EP2570753B1 - Pompe à chaleur avec éjecteur - Google Patents

Pompe à chaleur avec éjecteur Download PDF

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Publication number
EP2570753B1
EP2570753B1 EP12184177.9A EP12184177A EP2570753B1 EP 2570753 B1 EP2570753 B1 EP 2570753B1 EP 12184177 A EP12184177 A EP 12184177A EP 2570753 B1 EP2570753 B1 EP 2570753B1
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EP
European Patent Office
Prior art keywords
heat pump
refrigerant
pressure
ejector
outlet
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EP12184177.9A
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German (de)
English (en)
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EP2570753A3 (fr
EP2570753A2 (fr
Inventor
Steffen Oberländer
Eberhard Wobst
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Engie Refrigeration GmbH
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Engie Refrigeration GmbH
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Publication of EP2570753A3 publication Critical patent/EP2570753A3/fr
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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
    • F25B41/00—Fluid-circulation 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure

Definitions

  • the invention relates to a high-temperature heat pump or a refrigeration machine (which can also be operated in cold/heat coupling) with at least one ejector, in which high pressure differences between the high and low pressure sides occur due to the operating conditions.
  • Heat pumps and chillers transport heat from a low temperature level to a higher one by using work. They differ only in the temperature levels reached during operation (usually the high temperature level is higher with heat pumps than with chillers, while the low temperature level is correspondingly lower with chillers) and in which sides are used (heat pump: warm side; chiller cold side; Heat-cold coupling: warm and cold side).
  • heat pump warm side; chiller cold side; Heat-cold coupling: warm and cold side.
  • the term “heat pump” is therefore generally used below for the terms "heat pump/refrigeration machine/heat-cold coupling”.
  • two-stage (also multi-stage) heat pumps are usually used, for which there are numerous implementation options based on two-stage compressors or two compressors connected in series.
  • Intermediate cooling is usually used to keep the compression end temperature within the permissible limits.
  • the conventional two-stage heat pumps have the disadvantage on the one hand that both compressors have to be supplied with energy from outside; on the other hand, oil-lubricated compressors are used in such heat pumps according to the prior art, for which measures for oil return (e.g. by oil separators and oil management systems) must be taken. These measures cause additional technical and economic effort, lead to an unnecessary deterioration in the coefficient of performance and cause unnecessary environmental pollution due to the consumption of oil.
  • chillers are presented in which (in the evaporator) evaporated refrigerant (low pressure level) is conveyed through the ejector into a separator collector (medium pressure level).
  • the ejector thus acts as the first compressor stage.
  • a compressor usually oil-lubricated, conveys the refrigerant from the separation collector into the gas cooler and brings the refrigerant to the high-pressure level (second compressor stage). Intercooling is not required because the compressor draws saturated refrigerant from the separator header.
  • a technical solution for the required oil return is not specified.
  • the object of the invention is to provide a two-stage high-temperature heat pump in which, due to the operating conditions, high pressure differences occur between the high and low-pressure sides and with which high COP values can be achieved.
  • the starting point is an at least two-stage heat pump with at least one first compressor stage, which is designed to increase the pressure in the refrigerant from a low pressure to a medium-pressure level, and with at least one second compressor stage, which is designed to increase the pressure in the refrigerant from a Medium pressure is set up at a high pressure level at which the refrigerant is preferably supercritical.
  • the heat pump also includes at least one gas cooler operated at the high pressure level of the heat pump (or a condenser if the refrigerant used becomes liquid on the high pressure side during operation of the heat pump), the at least one gas cooler or the condenser having an inlet and an outlet, at least one evaporator operated at the low-pressure level of the heat pump, which has an inlet and an outlet, at least one throttle valve, which is connected between the second outlet of a separator collector and the inlet of the at least one evaporator, and which is used to expand the refrigerant from the medium-pressure level to the low-pressure level used for the heat pump, as well as the separator collector operated at the medium pressure level of the heat pump.
  • at least one gas cooler operated at the high pressure level of the heat pump or a condenser if the refrigerant used becomes liquid on the high pressure side during operation of the heat pump
  • the at least one gas cooler or the condenser having an inlet and an outlet
  • At least one internal heat exchanger can be used with the heat from the refrigerant escaping from at least one gas cooler/condenser is transferred to the suction gas or suction gas is heated from an additional external heat source.
  • the separation collector serves to separate and collect liquid refrigerant, ie in addition to its function as a separator it also serves to store excess refrigerant. Accordingly, the separation header contains liquid and gaseous refrigerants, when a large amount of refrigerant is stored in the separation header, the proportion of the liquid refrigerant is high, and when a small amount of refrigerant is stored in the separation header, the proportion of the liquid refrigerant is correspondingly smaller.
  • the separator header has an inlet, a first outlet in communication with the gaseous refrigerant, and a second outlet in communication with the liquid refrigerant.
  • the at least one first compressor stage is implemented as at least one compression ejector and the at least one second compressor stage can be implemented as at least one oil-free turbo compressor unit.
  • Both the at least one compression ejector and the at least one turbo compressor unit can be constructed from a plurality of individual compression ejectors or turbo compressor units connected in series and/or in parallel.
  • the at least one compression ejector has a pressure port, an outlet and a suction port.
  • refrigerant enters the at least one compression ejector via the pressure connection, the refrigerant is guided (e.g. by means of nozzles) in a jet form through the at least one compression ejector and exits through the outlet of the at least one compression ejector.
  • the jet formed in this way generates a pressure drop at the suction connection (similar to that of a water jet pump), as a result of which gaseous refrigerant is drawn in from the at least one evaporator.
  • the pressure prevailing in the refrigerant increases, whereby the pressure in the refrigerant is raised from the low-pressure to the medium-pressure level (at the outlet of the at least one compression ejector) of the heat pump.
  • the compression ejector itself can be designed to be adjustable, i. i.e. its flow resistance can be changed continuously or in steps. An optimal flow through the compression ejector can then be achieved in the entire working area of the heat pump without excessive pressure being able to occur on the high-pressure side due to excessive flow resistance of the compression ejector. Compression ejectors with controllable flow resistances are, however, comparatively complex and expensive due to their construction.
  • less expensive compression ejectors with a fixed flow resistance can also be used.
  • a compression ejector with a comparatively high flow resistance can be used, with which a control valve (as a bypass) is connected in parallel, with the control valve being opened when the pressure on the high-pressure side of the heat pump exceeds a set value (a partial flow of the refrigerant is then drawn off at the ejector bypassed), or a compression ejector with a control valve connected in series can be used, with the compression ejector having such a small flow resistance that (when the control valve is fully open) an excess pressure on the high-pressure side of the heat pump caused by the flow resistance of the ejector can be ruled out.
  • the variant with the control valve in the bypass has the advantage that the full pressure difference is always present at the ejector, but the refrigerant flow is not fully utilized at times due to the bypass.
  • the variant with the serial control valve has the advantage that the entire refrigerant flow is always used by the ejector, but has the disadvantage that the entire pressure difference is not present at the ejector, at least at times.
  • the integration of the at least two compressor stages is implemented by connecting the suction port of the at least one compression ejector to the outlet of the at least one evaporator, the pressure port of the at least one compression ejector directly or via a control valve to the The outlet of the at least one gas cooler (or the condenser) or the at least one internal heat exchanger and the outlet of the at least one compression ejector is connected to the inlet of the separating collector.
  • an ejector (as the at least one first compressor stage) is used for the first time in an oil-free system (oil-free variant).
  • an ejector in conjunction with ammonia as a refrigerant (ammonia high-temperature variant) in a high-temperature heat pump with a high pressure difference (between the high-pressure side and the low-pressure side), e.g. greater than 35 bar (typically 50 to 80 bar).
  • the at least one compression ejector obtains all of the energy required for operation from the refrigerant circulating (in the circulating process), i.e. it does not require any energy (oil-free and high-temperature ammonia variants), and the refrigerant circuit of the heat pump may be oil-free (only oil-free variants)
  • the heat pump according to the invention high COP values and higher thermal outputs can be achieved, as a result of which an undesired heat transfer through the recirculation of separated oil is avoided.
  • hardware costs and performance reductions caused by the oil as well as restrictions on the application limits of the heat pump are avoided.
  • At least one compression ejector in one stage; however, if required by the process control, at least one multi-stage ejector can also be used. Compared to comparable single-stage ejectors, multi-stage ejectors are characterized by higher pump capacities (pressure ratio).
  • Turbo compressor units are preferably used as oil-free compressors (in the oil-free variant), which are operated at speeds of 15,000 to 200,000 revolutions per minute (rpm) and which are semi-hermetic, i. That is, the compressor and the associated drive motor are each accommodated in a housing that is sealed in a gas-tight manner by means of detachable connections.
  • turbo compressor units with higher outputs tend to be operated at lower speeds (eg 15,000 to 50,000 rpm) and turbo compressor units with lower outputs tend to be operated at higher speeds (eg 45,000 to 200,000 rpm).
  • both the compressor and the drive motor are located in a refrigerant atmosphere.
  • a refrigerant such. B. carbon dioxide, which has high densities as a gas and a compressor that works at high speeds (turbo compressor unit with a speed greater than 15,000 rpm)
  • high friction forces would occur, which on the one hand an increase in the required drive energy (reduction of the COP) and on the other hand would result in inadmissibly high compressor temperatures (inadmissibly high heat input into the refrigerant circuit).
  • turbo compressors with carbon dioxide as a refrigerant is hardly practicable or even impossible under these conditions.
  • the drive motor is sealed off from the refrigerant circuit, in which the at least one compressor is integrated, by means of a shaft seal.
  • shaft seals for shafts that operate at high speeds, e.g. B. greater than 15,000 rpm, rotate to manufacture with sufficiently low leakage rates.
  • the case fills up with refrigerant (carbon dioxide) after a certain period of time, the case has a suction port through which (due to the unavoidable Leaks in the shaft seal) refrigerant entering the housing is sucked off by means of a compressor or a pump (hereinafter: pump) and fed back into the refrigeration circuit. In this way, the pressure in the housing (the density of the refrigerant) is lowered and the friction loss of the at least one semi-hermetic or hermetic turbo compressor unit is reduced.
  • An extraction ejector is preferably used as (the at least one) pump (for extracting refrigerant from the motor housing), the suction connection of which is connected to the housing.
  • the outlet of the suction ejector is connected to the suction port of the at least one compression ejector and the pressure port of both the at least one compression and suction ejector is connected directly or via a control valve to the outlet of the at least one gas cooler or condenser of the heat pump.
  • the suction ejector can also be designed to be directly controllable (variable flow resistance) or an suction ejector with a fixed flow resistance can be used, which is connected either in parallel (bypass) or in series with a control valve.
  • the pump required for pumping out the housing (to reduce the friction to a level that makes sensible use of the turbo compressor unit possible in the first place) of the at least one turbo compressor unit is implemented as an ejector (suction ejector), which draws the energy required for its operation from the (im cycle process) circulating refrigerant, additional drive energy is avoided and the COP is kept at a high level.
  • refrigerant can only be extracted from the housing when the heat pump is in operation.
  • the leakage rate of the shaft seal of the at least one turbo compressor unit will decrease when the shaft is stationary, it cannot be completely ruled out that refrigerant will get into the housing, especially during longer downtimes.
  • the pressure of the refrigerant in the housing is high, then frictional forces can occur in the at least one semi-hermetic or hermetic turbo-compressor unit, which makes a restart possible without additional measures impede.
  • the refrigerant that has accumulated in the housing during the heat pump standstill can be removed from the housing using three methods before or during the restart of the heat pump.
  • the heat pump can be equipped with an external single or multi-stage compressor, the suction connection of which is connected to the casing. Before restarting the heat pump, the external compressor is switched on and the refrigerant is pumped back into the circuit from the housing. If necessary, the external compressor can continue to be operated during operation instead of or to support the suction ejector
  • the heat pump can be equipped with a control unit which allows the at least one semi-hermetic or hermetic turbo compressor unit of the heat pump to be restarted slowly (slow increase in speed) after downtimes.
  • the suction ejector's pump capacity increases and it pumps the refrigerant from the housing back into the refrigeration circuit.
  • the increase in the speed of at least one turbo compressor unit must be so slow that the refrigerant is largely removed from the housing before the at least one turbo compressor unit has reached its maximum speed.
  • the heat pump uses an environmentally friendly refrigerant
  • the refrigerant can be discharged to the environment before it is put into operation.
  • the heat pump includes a control unit and the housing has an opening to the environment, which is closed by means of a controllable valve. Before the heat pump is put into operation again, the controllable valve is opened by means of the control unit.
  • the machine can also be equipped with an additional refrigerant collector/storage tank, which can compensate for refrigerant losses over a longer period of operation.
  • the semi-hermetic or hermetic turbo compressor unit 1 delivers refrigerant to the gas cooler 2, where the refrigerant is cooled while releasing heat (shown schematically in the drawing by the arrows marked "WWA” and "WWE").
  • the term “gas cooler” is used instead of the term “liquefier”; For the sake of simplicity, the term gas cooler is always used below.
  • the refrigerant From the outlet 2.2 of the gas cooler 2, the refrigerant enters the pressure connection 3.1 of the compression ejector 3, emerges from its outlet 3.2 as a jet and enters the inlet 4.1 of the separating collector 4; the refrigerant is brought to the medium-pressure level of the heat pump.
  • the compression ejector 3 generates a pressure drop at the suction connection 3.3, as a result of which refrigerant is sucked out of the evaporator 5 (via its outlet 5.2).
  • a control valve 13.1 is connected in parallel with the (non-controllable) compression ejector 3.
  • the turbo compressor unit 1 From the first outlet 4.2 of the separating collector 4, which is usually connected to the gaseous phase of the refrigerant, refrigerant is sucked in by the turbo compressor unit 1. From the second outlet 4.3 of the separating collector 4, which is connected to the liquid phase of the refrigerant, occurs as a result of a pressure drop (the evaporator 5 is at the low-pressure level of the heat pump) refrigerant, is expanded via the throttle valve 6 from the medium-pressure level to the low-pressure level and finally reaches the evaporator 5 (via its inlet 5.1). In the evaporator, the refrigerant absorbs heat while cooling the environment (represented schematically by the arrows labeled "WQA" and "WQE").
  • a single-stage heat pump is shown using a flooded evaporator and a semi-hermetic or hermetic turbo-compressor unit 1 .
  • the flooded evaporator consists of the evaporator 5 and a separating collector 7 arranged above the evaporator.
  • the separating header 7 arranged above the evaporator has not just one but two outlets which are connected to the liquid refrigerant.
  • One of the outlets of the separating collector 7, which is connected to the liquid refrigerant, is connected to the inlet 5.1 and the other outlet is connected to the outlet 5.2 of the evaporator 5.
  • the term "flooded evaporator" comes from the fact that the level of the entire liquid level (in the separating header 7) of the refrigerant is above the evaporator 5,
  • the semi-hermetic or hermetic turbo-compressor unit consists of a turbo-compressor 8, a drive motor 9 and a housing 10 which surrounds the drive motor 9 and the turbo-compressor 8.
  • the interior of the housing 10 and the drive motor 9 are sealed off from the refrigerant circuit by means of a shaft seal 11 (which separates the turbo compressor 8 from the drive motor 9).
  • the pressure connection 12.1 of the suction ejector 12 is connected to the outlet 2.2 of the gas cooler 2 and the outlet 12.2 of the suction ejector 12 is connected to the outlet 5.2 of the evaporator 5.
  • a control valve 13.2 is connected in parallel with the (non-controllable) suction ejector 12.
  • the external compressor 15 is used to extract refrigerant that accumulates after long downtimes of the heat pump inevitably collects in the housing 10.
  • the external compressor 15 can also be operated during operation to support or replace the suction ejector 12 .
  • FIG. 3 shows a two-stage heat pump in which the first compressor stage is designed as compression ejector 3 (according to the in 1 circuit shown) and the second compressor stage is realized as a semi-hermetic or hermetic turbo compressor unit, the turbo compressor 8 being separated from the drive motor 9 by means of a shaft seal 11 and the housing 10 being sucked off by means of the suction ejector 12 (according to the in 2 shown circuit).
  • a separator collector 4 is used, in which the first outlet 4.2 is connected to the gaseous phase and the second outlet 4.3 is connected to the liquid phase of the refrigerant.
  • a separating header 7 arranged above the evaporator (as in the case of Fig 2 shown, flooded evaporator) are used.
  • Both the compression ejector 3 and the suction ejector 12 are not designed to be adjustable and are each provided with a control valve 13.1, 13.2 connected in the bypass.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Claims (6)

  1. Pompe à chaleur, avec au moins un premier étage de compresseur, qui est conçu pour augmenter la pression régnant dans le réfrigérant d'un niveau de basse pression à un niveau de moyenne pression ; avec au moins un deuxième étage de compresseur, qui est conçu pour augmenter la pression régnant dans le réfrigérant d'un niveau de moyenne pression à un niveau de haute pression; avec au moins un refroidisseur de gaz (2) ou un condenseur fonctionnant au niveau de haute pression de la pompe à chaleur, le au moins un refroidisseur de gaz (2) ou condenseur ayant une entrée (2.1) et une sortie (2.2); avec au moins un évaporateur (5) fonctionnant au niveau de basse pression de la pompe à chaleur, qui comprend une entrée (5.1) et une sortie (5.2); avec un collecteur séparateur (4) fonctionnant au niveau de moyenne pression de la pompe à chaleur, qui sert à séparer et à collecter le réfrigérant liquide et qui dispose d'une entrée (4.1), d'une première sortie (4.2) ainsi que d'une deuxième sortie (4.3) communiquant avec le réfrigérant liquide; et avec au moins une vanne papillon (6) qui est montée entre la deuxième sortie (4.3) du collecteur séparateur (4) et l'entrée (5.1) de l'au moins un évaporateur (5) et qui sert à détendre le réfrigérant du niveau de moyenne pression au niveau de basse pression de la pompe à chaleur, l'au moins un premier étage de compresseur étant réalisé sous la forme d'au moins un éjecteur de compression (3) qui dispose d'un raccord de pression (3.1), une sortie (3.2) et un raccord d'aspiration (3.3), dans lequel, lors du fonctionnement de l'au moins un éjecteur de compression (3), du réfrigérant pénètre dans l'au moins un éjecteur de compression (3) par le raccord de pression (3.1), s'écoule sous forme de jet dans l'au moins un éjecteur de compression (3), ce qui produit une baisse de pression au raccord d'aspiration (3.3), et sort par la sortie (3.2) de l'au moins un éjecteur de compression (3), caractérisé en ce que
    - le réfrigérant utilisé est l'ammoniac, et la pompe à chaleur est configurée comme une pompe à chaleur à haute température, la différence de pression entre l'ammoniac du côté basse pression et l'ammoniac du côté haute pression étant d'au moins 35 bars.
  2. Pompe à chaleur selon la revendication 1, caractérisée en ce que l'éjecteur de compression (3) est réalisé de manière réglable ou la vanne de régulation (13.1) est montée en parallèle avec l'éjecteur de compression (3) ou la vanne de régulation (13.1) est montée en série avec l'éjecteur de compression (3).
  3. Pompe à chaleur selon l'une des revendications 1 ou 2, caractérisée en ce qu'elle comprend au moins un échangeur de chaleur interne qui est adapté pour transférer la chaleur du réfrigérant sortant de l'au moins un refroidisseur de gaz (2) ou condenseur au gaz d'aspiration ou pour chauffer le gaz d'aspiration à partir d'une source de chaleur externe supplémentaire.
  4. Pompe à chaleur selon l'une des revendications 1 à 3, caractérisée en ce que, lors du fonctionnement de la pompe à chaleur, le réfrigérant est supercritique du côté haute pression.
  5. Pompe à chaleur selon l'une des revendications 1 à 4, caractérisée en ce que l'au moins un éjecteur de compression (3) est réalisé à plusieurs étages.
  6. Pompe à chaleur selon l'une des revendications 1 à 5, caractérisée en ce que l'évaporateur (5) est conçu comme un évaporateur noyé.
EP12184177.9A 2011-09-14 2012-09-13 Pompe à chaleur avec éjecteur Active EP2570753B1 (fr)

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DE102011053594 2011-09-14

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EP2570753A2 EP2570753A2 (fr) 2013-03-20
EP2570753A3 EP2570753A3 (fr) 2015-07-08
EP2570753B1 true EP2570753B1 (fr) 2022-06-08

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EP3862657A1 (fr) 2020-02-10 2021-08-11 Carrier Corporation Système de réfrigération comportant plusieurs échangeurs de chaleur absorbant la chaleur
CN112880221B (zh) * 2021-01-14 2021-11-30 山东大学 一种中低温热源驱动的功冷气联供系统
DE102022100491A1 (de) 2022-01-11 2023-07-13 Schaeffler Technologies AG & Co. KG Ejektor
DE102022125806A1 (de) 2022-10-06 2024-04-11 Man Energy Solutions Se System zur Wasserelektrolyse unter Verwendung einer Wärmepumpe zur Nutzung von bei der Wasserelektrolyse entstehender, thermischer Energie
DE202022107104U1 (de) * 2022-12-20 2023-03-01 Technische Universität Chemnitz, Körperschaft des öffentlichen Rechts Anlage zur Erzeugung von Eis, Eisbrei/Eispartikeln, Schnee, Hydraten, Kaltwasser oder deren Kombinationen bzw. Mischung/Suspension in einem geschlossenen Prozess

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JP4075530B2 (ja) * 2002-08-29 2008-04-16 株式会社デンソー 冷凍サイクル
JP4069880B2 (ja) * 2004-02-18 2008-04-02 株式会社デンソー エジェクタ
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US20100313582A1 (en) * 2009-06-10 2010-12-16 Oh Jongsik High efficiency r744 refrigeration system and cycle

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