EP2570753A2 - Pompe à chaleur avec éjecteur - Google Patents

Pompe à chaleur avec éjecteur Download PDF

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Publication number
EP2570753A2
EP2570753A2 EP12184177A EP12184177A EP2570753A2 EP 2570753 A2 EP2570753 A2 EP 2570753A2 EP 12184177 A EP12184177 A EP 12184177A EP 12184177 A EP12184177 A EP 12184177A EP 2570753 A2 EP2570753 A2 EP 2570753A2
Authority
EP
European Patent Office
Prior art keywords
heat pump
refrigerant
outlet
ejector
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12184177A
Other languages
German (de)
English (en)
Other versions
EP2570753A3 (fr
EP2570753B1 (fr
Inventor
Steffen Oberländer
Eberhard Wobst
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.)
Engie Refrigeration GmbH
Original Assignee
Thermea Energiesysteme GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Thermea Energiesysteme GmbH filed Critical Thermea Energiesysteme GmbH
Publication of EP2570753A2 publication Critical patent/EP2570753A2/fr
Publication of EP2570753A3 publication Critical patent/EP2570753A3/fr
Application granted granted Critical
Publication of EP2570753B1 publication Critical patent/EP2570753B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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 refrigerating machine (which can also be operated in refrigeration and heat coupling) with at least one ejector, occur due to the operating conditions high pressure differences between the high and the low pressure side.
  • Heat pumps and chillers transport heat from a low temperature level to a higher one at the expense of work. They differ only in the temperature levels achieved during operation (heat pumps usually have a higher temperature level than chillers, while chillers have a lower temperature level) and which sides are used (heat pump: warm side; chiller cold side; Heat-cold-coupling: hot and cold side).
  • heat pump is therefore generally used below for the terms “heat pump / chiller / heat-cold-coupling”.
  • two-stage (also multi-stage) heat pumps are used, for which there are numerous implementation options based on two-stage compressor or the series connection of two compressors.
  • an intermediate cooling is used in order to keep the compression end temperature within the permissible limits.
  • the ejector thus acts as the first compressor stage.
  • a usually oil-lubricated compressor conveys the refrigerant from the collector into the gas cooler and brings the refrigerant to high pressure level (second compressor stage). Intercooling is not required because the compressor draws in saturated refrigerant from the separator collector. However, a technical solution for the required oil return is not specified.
  • the invention has for its object to provide a two-stage high-temperature heat pump in which high pressure differences between the high and the low pressure side occur due to the operating conditions and can be achieved with the high COP values.
  • the starting point is an at least two-stage heat pump with at least one first compressor stage, which is set up to increase the pressure prevailing in the refrigerant from a low-pressure to a medium-pressure level, and with at least one second compressor stage which leads to an increase in the pressure prevailing in the refrigerant Medium pressure to a high pressure level on which the refrigerant is preferably present supercritical, is set up.
  • the heat pump further comprises at least one gas cooler operated at the high pressure level of the heat pump (or a condenser, when the refrigerant used becomes liquid in the operation of the heat pump on the high pressure side), wherein the at least one gas cooler or the condenser has an inlet and an outlet, a driven at the low pressure level of the heat pump, at least one evaporator having an inlet and an outlet, at least one throttle valve which is connected between the second outlet of a collector and the inlet of the at least one evaporator and the relaxation of the refrigerant from the medium pressure level to the low pressure level the heat pump is used, as well as operated at the medium pressure level of the heat pump separation collector.
  • at least one internal heat exchanger can be used, with the heat from the transfer refrigerant exiting at least one gas cooler / condenser to the suction gas or heated suction gas from an additional external heat source.
  • the collector is used for separating and collecting liquid refrigerant, d. h., in addition to its function as a separator, it also serves to store excess refrigerant. Accordingly, the separator collector contains liquid and gaseous refrigerant, and when a large amount of refrigerant is stored in the collector, the ratio of the liquid refrigerant is high and, if a small amount of refrigerant is stored in the collector, the proportion of the liquid refrigerant is correspondingly smaller.
  • the separator collector has an inlet, a first outlet which communicates with the gaseous refrigerant, and a second outlet which adjoins the liquid refrigerant.
  • the at least one first compressor stage is realized as at least one compression ejector and the at least one second compressor stage is realized as at least one oil-free turbocompressor unit.
  • Both the at least one compression ejector and the at least one turbocompressor unit can be constructed from a plurality of serially and / or parallel connected individual compression ejectors or turbocompressor units.
  • 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 in a jet shape (eg by means of nozzles) through the at least one compression ejector and exits through the outlet of the at least one compression ejector.
  • the jet thus formed generates a pressure reduction at the suction connection (analogous to a water jet pump), whereby gaseous refrigerant is sucked out of the at least one evaporator.
  • the pressure prevailing in the refrigerant increases, as a result of which 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 made controllable, d. h., Its flow resistance is continuously or in stages changeable. Then, an optimal flow through the compression ejector can be achieved in the entire working field of the heat pump, without that, due to excessive flow resistance of the compression ejector, too high pressures can occur on the high pressure side.
  • compression ejectors with controllable flow resistances are comparatively complicated and expensive due to the design.
  • more cost-effective compression ejectors can be used with a fixed flow resistance.
  • a compression ejector with a comparatively high flow resistance can be used, to which a control valve (as bypass) is connected in parallel, 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 at the ejector bypassed), or a Verdichtungsejektor with a series-connected control valve can be used, wherein the Verdichtungsejektor has a small flow resistance, that (with fully open control valve) caused by the flow resistance of the ejector pressure overshoot on the high pressure side of the heat pump can be excluded.
  • the variant with the control valve in bypass has the advantage that the ejector always the full pressure difference is applied, but the refrigerant flow is temporarily not fully used due to the bypass.
  • the variant with the serial control valve has the advantage that always the entire refrigerant flow is used by the ejector, but has the disadvantage that at least temporarily not the entire pressure difference is applied to the ejector.
  • the integration of the at least two compressor stages is realized in that in each case the suction connection of the at least one compression ejector with the outlet of the at least one evaporator, the pressure port of the at least one Verdichtungsejektors directly or via a control valve with the Outlet of the at least one gas cooler (or the condenser) or the at least one inner heat exchanger and the outlet of the at least one Verdichtungsejektors is connected to the entrance of the collecting 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).
  • a high temperature heat pump with a high pressure difference (between the high pressure side below the low pressure side), e.g. greater than 35 bar (typically 50 to 80 bar), use an ejector in conjunction with ammonia as the refrigerant (ammonia high-temperature variant).
  • the at least one compression ejector completely recovers the energy required for operation from the circulating (in the cycle) refrigerant, ie no energy requirement causes (oil-free and ammonia high-temperature variant), and possibly the refrigerant circuit of the heat pump is realized oil-free (only oil-free variant) , whereby an undesirable heat transfer is avoided by the return of separated oil, high COP values and greater thermal performance can be achieved with the heat pump according to the invention.
  • oil-free only oil-free variant
  • Multi-stage ejectors are distinguished from comparable single-stage ejectors by higher pumping powers (pressure ratio).
  • turbo compressor units As oil-free compressors (in the oil-free variants) preferably turbo compressor units are used, which are operated at speeds of 15,000 to 200,000 revolutions per minute (rpm) and which are carried out semi-hermetically, d. h., The compressor and the associated drive motor are each housed in a sealed by means of detachable connections housing.
  • turbocharger units of higher performance tend to operate at lower (eg, 15,000 to 50,000 rpm) and turbo-compressor units with lower powers tend to operate at higher speeds (eg, 45,000 to 200,000 rpm).
  • both the compressor and the drive motor are under a refrigerant atmosphere.
  • a refrigerant such as carbon dioxide, which has high densities as gas and a compressor that operates at high speeds (turbo compressor unit with a speed greater than 15,000 rev / min) used, high frictional forces would occur, on the one hand, an increase in the required drive energy (COP reduction) and on the other hand impermissibly high compressor temperatures (unacceptably high heat input into the refrigerant circuit) would result. It has been shown in practice that the operation of turbocompressors with carbon dioxide as refrigerant under these conditions is hardly practical or even impossible.
  • the drive motor by means of a shaft seal against the refrigerant circuit, in which the at least one compressor is integrated, sealed off.
  • shaft seals for shafts that rotate at high speeds, eg. B. greater than 15,000 rev / min, rotate to produce with sufficiently low leakage rates.
  • the case In order to prevent the case from filling up with refrigerant (carbon dioxide) after a certain period of time, the case has a suction connection over which (due to the unavoidable Leakages of the shaft seal) in the housing passing refrigerant by means of a compressor or a pump (hereinafter referred to as pump) sucked and fed back into the refrigeration cycle.
  • pump a pump
  • the suction port is connected to the housing.
  • the outlet of the suction ejector is connected to the suction connection of the at least one compression ejector, and the pressure connection of both the at least one compression and the 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 a suction ejector with a fixed flow resistance can be used, which is connected either in parallel (bypass) or serially with a control valve.
  • refrigerant can only be sucked out of the housing during operation of the heat pump.
  • the leakage rate of the shaft seal of the at least one turbocompressor unit will decrease when the shaft is stationary, it can not be completely ruled out that, in particular during prolonged downtimes, refrigerant enters the housing. If the pressure of the refrigerant in the housing is high, then frictional forces may occur in the at least one semi-hermetic or hermetic turbocompressor unit that requires a restart without additional measures prevent.
  • the refrigerant that has accumulated in the housing during the standstill of the heat pump can be removed from the housing by means of three methods before or during the restart of the heat pump.
  • the heat pump in addition to the Absaugejektor be equipped with an external single or multi-stage compressor whose suction port is connected to the housing.
  • the external compressor is switched on and the refrigerant is pumped out of the housing back into the circuit.
  • the external compressor can also be operated during operation instead of or in support of the suction ejector
  • the heat pump may be equipped with a control unit that allows a slow restart (slow increase in speed) of the at least one semi-hermetic or hermetic turbo-compressor unit of the heat pump after downtime.
  • a slow restart slow increase in speed
  • the pumping power of the suction ejector increases, and it returns the refrigerant from the housing into the refrigeration cycle.
  • the increase in the speed of the at least one turbocompressor unit must be so slow that the refrigerant is largely removed from the housing before the at least one turbocompressor unit has reached its maximum speed.
  • the heat pump comprises a control unit and the housing has an opening to the environment, which is closed by means of a controllable valve. Before restarting the heat pump, 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 the refrigerant losses over a longer operating period.
  • the two-stage heat pump shown in FIG. 1 conveys the semi-hermetic or hermetic turbocompressor unit 1 refrigerant into the gas cooler 2 where the refrigerant is cooled by releasing heat (indicated schematically by the arrows marked "WWA” and "WWE” in the drawing). If the refrigerant condenses, not the term gas cooler but the term condenser is used; In the following, the term gas cooler is always used for the sake of simplicity.
  • the pressure of the refrigerant is raised to the high pressure level of the heat pump.
  • the refrigerant From the outlet 2.2 of the gas cooler 2, the refrigerant enters the pressure port 3.1 of the compression ejector 3, exits from the outlet 3.2 as a jet and enters the inlet 4.1 of the collector 4; The refrigerant is thereby brought to the medium pressure level of the heat pump.
  • the compression ejector 3 generates a pressure reduction at the suction connection 3.3, as a result of which refrigerant (via its outlet 5.2) is sucked out of the evaporator 5.
  • the (non-controllable) compression ejector 3, a control valve 13.1 is connected in parallel.
  • Fig. 2 shows a single-stage heat pump, in which a flooded evaporator and a semi-hermetic or hermetic turbo compressor unit 1 are used.
  • the flooded evaporator is composed of the evaporator 5 and a collecting collector 7 arranged above the evaporator. Notwithstanding the collecting collector 4, the collecting collector 7 arranged above the evaporator not only has one but two outlets, which communicate with the liquid refrigerant. One of the outlets of the collecting collector 7, which is connected to 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" is due to the fact that the level of the entire liquid level (in the separation collector 7) of the refrigerant is above the evaporator 5,
  • the semi-hermetic or hermetic turbocompressor unit consists of a turbocompressor 8, a drive motor 9 and a housing 10, which surrounds the drive motor 9 and the turbocompressor 8.
  • the interior of the housing 10 and the drive motor 9 are isolated 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 for suction of refrigerant, which is after longer periods of downtime of the heat pump inevitably collects in the housing 10.
  • the external compressor 15 may also be operated during operation to assist or replace the suction ejector 12.
  • Fig. 3 shows a two-stage heat pump, in which the first compressor stage as compression ejector 3 (corresponding to the in Fig. 1
  • the second compressor stage is realized as a semi-hermetic or hermetic turbo-compressor unit, wherein the turbo-compressor 8 is separated from the drive motor 9 by means of a shaft seal 11 and the housing 10 is sucked off by means of the suction ejector 12 (corresponding to the one in FIG Fig. 2 shown circuit).
  • a separator collector 4 is used in which the first outlet 4.2 is in communication with the gaseous phase and the second outlet 4.3 is in communication with the liquid phase of the refrigerant.
  • a collecting collector 7 arranged above the evaporator (as in FIG Fig. 2 shown, flooded evaporator) can be used.
  • Both the compression ejector 3 and the suction ejector 12 are not designed to be adjustable and each provided with a control valve connected in the bypass 13.1, 13.2.

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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)
EP12184177.9A 2011-09-14 2012-09-13 Pompe à chaleur avec éjecteur Active EP2570753B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011053594 2011-09-14

Publications (3)

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

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP12184177.9A Active EP2570753B1 (fr) 2011-09-14 2012-09-13 Pompe à chaleur avec éjecteur

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EP (1) EP2570753B1 (fr)
DK (1) DK2570753T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110469376A (zh) * 2019-08-29 2019-11-19 中国船舶重工集团公司第七一九研究所 布雷顿循环发电系统及方法
CN112880221A (zh) * 2021-01-14 2021-06-01 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
US11754320B2 (en) 2020-02-10 2023-09-12 Carrier Corporation Refrigeration system with multiple heat absorbing heat exchangers
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

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10332104A1 (de) 2002-07-16 2004-01-29 Denso Corp., Kariya Kältemittelkreislauf mit einem Ejektor
DE102009020062A1 (de) 2008-05-12 2009-12-31 DENSO CORPORATION, Kariya-shi Kältmitttelkreislaufvorrichtung mit Ejektor
DE112009000608T5 (de) 2008-04-18 2011-05-19 Denso Corporation, Kariya-City Kälteerzeugungszyklusvorrichtung eines Ejektor-Typs

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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
JP2009133624A (ja) * 2005-03-14 2009-06-18 Mitsubishi Electric Corp 冷凍空調装置
DE102008024772B4 (de) * 2007-05-25 2018-05-03 Denso Corporation Kältemittelkreislaufvorrichtung mit einem zweistufigen Kompressor
JP4577365B2 (ja) * 2008-01-21 2010-11-10 株式会社デンソー エジェクタを用いたサイクル
US20100313582A1 (en) * 2009-06-10 2010-12-16 Oh Jongsik High efficiency r744 refrigeration system and cycle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10332104A1 (de) 2002-07-16 2004-01-29 Denso Corp., Kariya Kältemittelkreislauf mit einem Ejektor
DE112009000608T5 (de) 2008-04-18 2011-05-19 Denso Corporation, Kariya-City Kälteerzeugungszyklusvorrichtung eines Ejektor-Typs
DE102009020062A1 (de) 2008-05-12 2009-12-31 DENSO CORPORATION, Kariya-shi Kältmitttelkreislaufvorrichtung mit Ejektor

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110469376A (zh) * 2019-08-29 2019-11-19 中国船舶重工集团公司第七一九研究所 布雷顿循环发电系统及方法
CN110469376B (zh) * 2019-08-29 2024-01-16 中国船舶重工集团公司第七一九研究所 布雷顿循环发电系统及方法
US11754320B2 (en) 2020-02-10 2023-09-12 Carrier Corporation Refrigeration system with multiple heat absorbing heat exchangers
CN112880221A (zh) * 2021-01-14 2021-06-01 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

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Publication number Publication date
EP2570753A3 (fr) 2015-07-08
EP2570753B1 (fr) 2022-06-08
DK2570753T3 (da) 2022-09-12

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