EP2647925B1 - Appareil de circuit de réfrigération - Google Patents

Appareil de circuit de réfrigération Download PDF

Info

Publication number
EP2647925B1
EP2647925B1 EP13166592.9A EP13166592A EP2647925B1 EP 2647925 B1 EP2647925 B1 EP 2647925B1 EP 13166592 A EP13166592 A EP 13166592A EP 2647925 B1 EP2647925 B1 EP 2647925B1
Authority
EP
European Patent Office
Prior art keywords
temperature
refrigerant
detection means
heat exchanger
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
EP13166592.9A
Other languages
German (de)
English (en)
Other versions
EP2647925A3 (fr
EP2647925A2 (fr
Inventor
Takashi Okazaki
Fumitake Unezaki
Tomoyoshi Oobayashi
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP2647925A2 publication Critical patent/EP2647925A2/fr
Publication of EP2647925A3 publication Critical patent/EP2647925A3/fr
Application granted granted Critical
Publication of EP2647925B1 publication Critical patent/EP2647925B1/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
    • 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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2102—Temperatures at the outlet of the gas cooler
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters

Definitions

  • the present invention relates to a refrigeration cycle apparatus using an internal heat exchanger; more particularly to a refrigerant control for stably securing performance.
  • a hot water supply apparatus is proposed as a built-in refrigeration cycle apparatus such as:
  • a water heater is also proposed such as:
  • the present invention is made to solve the above problems in the prior art.
  • the object is to obtain a refrigeration cycle apparatus capable of stably achieving efficient operation conditions by controlling operation values based on standard conditions of the radiator and outlet conditions of the radiator to be a target value.
  • the refrigeration cycle apparatus includes at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of the radiator and the refrigerant at the outlet of the heat absorber.
  • the refrigeration cycle apparatus is characterized in that at least first refrigerant conditions detection means for detecting standard conditions of the radiator and second refrigerant conditions detection means for detecting refrigerant conditions between an outlet of the radiator and a high-pressure side inlet of an internal heat exchanger are provided, and an opening degree of decompression means is controlled so that a calculation value calculated based on an output of the first refrigerant conditions detection means and the output of the second refrigerant conditions detection means becomes a target value.
  • the expansion valve opening degree is controlled so that the COP becomes maximum based on standard conditions of the radiator and refrigerant conditions of the radiator outlet part, so that a refrigerant cycle apparatus capable of stably achieving efficient operation can be obtained.
  • Fig. 1 shows a configuration diagram of the refrigerant cycle apparatus according to the invention.
  • the refrigerant cycle apparatus according to the present embodiment is a hot water supply apparatus using carbon dioxide (hereinafter, CO 2 as a refrigerant, composed of a heat source apparatus 50, a hot water storage apparatus 60, and a controller 40 for controlling these. It shows an example of the hot water supply apparatus, however, it is not limited thereto.
  • the apparatus may be an air conditioner.
  • the refrigerant is not limited to carbon dioxide but an HFC refrigerant may be used.
  • the heat source apparatus 50 is composed of a compressor 1 for compressing the refrigerant, a radiator 2 (hereinafter, referred to “water heat exchanger") for taking out heat of a high-temperature high-pressure refrigerant compressed in the compressor 1, an internal heat exchanger 5 for further cooling the refrigerant output from the water heat exchanger 2, a decompressor 3 (hereinafter, referred to “expansion valve”) that decompresses the refrigerant and whose opening degree can be changed, an heat-absorber 4 (hereinafter, referred to “evaporator”) for evaporating the refrigerant decompressed in the expansion valve 3, and an internal heat exchanger 5 for further heating the refrigerant flowed out of the evaporator 4.
  • a compressor 1 for compressing the refrigerant
  • a radiator 2 hereinafter, referred to "water heat exchanger”
  • water heat exchanger 5 for taking out heat of a high-temperature high-pressure refrigerant compressed in the compressor 1
  • the internal heat exchanger 5 is a heat exchanger that heat-exchanges the refrigerant at an outlet of the water heat exchanger 2 with the refrigerant at the outlet of the evaporator 4.
  • a blower 29 is provided for sending air on an outer surface of the evaporator 4.
  • first temperature detection means 30 for detecting a discharge temperature of the compressor 1
  • second temperature detection means 31 for detecting an outlet temperature of the water heat exchanger 2
  • fifth temperature detection means 32 for detecting an inlet refrigerant temperature of the evaporator 4
  • sixth temperature detection means 33 for detecting a suction temperature of the compressor 1.
  • the first temperature detection means 30 and the second temperature detection means 31 correspond to a first refrigerant conditions detection means and second refrigerant conditions detection means respectively in an example of control in Fig. 7 to be described later.
  • a hot water storage apparatus 60 is connected with the water heat exchanger 2, which is a radiator, via piping, being composed of a heat source side pump 20, a hot water storage tank 21, a use side pump 22, and on-off valves 23, 24, 25.
  • on-off valves 23, 24, 25 may be a simple valve only for switching operation or an opening variable valve.
  • the on-off valves 23, 25 are closed, the on-off valve 24 is opened, and circulation heating operation is performed in which low-temperature hot water in the hot water storage tank 21 is re-boiled.
  • the on-off valves 23, 24 are closed, the on-off valve 25 is opened, the use side pump 22 starts operation to transfer stored hot water to the use side.
  • third temperature detection means 41 is attached for detecting an inlet temperature of a medium (water) to be heated.
  • fourth temperature detection means 42 is attached for detecting the outlet temperature of the medium (water) to be heated.
  • a controller 40 performs calculation using detected values from first temperature detection means 30, second temperature detection means 31, fifth temperature detection means 32, sixth temperature detection means 33, third temperature detection means 41, and fourth temperature detection means 42 to control an opening degree of the expansion valve 3, a rotation speed of the compressor 1, and the rotation speed of the hot water supply side pump 20, respectively.
  • Fig. 2 is a P-h diagram describing cycle conditions during hot water storage operation in the refrigeration cycle apparatus shown in Fig. 1 .
  • solid lines denote refrigerant conditions at a certain expansion valve opening degree and A, B, C, D, and E denote refrigerant conditions in the hot water storage operation.
  • A high-temperature high-pressure refrigerant
  • the refrigerant heats supplied water while dissipating heat to water circulating the hot water storage circuit to decrease the own temperature.
  • a refrigerant (B) flowed out of the water heat exchanger 2 dissipates heat in the internal heat exchanger 5 to further decrease (C) the temperature, being decompressed (D) by the expansion valve 3 to turn into a low-temperature low-pressure refrigerant.
  • the low-temperature low-pressure refrigerant absorbs heat from the air in the evaporator 4 to evaporate (E).
  • the refrigerant flowed out of the evaporator 4 is heated in the internal heat exchanger 5 to turn into a gas (F) and sucked by the compressor 1 to form a refrigeration cycle.
  • the expansion valve 3 is controlled so that a suction superheat degree of the compressor 1 becomes a target value (for example, 5 to 10 °C).
  • a target value for example, 5 to 10 °C.
  • an evaporation temperature (ET) is estimated, a suction superheat degree SH s is calculated by the following formula using a detection value (T s ) of sixth temperature detection means 33 detecting a suction temperature of the compressor 1.
  • SH S T S ⁇ ET
  • an opening degree of the expansion valve 3 is controlled so that SH s becomes a target value.
  • An example is given in which an evaporation temperature (ET) is estimated based on the detection value of the fifth temperature detection means 32, however, it is not limited thereto.
  • Pressure detection means (second pressure detection means) 51 (refer to Fig. 1 ) is installed between a low-pressure side outlet of the internal heat exchanger 5 and the inlet of the compressor 1, and from the detection value, a refrigerant saturation temperature may be obtained.
  • a suction superheat degree control precedes other high efficiency operation control because a function to prevent liquid return of the compressor 1 precedes a function to efficiently operate the water heat exchanger 2 from the viewpoint of securing reliability of the equipment.
  • Fig. 3 shows a refrigerant and water temperature distribution in the water heat exchanger 2.
  • thick solid lines show a change in refrigerant temperature
  • a thin solid lines denote a change in water temperature
  • ⁇ T1 denotes a temperature difference between the water heat exchanger inlet temperature and water outlet temperature
  • ⁇ T2 denotes a temperature difference between the water heat exchanger outlet temperature and water inlet temperature
  • ⁇ Tp is a temperature difference at a pinch point where the temperature difference between a refrigerant and water in the water heat exchanger 2 becomes minimum.
  • ⁇ T denotes a temperature difference between the water heat exchanger inlet temperature and the water heat exchanger outlet temperature.
  • Fig. 5 shows changes in operation values obtained from the temperature of each part when the opening degree of the expansion valve 3 changes.
  • the horizontal axis represents the opening degree (%) of the expansion valve 3
  • the vertical axis represents the suction superheat degree, discharge temperature, temperature difference ⁇ T2 between the outlet temperature of the water heat exchanger and water inlet temperature, heating ability ratio, COP ratio.
  • the heating ability ratio and COP ratio show a ratio when a maximum value against the expansion valve opening degree is set as 100%, respectively.
  • changes in the suction superheat degree can be regarded as almost a constant value, so that it is understood that changes in the heating ability ratio and the COP ratio cannot be judged by the suction superheat degree.
  • Fig. 6 shows changes in other operation values obtained from temperatures of each part when the opening degree of the expansion valve 3 is changed.
  • the horizontal axis represents the opening degree (%) of the expansion valve 3.
  • the vertical axis represents an outlet/inlet temperature difference ⁇ Thx of the internal heat exchanger, a temperature difference ⁇ T between a discharge temperature and an outlet temperature of the water heat exchanger, a total temperature difference ⁇ ⁇ T of the above ⁇ T1 and ⁇ T2, heating ability, and a COP ratio, respectively.
  • a total temperature difference ⁇ T of the temperature difference ⁇ T1 between the water heat exchanger inlet temperature and water outlet temperature and the temperature difference ⁇ T2 between the water heat exchanger outlet temperature and water inlet temperature becomes a minimum.
  • the control based on such an index has a physical meaning and being reasonable.
  • high-precision temperature detection is required because change in temperature is small in the vicinity where the COP becomes a maximum compared with the temperature difference ⁇ T.
  • a temperature difference ⁇ Tp at a pinch point is almost the same as that of ⁇ T2 between the water heat exchanger outlet temperature and water inlet temperature.
  • Fig. 7 is a flowchart showing a control operation of the refrigeration cycle apparatus.
  • the suction superheat degree (SHs) control of the compressor 1 precedes the temperature difference ⁇ T control for securing the heating ability.
  • the expansion valve opening degree is increased until the suction superheat degree (SHs) converges.
  • the temperature difference ⁇ T is made to converge at the target value.
  • the temperature difference ⁇ T is made to converge at the target value.
  • the expansion opening degree is increased and ⁇ T is made to converge.
  • ⁇ Thx When using ⁇ Thx, internal heat exchanger outlet temperature detection means 52 is attached (refer to Fig. 1 ) between a high-pressure side outlet of the internal heat exchanger 5 and an inlet of the expansion valve 3, the temperature difference ⁇ Thx is obtained from a detection temperatures by the second temperature detection means 31 and the internal heat exchanger outlet temperature detection means 52.
  • the expansion valve opening degree is made to be controlled so that the COP becomes maximum based on a temperature difference ⁇ T1 - ⁇ T2 between the discharge temperature and the water heat exchanger outlet temperature, a high efficiency refrigeration cycle apparatus can be obtained.
  • a refrigerant saturation temperature (ET) is obtained based on an output of the fifth temperature detection means 32 or pressure detection means, the suction superheat degree (SHs) is obtained by the detection temperature (Ts) of the sixth temperature detection means and the refrigerant saturation temperature (ET), and the expansion valve opening degree is controlled so that the suction superheat degree (SHs) becomes a target value, so that the superheat degree of the suction part of the compressor 1 is secured , liquid return to the compressor 1 can be prevented, and reliability can be secured.
  • Ts detection temperature
  • ET refrigerant saturation temperature
  • the fifth temperature detection means 32 is provided between the expansion valve 3 and the evaporator 4, it can be disposed at any position between the inlet of the evaporator 4 and a low-pressure side inlet of the internal heat exchanger 5.
  • the radiator is composed of the water heat exchanger, so that a high efficiency hot water supply apparatus can be obtained.
  • thermoelectric in said refrigerant cycle apparatus fifth temperature detection means may be provided between the inlet of said heat absorber and the low-pressure side inlet of said internal heat exchanger and
  • a priority may be given to control said superheat degree over said temperature difference.
  • said radiator may be a heat exchanger that exchanges heat with water.
  • carbon dioxide may be used as a refrigerant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Claims (7)

  1. Appareil à cycle de produit frigorigène comprenant :
    au moins un compresseur (1), un radiateur (2), des moyens de décompression (3) susceptibles de pouvoir modifier un degré d'ouverture, un dispositif d'absorption de la chaleur (4), un échangeur de chaleur interne (5) qui exécute un échange de chaleur entre un fluide frigorigène au niveau d'une sortie du radiateur (2) et le fluide frigorigène au niveau d'une sortie du dispositif d'absorption de la chaleur (4), dans lequel:
    sont fournis des premiers moyens de détection de la température (30) destinés à détecter la température du fluide frigorigène entre une sortie du compresseur (1) et une entrée du radiateur (2), des deuxièmes moyens de détection de la température (31) destinés à détecter la température du fluide frigorigène entre la sortie du radiateur (2) et une entrée du côté haute pression de l'échangeur de chaleur interne (5), des troisièmes moyens de détection de la température (41) destinés à détecter la température d'entrée d'un milieu à chauffer, et des quatrièmes moyens de détection de la température (42) destinés à détecter la température de sortie du milieu à chauffer, caractérisé en ce que :
    le degré d'ouverture des moyens de décompression (3) est commandé de telle sorte que la différence (ΔT1 - ΔT2) entre une deuxième différence de température (ΔT1) entre la température de détection par les premiers moyens de détection de la température (30), et la température de détection par les quatrièmes moyens de détection de la température (42), et une troisième différence de température (ΔT2) entre la température de détection par les deuxièmes moyens de détection de la température (31), et la température de détection par les troisièmes moyens de détection de la température (41), devienne une valeur cible.
  2. Appareil à cycle de produit frigorigène selon la revendication 1, dans lequel:
    sont fournis des sixièmes moyens de détection de la température (33) destinés à détecter la température du fluide frigorigène entre une sortie du côté basse pression de l'échangeur de chaleur interne (5) et une entrée du compresseur (1) ;
    le degré de surchauffe d'une partie aspiration du compresseur, est calculé à partir d'une température de saturation du fluide frigorigène au niveau d'un point de détection des sixièmes moyens de détection de la température (33), et d'une température de détection par les sixièmes moyens de détection de la température (33) ; et
    le degré d'ouverture des moyens de décompression (3) est commandé de telle sorte que le degré de surchauffe devienne la valeur cible.
  3. Appareil à cycle de produit frigorigène selon la revendication 2, dans lequel :
    des seconds moyens de détection de la pression (51) sont fournis entre la sortie du côté basse pression de l'échangeur de chaleur interne (5) et l'entrée du compresseur (1); et
    la température de saturation du fluide frigorigène est calculée sur la base d'une valeur de détection des seconds moyens de détection de la pression (51).
  4. Appareil à cycle de produit frigorigène selon la revendication 2, dans lequel :
    des cinquièmes moyens de détection de la température (32) sont fournis entre l'entrée du dispositif d'absorption de la chaleur (4), et l'entrée du côté basse pression de l'échangeur de chaleur interne (5) ; et
    la température de saturation du fluide frigorigène est calculée sur la base de la température de détection des cinquièmes moyens de détection de la température (32).
  5. Appareil à cycle de produit frigorigène selon l'une quelconque des revendications 2 à 4, dans lequel:
    une priorité est accordée sur la différence de la température, de façon à commander le degré de surchauffe.
  6. Appareil à cycle de produit frigorigène selon l'une quelconque des revendications 1 à 5, dans lequel :
    le radiateur (2) est un échangeur de chaleur qui échange de la chaleur avec de l'eau.
  7. Appareil à cycle de produit frigorigène selon l'une quelconque des revendications 1 à 6, dans lequel :
    du dioxyde de carbone est utilisé en tant que fluide frigorigène.
EP13166592.9A 2007-11-30 2008-11-20 Appareil de circuit de réfrigération Active EP2647925B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007310097A JP4948374B2 (ja) 2007-11-30 2007-11-30 冷凍サイクル装置
EP08855672.5A EP2196745B1 (fr) 2007-11-30 2008-11-20 Dispositif de cycle de réfrigération

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP08855672.5 Division 2008-11-20
EP08855672.5A Division EP2196745B1 (fr) 2007-11-30 2008-11-20 Dispositif de cycle de réfrigération
EP08855672.5A Division-Into EP2196745B1 (fr) 2007-11-30 2008-11-20 Dispositif de cycle de réfrigération

Publications (3)

Publication Number Publication Date
EP2647925A2 EP2647925A2 (fr) 2013-10-09
EP2647925A3 EP2647925A3 (fr) 2015-08-05
EP2647925B1 true EP2647925B1 (fr) 2016-12-21

Family

ID=40678426

Family Applications (5)

Application Number Title Priority Date Filing Date
EP13166595.2A Active EP2647927B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération
EP13166592.9A Active EP2647925B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération
EP13166593.7A Active EP2647926B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération
EP08855672.5A Active EP2196745B1 (fr) 2007-11-30 2008-11-20 Dispositif de cycle de réfrigération
EP13166596.0A Active EP2647928B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP13166595.2A Active EP2647927B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération

Family Applications After (3)

Application Number Title Priority Date Filing Date
EP13166593.7A Active EP2647926B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération
EP08855672.5A Active EP2196745B1 (fr) 2007-11-30 2008-11-20 Dispositif de cycle de réfrigération
EP13166596.0A Active EP2647928B1 (fr) 2007-11-30 2008-11-20 Appareil de circuit de réfrigération

Country Status (7)

Country Link
US (1) US20100205987A1 (fr)
EP (5) EP2647927B1 (fr)
JP (1) JP4948374B2 (fr)
CN (2) CN101842645B (fr)
DK (5) DK2647927T3 (fr)
ES (5) ES2823758T3 (fr)
WO (1) WO2009069524A1 (fr)

Families Citing this family (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5330915B2 (ja) * 2009-07-22 2013-10-30 株式会社前川製作所 ２元冷凍サイクル装置及びその制御方法
JP5689079B2 (ja) * 2010-02-12 2015-03-25 三菱電機株式会社 冷凍サイクル装置
JP5558937B2 (ja) * 2010-06-30 2014-07-23 株式会社コロナ ヒートポンプ式給湯装置
WO2012050087A1 (fr) * 2010-10-15 2012-04-19 東芝キヤリア株式会社 Appareil de source de chaleur
WO2013018148A1 (fr) * 2011-08-04 2013-02-07 三菱電機株式会社 Dispositif de réfrigération
KR20130041640A (ko) * 2011-10-17 2013-04-25 엘지전자 주식회사 공기조화기 및 그 운전 방법
EP3112777B1 (fr) * 2011-10-25 2018-11-14 LG Electronics Inc. Climatiseur et son procede de fonctionnement
ES2748573T3 (es) * 2011-11-29 2020-03-17 Mitsubishi Electric Corp Dispositivo de refrigeración/acondicionamiento de aire
JP5875396B2 (ja) * 2012-02-10 2016-03-02 三菱重工業株式会社 ヒートポンプの制御装置、ヒートポンプ、及びヒートポンプの制御方法
JP5861577B2 (ja) * 2012-07-05 2016-02-16 株式会社デンソー 給湯装置
JP5831423B2 (ja) * 2012-10-08 2015-12-09 株式会社デンソー 冷凍サイクル装置
EP2940405B1 (fr) * 2012-12-26 2018-06-06 Mitsubishi Electric Corporation Dispositif de cycle de réfrigération et procédé de commande de dispositif de cycle de réfrigération
DE102013001455A1 (de) * 2013-01-28 2014-08-14 Hochschule für angewandte Wissenschaften München Anordnung und Verfahren zur Wärmeversorgung eines Gebäudes
JP6080939B2 (ja) * 2013-02-19 2017-02-15 三菱電機株式会社 空気調和装置
DE102013210175A1 (de) * 2013-05-31 2014-12-18 Siemens Aktiengesellschaft Wärmepumpe zur Verwendung von umweltverträglichen Kältemitteln
CN105940276A (zh) * 2014-01-23 2016-09-14 三菱电机株式会社 热泵装置
JP5874754B2 (ja) * 2014-01-31 2016-03-02 ダイキン工業株式会社 冷凍装置
WO2015136595A1 (fr) * 2014-03-10 2015-09-17 三菱電機株式会社 Système de pompe à chaleur
WO2016057492A1 (fr) * 2014-10-09 2016-04-14 Carrier Corporation Échangeur de chaleur à aspiration de liquide interne
GB2547144B (en) * 2014-12-05 2020-07-08 Mitsubishi Electric Corp Air-conditioning apparatus
JP6456139B2 (ja) * 2014-12-26 2019-01-23 株式会社前川製作所 冷凍又は空調装置及びその制御方法
CN108027189B (zh) * 2015-09-18 2021-07-06 开利公司 用于制冷机的冻结防护系统和方法
JP2017088137A (ja) * 2015-11-17 2017-05-25 株式会社ヴァレオジャパン 車両用空調装置の冷凍サイクル及びこれを搭載した車両
JP6745657B2 (ja) * 2016-06-29 2020-08-26 リンナイ株式会社 給湯システム
EP3594587B1 (fr) * 2017-03-09 2021-04-21 Mitsubishi Electric Corporation Dispositif d'alimentation en eau chaude d'une pompe à chaleur
WO2020075238A1 (fr) * 2018-10-10 2020-04-16 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif de pompe à chaleur
CN111854206B (zh) * 2019-04-28 2022-01-25 青岛海尔智能技术研发有限公司 一种冷柜设备、制冷系统及其控制方法
AT522875B1 (de) * 2019-10-30 2021-03-15 Lambda Waermepumpen Gmbh Verfahren zur Regelung eines Expansionsventils
DE102020115274A1 (de) 2020-06-09 2021-12-09 Stiebel Eltron Gmbh & Co. Kg Verfahren zum Betrieb einer Kompressionskälteanlage
JP7014988B1 (ja) * 2020-12-02 2022-02-02 ダイキン工業株式会社 冷凍装置
JPWO2022162819A1 (fr) * 2021-01-28 2022-08-04
DE102021127213A1 (de) 2021-10-20 2023-04-20 Lauda Dr. R. Wobser Gmbh & Co. Kg Kälteanlage und Verfahren zum Betreiben einer Kälteanlage
CN114234450B (zh) * 2021-12-24 2023-09-08 山东雅士股份有限公司 一种变频co2热水机机组的控制方法
DE102022118670A1 (de) 2022-07-26 2024-02-01 Lauda Dr. R. Wobser Gmbh & Co. Kg Prozesskühlaggregat und Verfahren zur Regelung eines Prozesskühlaggregrats

Family Cites Families (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05106922A (ja) * 1991-10-18 1993-04-27 Hitachi Ltd 冷凍装置の制御方式
US5457965A (en) * 1994-04-11 1995-10-17 Ford Motor Company Low refrigerant charge detection system
CN1135341C (zh) * 1994-05-30 2004-01-21 三菱电机株式会社 制冷循环系统
JPH0966736A (ja) * 1995-06-23 1997-03-11 Denso Corp 車両用空調装置
US5704219A (en) * 1995-08-01 1998-01-06 Nippondenso Co., Ltd. Air conditioning apparatus
JPH11108485A (ja) * 1997-09-30 1999-04-23 Matsushita Electric Ind Co Ltd 空気調和機及び冷媒加熱器出口温度の制御方法
JP3227651B2 (ja) * 1998-11-18 2001-11-12 株式会社デンソー 給湯器
JP3601369B2 (ja) * 1999-09-03 2004-12-15 ダイキン工業株式会社 給湯装置
JP2001235239A (ja) * 2000-02-23 2001-08-31 Seiko Seiki Co Ltd 超臨界蒸気圧縮サイクル装置
EP1148307B1 (fr) * 2000-04-19 2004-03-17 Denso Corporation Chauffe-eau avec pompe à chaleur
JP3737381B2 (ja) * 2000-06-05 2006-01-18 株式会社デンソー 給湯装置
JP4538919B2 (ja) * 2000-08-08 2010-09-08 三菱電機株式会社 室内マルチ空気調和機
DE10246004B4 (de) * 2001-10-03 2017-05-18 Denso Corporation Überkritisches Kühlkreislaufsystem und dieses verwendender Warmwasserbereiter
JP2003176957A (ja) * 2001-10-03 2003-06-27 Denso Corp 冷凍サイクル装置
JP3737414B2 (ja) * 2001-11-05 2006-01-18 株式会社デンソー 給湯装置
TWI263025B (en) * 2002-01-24 2006-10-01 Daikin Ind Ltd Freezing device
JP2004061061A (ja) * 2002-07-31 2004-02-26 Matsushita Electric Ind Co Ltd 冷凍サイクル装置およびその運転方法
US7000413B2 (en) * 2003-06-26 2006-02-21 Carrier Corporation Control of refrigeration system to optimize coefficient of performance
JP3915770B2 (ja) * 2003-10-31 2007-05-16 松下電器産業株式会社 ヒートポンプ給湯機
JP2005156030A (ja) * 2003-11-26 2005-06-16 Hitachi Home & Life Solutions Inc ヒートポンプ装置
JP4269323B2 (ja) * 2004-03-29 2009-05-27 三菱電機株式会社 ヒートポンプ給湯機
CN100494829C (zh) * 2004-05-20 2009-06-03 上海交通大学 蒸发器出口制冷剂为大干度二相状态的高效制冷系统
JP4337880B2 (ja) * 2004-07-12 2009-09-30 株式会社デンソー ヒートポンプ式給湯器
JP2006077998A (ja) * 2004-09-07 2006-03-23 Matsushita Electric Ind Co Ltd 冷凍サイクル装置および制御方法
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
JP4670329B2 (ja) * 2004-11-29 2011-04-13 三菱電機株式会社 冷凍空調装置、冷凍空調装置の運転制御方法、冷凍空調装置の冷媒量制御方法
US8096141B2 (en) * 2005-01-25 2012-01-17 Trane International Inc. Superheat control by pressure ratio
CN1862151A (zh) * 2005-05-12 2006-11-15 乐金电子(天津)电器有限公司 回热式制冷循环系统空调器
JP2007093100A (ja) * 2005-09-28 2007-04-12 Mitsubishi Electric Corp ヒートポンプ給湯機の制御方法及びヒートポンプ給湯機
EP1813887B1 (fr) * 2006-01-31 2009-05-06 Sanyo Electric Co., Ltd. Dispositif de climatisation
JP4613916B2 (ja) * 2006-03-17 2011-01-19 三菱電機株式会社 ヒートポンプ給湯機
JP4569508B2 (ja) * 2006-03-31 2010-10-27 株式会社デンソー 超臨界サイクル及び冷凍サイクルに用いられる膨張弁

Also Published As

Publication number Publication date
CN101842645A (zh) 2010-09-22
ES2611980T3 (es) 2017-05-11
ES2700938T3 (es) 2019-02-20
WO2009069524A1 (fr) 2009-06-04
EP2647927A2 (fr) 2013-10-09
DK2647926T3 (en) 2019-01-07
EP2647925A3 (fr) 2015-08-05
EP2647928A3 (fr) 2015-08-05
JP4948374B2 (ja) 2012-06-06
ES2650233T3 (es) 2018-01-17
JP2009133547A (ja) 2009-06-18
EP2647926B1 (fr) 2018-10-24
DK2647927T3 (da) 2020-10-19
EP2647925A2 (fr) 2013-10-09
EP2196745A4 (fr) 2013-02-13
EP2647928B1 (fr) 2016-10-26
ES2605462T3 (es) 2017-03-14
EP2647926A3 (fr) 2015-07-29
DK2196745T3 (en) 2017-12-11
CN102425872B (zh) 2014-06-25
CN101842645B (zh) 2012-11-28
EP2647926A2 (fr) 2013-10-09
EP2647928A2 (fr) 2013-10-09
US20100205987A1 (en) 2010-08-19
EP2647927B1 (fr) 2020-09-16
DK2647928T3 (en) 2016-12-12
ES2823758T3 (es) 2021-05-10
EP2196745B1 (fr) 2017-11-08
EP2196745A1 (fr) 2010-06-16
EP2647927A3 (fr) 2015-07-29
DK2647925T3 (en) 2017-02-06
CN102425872A (zh) 2012-04-25

Similar Documents

Publication Publication Date Title
EP2647925B1 (fr) Appareil de circuit de réfrigération
US8353173B2 (en) Refrigerating cycle apparatus and operation control method therefor
EP2631562B1 (fr) Dispositif de chauffage de l'air du type pompe à chaleur
JP4337880B2 (ja) ヒートポンプ式給湯器
CN105157266B (zh) 制冷剂蒸气压缩系统的运行
JP5196452B2 (ja) 充填量管理を備えた遷臨界冷媒蒸気圧縮システム
US8020393B2 (en) Heat pump type hot water supply outdoor apparatus
US20100023166A1 (en) Free-cooling limitation control for air conditioning systems
US7210303B2 (en) Transcritical heat pump water heating system using auxiliary electric heater
KR101445992B1 (ko) 열매체 유량 추정 장치, 열원기 및 열매체 유량 추정 방법
JP2010526985A (ja) フラッシュタンクエコノマイザを備えた冷媒蒸気圧縮システム
JP2011521194A (ja) 冷媒蒸気圧縮システムにおける充填管理
EP2589901A2 (fr) Appareil de cycle de réfrigération et générateur d'eau chaude
EP2482013A2 (fr) Appareil à cycle de réfrigération
EP2594867B1 (fr) Appareil de cycle de réfrigération et appareil de production d'eau chaude
EP2538159A2 (fr) Appareil à cycle de réfrigération et appareil de chauffage hydronique comportant l'appareil à cycle de réfrigération
JP2019060581A (ja) 冷凍サイクル装置
CA2779757A1 (fr) Dispositif de regulation de la temperature d'un compresseur d'aspiration pour des compresseurs r-744 transcritiques et sous-critiques

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: 20130506

AC Divisional application: reference to earlier application

Ref document number: 2196745

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A2

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 1/00 20060101AFI20150702BHEP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602008048082

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F25B0009000000

Ipc: F25B0041060000

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 41/06 20060101AFI20160107BHEP

Ipc: F25B 9/00 20060101ALI20160107BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20160630

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 2196745

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

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

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 855846

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602008048082

Country of ref document: DE

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20170202

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

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

Ref country code: LV

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: 20161221

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20161221

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

Ref country code: LT

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: 20161221

Ref country code: NO

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: 20170321

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: 20170322

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2611980

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20170511

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 855846

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161221

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

Ref country code: FI

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: 20161221

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: 20161221

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

Ref country code: NL

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: 20161221

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

Ref country code: EE

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: 20161221

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: 20161221

Ref country code: RO

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: 20161221

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: 20170421

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: 20161221

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

Ref country code: AT

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: 20161221

Ref country code: BG

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: 20170321

Ref country code: PT

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: 20170421

Ref country code: PL

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: 20161221

Ref country code: BE

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: 20161221

Ref country code: IT

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: 20161221

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602008048082

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

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

26N No opposition filed

Effective date: 20170922

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

Ref country code: SI

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: 20161221

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

Ref country code: MC

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: 20161221

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

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171130

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171130

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

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171120

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171120

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

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

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171120

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602008048082

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20190122

REG Reference to a national code

Ref country code: ES

Ref legal event code: GC2A

Effective date: 20190416

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

Ref country code: HU

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

Effective date: 20081120

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161221

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

Ref country code: TR

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: 20161221

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602008048082

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F25B0041060000

Ipc: F25B0041300000

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230512

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

Ref country code: GB

Payment date: 20230928

Year of fee payment: 16

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

Ref country code: FR

Payment date: 20230929

Year of fee payment: 16

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

Ref country code: ES

Payment date: 20231201

Year of fee payment: 16

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

Ref country code: SE

Payment date: 20231002

Year of fee payment: 16

Ref country code: DK

Payment date: 20231116

Year of fee payment: 16

Ref country code: DE

Payment date: 20230929

Year of fee payment: 16