EP3071902B1 - Dispositif à fluide frigorigène pour l'augmentation du rendement thermodynamique - Google Patents

Dispositif à fluide frigorigène pour l'augmentation du rendement thermodynamique Download PDF

Info

Publication number
EP3071902B1
EP3071902B1 EP14824056.7A EP14824056A EP3071902B1 EP 3071902 B1 EP3071902 B1 EP 3071902B1 EP 14824056 A EP14824056 A EP 14824056A EP 3071902 B1 EP3071902 B1 EP 3071902B1
Authority
EP
European Patent Office
Prior art keywords
fluid
condenser
widening
bulge
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.)
Active
Application number
EP14824056.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3071902C0 (fr
EP3071902A1 (fr
Inventor
Frédéric BARBAN
Bruno DEBOUX
Pascal KALINOWSKI
Joëlle RIZK
Jimmy MORO-PEREZ
Gilles Castelain
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.)
Dynaes SAS
Original Assignee
Dynaes SAS
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 Dynaes SAS filed Critical Dynaes SAS
Publication of EP3071902A1 publication Critical patent/EP3071902A1/fr
Application granted granted Critical
Publication of EP3071902C0 publication Critical patent/EP3071902C0/fr
Publication of EP3071902B1 publication Critical patent/EP3071902B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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 invention relates to a heat pump, its use, and in particular the improvement of the thermodynamic efficiency of a heat pump.
  • Prior art has international demand WO20009004124 , a prior art device for producing heat, in a thermodynamic system, by circulating a fluid under pressure through a plurality of pipes in a bulge of a pipe of a heat pump in which the fluid is in gaseous form, between an exchanger and a compressor.
  • the present invention aims to overcome the drawbacks of the state of the art.
  • This heat pump comprises a closed circuit containing a refrigerant and a lubricant, the closed circuit comprising a fluid compressor and a fluid return circuit to the compressor, the compressor extending in the closed circuit between a fluid inlet and a fluid outlet, the return circuit extending in the closed circuit, complementary to the compressor, between the fluid outlet and the fluid inlet, the return circuit comprising a condenser, an expansion valve and an evaporator, said return circuit comprising a first pipe extending between the fluid outlet and the condenser, a second pipe extending between the condenser and the expansion valve, a third pipe extending between the expansion valve and the evaporator, and a fourth pipe extending between the evaporator and the fluid inlet, said closed circuit comprising a first bulge of a pipe of the return circuit containing tubing, the fluid comprising a mixture of a first freon R32 (di)
  • said refrigerant fluid is rising in the first bulge.
  • figure 1 schematically represents a heat pump according to an advantageous embodiment of the present invention.
  • the closed circuit comprises the fluid compressor 1 and a fluid return circuit to the compressor.
  • the compressor extends in the closed circuit between the fluid inlet and the fluid outlet, the return circuit extending in the closed circuit, complementary to the compressor, between the fluid outlet and the fluid inlet.
  • the return circuit comprises the condenser 2, the expansion valve 3 and the evaporator 4. Said return circuit thus comprises a first pipe extending between the fluid outlet and the condenser, a second pipe extending between the condenser and the expansion valve, a third pipe extending between the expansion valve and the evaporator, and a fourth pipe extending between the evaporator and the fluid inlet.
  • said closed circuit comprises a first bulge 5 of a return circuit pipe containing pipes 50, the fluid comprising a mixture of a first freon R32 (difluoromethane), a second freon R125 (pentafluoroethane) and a third freon R134a (1,1,1,2-tetrafluoroethane), and the lubricant comprises a synthetic polyolester oil.
  • FIG. 1 represents a heat pump provided with two pipe bulges: a first pipe bulge 5, with pipes 50, arranged between a fluid outlet of the compressor 1 of the pump and a condenser 2 of the pump and a second bulge 6 without pipes arranged between the condenser 2 and the expansion valve 3 of the pump.
  • the pump also has an evaporator 4.
  • a single bulge is also possible.
  • the invention can also be implemented with an AIRMEC ® heat pump of model reference ANF 50 with a power of 15kW or ANF 100 with a power equal to 35kW.
  • the invention is therefore not limited to a particular manufacturer or model.
  • the pump may use a set of copper pipes with an internal diameter of fourteen millimetres (14 mm) forming a closed circuit sealed against gases and liquids, the closed circuit being immersed in the atmosphere.
  • a compressor 1 of reference ZB38KCE having a fluid inlet and a fluid outlet.
  • the first tube bulge is formed, on a first 14 mm pipe, by a local increase in the internal diameter of the pipe or first bulge.
  • This first bulge 5 contains internal tubes 50, for example seven tubes with an internal diameter of 5 mm for an external diameter of 8.5 mm, surrounded by the first bulge of the pipe.
  • the internal diameter of the bulge is adapted to be able to enclose the tubes and the thickness of the bulge is adapted to support the maximum pressure specified for the fluid in this part of the pump.
  • the inner diameter of the bulge is for 7 tubes arranged compactly, equal to 3 times the outer diameter of a tube or approximately 25.5mm. For a larger number of tubes, this inner diameter of the bulge can be deduced as being the outer diameter of the tubes, compactly packed.
  • the same ratio between the diameter of the pipes and the diameter of the pipe will be chosen as that of this first embodiment, i.e. here a ratio equal to 14mm/5mm or 2.8.
  • the length of the pipes of the first bulge will be taken as approximately 22 cm for an original AERMEC ® pump and 13 cm for an original AIRWELL ® pump.
  • the condenser a known element, is encountered in the circuit following the first bulge.
  • the second bulge is designed to operate in the liquid phase for the refrigerant and the oil, it is for example identical to the first bulge but it may or may not include pipes, these not having been recognized as essential for obtaining the effect of the invention with the second bulge present in the circuit in addition to the first bulge.
  • the second bulge is followed, downstream, by the expansion valve.
  • the expansion valve is a known element, operating in the mainly liquid phase, at its inlet, and designed to produce a two-phase mixture of gas and liquid in the normal operation of the heat pump of the invention.
  • the expansion valve is followed downstream of the evaporator, a known element.
  • the pump In heating mode use, the pump is brought into contact at the evaporator with the atmosphere surrounding an enclosure to be heated and at the condenser with a heating circuit of the enclosure.
  • the pump In cooling mode operation, the pump is placed in contact at the evaporator with an enclosure to be cooled and at the condenser with the atmosphere surrounding the enclosure.
  • Known fluidic valves can allow switching on a user action from a heating mode to a cooling mode, if the pump according to the invention must be reversible.
  • freon chosen for all pumps is R407C or R407A freon and the oil is EMKARATE ® RL32-3 MAF oil, miscible with the chosen freon at all operating temperatures.
  • a refrigerant or cooling fluid and an oil which are miscible with each other will be used.
  • the family of refrigerant fluids consisting of freons with the name R407 and oils miscible with the freons of this family constitute in particular a set of fluids which can be used with the invention.
  • the general principle of the invention is considered at the date of the patent to be the ability to transport the oil of a heat pump, in the form of an emulsion of oil drops, suitable for increasing the heat exchanges in the condenser and in the evaporator of the pump.
  • the means of the invention which are the first and second bulges therefore tend to regenerate or maintain this emulsion in its form suitable for improving the operation of the heat exchangers (condenser and evaporator) of the pump.
  • drops taken as synonyms for bubbles (containing gas) in a gaseous transport medium or drops taken as synonyms for "antibubbles" (oil bubbles containing gas) in a liquid transport medium, is considered to provide nucleation sites for the condensation of the transport medium or for the evaporation of this medium, promoting heat exchanges, during its phase changes in the pump exchangers.
  • This emulsion is estimated, in the gas phase, to be a mist of droplets forming a "monodispersed" oil emulsion, in a gas phase (i.e. droplets whose diameter values are strongly centered on a common value) with a sufficient lifetime to reach the condenser and improve heat exchanges there.
  • the invention therefore uses a first means of forming an oil mist between the compressor and the condenser.
  • a particular means is thus a means of imposing a depression on drops of oil having absorbed a transport refrigerant gas due to the solubility of the gas in the oil and causing the appearance of gas bubbles in the drops capable of bursting into finer droplets.
  • This emulsion is estimated, in liquid phase, to be a mixture of oil droplets forming a "monodispersed" oil emulsion, in a liquid phase, of sufficient lifetime to reach the expander, pass through it, reach the evaporator and improve heat exchanges there, to finally return to the compressor regularly over time and in the form of an oil mist of regular oil droplet diameter and improve its isentropic efficiency by improved lubrication, compared to a commercial pump.
  • the invention thus uses, to improve the COP of a heat pump, a first means of forming an oil mist between the compressor and the condenser and a second means of forming a dispersion of oil drops in liquid phase between the condenser and the compressor, these drops being able to burst into droplets or bubbles when passing through the expansion valve and reaching the evaporator.
  • the elements of the invention namely the first tube bulge and the second bulge, can thus be adapted by those skilled in the art to achieve this goal.
  • thermodynamic efficiency or the COP of an entire heat pump using one or two bulges, a particular refrigerant and an oil miscible with the fluid was therefore not expected in the prior art.
  • the effect obtained makes it possible to envisage heating or cooling uses with a pump equipped with at least one bulge.
  • the first bulge is composed along its length, running through the closed circuit from the compressor fluid outlet on the first pipe joining the compressor fluid outlet to the condenser, of a first zone of increase in the internal diameter of the pipe, of a second zone of constant internal diameter of the pipe and of a third zone of reduction in the internal diameter of the pipe.
  • the change in diameter of the first zone can be carried out by a first cone whose apex angle allows, for the normal fluid operating conditions of the pump, to cause a separation of the current lines of the fluid flowing through the pump.
  • the change in diameter of the third zone can be carried out by a second cone whose apex angle allows, for the normal fluid operating conditions of the pump, not to cause a separation of the current lines of the fluid flowing through the pump.
  • the second zone of the first bulge will advantageously be arranged vertically, when the refrigerant is a mixture of freons and oil.
  • This zone will thus have a chimney arrangement or a chimney or vertical duct function for the first swelling, which normally operates with gaseous refrigerant and oil drops.
  • This arrangement will allow heat transfer to the condenser and not heat production not reaching the condenser by increasing the life of the freon emulsion and oil drops after the fluid has passed through the first bulge and allowing them to reach the condenser despite coalescence.
  • Such a vertical structure allows, for a soluble freon or a mixture of soluble freons in an oil present in drops transported with the gas, numerous simultaneous effects resulting in creating or regenerating a stable emulsion over time of gas and oil, such as that conventionally produced by the compressor, at its discharge outlet, and in which the drops are usually "polydispersed" (i.e. widely variable around a central value) in diameter.
  • a change in the circulating composition of the mixture initially introduced into the fluid circuit may be an indication of operation of the invention.
  • the compositions of the mixture measured at the compressor outlet, over time depending on the operating conditions: outside temperature, temperature of the hydraulic circuit, setting of the expansion valve. Since the differential solubility of the components of R407C in the oil is variable, trapping of the oil in the tubes of the first bulge may also explain this variation in circulating composition.
  • the person skilled in the art in the presence of such an increase, will be able to adjust the length of the tubes or adjust the distance separating the first bulge from the condenser, in the fluid circuit, to optimize the increase in power observed in the condenser, for example by measuring the temperature of a hot water outlet of a heating circuit in thermal contact with the condenser. He will also be able to vary the verticality of the tubes by admitting an angle maintaining a slope to the tubes allowing the flow of oil downwards, maintaining an effect on the thermal power of the condenser compared to a strict verticality.
  • the COP improvement percentages for R407C, R407A and R407F are as follows: 407C 407A 407F Ambient air COP gain COP gain COP gain 7°C 27% 21% -3% 0°C 34% 23% 12% -7°C 37% 14% 3%
  • this structure is designed to provide a means of regularly dividing the oil drops with the result of forming an emulsion of drops and gas sufficiently stable, in terms of droplet lifetime, to allow them to reach the condenser and form nucleation sites improving heat exchange in the condenser and the thermodynamic efficiency of the pump.
  • the same general inventive idea of a means of forming an emulsion will be applied to the design of the first bulge with tubes but instead of an emulsion of drops in a gas or gases, the first bulge will be designed to form an emulsion of bubbles in the gas or gases.
  • a mixed mode in which an emulsion of drops but also of oil bubbles is formed by the first bulge between the oil and the freons present in the first line is not excluded depending on the relative surface tension properties of the oil and the freons at the operating temperature and pressure of the fluid in the first line.
  • the invention was tested with mixtures of freons R32, R125 and R134a induced by an introduction of R407C and a particular oil EMKARATE ® RL32-3 MAF in the circuit of a pump modified by the first bulge arranged vertically and having the second bulge.
  • a compressor (referenced ZB38KCE) is used.
  • the oil is considered in liquid form throughout the closed circuit at the temperatures and pressures mentioned.
  • the mixture of R32, R125 and R134a is gaseous at the outlet. There is therefore, in normal operation in this embodiment, no increase in temperature at the outlet of the first bulge compared to its inlet, and this bulge therefore does not function as a heat source.
  • the mixture of R32, R125 and R134a is liquid at the outlet.
  • the mixture of R32, R125 and R134a is liquid at the outlet, with liquid-gas two-phase periods, where bubbles appear. There is therefore, in normal operation in this embodiment, no increase in temperature at the outlet of the second bulge compared to its inlet, and this bulge therefore does not function as a heat source.
  • the mixture of R32, R125 and R134a is two-phase liquid-gas at the outlet.
  • the mixture of R32, R125 and R134a is gaseous at the outlet.
  • the COP gains are comparable to those of an AIRWELL ® brand machine mentioned previously for the first mode, over the temperature range from -7°C to +7°C.
  • the invention is susceptible to industrial application in the field of heat pumps and air conditioners.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubricants (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP14824056.7A 2013-11-22 2014-11-21 Dispositif à fluide frigorigène pour l'augmentation du rendement thermodynamique Active EP3071902B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1361503A FR3013812B1 (fr) 2013-11-22 2013-11-22 Pompe a chaleur.
PCT/FR2014/052987 WO2015075393A1 (fr) 2013-11-22 2014-11-21 Dispositif a fluide frigorigene pour l'augmentation du rendement thermodynamique

Publications (3)

Publication Number Publication Date
EP3071902A1 EP3071902A1 (fr) 2016-09-28
EP3071902C0 EP3071902C0 (fr) 2025-02-19
EP3071902B1 true EP3071902B1 (fr) 2025-02-19

Family

ID=50473400

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14824056.7A Active EP3071902B1 (fr) 2013-11-22 2014-11-21 Dispositif à fluide frigorigène pour l'augmentation du rendement thermodynamique

Country Status (12)

Country Link
US (1) US10274234B2 (pl)
EP (1) EP3071902B1 (pl)
JP (1) JP6364090B2 (pl)
KR (1) KR102246125B1 (pl)
CN (1) CN106415155B (pl)
AU (1) AU2014351648B2 (pl)
BR (1) BR112016011701B1 (pl)
ES (1) ES3022583T3 (pl)
FR (1) FR3013812B1 (pl)
PL (1) PL3071902T3 (pl)
RU (1) RU2677315C1 (pl)
WO (1) WO2015075393A1 (pl)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6315071B1 (ja) * 2016-11-28 2018-04-25 ダイキン工業株式会社 冷媒組成物の移充填方法
CN116972557A (zh) * 2023-07-26 2023-10-31 广东美的暖通设备有限公司 冷媒循环系统及空调器

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5040122Y2 (pl) * 1971-10-20 1975-11-17
US4214453A (en) * 1979-02-09 1980-07-29 Barrow Billy E Injector cooler controls
US4478050A (en) * 1982-11-19 1984-10-23 Hussmann Corporation Oil separation for refrigeration system
JPS6315058A (ja) 1986-07-04 1988-01-22 株式会社デンソー 冷凍サイクル
JP4294764B2 (ja) * 1998-09-10 2009-07-15 三菱電機株式会社 冷凍サイクル
JP2001317840A (ja) * 2000-05-09 2001-11-16 Mitsubishi Electric Corp 減圧装置、冷凍回路、ヒートポンプ式空気調和機、減圧装置の製造方法
JP2002106959A (ja) * 2000-09-28 2002-04-10 Sanyo Electric Co Ltd ヒートポンプ給湯機
DE102004038220B4 (de) * 2004-08-05 2009-07-23 Proton Technology Gmbh I.Gr. Thermische Biomassenverölung
JP2006266636A (ja) * 2005-03-25 2006-10-05 Daikin Ind Ltd 冷凍装置
CN101432385A (zh) * 2005-06-08 2009-05-13 开利公司 以节约器操作空调系统的方法和装置
MX2009014089A (es) 2007-07-05 2010-03-01 Ib Ntec Un dispositivo para producir calor al circular un fluido bajo presion a traves de una pluralidad de tubos, y un sistema termodinamico que implementa tal dispositivo.
WO2009053726A2 (en) * 2007-10-24 2009-04-30 Thermal Energy Systems Limited Heat pump
WO2011028970A1 (en) 2009-09-04 2011-03-10 E. I. Du Pont De Nemours And Company Compositions comprising refrigerant and lubricant and methods for replacing cfc and hcfc refrigerants without flushingfield of the invention
CN201724472U (zh) * 2010-07-30 2011-01-26 中国汽车工业工程公司 直接膨胀式土壤源热泵的回油控制装置
CN102003844B (zh) * 2010-12-07 2012-01-18 东南大学 一种高效全湿内表面蒸发器
FR2990264B1 (fr) * 2012-05-04 2018-07-27 Valeo Systemes Thermiques Installation de chauffage, ventilation et/ou climatisation a masse circulante reduite.

Also Published As

Publication number Publication date
FR3013812B1 (fr) 2019-03-15
KR102246125B1 (ko) 2021-04-30
WO2015075393A1 (fr) 2015-05-28
EP3071902C0 (fr) 2025-02-19
US10274234B2 (en) 2019-04-30
FR3013812A1 (fr) 2015-05-29
PL3071902T3 (pl) 2025-07-07
US20160290687A1 (en) 2016-10-06
BR112016011701B1 (pt) 2022-03-22
RU2677315C1 (ru) 2019-01-16
AU2014351648B2 (en) 2018-10-18
RU2016124553A (ru) 2017-12-27
KR20160089424A (ko) 2016-07-27
AU2014351648A1 (en) 2016-06-09
CN106415155A (zh) 2017-02-15
EP3071902A1 (fr) 2016-09-28
ES3022583T3 (en) 2025-05-28
JP2016539313A (ja) 2016-12-15
JP6364090B2 (ja) 2018-07-25
CN106415155B (zh) 2020-06-26
BR112016011701A2 (pl) 2017-08-08

Similar Documents

Publication Publication Date Title
EP2475737B2 (fr) Procede de transfert de chaleur
EP2475732B1 (fr) Compositions ternaires pour refrigeration haute capacite
EP3044278B1 (fr) Fluides de transfert de chaleur comprenant du difluoromethane, du pentafluoroethane, du tetrafluoropropene et eventuellement du propane
EP3071902B1 (fr) Dispositif à fluide frigorigène pour l'augmentation du rendement thermodynamique
CN1526061A (zh) 冷冻循环装置
EP3071901B1 (fr) Dispositif utilisable avec un fluide frigorigène pour l'augmentation du rendement thermodynamique.
WO2007090861A1 (fr) Dispositif echangeur de chaleur destine aux systemes de chauffage ou de climatisation
EP3601469A1 (fr) Procede de chauffage et/ou climatisation d'un vehicule
CA2844478A1 (fr) Fluides de transfert de chaleur supercritiques a base de tetrafluoropropene
EP2708436A1 (fr) Dispositif de climatisation d'air, notamment pour un véhicule ferroviaire
WO2015075394A1 (fr) Procede d'augmentation du rendement d'un dispositif thermodynamique a fluide frigorigene
FR2986309A1 (fr) Systeme de refrigeration en cascade
WO2015104330A1 (fr) Pompe à chaleur produisant du froid
EP2411743A1 (fr) Installation et procédé pour la production de froid et/ou de chaleur
WO2024156698A1 (fr) Amélioration de la puissance des machines thermodynamiques
EP1956328A1 (fr) Echangeur di phasique
FR3033796A1 (fr) Fluide frigorigene

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20160609

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIN1 Information on inventor provided before grant (corrected)

Inventor name: CASTELAIN, GILLES

Inventor name: MORO-PEREZ, JIMMY

Inventor name: KALINOWSKI, PASCAL

Inventor name: RIZK, JOELLE

Inventor name: DEBOUX, BRUNO

Inventor name: BARBAN, FREDERIC

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20190925

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20240911

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014091578

Country of ref document: DE

U01 Request for unitary effect filed

Effective date: 20250319

U07 Unitary effect registered

Designated state(s): AT BE BG DE DK EE FI FR IT LT LU LV MT NL PT RO SE SI

Effective date: 20250325

RAP4 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: DYNAES

U1H Name or address of the proprietor changed after the registration of the unitary effect

Owner name: DYNAES; FR

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 3022583

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20250528

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250519

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250619

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250520

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20250219

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

U20 Renewal fee for the european patent with unitary effect paid

Year of fee payment: 12

Effective date: 20251125

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20251120

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NO

Payment date: 20251126

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20251117

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PL

Payment date: 20251118

Year of fee payment: 12

26N No opposition filed

Effective date: 20251120

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20251212

Year of fee payment: 12