EP2602571A1 - Dispositif de pompe à chaleur réversible et son procédé de fonctionnement - Google Patents

Dispositif de pompe à chaleur réversible et son procédé de fonctionnement Download PDF

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Publication number: EP2602571A1
Authority: EP; European Patent Office
Prior art keywords: heat exchanger; flow; expansion valve; compressor; hot water
Prior art date: 2011-12-06
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

EP12195447.3A

Other languages

German (de)

English (en)

Other versions

EP2602571B1 (fr

Inventor

Inga Troestler

Dennis Pfeil

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.)

Robert Bosch GmbH

Original Assignee

Robert Bosch 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.)

2011-12-06

Filing date

2012-12-04

Publication date

2013-06-12

2012-12-04 Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH

2013-06-12 Publication of EP2602571A1 publication Critical patent/EP2602571A1/fr

2014-09-17 Application granted granted Critical

2014-09-17 Publication of EP2602571B1 publication Critical patent/EP2602571B1/fr

Status Not-in-force legal-status Critical Current

2032-12-04 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
- 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
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel 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
- 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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
- 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
- F25B2400/075—Details of compressors or related parts with parallel compressors
- F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities

Definitions

the invention relates to a reversible heat pump device according to the preamble of claim 1, and a method for their operation according to claim 5.
thermodynamic principle of the heat pump is well known and is commonly used for heating or for cooling Tempertechnischsdusen, such as in refrigerators, air conditioners or brine heat pumps.
a heat pump has a first heat exchanger for heat absorption and a second heat exchanger for heat dissipation.
the heat exchangers are fluidly connected to each other via two connecting lines and thus form a circuit for refrigerant.
a compressor and in the other an expansion valve is arranged in one of the connecting lines.
One of the heat exchangers lies in the flow direction of the refrigerant behind the compressor and one behind the expansion valve.
the refrigerant Upon activation of the compressor, the refrigerant is compressed by means of the compressor, whereby the temperature of the compressed refrigerant increases. As it flows through the adjoining heat exchanger, the warm refrigerant gives off heat. On the other side of the heat exchanger, the refrigerant is relieved by a throttle. This lowers the temperature of the expanded refrigerant so that the refrigerant in this heat exchanger can absorb heat from a heat source. The more the refrigerant is released, the lower the temperature of the heat source can be, for example the interior of a freezer.
the heat pump process for heating and for cooling a tempering object, for example a building
the heat absorption and output of the heat exchanger reverses depending on the flow direction of the refrigerant.
One of the heat exchangers then corresponds to the air conditioning, for example, with the building and a periphery outside the building.
the heat pump device in addition to the heating and cooling of the building for supplying a further heating object with heat.
water can be heated simultaneously.
Another problem is that for the warming of hot water actually a different temperature level is necessary than that at the heat-emitting heat exchanger usually present.
hot water is heated more strongly, for example to 55 ° C, than the flow of building heating in winter, for example 45 ° C.
the different temperature requirements are not taken into account in the prior art, whereby the efficiency of the reversible heat pump device is not optimal.
even a further device for supplementary reheating of the hot water is required.
the object of the invention is therefore to eliminate the deficiencies of the prior art and to provide a reversible heat pump device with adapted cooling or heating power in summer or winter, wherein the heat pump device should also be suitable for heating a further heating object, in particular for heating of hot water, and wherein the different temperature level of the additional heating object is taken into account so that the efficiency of the heat pump device is high.
the heat pump device should be simple and inexpensive to produce, as well as uncomplicated and safe to operate.
the invention relates to a reversible heat pump apparatus having a main circuit for a refrigerant, which consists of a main compressor line with a main compressor and an expansion valve line with a first expansion valve, wherein a peripheral heat exchanger and an air-heat exchanger are arranged in the main circuit, wherein a second expansion valve serially is arranged to the first expansion valve in the expansion valve line, and wherein a hot water heat exchanger via a flow with an additional compressor and via a return flow with a third expansion valve to the main circuit is flow-connected, wherein the flow to the main compressor line is flow-connected, and wherein the return between the first and second expansion valve is flow-connected to the expansion valve line.
the main circuit As a function of the conveying direction of the main compressor for cooling or for heating a temperature-controlled object assigned to the air-conditioning heat exchanger.
the main compressor should be bidirectional. A technical possibility to achieve this is to form the monodirectional compressor with a multi-way valve with reverse loop.
the air conditioning heat exchanger should thus therefore correspond to a Temper michsfect
the Temper michsfect is preferably a building.
the hot water heat exchanger should correspond with a hot water preparation device.
the latter can have, in addition to a hot water tank, an additional conventional heating device, for example one powered by electricity or gas.
connection of the hot water heat exchanger to the main circuit is made possible in particular by the second expansion valve according to the invention in the expansion valve line.
the two expansion valves in the main circuit should be openable for this purpose, for example by means of an openable valve bypass.
each of these expansion valves would then be open in the pressurized line section of the main circuit in heating and cooling operation.
the heat exchanger of the main circuit are defined for the intended use as air-heat exchanger and peripheral heat exchanger.
the main compressor and the auxiliary compressor may be connected in series. That is, part of the refrigerant is compressed in two stages. The slightly higher required temperature level in the hot water heat exchanger is thus achieved by the additional compression with the additional compressor.
cooling mode In cooling mode, the temperature difference between air conditioning heat exchanger and hot water heat exchanger is much lower than in heating mode. Therefore, in the cooling mode, a single-stage compression by the auxiliary compressor is sufficient to heat the hot water. In cooling mode, the two compressors are therefore connected in parallel. By controlling the amount of refrigerant delivered by the additional compressor, the heat can be distributed to the peripheral heat exchanger and the hot water heat exchanger, depending on the amount of heat required for hot water production.
a particular advantage of the heat pump device is that the necessary in summer high cooling capacity is not completely discharged to the periphery, but large parts of this heat can be used for heating the hot water.
the peripheral heat exchanger will usually correspond with an environment, in particular the environment of a building. For this purpose, both the air space and the soil are counted.
the third expansion valve in the return flow should be able to be opened or closed by the hot water heat exchanger.
an additional closure valve could be placed in the return.
a closable valve for example a second closing valve, should also be arranged in the supply line.
a development of the invention provides that in the flow connection between the return of the hot water heat exchanger and the expansion valve line, a medium-pressure cylinder is arranged.
a medium-pressure bottle essentially forms a cavity in which in the operation of the heat pump device at an expansion valve expanded refrigerant separates into a gas and a condensate phase.
the return of the warm water heat exchanger should be flow-connected to a geodetically upper region of the medium-pressure cylinder.
This area of the medium-pressure bottle is the one in which the refrigerant is in gas phase.
the expansion valve line should be flow-connected to a geodetically lower area of the medium-pressure cylinder. Due to the higher density, the medium-pressure bottle collects the liquid refrigerant in this area.
a controllable flow valve is arranged in the flow of the hot water heat exchanger between the additional compressor and the flow connection with the main compressor line.
the amount of the refrigerant which is sucked by the booster compressor be regulated.
the flow valve thus allows particularly well the control of the heat consumption through the hot water heat exchanger.
it is suitable to completely separate the flow from the main circuit when the booster compressor is deactivated. An additional valve in the flow is therefore unnecessary.
the flow and the return of the hot water heat exchanger are flow-connected via a bypass with a control valve, wherein the bypass is flow-connected to the flow between the auxiliary compressor and the flow connection with the main compressor line, and wherein the bypass with the return between the third expansion valve and the flow connection with the expansion valve line is fluidly connected.
a cooling of the refrigerant can take place before the additional compressor. This is particularly useful in heating mode to reduce the suction gas temperature and thus the compression temperature of the additional compressor.
the refrigerant in front of the additional compressor is gaseous and also in the return behind the third expansion valve, the refrigerant has a gaseous form.
the refrigerant from the return line has already been cooled in the hot water heat exchanger and can thus be metered as steam into the flow before the additional compressor (Vapor injection).
the auxiliary compressor is protected against overheating by the intermediate steam injection.
bypass should be flow connected to the flow between the auxiliary compressor and the flow valve.
control valve should be closable, since advantages are achieved with the intermediate vapor injection, in particular in heating operation with the two-stage compression.
the main compressor and the additional compressor act in opposite directions, so that the refrigerant already has a very low temperature before the additional compressor.
the bypass could also be connected to the geodetically upper region of the medium-pressure cylinder, because functionally, the line section adjoining the upper region of the medium-pressure bottle up to the third expansion valve is an extension of this upper region.
the main circuit can be used for cooling or for heating the temperature-controlled object, preferably a building, associated with the air-conditioning heat exchanger.
the main compressor should be bidirectional. A technical possibility to achieve this is to form a reverse loop with a multi-way valve. In order to switch between a heating mode and a cooling mode, so the main compressor must be switched. For example, this is possible by reversing the direction of flow or by means of the described multi-way valve.
auxiliary compressor At the same time can be heated by activation of the auxiliary compressor with a heat demand of the hot water. If the heat for hot water preparation is insufficient, an additional conventional heating device, for example one operated with electricity or gas, could be added.
the main compressor and the auxiliary compressor are connected in series. That is, part of the refrigerant is compressed in two stages. The slightly higher required temperature level in the hot water heat exchanger is thus achieved by the additional compression with the additional compressor.
cooling mode In cooling mode, the temperature difference between air conditioning heat exchanger and hot water heat exchanger is much lower than in heating mode. Therefore, in the cooling mode, a single-stage compression by the auxiliary compressor is sufficient to heat the hot water. In cooling mode, the two compressors are therefore connected in parallel. By regulating the amount of refrigerant delivered by the additional compressor, the heat can be distributed to the peripheral heat exchanger and the hot water heat exchanger, depending on the amount of heat required for hot water production.
a particular advantage of the heat pump device is that the necessary in summer high cooling capacity is not completely discharged to the periphery, but large parts of this heat can be used for heating the hot water. Only the excess amount of heat that can not be used to heat water, is discharged through the periphery heat exchanger to the periphery.
the third expansion valve in the return flow from the hot water heat exchanger should also be able to be opened or closed.
an additional closure valve could be placed in the return. An additional method step would then provide that the third expansion valve or the additional closing valve is closed when the auxiliary heating program is deactivated.
a closable valve for example a second closing valve, should also be arranged in the supply line.
an additional method step would then provide for the second closure valve to be closed in the flow when the auxiliary heating program is deactivated.
the heat up or down respectively leads to a decrease or increase in the temperature of the refrigerant flowing through the respective heat exchanger, as well as a heating or cooling of the associated heat exchanger opposite side, that is to say the temperature object, the environment and the hot water.
the amount of the refrigerant which is sucked by the booster compressor be regulated.
This is particularly advantageous because the intake and the compression by means of the additional compressor can only be made limited by the latter itself.
the flow valve thus allows particularly well the control of the heat consumption through the hot water heat exchanger.
the method would include a step which provides for closing the flow valve when the auxiliary heating program is deactivated. An additional valve in the flow is therefore unnecessary.
a step is provided in the heating mode in which [a1c)] the pressures and / or the temperature of the refrigerant in the air conditioning and in the hot water heat exchanger is regulated by regulating the compression of the main compressor and / or the auxiliary compressor.
[a2c)] can control the pressures and / or the temperature of the refrigerant in the air-conditioning and hot-water heat exchangers by controlling the compression of the main compressor and / or the auxiliary compressor. Even in cooling mode, the heat demands are thus individually adaptable to the present tempering situation.
the refrigerant in front of the additional compressor is gaseous and also in the return behind the third expansion valve, the refrigerant has a gaseous form.
the refrigerant from the return has already been cooled in the hot water heat exchanger and can thus be metered as steam into the flow before the additional compressor (intermediate steam injection).
the auxiliary compressor is protected against overheating.
bypass should be flow connected to the flow between the auxiliary compressor and the flow valve.
control valve should be lockable, since advantages are achieved with the intermediate vapor injection only in heating operation with the two-stage compression. Accordingly, the control valve should be regulated in heating mode and closed in cooling mode.
the method could optionally also provide that closed in the cooling mode, the first expansion valve and the main compressor off, and the auxiliary compressor are activated so that all the heat is used for hot water.
the main compressor should then not be permeable, for example by a blocked multiway valve. A vapor intermediate injection is not required in this case.
Fig. 1 and Fig. 2 show a reversible heat pump apparatus 1 with a main circuit 2 for a refrigerant M, which consists of a main compressor line 211 with a bidirectional main compressor 21 and an expansion valve line 212 with a first expansion valve 31, in which a peripheral heat exchanger 11 and an air-heat exchanger 12 is arranged are.
a second expansion valve 32 is serially arranged to the first expansion valve 31 in the expansion valve passage 212. Both the first expansion valve 31 and the second expansion valve 32 are designed to be openable.
a hot water heat exchanger 13 via a feed line 131 with an additional compressor 22 and via a return 132 with a third expansion valve 33 to the main circuit 2 fluidly connected.
the third expansion valve 33 is designed to be closable.
the flow 131 is fluidly connected to the main compressor line 211, in particular between the main compressor 21 and the air-conditioning heat exchanger 12.
the return 132 is flow-connected to the expansion valve line 212 between the first and second expansion valves 31, 32.
the first expansion valve 31 is disposed between the periphery heat exchanger 11 and the second expansion valve 32.
peripheral heat exchanger 11 With an environment of the air-conditioning heat exchanger 12 with a Temper michsfect, wherein the Temper michsfect is preferably a building, and the hot water heat exchanger 13 with a hot water preparation device.
Fig. 3 and Fig. 4 show a reversible heat pump device 1 with a main circuit 2 for a refrigerant M, which consists of a main compressor line 211 with a main compressor 21 and an expansion valve line 212 with a first expansion valve 31.
a peripheral heat exchanger 11 and an air-conditioning heat exchanger 12 are arranged in the main circuit 2.
a second expansion valve 32 is serially arranged to the first expansion valve 31 in the expansion valve passage 212. Both the first expansion valve 31 and the second expansion valve 32 are designed to be openable, in particular in each case by means of a valve bypass 310, 320 with a closure valve 311, 321.
a hot water heat exchanger 13 via a feed line 131 with an additional compressor 22 and via a return 132 with a third expansion valve 33 to the main circuit 2 fluidly connected.
the third expansion valve 33 is designed to be closable.
the flow 131 is fluidly connected to the main compressor line 211, in particular between the main compressor 21 and the air-conditioning heat exchanger 12.
the return 132 is flow-connected to the expansion valve line 212 between the first and second expansion valves 31, 32.
the first expansion valve 31 is disposed between the periphery heat exchanger 11 and the second expansion valve 32.
a medium pressure cylinder 40 In the flow connection between the return 132 of the hot water heat exchanger 13 and the expansion valve line 212 is a medium pressure cylinder 40.
This essentially forms a cavity in which in the operation of the heat pump device 1 to the expansion valves 31, 32, 33 relaxed refrigerant M, into a gas phase G and a condensate phase F separates.
the medium-pressure bottle 40 is equipped with a maximum level limiter, not shown, with warning device for the liquid / the condensate F.
the return 132 of the hot water heat exchanger 13 is fluidly connected to a geodetically upper portion of the medium pressure cylinder 40. This area of the medium-pressure bottle M is the one in which the refrigerant M is in gas phase G.
the expansion valve line 212 is fluidly connected to a geodetically lower portion of the medium pressure bottle 40. Due to the higher density accumulates in this area of the medium-pressure cylinder 40 which is present as condensate / liquid F refrigerant M. Only schematically indicated is an intercepting plate 41 for intercepting entrained refrigerant droplets. This is only necessary if the pipeline of the bypass 60 is fluidly connected directly to the medium-pressure bottle 40. The larger the cross section of the conduit in the region of the intercepting plate 41, the lower the flow velocity of the refrigerant M, which makes it easier to intercept it. Therefore, the Abfangblech 41 sits in the geodesic upper portion of the medium-pressure bottle 40 and extends over the cross section.
a controllable flow valve 50 is arranged in the flow 131 of the hot water heat exchanger 13 between the additional compressor 22 and the flow connection with the main compressor line 211. With this, the amount of the refrigerant M sucked by the booster compressor 22 can be controlled. In addition, the flow valve 50 is closable so that it can separate the flow 131 from the main circuit 2.
a flow connection of the flow 131 and the return 132 of the hot water heat exchanger 13 via a bypass 60 with a control valve 61 can be seen.
the bypass 60 with the flow 131 between the booster compressor 22 and the flow connection with the main compressor line 211 is fluidly connected.
the other end of the bypass 60 is with the return 132 between the third Expansion valve 33 and the flow connection with the expansion valve line 212 fluidly connected.
the bidirectional main compressor 21 has the feature that it comprises a monodirectional compressor 213 and a multi-way valve 214 with reverse loop 215. By switching the multi-way valve 214, as indicated by the radial arrow in its center, the conveying direction of the monodirectional compressor 213 can be reversed.
Fig. 3 and Fig. 4 a correspondence of the peripheral heat exchanger 11 with an environment, the air-conditioning heat exchanger 12 with a Temper michsfect, wherein the Temper michsfect is preferably a building, and the hot water heat exchanger 13 with a hot water preparation device.

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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)

EP12195447.3A 2011-12-06 2012-12-04 Dispositif de pompe à chaleur réversible et son procédé de fonctionnement Not-in-force EP2602571B1 (fr)

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
DE102011120176A DE102011120176B4 (de)	2011-12-06	2011-12-06	Reversible Wärmepumpenvorrichtung sowie Verfahren zu deren Betrieb

Publications (2)

Publication Number	Publication Date
EP2602571A1 true EP2602571A1 (fr)	2013-06-12
EP2602571B1 EP2602571B1 (fr)	2014-09-17

Family

ID=47294740

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP12195447.3A Not-in-force EP2602571B1 (fr)	2011-12-06	2012-12-04	Dispositif de pompe à chaleur réversible et son procédé de fonctionnement

Country Status (2)

Country	Link
EP (1)	EP2602571B1 (fr)
DE (1)	DE102011120176B4 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP3336450A1 (fr) *	2016-12-09	2018-06-20	Lennox Industries Inc.	Circuit hvac et méthode d'opération d'un circuit hvac
WO2025210502A1 (fr) *	2024-04-03	2025-10-09	Turboden S.p.A.	Système pour pompe à chaleur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE102017100591B3 (de)	2017-01-13	2018-05-09	Hanon Systems	Kältemittelkreislauf, insbesondere für Kraftfahrzeuge mit Elektro- oder Hybridantrieb und Verfahren zum Betreiben des Kältemittelkreislaufes
NL2025130B1 (en) *	2020-03-13	2021-10-19	Air Supplies Holland B V	Climate control unit and system comprising the same

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CA2597372A1 (fr) *	2007-08-15	2009-02-15	Purdue Research Foundation	Systeme de thermopompe avec compression multietagee
EP2163838A1 (fr) *	2007-05-25	2010-03-17	Mitsubishi Electric Corporation	Dispositif à cycle de réfrigération
US20100083677A1 (en) *	2007-02-26	2010-04-08	Alexander Lifson	Economized refrigerant system utilizing expander with intermediate pressure port
EP2317251A1 (fr) *	2008-08-27	2011-05-04	Mayekawa Mfg. Co., Ltd.	Appareil de cycle pour pompe a chaleur avec compresseur a deux etages

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DD211847A1 (de) *	1982-11-19	1984-07-25	Inst Energetik Rational	Verfahren zur sekundaerenergienutzung
JP4459776B2 (ja) *	2004-10-18	2010-04-28	三菱電機株式会社	ヒートポンプ装置及びヒートポンプ装置の室外機
DE102011012644A1 (de) *	2011-02-28	2012-08-30	Gea Bock Gmbh	Kälteanlage

2011
- 2011-12-06 DE DE102011120176A patent/DE102011120176B4/de not_active Expired - Fee Related
2012
- 2012-12-04 EP EP12195447.3A patent/EP2602571B1/fr not_active Not-in-force

Patent Citations (4)

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Publication number	Priority date	Publication date	Assignee	Title
US20100083677A1 (en) *	2007-02-26	2010-04-08	Alexander Lifson	Economized refrigerant system utilizing expander with intermediate pressure port
EP2163838A1 (fr) *	2007-05-25	2010-03-17	Mitsubishi Electric Corporation	Dispositif à cycle de réfrigération
CA2597372A1 (fr) *	2007-08-15	2009-02-15	Purdue Research Foundation	Systeme de thermopompe avec compression multietagee
EP2317251A1 (fr) *	2008-08-27	2011-05-04	Mayekawa Mfg. Co., Ltd.	Appareil de cycle pour pompe a chaleur avec compresseur a deux etages

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP3336450A1 (fr) *	2016-12-09	2018-06-20	Lennox Industries Inc.	Circuit hvac et méthode d'opération d'un circuit hvac
US10520235B2 (en)	2016-12-09	2019-12-31	Lennox Industries Inc.	Method to avoid fan cycling during low ambient operation
US11353252B2 (en)	2016-12-09	2022-06-07	Lennox Industries Inc.	Method to avoid fan cycling during low ambient operation
WO2025210502A1 (fr) *	2024-04-03	2025-10-09	Turboden S.p.A.	Système pour pompe à chaleur

Also Published As

Publication number	Publication date
DE102011120176B4 (de)	2013-06-20
EP2602571B1 (fr)	2014-09-17
DE102011120176A1 (de)	2013-06-06

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DE2545606C2 (de)	1985-08-14	Verfahren zum Betrieb eines Kühlsystems sowie Kühlsystem zur Durchführung des Verfahrens
DE602004008450T2 (de)	2008-05-29	Dampfkompressionssystem mit bypass/economiser-kreisläufen
EP1914491B1 (fr)	2024-01-17	Installation de refroidissement
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