EP3318820B1 - Dispositif de cycle frigorifique - Google Patents

Dispositif de cycle frigorifique Download PDF

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Publication number
EP3318820B1
EP3318820B1 EP16817487.8A EP16817487A EP3318820B1 EP 3318820 B1 EP3318820 B1 EP 3318820B1 EP 16817487 A EP16817487 A EP 16817487A EP 3318820 B1 EP3318820 B1 EP 3318820B1
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EP
European Patent Office
Prior art keywords
heat exchanger
pressure
refrigerant
compressor
temperature sensor
Prior art date
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Application number
EP16817487.8A
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German (de)
English (en)
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EP3318820A1 (fr
EP3318820A4 (fr
Inventor
Masazumi Chisaki
Satoru Yanachi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3318820A4 publication Critical patent/EP3318820A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2500/31—Low ambient temperatures
    • 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
    • F25B2700/1931—Discharge 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
    • F25B2700/19—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
    • F25B2700/2115—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
    • F25B2700/21153—Temperatures of a compressor or the drive means therefor of electronic components
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus, and in particular, relates to a refrigeration cycle apparatus capable of performing gas injection to improve heating capacity in a low outside air temperature.
  • Patent Literature 1 discloses an example using the technique.
  • a heat pump water heater has as an object to prevent decrease in heating capacity even in a low outside air temperature, and has a refrigerant circuit including a compressor having an injection port, a load-side heat exchanger, an internal heat exchanger, a pressure vessel, a heat-source side heat exchanger, and an expansion device. Then, technical details for calculating subcooling (a degree of subcooling) at an outlet of the load-side heat exchanger and feeding the calculated subcooling back to control of the expansion device are described.
  • EP 2 119 984 A2 discloses an apparatus according to the preamble of claim 1 and is directed to a refrigeration/air conditioning equipment that includes a first internal heat exchanger for exchanging heat between a refrigerant to be sucked in a compressor and a high-pressure liquid refrigerant, an injection circuit for evaporating a bypassed high-pressure liquid at intermediate pressure and injecting the vaporized refrigerant into the compressor, a second internal heat exchanger for exchanging heat between the high-pressure liquid refrigerant and the refrigerant to be injected, and a heat source for heating the refrigerant to be injected.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2009-186121
  • heating capacity is controlled by calculating subcooling from a measured value of a discharge pressure measured by a discharge pressure sensor and a measured value of a refrigerant temperature measured by a temperature sensor provided at an outlet of a load-side heat exchanger and controlling an expansion device on the basis of the subcooling. Consequently, for exerting a capability of a refrigeration cycle apparatus, it is necessary to calculate the subcooling with accuracy.
  • the load-side heat exchanger and the internal heat exchanger are configured separately, and, as the temperature sensor for measuring a measured temperature value used for calculating the subcooling, a temperature sensor provided between the load-side heat exchanger and the internal heat exchanger is used.
  • a temperature sensor provided between the load-side heat exchanger and the internal heat exchanger is used.
  • the internal heat exchanger is placed directly downstream of the load-side heat exchanger, or, when the load-side heat exchanger and the internal heat exchanger will be integrally configured in future for responding to recent downsizing requests, it is impossible to provide the temperature sensor between the load-side heat exchanger and the internal heat exchanger. In this case, a problem of incapability to calculate the subcooling occurs.
  • the present invention has been made in consideration of the above situation and has as an object to provide a refrigeration cycle apparatus capable of calculating subcooling without using a refrigerant temperature between a load-side heat exchanger and an internal heat exchanger.
  • a refrigeration cycle apparatus according to the present invention is disclosed in independent claim 1. Further preferred embodiments are defined by the dependent claims.
  • a refrigeration cycle apparatus capable of calculating subcooling without using a refrigerant temperature between a load-side heat exchanger and an internal heat exchanger.
  • Fig. 1 is a system configuration view of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the air-conditioning apparatus can switch the cooling operation and the heating operation by switching a four-way valve 2.
  • the present invention can be applied to the heating operation, the following description will be focused on the heating operation.
  • the air-conditioning apparatus includes a refrigerant circuit provided with a compressor 1, the four-way valve 2, a load-side heat exchanger 3, a high-pressure side flow path of an internal heat exchanger 4, an expansion device 5, a pressure vessel 6, an expansion device 7, and a heat-source side heat exchanger 8.
  • the refrigerant circuit of the refrigeration cycle apparatus according to the present invention is not limited to the refrigerant circuit in Fig. 1 .
  • the refrigerant circuit of the refrigeration cycle apparatus may include at least the compressor 1, the load-side heat exchanger 3, the high-pressure side flow path of the internal heat exchanger 4, the expansion device (a first expansion device), and the heat-source side heat exchanger 8.
  • the air-conditioning apparatus further includes an injection circuit 15 that branches from between the internal heat exchanger 4 and the expansion device 5 to be connected to the compressor 1 for injection performed during compression.
  • the injection circuit 15 is provided with an expansion device (a second expansion device) 9 and a low-pressure side flow path of the internal heat exchanger 4.
  • the load-side heat exchanger 3 is disposed in an indoor unit (not shown), and the heat-source side heat exchanger 8 is disposed in an outdoor unit (not shown).
  • Fig. 1 a state in which the load-side heat exchanger 3 and the internal heat exchanger 4 are configured separately is shown; however, the load-side heat exchanger 3 and the internal heat exchanger 4 may be configured integrally.
  • the refrigerant circuit described above is provided with a discharge temperature sensor 11, an internal heat exchanger outlet temperature sensor 12, a suction temperature sensor 13, a discharge pressure sensor 14, and a heat-source side heat exchanger temperature sensor 16.
  • the discharge temperature sensor 11 measures the temperature of refrigerant discharged from the compressor 1.
  • the internal heat exchanger outlet temperature sensor 12 measures the temperature of refrigerant having flowed from the high-pressure side flow path of the internal heat exchanger 4.
  • the suction temperature sensor 13 measures the temperature of refrigerant to be sucked into the compressor 1.
  • the discharge pressure sensor 14 measures the pressure of refrigerant discharged from the compressor 1.
  • the heat-source side heat exchanger temperature sensor 16 is disposed in the heat-source side heat exchanger 8 and measures the temperature of refrigerant flowing inside the heat-source side heat exchanger 8.
  • the heat-source side heat exchanger temperature sensor 16 is disposed on an inlet side of the heat-source side heat exchanger 8, to be specific, at the middle part of the entire length of the pipe of the heat-source side heat exchanger 8 or on an inlet side of the middle part to make it possible to measure the evaporating temperature of the refrigerant in the two-phase state.
  • the suction pressure of refrigerant to be sucked into the compressor 1 can be obtained by saturation pressure conversion of the temperature measured by the heat-source side heat exchanger temperature sensor 16, the heat-source side heat exchanger temperature sensor 16 corresponds to a suction pressure detection device according to the present invention.
  • the refrigerant circuit further includes a controller 20.
  • the controller 20 is connected to various kinds of sensors to be able to receive measurement signals from the various kinds of sensors in the air-conditioning apparatus. Then, the controller 20 calculates subcooling SC at the outlet of the load-side heat exchanger 3 on the basis of the measurement signals from the various kinds of sensors and other information and feeds the calculated subcooling SC back to control of the expansion device 5. Intended air-conditioning capability can be exerted by controlling the expansion device 5 on the basis of the subcooling SC.
  • the controller 20 can be composed of hardware, such as a circuit device that implements functions of the controller 20, or can be composed of a computing device, such as a microcomputer and a CPU, and software executed on the computing device.
  • Fig. 2 is a p-h diagram showing action in the refrigerant circuit of the air-conditioning apparatus in heating operation according to Embodiment 1 of the present invention.
  • the horizontal axis indicates specific enthalpy [kJ/kg], and the vertical axis indicates a refrigerant pressure [MPa].
  • the reference signs A to F in Fig. 1 correspond to the reference signs A to F in Fig. 2 (the states I and J are not shown in Fig. 1 ).
  • gas refrigerant of high temperature and high pressure (the state A) discharged from the compressor 1 passes through the four-way valve 2 to flow into the load-side heat exchanger 3.
  • the gas refrigerant of high temperature and high pressure is subjected to heat exchange in the load-side heat exchanger 3 to be liquid refrigerant of low temperature and high pressure in a subcooled state (the state B).
  • the liquid refrigerant having flowed from the load-side heat exchanger 3 flows into the internal heat exchanger 4.
  • the high-pressure side refrigerant having flowed from the load-side heat exchanger 3 and having flowed into the high-pressure side flow path of the internal heat exchanger 4 exchanges heat with low-pressure side refrigerant in the low-pressure side flow path of the internal heat exchanger 4, and thereby, the high-pressure side refrigerant having flowed into the high-pressure side flow path of the internal heat exchanger 4 is cooled (the state C).
  • a part of the refrigerant having flowed from the high-pressure side flow path of the internal heat exchanger 4 is branched to the injection circuit 15 while a mainstream of the refrigerant flows into the expansion device 5 to be subjected to pressure reduction (the state E).
  • the refrigerant subjected to pressure reduction in the expansion device 5 flows into the pressure vessel 6.
  • the refrigerant provides heat to the low-temperature refrigerant on the suction side of the compressor 1 to lower the temperature of the refrigerant, and becomes liquid refrigerant to flow out (the state F).
  • the refrigerant having flowed from the pressure vessel 6 is subjected to pressure reduction in the expansion device 7 (the state G), and then, flows into the heat-source side heat exchanger 8.
  • the refrigerant having flowed into the heat-source side heat exchanger 8 exchanges heat with outside air and absorbs heat to be low-pressure gas refrigerant. Subsequently, the low-pressure gas refrigerant passes through the four-way valve 2, exchanges heat with high-pressure refrigerant in the pressure vessel 6, and is further heated (the state H) to be sucked into the compressor 1.
  • the refrigerant branched to the injection circuit 15 is subjected to pressure reduction in the expansion device 9 to an intermediate pressure (the state D), flows into the low-pressure side flow path of the internal heat exchanger 4, and exchanges heat with refrigerant in the high-pressure side flow path to be heated (the state K).
  • the compressor 1 sucks the low-pressure gas refrigerant heated in the pressure vessel 6 (the state H) and compresses the refrigerant to an intermediate pressure (the state I). Moreover, the compressor 1 sucks the refrigerant injected from the injection circuit 15 (the state K). Consequently, in the compressor 1, the refrigerant in the state I and the refrigerant in the state K merge to be refrigerant in the state J.
  • the refrigerant in the state J is subjected to pressure rise to high pressure and discharged from the compressor 1 (the state A).
  • the subcooling SC at the outlet of the load-side heat exchanger 3 can be calculated by the following expression.
  • Subcooling SC "condensing temperature of refrigerant” ⁇ "outlet temperature of load-side heat exchanger 3: temperature in state B"
  • condensing temperature of refrigerant can be obtained by saturation temperature conversion of the measured pressure by the discharge pressure sensor 14.
  • temperature in state B is obtained from, when the load-side heat exchanger 3 and the internal heat exchanger 4 are separately configured, the temperature sensor provided at the outlet of the load-side heat exchanger 3.
  • the load-side heat exchanger 3 and the internal heat exchanger 4 are integrally configured, it is impossible to attach the temperature sensor to the outlet of the load-side heat exchanger 3.
  • the load-side heat exchanger 3 and the internal heat exchanger 4 are separately configured, a case is assumed in which the temperature sensor is not attached to the outlet of the load-side heat exchanger 3 from the standpoint of, for example, reducing the number of sensors.
  • the enthalpy in the state B is calculated on the assumption that the heat exchange amount Q1 in the high-pressure side flow path of the internal heat exchanger 4 in the state B to the state C in Fig. 2 is equal to the heat exchange amount Q2 in the low-pressure side flow path of the internal heat exchanger 4 in the state D to the state K in Fig. 2 .
  • the enthalpy at the outlet of the high-pressure side flow path of the internal heat exchanger 4 (the state C) is obtained from the measured temperature of the internal heat exchanger outlet temperature sensor 12 and the measured pressure of the discharge pressure sensor 14. Moreover, the enthalpy in the state D is the same as the enthalpy in the state C. Consequently, when the enthalpy in the state K is obtained, it is possible to obtain the heat exchange amount Q2 in the low-pressure side flow path of the internal heat exchanger 4.
  • the enthalpy in the state K can be obtained by using the fact that the refrigerant in the state K and the refrigerant in the state I merge inside the compressor 1 to be the refrigerant in the state J.
  • the enthalpy in each of the state I and the state J can be obtained by using the suction pressure resulting from the saturation pressure conversion of the temperature measured by the heat-source side heat exchanger temperature sensor 16, the suction temperature measured by the suction temperature sensor 13, the discharge pressure measured by the discharge pressure sensor 14, the discharge temperature measured by the discharge temperature sensor 11, and the position of an injection port 10 in a compression chamber in the compressor 1.
  • "Position of an injection port 10 in a compression chamber in the compressor 1" means that, for example, when a scroll compressor is taken as an example, a position (phase angle) at which the injection port 10 is placed in a scroll-shaped cylinder that forms the compression chamber.
  • the enthalpy in the state K can be obtained from the enthalpies in the state I and the state J.
  • the heat exchange amount Q2 in the internal heat exchanger 4 can be obtained on the basis of the obtained enthalpy in the state K.
  • the enthalpy in the state B can be obtained.
  • the temperature in the state B can be obtained from the enthalpy in the state B calculated as described above and the pressure in the state B obtained by the discharge pressure sensor 14, and consequently, the subcooling SC can be obtained by the above [Expression 1].
  • Embodiment 1 of the present invention without using the refrigerant temperature between the load-side heat exchanger 3 and the internal heat exchanger 4, it is possible to calculate the subcooling SC by use of the measured value of each of the discharge temperature sensor 11, the internal heat exchanger outlet temperature sensor 12, the suction temperature sensor 13, the discharge pressure sensor 14, and the heat-source side heat exchanger temperature sensor 16, and the position of the injection port 10. Consequently, even in a configuration in which the temperature sensor cannot be provided between the load-side heat exchanger 3 and the internal heat exchanger 4 due to the internal heat exchanger 4 being placed immediately downstream of the load-side heat exchanger 3 or the load-side heat exchanger 3 and the internal heat exchanger 4 being configured integrally, it is possible to calculate the subcooling SC.
  • Embodiment 1 of the present invention description is given by taking the air-conditioning apparatus as an example; however, the present invention can be used for other arbitrary facility appliances.
  • the present invention is applicable to facility appliances, such as a water heater and a water cooler.
  • the heat-source side heat exchanger temperature sensor 16 is described to correspond to the suction pressure detection device of the present invention; however, the suction pressure detection device may be configured as follows. That is, as indicated by the dotted line in Fig. 1 , a suction pressure sensor 17 that measures the suction pressure of the refrigerant to be sucked into the compressor 1 is provided on the suction side of the compressor 1, and the suction pressure sensor 17 may correspond to the suction pressure detection device of the present invention. Moreover, in Fig.
  • the suction pressure sensor 17 is provided between the compressor 1 and the pressure vessel 6; however, the suction pressure sensor 17 may be provided between the pressure vessel 6 and the four-way valve 2, or, when the case is limited to the heating operation, between the four-way valve 2 and the heat-source side heat exchanger 8.
  • compressor 2 four-way valve 3 load-side heat exchanger 4 internal heat exchanger 5 expansion device 6 pressure vessel 7 expansion device 8 heat-source side heat exchanger 9 expansion device 10 injection port 11 discharge temperature sensor 12 internal heat exchanger outlet temperature sensor 13 suction temperature sensor 14 discharge pressure sensor 15 injection circuit 16 heat-source side heat exchanger temperature sensor 17 suction pressure sensor 20 controller

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (3)

  1. Appareil à cycle de réfrigération comprenant :
    un circuit de réfrigération incluant un compresseur (1), un échangeur de chaleur côté charge (3), un passage côté haute pression d'un échangeur de chaleur interne (4), un premier dispositif d'expansion (5), et un échangeur de chaleur côté source de chaleur (8) ;
    un circuit d'injection (15) qui se sépare entre l'échangeur de chaleur interne (4) et le premier dispositif d'expansion (5) et relié à un port d'injection (10) du compresseur (1) par l'intermédiaire d'un second dispositif d'expansion (9) et d'un passage côté basse pression de l'échangeur de chaleur interne (4) ;
    un capteur de température d'aspiration (13) mesurant une température d'aspiration du compresseur (1) ;
    un capteur de température de libération (11) mesurant une température de libération du compresseur (1) ; et
    un dispositif de commande (20) ;
    caractérisé en ce que
    l'appareil à cycle de réfrigération comprend en outre :
    un dispositif de détection de la pression d'aspiration mesurant une pression d'aspiration du compresseur (1) ;
    un capteur de pression de libération (14) mesurant une pression de libération du compresseur (1) ; et
    un capteur de température de sortie d'échangeur de chaleur interne (12) disposé au niveau d'une sortie du passage côté haute pression de l'échangeur de chaleur interne (4) et mesurant une température de réfrigération au niveau de la sortie du passage côté haute pression ;
    dans lequel le dispositif de commande (20) est conçu pour calculer le sous-refroidissement au niveau d'une sortie de l'échangeur de chaleur côté charge (3) en utilisant une valeur mesurée de chacun du capteur de température d'aspiration (13), du dispositif de détection de pression d'aspiration, du capteur de température de libération (11), du capteur de pression de libération (14) et du capteur de température de sortie de l'échangeur de chaleur interne (12), et les informations liées à une position du port d'injection (10) dans une unité de compression du compresseur (1), et
    dans lequel le dispositif de commande est conçu pour
    - calculer une enthalpie du réfrigérant au niveau de la sortie du passage côté basse pression de l'échangeur de chaleur interne (4) en utilisant la pression d'aspiration, la température d'aspiration mesurée par le capteur de température d'aspiration (13), la pression de libération mesurée par le capteur de pression de libération (14), la température de libération mesurée par le capteur de température de libération (11), et la position du port d'injection (10) dans une chambre de compression dans le compresseur (1),
    - calculer une enthalpie du réfrigérant au niveau de la sortie du passage côté haute pression de l'échangeur de chaleur interne (4) en utilisant la température mesurée par le capteur de température de sortie de l'échangeur de chaleur interne (12) et la pression de libération mesurée par le capteur de pression de libération (14),
    - calculer une enthalpie du réfrigérant au niveau de la sortie de l'échangeur de chaleur côté charge (3) en utilisant l'enthalpie du réfrigérant au niveau de la sortie du passage côté basse pression de l'échangeur de chaleur interne (4) et l'enthalpie du réfrigérant au niveau de la sortie du passage côté haute pression de l'échangeur de chaleur interne (4), en supposant que la quantité d'échange de chaleur dans le passage côté basse pression de l'échangeur de chaleur interne (4) est égale à la quantité d'échange de chaleur dans le passage côté haute pression de l'échangeur de chaleur interne (4), et
    - calculer le sous-refroidissement en utilisant l'enthalpie du réfrigérant au niveau de la sortie de l'échangeur de chaleur côté charge (3) et la valeur mesurée du capteur de pression de libération (14).
  2. Appareil à cycle de réfrigération selon la revendication 1, dans lequel le dispositif de détection de pression d'aspiration inclut un capteur de température d'échangeur de chaleur côté source de chaleur (16) mesurant une température de réfrigération au niveau d'un côté d'entrée de l'échangeur de chaleur côté source de chaleur (8) pour obtenir la pression d'aspiration par conversion de saturation d'une température mesurée du capteur de température d'échangeur de chaleur côté source de chaleur (16).
  3. Appareil à cycle de réfrigération selon la revendication 1, dans lequel le dispositif de détection de pression d'aspiration comprend un capteur de pression d'aspiration (17) mesurant la pression d'aspiration du compresseur (1).
EP16817487.8A 2015-07-01 2016-02-03 Dispositif de cycle frigorifique Active EP3318820B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/JP2015/069039 WO2017002238A1 (fr) 2015-07-01 2015-07-01 Dispositif de cycle frigorifique
PCT/JP2016/053144 WO2017002377A1 (fr) 2015-07-01 2016-02-03 Dispositif de cycle frigorifique

Publications (3)

Publication Number Publication Date
EP3318820A1 EP3318820A1 (fr) 2018-05-09
EP3318820A4 EP3318820A4 (fr) 2019-02-20
EP3318820B1 true EP3318820B1 (fr) 2021-12-22

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CN107143953B (zh) * 2017-05-19 2019-06-14 广东志高暖通设备股份有限公司 一种喷气增焓空调系统
CN107165814B (zh) * 2017-05-27 2018-12-25 珠海格力电器股份有限公司 双压缩机制冷空调系统的控制方法及装置
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JP6362780B2 (ja) 2018-07-25
EP3318820A1 (fr) 2018-05-09
WO2017002377A1 (fr) 2017-01-05
EP3318820A4 (fr) 2019-02-20
WO2017002238A1 (fr) 2017-01-05
JPWO2017002377A1 (ja) 2017-11-02

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