WO2006057212A1 - 流体機械およびそれを用いたヒートポンプ装置 - Google Patents
流体機械およびそれを用いたヒートポンプ装置 Download PDFInfo
- Publication number
- WO2006057212A1 WO2006057212A1 PCT/JP2005/021349 JP2005021349W WO2006057212A1 WO 2006057212 A1 WO2006057212 A1 WO 2006057212A1 JP 2005021349 W JP2005021349 W JP 2005021349W WO 2006057212 A1 WO2006057212 A1 WO 2006057212A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- working fluid
- suction
- pressure
- discharge
- expander
- Prior art date
Links
Classifications
-
- 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
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F01C1/3562—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F01C1/3564—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F01C1/3442—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
-
- 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
- F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
-
- 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
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
- F04C18/34—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 relative reciprocation between the co-operating members
- F04C18/344—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F04C18/3442—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
-
- 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
- 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
- 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
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and 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
- 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
Definitions
- the present invention relates to an expander-integrated fluid machine connected to an expander that supplies a high-pressure working fluid to generate rotational power, and a heat pump device using the expander-integrated fluid machine.
- FIG. 11 shows a system configuration of a conventional general power recovery type air conditioner.
- the system includes a condenser 101, an evaporator 102, a compressor 103, and an expander 104.
- the compressor 103 compresses the working fluid and an expansion that generates rotational power from the high-pressure working fluid.
- the machine 104 is connected to the motor 105 in one axis.
- the expander 104 is configured to generate rotational power by ideally entropy expansion of the high-pressure working fluid and directly assist the driving power of the compressor 103.
- the reason why the compressor 103 and the expander 104 are connected to each other is that the structure is simple and the power recovery loss is small.
- Fig. 12 shows how the refrigeration cycle changes when the working fluid is carbon dioxide.
- 1 ⁇ 2 is the compression process in which the working fluid is compressed and raised from the low pressure P1 to the high pressure Ph in the compressor 103
- 2 ⁇ 3 is in the condenser 101
- 3 ⁇ 4 is the expansion process in which the working fluid is expanded from the high pressure Ph to the low pressure P1 in the expander 104 to recover the power
- 4 ⁇ 1 is the isobaric heat absorption process in the evaporator 102. Show.
- FIG. 13 shows another conventional air conditioner system. The configuration is shown. In the present air conditioner, a bypass pipe 112 is provided between the discharge pipe 110 and the suction pipe 111 of the expander 104, and the passage area of the bypass pipe 112 is adjusted to increase or decrease. A control valve 106 is provided.
- the air conditioner having such a configuration performs the following operations.
- a target value of the discharge temperature of the compressor 103 is set, and then the opening degree of the control valve 106 is controlled so that the discharge temperature of the compressor 103 becomes the target value.
- the control valve 106 is controlled in the closing direction, the amount of working fluid passing through the bypass line 112 decreases, and the amount of working fluid entering the expander 104 increases.
- the control valve 106 is controlled to open, the amount of working fluid that passes through the bypass line 112 increases, and the amount of working fluid that enters the expander 104 decreases.
- the pressure after the expansion of the working fluid is reduced under the operating conditions where the ratio of the high pressure to the low pressure of the system (pressure ratio) is smaller than the pressure ratio assumed in the design of the expander. This is to prevent the amount of recovered power from falling below the pressure (loss due to overexpansion).
- the communication passage is branched from the working fluid inflow side of the expander and communicates with the suction Z expansion process position of the expander, and the communication passage is provided with a valve for controlling the passage of the working fluid. When the conditions arise, the valve is opened to allow a part of the working fluid to flow into the expander, increasing the amount of working fluid entering the expander, and increasing the pressure of the working fluid after expansion.
- the carbon dioxide supercritical refrigeration cycle rotary expansion device (not shown) is mainly composed of a cylinder body, a rolling piston, an eccentric cam shaft, a pedestal, and an electromagnetic valve.
- the inner chamber of the expansion device is divided into two high-pressure chambers and two low-pressure chambers by the main / sub bearings and the intermediate partition plate.
- Carbon dioxide enters the expansion cylinder, moves the force eccentric cam shaft, changes the volume of the expansion cylinder, lowers the fluid pressure, and outputs mechanical power.
- the intake time of the expansion device is controlled by outputting a signal based on the rotation angle of the eccentric cam shaft and controlling the opening of the electromagnetic valve, and this causes the power generation cycle to be performed.
- Patent Document 1 JP 2001-116371 A
- Patent Document 2 JP 2004-197640 A
- Patent Document 3 Patent CN1164904C
- the dead space on the intake side it is possible to recover the maximum power from the high-pressure working fluid and to provide an expander-integrated fluid machine that always obtains high operating efficiency.
- the fluid machine of the present invention has a compression chamber and a drive shaft, and compresses the working fluid sucked into the compression chamber by rotating the drive shaft, and the expansion chamber and the expansion chamber. It has a suction hole that guides the working fluid with pressure, a discharge hole that discharges the working fluid from the expansion chamber, and a power recovery shaft connected to the drive shaft. The working fluid sucked into the expansion chamber is expanded to expand the power recovery shaft.
- An expander unit for obtaining rotational power a sealed container having a compressor unit and an expander unit disposed therein, and a suction valve for controlling the amount of working fluid introduced into the expansion chamber in the sealed container. It is a thing. According to the present embodiment, the dead space between the suction valve and the expansion chamber can be reduced, and the amount of working fluid introduced into the expansion chamber by the suction valve can be controlled with high operating efficiency.
- the fluid machine of the present invention detects the expander discharge pressure of the working fluid discharged by the discharge hole force.
- the pressure of the suction valve and the amount of working fluid guided from the suction hole to the expansion chamber become a target amount determined from the expander suction pressure and the expander discharge pressure that maximize the refrigeration cycle efficiency.
- an opening / closing timing control means for controlling the opening / closing timing.
- an expander-integrated fluid machine capable of always obtaining high operating efficiency can be obtained by varying the opening / closing timing of the suction valve so that the expansion chamber has an ideal volume. provide.
- the fluid machine of the present invention includes a suction temperature sensor that measures the suction temperature of the working fluid sucked into the suction hole, and a discharge temperature sensor that measures the discharge temperature of the working fluid discharged from the discharge hole.
- the expansion machine suction pressure is obtained from the discharge temperature.
- the target suction pressure that maximizes the refrigeration cycle efficiency can be obtained by calculation.
- the fluid machine of the present invention includes a discharge temperature sensor that measures the discharge temperature of the working fluid discharged from the discharge hole, and the discharge temperature force also obtains the expander discharge pressure, and the working fluid guided from the suction hole to the expansion chamber And an opening / closing timing control means for controlling the opening / closing timing of the intake valve so that the amount of air reaches the target amount obtained from the expander suction pressure and the expander discharge pressure that maximize the refrigeration cycle efficiency. It is. According to this embodiment, it can be linked to cost reduction.
- the suction valve is an electromagnetic valve. According to the present embodiment, the opening / closing timing can be easily measured, and the problem of non-inflation can be prevented.
- the opening timing at which the suction valve is opened from the closed time is defined as the suction start time at which the volume of the expansion chamber is minimized, and the closing timing at which the suction valve is opened from the closed time is determined from the suction start time to the expansion chamber. It is configured to have a control function that sets the time until the volume reaches the volume corresponding to the target amount. According to the present embodiment, the brake loss can be minimized, and the volume of the expansion chamber into which the working fluid is introduced can be set to an ideal volume.
- the fluid machine of the present invention is provided with a working fluid state holding unit that holds the relationship between the volume and pressure of the working fluid when expanding in the expansion chamber, and the operation that the working fluid state holding unit holds The target amount is obtained using the relationship between the volume of the fluid and the pressure.
- the relationship between the volume of the working fluid and the pressure can be an approximate expression of a practical expansion process, for example, and higher operating efficiency can be obtained.
- the fluid machine of the present invention operates using a working fluid that expands from a supercritical phase to a liquid phase or a gas-liquid two phase.
- the fluid machine of the present invention is operated using a working fluid mainly composed of carbon dioxide.
- the fluid machine of the present invention is provided with a discharge valve in the first discharge hole of the expander. According to the present embodiment, it is possible to prevent occurrence of overexpansion loss.
- the discharge valve is a reed valve, and the discharge valve opens when the pressure in the expansion chamber reaches a predetermined value.
- the reed valve automatically opens when the pressure reaches a predetermined value, and recompression is possible so as not to cause an overexpansion loss.
- the heat pump device controls the opening / closing timing of the intake valve so that the amount of the working fluid guided to the expansion chamber becomes a target amount that maximizes the refrigeration cycle efficiency. According to the present embodiment, the operation efficiency of the heat pump device can always be increased.
- the opening / closing timing of the suction valve can be controlled, and the amount of working fluid guided to the expansion chamber can be set to a target amount that provides high operating efficiency.
- FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view of an expander section in the compressor of the present embodiment
- FIG. 4 is a diagram showing the relationship between the opening / closing timing of the solenoid valve and the flow rate of the working fluid entering the working chamber in the present embodiment.
- FIG. 5 is a perspective view of an angle detection gear in the compressor of the present embodiment.
- FIG. 13 System configuration diagram of another conventional air conditioner
- FIG. 1 is a longitudinal sectional view of the compressor according to the first embodiment of the present invention
- FIG. 2 is a transverse sectional view of an expander section in the compressor according to the present embodiment.
- 1 and 2 show a rotary vane compressor and expander, but the compressor and expander are not limited to this.
- the rotary type, reciprocating type and scrolling type may be used.
- As the working fluid a working fluid that expands from a supercritical phase to a liquid phase or a gas-liquid two phase, for example, a working fluid mainly composed of carbon dioxide is used.
- the compressor according to the present embodiment includes a compressor unit 12, an electric motor unit 16, an expander unit 20, and a control unit inside a hermetic container 10.
- This control unit may be arranged inside or outside the closed container 10.
- the compressor unit 12 includes a compression chamber 13, a drive shaft 14, and a rotor 15. By rotating the drive shaft 14 and the rotor 15, the working fluid sucked into the compression chamber 13 is changed from a low pressure to a high pressure. Compress.
- the electric motor section 16 includes a stator 17 and a rotor 18, and the rotor 18 is fixed to the drive shaft 14.
- the expander unit 20 includes a cylinder 21, a rotor 23, and a power recovery shaft 26 (hereinafter referred to as a shaft 26).
- the expander unit 20 sucks the working fluid through the suction path 32 and the suction hole 27, and the cylinder 21 and the rotor 23 A high pressure is expanded to a low pressure in the working chamber 25 as an expansion chamber to be formed, and the shaft 26 is rotated by discharging from the working chamber 25 through the discharge chamber 33 and the discharge passage 34. This rotational power is transmitted from the shaft 26 to the drive shaft 14 and is recovered as the driving force of the compressor section 12.
- the expander section 20 provided in the sealed container 10 includes a cylinder 21, a port 23, four vanes 24, a shaft 26, a canopy 31, a suction pipe. 35 and a solenoid valve 40.
- the cylinder 21 has a cylindrical inner wall 21a, and side plates 21b and 21c (see FIG. 1) are provided at both ends thereof.
- a cylindrical rotor 23 is disposed inside the cylinder 21, and a part of the outer periphery of the rotor 23 forms a small gap 22 with the inner wall 21 a of the cylinder 21.
- the inner wall 21 a and the outer periphery of the rotor 23 are in contact with each other at the base point (contact point) of the small gap 22.
- the rotor 23 is provided with four grooves 23a perpendicular to the upper and lower end surfaces at a pitch of 90 deg.
- Each vane 24 is slidably inserted in each groove 23 a, and the tip of the vane 24 is in contact with the inner wall 21 a of the cylinder 21.
- the working chamber 25 is formed as a space 25a, 25b, 25c, 25d, 25e surrounded by the inner wall 21a of the cylinder 21, the rotor 23 and the vanes 24! /.
- the shaft 26 is formed integrally with the rotor 23, and is rotatably supported by the side plates 21b and 21c. It is connected to 12 drive shafts 14.
- the cylinder 21 is provided with a suction hole 27 through which the working fluid flows into the working chamber 25 and a discharge hole 28 through which the working chamber 25 force also flows out the working fluid.
- the electromagnetic valve 40 that constitutes a part of the expander unit 20 in the sealed container 10 is disposed in the suction hole 27 immediately before the inlet of the working chamber 25 (that is, the expansion chamber).
- an opening 28a that is opened in a range in the circumferential direction of the inner wall 21a of the cylinder 21.
- the range in which the opening 28a is provided is that if the number of vanes 24 is n, the base force of the small gap 22 is also at the start position 28b of ⁇ 180 X (l + 1 / n) ⁇ deg in the rotational direction indicated by the arrow of the shaft 26.
- the range starts and ends at the end position 28c in the vicinity of the small gap 22.
- the starting position 28b of the opening 28a in FIG. 2 is a position of 225 deg because there are four vanes 24.
- a cover 31 is provided on the side of the cylinder 21, and a suction pipe 35 is inserted into the cover 31, and a suction path 32 that guides the working fluid to the suction hole 27 is formed inside the suction pipe 35.
- a discharge chamber 33 for temporarily storing the working fluid flowing out from the discharge hole 28 is formed inside the sealed container 10, and inside the discharge pipe 36 joined to the sealed container 10, A discharge path 34 is formed through which the working fluid flows out from the discharge chamber 33.
- control unit includes a discharge pressure sensor 48, a suction temperature sensor 50, a discharge temperature sensor 51, a gap sensor 52, a solenoid valve control unit 60, and a working fluid state holding unit 61. Composed.
- the solenoid valve 40 is energized via the solenoid valve control unit 60, and the solenoid valve 40 is electrically opened and closed to control the communication between the working chamber 25 and the suction hole 27.
- the solenoid valve 40 be normally opened and closed when energized (controlled), assuming an electrical problem. The reason for this is that if the solenoid valve is a normally open solenoid valve, it is easy to control the opening and closing of the valve (measure the timing of opening and closing), and it will not close even if an electrical problem occurs. This is because it does not function as an expander, which prevents the problem of non-expansion.
- the suction temperature sensor 50 measures the temperature of the working fluid in the suction path 32 or the suction hole 27 as the suction temperature Tb of the expander. Further, the discharge pressure sensor 48 and the discharge temperature sensor 51 measure the pressure and temperature of the working fluid in the discharge chamber 33 or the discharge path 34 as the discharge pressure Pc and the discharge temperature Tc of the expander. Any temperature sensor or pressure sensor may be used as long as it can measure the temperature and pressure of the working fluid. Also, the expander intake temperature Tb is measured between the condenser (see Fig. 11) and the intake pipe 35, and the expander discharge pressure Pc and the expander (see Fig. 11) are measured between the discharge pipe 36 and the evaporator (see Fig. 11). The discharge temperature Tc may be measured. The gap sensor 52 detects the rotation angle ⁇ X of the shaft 14 using an angle detection gear 45 provided on the shaft 14.
- the solenoid valve control unit 60 controls the opening and closing of the solenoid valve 40.
- the working fluid state holding unit 61 holds data indicating the relationship between the volume and pressure of the working fluid when the working fluid expands in the working chamber 25, an approximate expression, and the like, and is configured using, for example, a semiconductor memory. Has been.
- the working fluid state holding unit 61 may be integrated with the solenoid valve control unit 60! / ⁇ .
- the working chamber 25 is a space 25 a on the suction hole 27 side of the small gap 22. Thereafter, while the volume is increased with the rotation of the rotor 23, a process of sucking a working fluid having a suction pressure Pb corresponding to the high pressure Ph of the refrigeration cycle from the suction hole 27, that is, a suction process is performed.
- the inhalation process corresponds to AB in Fig. 3.
- the working chamber 25 When the working chamber 25 reaches the position of the space 25b, the communication with the suction hole 27 is cut off to become a sealed space, and then the volume increases with the rotation of the rotor 23, and the pressure of the working fluid inside decreases.
- the process of going, that is, the expansion process is performed.
- the expansion process corresponds to BC in Fig. 3.
- the working chamber 25 has a maximum volume at the position of the space 25c. This time corresponds to C in Fig. 3, and the discharge pressure in the working chamber 25 is Pc. From the moment when the rotor 23 is slightly rotated from here, the working chamber 25 located in the space 25c communicates with the discharge hole 28 through the opening 28a, and the working fluid is pushed out from the working chamber 25 to the discharge chamber 33.
- the low pressure P1 of the refrigeration cycle varies depending on the heat exchange conditions in the evaporator (see FIG. 11), the operating conditions of the refrigeration cycle, and the like.
- the ratio of the volume at the moment when the working fluid is sealed (space 25b in FIG. 2) to the volume immediately before the working fluid is discharged (space 25c in FIG. 2), that is, the expansion ratio is constant. Therefore, when the low pressure P1 fluctuates, it cannot be made equal to the discharge pressure Pc of the expander. Therefore, in the present embodiment, the operation of changing the amount of working fluid sucked into the working chamber 25 using the electromagnetic valve 40 and controlling the discharge pressure Pc of the expander and the low pressure P1 of the refrigeration cycle to be equal is performed. Done.
- FIG. 4 shows the relationship between the opening / closing timing of the solenoid valve 40 in the present embodiment and the flow rate of the working fluid entering the working chamber 25 during the suction process.
- time Top the time from when the solenoid valve 40 is closed to open
- time Tel the time from when the solenoid valve 40 is opened to closed
- the solenoid valve 40 is controlled to be opened immediately before the working chamber 25 communicates with the suction hole 27. If the solenoid valve 40 is kept closed at this time, the working chamber 25 is evacuated as it rotates, which causes a loss of braking the rotation of the rotor 23, which is not preferable. That is, the brake loss is minimized by a configuration having a control function in which the opening timing (that is, the time Top) at which the solenoid valve 40 is opened from the closed state is set to the suction start time at which the volume of the working chamber 25 is minimized. Can do.
- the working chamber 25 communicates with the suction hole 27 and the working fluid is sucked into the working chamber 25.
- the electromagnetic valve 40 is closed at a time Tel in which the working chamber 25 reaches the maximum volume Vb that can be sucked.
- the suction amount of the working fluid becomes a volume Vb ′ smaller than the maximum volume Vb.
- the magnitude of Vb ′ can be varied by changing the timing of the closing time Tel of the solenoid valve 40.
- the configuration having a control function that sets the closing timing (that is, at the time of time Tel) for closing the solenoid valve 40 from the suction start time to the time when the volume of the working chamber 25 becomes the maximum The amount of inhalation can be varied.
- a solenoid valve 40 is provided in the suction hole 27 just before the inlet of the working chamber 25, and the distance from the solenoid valve 40 to the inlet of the working chamber 25 of the suction hole 27 is shortened.
- the dead space in which the water cannot be recovered becomes smaller, and the reduction in expansion efficiency can be avoided.
- the efficiency of the refrigeration cycle and the high pressure Ph have a relationship that maximizes the efficiency at a certain high pressure.
- the optimal pressure Popt the high pressure that maximizes the refrigeration cycle efficiency
- te is the evaporator temperature (that is, the temperature corresponding to the discharge temperature Tc of the expander)
- tg is the condenser outlet temperature (that is, the temperature corresponding to the suction temperature Tb of the expander)
- the respective temperatures are the discharge temperatures. It can be measured by the sensor 51 and the suction temperature sensor 50. Then, using Equation 1, a target expander suction pressure Popt can be calculated from the suction temperature Tb and the discharge temperature Tc.
- the refrigeration cycle is operated so that the high pressure Ph, that is, the suction pressure Pb of the expander corresponding to the high pressure Ph becomes the optimum pressure Popt as the target expander suction pressure. It is desirable because it maximizes.
- the saturation pressure 'temperature of the working fluid is determined based on the evaporator temperature te. From this relationship, the low pressure P1 (evaporator pressure) of the refrigeration cycle, that is, the discharge pressure Pc of the expander corresponding to the low pressure P1 can be obtained. That is, even if the discharge pressure sensor 48 is not provided, a configuration in which the discharge temperature Tc measured by the discharge temperature sensor 51 is converted to obtain the expander discharge pressure Pc can be obtained, which leads to cost reduction.
- the volume Vc of the working chamber 25 in the final state C (space 25c in FIG. 3) of the expansion process (curve BC in FIG. 3) is also known from the design specifications. Therefore, if the relationship between the volume of the working chamber 25 and the pressure is known, the target volume Vb of the expansion chamber that sucks the working fluid is determined by changing the state transition from the final state C to the initial state B of the expansion process. can do. For example, assuming that the working fluid is an ideal gas and the ideal isentropic change that does not cause leakage, friction, or heat in / out during the expansion process, the relationship between the volume of the working chamber 25 and the pressure is expressed by the following equation.
- Equation 2 in order to obtain the optimum pressure Popt with the suction pressure Pb as the target in the initial state B of the expansion process, the low pressure P1 in the final state C (that is, the detected discharge pressure Pc) From the chamber volume Vc (known from the design specifications), Vb expressed by the following equation is the target volume to be set for B, that is, the working fluid suction amount.
- Vbo ' (Pl / Popt) 1 / ⁇ Vc
- the timing of closing the electromagnetic valve 40 is determined. That is, the amount of working fluid introduced into the expansion chamber is determined by the expansion machine discharge pressure Pc (i.e., low pressure P1), suction temperature Tb, and discharge temperature Tc force. The time Tel will be determined so that the target amount obtained from
- An example of the method for determining the time Tel from the target volume Vb is as follows.
- An angle detection gear 45 for detecting the rotation angle is installed on a part of the shaft 14.
- the angle detection gear 45 has a shape in which irregularities are regularly engraved in the circumferential direction, part of which is not concave, and a part 45a. Without the recess, the rotation angle ⁇ X of the shaft 14 is detected by reading the unevenness of the angle detection gear 45 accompanying the rotation of the shaft 14 with the gap sensor 52 using the portion 45a as a rotation base.
- the rotation angle ⁇ bo from the base point to the point of the target volume Vb is obtained and the detected rotation
- the time when the angle ⁇ X reaches the rotation angle ⁇ bo is time Tel, and is the closing timing of the solenoid valve 40.
- the relationship between the volume and pressure of the working fluid in the expansion process is preferably expressed using experimental data or an approximate expression that also obtains experimental data force.
- obtaining the target volume Vb will result in higher operating efficiency compared to obtaining the target volume Vb.
- the above-described working fluid state holding unit 61 holds data and approximate expressions representing the relationship between the volume and pressure of the above-described working fluid and the relationship between the saturation pressure and the temperature of the above-described working fluid.
- the working fluid state holding unit 61 that holds the relationship between the volume and pressure of the working fluid when expanding in the expansion chamber is provided, and the target volume Vb (that is, the target that maximizes the refrigeration cycle efficiency) is provided using this relationship. If it is the structure which calculates
- the electromagnetic valve 40 is installed in the suction hole 27 in the sealed container 10 and immediately before the working chamber 25, and the low pressure P1 of the refrigeration cycle is detected. Operates by controlling the opening time (Tel Top) of the solenoid valve 40 with the solenoid valve controller 60 so that the high pressure Ph of the refrigeration cycle becomes the optimum pressure Popt that maximizes the refrigeration cycle efficiency based on P1 In other words, the flow rate of the working fluid entering the chamber 25 is adjusted.
- the compressor of the present embodiment is used in a heat pump device to control the opening / closing timing of the intake valve of the compressor so that the amount of working fluid led to the expansion chamber becomes a target amount that maximizes the refrigeration cycle efficiency. As a result, the operation efficiency of the heat pump device can be constantly increased.
- FIG. 6 is a longitudinal sectional view of the compressor according to the second embodiment of the present invention
- FIG. 7 is a transverse sectional view of the compressor shown in FIG.
- the compressor of the present embodiment shows the detailed shape of the rolling piston type expander section and the solenoid valve, and has a different configuration and operation from the first embodiment. I will explain the work. And the description regarding the same composition and the same operation is omitted.
- the compressor according to the present embodiment includes a compressor unit 12, an electric motor unit 16, an expander unit 70, and a control unit inside the sealed container 10.
- the expander unit 70 is fitted with a power recovery shaft 76 having an eccentric portion 76a (hereinafter referred to as shaft 76), a cylinder 71 having a cylindrical inner wall 71a, and the eccentric portion 76a.
- a rotor 73 that performs eccentric rotational movement inside the cylinder 71, and reciprocates inside the vane groove 71b of the cylinder 71 with its tip in contact with the rotor 73, and serves as an expansion chamber between the cylinder 71 and the rotor 73.
- the side plate 71c including 71c, 71d (see FIG. 6), the suction pipe 35, and the solenoid valve 40 is connected to the suction pipe 35, and the working fluid sucked from the suction pipe 35 is introduced into the working chamber 25. It has a suction hole 27.
- the side plate 71d has a discharge hole 78 for discharging the working fluid expanded in the working chamber 25 to the discharge chamber 33.
- the electromagnetic valve 40 that is part of the expander unit 70 in the sealed container 10 includes a frame 80, a plunger 81, a core 82, a solenoid 83, and a spring 8. 4 and the like, and is arranged near the inlet of the working chamber 25 of the suction hole 27.
- the electromagnetic valve 40 is installed in the airtight container 10 in the vicinity of the working chamber 25 of the suction hole 27, and the opening / closing timing of the electromagnetic valve 40 is varied to enter the working chamber 25.
- the number of bypass lines can be reduced and the valve control
- the maximum power recovery from the high-pressure working fluid can be achieved to always obtain high operating efficiency. Can do.
- the rolling piston type expander part of the present embodiment has an advantage that the number of times of opening and closing the electromagnetic valve can be reduced as compared with the rotary vane type expander part of the first embodiment.
- FIG. 8 is a longitudinal sectional view of the compressor according to the third embodiment of the present invention
- FIG. 9 is a transverse sectional view of an expander section in the compressor according to the present embodiment.
- 8 and 9 show rotary vane type compressors and expanders, but the compressor and expander types are not limited to this, and other types such as rotary type, reciprocating type, scroll type, etc. But you can.
- the working fluid a working fluid that expands from a liquid phase or a supercritical phase to a gas-liquid two phase, or a working fluid mainly composed of carbon dioxide is used.
- the compressor of the present embodiment is configured to include a compressor unit 12, an electric motor unit 16, and an expander unit 20 inside the hermetic container 10.
- the compressor unit 12 includes a compression chamber 13, a drive shaft 14, and a rotor 15, and compresses the working fluid sucked into the compression chamber 13 from a low pressure to a high pressure by rotating the drive shaft 14 and the rotor 15.
- the electric motor unit 16 includes a stator 17 and a rotor 18, and the rotor 18 is fixed to the drive shaft 14.
- the expander unit 20 includes a cylinder 21, a rotor 23, and a shaft 26, and sucks the working fluid through the suction passage 32 and the suction hole 27, and is high in the working chamber 25 formed by the cylinder 21 and the rotor 23.
- the pressure is also expanded to a low pressure and discharged from the working chamber 25 through the discharge chamber 33 and the discharge path 34, thereby obtaining rotational power for the shaft 26.
- This rotational power is transmitted from the shaft 26 to the drive shaft 14 and is recovered as the drive force of the compressor unit 12.
- the expander ⁇ 20 has a cylinder 21, a rotor 23, four vanes 24, a shaft 26, a valve mechanism 30, a cover 31, a suction pipe 35, an electromagnetic That is, the cylinder 21 includes a cylindrical inner wall 21a, and side plates 21b and 21c (see FIG. 8) at both ends thereof. Is provided.
- a cylindrical rotor 23 is disposed inside the cylinder 21, and a part of the outer periphery of the rotor 23 forms a small gap 22 with the inner wall 21 a of the cylinder 21.
- the inner wall 21 a and the outer periphery of the rotor 23 are in contact with each other at the base point (contact point) of the small gap 22.
- the rotor 23 is provided with four grooves 23a perpendicular to the upper and lower end surfaces at a pitch of 90 deg.
- Each vane 24 is slidably inserted in each groove 23 a, and the tip of the vane 24 is in contact with the inner wall 21 a of the cylinder 21.
- the working chamber 25 is formed as a space 25a, 25b, 25c, 25d, 25e surrounded by the inner wall 21a of the cylinder 21, the rotor 23 and the vanes 24! /.
- the shaft 26 is formed integrally with the rotor 23, is rotatably supported on the side plates 21b and 21c, and is connected to the drive shaft 14 of the compressor unit 12.
- the electromagnetic valve 40 that is part of the expander unit 20 in the sealed container 10 is disposed at a position close to the working chamber 25 of the suction hole 27.
- the cylinder 21 has a suction hole 27 through which the working fluid flows into the working chamber 25, a first discharge hole 28 (hereinafter referred to as a discharge hole 28) and a second discharge hole 29 through which the working chamber 25 force working fluid flows out. (Hereinafter, the discharge hole 29) is provided.
- the discharge hole 28 is moved to a position where the base force of the small gap 22 has moved by an angle of ⁇ 180 X (1 + 1 / n) ⁇ deg in the rotation direction indicated by the arrow of the shaft 26. Is provided.
- the discharge hole 28 is provided with a valve mechanism 30 including a discharge valve lead valve 30a and a valve stop 30b.
- the discharge hole 29 is provided in the vicinity of the base point of the small gap 22, and a part of the discharge hole 29 has a shape including the position of the base point of the small gap 22 at a position of 315 deg in the rotation direction of the shaft 26.
- No valve mechanism is provided.
- the position of the discharge hole 29 is not limited to this. If the center angle around the shaft 26 of the inner wall 21a of the cylinder 21 between the suction hole 27 and the discharge hole 29 is n vanes 24 (360Zn) or less As long as the discharge hole 29 is in the vicinity of the base point of the small gap 22.
- a cover 31 is provided on the side of the cylinder 21, and the suction pipe 35 is provided on the cover 31. Is inserted, and a suction passage 32 for guiding the working fluid to the suction hole 27 is formed in the suction pipe 35.
- a discharge chamber 33 for storing and storing the working fluid flowing out from the discharge holes 28 and 29 is formed inside the sealed container 10, and the discharge pipe 36 joined to the sealed container 10 is provided. Inside, a discharge path 34 is formed for allowing the working fluid to flow out from the discharge chamber 33 to the outside.
- the solenoid valve 40 is energized through a wiring (not shown) from a control device (not shown), and the solenoid valve 40 is electrically opened and closed, whereby communication between the suction hole 27 and the suction path 32 is established. It is configured to control. In addition, it is desirable that the solenoid valve 40 be normally opened and closed when energized (controlled), assuming an electrical problem. The reason for this is that if an electromagnetic valve is used, it is easy to control the opening and closing of the valve (timing the opening and closing timing), and since it is a normally open solenoid valve that does not close even with an electrical trouble, the expander As a result, the non-inflating harmful effect of not functioning as a non-function is prevented.
- FIG. 3 is a PV diagram of the working chamber when the solenoid valve is normally open in the present embodiment, that is, a PV diagram of the working chamber 25 of the expansion unit 20. Note that the description of the compressor section not related to the features of the present invention is omitted.
- the working chamber 25 is generated in a space 25 a on the suction hole 27 side of the small gap 22. Thereafter, the process of sucking the working fluid having the high-pressure side pressure Pb from the suction hole 27, that is, the suction process is performed while increasing the volume as the rotor 23 rotates.
- the inhalation process corresponds to AB in Figure 3.
- the working chamber 25 When the working chamber 25 reaches the position of the space 25b, the communication with the suction hole 27 is cut off to become a sealed space, and then the volume increases with the rotation of the rotor 23, and the pressure of the working fluid inside decreases.
- the process of going, that is, the expansion process is performed.
- the expansion process corresponds to BC in Fig. 3.
- the working chamber 25 has a maximum volume at the position of the space 25c. This time corresponds to C in Fig. 3, and the pressure in the working chamber 25 is Pc. Then, at the moment when the rotor 23 is slightly rotated, the working chamber 25 positioned in the space 25 c communicates with the discharge hole 28.
- FIG. 4 shows the relationship between the opening / closing timing of the electromagnetic valve 40 in the present embodiment and the flow rate of the working fluid entering the working chamber 25 during the suction process.
- time Top the time from when the solenoid valve 40 is closed to open
- time Tel the time from when the solenoid valve 40 is opened to closed
- the solenoid valve 40 is controlled to be opened immediately before the working chamber 25 communicates with the suction hole 27. If the solenoid valve 40 is kept closed at this time, the working chamber 25 is evacuated as it rotates, which causes a loss of braking the rotation of the rotor 23, which is not preferable. That is, the brake loss is minimized by a configuration having a control function in which the opening timing (that is, the time Top) at which the solenoid valve 40 is opened from the closed state is set to the suction start time at which the volume of the working chamber 25 is minimized. Can do.
- the working chamber 25 communicates with the suction hole 27 and the working fluid is sucked into the working chamber 25.
- the solenoid valve 40 is closed at the time Tel that the working chamber 25 reaches the maximum volume Vb that can be sucked.
- the amount of working fluid drawn becomes V, which is smaller than Vb.
- the magnitude of Vb ′ can be varied by changing the timing of the closing time Tel of the solenoid valve 40.
- the expansion chamber has a control function in which the closing timing for opening the solenoid valve 40 from opening to closing (that is, at the time of time Tel) is the time from the suction start time until the volume of the working chamber 25 becomes maximum.
- the flow rate of the working fluid entering can be varied.
- the working chamber 25 performs a suction process in which the working fluid of the pressure Pb on the high pressure side is sucked from the suction hole 27 until the state force of the space 25a in FIG. 9 also closes the electromagnetic valve 40.
- the inhalation process corresponds to that of Fig. 10.
- the amount of inhalation at this time is Vb '.
- the working chamber 25 has a maximum volume at the position of the space 25c. At this time, the pressure in the working chamber 25 is P lower than the pressure Pc when the solenoid valve 40 is normally opened. . This process corresponds to HC in Fig. 10.
- the reed valve 30a is provided in the discharge hole 28, and the reed valve 30a closes the discharge hole 28 by the pressure difference between the pressure PcT of the discharge chamber 33 and the pressure Pc of the working chamber 25. Therefore, the working fluid can be prevented from flowing from the discharge chamber 33 into the working chamber 25. Thereafter, the volume of the working chamber 25 decreases with the rotation of the rotor 3, but since it remains closed by the discharge hole 28 force S reed valve 30a, compression occurs in the space 25c, and the pressure is again in FIG. Ascend C'B '.
- the reed valve 30a is opened for the first time at the moment when the pressure in the working chamber 25 exceeds Pc, that is, at H in FIG. 10 when the pressure in the working chamber 25 reaches a predetermined value. This process corresponding to H is called the recompression process. Since the discharge valve is the reed valve 30a, there is an advantage that when the pressure in the working chamber 25 reaches a predetermined value, it automatically opens and recompression is performed.
- the working chamber 25 reduces the volume while discharging the working fluid having the low-pressure side pressure Pc from the discharge hole 28, that is, a discharge process.
- the force that eliminates the communication with the discharge hole 28 while the working chamber 25 moves from the space 25d to the position of the space 25e causes a part of the discharge hole 29 to rotate from the base point of the small gap 22 to the rotation direction of the shaft 26.
- the shape includes the position moved in the circumferential direction by (360 Zn) deg, which is the pitch of the vanes 24 from the discharge holes 28. Continue from hole 29.
- This discharge process corresponds to HD in Fig. 10.
- time-telling change control for closing the solenoid valve 40 will be described.
- the discharge pressure of the working fluid discharged from the compressor is measured by, for example, a pressure sensor, and the target discharge efficiency and the efficiency of the entire system including the compressor and expander are the best.
- the time width from time Top to time Tc is controlled by comparing the pressure with the discharge pressure of the compressor and the target pressure. In other words, when the discharge pressure of the compressor is higher than the target pressure, the flow rate of the working fluid is increased by increasing the time width of the difference between the time Top and the time Tel. In addition, when the discharge pressure of the compressor is smaller than the target pressure, the time width of the time Top and the time Tel is reduced to reduce the flow rate of the working fluid. As a result, the efficiency of the entire system can be maximized.
- the operating efficiency of the heat pump device is always high. Can be.
- the target pressure is a value that can determine the physical property value of the working fluid.
- changing the intake valve opening / closing timing that is, controlling the time width, for example, detects the rotation speed of the expander and the rotation angle from the base point, and based on this rotation speed and rotation angle!
- This can be done with a configuration (not shown) that opens and closes the solenoid valve 40 by setting the inhalation start time (time point) and time span.
- the solenoid valve 40 is installed in the sealed container 10 at a position close to the working chamber 25 of the suction hole 27 and the time width (Tel Top) during which the solenoid valve 40 is open is controlled.
- the discharge chamber 33 can be used in the case of overexpansion that can occur when the electromagnetic valve 40 is controlled.
- the working fluid is prevented from flowing back into the working chamber 25 and can be recompressed to the discharge pressure Pc, so there is no overexpansion loss (corresponding to the area of CC'H in Fig. 10)!
- a machine-integrated compressor can be provided.
- valve mechanism 30 described in the third embodiment is applied to the discharge hole 78 in the second embodiment. I'll do it for you.
- the compressor according to the present invention and the heat pump device using the compressor control the expansion chamber volume of the expander into which the working fluid is sucked by opening and closing a suction valve installed in the suction hole immediately before the inlet of the expansion chamber, Since high-pressure working fluid force also recovers power to the maximum, high operation efficiency can be obtained at all times, and it can be applied to an expander-integrated compressor, a heat pump device using the compressor, an air conditioner, and the like.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004339833A JP2008031845A (ja) | 2004-11-25 | 2004-11-25 | 圧縮機およびそれを用いたヒートポンプ装置 |
JP2004-339833 | 2004-11-25 | ||
JP2004371854A JP2008032234A (ja) | 2004-12-22 | 2004-12-22 | 圧縮機およびそれを用いたヒートポンプ装置 |
JP2004-371854 | 2004-12-22 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006057212A1 true WO2006057212A1 (ja) | 2006-06-01 |
Family
ID=36497949
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/021349 WO2006057212A1 (ja) | 2004-11-25 | 2005-11-21 | 流体機械およびそれを用いたヒートポンプ装置 |
Country Status (1)
Country | Link |
---|---|
WO (1) | WO2006057212A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008128576A (ja) * | 2006-11-22 | 2008-06-05 | Hitachi Appliances Inc | 冷凍サイクル装置 |
JP2009085189A (ja) * | 2007-10-03 | 2009-04-23 | Panasonic Corp | 容積型膨張機、膨張機一体型圧縮機、および冷凍サイクル装置 |
CN112253257A (zh) * | 2020-11-12 | 2021-01-22 | 意朗实业(上海)有限公司 | 一种膨胀机***以及发电*** |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000241033A (ja) * | 1999-02-23 | 2000-09-08 | Aisin Seiki Co Ltd | 蒸気圧縮式冷凍装置 |
JP2001165513A (ja) * | 1999-12-03 | 2001-06-22 | Aisin Seiki Co Ltd | 冷凍空調機 |
WO2003089766A1 (fr) * | 2002-04-19 | 2003-10-30 | Matsushita Electric Industrial Co., Ltd. | Moteur a expansion rotatif a ailettes |
JP2004190559A (ja) * | 2002-12-11 | 2004-07-08 | Daikin Ind Ltd | 容積型膨張機及び流体機械 |
JP2004257303A (ja) * | 2003-02-26 | 2004-09-16 | Mitsubishi Electric Corp | スクロール膨張機及び冷凍空調装置 |
-
2005
- 2005-11-21 WO PCT/JP2005/021349 patent/WO2006057212A1/ja not_active Application Discontinuation
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000241033A (ja) * | 1999-02-23 | 2000-09-08 | Aisin Seiki Co Ltd | 蒸気圧縮式冷凍装置 |
JP2001165513A (ja) * | 1999-12-03 | 2001-06-22 | Aisin Seiki Co Ltd | 冷凍空調機 |
WO2003089766A1 (fr) * | 2002-04-19 | 2003-10-30 | Matsushita Electric Industrial Co., Ltd. | Moteur a expansion rotatif a ailettes |
JP2004190559A (ja) * | 2002-12-11 | 2004-07-08 | Daikin Ind Ltd | 容積型膨張機及び流体機械 |
JP2004257303A (ja) * | 2003-02-26 | 2004-09-16 | Mitsubishi Electric Corp | スクロール膨張機及び冷凍空調装置 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008128576A (ja) * | 2006-11-22 | 2008-06-05 | Hitachi Appliances Inc | 冷凍サイクル装置 |
JP2009085189A (ja) * | 2007-10-03 | 2009-04-23 | Panasonic Corp | 容積型膨張機、膨張機一体型圧縮機、および冷凍サイクル装置 |
CN112253257A (zh) * | 2020-11-12 | 2021-01-22 | 意朗实业(上海)有限公司 | 一种膨胀机***以及发电*** |
CN112253257B (zh) * | 2020-11-12 | 2024-06-07 | 意朗实业(上海)有限公司 | 一种膨胀机***以及发电*** |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2295720B1 (en) | Two-stage rotary expander, expander-integrated compressor, and refrigeration cycle device | |
US7585163B2 (en) | Compression system, multicylinder rotary compressor, and refrigeration apparatus using the same | |
KR100747496B1 (ko) | 로터리 압축기 및 그 제어방법 그리고 이를 이용한공기조화기 | |
AU2007241901A1 (en) | Refrigerating apparatus | |
US10309700B2 (en) | High pressure compressor and refrigerating machine having a high pressure compressor | |
JP4866887B2 (ja) | スクロール圧縮機 | |
AU2007241900A1 (en) | Refrigerating apparatus | |
US8979509B2 (en) | Screw compressor having reverse rotation protection | |
JP2001323881A (ja) | 圧縮機 | |
JP4719432B2 (ja) | 空気調和機及びそれに用いられるロータリ式2段圧縮機 | |
WO2006057212A1 (ja) | 流体機械およびそれを用いたヒートポンプ装置 | |
WO2012042894A1 (ja) | 容積型圧縮機 | |
JP2006177225A (ja) | ロータリ圧縮機 | |
JP2008106668A (ja) | 膨張機、膨張機一体型圧縮機、およびそれを用いた冷凍サイクル装置 | |
JP6169261B2 (ja) | ロータリ式圧縮機、およびこれを搭載したヒートポンプ装置 | |
JP2007017040A (ja) | 膨張機およびその膨張機を用いた冷凍サイクル装置 | |
JP2008032234A (ja) | 圧縮機およびそれを用いたヒートポンプ装置 | |
KR101002555B1 (ko) | 다단 로터리 압축기 및 이를 적용한 냉동사이클 장치 | |
KR20210015098A (ko) | 압축기와 팽창기를 동시에 제어하는 인버터를 구비한 냉동사이클 시스템 | |
CN100455806C (zh) | 螺旋压缩机 | |
KR100585808B1 (ko) | 다단 로터리 압축기 | |
KR20070014914A (ko) | 로터리 압축기 | |
JP2009013798A (ja) | 膨張機一体型圧縮機 | |
JP2008031845A (ja) | 圧縮機およびそれを用いたヒートポンプ装置 | |
JP2004293450A (ja) | 冷媒サイクル装置 |
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 JP KE KG KM KN KP KR KZ LC LK LR LS LT LU LV LY 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): 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 | ||
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 05809674 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: JP |
|
WWW | Wipo information: withdrawn in national office |
Country of ref document: JP |