EP2647925B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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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
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EP
European Patent Office
Prior art keywords
temperature
refrigerant
detection means
heat exchanger
compressor
Prior art date
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Application number
EP13166592.9A
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English (en)
French (fr)
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EP2647925A2 (de
EP2647925A3 (de
Inventor
Takashi Okazaki
Fumitake Unezaki
Tomoyoshi Oobayashi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP2647925A2 publication Critical patent/EP2647925A2/de
Publication of EP2647925A3 publication Critical patent/EP2647925A3/de
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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
    • 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.

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  • 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. Kühlmittelkreislaufvorrichtung, die Folgendes umfasst:
    wenigstens einen Kompressor (1), einen Radiator (2), ein Dekompressionsmittel (3), das einen Öffnungsgrad ändern kann, einen Wärmeabsorber (4), einen inneren Wärmetauscher (5), der einen Wärmeaustausch zwischen einem Kühlmittel an einem Auslass des Radiators (2) und dem Kühlmittel an einem Auslass des Wärmeabsorbers (4) durchführt, wobei
    ein erstes Temperaturdetektionsmittel (30) zum Detektieren einer Kühlmitteltemperatur zwischen einem Auslass des Kompressors (1) und einem Einlass des Radiators (2) und ein zweites Temperaturdetektionsmittel (31) zum Detektieren der Kühlmitteltemperatur zwischen dem Auslass des Radiators (2) und einem Einlass auf der Hochdruckseite des inneren Wärmetauschers (5), ein drittes Temperaturdetektionsmittel (41) zum Detektieren einer Einlasstemperatur eines Mediums, das erwärmt werden soll, und ein viertes Temperaturdetektionsmittel (42) zum Detektieren einer Auslasstemperatur des Mediums, das erwärmt werden soll, vorgesehen sind, dadurch gekennzeichnet, dass
    ein Öffnungsgrad des Dekampressionsmittels (3) so gesteuert wird, dass ein Unterschied (ΔT1 - ΔT2) zwischen einem zweiten Temperaturunterschied (ΔT1) zwischen einer Detektionstemperatur durch das erste Temperaturdetektionsmittel (30) und der Detektionstemperatur durch das vierte Temperaturdetektionsmittel (42) und einem dritten Temperaturunterscheid (ΔT2) zwischen der Detektionstemperatur durch das zweite Temperaturdetektionsmittel (31) und der Detektionstemperatur durch das dritte Temperaturdetektionsmittel (41) einen Sollwert annimmt.
  2. Kühlmittelkreislaufvorrichtung nach Anspruch 1, wobei
    ein sechstes Temperaturdetektionsmittel (33) zum Detektieren der Kühlmitteltemperatur zwischen einem Auslass auf der Niederdruckseite des inneren Wärmetauschers (5) und einem Einlass des Kompressors (1) vorgesehen ist,
    ein Überhitzungsgrad eines Kompressor-Saugelements aus einer Kühlmittelsättigungstemperatur bei einem Detektionspunkt des sechsten Temperaturdetektionsmittels (33) und einer Detektionstemperatur durch das sechste Temperaturdetektionsmittel (33) berechnet wird, und
    der Öffnungsgrad der Dekompressionsmittel (3) so gesteuert wird, dass der Überhitzungsgrad den Sollwert einnimmt.
  3. Kühlmittelkreislaufvorrichtung nach Anspruch 2, wobei
    ein zweites Druckdetektionsmittel (51) zwischen dem Auslass auf der Niederdruckseite des inneren Wärmetauschers (5) und dem Einlass des Kompressors (1) vorgesehen ist, und
    die Kühlmittelsättigungstemperatur auf Basis eines Detektionswerts des zweiten Druckdetektionsmittels (51) berechnet wird.
  4. Kühlmittelkreislaufvorrichtung nach Anspruch 2, wobei
    ein fünftes Temperaturdetektionsmittel (32) zwischen dem Einlass des Wärmeabsorbers (4) und dem Einlass auf der Niederdruckseite des inneren Wärmetauschers (5) vorgesehen ist, und
    die Kühlmittelsättigungstemperatur auf Basis der Detektionstemperatur des fünften Temperaturdetektionsmittels (32) berechnet wird.
  5. Kühlmittelkreislaufvorrichtung nach einem der Ansprüche 2 bis 4, wobei
    der Steuerung des Überhitzungsgrads gegenüber der des Temperaturunterschieds Priorität eingeräumt wird.
  6. Kühlmittelkreislaufvorrichtung nach einem der Ansprüche 1 bis 5, wobei
    der Radiator (2) ein Wärmetauscher ist, der Wärme mit Wasser tauscht.
  7. Kühlmittelkreislaufvorrichtung nach einem der Ansprüche 1 bis 6, wobei
    Kohlenstoffdioxid als ein Kühlmittel verwendet wird.
EP13166592.9A 2007-11-30 2008-11-20 Kältekreislaufvorrichtung Active EP2647925B1 (de)

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 (de) 2007-11-30 2008-11-20 Kühlkreislaufvorrichtung

Related Parent Applications (3)

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

Publications (3)

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

Family

ID=40678426

Family Applications (5)

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

Family Applications Before (3)

Application Number Title Priority Date Filing Date
EP08855672.5A Active EP2196745B1 (de) 2007-11-30 2008-11-20 Kühlkreislaufvorrichtung
EP13166595.2A Active EP2647927B1 (de) 2007-11-30 2008-11-20 Kältekreislaufvorrichtung
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EP2196745B1 (de) 2017-11-08
EP2647927A3 (de) 2015-07-29
CN101842645A (zh) 2010-09-22
EP2196745A4 (de) 2013-02-13
ES2605462T3 (es) 2017-03-14
EP2647926A2 (de) 2013-10-09
ES2611980T3 (es) 2017-05-11
EP2647925A2 (de) 2013-10-09
DK2647928T3 (en) 2016-12-12
DK2647926T3 (en) 2019-01-07
DK2196745T3 (en) 2017-12-11
ES2700938T3 (es) 2019-02-20
DK2647925T3 (en) 2017-02-06
DK2647927T3 (da) 2020-10-19
CN102425872A (zh) 2012-04-25
US20100205987A1 (en) 2010-08-19
EP2647928A2 (de) 2013-10-09
CN102425872B (zh) 2014-06-25
EP2647926B1 (de) 2018-10-24
EP2647927B1 (de) 2020-09-16
EP2647927A2 (de) 2013-10-09
CN101842645B (zh) 2012-11-28
EP2647928B1 (de) 2016-10-26
EP2647926A3 (de) 2015-07-29
WO2009069524A1 (ja) 2009-06-04
JP4948374B2 (ja) 2012-06-06
JP2009133547A (ja) 2009-06-18
ES2650233T3 (es) 2018-01-17
EP2647928A3 (de) 2015-08-05
EP2647925A3 (de) 2015-08-05
EP2196745A1 (de) 2010-06-16
ES2823758T3 (es) 2021-05-10

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