WO2016157688A1 - シリンダ回転型圧縮機 - Google Patents
シリンダ回転型圧縮機 Download PDFInfo
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- WO2016157688A1 WO2016157688A1 PCT/JP2016/000851 JP2016000851W WO2016157688A1 WO 2016157688 A1 WO2016157688 A1 WO 2016157688A1 JP 2016000851 W JP2016000851 W JP 2016000851W WO 2016157688 A1 WO2016157688 A1 WO 2016157688A1
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- rotor
- cylinder
- compression chamber
- side plate
- shaft
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
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- 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
- F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/332—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/332—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
- F04C18/336—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member and hinged to the inner member
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- 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
- F04C2240/00—Components
- F04C2240/40—Electric motor
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- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
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- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
Definitions
- the present disclosure relates to a cylinder rotary compressor that rotates a cylinder that forms a compression chamber therein.
- a cylinder rotary type compressor that compresses and discharges a fluid by changing a volume of the compression chamber by rotating a cylinder that forms a compression chamber therein is known.
- Patent Document 1 discloses a cylindrical cylinder integrally formed with a rotor of an electric motor unit (electric motor unit), a cylindrical rotor disposed inside the cylinder, and a groove formed in the rotor.
- a cylinder rotary compressor is disclosed that includes a plate-like vane that is slidably fitted into a (slit portion) and partitions a compression chamber.
- the volume of the compression chamber is changed by displacing the vane by rotating the cylinder and the rotor in conjunction with different rotating shafts. Furthermore, in the cylinder rotation type compressor of patent document 1, it aims at size reduction as the whole compressor by arrange
- the outer diameter of the electric motor unit disposed on the outer peripheral side of the cylinder also increases, so that the above-described compressor as a whole can be reduced in size. It becomes difficult to obtain.
- the discharge capacity is increased, torque fluctuations during the operation of the compressor also increase, which increases the noise and vibration of the compressor as a whole.
- This disclosure is intended to provide a cylinder rotary type compressor capable of expanding the capacity of a compression chamber without causing an increase in radial size.
- a cylinder rotary compressor in one aspect of the present disclosure, includes a cylindrical cylinder that rotates about a central axis, and a cylinder that is disposed inside the cylinder and rotates about an eccentric shaft that is eccentric with respect to the central axis of the cylinder.
- a first vane for partitioning the first compression chamber formed between the outer peripheral surface and the inner peripheral surface of the cylinder and a second groove formed in the second rotor are slidably fitted into the outer periphery of the second rotor.
- the first rotor and the second rotor are arranged side by side in the central axis direction of the cylinder.
- the first compression chamber and the second compression chamber can be formed. Therefore, the total capacity (total discharge capacity) of the first compression chamber and the second compression chamber can be easily increased. Furthermore, since the first rotor and the second rotor are arranged side by side in the central axis direction of the cylinder, the total discharge capacity can be increased without increasing the outer diameter of the cylinder.
- the eccentric shaft of the first rotor and the eccentric shaft of the second rotor may be arranged coaxially. According to this, it is not necessary to form the part which has a different eccentric shaft in a shaft, and a shaft can be formed easily.
- the rotation angle of the cylinder at which the fluid pressure in the first compression chamber reaches the maximum pressure and the rotation angle of the cylinder at which the fluid pressure in the second compression chamber reaches the maximum pressure may be shifted by 180 °. According to this, an increase in torque fluctuation due to the expansion of the capacity of the compression chamber can be suppressed, and an increase in noise and vibration as the whole compressor can be effectively suppressed.
- 180 ° misalignment does not mean that it is completely 180 ° misalignment, and it includes a slight error with respect to 180 ° due to manufacturing or assembly errors. It is meant to include.
- FIG. 2 is a sectional view taken along the line II-II in FIG.
- FIG. 3 is a sectional view taken along line III-III in FIG.
- a cylinder rotary compressor 1 (hereinafter simply referred to as a compressor 1) of the present embodiment is applied to a vapor compression refrigeration cycle apparatus that cools air blown into a vehicle interior by a vehicle air conditioner.
- the refrigerant serving as a compression target fluid is compressed and discharged.
- an HFC refrigerant (specifically, R134a) is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. Further, the refrigerant is mixed with refrigerating machine oil that is a lubricating oil for lubricating the sliding portion of the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
- refrigerating machine oil that is a lubricating oil for lubricating the sliding portion of the compressor 11
- the compressor 1 includes a compression mechanism portion 20 that compresses and discharges a refrigerant into a housing 10 that forms an outer shell thereof, and an electric motor portion (electric motor portion) that drives the compression mechanism portion 20. ) Is configured as an electric compressor containing 30.
- the up and down arrows in FIG. 1 indicate the up and down directions in a state where the compressor 1 is mounted on the vehicle air conditioner.
- the housing 10 is configured by combining a plurality of metal members, and has a sealed container structure that forms a substantially cylindrical space inside.
- the housing 10 includes a bottomed cylindrical (cup-shaped) main housing 11, and a bottomed cylindrical sub-unit disposed so as to close the opening of the main housing 11. It is configured by combining the housing 12 and a disk-shaped lid member 13 arranged so as to close the opening of the sub-housing 12.
- a seal member made of an O-ring or the like is interposed in the contact portions of the main housing 11, the sub housing 12, and the lid member 13, so that the refrigerant does not leak from each contact portion.
- a discharge port 11 a that discharges the high-pressure refrigerant pressurized by the compression mechanism 20 to the outside of the housing 10 (specifically, the refrigerant inlet side of the condenser of the refrigeration cycle apparatus). Is formed.
- a suction port 12 a that sucks low-pressure refrigerant (specifically, low-pressure refrigerant flowing out of the evaporator of the refrigeration cycle apparatus) from the outside of the housing 10 is formed on the cylindrical side surface of the sub-housing 12.
- a housing side suction passage 13a for guiding the low-pressure refrigerant sucked from the suction port 12a to the first and second compression chambers Va and Vb of the compression mechanism portion 20 is formed.
- a drive circuit (inverter) 30 a for supplying electric power to the motor unit 30 is attached to the surface of the lid member 13 opposite to the surface on the sub housing 12 side.
- the electric motor unit 30 has a stator 31 as a stator.
- the stator 31 includes a stator core 31a formed of a metal magnetic material and a stator coil 31b wound around the stator core 31a.
- the stator 31 is press-fitted, shrink-fitted, bolted, etc. to the inner peripheral surface of the cylindrical side surface of the main housing 11. It is fixed by means of
- the cylinder 21 is formed of a cylindrical metal magnetic material, and forms first and second compression chambers Va and Vb of the compression mechanism unit 20 as will be described later.
- a magnet (permanent magnet) 32 is fixed to the cylinder 21.
- the cylinder 21 also has a function as a rotor of the electric motor unit 30.
- the cylinder 21 rotates around the central axis C1 by the rotating magnetic field generated by the stator 31.
- the rotor of the electric motor unit 30 and the cylinder 21 of the compression mechanism unit 20 are integrally configured.
- the rotor of the electric motor unit 30 and the cylinder 21 of the compression mechanism unit 20 may be configured as separate members and integrated by means such as press-fitting.
- the stator (stator core 31 a and stator core 31 a) of the electric motor unit 30 is disposed on the outer peripheral side of the cylinder 21.
- first compression mechanism portion 20a two compression mechanism portions 20 are provided, a first compression mechanism portion 20a and a second compression mechanism portion 20b.
- the basic configurations of the first and second compression mechanisms 20a and 20b are equivalent to each other.
- the first and second compression mechanism portions 20 a and 20 b are connected in parallel to the refrigerant flow inside the housing 10.
- the first and second compression mechanism portions 20a and 20b are arranged side by side in the central axis direction of the cylinder 21, as shown in FIG.
- the one disposed on the bottom surface side of the main housing 11 is the first compression mechanism portion 20a
- the one disposed on the sub housing 12 side is the second compression mechanism. Part 20b.
- the reference numerals corresponding to the equivalent constituent members of the first compression mechanism portion 20 a are used, and the alphabet at the end is changed from “a” to “b”. Changed to show.
- the second rotor that is a constituent member corresponding to the first rotor 22a of the first compression mechanism portion 20a is denoted by the symbol “22b”.
- the first compression mechanism unit 20a includes a cylinder 21, a first rotor 22a, a first vane 23a, a shaft 24, and the like.
- the second compression mechanism portion 20b includes a cylinder 21, a second rotor 22b, a second vane 23b, a shaft 24, and the like. That is, as shown in FIG. 1, in the cylinder 21 and the shaft 24, a part on the bottom surface side of the main housing 11 constitutes the first compression mechanism portion 20a, and another part on the sub housing 12 side is the second.
- the compression mechanism part 20b is comprised.
- the cylinder 21 rotates around the central axis C1 as a rotor of the electric motor unit 30, and includes the first compression chamber Va of the first compression mechanism unit 20a and the second compression chamber of the second compression mechanism unit 20b. It is a cylindrical member that forms Vb.
- a first side plate 25a which is a closing member that closes the opening end of the cylinder 21, is fixed to one axial end of the cylinder 21 by means such as bolting.
- a second side plate 25b is fixed to the other axial end of the cylinder 21.
- the first and second side plates 25a and 25b have a disk-shaped portion that extends in a direction substantially perpendicular to the rotation axis of the cylinder 21, and a boss portion that is disposed at the center of the disk-shaped portion and protrudes in the axial direction. is doing. Furthermore, a through-hole penetrating the front and back of the first and second side plates 25a and 25b is formed in the boss portion.
- a bearing mechanism (not shown) is disposed in each of these through holes, and the cylinder 21 is rotatably supported with respect to the shaft 24 by inserting the shaft 24 into the bearing mechanism. Both end portions of the shaft 24 are fixed to the housing 10 (specifically, the main housing 11 and the sub housing 12). Therefore, the shaft 24 does not rotate with respect to the housing 10.
- the cylinder 21 of the present embodiment forms a first compression chamber Va and a second compression chamber Vb that are partitioned from each other inside. For this reason, a disc-shaped intermediate side plate 25c for partitioning the first compression chamber Va and the second compression chamber Vb is disposed between the first rotor 22a and the second rotor 22b inside the cylinder 21. Has been.
- the intermediate side plate 25c also has the same function as the first and second side plates 25a and 25b.
- both end portions in the axial direction of the portion constituting the first compression mechanism portion 20a are closed by the first side plate 25a and the intermediate side plate 25c.
- part which comprises the 2nd compression mechanism part 20b among the cylinders 21 are obstruct
- the first side plate 25a partitions the first compression chamber Va together with the intermediate side plate 25c, the first rotor 22a, and the like
- the second side plate 25b includes the intermediate side plate 25c, the second rotor 22b, and the like.
- the second compression chamber Vb is partitioned.
- the intermediate side plate 25c is disposed between the first rotor 22a and the second rotor 22b, and partitions the first compression chamber Va and the second compression chamber Vb.
- the cylinder 21 and the intermediate side plate 25c are integrally formed.
- the cylinder 21 and the intermediate side plate 25c are formed as separate members and integrated by means such as press-fitting. Also good.
- the axial length of the first rotor 22a and the axial length of the second rotor 22b are equal, and the first compression chamber Va and the second compression chamber Vb have their maximum volumes. Are partitioned so as to have substantially the same volume.
- the shaft 24 is a substantially cylindrical member that rotatably supports the cylinder 21 (specifically, the side plates 25a, 25b, and 25c fixed to the cylinder 21), the first rotor 22a, and the second rotor 22b. is there.
- An eccentric portion 24c having an outer diameter smaller than that of the end portion on the sub housing 12 side is provided at the central portion of the shaft 24 in the axial direction.
- the central axis of the eccentric portion 24c is an eccentric shaft C2 that is eccentric with respect to the central axis C1 of the cylinder 21.
- the first and second rotors 22a and 22b are rotatably supported by the eccentric portion 24c via a bearing mechanism (not shown).
- the first and second compression mechanism portions 20a and 20b of the present embodiment are arranged side by side in the central axis direction of the cylinder 21. Therefore, the first rotor 22a and the second rotor 22b are also arranged side by side in the central axis direction of the cylinder 21, as shown in FIGS. Further, when the first and second rotors 22a and 22b rotate, the first and second rotors 22a and 22b rotate around a common eccentric axis C2 that is eccentric with respect to the central axis C1 of the cylinder 21. That is, in the present embodiment, the eccentric shaft of the first rotor 22a and the eccentric shaft of the second rotor 22b are arranged coaxially.
- the shaft 24 is in communication with the housing-side suction passage 13 a to guide the low-pressure refrigerant flowing from the outside to the first and second compression chambers Va, Vb. 24d is formed.
- a plurality of (four in this embodiment) first and second shaft-side outlet holes 240 a and 240 b through which low-pressure refrigerant flowing through the shaft-side suction passage 24 d flows out are opened on the outer peripheral surface of the shaft 24.
- first and second shaft-side recesses 241 a and 241 b are formed on the outer peripheral surface of the shaft 24.
- the first and second shaft-side recesses 241 a and 241 b are formed.
- the 1st, 2nd shaft side exit holes 240a and 240b are opening to the site
- the first and second shaft side outlet holes 240a and 240b are annular first and second shaft side communication spaces 242a and 242b formed inside the first and second shaft side recesses 241a and 241b, respectively.
- the first rotor 22 a is a cylindrical member that is disposed inside the cylinder 21 and extends in the central axis direction of the cylinder 21. As shown in FIG. 1, the axial length of the first rotor 22 a is formed to have a dimension substantially equal to the axial length of the portion that constitutes the first compression mechanism portion 20 a of the shaft 24 and the cylinder 21.
- the outer diameter dimension of the first rotor 22a is smaller than the inner diameter dimension of the columnar space formed inside the cylinder 21. More specifically, as shown in FIGS. 2 and 3, the outer diameter of the first rotor 22a is such that the outer circumference of the first rotor 22a and the inner circumference of the cylinder 21 when viewed from the axial direction of the eccentric shaft C2. The surface is set to contact at one contact point C3.
- a transmission mechanism is disposed between the first rotor 22a and the intermediate side plate 25c and between the first rotor 22a and the first side plate 25a.
- the transmission mechanism rotates from the cylinder 21 (more specifically, the intermediate side plate 25c and the first side plate 25a rotating together with the cylinder 21) to the first rotor 22a so that the first rotor 22a rotates synchronously with the cylinder 21. Transmits driving force.
- the transmission mechanism will be described by taking as an example one disposed between the first rotor 22a and the intermediate side plate 25c.
- the transmission mechanism includes a plurality of (four in this embodiment) circular first hole portions 221a formed on the surface of the first rotor 22a on the intermediate side plate 25c side, and the intermediate side A plurality of (four in this embodiment) drive pins 251c project in the central axis direction from the plate 25c toward the first rotor 22a.
- the plurality of drive pins 251c are formed to have a smaller diameter than the first hole 221a, protrude in the axial direction toward the rotor 22, and are respectively fitted in the first holes 221a. Therefore, the drive pin 251c and the first hole 221a constitute a mechanism equivalent to a so-called pin-hole type rotation prevention mechanism. The same applies to the transmission mechanism provided between the first rotor 22a and the first side plate 25a.
- the relative position (relative distance) between each drive pin 251c and the eccentric portion 24c of the shaft 24 changes. Due to the change in the relative position (relative distance), the side wall surface of the first hole 221a of the first rotor 22a receives a load in the rotational direction from the drive pin 251c. As a result, the first rotor 22a rotates around the eccentric axis C2 in synchronization with the rotation of the cylinder 21.
- the transmission mechanism of the present embodiment power is sequentially transmitted to the rotor 22 by the plurality of drive pins 251c and the first hole portion 221a. Therefore, it is desirable that the plurality of drive pins 251c and the first hole 221a be arranged at equiangular intervals around the eccentric axis C2. Furthermore, a metal ring member 223a is fitted in each first hole 221a to suppress wear on the outer peripheral side wall surface with which the drive pin 251c contacts.
- a first oil passage 225a extending in the axial direction of the eccentric shaft C2 and penetrating from one end side in the axial direction to the other end side is formed inside the first rotor 22. ing.
- the first oil passage 225a is supplied through the first oil return passage 11b formed on the bottom surface side of the main housing 11, the oil passage 252a formed in the gap between the shaft 24 and the boss portion of the first side plate 25a, and the like. It is a lubricating oil passage which distributes the refrigerating machine oil.
- the first oil return passage 11b is a lubricating oil passage that guides the refrigeration oil accumulated in the lower side of the internal space of the housing 10 to the first oil passage 225a side.
- first hole 221a of the transmission mechanism provided between the first rotor 22a and the intermediate side plate 25c and between the first rotor 22a and the first side plate 25a is respectively connected to the first oil passage 225a. It is formed by both axial ends.
- the first hole portions 221a communicate with each other via the first oil passage 225a.
- a first groove portion (first slit portion) 222a is formed on the outer peripheral surface of the first rotor 22a.
- a first vane 23a which will be described later, is slidably fitted in the first groove 222a.
- the sliding surface of the first vane 23a (the friction surface with the first vane 23a) is inclined with respect to the radial direction of the first rotor 22a when viewed from the axial direction of the eccentric shaft C2. is doing. More specifically, in the first groove portion 222a, the sliding surface of the first vane 23a is inclined in the rotational direction from the inner peripheral side toward the outer peripheral side. For this reason, the 1st vane 23a inserted in the 1st groove part 222a is also displaced in the direction inclined with respect to the radial direction of the 1st rotor 22a.
- the first rotor 22 a extends in the radial direction in the same manner as the first groove 222 a, as shown in FIG. 3.
- a first rotor side suction passage 224a is formed to communicate between the shaft side communication space 242a side) and the outer peripheral side (first compression chamber Va side). As a result, the refrigerant flowing from the outside into the shaft side suction passage 24d is guided to the first rotor side suction passage 224a side.
- the outlet hole of the first rotor-side suction passage 224a opens to the outer peripheral surface of the first rotor 22a on the rear side in the rotational direction with respect to the first groove portion 222a.
- the first rotor-side suction passage 224a and the first groove 222a are partitioned from each other, and are formed so that the internal spaces do not communicate with each other.
- the first vane 23 a is a plate-like partition member that partitions the first compression chamber Va formed between the outer peripheral surface of the first rotor 22 a and the inner peripheral surface of the cylinder 21.
- the axial length of the first vane 23a is formed to be approximately the same as the axial length of the first rotor 22a.
- the outer peripheral side front end portion of the first vane 23 a is arranged to be slidable with respect to the inner peripheral surface of the cylinder 21.
- the cylinder 21 is surrounded by the inner wall surface of the cylinder 21, the outer peripheral surface of the first rotor 22a, the plate surface of the first vane 23a, the first side plate 25a, and the intermediate side plate 25c.
- the first compression chamber Va is formed by the space. That is, the first vane 23a partitions the first compression chamber Va formed between the inner peripheral surface of the cylinder 21 and the outer peripheral surface of the first rotor 22a.
- the first side plate 25a is formed with a first discharge hole 251a for discharging the refrigerant compressed in the first compression chamber Va to the internal space of the housing 10. Furthermore, the lead which suppresses that the refrigerant
- a first discharge valve comprising a valve is disposed.
- the second compression mechanism unit 20 will be described.
- the basic configuration of the second compression mechanism 20b is the same as that of the first compression mechanism 20a. Therefore, as shown in FIG. 1, the 2nd rotor 22b is comprised by the cylindrical member of the dimension substantially equivalent to the axial direction length of the site
- the eccentric shaft C2 of the second rotor 22b and the eccentric shaft C2 of the first rotor 22a are arranged coaxially, when viewed from the axial direction of the eccentric shaft C2, the outer circumferential surface of the second rotor 22b The inner peripheral surface of the cylinder 21 is in contact with the contact point C3 shown in FIGS. 2 and 3 in the same manner as the first rotor 22a.
- a transmission mechanism similar to the transmission mechanism that transmits the rotational driving force to the first rotor 22a is provided between the second rotor 22b and the intermediate side plate 25c and between the second rotor 22b and the first side plate 25a. It has been. Accordingly, the second rotor 22b is formed with a plurality of circular second holes into which the plurality of driving pins 251c are fitted. A ring member similar to the first hole 221a is fitted into the second hole.
- the drive pin 251c protruding from the intermediate side plate 25c toward the second rotor 22b is formed of the same member as the drive pin 251c protruding from the intermediate side plate 25c toward the first rotor 22b. That is, the drive pin 251c fixed to the intermediate side plate 25c projects in the central axis direction toward both the first rotor 22a side and the second rotor 22b side.
- the second rotor 22b As shown in FIG. 1, in the second rotor 22b, as in the first oil passage 225a of the first rotor 22a, the second rotor 22b extends in the axial direction of the eccentric shaft C2, and extends from one end side to the other end side in the axial direction. A penetrating second oil passage 225b is formed.
- the second oil passage 225b is supplied through a second oil return passage 12b formed in the sub housing 12, an oil passage 252b formed in a gap between the shaft 24 and the boss portion of the second side plate 25b, and the like. This is a lubricating oil passage for circulating machine oil.
- the second oil return passage 12b is a lubricating oil passage that guides the refrigerating machine oil accumulated on the lower side of the internal space of the housing 10 to the second oil passage 225b side.
- both end portions in the axial direction of the second oil passage 225b form second hole portions of the transmission mechanism in the same manner as the first oil passage 225a.
- a second groove portion (second slit portion) 222b that is recessed toward the inner periphery over the entire area in the axial direction is formed on the outer peripheral surface of the second rotor 22b. ing. Similar to the first vane 23a of the first groove 222a, the second vane 23b is slidably fitted into the second groove 222b.
- the inner side of the second rotor 22b and the outer side of the second rotor 22b extend in the radial direction in the same manner as the second groove 222b.
- a second rotor side suction passage 224b is formed to communicate with the (second compression chamber Vb side).
- the cylinder 21 is surrounded by the inner wall surface of the cylinder 21, the outer peripheral surface of the second rotor 22b, the plate surface of the second vane 23b, the second side plate 25b, and the intermediate side plate 25c.
- a second compression chamber Vb is formed by the space. That is, the second vane 23b partitions the second compression chamber Vb formed between the inner peripheral surface of the cylinder 21 and the outer peripheral surface of the second rotor 22b.
- the second side plate 25b is formed with a second discharge hole 251b through which the refrigerant compressed in the second compression chamber Vb is discharged into the internal space of the housing 10. Furthermore, the second side plate 25b has a lead that prevents the refrigerant that has flowed out of the second discharge hole 251b into the internal space of the housing 10 from flowing back into the second compression chamber Vb through the second discharge hole 251b.
- a second discharge valve comprising a valve is arranged.
- the second vane 23b, the second rotor side suction passage 224b, and the second discharge hole 251b of the second side plate 25b are disposed at positions that are approximately 180 ° out of phase with respect to the first vane 23a of the first compression mechanism portion 20a, the first rotor side suction passage 224a, the first discharge holes 251a of the first side plate 25a, and the like. ing.
- FIG. 5 is an explanatory view continuously showing changes in the first compression chamber Va accompanying the rotation of the cylinder 21 in order to explain the operating state of the compressor 1.
- the rotation angle ⁇ is 0 °
- the contact point C3 and the outer peripheral end of the first vane 23a overlap.
- the first compression chamber Va having the maximum volume is formed on the front side in the rotation direction of the first vane 23a, and the minimum volume (that is, the volume is 0) is also formed on the rear side in the rotation direction of the first vane 23a.
- a first compression chamber Va for the suction stroke is formed.
- the first compression chamber Va in the suction stroke means the first compression chamber Va that has a stroke in which the volume is expanded, and the first compression chamber Va in the compression stroke is a stroke in which the volume is reduced. Means the first compression chamber Va.
- the low-pressure refrigerant sucked from the suction port 12a formed in the sub-housing 12 is in the order of the housing-side suction passage 13a ⁇ the first shaft-side outlet hole 240a of the shaft-side suction passage 24d ⁇ the first rotor-side suction passage 224a. And flows into the first compression chamber Va in the suction stroke.
- the centrifugal force accompanying the rotation of the rotor 22 acts on the first vane 23a, the outer peripheral side tip of the first vane 23a is pressed against the inner peripheral surface of the cylinder 21. Accordingly, the first vane 23a partitions the first compression chamber Va for the suction stroke and the first compression chamber Va for the compression stroke.
- the refrigerant pressure in the first compression chamber Va exceeds the valve opening pressure of the first discharge valve determined according to the refrigerant pressure in the internal space of the housing 10 (that is, the maximum pressure in the first compression chamber Va).
- the refrigerant in the first compression chamber Va is discharged into the internal space of the housing 10 through the first discharge hole 251a.
- the cylinder 21 has the refrigerant suction stroke described when the rotation angle ⁇ changes from 0 ° to 360 ° and the refrigerant compression stroke described when the rotation angle ⁇ changes from 360 ° to 720 °. It is performed simultaneously with one rotation.
- the second compression mechanism unit 20b operates in the same manner, and refrigerant is compressed and sucked.
- the second vane 23b and the like are arranged at a position that is 180 ° out of phase with respect to the first vane 23a and the like of the first compression mechanism portion 20a. Therefore, in the second compression chamber Vb in the compression stroke, the refrigerant is compressed and sucked at a rotation angle that is 180 ° out of phase with respect to the first compression chamber Va.
- the refrigerant pressure in the second compression chamber Vb in the compression stroke rises, and the refrigerant pressure in the second compression chamber Vb is changed to the valve opening pressure (that is, the first discharge valve disposed in the second side plate 25b).
- the valve opening pressure that is, the first discharge valve disposed in the second side plate 25b.
- the combined refrigerant of the high-pressure gas-phase refrigerant discharged from the first compression mechanism unit 20 a and the high-pressure gas-phase refrigerant discharged from the second compression mechanism unit 20 b reduces the flow velocity in the internal space of the housing 10. Thereby, the refrigerating machine oil discharged from the first and second discharge holes 251a and 251b together with the high-pressure gas-phase refrigerant falls downward due to the action of gravity and is separated from the merged refrigerant.
- the combined refrigerant from which the refrigerating machine oil has been separated is discharged from the discharge port 11 a of the housing 10.
- the refrigerating machine oil separated from the combined refrigerant is stored in the lower side of the internal space of the housing 10.
- the refrigerating machine oil stored in the lower side of the internal space of the housing 10 flows into the first and second oil passages 225a and 225b via the first and second oil return passages 11b and 12b.
- the shaft 24, the first and second rotors 22a and 22b, and the sliding portions of the side plates 25a to 25c are supplied.
- the refrigerant (fluid) can be sucked, compressed, and discharged in the refrigeration cycle apparatus.
- the compression mechanism part 20 is arrange
- the compressor 1 of the present embodiment includes the first rotor 22a (first compression mechanism portion 20a) and the second rotor 22b (second compression mechanism portion 20b), the first compression chamber Va and the second compression chamber Va.
- the compression chamber Vb can be formed. Therefore, the total discharge capacity of the first compression chamber Va and the second compression chamber Vb can be easily expanded in accordance with the applied system (in this embodiment, the refrigeration cycle apparatus).
- the outer diameter of the cylinder 21 may be increased in order to increase the total discharge capacity. Absent. Therefore, the outer diameter of the stator 31 of the electric motor unit 30 and the main housing 11 that accommodates the stator 31 is not increased.
- the capacity of the compression chambers (Va, Vb) can be increased without increasing the radial size.
- the eccentric shaft C2 of the first rotor 22a and the eccentric shaft C2 of the second rotor 22b are arranged coaxially, so that a portion having a different eccentric shaft is formed on the shaft 24.
- the shaft 24 can be easily formed.
- the maximum volumes of the first compression chamber Va and the second compression chamber Vb are substantially equal to each other, and the refrigerant in the first compression chamber Va reaches the maximum pressure.
- the rotation angle ⁇ of the cylinder 21 and the rotation angle ⁇ of the cylinder 21 at which the refrigerant in the second compression chamber Vb reaches the maximum pressure are shifted by 180 °.
- FIG. 6 shows a total torque fluctuation of the compressor 1 of the present embodiment and a cylinder rotary compressor (single cylinder compressor) having a single compression mechanism portion similar to the first compression mechanism portion 20a. It is the graph which compared torque fluctuation.
- the total torque fluctuation is a torque fluctuation caused by a refrigerant pressure fluctuation in the first compression chamber Va of the first compression mechanism section 20a and a refrigerant pressure fluctuation in the second compression chamber Vb of the second compression mechanism section 20b. Is a sum of torque fluctuations caused by
- the discharge capacity of the single-cylinder compressor shown in FIG. 6 matches the total discharge capacity of the first compression chamber Va and the second compression chamber Vb of the compressor 1 of the present embodiment. Further, the suction refrigerant pressure and the discharge refrigerant pressure of the single cylinder compressor shown in FIG. 6 are set to be equal to the suction refrigerant pressure and the discharge refrigerant pressure with the compressor 1 of the present embodiment, respectively.
- the first and second oil passages 225a and 225b are formed in the first and second rotors 22a and 22b, so the shaft 24, the first and second rotors 22a and 22b are formed. , And the sliding portions of the side plates 25a to 25c can be lubricated. As a result, the durability performance of the compressor 1 as a whole can be improved.
- first and second oil passages 225a and 225b are formed, the first and second rotors 22a and 22b and the intermediate side plate 25c, which are positioned at the central portion in the central axis direction in the cylinder 21, are formed. This is effective in that refrigeration oil can be introduced into the sliding portion.
- a transmission mechanism having the same configuration as a so-called pin-hole type rotation prevention mechanism is employed, so that the transmission mechanism can be realized with a simple configuration. Furthermore, since the ring member 223a is fitted in the hole of the transmission mechanism, the wear resistance of the hole can be improved. As a result, the durability performance of the compressor 1 as a whole can be improved.
- first and second hole portions 221a are formed at axial ends of the first and second oil passages 225a and 225b. Therefore, the space for arranging the transmission mechanism can be reduced, and the size of the compressor 1 as a whole can be further reduced.
- the suction passage that guides the refrigerant sucked from the outside to the first and second compression chambers Va, Va serves as the shaft-side suction passage 24d and the first and second rotor-side suction passages 224a. 224b or the like. Therefore, compared with the case where a part of the suction passage is formed in the first and second side plates 25a, 25b and the like that rotate together with the cylinder 21, the passage configuration of the suction passage and the sealing structure are not complicated.
- first and second discharge holes 251a and 251b are formed in the first and second side plates 25a and 25b, the refrigerant flows through the first and second compression mechanisms 20a and 20b inside the housing 10. It is possible to easily realize a configuration for connecting in parallel.
- FIG. 7 is a cross-sectional view corresponding to FIG. 3 described in the first embodiment, and shows a vertical cross section in the axial direction of the first compression mechanism portion 20a.
- FIG. 7 the same code
- FIG. 8 described in the following embodiment.
- the first hinge portion 231a is formed at the outer peripheral side end portion of the first vane 23a.
- the first hinge portion 231a is supported by a hinge groove formed on the inner peripheral surface of the cylinder 21 so as to be swingable in the circumferential direction. For this reason, the vane 23 does not leave the cylinder 21, and the inner peripheral side of the first vane 23a is slidably displaced in the first groove 222a.
- an arc-shaped portion having a diameter equivalent to the width dimension of the first groove portion 222a is formed at the inner peripheral side end portion of the first vane 23a.
- the basic configuration of the second compression mechanism unit 20b is the same as that of the first compression mechanism unit 20a. Therefore, as shown by a broken line in FIG. 7, the outer peripheral side end of the second vane 23b is also supported by the cylinder so as to be swingable.
- the compressor 1 of this embodiment when operated, it operates similarly to the first embodiment, and the refrigerant (fluid) can be sucked, compressed and discharged in the refrigeration cycle apparatus. Further, similarly to the first embodiment, the capacity of the compression chambers (Va, Vb) can be increased without increasing the radial size, and the increase in noise and vibration of the entire compressor is suppressed. be able to.
- a first shoe 232a having a shape (substantially semicircular shape) in which the cross-sectional shape when viewed from the axial direction of the central axis C1 is a part of a circle is cut into the first vane 222a. It arrange
- the axial length of the first shoe 232a is substantially the same as that of the first rotor 22a and the first vane 23a.
- the basic configuration of the second compression mechanism unit 20b is the same as that of the first compression mechanism unit 20a.
- the sealing performance between the first and second vanes 23a and 23b and the inner wall surfaces of the first and second groove portions 222a and 222b is effective. Can be improved. Thereby, the compression efficiency of the compressor 1 can be improved.
- the cylinder rotary compressor 1 is not limited to this. That is, the cylinder rotary compressor 1 can be applied to a wide range of uses as a compressor that compresses various fluids.
- the power transmission means is not limited to this.
- the electric motor unit 30 in which the stator is disposed on the outer peripheral side of the cylinder 21 configured integrally with the rotor has been described, but the electric motor unit 30 is not limited thereto.
- the electric motor unit and the cylinder 21 may be arranged side by side in the direction of the central axis C1 of the cylinder 21, and the electric motor unit and the cylinder 21 may be connected. Further, the rotational driving force of the electric motor unit may be transmitted to the cylinder 21 via a belt without arranging the rotational center of the electric motor unit and the central axis C1 of the cylinder 21 on the same axis.
Abstract
Description
以下、図面を用いて、第1実施形態を説明する。本実施形態のシリンダ回転型圧縮機1(以下、単に圧縮機1と記載する。)は、車両用空調装置にて車室内へ送風される送風空気を冷却する蒸気圧縮式の冷凍サイクル装置に適用されており、この冷凍サイクル装置において圧縮対象流体である冷媒を圧縮して吐出する機能を果たす。
本実施形態では、第1実施形態に対して、図7に示すように、圧縮機構部20の構成を変更した例を説明する。なお、図7は、第1実施形態で説明した図3に対応する断面図であって、第1圧縮機構部20aの軸方向垂直断面を示している。また、図7では、第1実施形態と同一もしくは均等部分には同一の符号を付している。このことは、以下の実施形態で説明する図8においても同様である。
本実施形態では、第2実施形態に対して、図8に示すように、圧縮機構部20の構成を変更した例を説明する。より具体的には、本実施形態の第1圧縮機構部20aでは、第1ベーン23aの第1ヒンジ部231aよりも内周側を平板上に形成している。
本開示は上述の実施形態に限定されることなく、本開示の趣旨を逸脱しない範囲内で、以下のように種々変形可能である。
Claims (9)
- 中心軸(C1)周りに回転する円筒状のシリンダ(21)と、
前記シリンダ(21)の内部に配置されて、前記シリンダ(21)の中心軸(C1)に対して偏心した偏心軸(C2)周りに回転する円筒状の第1ロータ(22a)および第2ロータ(22b)と、
前記第1ロータ(22a)および前記第2ロータ(22b)を回転可能に支持するシャフト(24)と、
前記第1ロータ(22a)に形成された第1溝部(222a)に摺動可能に嵌め込まれて、前記第1ロータ(22a)の外周面と前記シリンダ(21)の内周面との間に形成される第1圧縮室(Va)を仕切る第1ベーン(23a)と、
前記第2ロータ(22b)に形成された第2溝部(222b)に摺動可能に嵌め込まれて、前記第2ロータ(22b)の外周面と前記シリンダ(21)の内周面との間に形成される第2圧縮室(Vb)を仕切る第2ベーン(23b)と、を備え、
前記第1ロータ(22a)および前記第2ロータ(22b)は、前記シリンダ(21)の中心軸(C1)方向に並んで配置されているシリンダ回転型圧縮機。 - 前記第1ロータ(22a)の偏心軸および前記第2ロータ(22b)の偏心軸は、同軸上に配置されている請求項1に記載のシリンダ回転型圧縮機。
- 前記第1圧縮室(Va)内の流体圧力が最大圧力に到達する前記シリンダ(21)の回転角(θ)と前記第2圧縮室(Vb)内の流体圧力が最大圧力に到達する前記シリンダ(21)の回転角(θ)が、180°ずれている請求項1または2に記載のシリンダ回転型圧縮機。
- 前記第1ロータ(22a)および前記第2ロータ(22b)には、それぞれ前記シャフト(24)の軸方向に延びて、摺動部位を潤滑する潤滑油を流通させる第1オイル通路(225a)および第2オイル通路(225b)が形成されている請求項1ないし3のいずれか1つに記載のシリンダ回転型圧縮機。
- 前記第1ロータ(22a)および前記第2ロータ(22b)が前記シリンダ(21)と同期回転するように、前記シリンダ(21)から前記第1ロータ(22a)および前記第2ロータ(22b)へ回転駆動力を伝達する伝動機構(251c、221a)と、
前記第1ロータ(22a)と前記第2ロータ(22b)との間に配置されて前記第1圧縮室(Va)と前記第2圧縮室(Vb)とを仕切るとともに、前記シリンダ(21)とともに回転する中間サイドプレート(25c)と、を備え、
前記伝動機構は、前記中間サイドプレート(25c)から前記第1ロータ(22a)側および前記第2ロータ(22b)側へ中心軸方向に突出する駆動ピン(251c)、並びに、それぞれ前記第1ロータ(22a)および前記第2ロータ(22b)に形成されて前記駆動ピン(251c)が嵌め込まれる第1穴部(221a)および第2穴部によって構成されている請求項1ないし4のいずれか1つに記載のシリンダ回転型圧縮機。 - 前記第1、第2穴部(221a)には、前記駆動ピン(251c)が接触する外周側壁面の摩耗を抑制するためのリング部材(223a)が嵌め込まれている請求項5に記載のシリンダ回転型圧縮機。
- 前記第1ロータ(22a)には、前記偏心軸(C2)の軸方向に延びて、摺動部位を潤滑する潤滑油を流通させる第1オイル通路(225a)が形成されており、
前記第1穴部(221a)は、前記第1オイル通路(225a)の軸方向端部に形成されており、
前記第2ロータ(22b)には、前記偏心軸(C2)の軸方向に延びて、摺動部位を潤滑する潤滑油を流通させる第2オイル通路(225b)が形成されており、
前記第2穴部は、前記第2オイル通路(225b)の軸方向端部に形成されている請求項5または6に記載のシリンダ回転型圧縮機。 - 前記第1ロータ(22a)と前記第2ロータ(22b)との間に配置されて前記第1圧縮室(Va)と前記第2圧縮室(Vb)とを仕切るとともに、前記シリンダ(21)とともに回転する中間サイドプレート(25c)と、
前記シリンダ(21)の軸方向一端側に固定されて、前記中間サイドプレート(25c)とともに前記第1圧縮室(Va)を仕切る第1サイドプレート(25a)と、
前記シリンダ(21)の軸方向他端側に固定されて、前記中間サイドプレート(25c)とともに前記第2圧縮室(Vb)を仕切る第2サイドプレート(25b)と、を備え、
前記第1ロータ(22a)には、前記第1圧縮室(Va)へ圧縮対象流体を流入させる第1ロータ側吸入通路(224a)が形成され、
前記第1サイドプレート(25a)には、前記第1圧縮室(Va)から圧縮対象流体を流出させる第1吐出穴(251a)が形成され、
前記第2ロータ(22b)には、前記第2圧縮室(Vb)へ圧縮対象流体を流入させる第2ロータ側吸入通路(224b)が形成され、
前記第2サイドプレート(25b)には、前記第2圧縮室(Vb)から圧縮対象流体を流出させる第2吐出穴(251b)が形成され、
さらに、前記シャフト(24)には外部から吸入された圧縮対象流体を前記第1ロータ側吸入通路(224a)および前記第2ロータ側吸入通路(224b)へ導く、シャフト側吸入通路(24d)が形成されている請求項1ないし7のいずれか1つに記載のシリンダ回転型圧縮機。 - 前記シリンダ(21)を回転させる電動機部(30)を備え、
前記シリンダ(21)は、前記電動機部(30)の回転子と一体的に形成されており、
前記電動機部(30)の固定子は、前記シリンダ(21)の外周側に配置されている請求項1ないし8のいずれか1つに記載のシリンダ回転型圧縮機。
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CN201680018336.8A CN107532597B (zh) | 2015-03-27 | 2016-02-18 | 气缸旋转型压缩机 |
DE112016001440.6T DE112016001440T5 (de) | 2015-03-27 | 2016-02-18 | Kompressor vom Typ mit einem sich drehenden Zylinder |
KR1020177020128A KR101931627B1 (ko) | 2015-03-27 | 2016-02-18 | 실린더회전형 압축기 |
US15/554,236 US20180038372A1 (en) | 2015-03-27 | 2016-02-18 | Rotating cylinder type compressor |
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JP2015066056A JP2016186235A (ja) | 2015-03-27 | 2015-03-27 | シリンダ回転型圧縮機 |
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PCT/JP2016/000851 WO2016157688A1 (ja) | 2015-03-27 | 2016-02-18 | シリンダ回転型圧縮機 |
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US (1) | US20180038372A1 (ja) |
JP (1) | JP2016186235A (ja) |
KR (1) | KR101931627B1 (ja) |
CN (1) | CN107532597B (ja) |
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JP2012117476A (ja) * | 2010-12-02 | 2012-06-21 | Denso Corp | 圧縮機 |
JP2014238023A (ja) * | 2013-06-06 | 2014-12-18 | 株式会社デンソー | 回転型圧縮機構 |
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US917994A (en) * | 1908-01-18 | 1909-04-13 | Joseph A Boehringer | Zither-piano. |
US2420124A (en) * | 1944-11-27 | 1947-05-06 | Coulson Charles Chilton | Motor-compressor unit |
JP3561598B2 (ja) | 1997-01-17 | 2004-09-02 | 三洋電機株式会社 | 圧縮機および空気調和機 |
CN1238637C (zh) | 2002-05-22 | 2006-01-25 | 乐金电子(天津)电器有限公司 | 压缩机气缸盖的结构 |
US8790099B2 (en) * | 2008-01-29 | 2014-07-29 | Dafeng Fengtai Fluid Machinery Technology Co., Ltd. | Rotary compressor with synchronous turning between cylinder block and rotor |
CN101978168A (zh) * | 2008-02-18 | 2011-02-16 | 南洋理工大学 | 旋叶式压缩机以及它的制造方法 |
US9080569B2 (en) * | 2009-01-22 | 2015-07-14 | Gregory S. Sundheim | Portable, rotary vane vacuum pump with automatic vacuum breaking arrangement |
JP5757335B2 (ja) * | 2011-10-19 | 2015-07-29 | 富士電機株式会社 | 混入空気除去装置およびこれを備えた発電装置 |
JP5729343B2 (ja) * | 2012-03-29 | 2015-06-03 | 株式会社豊田自動織機 | タンデム式ベーン型圧縮機 |
JP5901446B2 (ja) * | 2012-06-26 | 2016-04-13 | 株式会社デンソー | 回転型圧縮機 |
CN203685335U (zh) * | 2014-02-27 | 2014-07-02 | 南宁昂奇动力科技有限责任公司 | 转子内燃机润滑系统 |
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JP2012117476A (ja) * | 2010-12-02 | 2012-06-21 | Denso Corp | 圧縮機 |
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KR101931627B1 (ko) | 2018-12-21 |
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CN107532597B (zh) | 2019-05-14 |
KR20170098265A (ko) | 2017-08-29 |
CN107532597A (zh) | 2018-01-02 |
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