. Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass die Ausgleichszirkulation des Schmierfluids auch beim Stopp der Anlage durchgeführt wird, nachdem die zwei Kompressoren (1, C1; C2, 2) zusammen in Reihe geschaltet funktionierten, indem die selektiven Zirkulationsmittel (55, 56, 57, 59) geöffnet werden, die zwischen den Behältern (100, 200) angeordnet sind, so dass diese Zirkulation vom Schmierstoffbehälter (200) des zweiten Kompressors hin zu demjenigen des ersten Kompressors (C1, 1) durchgeführt wird.
EP09153255.6A 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung Not-in-force EP2221559B1 (de)

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Application Number Priority Date Filing Date Title
EP09153255.6A EP2221559B1 (de) 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung
ES09153255.6T ES2600474T3 (es) 2009-02-19 2009-02-19 Instalación termodinámica con lubricación mejorada

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EP09153255.6A EP2221559B1 (de) 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung

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EP2221559A1 EP2221559A1 (de) 2010-08-25
EP2221559B1 true EP2221559B1 (de) 2016-08-10

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EP2487437B1 (de) * 2011-02-11 2015-08-05 STIEBEL ELTRON GmbH & Co. KG Wärmepumpenvorrichtung
FR2977657B1 (fr) 2011-07-06 2018-05-04 Electricite De France Procede d'equilibrage des niveaux de lubrifiant dans une unite de compression multi-etagee d'un systeme d'echange thermique et systeme d'echange thermique mettant en oeuvre un tel procede
DE102013014542A1 (de) * 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung
DE102013014543A1 (de) * 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung
EP3040643B1 (de) * 2013-09-30 2018-12-26 Mitsubishi Heavy Industries Thermal Systems, Ltd. Wärmepumpensystem und wärmepumpenwassererhitzer
CN106537064B (zh) 2014-07-09 2019-07-09 开利公司 制冷系统
US11460224B2 (en) * 2018-10-31 2022-10-04 Emerson Climate Technologies, Inc. Oil control for climate-control system
CN113513856A (zh) * 2021-07-15 2021-10-19 广东纽恩泰新能源科技发展有限公司 一种热泵系统及控制方法

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US3621670A (en) * 1970-01-12 1971-11-23 Vilter Manufacturing Corp Lubricating oil equalizing system
DE19823524A1 (de) * 1998-05-26 1999-12-02 Linde Ag Verbund(kälte)anlage und Verfahren zum Betreiben einer Verbund(kälte)anlage
JP2001147047A (ja) * 1999-11-19 2001-05-29 Fujitsu General Ltd 空気調和機
DE102005019795A1 (de) * 2004-05-07 2005-12-01 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Klimakompressor
FR2889733B1 (fr) 2005-08-12 2012-10-12 A C E Ind Systeme de pompe a chaleur avec deux compresseurs
KR101387478B1 (ko) * 2007-03-13 2014-04-24 엘지전자 주식회사 압축 시스템 및 이를 이용한 공기조화 시스템

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ES2600474T3 (es) 2017-02-09

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