WO2006004047A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
- Publication number
- WO2006004047A1 WO2006004047A1 PCT/JP2005/012219 JP2005012219W WO2006004047A1 WO 2006004047 A1 WO2006004047 A1 WO 2006004047A1 JP 2005012219 W JP2005012219 W JP 2005012219W WO 2006004047 A1 WO2006004047 A1 WO 2006004047A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- high pressure
- refrigeration cycle
- refrigeration
- valve
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
-
- 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
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
- F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
-
- 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
- F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
- F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
- F04C18/44—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
- F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
-
- 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
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
Definitions
- the present invention relates to a refrigeration apparatus that includes an expander and performs a refrigeration cycle.
- Patent Document 1 discloses this refrigeration apparatus including an expander.
- an expander is connected to a compressor via a single shaft.
- This refrigeration system expands the high-pressure refrigerant after heat dissipation with an expander to recover power, and uses the power recovered by the expander to drive the compressor to improve the coefficient of performance (COP).
- COP coefficient of performance
- the refrigerant circulates in the refrigerant circuit configured in a closed circuit, so that the mass flow rate of the refrigerant passing through the expander is always equal to the mass flow rate of the refrigerant passing through the compressor.
- the mass flow rate of the refrigerant passing through the expander is always equal to the mass flow rate of the refrigerant passing through the compressor.
- both the expander and the compressor are configured by a positive displacement fluid machine, an imbalance occurs between the mass flow rate of the refrigerant passing through the expander and the mass flow rate of the refrigerant passing through the compressor, which is stable.
- the refrigeration cycle may not be continued.
- a bypass passage is provided in parallel with the expander, and a flow rate control valve is provided in the bypass passage. If the mass flow rate of the refrigerant that can pass through the expander is too small compared to the mass flow rate of the refrigerant that passes through the compressor, flow the refrigerant through both the expander and the bypass passage.
- Patent Document 1 JP 2001-116371 A
- the present invention has been made in view of the points to be worked on, and the object of the present invention is to stabilize in a wide range of operating conditions while minimizing the reduction in power recovered from the refrigerant in the expander. It is an object of the present invention to provide a refrigeration apparatus that can be operated.
- a first invention includes a refrigerant circuit (20) to which a compressor (50), a radiator, an expander (60), and an evaporator are connected, and refrigerant is contained in the refrigerant circuit (20).
- the target is a refrigeration system (10) that circulates and performs a refrigeration cycle.
- An refrigerant passage (26) for introducing a part of the refrigerant flowing in the refrigerant circuit (20) toward the expander (60) into the expansion chamber (66) in the expansion process of the expander (60).
- a flow rate adjusting valve (27) for adjusting the flow rate of the refrigerant in the indication passage (26).
- a second aspect of the present invention is the flow control valve according to the first aspect, wherein the coefficient of performance of the refrigeration cycle in the refrigerant circuit (20) is the highest value obtained in the operating state at that time. ) Is provided with control means (90) for adjusting the opening degree.
- control means (90) derives, as a control target value, the high pressure of the refrigeration cycle having the highest coefficient of performance based on the actually measured value indicating the operating state.
- the opening of the flow control valve (27) is adjusted so that the high pressure of the refrigeration cycle becomes the control target value.
- the control means (90) is characterized in that the high pressure of the refrigeration cycle has the highest coefficient of performance based on a change in the coefficient of performance when the high pressure of the refrigeration cycle is increased or decreased. Is derived as a control target value, and the opening of the flow control valve (27) is adjusted so that the high pressure of the refrigeration cycle becomes the control target value.
- the refrigerant circuit (20) includes a bypass passage (28) connecting the upstream side and the downstream side of the expander (60).
- the sub control operation is performed to adjust the opening of the bypass control valve (29), and the main control operation is resumed when the bypass control valve (29) is fully closed during the sub control operation. Chino.
- control means (90) derives, as a control target value, the high pressure of the refrigeration cycle that provides the highest coefficient of performance based on the actually measured value indicating the operating state.
- the operation of adjusting the opening degree of the bypass control valve (29) so that the high pressure of the refrigeration cycle becomes the control target value is performed as a sub-control operation.
- control means (90) is configured such that the high pressure of the refrigeration cycle has the highest coefficient of performance based on a change in the coefficient of performance when the high pressure of the refrigeration cycle is increased or decreased. Is derived as a control target value, and the operation of adjusting the opening of the flow rate control valve (27) so that the high pressure of the refrigeration cycle becomes the control target value is performed as a sub-control operation.
- An eighth invention is the refrigeration performed in the refrigerant circuit (20), wherein the refrigerant circuit (20) is filled with carbon dioxide as a refrigerant in any one of the first to seventh powers.
- the high pressure of the cycle is set above the critical pressure of carbon dioxide.
- the refrigeration cycle is performed in the refrigerant circuit (20).
- the refrigerant discharged from the compressor (50) is dissipated by the radiator, depressurized by the expander (60), and then evaporated by the evaporator. Are sucked into the compressor (50) and compressed.
- the expander (60) the high-pressure refrigerant radiated by the radiator expands and power is recovered from the high-pressure refrigerant. The power recovered from the refrigerant in the expander (60) is used to drive the compressor (50).
- the expansion chamber (66) of the expander (60) is also released from the injection passage (26). Refrigerant is introduced into).
- the refrigerant introduced into the expansion chamber from the injection passage (26) It expands with the refrigerant introduced into the expansion chamber from the inflow port of the tension machine (60). Further, the flow rate of the refrigerant flowing through the injection passage (26) is changed by changing the opening degree of the flow control valve (27).
- the refrigeration apparatus (10) is provided with the control means (90) for controlling the opening degree of the flow rate control valve (27).
- the control means (90) of the present invention allows the flow control valve (90) so that the coefficient of performance of the refrigeration cycle in the refrigerant circuit (20) becomes the highest value obtained in the operating state of the refrigeration apparatus (10) at that time. Adjust the opening in 27).
- control means (90) sets the control target value for the high pressure of the refrigeration cycle. At that time, the control means (90) derives the value of the high pressure of the refrigeration cycle having the highest coefficient of performance in the operating state based on the actually measured value indicating the operating state, and sets that value as the control target value. Then, the control means (90) adjusts the opening degree of the flow control valve (27) so that the high pressure of the actual refrigeration cycle becomes the control target value.
- the control means (90) sets the control target value based on the high pressure of the refrigeration cycle. At that time, the control means (90) performs an operation to increase or decrease the high pressure of the refrigeration cycle as a trial in order to set the control target value. Changing the refrigeration cycle's high pressure also changes the coefficient of performance of the refrigeration cycle. The control means (90) derives the value of the high pressure of the refrigeration cycle that obtains the highest coefficient of performance based on the change in the coefficient of performance at that time, and uses that value as the control target value. Then, the control means (90) adjusts the opening degree of the flow rate control valve (27) so that the actual high pressure in the refrigeration cycle becomes the control target value.
- the bypass passage (28) and the bypass control valve (29) are provided in the refrigerant circuit (20).
- the bypass control valve (29) In the state where the bypass control valve (29) is opened, a part of the refrigerant radiated by the radiator flows into the bypass passage (28), and the rest is sent to the expander (60).
- Part of the refrigerant sent to the expander (60) is directly introduced into the inflow port of the expander (60), and the rest is introduced into the expansion chamber of the expander (60) through the injection passage (26). Is done.
- the refrigerant flowing into the bypass passage (28) is depressurized when passing through the bypass control valve (29). After that, it merges with the refrigerant that has passed through the expander (60) and is sent to the evaporator.
- the control means (90) performs a main control operation and a sub control operation.
- the control means (90) during the main control operation adjusts the flow rate of the flow control valve (27) with the bypass control valve (29) fully closed to adjust the refrigerant flow rate in the index passage (26).
- the control means (90) is controlled by the sub-control. Start operation.
- the control means (90) during the sub-control operation adjusts the opening of the bypass control valve (29) with the flow rate control valve (27) fully opened, thereby adjusting the refrigerant flow rate in the bypass passage (28). If the bypass control valve (29) is fully closed during the sub-control operation, that is, there is no need to circulate the refrigerant in the bypass passage (28), the control means (90) Starts main control operation.
- control means (90) during the sub-control operation sets a control target value for the high pressure of the refrigeration cycle. At that time, the control means (90) derives the value of the high pressure of the refrigeration cycle in which the coefficient of performance is the highest in the operating state based on the actual value indicating the operating state, and uses that value as the control target value.
- the control means (90) during the sub-control operation is bypassed so that the high pressure of the actual refrigeration cycle becomes the control target value with the flow rate regulating valve (27) of the injection passage (26) held fully open. Adjust the opening of the control valve (29).
- the control means (90) during the sub-control operation sets a control target value for the high pressure of the refrigeration cycle. At that time, the control means (90) performs an operation of increasing or decreasing the high pressure of the refrigeration cycle as a trial in order to set the control target value. When the high pressure of the refrigeration cycle is changed, the coefficient of performance of the refrigeration cycle changes accordingly.
- the control means (90) derives the value of the high pressure of the refrigeration cycle at which the highest coefficient of performance is obtained based on the change in the coefficient of performance at that time, and uses that value as the control target value. Then, the control means (90) during the sub-control operation keeps the flow control valve (27) of the index passage (26) fully open so that the actual high pressure of the refrigeration cycle becomes the control target value. Adjust the opening of the bypass control valve (29).
- the refrigerant circuit (20) is filled with carbon dioxide as a refrigerant.
- a refrigeration cycle is performed by circulating carbon dioxide as a refrigerant. Is called.
- the compressor (50) of the refrigerant circuit (20) the carbon dioxide as the refrigerant is compressed to the critical pressure or higher.
- the refrigeration apparatus (10) of the present invention if the balance between the refrigerant amount passing through the expander (60) and the refrigerant amount passing through the compressor (50) is lost, the injection passage (26) Also, by introducing the refrigerant into the expander (60), the amount of refrigerant passing through the expander (60) and the compressor (50) can be balanced. For this reason, refrigerant that has been forced to bypass the expander (60) is introduced into the expander (60) in the past, and power is also recovered from the refrigerant that has been unable to recover power in the past. It becomes possible to do. Therefore, according to the present invention, it is possible to realize the refrigeration apparatus (10) capable of stable operation under a wide range of operating conditions without substantially reducing the decrease in power collected from the refrigerant.
- the control means (90) adjusts the opening of the flow rate control valve (27) so as to obtain the highest coefficient of performance. Therefore, according to the present invention, the refrigeration is performed under the condition that the highest coefficient of performance can be obtained simply by balancing the amount of refrigerant passing through the expander (60) and the compressor (50) and continuing a stable refrigeration cycle. A cycle can be performed.
- the refrigerant circuit (20) is provided with the bypass passage (28), and the refrigerant from which the radiator power has also flowed out passes through both the expander (60) and the bypass passage (28). Can be sent to. For this reason, even if the injection passage (26) force introduces refrigerant into the expander (60) and the amount of refrigerant passing through the expander (60) and compressor (50) cannot be balanced, the refrigerant is bypassed. By flowing to (28), the amount of refrigerant circulating in the refrigerant circuit (20) can be secured.
- control means (90) of the present invention opens the binos control valve (29) only when the flow rate control valve (27) in the injection passage (26) is fully opened. For this reason, the refrigerant flow rate in the bypass passage (28) can be minimized to ensure the maximum amount of refrigerant passing through the expander (60), and the refrigerant capacity is also recovered by the expander (60). The reduction in power required can be kept to a minimum.
- FIG. 1 is a schematic configuration diagram showing a configuration of an air conditioner and an operation during cooling operation.
- FIG. 2 is a schematic configuration diagram showing the configuration of the air conditioner and the operation during heating operation.
- 3] A schematic cross-sectional view of a compression / expansion unit.
- FIG. 4 is an enlarged view of a main part of the expansion mechanism.
- FIG. 8 is a flowchart showing the control operation of the controller.
- the air conditioner (10) of the present embodiment is constituted by the refrigeration apparatus according to the present invention.
- the air conditioner (10) is a so-called separate type, Machine (11) and indoor unit (13).
- the outdoor unit (11) houses an outdoor heat exchange (23), a four-way switching valve (21), a bridge circuit (22), an accumulator (25), and a compression / expansion unit (30).
- the indoor unit (13) stores an indoor heat exchanger (24).
- the outdoor unit (1 1) is installed outdoors, and the indoor unit (13) is installed indoors.
- the outdoor unit (11) and the indoor unit (13) are connected by a pair of connecting pipes (15, 16). Details of the compression / expansion unit (30) will be described later.
- the air conditioner (10) is provided with a refrigerant circuit (20).
- This refrigerant circuit (20) is a closed circuit to which a compression / expansion unit (30), indoor heat exchange (24), and the like are connected.
- the refrigerant circuit (20) is filled with carbon dioxide (CO 2) as a refrigerant.
- Both the outdoor heat exchanger (23) and the indoor heat exchanger (24) are constituted by a cross fin type fin-and-tube heat exchanger.
- the refrigerant circulating in the refrigerant circuit (20) exchanges heat with outdoor air.
- the indoor heat exchanger (24) the refrigerant circulating in the refrigerant circuit (20) exchanges heat with the indoor air.
- the four-way selector valve (21) includes four ports.
- the four-way selector valve (21) has a first port connected to the discharge pipe (36) of the compression / expansion unit (30) and a second port connected to the compression / expansion unit (30) via the accumulator (25).
- the third port is connected to one end of the outdoor heat exchanger (23), and the fourth port is connected to one end of the indoor heat exchanger (24) via the connecting pipe (15), to the suction port (32).
- This four-way selector valve (21) has a state in which the first port and the third port communicate with each other and the second port and the fourth port communicate with each other (the state shown in FIG. 1), The state is switched to the state where the port communicates with the fourth port and the second port communicates with the third port (the state shown in FIG. 2).
- the bridge circuit (22) is formed by connecting four check valves (CV-1 to CV-4) in a bridge shape.
- the inflow side of the first check valve (CV-1) and the fourth check valve (CV-4) is connected to the outflow port (35) of the compression / expansion unit (30).
- the outflow side of the check valve (CV-2) and the third check valve (CV-3) flows into the inflow port (34) of the compression / expansion unit (30), and the outflow of the first check valve (CV-1) Side and the inflow side of the second check valve (CV-2) are connected to the other end of the indoor heat exchanger (24) via the connecting pipe (16) and the inflow side of the third check valve (CV-3) and The outflow side of the fourth check valve (CV-4) is connected to the other end of the outdoor heat exchanger (23).
- the refrigerant circuit (20) is provided with an injection pipe (26).
- the injection pipe (26) constitutes an injection passage.
- the injection pipe (26) has one end between the bridge circuit (22) and the inflow port (34) of the compression / expansion unit (30) and the other end of the compression / expansion unit (30). Connected to each injection port (37).
- the injection pipe (26) is provided with an injection valve (27).
- the injection valve (27) is an electric valve for adjusting the refrigerant flow rate in the injection pipe (26), and constitutes a flow rate adjusting valve.
- the refrigerant circuit (20) is provided with a bypass pipe (28).
- This bypass pipe (28) constitutes a bypass passage.
- the bypass pipe (28) has one end between the bridge circuit (22) and the inflow port (34) of the compression / expansion unit (30) and the other end of the compression / expansion unit (30). Connected between the inflow port (34) and the bridge circuit (22).
- the bypass pipe (28) is provided with a bypass valve (29).
- the bypass valve (29) is an electric valve for adjusting the refrigerant flow rate in the bypass pipe (28), and constitutes a no-pass adjustment valve.
- the refrigerant circuit (20) of the air conditioner (10) is provided with temperature and pressure sensors. Specifically, the high pressure sensor (95) is connected to the piping connecting the discharge pipe (36) of the compression / expansion unit (30) and the four-way selector valve (21), and the compression / expansion unit (30) The pressure of the high-pressure refrigerant discharged from the is detected.
- the low pressure sensor (96) is connected to the pipe connecting the four-way selector valve (21) and the suction port (32) of the compression / expansion unit (30), and is sucked into the compression / expansion unit (30). The pressure of the low-pressure refrigerant is detected.
- the outdoor refrigerant temperature sensor (97) is attached near the end of the outdoor heat exchanger (23) near the bridge circuit (22).
- the indoor side refrigerant temperature sensor (98) is attached near the end of the indoor heat exchanger (24) near the connecting pipe (16).
- the air conditioner (10) is provided with a controller (90) that constitutes a control means. Detection values obtained by the high pressure sensor (95), the low pressure sensor (96), the outdoor refrigerant temperature sensor (97), and the indoor refrigerant temperature sensor (98) are input to the controller (90).
- the controller (90) sets the high pressure control target value of the refrigeration cycle based on the detection values obtained by these sensors, so that the detection value of the high pressure sensor (95) becomes the control target value. It is configured to control the opening of the injection valve (27) and bypass valve (29)! Speak.
- the compression / expansion unit (30) includes a casing (31) which is a vertically long and cylindrical sealed container. Inside this casing (31), from bottom to top
- the compression mechanism section (50), the electric motor (45), and the expansion mechanism section (60) are arranged.
- a discharge pipe (36) is attached to the casing (31).
- the discharge pipe (36) is disposed between the electric motor (45) and the expansion mechanism section (60), and communicates with the internal space of the casing (31).
- the electric motor (45) is disposed at the center in the longitudinal direction of the casing (31).
- This electric motor (45) consists of a stator (46) and a rotor (47)! RU
- the stator (46) is fixed to the casing (31).
- the rotor (47) is disposed inside the stator (46).
- the main shaft portion (44) of the shaft (40) passes through the rotor (47) coaxially with the rotor (47).
- Two lower eccentric portions (58, 59) are formed on the lower end side of the shaft (40). These two lower eccentric portions (58, 59) are formed to have a larger diameter than the main shaft portion (44), and the lower one is the first lower eccentric portion (58) and the upper one is the upper one. Constitute the second lower eccentric part (59). In the first lower eccentric portion (58) and the second lower eccentric portion (59), the eccentric directions with respect to the axial center of the main shaft portion (44) are reversed.
- Two large-diameter eccentric parts (41, 42) are formed on the upper end side of the shaft (40). These two large-diameter eccentric parts (41, 42) are formed with a larger diameter than the main shaft part (44), and the lower one constitutes the first large-diameter eccentric part (41) and the upper one. Constitutes the second large-diameter eccentric part (42).
- the first large-diameter eccentric part (41) and the second large-diameter eccentric part (42) are both eccentric in the same direction.
- the outer diameter of the second large-diameter eccentric part (42) is larger than the outer diameter of the first large-diameter eccentric part (41). Further, the amount of eccentricity of the main shaft portion (44) with respect to the shaft center is larger in the second large diameter eccentric portion (42) than in the first large diameter eccentric portion (41).
- the compression mechanism section (50) constitutes an oscillating piston type rotary compressor.
- the compressor structure (50) includes two cylinders (51, 52) and two pistons (57).
- the rear head (55), the first cylinder (51), and the intermediate plate are arranged in order from bottom to top. (56), the second cylinder (52), and the front head (54) are stacked.
- One cylindrical piston (57) is disposed inside each of the first and second cylinders (51, 52). Although not shown, a flat blade is projected on the side surface of the piston (57), and this blade is supported by the cylinder (51, 52) via a swing bush.
- the piston (57) in the first cylinder (51) engages with the first lower eccentric part (58) of the shaft (40).
- the piston (57) in the second cylinder (52) engages with the second lower eccentric portion (59) of the shaft (40).
- Each piston (57, 57) has its inner peripheral surface in sliding contact with the outer peripheral surface of the lower eccentric portion (58, 59) and its outer peripheral surface in sliding contact with the inner peripheral surface of the cylinder (51, 52).
- a compression chamber (53) is formed between the outer peripheral surface of the piston (57, 57) and the inner peripheral surface of the cylinder (51, 52).
- One suction port (33) is formed in each of the first and second cylinders (51, 52). Each suction port (33) penetrates the cylinder (51, 52) in the radial direction, and the end thereof opens to the inner peripheral surface of the cylinder (51, 52). Each intake port (33) is extended to the outside of the casing (31) by piping.
- One discharge port is formed in each of the front head (54) and the rear head (55).
- the discharge port of the front head (54) allows the compression chamber (53) in the second cylinder (52) to communicate with the internal space of the casing (31).
- the discharge port of the rear head (55) allows the compression chamber (53) in the first cylinder (51) to communicate with the internal space of the casing (31).
- Each discharge port is provided with a discharge valve that also has a reed valve force at its end, and is opened and closed by this discharge valve. In FIG. 3, the discharge port and the discharge valve are not shown.
- the gas refrigerant discharged from the compressor structure (50) into the internal space of the casing (31) is sent out from the compression / expansion unit (30) through the discharge pipe (36).
- the expansion mechanism section (60) constitutes a so-called oscillating piston type rotary expander.
- the expansion mechanism (60) is provided with two pairs of cylinders (71, 81) and pistons (75, 85).
- the expansion mechanism section (60) includes a front head (61), an intermediate plate (63), and a rear head (62).
- the front head (61), the first cylinder (71), the intermediate plate (63), the second cylinder (81), the rear head ( 62) are stacked.
- the lower end surface of the first cylinder (71) is the front head ( 61) and the upper end face thereof is closed by the intermediate plate (63).
- the second cylinder (81) has its lower end face closed by the intermediate plate (63) and its upper end face closed by the rear head (62).
- the inner diameter of the second cylinder (81) is larger than the inner diameter of the first cylinder (71).
- the shaft (40) passes through the stacked front head (61), first cylinder (71), intermediate plate (63), second cylinder (81), and rear head (62). Yes.
- the shaft (40) has its first large-diameter eccentric part (41) located in the first cylinder (71) and its second large-diameter eccentric part (42) located in the second cylinder (81). And then.
- the first piston (75) force is in the first cylinder (71), and the second piston (85) is in the second cylinder (81). It is provided.
- the first and second pistons (75, 85) are both formed in an annular shape or a cylindrical shape.
- the outer diameter of the first piston (75) and the outer diameter of the second piston (85) are equal to each other.
- the inner diameter of the first piston (75) is approximately equal to the outer diameter of the first large-diameter eccentric part (41), and the inner diameter of the second piston (85) is approximately equal to the outer diameter of the second large-diameter eccentric part (42). Yes.
- the first large-diameter eccentric portion (41) penetrates through the first piston (75), and the second large-diameter eccentric portion (42) penetrates through the second piston (85).
- the first piston (75) has an outer peripheral surface on the inner peripheral surface of the first cylinder (71), one end surface force S on the front head (61), and the other end surface on the intermediate plate (63). Each is in sliding contact.
- a first expansion chamber (72) is formed in the first cylinder (71) between its inner peripheral surface and the outer peripheral surface of the first piston (75).
- the second piston (85) has an outer peripheral surface on the inner peripheral surface of the second cylinder (81), one end surface on the rear head (62), and the other end surface on the intermediate plate (63). It is in sliding contact.
- a second expansion chamber (82) is formed in the second cylinder (81) between its inner peripheral surface and the outer peripheral surface of the second piston (85).
- Each of the first and second pistons (75, 85) is provided with one blade (76, 86).
- the blade (76, 86) is formed in a plate shape extending in the radial direction of the piston (75, 85), and projects outward from the outer peripheral surface of the piston (75, 85).
- Each cylinder (71, 81) is provided with a pair of bushes (77, 87).
- Each bush (77, 87) is a small piece formed so that the inner surface is a flat surface and the outer surface is a circular arc surface.
- the pair of bushes (77, 87) are installed with the blade (76, 86) sandwiched between them. It is.
- Each bush (77, 87) slides on its inner side with the blade (76, 86) and on its outer side with the cylinder (71, 81).
- the blade (76, 86) integrated with the piston (75, 85) is supported by the cylinder (71, 81) via the bush (77, 87), and rotates with respect to the cylinder (71, 81). Be free and move forward and backward!
- the first expansion chamber (72) in the first cylinder (71) is partitioned by a first blade (76) integral with the first piston (75), and the first blade (76) in FIG.
- the left side is a high pressure side first high pressure chamber (73), and the right side is a low pressure side first low pressure chamber (74).
- the second expansion chamber (82) in the second cylinder (81) is partitioned by a second blade (86) integral with the second piston (85), and the left side of the second blade (86) in FIG.
- the second high pressure chamber (83) on the high pressure side becomes the second low pressure chamber (84) on the right side.
- the first cylinder (71) and the second cylinder (81) are arranged in a posture in which the positions of the bushes (77, 87) in the respective circumferential directions coincide.
- the arrangement angle of the second cylinder (81) with respect to the first cylinder (71) is 0 °.
- the first large-diameter eccentric portion (41) and the second large-diameter eccentric portion (42) are eccentric in the same direction with respect to the axis of the main shaft portion (44). Therefore, the first blade (76) is in the most retracted state outside the first cylinder (71), and the second blade (86) is in the most retracted state outside the second cylinder (81). .
- the first cylinder (71) has an inflow port (34).
- the inflow port (34) opens at a position slightly on the left side of the bush (77) in FIGS. 4 and 5 on the inner peripheral surface of the first cylinder (71).
- the inflow port (34) can communicate with the first high pressure chamber (73) (that is, the high pressure side of the first expansion chamber (72)).
- the second cylinder (81) is formed with an outflow port (35).
- the outflow port (35) opens at a position slightly on the right side of the bush (87) in FIGS. 4 and 5 in the inner peripheral surface of the second cylinder (81).
- the outflow port (35) can communicate with the second low pressure chamber (84) (that is, the low pressure side of the second expansion chamber (82)).
- the intermediate plate (63) is formed with a communication path (64).
- the communication path (64) penetrates the intermediate plate (63) in the thickness direction.
- On the surface of the intermediate plate (63) on the first cylinder (71) side one end of the communication path (64) opens at a position on the right side of the first blade (76).
- On the surface of the intermediate plate (63) on the second cylinder (81) side the other end of the communication path (64) is opened at the left side of the second blade (86).
- the communication path (64) Extends obliquely with respect to the thickness direction of the intermediate plate (63), and includes the first low pressure chamber (74) (ie, the low pressure side of the first expansion chamber (72)) and the second high pressure chamber (83) (ie, the first pressure chamber).
- the expansion chamber (82) is connected to the high pressure side).
- the intermediate plate (63) is formed with an injection port (37) (see Fig. 3).
- the injection port (37) is formed so as to extend in a substantially horizontal direction, and its end opens into the communication passage (64).
- the starting end side of the injection port (37) extends to the outside of the casing (31) via a pipe.
- the injection pipe (26) is connected to the injection port (37).
- the first cylinder (71), the bush (77) provided there, the first piston (75), and the first piston One blade (76) constitutes the first rotary mechanism (70).
- the second cylinder (81), the bush (87) provided there, the second piston (85), and the second blade (86) constitute the second rotary mechanism (80). .
- the timing at which the first blade (76) is most retracted to the outside of the first cylinder (71) and the second blade (86) is the second cylinder (81).
- the timing of the most receding outside is synchronized.
- the volume of the first low pressure chamber (74) decreases in the first rotary mechanism (70) and the volume of the second high pressure chamber (83) increases in the second rotary mechanism (80).
- the process is synchronized (see Fig. 6).
- the first low pressure chamber (74) of the first rotary mechanism section (70) and the second high pressure chamber (83) of the second rotary mechanism section (80) have a communication path (64). Are in communication with each other.
- the first low pressure chamber (74), the communication passage (64), and the second high pressure chamber (83) form one closed space, and this closed space constitutes the expansion chamber (66). This point will be described with reference to FIG.
- the rotation angle of the shaft (40) when the first blade (76) is most retracted to the outer peripheral side of the first cylinder (71) is set to 0 °. Further, here, it is assumed that the maximum volume of the first expansion chamber (72) is 3 ml (milliliter) and the maximum volume of the second expansion chamber (82) is 10 ml.
- the volume of the first low pressure chamber (74) reaches a maximum value of 3 ml, and the second high pressure chamber (83)
- the volume is Oml which is the minimum value.
- the volume of the first low pressure chamber (74) gradually decreases as the shaft (40) rotates, as indicated by the alternate long and short dash line in the figure, and reaches the minimum value of Oml when the rotation angle reaches 360 °.
- the volume of the second high pressure chamber (83) gradually increases as the shaft (40) rotates, as indicated by the two-dot chain line in the figure, and reaches its maximum value when the rotation angle reaches 360 °. 10ml.
- the volume of the expansion chamber (66) at a certain rotation angle is the volume of the first low pressure chamber (74) and the volume of the second high pressure chamber (83) at that rotation angle.
- the value is the sum of and.
- the volume of the expansion chamber (66) becomes the minimum value of 3 ml when the rotation angle of the shaft (40) is 0 ° as shown by the solid line in the figure, and gradually increases as the shaft (40) rotates.
- the maximum value is 10 ml.
- the operation of the air conditioner (10) will be described.
- the operation of the air conditioner (10) during the cooling operation and the heating operation will be described, and then the operation of the expansion mechanism section (60) will be described.
- the four-way selector valve (21) is set to the state shown in FIG.
- the electric motor (45) of the compression / expansion unit (30) is energized in this state, the refrigerant circulates in the refrigerant circuit (20), and a vapor compression refrigeration cycle is performed.
- the outdoor heat exchanger (23) serves as a radiator, and the indoor heat exchanger (24) serves as an evaporator.
- the injection valve (27) and the bypass valve (29) are fully closed.
- the refrigerant compressed by the compression mechanism section (50) is discharged from the compression / expansion unit (30) through the discharge pipe (36). In this state, the refrigerant pressure is higher than its critical pressure.
- the discharged refrigerant is sent to the outdoor heat exchanger (23) through the four-way switching valve (21). In the outdoor heat exchange (23), the refrigerant flowing in dissipates heat to the outdoor air.
- the refrigerant that has dissipated heat in the outdoor heat exchanger (23) passes through the third check valve (CV-3) of the bridge circuit (22), passes through the inflow port (34), and is compressed and expanded ( It flows into the expansion mechanism (60) of 30).
- the high-pressure refrigerant expands, and the internal energy is converted into the rotational power of the shaft (40).
- the low-pressure refrigerant after expansion also flows out of the compression / expansion unit (30) through the outflow port (35), passes through the first check valve (CV-1) of the bridge circuit (22), and heats the room. Sent to Ko (24).
- the refrigerant that has flowed in absorbs heat from the room air and evaporates, thereby cooling the room air.
- the low-pressure gas refrigerant coming out of the indoor heat exchanger (24) passes through the four-way selector valve (21), passes through the suction port (32), and goes to the compression mechanism (50) of the compression / expansion unit (30). Inhaled.
- the compression mechanism section (50) compresses and discharges the sucked refrigerant.
- the four-way selector valve (21) is switched to the state shown in FIG. In this state, when the electric motor (45) of the compression / expansion unit (30) is energized, the refrigerant circulates in the refrigerant circuit (20) to perform a vapor compression refrigeration cycle. At that time, the indoor heat exchanger (24) becomes a radiator, and the outdoor heat exchanger (23) becomes an evaporator. In the following description, it is assumed that the instruction valve (27) and the bypass valve (29) are fully closed.
- the refrigerant compressed by the compression mechanism section (50) is discharged from the compression / expansion unit (30) through the discharge pipe (36). In this state, the refrigerant pressure is higher than its critical pressure.
- the discharged refrigerant passes through the four-way switching valve (21) and is sent to the indoor heat exchanger (24). In the indoor heat exchanger (24), the refrigerant flowing in dissipates heat to the indoor air, and the indoor air is heated.
- the refrigerant that has dissipated heat in the indoor heat exchanger (24) passes through the second check valve (CV-2) of the bridge circuit (22), passes through the inflow port (34), and is compressed and expanded ( It flows into the expansion mechanism (60) of 30).
- the expansion mechanism section (60) the high-pressure refrigerant expands, and the internal energy is converted into the rotational power of the shaft (40).
- the low-pressure refrigerant after expansion also flows out of the compression / expansion unit (30) through the outflow port (35), passes through the fourth check valve (CV-4) of the bridge circuit (22), To 23).
- the refrigerant that has flowed in absorbs heat from the outdoor air and evaporates.
- the low-pressure gas refrigerant discharged from the outdoor heat exchanger (23) passes through the four-way selector valve (21) and is sucked into the compression mechanism (50) of the compression / expansion unit (30) through the suction port (32). Is done.
- the compression mechanism section (50) compresses and discharges the sucked refrigerant.
- the first low pressure chamber (74) and the second high pressure chamber (83) communicate with each other via the communication passage (64).
- the refrigerant begins to flow from (74) into the second high pressure chamber (83).
- the volume of the second high pressure chamber (83) gradually decreases as the volume of the first low pressure chamber (74) gradually decreases.
- the volume of the expansion chamber (66) gradually increases. This increase in the volume of the expansion chamber (66) continues until just before the rotation angle of the shaft (40) reaches 360 °.
- the refrigerant in the expansion chamber (66) expands in the process of increasing the volume of the expansion chamber (66), and the shaft (40) is rotationally driven by the expansion of the refrigerant.
- the refrigerant in the first low pressure chamber (74) flows through the communication passage (64) while expanding into the second high pressure chamber (83).
- the refrigerant pressure in the expansion chamber (66) gradually decreases as the rotation angle of the shaft (40) increases, as indicated by a broken line in FIG. Specifically, the supercritical refrigerant that fills the first low pressure chamber (74) suddenly drops in pressure until the rotation angle of the shaft (40) reaches about 55 °, and becomes a saturated liquid state. Thereafter, the pressure in the expansion chamber (66) gradually decreases while part of the refrigerant evaporates.
- the second low pressure chamber (84) begins to communicate with the outflow port (35) when the rotation angle of the shaft (40) is 0 °. That is, the refrigerant begins to flow out from the second low pressure chamber (84) to the outflow port (35). After that, the rotation angle of the shaft (40) gradually increased to 90 °, 180 °, 270 °, and the second low-pressure chamber (84) force also expanded after the rotation angle reached 360 °.
- the low-pressure refrigerant flows out.
- the controller (90) performs a main control operation and a sub control operation. During the main control operation, the controller (90) adjusts the opening of the injection valve (27) while keeping the bypass valve (29) fully closed. If the injection valve (27) is fully opened during the main control operation and the refrigerant flow in the induction pipe (26) cannot be increased any more, the controller (90) starts the sub control operation. .
- the controller (90) in the sub control operation adjusts the opening degree of the bypass valve (29) with the indication valve (27) fully opened, and adjusts the refrigerant flow rate in the bypass pipe (28). If the bypass valve (29) is fully closed during the sub-control operation, that is, if it becomes unnecessary to circulate the refrigerant in the bypass pipe (28), the controller (90) performs the main control operation. Resume.
- step ST10 the controller (90) measures the operating state of the air conditioner (10).
- the controller (90) receives output signals of the high pressure sensor (95), the low pressure sensor (96), the outdoor refrigerant temperature sensor (97), and the indoor refrigerant temperature sensor (98). In subsequent step ST11, the controller (90) calculates a control target value Pd_obj of the high pressure of the refrigeration cycle using the detection value of each sensor (95 to 98) received in step ST11. The process of calculating this control target value Pd_obj will be described later.
- step ST12 the controller (90) compares the detected value of the high pressure sensor (95), that is, the actual measurement value Pd of the refrigeration cycle with the control target value Pd_obj calculated in step ST11. If the actual measurement value Pd of the refrigeration cycle is greater than or equal to the control target value Pd_obj, the process proceeds to step ST13. If the actual measurement value Pd of the refrigeration cycle is less than the control target value Pd_obj, the process proceeds to step ST16.
- step ST13 If Pd ⁇ Pd_obj, it is determined in step ST13 whether or not the injection valve (27) is fully open.
- step ST14 the controller (90) Open the bypass valve (29) while keeping the valve (27) fully open, start introducing refrigerant into the bypass pipe (28), or increase the refrigerant flow rate in the bypass pipe (28). . That is, in this state, the actual value Pd of the high pressure of the refrigeration cycle is equal to or higher than the control target value PcLobj, although the refrigerant flow rate in the instruction pipe (26) cannot be increased any more. Therefore, the controller (90) increases the amount of refrigerant flowing into the bypass pipe (28) in order to reduce the high pressure of the refrigeration cycle.
- step ST15 the controller (90) increases the opening of the injection valve (27) while keeping the bypass valve (29) fully closed, and increases the refrigerant flow rate in the injection pipe (26). That is, in this state, unlike the state of step ST14, it is possible to increase the refrigerant flow rate in the instruction pipe (26). Therefore, the controller (90) increases the amount of refrigerant flowing into the injection pipe (26) in order to reduce the high pressure of the refrigeration cycle.
- step ST16 it is determined in step ST16 whether or not the bypass valve (29) is fully closed.
- step ST16 If it is determined in step ST16 that the bypass valve (29) is still fully closed, the process proceeds to step ST17.
- step ST17 the controller (90) reduces the opening of the injection valve (27) while keeping the bypass valve (29) fully closed, and decreases the refrigerant flow rate in the injection pipe (26). That is, in this state, the refrigerant has not yet been introduced into the bypass pipe (28), and the injection valve (27) has not yet been fully opened. Therefore, the controller (90) reduces the amount of refrigerant flowing into the induction pipe (26) in order to increase the high pressure of the refrigeration cycle.
- Step ST18 the controller (90) reduces the opening of the bypass valve (29) while keeping the injection valve (27) fully open, reduces the refrigerant flow rate in the bypass pipe (28), or bypass pipe ( 28) Stop introducing the refrigerant to. That is, in this state, the high-pressure actual value Pd of the refrigeration cycle is lower than the control target value PcLobj with the bypass valve (29) already opened. So the controller (90) To increase the high pressure of the cycle, reduce the amount of refrigerant flowing into the bypass pipe (28).
- step ST10, 11, 12 in FIG. 8 the operations from step ST10, 11, 12 in FIG. 8 through step ST13 to step ST15 and the operation from step ST16 to step ST17 are the main control operations.
- step ST10, 11, 12 to step ST13 through step ST14 and the operation from step ST16 to step ST18 in FIG. are the main control operations.
- the coefficient of performance (COP) of the refrigeration cycle changes according to the high pressure of the refrigeration cycle, and when the high pressure of the refrigeration cycle reaches a specific value, the coefficient of performance of the refrigeration cycle is the maximum.
- the controller (90) applies the detected value of the low pressure sensor (96) and the detected value of the outdoor refrigerant temperature sensor (97) to a matrix or correlation equation during cooling operation,
- the control target value is the high pressure value of the refrigeration cycle that provides the highest coefficient of performance in the operating state.
- controller (90) applies a matrix or correlation equation that stores the detection value of the low-pressure sensor (96) and the detection value of the indoor refrigerant temperature sensor (98) during heating operation, and the operation state Set the high-pressure value of the refrigeration cycle that gives the highest coefficient of performance to the control target value Pd_obj.
- the controller (90) has the highest coefficient of performance in the current operating state. Is set to the control target value Pd_obj. The controller (90) then opens the opening of the instruction valve (27) and the bypass valve (29) so that the actual measured value Pd of the refrigeration cycle detected by the high pressure sensor (95) becomes the control target value Pd_obj. Take control.
- the indication pipe (26) when the balance between the refrigerant amount passing through the expansion mechanism portion (60) and the refrigerant amount passing through the compression mechanism portion (50) is lost, the indication pipe (26) Also, by introducing the refrigerant into the expansion mechanism section (60), the amount of refrigerant passing through the expansion mechanism section (60) and the compression mechanism section (50) can be balanced. For this reason, conventionally, a refrigerant that has had to bypass the expansion mechanism (60) is introduced into the expansion mechanism (60). The power can be recovered. Therefore, according to the present embodiment, it is possible to realize the air conditioner (10) that is wide and can operate stably under the operating conditions without substantially reducing the reduction in the power recovered from the refrigerant.
- the controller (90) adjusts the opening degree of the injection valve (27) so that the highest coefficient of performance can be obtained. For this reason, according to this embodiment, not only can the refrigerant flowing through the expansion mechanism (60) and the compression mechanism (50) be balanced, but a stable refrigeration cycle can be continued, and the highest coefficient of performance can be obtained.
- the refrigeration cycle can be performed under certain conditions.
- the refrigerant circuit (20) is provided with the no-pass pipe (28), and the high-pressure refrigerant after heat radiation evaporates through both the expansion mechanism section (60) and the bypass pipe (28). It is possible to send it to the heat exchanger ⁇ (23, 24) of the person who is the container. For this reason, even if refrigerant is introduced from the injection pipe (26) into the expansion mechanism section (60), the amount of refrigerant passing through the expansion mechanism section (60) and the compression mechanism section (50) cannot be balanced. By allowing the refrigerant to flow to the bypass pipe (28), the amount of refrigerant circulating in the refrigerant circuit (20) can be secured.
- controller (90) of the present embodiment opens the bypass valve (29) only when the injection valve (27) of the injection pipe (26) is fully opened. For this reason, the refrigerant flow rate in the bypass pipe (28) can be minimized to ensure the maximum amount of refrigerant passing through the expansion mechanism section (60). Minimize the reduction in power recovered.
- control target value P d — obj regarding the high pressure of the refrigeration cycle may be set as follows.
- the controller (90) of this modification changes the opening degree of the induction valve (27) or bypass valve (29) to increase or decrease the pressure of the refrigeration cycle as a trial. Perform an action to try. If the binos valve (29) is fully closed and only the injection valve (27) is open, the controller (90) changes the opening of the injection valve (27) to change the refrigeration cycle. Increase or decrease the high pressure, and if the injection valve (27) is fully open and the bypass valve (29) is also open, change the opening of the bypass valve (29) to increase or decrease the refrigeration cycle high pressure. .
- This controller (90) measures the coefficient of performance of the refrigeration cycle when the high pressure of the refrigeration cycle is increased or decreased.
- the controller (90) derives the correlation between the change in the refrigeration cycle's high pressure and the change in the coefficient of performance, and uses this correlation to find the value of the refrigeration cycle's high pressure at which the highest coefficient of performance is obtained. Set the value to the control target value Pd_obj.
- the controller (90) of the above embodiment controls the opening of the injection valve (27) and the bypass valve (29) using the temperature of the refrigerant discharged from the compression mechanism section (50) (discharged refrigerant temperature) as a parameter. Also good.
- the discharge refrigerant temperature at which the highest coefficient of performance is obtained under the operating conditions at that time is set as the control target value, and the injection valve (27) and bypass valve (29 ) May be controlled in opening.
- the control target value of the discharge refrigerant temperature is set instead of the control target value related to the high pressure of the refrigeration cycle, and in step ST12, the measured value of the discharge refrigerant temperature becomes equal to or greater than the control target value. Determine whether or not.
- the degree of opening of the injection valve (27) and the bypass valve (29) may be controlled using the temperature of the air that has passed through the heat exchanger acting as a radiator as a parameter. .
- the controller (90) of the present modification includes the temperature of the air that has passed through the indoor heat exchanger (24) that serves as a radiator during heating operation, that is, the air blown out by the indoor unit (13) during heating operation.
- the set value for the temperature is entered by the user.
- the controller (90) then controls the injection valve (27) and bypass valve (29) so that the measured value of the temperature of the air that has passed through the indoor heat exchanger (24) during heating operation becomes the input target value.
- the high pressure of the refrigeration cycle is adjusted by controlling the opening degree.
- the high pressure sensor (95) is provided in the refrigerant circuit (20) to actually measure the high pressure of the refrigeration cycle.
- the detected value force of other sensors is not directly measured.
- the high pressure of the refrigeration cycle may be estimated. For example, if the rotational speed of the compressor mechanism (50), the power consumption of the electric motor (45) that drives the compression mechanism (50), and the refrigerant temperature at the outlet of the radiator are measured, these measured values Force It is possible to estimate the high pressure of the refrigeration cycle.
- the present invention is useful for a refrigeration apparatus including an expander.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/631,674 US7730741B2 (en) | 2004-07-07 | 2005-07-01 | Refrigeration apparatus with expander control for improved coefficient of performance |
KR1020077003013A KR100828268B1 (ko) | 2004-07-07 | 2005-07-01 | 냉동장치 |
EP05765258.8A EP1780478B1 (en) | 2004-07-07 | 2005-07-01 | Freezing device |
AU2005258417A AU2005258417B2 (en) | 2004-07-07 | 2005-07-01 | Refrigeration apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004200987A JP4389699B2 (ja) | 2004-07-07 | 2004-07-07 | 冷凍装置 |
JP2004-200987 | 2004-07-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006004047A1 true WO2006004047A1 (ja) | 2006-01-12 |
Family
ID=35782851
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/012219 WO2006004047A1 (ja) | 2004-07-07 | 2005-07-01 | 冷凍装置 |
Country Status (7)
Country | Link |
---|---|
US (1) | US7730741B2 (ja) |
EP (1) | EP1780478B1 (ja) |
JP (1) | JP4389699B2 (ja) |
KR (1) | KR100828268B1 (ja) |
CN (1) | CN100445667C (ja) |
AU (1) | AU2005258417B2 (ja) |
WO (1) | WO2006004047A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012098024A (ja) * | 2006-12-08 | 2012-05-24 | Daikin Industries Ltd | 冷凍装置 |
JP2012515890A (ja) * | 2009-01-20 | 2012-07-12 | パナソニック株式会社 | 冷凍サイクル装置 |
EP2090746A4 (en) * | 2006-12-08 | 2016-06-01 | Daikin Ind Ltd | FREEZING APPARATUS AND REGULATOR |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5309424B2 (ja) * | 2006-03-27 | 2013-10-09 | ダイキン工業株式会社 | 冷凍装置 |
EP2072753B1 (en) * | 2006-10-11 | 2018-02-14 | Panasonic Intellectual Property Management Co., Ltd. | Rotary expander |
JP4991255B2 (ja) * | 2006-11-22 | 2012-08-01 | 日立アプライアンス株式会社 | 冷凍サイクル装置 |
JP2009215985A (ja) * | 2008-03-11 | 2009-09-24 | Daikin Ind Ltd | 膨張機 |
US20110225999A1 (en) * | 2008-06-03 | 2011-09-22 | Panasonic Corporation | Refrigeration cycle apparatus |
WO2010007730A1 (ja) * | 2008-07-18 | 2010-01-21 | パナソニック株式会社 | 冷凍サイクル装置 |
JP4466774B2 (ja) * | 2008-09-10 | 2010-05-26 | ダイキン工業株式会社 | 調湿装置 |
WO2010039630A2 (en) * | 2008-10-01 | 2010-04-08 | Carrier Corporation | High-side pressure control for transcritical refrigeration system |
KR101252173B1 (ko) * | 2010-11-23 | 2013-04-05 | 엘지전자 주식회사 | 히트 펌프 및 그 제어방법 |
JP2011153825A (ja) * | 2011-05-20 | 2011-08-11 | Mitsubishi Electric Corp | 冷凍空調装置 |
KR101837451B1 (ko) * | 2011-11-29 | 2018-03-12 | 삼성전자주식회사 | 냉장고 |
JP5500240B2 (ja) * | 2012-05-23 | 2014-05-21 | ダイキン工業株式会社 | 冷凍装置 |
CN103423909B (zh) * | 2013-09-12 | 2015-08-12 | 张周卫 | 螺旋压缩膨胀制冷机 |
CN111536712A (zh) * | 2020-04-13 | 2020-08-14 | 南京天加环境科技有限公司 | 一种双压缩机空气源冷水热泵机组及其控制方法 |
DE102020117343A1 (de) * | 2020-07-01 | 2022-01-05 | Weinmann Emergency Medical Technology Gmbh + Co. Kg | Pumpvorrichtung, Vorrichtung zur Beatmung sowie Verfahren zur Bereitstellung eines Atemgases |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004060989A (ja) * | 2002-07-29 | 2004-02-26 | Denso Corp | 蒸気圧縮式冷凍機及び膨脹機一体型圧縮機 |
JP2004108683A (ja) * | 2002-09-19 | 2004-04-08 | Mitsubishi Electric Corp | 冷凍空調装置及び冷凍空調装置の運転方法 |
JP2004150748A (ja) * | 2002-10-31 | 2004-05-27 | Matsushita Electric Ind Co Ltd | 冷凍サイクル装置 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07217406A (ja) * | 1994-02-01 | 1995-08-15 | Hitachi Ltd | 膨張機のバイパスライン |
SE510794C2 (sv) * | 1997-12-17 | 1999-06-21 | Svenska Rotor Maskiner Ab | Sätt och anordning för styrning av kyleffekt i kalluftssystem |
AU750232B2 (en) * | 1998-08-13 | 2002-07-11 | United States Environmental Protection Agency | Dual-cylinder expander engine and combustion method with two expansion strokes per cycle |
JP4172088B2 (ja) * | 1999-04-30 | 2008-10-29 | ダイキン工業株式会社 | 冷凍装置 |
JP2001116371A (ja) | 1999-10-20 | 2001-04-27 | Daikin Ind Ltd | 空気調和装置 |
CN2453345Y (zh) * | 2000-12-05 | 2001-10-10 | 浙江大学 | 利用涡旋机械的绿色天然工质制冷空调器 |
US6595024B1 (en) * | 2002-06-25 | 2003-07-22 | Carrier Corporation | Expressor capacity control |
JP3897681B2 (ja) * | 2002-10-31 | 2007-03-28 | 松下電器産業株式会社 | 冷凍サイクル装置の高圧冷媒圧力の決定方法 |
-
2004
- 2004-07-07 JP JP2004200987A patent/JP4389699B2/ja not_active Expired - Fee Related
-
2005
- 2005-07-01 US US11/631,674 patent/US7730741B2/en not_active Expired - Fee Related
- 2005-07-01 WO PCT/JP2005/012219 patent/WO2006004047A1/ja active Application Filing
- 2005-07-01 KR KR1020077003013A patent/KR100828268B1/ko not_active IP Right Cessation
- 2005-07-01 AU AU2005258417A patent/AU2005258417B2/en not_active Ceased
- 2005-07-01 EP EP05765258.8A patent/EP1780478B1/en not_active Not-in-force
- 2005-07-01 CN CNB200580020728XA patent/CN100445667C/zh not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004060989A (ja) * | 2002-07-29 | 2004-02-26 | Denso Corp | 蒸気圧縮式冷凍機及び膨脹機一体型圧縮機 |
JP2004108683A (ja) * | 2002-09-19 | 2004-04-08 | Mitsubishi Electric Corp | 冷凍空調装置及び冷凍空調装置の運転方法 |
JP2004150748A (ja) * | 2002-10-31 | 2004-05-27 | Matsushita Electric Ind Co Ltd | 冷凍サイクル装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1780478A4 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012098024A (ja) * | 2006-12-08 | 2012-05-24 | Daikin Industries Ltd | 冷凍装置 |
EP2090746A4 (en) * | 2006-12-08 | 2016-06-01 | Daikin Ind Ltd | FREEZING APPARATUS AND REGULATOR |
JP2012515890A (ja) * | 2009-01-20 | 2012-07-12 | パナソニック株式会社 | 冷凍サイクル装置 |
Also Published As
Publication number | Publication date |
---|---|
JP2006023004A (ja) | 2006-01-26 |
JP4389699B2 (ja) | 2009-12-24 |
US7730741B2 (en) | 2010-06-08 |
CN1973167A (zh) | 2007-05-30 |
CN100445667C (zh) | 2008-12-24 |
US20070251245A1 (en) | 2007-11-01 |
KR20070035067A (ko) | 2007-03-29 |
AU2005258417B2 (en) | 2008-10-16 |
KR100828268B1 (ko) | 2008-05-07 |
EP1780478A1 (en) | 2007-05-02 |
EP1780478A4 (en) | 2014-12-24 |
EP1780478B1 (en) | 2016-12-21 |
AU2005258417A1 (en) | 2006-01-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2006004047A1 (ja) | 冷凍装置 | |
JP2006023004A5 (ja) | ||
JP4517684B2 (ja) | ロータリ式膨張機 | |
JP4946840B2 (ja) | 冷凍装置 | |
WO2006013959A1 (ja) | 容積型膨張機及び流体機械 | |
WO2006098165A1 (ja) | 冷凍装置 | |
WO2005090875A1 (ja) | 冷凍装置 | |
JP2001116371A (ja) | 空気調和装置 | |
WO2006013961A1 (ja) | 膨張機 | |
JP2003121018A (ja) | 冷凍装置 | |
JP2006138525A (ja) | 冷凍装置及び空気調和機 | |
JP2003287295A (ja) | ターボ冷凍機の容量制御駆動機構 | |
JP4735159B2 (ja) | 膨張機 | |
JP2006010278A (ja) | 冷蔵庫 | |
JP2004003692A (ja) | 冷凍装置 | |
JP4581795B2 (ja) | 冷凍装置 | |
JP2013096602A (ja) | 冷凍サイクル装置 | |
JP3661014B2 (ja) | 冷凍装置 | |
JP2009133319A (ja) | 容積型膨張機及び流体機械 | |
JP2013019336A (ja) | 膨張機および冷凍装置 | |
JP2006284086A (ja) | 冷凍装置 | |
JP5240356B2 (ja) | 冷凍装置 | |
JP5169003B2 (ja) | 空気調和装置 | |
JP5233690B2 (ja) | 膨張機 | |
JP2010243021A (ja) | 膨張機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS KE KG KM KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NG NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU LV MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2005258417 Country of ref document: AU Ref document number: 200580020728.X Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 11631674 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: DE |
|
REEP | Request for entry into the european phase |
Ref document number: 2005765258 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2005765258 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 2005258417 Country of ref document: AU Date of ref document: 20050701 Kind code of ref document: A |
|
WWP | Wipo information: published in national office |
Ref document number: 2005258417 Country of ref document: AU |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020077003013 Country of ref document: KR |
|
WWP | Wipo information: published in national office |
Ref document number: 1020077003013 Country of ref document: KR |
|
WWP | Wipo information: published in national office |
Ref document number: 2005765258 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 11631674 Country of ref document: US |