EP2535674B1 - Appareil de cycle de réfrigération et dispositif de chauffage hydronique utilisant l'appareil de cycle de réfrigération - Google Patents

Appareil de cycle de réfrigération et dispositif de chauffage hydronique utilisant l'appareil de cycle de réfrigération Download PDF

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Publication number
EP2535674B1
EP2535674B1 EP12171898.5A EP12171898A EP2535674B1 EP 2535674 B1 EP2535674 B1 EP 2535674B1 EP 12171898 A EP12171898 A EP 12171898A EP 2535674 B1 EP2535674 B1 EP 2535674B1
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Prior art keywords
compressor
refrigerant
temperature
refrigeration cycle
rotations
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EP12171898.5A
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German (de)
English (en)
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EP2535674A2 (fr
EP2535674A3 (fr
Inventor
Shunji Moriwaki
Shigeo Aoyama
Michiyoshi Kusaka
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Panasonic Corp
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Panasonic Corp
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    • 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
    • F25B49/025—Motor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • 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
    • F25B2600/2509—Economiser 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
    • F25B2600/25—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
    • F25B2700/21—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
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers

Definitions

  • the present invention relates to a refrigeration cycle apparatus which bypasses a portion of a refrigerant flowing out from a radiator, which heat-exchanges between a mainstream refrigerant and a bypassing refrigerant, thereby supercooling the mainstream refrigerant.
  • a supercooling heat exchanger is provided at a location downstream of a radiator of a refrigerant circuit, an expanded refrigerant is made to flow into the supercooling heat exchanger, thereby supercooling the refrigerant which flows out from the radiator (see patent document 1 for example).
  • Fig. 6 shows the conventional refrigeration cycle apparatus described in patent document 1.
  • a refrigeration cycle apparatus 100 includes a refrigerant circuit 110 through which a refrigerant is circulated, and a bypass passage 120.
  • the refrigerant circuit 110 includes a compressor 111, a radiator 112, a supercooling heat exchanger 113, a main expansion valve 114 and an evaporator 115 which are annularly connected to one another through pipes.
  • the refrigeration cycle apparatus 100 includes a temperature sensor 141 which detects a temperature (compressor discharge pipe temperature) Td of a refrigerant discharged from the compressor 111, a temperature sensor 142 which detects a temperature (evaporator inlet temperature) Te of a refrigerant flowing into the evaporator 115, a temperature sensor 143 which detects a temperature (bypass-side inlet temperature) Tbi of a refrigerant flowing into the supercooling heat exchanger 113 in the bypass passage 120, and a temperature sensor 144 which detects a temperature (bypass-side outlet temperature) Tbo of a refrigerant flowing out from the supercooling heat exchanger 113 in the bypass passage 120.
  • a temperature sensor 141 which detects a temperature (compressor discharge pipe temperature) Td of a refrigerant discharged from the compressor 111
  • a temperature sensor 142 which detects a temperature (evaporator inlet temperature) Te of a refrigerant flowing into the evaporator
  • a target temperature Td (target) of a discharge pipe of the compressor is set by an evaporator inlet temperature Te which is detected by the temperature sensor 142.
  • a main expansion valve control unit controls the main expansion valve 114 such that a discharge pipe temperature Td detected by the temperature sensor 141 becomes equal to the target temperature Td (target).
  • a bypass expansion valve control unit controls the bypass expansion valve 121 such that a difference (Tbo-Tbi) between the bypass-side outlet temperature Tbo and the bypass-side inlet temperature Tbi in the supercooling heat exchanger 113 becomes equal to a predetermined target value.
  • Patent Document 2 forming the closest prior art from which the present invention starts, discloses a refrigeration cycle apparatus which includes a refrigeration circuit provided with a subcooling heat exchanger, a bypass passage extending through the subcooling heat exchanger, and a controller for controlling a main expansion means in the refrigerant circuit and a bypass expansion means in the bypass passage.
  • the bypass expansion means is controlled so that a bypass side outlet temperature conforms to saturation temperature at a pressure of a refrigerant to be drawn into a compressor, and a degree of superheat at an outlet of an evaporator calculated based on an evaporator outlet temperature is equal to or lower than a predetermined degree of super heat.
  • bypass expansion valve 121 provided in the bypass passage 120 operates to control a temperature difference between an inlet and an outlet of the bypass passage 120, that is, degree of superheat at the outlet of the bypass passage 120, control cannot be performed such that the refrigerant state at the outlet of the bypass passage 120 is brought into a moist state.
  • the bypass passage 120 can not be used, and the operation efficiency enhancing effect exerted when the bypass passage 120 is used can not be obtained. Therefore, the conventional apparatus has a problem that efficiency is poor and sufficient heating ability can not be secured.
  • the present invention has been accomplished to solve the conventional apparatus, and it is an object of the invention to provide a refrigeration cycle apparatus and a hydronic heater having the refrigeration cycle apparatus capable of securing efficiency and sufficient heating ability even when an outside air temperature is low by controlling the refrigeration cycle apparatus into an appropriate refrigeration cycle state.
  • this refrigeration cycle apparatus in a low number of rotation state in which a compression ratio of the compressor is small, control is performed such that a state of the refrigerant at the outlet of the bypass passage is brought from an overheated state to a saturated state and then, the number of rotations of the compressor is increased in stages while bypassing a gas/liquid two-phase refrigerant. Therefore, it is possible to restrain the discharge temperature of the compressor from rising abnormally.
  • the present invention it is possible to provide a refrigeration cycle apparatus and a hydronic heater having the refrigeration cycle apparatus capable of securing efficiency and sufficient heating ability even when an outside air temperature is low by controlling the refrigeration cycle apparatus into an appropriate refrigeration cycle state.
  • a first aspect of the invention provides a refrigeration cycle apparatus comprising a refrigerant circuit in which a compressor, a radiator, a supercooling heat exchanger, main expansion means and an evaporator are annularly connected to one another, a bypass passage which branches off from the refrigerant circuit between the radiator and the main expansion means, and which is connected to the compressor through the supercooling heat exchanger or connected to the refrigerant circuit between the evaporator and the compressor, bypass expansion means provided in the bypass passage at a location upstream of the supercooling heat exchanger, a first temperature sensor which detects a temperature of a refrigerant flowing out from the supercooling heat exchanger, saturation temperature detecting means which detects a saturation temperature of a refrigerant sucked into the compressor, and a control device, wherein the control device controls operation of the bypass expansion means such that a temperature detected by the first temperature sensor becomes equal to the saturation temperature detected by the saturation temperature detecting means until a number of rotations of the compressor reaches a predetermined target number
  • control is performed such that a state of the refrigerant at the outlet of the bypass passage is brought from an overheated state to a saturated state and then, the number of rotations of the compressor is increased in stages while bypassing a gas/liquid two-phase refrigerant. Therefore, it is possible to restrain the discharge temperature of the compressor from rising abnormally.
  • the refrigeration cycle apparatus further includes a second temperature sensor which detects a temperature of a refrigerant discharged from the compressor, the control device operates an opening degree of the main expansion means into a closing direction when a temperature detected by the second temperature sensor becomes equal to or higher than a predetermined temperature.
  • the refrigeration cycle apparatus of the second aspect when a refrigerant flows to the bypass passage, it is determined that the discharge temperature rises, and the main expansion means is closed by a predetermined amount. Hence, the flow rate of the refrigerant flowing toward the bypass passage is swiftly increased, and it is possible to control an excessive overheated state of a refrigerant at the outlet of the bypass passage into a saturated state within shorter time.
  • a third aspect of the invention provides a hydronic heater having the refrigeration cycle apparatus according the first or second aspect.
  • the present invention can be applied not only to a case where the radiator is a heat exchanger between refrigerant and air, but also to a case where the radiator is a heat exchanger between refrigerant and water.
  • the same effect as that of the first or second invention can be obtained.
  • Fig. 1 is a schematic block diagram of a hydronic heater having a refrigeration cycle apparatus according to an embodiment of the invention.
  • the refrigeration cycle apparatus 1A includes a refrigerant circuit 2 through which a refrigerant is circulated, a bypass passage 3 connected to the refrigerant circuit 2, and a control device 4 which controls the refrigerant circuit 2 and the bypass passage 3.
  • a refrigerant used in the invention it is possible to use a zeotropic refrigerant mixture such as R407C, a pseudo-azeotropic refrigerant mixture such as R410A or a single refrigerant.
  • the refrigerant circuit 2 provided in the refrigeration cycle apparatus 1A includes a compressor 21, a radiator 22, a supercooling heat exchanger 23, a main expansion valve (main expansion means) 24 and an evaporator 25, and these constituent members are annularly connected to one another through pipes.
  • a sub-accumulator 26 and a main accumulator 27 which separate gas and liquid from each other are provided between the evaporator 25 and the compressor 21 which are annularly connected to each other through a pipe.
  • the refrigerant circuit 2 is provided with a four-way valve 28 which switches between a normal operation and a defrosting operation of the refrigeration cycle apparatus.
  • the refrigeration cycle apparatus 1A configures heating means of a hydronic heater which utilizes hot water produced by the heating means for heating a room, and the radiator 22 provided in the refrigerant circuit 2 is a heat exchanger which exchanges heat between a refrigerant and water to heat the water.
  • the hot water collected through the collecting pipe 72 connected to the radiator 22 is sent directly to a heater, or sent to the heater through a hot water tank, thereby heating a room.
  • the bypass passage 3 connected to the refrigerant circuit 2 branches off from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve (main expansion means) 24, and is connected to the refrigerant circuit 2 between the sub-accumulator 26 and the main accumulator 27 between the evaporator 25 and the compressor 21 through the supercooling heat exchanger 23.
  • bypass passage 3 may branch off from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve (main expansion means) 24, and connected to a compression chamber suction inlet in the compressor 21 through the supercooling heat exchanger 23.
  • a refrigerant discharged from the compressor 21 is sent to the radiator 22 through the four-way valve 28.
  • a refrigerant discharged from the compressor 21 is sent to the evaporator 25 through the four-way valve 28.
  • arrows show a flowing direction of a refrigerant at the time of the normal operation.
  • a high-pressure refrigerant discharged from the compressor 21 configuring the refrigerant circuit 2 flows into the radiator 22, and radiates heat to water which passes through the radiator 22.
  • the high-pressure refrigerant which flows out from the radiator 22 flows into the supercooling heat exchanger 23, and the refrigerant is supercooled by a low-pressure refrigerant which is decompressed by the bypass expansion valve 31.
  • the high-pressure refrigerant which flows out from the supercooling heat exchanger 23 is distributed to the main expansion valve 24 and the bypass expansion valve 31.
  • the high-pressure refrigerant distributed to the main expansion valve 24 (main expansion means) is decompressed by the main expansion valve 24 and expanded and then, the refrigerant flows into the evaporator 25.
  • the low-pressure refrigerant which flows into the evaporator 25 absorbs heat from air in the evaporator 25.
  • the high-pressure refrigerant distributed to the bypass expansion valve (bypass expansion means) 31 is decompressed by the bypass expansion valve 31 and expanded and then, the refrigerant flows into the supercooling heat exchanger 23.
  • the low-pressure refrigerant which flows into the supercooling heat exchanger 23 is heated by the high-pressure refrigerant which flows out from the radiator 22. Thereafter, the low-pressure refrigerant which flows out from the supercooling heat exchanger 23 merges with the low-pressure refrigerant which flows out from the evaporator 25, and these refrigerants are again sucked into the compressor 21.
  • the configuration of the refrigeration cycle apparatus 1A of the embodiment is for avoiding a case where pressure of a refrigerant sucked into the compressor 21 is reduced when an outside air temperature is low, a refrigerant circulation amount is reduced and according to this, heating ability of the radiator 22 is prevented from being deteriorated.
  • an enthalpy difference in the evaporator 25 is increased by supercooling.
  • a refrigerant is made to flow to the bypass passage 3 through the bypass passage 3, thereby suppressing an amount of a gas-phase refrigerant which has a small heat-absorbing effect and which flows through a low-pressure side portion of the refrigerant circuit 2.
  • control device 4 which controls the refrigerant circuit 2 and the bypass passage 3 operates the bypass expansion valve 31 such that the outlet refrigerant of the bypass passage 3 is brought into the saturated state.
  • control is performed such that the number of rotations is increased to a next stage number of rotations of the compressor.
  • control device 4 controls such that the main expansion valve 24 operates in a closing direction by a predetermined value.
  • the refrigerant circuit 2 configuring the refrigeration cycle apparatus includes a pressure sensor 51 which detects a pressure (suction pressure) Ps of a refrigerant sucked into the compressor 21, and a second pressure sensor 62 which detects a temperature (discharge temperature) Td of a refrigerant discharged from the compressor 21.
  • the bypass passage 3 connected to the refrigerant circuit 2 includes a first temperature sensor 61 which detects a temperature (bypass passage outlet temperature) Tbo of a refrigerant flowing out from the supercooling heat exchanger 23.
  • the control device 4 operates the number of rotations of the compressor 21, carries out the switching operation of the four-way valve 28, and adjusts opening degrees of the main expansion valve 24 and the bypass expansion valve 31 based on detection values detected by the various sensors 51, 61 and 62.
  • the control device 4 When the operation of the refrigeration cycle apparatus is started, the control device 4 operates the compressor 21 at the actuation number of rotations Hzi which is lower than the preset predetermined compressor target number of rotations Hzt, and when the bypass passage outlet temperature Tbo becomes equal to the suction saturation temperature Ts, the control device 4 rises the number of rotations of the compressor 21 by a predetermined amount and operates the compressor 21. This operation is repeated until the number of rotations of the compressor reaches the compressor target number of rotations Hzt.
  • the control device 4 When the discharge temperature Td which is a temperature of a refrigerant discharged from the compressor 21 becomes higher than the preset predetermined target discharge temperature, the control device 4 operates the main expansion valve 24 into the closing direction by a predetermined value.
  • Fig. 4 is a block diagram showing a control device in terms of function realizing means.
  • the control device 4 includes discharge temperature comparing means 40 and main valve operation determining means 41 for operating the main expansion valve 24.
  • control device 4 For operating the bypass expansion valve 31, the control device 4 includes suction saturation temperature calculating means 42, saturation temperature comparing means 43, and bypass valve operation determining means 44.
  • the control device 4 includes compressor number of rotation changing means 45 which changes the number of rotations of the compressor 21, number of rotation comparing means 46 which determines whether the number of rotations of the compressor 21 is equal to the predetermined compressor target number of rotations Hzt, and actuation time control completion determining means which determines that the control at the time of actuation is completed when the number of rotations of the compressor 21 is equal to the predetermined compressor target number of rotations Hzt.
  • the suction saturation temperature calculating means 42 calculates a suction saturation temperature Ts under pressure of a refrigerant sucked into the compressor 21 from a suction pressure Ps detected by the pressure sensor 51.
  • the saturation temperature comparing means 43 compared, with each other, the suction saturation temperature Ts calculated by the suction saturation temperature calculating means 42 and the bypass passage outlet temperature Tbo detected by the first temperature sensor 61.
  • the compressor number of rotation changing means 45 rises the number of rotations of the compressor 21 to the predetermined number of rotations.
  • the number of rotation comparing means 46 determines whether the current number of rotations of the compressor 21 is equal to the predetermined compressor target number of rotations Hzt.
  • the actuation time control completion determining means 47 determines that the control at the time of actuation is completed, and control is shifted to appropriate control.
  • the discharge temperature comparing means 40 compares with the discharge temperature Td detected by the second temperature sensor 62 and the preset predetermined temperature Tdt with each other.
  • the target discharge temperature Tdt is previously stored.
  • Main operation determining means 41 determines an opening degree of the main expansion valve 24 such that the discharge temperature Td becomes equal to the predetermined temperature Tdt based on a result of comparison carried out by the discharge temperature comparing means 40, and outputs a determined operation amount to the main expansion valve 24.
  • control device 4 operates the compressor 21 with the predetermined actuation number of rotations Hzi (step 1).
  • the opening degree of the bypass expansion valve 31 is set to a predetermined initial opening degree (step 2).
  • control device 4 detects the suction pressure Ps by the pressure sensor 51 and detects the bypass passage outlet temperature Tbo by the first temperature sensor 61 (step 3).
  • control device 4 calculates the suction saturation temperature Ts under a pressure of a refrigerant sucked into the compressor 21 from the suction pressure Ps detected by the pressure sensor 51 (step 4).
  • the suction saturation temperature Ts is calculated using a refrigerant-properties equation.
  • control device 4 compares the bypass passage outlet temperature Tbo and the suction saturation temperature Ts with each other, and determines whether Tbo and Ts are equal to each other (step 5) .
  • the control device 4 determines that a bypass passage outlet refrigerant is in a superheated state. According to this determination, the control device 4 adjusts the opening degree of the bypass expansion valve 31 such that the bypass passage outlet temperature Tbo becomes equal to the suction saturation temperature Ts (step 6), and the procedure is advanced to step 9.
  • the control device 4 determines that the bypass passage outlet refrigerant is in the saturated state. According to this determination, the number of rotations of the compressor is increased by the predetermined number of rotations and the compressor is operated (step 7), and it is determined whether the current number of rotations is equal to the predetermined compressor target number of rotations Hzt (step 8).
  • step 8 If the current number of rotations of the compressor is equal to the compressor target number of rotations Hzt (YES in step 8), it is determined that the control at the time of actuation is completed, and control is shifted to an appropriate control.
  • the second temperature sensor 62 detects the discharge temperature Td (step 9). According to this, it is determined whether the discharge temperature Td is higher than the preset predetermined temperature Tdt (step 10).
  • step 10 If the discharge temperature Td is equal to or lower than the predetermined temperature Tdt (NO in step 10), it is determined that a flow rate of a refrigerant of the bypass passage 3 is secured, and the procedure is returned to step 3 as it is.
  • the refrigerant circuit 2 includes the pressure sensor 51 which detects a pressure of a refrigerant sucked into the compressor 21, the second temperature sensor 62 which detects a temperature of a refrigerant discharged from the compressor 21, a first temperature sensor 61 which detects a temperature of a refrigerant flowing out from the supercooling heat exchanger 23 in the bypass passage 3, and the control device 4.
  • the control device 4 operates the bypass expansion valve 31 such that a refrigerant at the outlet of the bypass passage 3 is brought into the saturated state in a section until the number of rotations of the compressor 21 reaches the predetermined compressor target number of rotations after the compressor 21 is actuated.
  • the control device 4 controls such that the number of rotations is increased to the next stage number of rotations of the compressor.
  • the configuration of the embodiment of the refrigeration cycle apparatus in the state of low number of rotations in which the compression ratio of the compressor is small, after the state of a refrigerant at the outlet of the bypass passage is controlled from the overheated state to the saturated state, the number of rotations of the compressor is increased in stages while bypassing the the gas/liquid two-phase refrigerant. According to this configuration, it is possible to restrain the discharge temperature of the compressor from abnormally rising.
  • the control device 4 determines that the discharge temperature rises and close the main expansion valve 24 by the predetermined amount. Therefore, the flow rate of the refrigerant toward the bypass passage 3 is swiftly increased. Therefore, the excessive overheated state of the refrigerant at the outlet of the bypass passage 3 can be controlled into the saturated state within shorter time.
  • the pressure sensor 51 which detects the sucked refrigerant pressure of the compressor 21 is provided between the main accumulator 27 and a position to which the bypass passage 3 in the refrigerant circuit 2 is connected in Fig. 1 , the pressure sensor 51 may be provided at any position of the refrigerant circuit 2 only if the pressure sensor 51 is provided between the evaporator 25 and the compressor 21.
  • the pressure sensor 51 may be provided at the bypass passage 3 at a location downstream of the supercooling heat exchanger 23.
  • bypass passage 3 branches off from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve 24, and the bypass passage 3 may branch off from the refrigerant circuit 2 between the radiator 22 and the supercooling heat exchanger 23.
  • connection of the bypass passage 3 is a suction pipe of the compressor 21.
  • the connection of the bypass passage 3 may be connected to an injection port.
  • main expansion valve 24 and the bypass expansion valve 31 of the invention are expansion valves, and they may be expansion devices which collect power from an expanding refrigerant.
  • the number of rotations of the expansion device may be control by varying a load by means of a power generator connected to the expansion device.

Claims (3)

  1. Appareil de cycle de réfrigération comprenant
    un circuit de fluide frigorigène dans lequel un compresseur (21), un radiateur (22), un échangeur de chaleur de surfusion (23), un moyen d'expansion principal (24) et un évaporateur (25) sont reliés de manière annulaire les uns aux autres,
    un passage de dérivation (3) qui part du circuit de fluide frigorigène entre le radiateur (22) et le moyen d'expansion principal (24), et qui est relié à une chambre de compression du compresseur (21) ou au circuit de fluide frigorigène entre l'évaporateur (25) et le compresseur (21), à travers l'échangeur de chaleur de surfusion,
    un moyen d'expansion de dérivation (31) disposé dans le passage de dérivation (3) au niveau d'un emplacement en amont de l'échangeur de chaleur de surfusion (23),
    un premier capteur de température (61) qui détecte une température d'un fluide frigorigène d'une sortie du passage de dérivation (3) s'écoulant hors de l'échangeur de chaleur de surfusion (23),
    un moyen de détection de température de saturation (51) qui détecte une température de saturation (51) d'un fluide frigorigène aspiré dans le compresseur (21), et
    un dispositif de commande (4) qui commande le fonctionnement du moyen d'expansion de dérivation (31)
    caractérisé en ce que,
    lorsque le fonctionnement de l'appareil de cycle de réfrigération est démarré, le dispositif de commande (4) actionne le compresseur (21) au nombre d'actionnement de rotations qui est inférieur au nombre cible prédéfini de rotations du compresseur,
    dans lequel le dispositif de commande (4) commande le fonctionnement du moyen d'expansion de dérivation (31) de telle sorte qu'une température détectée par le premier capteur de température (61) devienne égale à la température de saturation détectée par le moyen de détection de température de saturation (51) avant que le nombre de rotations du compresseur (21) ne soit augmenté à un nombre cible prédéterminé de rotations du compresseur (21), et
    dans lequel le dispositif de commande (4) augmente le nombre de rotations du compresseur (21) au nombre cible de rotations du compresseur lorsque la température détectée par le premier capteur de température atteint la température de saturation.
  2. Appareil de cycle de réfrigération selon la revendication 1,
    comprenant en outre un second capteur de température (62) qui détecte une température d'un fluide frigorigène évacué par le compresseur (21), dans lequel le dispositif de commande (4) actionne un degré d'ouverture du moyen d'expansion principal (24) dans une direction de fermeture lorsqu'une température détectée par le second capteur de température (62) devient égale ou supérieure à une température prédéterminée.
  3. Dispositif de chauffage hydronique utilisant l'appareil de cycle de réfrigération selon la revendication 1 ou 2.
EP12171898.5A 2011-06-17 2012-06-14 Appareil de cycle de réfrigération et dispositif de chauffage hydronique utilisant l'appareil de cycle de réfrigération Active EP2535674B1 (fr)

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KR102163859B1 (ko) * 2013-04-15 2020-10-12 엘지전자 주식회사 공기조화기 및 그 제어방법
JP6266942B2 (ja) * 2013-10-10 2018-01-24 日立ジョンソンコントロールズ空調株式会社 空気調和機
ITVI20130257A1 (it) * 2013-10-18 2015-04-19 Carel Ind Spa Metodo di azionamento di una macchina frigorifera dotata di apparato economizzatore
CN104633979B (zh) * 2013-11-13 2017-03-29 珠海格力电器股份有限公司 空调器及其控制方法
CN104729161B (zh) * 2013-12-19 2018-08-24 珠海格力电器股份有限公司 空调器及其控制方法
JP6282135B2 (ja) * 2014-02-17 2018-02-21 東芝キヤリア株式会社 冷凍サイクル装置
JP6400223B2 (ja) * 2015-10-13 2018-10-03 三菱電機株式会社 空気調和機および空気調和機の制御方法
JP2017155944A (ja) * 2016-02-29 2017-09-07 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置及びそれを備えた温水暖房装置
EP3742084A4 (fr) * 2018-01-15 2021-01-13 Mitsubishi Electric Corporation Dispositif de climatisation
JP6984015B2 (ja) * 2018-06-13 2021-12-17 三菱電機株式会社 冷凍サイクル装置
WO2020066000A1 (fr) * 2018-09-28 2020-04-02 三菱電機株式会社 Unité extérieure pour dispositif à cycle de réfrigération, dispositif à cycle de réfrigération et dispositif de climatisation
CN112178871A (zh) * 2020-09-21 2021-01-05 广东Tcl智能暖通设备有限公司 一种空调控制方法、空调及存储介质
WO2022168153A1 (fr) * 2021-02-02 2022-08-11 三菱電機株式会社 Dispositif à cycle de réfrigération

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EP2535674A2 (fr) 2012-12-19
CN102829568A (zh) 2012-12-19
DK2535674T3 (en) 2019-01-21
EP2535674A3 (fr) 2015-05-20
JP2013002744A (ja) 2013-01-07
JP5816789B2 (ja) 2015-11-18
CN102829568B (zh) 2016-03-30

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