WO2009142014A1 - 流体機械および冷凍サイクル装置 - Google Patents
流体機械および冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2009142014A1 WO2009142014A1 PCT/JP2009/002231 JP2009002231W WO2009142014A1 WO 2009142014 A1 WO2009142014 A1 WO 2009142014A1 JP 2009002231 W JP2009002231 W JP 2009002231W WO 2009142014 A1 WO2009142014 A1 WO 2009142014A1
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- WIPO (PCT)
- Prior art keywords
- suction
- working chamber
- piston
- closing member
- compressor
- Prior art date
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- 239000012530 fluid Substances 0.000 title claims abstract description 83
- 238000005057 refrigeration Methods 0.000 title claims description 31
- 238000011084 recovery Methods 0.000 claims abstract description 91
- 239000003507 refrigerant Substances 0.000 claims description 109
- 238000005192 partition Methods 0.000 claims description 31
- 230000002093 peripheral effect Effects 0.000 claims description 27
- 230000000903 blocking effect Effects 0.000 claims 2
- 238000001816 cooling Methods 0.000 claims 1
- 238000001704 evaporation Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 description 16
- 238000006073 displacement reaction Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 10
- 230000006835 compression Effects 0.000 description 9
- 238000007906 compression Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 9
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 8
- 230000004913 activation Effects 0.000 description 6
- 238000007599 discharging Methods 0.000 description 5
- 229910002092 carbon dioxide Inorganic materials 0.000 description 4
- 239000001569 carbon dioxide Substances 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 239000010721 machine oil Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
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- 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
- F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
-
- 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
- F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
- F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
-
- 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
- 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
- F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01C13/04—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby for driving pumps or compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/14—Power generation using energy from the expansion of the refrigerant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
Definitions
- the present invention relates to a fluid machine and a refrigeration cycle apparatus.
- the refrigerant circuit of the refrigeration cycle apparatus has a configuration in which a compressor, a radiator, an expansion valve, and an evaporator are sequentially connected.
- the refrigerant changes while expanding from a high pressure to a low pressure in the expansion valve, and releases internal energy at that time.
- the greater the pressure difference between the low pressure side (evaporator side) and the high pressure side (heatsink side) of the refrigerant circuit the greater the internal energy that is released, so the energy efficiency of the refrigeration cycle decreases.
- various techniques for recovering the internal energy of the refrigerant have been proposed.
- FIG. 8 is a configuration diagram of a conventional refrigeration cycle apparatus 501 disclosed in Japanese Patent Application Laid-Open No. 2004-324595 and International Publication No. 2008/050654.
- the refrigeration cycle apparatus 501 includes a refrigerant circuit in which a radiator 502, a power recovery unit 503 (expander), an evaporator 504, a positive displacement blower 505 (sub compressor), and a main compressor 506 are connected in order.
- the fluid machine 507 includes a power recovery means 503, a positive displacement blower 505, a shaft 508, and a sealed container 509 that accommodates them.
- the power recovery means 503 and the positive displacement blower 505 are connected to each other by a shaft 508 so that the power recovered by the power recovery means 503 is transmitted to the positive displacement blower 505. Part of the internal energy released from the refrigerant by the power recovery means 503 is converted into the torque of the shaft 508 and transmitted to the positive displacement blower 505, and is used as power for driving the positive displacement blower 505.
- the positive displacement blower 505 preliminarily boosts the refrigerant before being sucked into the main compressor 506.
- JP 2004-324595 A describes the activation (independent activation) of the fluid machine 507 as follows.
- the main compressor 506 When the main compressor 506 is started, first, negative pressure is generated in the discharge pipe of the positive displacement blower 505. Then, a torque for rotating the shaft 508 is generated. Next, a positive force is generated in the suction pipe of the power recovery means 503, whereby the power recovery means 503 rotates.
- the fluid machine 507 receives the starting force only from the negative pressure in the discharge pipe of the positive displacement blower 505 or the positive pressure in the suction pipe of the power recovery means 503. Therefore, there is a possibility that sufficient starting force cannot be secured.
- FIG. 9 is a cross-sectional view of the power recovery means in the fluid machine disclosed in International Publication No. 2008/050654.
- the power recovery means 503 includes a cylinder 510, a piston 513, and a vane 511.
- the refrigerant flows into the working chamber 515 through the suction pipe 514 and flows out of the power recovery means 503 through the discharge pipe 516 as the shaft 508 rotates.
- the power recovery means 503 when the piston 513 is stopped by overlapping with the suction port 517, the positive pressure generated in the suction pipe 514 is directed toward the end plate (the member closing the cylinder 510) at the next activation.
- the piston 513 is pushed. That is, the friction between the piston 513 and the end plate at the time of activation is relatively large. Therefore, extra torque is required to rotate the piston 513. This is not preferable for smooth activation of the fluid machine 507.
- the present invention has been made in view of the above problems, and an object of the present invention is to provide a fluid machine suitable for performing smooth start-up. Furthermore, the present invention provides a refrigeration cycle apparatus using the fluid machine.
- the present invention A power recovery mechanism for recovering power from the working fluid; A sub compressor driven by the recovered power; A shaft connecting the power recovery mechanism and the sub-compressor so that the recovered power is transmitted from the power recovery mechanism to the sub-compressor,
- the power recovery mechanism is (A1) a first closing member; (B1) a second closing member facing the first closing member; (C1) a cylinder that surrounds a part of the shaft in the circumferential direction and is closed at both ends by the first closing member and the second closing member; (D1) a piston that is attached to the shaft in the cylinder and forms a working chamber between an outer peripheral surface of the cylinder and an inner peripheral surface of the cylinder; (E1) a partition member that divides the working chamber into a high pressure side working chamber and a low pressure side working chamber; (F1) a first suction port provided in the first closing member so that the working fluid flows into the working chamber on the high pressure side by opening and closing with the rotation of the piston; (G1) The second closing member at a position facing the first su
- the power recovery mechanism includes the first suction port and the second suction port provided at a position facing the first suction port. Therefore, the positive pressure generated in the suction pipe acts on both the upper surface and the lower surface of the piston through the first and second suction ports. That is, the force that pushes the piston toward the closing member is canceled out. Therefore, according to the present invention, a fluid machine suitable for smooth start-up can be provided. In some cases, the assistance of an auxiliary drive device such as an electric motor is also unnecessary.
- FIG. 1 is a longitudinal sectional view of the fluid machine shown in FIG. Longitudinal section of the fluid machine at a cutting angle different from that of FIG. 2A
- FIG. 2 is a cross-sectional view taken along line D1-D1 of the fluid machine shown in FIG.
- Operation principle diagram of power recovery mechanism is a cross-sectional view taken along line D2-D2 of the fluid machine shown in FIG.
- a fluid pressure motor that is normally used only for an incompressible working fluid is used as a power recovery mechanism and sub-compressor of a refrigeration cycle apparatus that uses a compressible refrigerant as a working fluid. is doing. Thereby, the energy efficiency of the operation of the refrigeration cycle apparatus is improved.
- the “fluid pressure motor” refers to a rotating working fluid that is rotated by a pressure difference between the pressure of the working fluid (typically refrigerant) on the suction side and the pressure of the working fluid on the discharge side.
- the pressure of the working fluid on the suction side means the pressure of the working fluid to be sucked into the fluid pressure motor.
- the pressure of the working fluid on the discharge side means the pressure of the working fluid discharged from the fluid pressure motor.
- the fluid pressure motor refers to a motor that does not change the volume of the working fluid until the start of the discharge stroke.
- the inside of the fluid pressure motor is depressurized or pressurized, and the working fluid is expanded or compressed.
- the technique disclosed in this specification is particularly effective for a refrigeration cycle apparatus that uses a refrigerant that is in a supercritical state on the high-pressure side, such as carbon dioxide.
- a refrigerant that is in a supercritical state on the high pressure side such as carbon dioxide.
- the expansion coefficient of the refrigerant represented by the ratio of the refrigerant density at the outlet of the radiator and the refrigerant density at the inlet of the evaporator is very small.
- the energy released by this type of refrigerant during expansion is mostly internal energy released based on a pressure drop.
- the internal energy released based on the increase in specific volume is small, which in some cases is less than the overexpansion loss.
- the fluid pressure motor used as the power recovery mechanism and the sub-compressor performs the suction stroke for sucking the refrigerant and the discharge stroke for discharging the sucked refrigerant substantially continuously. is there. Specifically, there is substantially no period in which the suction port and the discharge port are closed at the same time, that is, at least one of the suction port and the discharge port is substantially opened over the entire period.
- the phrase “there is no substantial period during which the suction port and the discharge port are simultaneously closed” includes that the suction port and the discharge port are instantaneously closed at the same time as long as the torque fluctuation of the fluid pressure motor does not occur. It is a concept.
- the refrigerant circuit is configured so that at least a part of the refrigerant discharged from the power recovery mechanism is in a gas phase as described below.
- a part of the refrigerant becomes a gas phase and obtains compressibility, the water hammer force caused by fluctuations in the discharge flow velocity caused by intermittent refrigerant discharge is reduced.
- the power recovery mechanism can be started smoothly and vibration and noise can be reduced.
- the refrigeration cycle apparatus 101 includes a refrigerant circuit 109 having a main compressor 103, a radiator 104, a power recovery mechanism 105, an evaporator 106, and a sub compressor 102. .
- the refrigerant circuit 109 is filled with a refrigerant such as carbon dioxide or hydrofluorocarbon as a working fluid.
- a refrigerant that becomes a supercritical state on the high-pressure side of the refrigeration cycle such as carbon dioxide
- the present invention exhibits a particularly excellent effect.
- the main compressor 103 includes a compression mechanism 103a (compressor body), an electric motor 108 connected to the compression mechanism 103a, and a sealed container 160 that houses the compression mechanism 103a and the electric motor 108.
- the compression mechanism 103 a is driven by the electric motor 108.
- the compression mechanism 103a compresses the refrigerant circulating in the refrigerant circuit 109 to high temperature and high pressure.
- a positive displacement compressor such as a scroll compressor or a rotary compressor can be used as the main compressor 103.
- the heat radiator 104 is connected to the main compressor 103.
- the radiator 104 radiates the refrigerant compressed by the main compressor 103. In other words, the radiator 104 cools the refrigerant.
- the refrigerant cooled by the radiator 104 becomes a medium temperature and high pressure.
- the power recovery mechanism 105 is connected to the radiator 104.
- the power recovery mechanism 105 is configured by a fluid pressure motor. Specifically, the power recovery mechanism 105 performs a process of sucking the refrigerant from the radiator 104 and a process of discharging the sucked refrigerant substantially continuously. That is, the power recovery mechanism 105 sucks the refrigerant that has been changed to a medium temperature and high pressure by the radiator 104 and discharges it to the evaporator 106 side without substantially changing the volume.
- the radiator 104 side has a relatively high pressure across the power recovery mechanism 105
- the evaporator 106 side has a relatively low pressure. For this reason, the refrigerant sucked into the power recovery mechanism 105 expands to a low pressure when discharged from the power recovery mechanism 105.
- the evaporator 106 is connected to the power recovery mechanism 105.
- the evaporator 106 heats and evaporates the refrigerant from the power recovery mechanism 105.
- the sub compressor 102 is disposed between the evaporator 106 and the main compressor 103 in the refrigerant circuit 109.
- the sub compressor 102 is connected to the power recovery mechanism 105 by the shaft 12.
- the sub compressor 102 is driven by the power recovered by the power recovery mechanism 105. Similar to the power recovery mechanism 105, the sub compressor 102 is configured by a fluid pressure motor.
- the sub-compressor 102 performs the process of sucking the refrigerant from the evaporator 106 and the process of discharging the sucked refrigerant to the main compressor 103 side substantially continuously.
- the sub compressor 102 sucks the refrigerant from the evaporator 106 and discharges it to the main compressor 103 side without substantially changing the volume.
- the refrigerant from the evaporator 106 is preliminarily compressed by being discharged from the sub compressor 102.
- the preliminarily compressed refrigerant is further compressed by the main compressor 103 and becomes high temperature and high pressure
- the refrigeration cycle apparatus 101 also includes a bypass circuit 107a.
- the bypass circuit 107 a bypasses the sub compressor 102 and connects the outlet of the evaporator 106 and the inlet of the main compressor 103.
- a bypass valve 107b is provided in the bypass circuit 107a. During normal operation, the bypass valve 107b is closed so that a supercharging effect (preliminary compression effect) by the sub compressor 102 can be obtained.
- the bypass valve 107b is opened.
- a relatively large pressure difference can be generated between the inlet and the outlet of the power recovery mechanism 105. As a result, it becomes easy to start the refrigeration cycle apparatus 101 smoothly.
- the power recovery mechanism 105 (first fluid mechanism) and the sub-compressor 102 (second fluid mechanism) constitute one fluid machine 110.
- the fluid machine 110 has a sealed container 111 filled with refrigerating machine oil.
- the power recovery mechanism 105 and the sub compressor 102 are disposed in the sealed container 111. Thereby, the refrigeration cycle apparatus 101 is made compact.
- the fluid machine 110 is provided with a balance weight 152. Specifically, a balance weight 152 is attached to each end of the shaft 12. The balance weight 152 plays a role of reducing the weight variation around the central axis of the shaft 12.
- One end of an oil equalizing pipe 163 is connected to the sealed container 111. The other end of the oil equalizing pipe 163 is connected to the sealed container 160 of the main compressor 103.
- the fluid machine 110 does not have an electric motor.
- the power recovery mechanism 105 is disposed in the lower part of the sealed container 111.
- the power recovery mechanism 105 is constituted by a rotary fluid pressure motor.
- the power recovery mechanism 105 is not limited to a rotary fluid pressure motor.
- the power recovery mechanism 105 may be configured by an expander having a specific volume ratio, for example, a rotary expander or a scroll expander.
- the power recovery mechanism 105 includes a first closing member 115 and a second closing member 113.
- the first closing member 115 and the second closing member 113 are opposed to each other.
- a first cylinder 22 is arranged between the first closing member 115 and the second closing member 113.
- the first cylinder 22 has a substantially cylindrical internal space. The internal space of the first cylinder 22 is closed by the first closing member 115 and the second closing member 113.
- the first closing member 115 and the second closing member 113 are respectively positioned above and below the first cylinder 22.
- the shaft 12 passes through the first cylinder 22 in the axial direction of the first cylinder 22.
- the first cylinder 22 surrounds a part of the shaft 12 in the circumferential direction.
- the shaft 12 is disposed on the central axis of the first cylinder 22.
- the shaft 12 is supported by a second closing member 113 and a third closing member 114 described later.
- the shaft 12 is formed with an oil supply hole 12a penetrating the shaft 12 in the axial direction.
- the refrigerating machine oil in the sealed container 111 is supplied to the bearings and gaps of the sub compressor 102 and the power recovery mechanism 105 through the oil supply hole 12a.
- the shaft 12 may be composed of a single part or a plurality of parts.
- the first piston 21 is disposed in a substantially cylindrical internal space formed by the inner peripheral surface of the first cylinder 22, the first closing member 115, and the second closing member 113.
- the first piston 21 is attached to the shaft 12 in an eccentric state with respect to the central axis of the shaft 12.
- the shaft 12 includes an eccentric portion 12 b having a central axis different from the central axis of the shaft 12.
- a cylindrical first piston 21 is fitted in the eccentric portion 12b. For this reason, the first piston 21 is eccentric with respect to the central axis of the first cylinder 22. Therefore, the first piston 21 rotates eccentrically with the rotation of the shaft 12.
- a first working chamber 23 is formed in the first cylinder 22 by the outer peripheral surface of the first piston 21, the inner peripheral surface of the first cylinder 22, the first closing member 115, and the second closing member 113 (FIG. 4). See also).
- the volume of the first working chamber 23 is substantially unchanged even when the first piston 21 rotates with the shaft 12.
- the first cylinder 22 is formed with a linear groove 22 a that opens into the first working chamber 23.
- a plate-like first partition member 24 is slidably inserted into the linear groove 22a.
- a biasing means 25 is disposed between the first partition member 24 and the bottom of the linear groove 22a. The first partition member 24 is pressed toward the outer peripheral surface of the first piston 21 by the biasing means 25.
- the first working chamber 23 is partitioned into two spaces. Specifically, the first working chamber 23 is divided into a high-pressure side suction working chamber 23a and a low-pressure side discharge working chamber 23b.
- the urging means 25 can be constituted by a spring, for example.
- the biasing means 25 may be a compression coil spring.
- the biasing means 25 may be a so-called gas spring or the like. That is, when the first partition member 24 slides in the direction of reducing the volume of the back space of the first partition member 24, the pressure in the back space becomes higher than the pressure of the first working chamber 23, The first partition member 24 may be pushed toward the first piston 21 by the pressure difference.
- the back space of the first partition member 24 may be a sealed space, and a reaction force may be applied to the first partition member 24 when the volume of the back space decreases due to the retraction of the first partition member 24.
- the biasing means 25 may be constituted by a plurality of types of springs such as a compression coil spring and a gas spring.
- the pressure in the first working chamber 23 is the average pressure of the pressure in the suction working chamber 23a and the pressure in the discharge working chamber 23b.
- the back space refers to a space formed between the rear end of the first partition member 24 and the bottom of the linear groove 22a.
- the first closing member 115 is provided with a first suction port 26 so that the refrigerant flows into the suction working chamber 23a by opening and closing as the first piston 21 rotates.
- the second closing member 113 is opened and closed with the rotation of the first piston 21 so that the refrigerant flows into the suction working chamber 23a at a position facing the first suction port 26 in the axial direction of the shaft 12.
- a second suction port 27 is provided. That is, the power recovery mechanism 105 includes two suction ports 26 and 27. Even if the first piston 21 overlaps with the suction ports 26 and 27 and stops, positive pressure acts on both the upper surface and the lower surface of the first piston 21 at the next start-up.
- the power recovery mechanism 105 supplies refrigerant from the outside of the power recovery mechanism 105 (heat radiator 104) to the suction working chamber 23a through the first suction port 26 and the second suction port 27, respectively.
- the suction path 53 includes a common suction path 40, a first suction path 51, and a second suction path 52.
- the first suction port 26 is located at the end of the first suction path 51
- the second suction port 27 is located at the end of the second suction path 52.
- the power recovery mechanism 105 includes a suction pipe 28 that guides the refrigerant from the outside of the sealed container 111 to the suction path 53.
- the common suction path 40 is formed in the second closing member 113 and is a thick path extending from the outer peripheral surface of the second closing member 113 toward the center of the shaft 12.
- the suction pipe 28 is directly connected to the common suction path 40.
- the first suction path 51 branches from the common suction path 40 and penetrates the first cylinder 22 in the axial direction so that the refrigerant can be supplied from the common suction path 40 to the suction working chamber 23a through the first suction port 26.
- the second suction path 52 has a common suction on the inner side of the first suction path 51 in the radial direction of the shaft 12 so that the refrigerant can be supplied from the common suction path 40 to the suction working chamber 23a through the second suction port 27. It branches from the path 40 and extends in the axial direction to the second suction port 27. According to such a structure, the two suction ports 26 and 27 can be provided without increasing the number of suction pipes 28.
- the first suction path 51 includes a portion formed in the second closing member 113, a portion formed in the first cylinder 22, and a portion formed in the first closing member 115. With respect to the axial direction, the first suction path 51 extends from the lower side to the upper side of the working chamber 23. That is, the first suction path 51 has a hook-shaped cross-sectional profile.
- the structure which provides the common suction path 40 in the 1st cylinder 22 is also considered.
- the thickness of the first cylinder 22 is thin, so that the common suction path 40 cannot be provided in the first cylinder 22.
- the configuration of the present embodiment is effective. This also applies to the discharge path described later.
- the first closing member 115 opens and closes with the rotation of the first piston 21 so that the refrigerant flows out of the discharge working chamber 23b.
- Outlet Similarly, the second closing member 113 is opened and closed in a position facing the first discharge port 29 in the axial direction so that the refrigerant flows out of the discharge working chamber 23b by opening and closing with the rotation of the first piston 21.
- An outlet 30 (second outlet) is provided. That is, the power recovery mechanism 105 includes two discharge ports 29 and 30. Even if the first piston 21 overlaps the discharge ports 29 and 30 and stops, negative pressure acts on both the upper surface and the lower surface of the first piston 21 at the next start-up.
- the first piston 21 it is possible to avoid the first piston 21 from being strongly attracted toward the closing member 115 or 113, so that the refrigeration cycle apparatus 101 can be started smoothly. Further, even during normal operation, the pressure of the refrigerant acts on both the upper surface and the lower surface of the first piston 21. Therefore, the sliding loss between the first piston 21 and the closing member 115 or 113 is reduced, and the efficiency of the power recovery mechanism 105 is improved.
- the power recovery mechanism 105 guides the refrigerant from the discharge working chamber 23b to the outside of the power recovery mechanism 105 (evaporator 106) through the first discharge port 29 and the second discharge port 30, respectively.
- the discharge path 58 is included.
- the discharge path 58 includes a common discharge path 55, a first discharge path 56, and a second discharge path 57.
- the first discharge port 29 is positioned at the start end of the first discharge path 56
- the second discharge port 30 is positioned at the start end of the second discharge path 57.
- the power recovery mechanism 105 includes a discharge pipe 31 that guides the refrigerant from the discharge path 58 to the outside of the sealed container 111.
- the common discharge path 55 is a thick path formed in the second closing member 113 and extending from the outer peripheral surface of the second closing member 113 toward the center of the shaft 12.
- the discharge pipe 31 is directly connected to the common discharge path 55.
- the first discharge path 56 extends outward from the first discharge port 29 and extends the first cylinder 22 in the axial direction so as to guide the refrigerant from the discharge working chamber 23b through the first discharge port 29 to the common discharge path 55. It penetrates and merges into the common discharge path 55.
- the second discharge path 57 extends in the axial direction from the second discharge port 30 and is first in the radial direction of the shaft 12 so as to guide the refrigerant from the discharge working chamber 23 b through the second discharge port 30 to the common discharge path 55. It merges with the common discharge path 55 inside the discharge path 56. According to such a structure, the two discharge ports 29 and 30 can be provided without increasing the number of discharge pipes 31.
- the first discharge path 56 includes a portion formed in the first closing member 115, a portion formed in the first cylinder 22, and a portion formed in the second closing member 113. 23 wraps around from the upper side to the lower side. That is, the first discharge path 56 has a hook-shaped cross-sectional profile.
- the suction path 53 opens toward the suction working chamber 23a.
- the first suction path 51 and the second suction path 52 described with reference to FIG. 2A each open toward the suction working chamber 23a.
- the second suction port 27 is formed in a substantially fan shape extending in an arc shape in a direction in which the suction working chamber 23a extends from a portion adjacent to the first partition member 24 of the suction working chamber 23a.
- the second suction port 27 is completely closed by the first piston 21 only when the first piston 21 is located at the top dead center. Then, at least a part of the second suction port 27 is exposed to the suction working chamber 23a over the entire period except for the moment when the first piston 21 is located at the top dead center.
- the outer end side 27a of the second suction port 27 is formed in an arc shape along the outer peripheral surface of the first piston 21 located at the top dead center.
- the outer end side 27 a is formed in an arc shape having substantially the same radius as the outer peripheral surface of the first piston 21.
- the “outer end side” means an end side located on the outer side in the radial direction of the shaft 5.
- “Top dead center” means the position of the piston in a state where the vane is pushed all the way into the vane groove.
- the first suction port 26 has the same opening shape as that of the second suction port 27. Further, the first suction port 26 has an opening area equal to the opening area of the second suction port 27. According to such a configuration, the force acting on the lower surface can be effectively offset by the force acting on the upper surface of the first piston 21.
- the pressure loss in the first suction path 51 exceeds the pressure loss in the second suction path 52 when the sectional areas of both are equal. . For this reason, even if the first suction port 26 and the second suction port 27 are completely overlapped in the axial direction, the force acting on the upper surface of the first piston 21 due to the effect of the pressure loss is strictly speaking. , Not equal to the force acting on the lower surface.
- the first suction path 51 has a cross-sectional area larger than the cross-sectional area of the second suction path 52. According to this configuration, the pressure loss in the first suction path 51 can be suppressed, so that the force acting on the upper surface of the first piston 21 and the force acting on the lower surface are more effectively equalized. As a result, the effect of offsetting the force acting in the thickness direction of the first piston 21 is enhanced.
- each inhalation route has a circular cross section.
- the first suction port 26 and the second suction port 27 having the shape shown in FIG. 4 are formed by shallow spot facings provided at the ends of the first suction route 51 and the second suction route 52. Such a configuration can be used for the discharge path and the discharge port, and can also be used for the sub-compressor 102.
- the discharge path 58 opens toward the discharge working chamber 23b.
- the first discharge path 56 and the second discharge path 57 described with reference to FIG. 2B each open toward the discharge working chamber 23b.
- the second discharge port 30 is formed in a substantially fan shape extending in an arc shape in a direction in which the discharge working chamber 23b extends from a portion adjacent to the first partition member 24 of the discharge working chamber 23b.
- the second discharge port 30 is completely closed by the first piston 21 only when the first piston 21 is located at the top dead center.
- at least a part of the second discharge port 30 is exposed to the discharge working chamber 23b over the entire period except for the moment when the first piston 21 is located at the top dead center.
- the outer end side 30a of the second discharge port 30 is formed in an arc shape along the outer peripheral surface of the first piston 21 located at the top dead center.
- the outer end side 30 a is formed in an arc shape having substantially the same radius as the outer peripheral surface of the first piston 21.
- the first discharge port 29 has the same opening shape as the opening shape of the second discharge port 30. Further, the first discharge port 29 has an opening area equal to the opening area of the second discharge port 30. According to such a configuration, the force (suction force) acting on the lower surface can be effectively offset by the force (suction force) acting on the upper surface of the first piston 21.
- the first discharge path 56 may have a cross-sectional area larger than the cross-sectional area of the second discharge path 57. According to this configuration, since the pressure loss in the first discharge path 56 can be suppressed, there is an effect of making the force acting on the upper surface of the first piston 21 equal to the force acting on the lower surface.
- the effect of offsetting the force acting on the first piston 21 is obtained independently when the plurality of suction ports 26 and 27 are provided and when the plurality of discharge ports 29 and 30 are provided.
- the refrigerant pressure in the suction path 53 is much higher than the refrigerant pressure in the discharge path 58.
- carbon dioxide is used as the refrigerant
- the difference between the pressure in the suction path 53 and the pressure in the discharge path 58 reaches several MPa.
- the effect obtained by the combination of the suction ports 26 and 27 is higher than the effect obtained by the combination of the discharge ports 29 and 30.
- FIG. 5 is an operation principle diagram of the power recovery mechanism 105, and shows diagrams of four states from ST1 to ST4.
- the volume of the suction working chamber 23a is gradually increased by the high-pressure refrigerant flowing from the suction ports 26 and 27 as shown in FIG. 5 (ST2 to ST4). Increase.
- the rotational torque applied to the first piston 21 as the volume of the suction working chamber 23a increases becomes part of the rotational driving force of the shaft 12.
- the opening and closing timings of both the suction ports 26 and 27 also coincide.
- the opening / closing timings of both the discharge ports 29 and 30 also coincide.
- the evaporator 106 side When viewed from the power recovery mechanism 105, the evaporator 106 side has a lower pressure than the radiator 104 side.
- the low-temperature and high-pressure refrigerant in the discharge working chamber 23b is sucked to the evaporator 106 side and discharged from the discharge working chamber 23b to the discharge path 58.
- the specific volume of the refrigerant increases rapidly.
- the rotational torque applied to the first piston 21 by this refrigerant discharge stroke also becomes part of the rotational driving force of the shaft 12. That is, the shaft 12 is rotated by the flow of the high-pressure refrigerant into the suction working chamber 23a and the suction of the refrigerant in the discharge stroke.
- the rotational torque of the shaft 12 is used as power for the sub-compressor 102, as will be described in detail later.
- the suction working chamber 23a is always in communication with the suction path 53. Further, the discharge working chamber 23b is always in communication with the discharge path 58. In other words, in the power recovery mechanism 105, the process of sucking the refrigerant and the process of discharging the sucked refrigerant are performed substantially continuously. For this reason, the sucked refrigerant passes through the power recovery mechanism 105 without substantially changing its volume.
- both the suction port 27 and the discharge port 30 are completely closed only at the moment when the first piston 21 is located at the top dead center. That is, both the suction port 27 and the discharge port 30 are completely closed at the moment when the first working chamber 23 becomes one. More specifically, the suction working chamber 23 a communicates with the suction passage 53 until the moment when the suction working chamber 23 a communicates with the discharge passage 58. Then, after the moment when the suction working chamber 23 a communicates with the discharge path 58 and the suction working chamber 23 a becomes the discharge working chamber 23 b, the discharge working chamber 23 b is isolated from the suction path 53 by the first piston 21. For this reason, the blow-through of the refrigerant from the suction path 53 to the discharge path 58 is suppressed. Therefore, highly efficient power recovery is realized.
- both the suction port 27 and the discharge port 30 may be closed at the moment when the first piston 21 is located at the top dead center. preferable. However, even when only one of the suction port 27 and the discharge port 30 is closed at the moment when the first piston 21 is located at the top dead center, the timing at which the suction port 27 is closed and the discharge port 30 If the difference from the timing at which the valve is closed is smaller than about 10 ° in terms of the rotation angle of the shaft 12, no blow-through occurs substantially between the suction path 53 and the discharge path 58.
- the difference between the timing at which the suction port 27 is closed and the timing at which the discharge port 30 is closed is set to be smaller than about 10 ° in terms of the rotation angle of the shaft 12, so that the suction path 53 to the discharge path 58. It is possible to suppress the blow-through of the refrigerant.
- the opening / closing timings of the suction ports 26 and 27 coincide and the opening / closing timings of the discharge ports 29 and 30 also coincide.
- the sub compressor 102 is disposed above the power recovery mechanism 105 in the sealed container 111.
- the relatively high temperature sub-compressor 102 above the relatively low temperature power recovery mechanism 105 in this manner, heat exchange between the sub compressor 102 and the power recovery mechanism 105 can be suppressed.
- the sub compressor 102 may be disposed below the power recovery mechanism 105.
- the sub-compressor 102 is connected to the power recovery mechanism 105 by the shaft 12.
- the sub compressor 102 is not limited to a rotary fluid pressure motor.
- the sub compressor 102 may be composed of a compressor having a specific volume ratio, for example, a rotary compressor or a scroll compressor.
- the basic configuration of the sub compressor 102 is substantially the same as the power recovery mechanism 105 described above.
- the sub-compressor 102 includes a first closing member 115 as a lower closing member and a third closing member 114 as an upper closing member.
- the power recovery mechanism 105 and the sub compressor 102 are disposed in the hermetic container 111 adjacent to each other in the axial direction so that the first closing member 115 of the power recovery mechanism 105 is shared as a lower closing member of the sub compressor 102. Yes. With such a configuration, the number of parts can be reduced, and the fluid machine 110 can be made compact.
- the first closing member 115 and the third closing member 114 are opposed to each other. Specifically, the third closing member 114 faces the surface of the first closing member 115 opposite to the surface facing the second closing member 113.
- a second cylinder 42 is disposed between the first closing member 115 and the third closing member 114.
- the second cylinder 42 has a substantially cylindrical internal space. The internal space of the second cylinder 42 is closed by the first closing member 115 and the third closing member 114.
- the third closing member 114 and the first closing member 115 are positioned above and below the second cylinder 42, respectively.
- the shaft 12 passes through the second cylinder 42 in the axial direction of the second cylinder 42.
- the second cylinder 42 surrounds a part of the shaft 12 in the circumferential direction.
- the shaft 12 is disposed on the central axis of the second cylinder 42.
- the second piston 41 is disposed in a substantially cylindrical internal space formed by the inner peripheral surface of the second cylinder 42, the first closing member 115, and the third closing member 114.
- the second piston 41 is attached to the shaft 12 in an eccentric state with respect to the central axis of the shaft 12.
- the shaft 12 includes an eccentric portion 12 c having a central axis different from the central axis of the shaft 12.
- a cylindrical second piston 41 is fitted in the eccentric portion 12c. For this reason, the second piston 41 is eccentric with respect to the central axis of the second cylinder 42. Therefore, the second piston 41 rotates eccentrically with the rotation of the shaft 12.
- the eccentric part 12c is eccentric in the same direction as the eccentric part 12b.
- the eccentric direction of the first piston 21 with respect to the central axis of the first cylinder 22 and the eccentric direction of the second piston 41 with respect to the central axis of the second cylinder 42 are substantially the same. “Substantially the same” means not only the case where they are completely the same, but also the case where there is an error of about ⁇ 2 to 3 °.
- a second working chamber 43 is formed in the second cylinder 42 by the outer peripheral surface of the second piston 41, the inner peripheral surface of the second cylinder 42, the first closing member 115, and the third closing member 114 (FIG. 6). See also).
- the volume of the second working chamber 43 is substantially unchanged even when the second piston 41 rotates with the shaft 12.
- the second cylinder 42 is formed with a linear groove 42 a that opens into the second working chamber 43.
- a plate-like second partition member 44 is slidably inserted into the linear groove 42a.
- a biasing means 45 is disposed between the second partition member 44 and the bottom of the linear groove 42a. By this urging means 45, the second partition member 44 is pressed toward the outer peripheral surface of the second piston 41.
- the second working chamber 43 is partitioned into two spaces. Specifically, the second working chamber 43 is partitioned into a low-pressure side suction working chamber 43a and a high-pressure side discharge working chamber 43b.
- the urging means 45 can be constituted by a spring, for example.
- the urging means 45 may be a compression coil spring or a so-called gas spring, like the urging means 25 described above.
- the first closing member 115 has a first discharge port 49 (lower discharge port) that opens and closes with the rotation of the second piston 41 so that the refrigerant flows out of the discharge working chamber 43b. Is provided.
- the second closing member 114 is opened and closed at a position facing the first discharge port 49 in the axial direction so that the refrigerant flows out of the discharge working chamber 43b by opening and closing with the rotation of the second piston 41.
- An outlet 50 (upper discharge port) is provided. That is, the sub-compressor 102 includes two discharge ports 49 and 50. Even when the second piston 41 is stopped by overlapping the discharge ports 49 and 50, negative pressure acts on both the upper surface and the lower surface of the second piston 41 at the next start-up.
- the second piston 41 it is possible to avoid the second piston 41 from being strongly attracted toward the closing member 115 or 114, so that the refrigeration cycle apparatus 101 can be started smoothly. Further, the pressure of the refrigerant acts on both the upper surface and the lower surface of the second piston 41 even during normal operation. Therefore, the sliding loss between the second piston 41 and the closing member 115 or 114 is reduced, and the efficiency of the sub compressor 102 is improved.
- the sub compressor 102 guides the refrigerant from the discharge working chamber 43b to the outside of the sub compressor 102 (main compressor 103) through each of the first discharge port 49 and the second discharge port 50.
- the discharge path 68 is included.
- the discharge path 68 includes a common discharge path 65, a first discharge path 66, and a second discharge path 67.
- the first discharge port 49 is positioned at the start end of the first discharge path 66
- the second discharge port 50 is positioned at the start end of the second discharge path 67.
- the sub-compressor 102 includes a discharge pipe 151 that guides the refrigerant from the discharge path 68 to the outside of the sealed container 111.
- the common discharge path 65 is a thick path formed in the third closing member 114 and extending from the outer peripheral surface of the third closing member 114 toward the center of the shaft 12.
- a discharge pipe 151 is directly connected to the common discharge path 65.
- the first discharge path 66 extends outward from the first discharge port 49 and extends the second cylinder 42 in the axial direction so as to guide the refrigerant from the discharge working chamber 43b through the first discharge port 49 to the common discharge path 65. It penetrates and merges into the common discharge path 65.
- the second discharge path 67 extends in the axial direction from the second discharge port 50 and is first in the radial direction of the shaft 12 so as to guide the refrigerant from the discharge working chamber 43b to the common discharge path 65 through the second discharge port 50. It merges with the common discharge path 65 inside the discharge path 66. According to such a structure, the two discharge ports 49 and 50 can be provided without increasing the number of discharge pipes 151.
- the first discharge path 66 includes a portion formed in the first closing member 115, a portion formed in the second cylinder 42, and a portion formed in the third closing member 114, and the working chamber 43 goes from the lower side to the upper side. That is, the first discharge path 66 has a hook-shaped cross-sectional profile.
- the first closing member 115 opens and closes with the rotation of the second piston 41 so that the refrigerant flows into the suction working chamber 43a. Mouth).
- the third closing member 114 is opened and closed with the rotation of the second piston 41 so that the refrigerant flows into the suction working chamber 43a at a position facing the first suction port 46 in the axial direction of the shaft 12.
- a second suction port 47 (upper suction port) is provided. That is, the sub-compressor 102 includes two suction ports 46 and 47. Even if the second piston 41 is stopped by overlapping with the suction ports 46 and 47, negative pressure acts on both the upper surface and the lower surface of the second piston 41 at the next start-up.
- the second piston 41 it is possible to avoid the second piston 41 from being strongly attracted toward the closing member 115 or 114, so that the refrigeration cycle apparatus 101 can be started smoothly. Further, the pressure of the refrigerant acts on both the upper surface and the lower surface of the second piston 41 even during normal operation. Therefore, the sliding loss between the second piston 41 and the closing member 115 or 114 is reduced, and the efficiency of the sub compressor 102 is improved.
- the sub compressor 102 supplies the refrigerant from the outside (evaporator 106) of the sub compressor 102 to the suction working chamber 43a through the first suction port 46 and the second suction port 47, respectively.
- the suction path 63 includes a common suction path 60, a first suction path 61, and a second suction path 62.
- the first suction port 46 is located at the end of the first suction path 61
- the second suction port 47 is located at the end of the second suction path 62.
- the sub-compressor 102 includes a suction pipe 48 that guides the refrigerant from the outside of the sealed container 111 to the suction path 63.
- the common suction path 60 is a thick path formed in the third closing member 114 and extending from the outer peripheral surface of the third closing member 114 toward the center of the shaft 12.
- a suction pipe 48 is directly connected to the common suction path 60.
- the first suction path 61 branches from the common suction path 60 and penetrates the second cylinder 42 in the axial direction so that the refrigerant can be supplied from the common suction path 60 through the first suction port 46 to the suction working chamber 43a.
- the second suction path 62 has a common suction inside the first suction path 61 in the radial direction of the shaft 12 so that the refrigerant can be supplied from the common suction path 60 to the suction working chamber 43a through the second suction port 47. It branches from the path 60 and extends in the axial direction to the second suction port 47. According to such a structure, the two suction ports 46 and 47 can be provided without increasing the number of suction pipes 48.
- the first suction path 61 includes a portion formed in the third closing member 114, a portion formed in the second cylinder 42, and a portion formed in the first closing member 115. With respect to the axial direction, the first suction path 61 extends from the upper side to the lower side of the working chamber 43. That is, the first suction path 61 has a hook-shaped cross-sectional profile.
- the suction path 63 opens toward the suction working chamber 43a.
- the first suction path 61 and the second suction path 62 described with reference to FIG. 2A each open toward the suction working chamber 43a.
- the first suction port 46 is formed in a substantially fan shape extending in an arc shape in a direction in which the suction working chamber 43a extends from a portion adjacent to the second partition member 44 of the suction working chamber 43a.
- the first suction port 46 is completely closed by the second piston 41 only when the second piston 41 is located at the top dead center. At least a part of the first suction port 46 is exposed to the suction working chamber 43a over the entire period except for the moment when the second piston 41 is located at the top dead center.
- the outer end side 46a of the first suction port 46 is formed in an arc shape along the outer peripheral surface of the second piston 41 located at the top dead center.
- the outer end side 46 a is formed in an arc shape having substantially the same radius as the outer peripheral surface of the second piston 41.
- the second suction port 47 has the same opening shape as that of the first suction port 46. Further, the first suction port 46 has an opening area equal to the opening area of the second suction port 47. According to such a configuration, the force acting on the lower surface can be effectively offset by the force acting on the upper surface of the second piston 41.
- the discharge path 68 opens toward the discharge working chamber 43b.
- the first discharge path 66 and the second discharge path 67 described with reference to FIG. 2B open toward the discharge working chamber 43b.
- the first discharge port 49 is formed in a substantially fan shape extending in a circular arc shape in a direction in which the discharge working chamber 43b extends from a portion adjacent to the second partition member 44 of the discharge working chamber 43b.
- the first discharge port 49 is completely closed by the second piston 41 only when the second piston 41 is located at the top dead center. Then, at least a part of the first discharge port 49 is exposed to the discharge working chamber 43b over the entire period except for the moment when the second piston 41 is located at the top dead center.
- the outer end side 49a of the first discharge port 49 is formed in an arc shape along the outer peripheral surface of the second piston 41 located at the top dead center in plan view. In other words, the outer end side 49 a is formed in an arc shape having substantially the same radius as the outer peripheral surface of the second piston 41.
- the second discharge port 50 has the same opening shape as that of the first discharge port 49. That is, the first discharge port 49 has an opening area equal to the opening area of the second discharge port 50. According to such a configuration, the force acting on the lower surface can be effectively offset by the force acting on the upper surface of the second piston 41.
- the discharge path 68 is connected to the back space 155 via the communication path 156.
- the communication path 156 communicates with the back space 155 when the second partition member 44 is closest to the central axis of the shaft 12.
- the communication path 156 is closed by the second partition member 44 when the second partition member 44 is separated from the central axis of the shaft 12 to some extent. That is, the communication path 156 is changed from the open state to the closed state during the period in which the second partition member 44 slides from the forward position closest to the central axis of the shaft 12 to the retracted position farthest from the central axis of the shaft 12.
- the back space 155 changes from an open space that communicates with the communication path 156 to a sealed space that is blocked from the communication path 156. For this reason, after the communication path 156 is blocked by the second partition member 44 and the back space 155 becomes a sealed space, the back space 155 pushes the second partition member 44 toward the second piston 41 as a gas spring. .
- the first suction path 61 may have a cross-sectional area larger than the cross-sectional area of the second suction path 62.
- the first discharge path 66 may have a cross-sectional area larger than the cross-sectional area of the second discharge path 67. According to such a configuration, pressure loss in the first suction path 61 and the first discharge path 66 can be suppressed, so that the force acting on the upper surface of the second piston 41 and the force acting on the lower surface are made more equal. effective.
- the effect of canceling out the force acting on the second piston 41 is obtained independently when the plurality of suction ports 46 and 47 are provided and when the plurality of discharge ports 49 and 50 are provided.
- the effect obtained by the combination of the discharge ports 49 and 50 is higher than the effect obtained by the combination of the suction ports 46 and 47.
- the reason is as follows. First, when the refrigeration cycle apparatus 101 is activated, the pressures in the suction path 63 and the discharge path 68 are temporarily equal. This is because the bypass valve 107b is opened at the time of activation (see FIG. 1). On the other hand, since the bypass valve 107 b is closed after the refrigeration cycle apparatus 101 is started, the pressure in the discharge path 68 becomes higher than the pressure in the suction path 63. Therefore, according to the combination of the discharge ports 49 and 50, the sliding loss during the normal operation of the refrigeration cycle apparatus 101 can be more effectively reduced.
- FIG. 7 shows a diagram of four states T1 to T4.
- the operation principle of the sub-compressor 102 is substantially the same as the operation principle of the power recovery mechanism 105.
- the shaft 12 is rotated by the power recovered by the power recovery mechanism 105. Along with the rotation of the shaft 12, the second piston 41 also rotates, and the sub compressor 102 is driven.
- the opening and closing timings of both the suction ports 46 and 47 also coincide.
- the first discharge port 49 overlaps the second discharge port 50 with respect to the axial direction
- the opening and closing timings of both the discharge ports 49 and 50 also coincide.
- the volume of the second working chamber 43 is substantially unchanged.
- the suction working chamber 43 a is always in communication with the suction path 63.
- the discharge working chamber 43b is always in communication with the discharge path 68.
- the refrigerant is neither compressed nor expanded in the second working chamber 43 of the sub compressor 102.
- the shaft 12 is rotated by the power recovery mechanism 105 and the sub compressor 102 is driven, the pressure on the downstream side of the second working chamber 43 is higher than that on the upstream side of the second working chamber 43.
- the sub compressor 102 driven by the power recovered by the power recovery mechanism 105 causes the pressure on the main compressor 103 side from the discharge ports 49 and 50 to be closer to the evaporator 106 side than the suction ports 46 and 47. Higher than pressure. That is, the pressure is increased by the sub compressor 102.
- the suction working chamber 43a is always in communication with the suction path 63. Further, the discharge working chamber 43b is always in communication with the discharge path 68. In other words, in the sub-compressor 102, the process of sucking the refrigerant and the process of discharging the sucked refrigerant are performed substantially continuously. For this reason, the sucked refrigerant passes through the sub-compressor 102 without substantially changing the volume.
- the timing at which the first piston 21 is located at the top dead center substantially matches the timing at which the second piston 41 is located at the top dead center.
- both the suction port 46 and the discharge port 49 are completely closed only at the moment when the second piston 41 is located at the top dead center. That is, at the moment when the second working chamber 43 becomes one, both the suction port 46 and the discharge port 49 are completely closed. More specifically, the suction working chamber 43 a communicates with the suction passage 63 until the moment when the suction working chamber 43 a communicates with the discharge port 49. Then, after the moment when the suction working chamber 43a communicates with the discharge path 68 and the suction working chamber 43a becomes the discharge working chamber 43b, the second piston 41 isolates the discharge working chamber 43b from the suction path 63.
- both the suction path 63 and the discharge path 68 are closed at the moment when the second piston 41 is located at the top dead center. It is preferable. However, even when only one of the suction port 46 and the discharge port 49 is closed at the moment when the second piston 41 is located at the top dead center, the timing at which the suction port 46 is closed and the discharge port 49 If the difference from the timing at which the is closed is smaller than about 10 ° in terms of the rotation angle of the shaft 12, the reverse flow of the refrigerant from the discharge path 68 to the suction path 63 does not substantially occur.
- the difference between the timing at which the suction port 46 is closed and the timing at which the discharge port 49 is closed is set to be smaller than about 10 ° in terms of the rotation angle of the shaft 12, so The reverse flow of the refrigerant can be suppressed.
- the opening / closing timings of the suction ports 46 and 47 coincide and the opening / closing timings of the discharge ports 49 and 50 also coincide.
- the present invention is useful for refrigeration cycle apparatuses such as water heaters and air conditioners.
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Abstract
Description
作動流体から動力を回収する動力回収機構と、
前記回収された動力で駆動される副圧縮機と、
前記回収された動力が前記動力回収機構から前記副圧縮機に伝達されるように、前記動力回収機構と前記副圧縮機とを連結しているシャフトと、を備え、
前記動力回収機構は、
(a1)第1閉塞部材と、
(b1)前記第1閉塞部材に対向する第2閉塞部材と、
(c1)前記シャフトの一部を周方向に囲んでいるとともに、前記第1閉塞部材と前記第2閉塞部材とにより両端が閉塞されたシリンダと、
(d1)前記シリンダ内において前記シャフトに取り付けられ、自身の外周面と前記シリンダの内周面との間に作動室を形成するピストンと、
(e1)前記作動室を高圧側の作動室と低圧側の作動室とに仕切る仕切部材と、
(f1)前記ピストンの回転に伴って開閉して前記高圧側の作動室に作動流体が流入するように、前記第1閉塞部材に設けられた第1吸入口と、
(g1)前記ピストンの回転に伴って開閉して前記高圧側の作動室に作動流体が流入するように、前記シャフトの軸方向に関して前記第1吸入口と向かい合う位置であって前記第2閉塞部材に設けられた第2吸入口と、を含む、流体機械を提供する。
動力回収機構105は、密閉容器111内の下部に配置されている。本実施形態では、動力回収機構105がロータリ式の流体圧モータによって構成されている例について説明する。ただし、動力回収機構105がロータリ式の流体圧モータに限定されるわけではない。動力回収機構105が固有の容積比を有する膨張機、例えば、ロータリ膨張機やスクロール膨張機で構成されていてもよい。
図2Aに示すように、副圧縮機102は、密閉容器111内において、動力回収機構105よりも上方に配置されている。このように比較的高温の副圧縮機102を、比較的低温の動力回収機構105よりも上方に配置することにより、副圧縮機102と動力回収機構105との間の熱交換を抑制できる。ただし、副圧縮機102を動力回収機構105よりも下方に配置してもよい。
Claims (12)
- 作動流体から動力を回収する動力回収機構と、
前記回収された動力で駆動される副圧縮機と、
前記回収された動力が前記動力回収機構から前記副圧縮機に伝達されるように、前記動力回収機構と前記副圧縮機とを連結しているシャフトと、を備え、
前記動力回収機構は、
(a1)第1閉塞部材と、
(b1)前記第1閉塞部材に対向する第2閉塞部材と、
(c1)前記シャフトの一部を周方向に囲んでいるとともに、前記第1閉塞部材と前記第2閉塞部材とにより両端が閉塞されたシリンダと、
(d1)前記シリンダ内において前記シャフトに取り付けられ、自身の外周面と前記シリンダの内周面との間に作動室を形成するピストンと、
(e1)前記作動室を高圧側の作動室と低圧側の作動室とに仕切る仕切部材と、
(f1)前記ピストンの回転に伴って開閉して前記高圧側の作動室に作動流体が流入するように、前記第1閉塞部材に設けられた第1吸入口と、
(g1)前記ピストンの回転に伴って開閉して前記高圧側の作動室に作動流体が流入するように、前記シャフトの軸方向に関して前記第1吸入口と向かい合う位置であって前記第2閉塞部材に設けられた第2吸入口と、を含む、流体機械。 - 前記動力回収機構が、さらに、
(h1)前記ピストンの回転に伴って開閉して前記低圧側の作動室から作動流体が流出するように、前記第1閉塞部材に設けられた第1吐出口と、
(i1)前記ピストンの回転に伴って開閉して前記低圧側の作動室から作動流体が流出するように、前記軸方向に関して前記第1吐出口と向かい合う位置であって前記第2閉塞部材に設けられた第2吐出口を含む、請求項1に記載の流体機械。 - 前記第1吐出口が、前記第2吐出口の開口形状と同じ開口形状を有する、請求項2に記載の流体機械。
- 前記第1吐出口が、前記第2吐出口の開口面積に等しい開口面積を有する、請求項2または3に記載の流体機械。
- 前記第1吸入口が、前記第2吸入口の開口形状と同じ開口形状を有する、請求項1~4のいずれか1項に記載の流体機械。
- 前記第1吸入口が、前記第2吸入口の開口面積に等しい開口面積を有する、請求項1~5のいずれか1項に記載の流体機械。
- 前記動力回収機構は、当該動力回収機構の外部から、前記第1吸入口および前記第2吸入口のそれぞれを経て、前記高圧側の作動室へと作動流体を供給するための吸入経路をさらに含み、
前記吸入経路が、(i)前記第2閉塞部材の外周面から前記シャフトの中心に向かって延びている共通吸入経路と、(ii)前記共通吸入経路から前記第1吸入口を経て前記高圧側の作動室へと作動流体を供給しうるように、前記共通吸入経路から分岐するとともに前記シリンダを前記軸方向に貫いて前記第1吸入口に至る第1吸入経路と、(iii)前記共通吸入経路から前記第2吸入口を経て前記高圧側の作動室へと作動流体を供給しうるように、前記シャフトの径方向に関して前記第1吸入経路よりも内側において前記共通吸入経路から分岐するとともに前記軸方向に延びて前記第2吸入口に至る第2吸入経路と、を含む、請求項1~6のいずれか1項に記載の流体機械。 - 前記第1吸入経路が、前記第2吸入経路の断面積よりも大きい断面積を有する、請求項7に記載の流体機械。
- 前記副圧縮機が、
(a2)前記下閉塞部材と、
(b2)前記下閉塞部材に対向する上閉塞部材と、
(c2)前記シャフトの一部を周方向に囲んでいるとともに、前記下閉塞部材と前記上閉塞部材とにより両端が閉塞された第2シリンダと、
(d2)前記第2シリンダ内において前記シャフトに取り付けられ、自身の外周面と前記第2シリンダの内周面との間に作動室を形成する第2ピストンと、
(e2)前記作動室を低圧側の作動室と高圧側の作動室とに仕切る第2仕切部材と、
(f2)前記第2ピストンの回転に伴って開閉して前記低圧側の作動室に作動流体が流入するように、前記下閉塞部材に設けられた第1吸入口と、
(g2)前記第2ピストンの回転に伴って開閉して前記低圧側の作動室に作動流体が流入するように、前記シャフトの軸方向に関して前記第1吸入口と向かい合う位置であって前記上閉塞部材に設けられた第2吸入口とを含む、請求項1~8のいずれか1項に記載の流体機械。 - 前記副圧縮機が、さらに、
(h2)前記第2ピストンの回転に伴って開閉して前記高圧側の作動室から作動流体が流出するように、前記下閉塞部材に設けられた第1吐出口と、
(i2)前記第2ピストンの回転に伴って開閉して前記高圧側の作動室から作動流体が流出するように、前記軸方向に関して前記第1吐出口と向かい合う位置であって前記上閉塞部材に設けられた第2吐出口を含む、請求項9に記載の流体機械。 - 前記動力回収機構、前記副圧縮機および前記シャフトを収容している密閉容器をさらに備え、
前記動力回収機構の前記第1閉塞部材を前記副圧縮機の前記下閉塞部材として共用するように、前記動力回収機構と前記副圧縮機とが前記軸方向に隣接して前記密閉容器内に配置されている、請求項9または10に記載の流体機械。 - 冷媒が循環する冷媒回路を備えた冷凍サイクル装置であって、
前記冷媒回路は、
請求項1~11のいずれか1項に記載の流体機械と、
前記流体機械における副圧縮機で予備圧縮された冷媒をさらに圧縮する主圧縮機と、
前記主圧縮機により圧縮された冷媒を冷却する放熱器と、
前記流体機械における動力回収機構から吐出された冷媒を蒸発させる蒸発器と、
を有する、冷凍サイクル装置。
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CN200980117999.5A CN102037217B (zh) | 2008-05-22 | 2009-05-20 | 流体机械及制冷循环装置 |
JP2010512943A JP5296065B2 (ja) | 2008-05-22 | 2009-05-20 | 冷凍サイクル装置 |
US12/993,756 US20110100025A1 (en) | 2008-05-22 | 2009-05-20 | Fluid machine and refrigeration cycle apparatus |
EP09750376A EP2295721A1 (en) | 2008-05-22 | 2009-05-20 | Fluid machine and refrigeration cycle device |
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EP (1) | EP2295721A1 (ja) |
JP (1) | JP5296065B2 (ja) |
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WO2012029203A1 (ja) * | 2010-09-02 | 2012-03-08 | 三菱電機株式会社 | 膨張機および冷凍サイクル装置 |
WO2012107959A1 (ja) * | 2011-02-09 | 2012-08-16 | 三菱電機株式会社 | 冷凍空調装置 |
JP5478715B2 (ja) * | 2010-03-25 | 2014-04-23 | 三菱電機株式会社 | 冷凍サイクル装置及びその運転方法 |
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JP2022509452A (ja) * | 2018-10-26 | 2022-01-20 | トゥルボアルゴール ソチエタ ア レスポンサビリタ リミタータ | 冷凍装置及びその操作方法 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001012201A (ja) * | 1999-06-24 | 2001-01-16 | Sankyo Seiki Mfg Co Ltd | ロータリー式シリンダ装置 |
WO2008050654A1 (fr) * | 2006-10-25 | 2008-05-02 | Panasonic Corporation | Dispositif à cycle frigorifique et machine à fluide utilisée pour celui-ci |
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CN1153004C (zh) * | 1999-06-18 | 2004-06-09 | 株式会社三协精机制作所 | 旋转式缸装置 |
JP3953871B2 (ja) * | 2002-04-15 | 2007-08-08 | サンデン株式会社 | 冷凍空調装置 |
JP4306240B2 (ja) * | 2002-05-14 | 2009-07-29 | ダイキン工業株式会社 | ロータリ式膨張機及び流体機械 |
JP4735159B2 (ja) * | 2005-09-26 | 2011-07-27 | ダイキン工業株式会社 | 膨張機 |
JP4682795B2 (ja) * | 2005-10-19 | 2011-05-11 | パナソニック株式会社 | 膨張機一体型圧縮機及び冷凍サイクル装置 |
EP1953338B1 (en) * | 2005-10-31 | 2016-09-07 | Panasonic Intellectual Property Management Co., Ltd. | Expander and heat pump using the expander |
-
2009
- 2009-05-20 US US12/993,756 patent/US20110100025A1/en not_active Abandoned
- 2009-05-20 JP JP2010512943A patent/JP5296065B2/ja not_active Expired - Fee Related
- 2009-05-20 WO PCT/JP2009/002231 patent/WO2009142014A1/ja active Application Filing
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- 2009-05-20 CN CN200980117999.5A patent/CN102037217B/zh not_active Expired - Fee Related
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001012201A (ja) * | 1999-06-24 | 2001-01-16 | Sankyo Seiki Mfg Co Ltd | ロータリー式シリンダ装置 |
WO2008050654A1 (fr) * | 2006-10-25 | 2008-05-02 | Panasonic Corporation | Dispositif à cycle frigorifique et machine à fluide utilisée pour celui-ci |
Cited By (6)
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JP5478715B2 (ja) * | 2010-03-25 | 2014-04-23 | 三菱電機株式会社 | 冷凍サイクル装置及びその運転方法 |
US9222706B2 (en) | 2010-03-25 | 2015-12-29 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus and operating method of same |
WO2012029203A1 (ja) * | 2010-09-02 | 2012-03-08 | 三菱電機株式会社 | 膨張機および冷凍サイクル装置 |
JPWO2012029203A1 (ja) * | 2010-09-02 | 2013-10-28 | 三菱電機株式会社 | 膨張機および冷凍サイクル装置 |
WO2012107959A1 (ja) * | 2011-02-09 | 2012-08-16 | 三菱電機株式会社 | 冷凍空調装置 |
JP5484604B2 (ja) * | 2011-02-09 | 2014-05-07 | 三菱電機株式会社 | 冷凍空調装置 |
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EP2295721A1 (en) | 2011-03-16 |
US20110100025A1 (en) | 2011-05-05 |
CN102037217A (zh) | 2011-04-27 |
JPWO2009142014A1 (ja) | 2011-09-29 |
CN102037217B (zh) | 2013-04-17 |
JP5296065B2 (ja) | 2013-09-25 |
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