WO2016084874A1 - Vane type compressor - Google Patents
Vane type compressor Download PDFInfo
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- WO2016084874A1 WO2016084874A1 PCT/JP2015/083162 JP2015083162W WO2016084874A1 WO 2016084874 A1 WO2016084874 A1 WO 2016084874A1 JP 2015083162 W JP2015083162 W JP 2015083162W WO 2016084874 A1 WO2016084874 A1 WO 2016084874A1
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- WIPO (PCT)
- Prior art keywords
- plate
- oil supply
- vane
- insertion member
- side plate
- Prior art date
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Classifications
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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
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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
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
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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
- F04C2240/80—Other components
- F04C2240/805—Fastening means, e.g. bolts
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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
- F04C29/026—Lubricant separation
Definitions
- the present invention relates to a vane type compressor.
- Patent Documents 1 to 3 disclose conventional vane type compressors (hereinafter referred to as compressors). These compressors include a housing, a rotating shaft, a rotor, and a plurality of vanes. A suction pressure region, a cylinder chamber, and a discharge pressure region are formed in the housing.
- the rotation shaft is provided so as to be rotatable around an axis within the housing.
- the rotor is provided so as to be rotatable in synchronization with the rotation shaft in the cylinder chamber.
- a plurality of vane grooves are formed in the rotor. Each vane is provided in the vane groove so that it can appear and disappear.
- a plurality of compression chambers are formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and each vane. Further, a back pressure chamber is formed between the bottom surface of each vane and each vane groove.
- the housing is formed with a back pressure channel that communicates each back pressure chamber and the discharge pressure region. This back pressure channel is provided with a check valve, a pressure regulating valve or a small hole formed in the plug.
- each compression chamber expands and then shrinks.
- the compression chamber sucks the refrigerant gas in the suction pressure region, compresses it, and discharges it to the discharge pressure region.
- the lubricating oil in the discharge pressure region moves to each back pressure chamber through the back pressure flow path, and each back pressure chamber is pressurized.
- each vane is biased toward the inner peripheral surface of the cylinder chamber, and the compression chamber is suitably sealed.
- the lubricating oil is used for lubricating the rotating shaft and the like.
- the back pressure flow path is constituted by a check valve, a pressure regulating valve or a small hole formed in the plug, so the communication area of the back pressure flow path is not sufficiently small, and the power There is still room for improvement in terms of loss reduction.
- the communication area of the back pressure flow path is made smaller to reduce power loss, excessively high accuracy is required for the back pressure flow path, resulting in poor productivity and, consequently, difficult manufacturing cost reduction.
- foreign substances are likely to clog the back pressure flow path.
- the present invention has been made in view of the above-described conventional situation, and provides a vane type compressor capable of realizing reduction in manufacturing cost and improvement in reliability while reliably realizing reduction in power loss. This is a problem to be solved.
- the vane type compressor of the present invention includes a housing in which a discharge pressure region is formed, A cylinder chamber defined by a side plate in the housing; A rotating shaft rotatably provided in the housing; A rotor provided rotatably with the rotary shaft in the cylinder chamber, and formed with a plurality of vane grooves; A vane provided in each vane groove so as to be able to appear and disappear, A plurality of compression chambers are formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and the vanes.
- a back pressure chamber is formed between the bottom surface of each vane and each vane groove, In the discharge pressure region, an oil separation part that separates the lubricating oil from the refrigerant gas discharged from the compression chamber, and an oil storage part that stores the separated lubricating oil are formed,
- the back pressure flow path is formed by a gap between an oil supply hole that is linearly formed on the side plate and opens in the oil storage portion, and an insertion member that is inserted into the oil supply hole.
- the insertion member is formed in a spiral shape by an oil supply groove provided on at least one of the outer peripheral surfaces of the insertion member.
- the back pressure flow path that connects the discharge pressure region and each back pressure chamber is formed in a spiral shape.
- the length of the back pressure channel can be easily increased in a limited space.
- channel is satisfy
- the back pressure flow path composed of the gap between the oil supply hole and the insertion member is compared with the check valve, the pressure regulating valve or the small hole back pressure flow path formed in the plug in the conventional vane type compressor, It can be manufactured easily and stably in large quantities. Furthermore, since the communication area of the back pressure channel does not have to be excessively small, foreign matter is hardly clogged in the back pressure channel, and the reliability of the vane compressor is improved.
- an oil separation part that separates the lubricating oil from the refrigerant gas discharged from the compression chamber and an oil storage part that stores the separated lubricating oil are formed.
- the back pressure channel communicates the oil storage part with each back pressure chamber. For this reason, the oil supply groove is easily filled with the lubricating oil, and the power loss can be reliably reduced.
- the vane type compressor of the present invention can realize reduction in manufacturing cost and improvement in reliability while reliably realizing reduction in power loss.
- each vane in a general vane type compressor, the suction pressure region, each compression chamber, and the discharge pressure region are equalized after a long-term stop, so that when the startup is performed in that state, each vane is in the cylinder chamber. So-called chattering that vibrates without being favorably applied to the peripheral surface is likely to occur. For this reason, many types of vane compressors use a flow path that is different from the back pressure flow path to introduce lubricating oil or refrigerant gas at a discharge pressure that does not pass through the back pressure flow path into the back pressure chamber during startup, thereby preventing chattering. A mechanism is provided.
- the refrigerant gas at the discharge pressure quickly passes through the spiral oil supply groove to prevent chattering.
- the discharge pressure is reduced by the viscosity of the lubricating oil in the oil supply groove, and each back pressure chamber is pressurized. For this reason, it is possible to omit the conventional mechanism for preventing chattering. For this reason, the manufacturing cost can be further reduced.
- the vane type compressor of the present invention it is not necessary to change the shape of the housing greatly in forming the back pressure flow path, and the compressor is not enlarged. For this reason, the compressor can be reduced in size and can be mounted on a vehicle or the like.
- the oiling hole can be formed in a cylindrical shape.
- the insertion member can be a screw member having a male thread and a male thread groove.
- the oil supply groove is preferably a gap between the inner peripheral surface of the oil supply hole and the male screw groove. In this case, the oil supply hole can be easily formed, and the manufacturing cost can be further reduced.
- the side plate includes a first plate that forms a cylinder chamber and a second plate that is in contact with the first plate and has an oil supply hole.
- the first plate forming the cylinder chamber is made hard, or the second plate is made soft so that the oil supply holes can be easily formed in the second plate.
- the second plate can be made of different materials.
- the screw member is preferably for a ball screw.
- the external thread groove has a highly accurate cylindrical shape, the foreign matter is hardly clogged in the oil supply groove, and the compressor can exhibit high durability.
- the gap between the oil supply hole and the insertion member will vary unless the control of the press-fitting allowance is made strict, that is, the communication area of the back pressure flow path will vary. Compressor quality is difficult to stabilize. For this reason, in the vane type compressor of the present invention, it is preferable to insert the insertion member into the oil supply hole with a clearance fit so that the management can be performed more easily than the management of the press-fitting allowance.
- the vane type compressor of the present invention it is preferable that the refrigerant gas at the discharge pressure quickly passes through the oil supply groove and prevents chattering at the time of starting, so the gap between the oil supply hole and the insertion member is compared. Is preferably large. On the other hand, it is preferable that the gap between the oil supply hole and the insertion member becomes small and the power loss can be reduced while the operation is continued after starting.
- the side plate preferably has a hole forming portion in which an oil supply hole is formed. And it is preferable that the hole formation part protrudes in the discharge pressure area
- the hole forming part protrudes into the discharge pressure area, the diameter of the hole forming part is reduced by the high pressure if the discharge pressure area gradually becomes high as the operation continues, and the gap between the oil supply hole and the insertion member is activated. It is possible to make it smaller than time.
- the thermal expansion coefficient of the insertion member is larger than the thermal expansion coefficient of the hole forming portion, the discharge pressure region gradually becomes higher as the operation is continued, so that the insertion member expands larger than the hole forming portion and lubricates. It is possible to make the gap between the hole and the insertion member smaller than at the time of activation.
- the discharge pressure region gradually becomes high as the operation continues, so that the gap adjusting member is in contact with the hole forming portion and the insertion member. It expands, and it is possible to make the gap between the gap adjusting member and the insertion member in the oil supply hole smaller than at the time of activation.
- the second plate When the side plate is composed of the first plate and the second plate, the second plate preferably has a hole forming portion.
- the hole forming portion may be easily reduced in diameter by high pressure by using the second plate as a soft material, or the insertion member may be more easily expanded than the hole forming portion by using the second plate having a small thermal expansion coefficient.
- the wall thickness between the discharge pressure region and the oil supply hole in the hole forming portion is preferably set so that the oil supply hole has a small diameter by the pressure of the refrigerant gas in the discharge pressure region. In this case, the gap between the oil supply hole and the insertion member can be reliably reduced by the pressure of the refrigerant gas.
- the vane type compressor of the present invention can realize a reduction in manufacturing cost while reliably reducing power loss.
- FIG. 1 is a cross-sectional view of the electric vane compressor according to the first embodiment.
- FIG. 2 is a cross-sectional view in the direction perpendicular to the axis of the electric vane compressor according to the first embodiment.
- FIG. 3 is an enlarged cross-sectional view of a main part of the electric vane compressor according to the first embodiment.
- FIG. 4 is an enlarged cross-sectional view of a further main part of the electric vane compressor according to the first embodiment.
- FIG. 5 is an enlarged cross-sectional view of a main part of the electric vane compressor according to the second embodiment.
- FIG. 6 is an enlarged cross-sectional view of a main part of the electric vane compressor according to the third embodiment.
- FIG. 7 is an enlarged cross-sectional view of a main part of the electric vane compressor according to the fourth embodiment.
- FIG. 8 is an enlarged cross-sectional view of a main part of the electric vane compressor according to the fifth embodiment.
- FIG. 9 is an enlarged cross-sectional view of a main part of the electric vane compressor according to the sixth embodiment.
- FIG. 10 is a cross-sectional view of the electric vane compressor according to the seventh embodiment.
- FIG. 11 shows an essential part of the electric vane compressor according to the seventh embodiment, and is an enlarged cross-sectional view taken along the arrow XI in FIG.
- FIG. 12 is an enlarged cross-sectional view similar to FIG. 11, showing the main part of the electric vane compressor according to the eighth embodiment.
- FIG. 13 is an enlarged cross-sectional view similar to FIG. 11, showing the main part of the electric vane compressor according to the ninth embodiment.
- FIG. 14 is an enlarged cross-sectional view of a main part of the electric vane compressor according
- Embodiments 1 to 10 embodying the present invention will be described below with reference to the drawings.
- an electric vane type compressor (hereinafter simply referred to as a compressor) of Embodiment 1 includes a motor housing 1, a motor mechanism 3, first and second side plates 4, 5, and a cylinder block. 7, a cover 9, and a compression mechanism 13.
- the motor housing 1 side is the front
- the cover 9 side is the rear.
- the motor housing 1 extends in the axial direction from the front end side to the rear end side, has a bottomed cylindrical shape in which the front end side is closed by the bottom wall 1a and has an opening 1b on the rear end side.
- the motor housing 1 forms a motor chamber 1c that also serves as a suction pressure region.
- the motor housing 1 has a cylindrical portion 1d having a cylindrical shape and a bulging portion 1e bulging outward from the cylindrical portion 1d.
- the motor housing 1 is formed with a suction port 1f that communicates the outside with the motor chamber 1c.
- An evaporator 6 a of a vehicle air conditioner is connected to the suction port 1 f by a pipe 6.
- the evaporator 6 a is connected to the expansion valve 6 b by the pipe 6, and the expansion valve 6 b is connected to the condenser 6 c by the pipe 6.
- the motor mechanism 3 has a stator 15 and a motor rotor 17 in the motor chamber 1c.
- the stator 15 is fixed to the inner peripheral surface of the motor housing 1.
- An airtight terminal 16 capable of maintaining the motor chamber 1c in an airtight manner is provided in the bulging portion 1e of the motor housing 1 in the axial direction.
- the outer end of each hermetic terminal 16 is connected to a power supply device (not shown), and the inner end of each hermetic terminal 16 is connected to the stator 15 via the cluster block 2 by a lead wire 16a.
- the motor rotor 17 is inserted through a rotating shaft 19 extending in the axial direction and is disposed in the stator 15.
- a shaft support portion 1g is projected in the axial direction on the bottom wall 1a of the motor housing 1, and a bearing device 21 is provided on the shaft support portion 1g.
- a cover 9 is fixed to the rear end of the motor housing 1 by a plurality of bolts and nuts (not shown).
- the cover 9 has a bottomed cylindrical shape whose rear end is closed by a bottom wall 9d and has an opening 9e on the front end.
- the opening 9e of the cover 9 contacts the opening 1b of the motor housing 1, and the motor housing 1 and the cover 9 are closed.
- a flat plate-like first side plate 4 extending in the radial direction orthogonal to the axial direction is fitted to the opening 9 e side of the cover 9.
- An O-ring 23 is provided between the outer peripheral surface of the first side plate 4 and the inner peripheral surface of the cover 9.
- the first side plate 4 is provided with a shaft hole 4a through which the rotary shaft 19 is inserted.
- the shaft hole 4a is formed with a plating (not shown) for suitably sliding the rotating shaft 19.
- a flat plate-like second side plate 5 extending in the radial direction perpendicular to the axial direction is fitted in the substantially center of the cover 9.
- An O-ring 24 is provided between the outer peripheral surface of the second side plate 5 and the inner peripheral surface of the cover 9.
- the second side plate 5 is provided with a shaft hole 5a through which the rotary shaft 19 is inserted.
- the shaft hole 5a is formed with a plating (not shown) for suitably sliding the rotary shaft 19.
- the rear end portion of the rotary shaft 19 is pivotally supported by the shaft hole 5a.
- the rotating shaft 19 is pivotally supported by the shaft hole 4a of the first side plate 4 and the shaft hole 5a of the second side plate 5, and can be suitably rotated.
- the cylinder block 7 is fixed between the first side plate 4 and the second side plate 5 by a plurality of bolts 25 (see FIG. 2).
- the cylinder block 7 extends in a cylindrical shape in the axial direction.
- the cylinder block 7 is fixed to the first and second side plates 4 and 5, thereby forming a cylinder chamber 31 together with the first and second side plates 4 and 5.
- the cylinder chamber 31 has a perfect circular cross-sectional shape perpendicular to the axial direction.
- the axis of the cylinder chamber 31 is eccentric from the axis O.
- plating (not shown) that suitably slides the rotor 45 and the vanes 47a and 47b is formed on the front surface on the front end side, the inner peripheral surface, and the rear surface on the rear end side of the cylinder chamber 31, plating (not shown) that suitably slides the rotor 45 and the vanes 47a and 47b is formed.
- the first side plate 4 is formed with a suction passage 33a that opens in the axial direction and communicates with the motor chamber 1c.
- the cylinder block 7 is formed with a suction passage 33b communicating with the suction passage 33a.
- the suction passage 33 b communicates with the cylinder chamber 31 through a suction port 33 c that is recessed from the outer peripheral surface of the cylinder chamber 31.
- the cylinder block 7 is provided with a discharge space 37 that opens to the outer peripheral side.
- the discharge space 37 communicates with the cylinder chamber 31 through a discharge port 37 a that is recessed from the inner peripheral surface of the cylinder chamber 31.
- a discharge reed valve 39 that opens and closes the discharge port 37 a and a retainer 41 that regulates the opening degree of the discharge reed valve 39 are fixed to the cylinder block 7 by bolts 43.
- the rotor 45 is rotatably provided by the rotary shaft 19.
- the rotor 45 is press-fitted or key-connected to the rotary shaft 19.
- the rotor 45 has a perfect circle in cross section perpendicular to the axial direction.
- the axis of the rotor 45 coincides with the axis O.
- the rotor 45 has two vane grooves 45a and 45b.
- the vane grooves 45a and 45b are parallel to a virtual reference plane including the axis O.
- Flat vanes 47a and 47b are provided in the vane grooves 45a and 45b so as to be able to appear and disappear.
- Back pressure chambers 49a and 49b are provided between the bottom surfaces of the vanes 47a and 47b and the vane grooves 45a and 45b, respectively.
- the rotor 45 and the vanes 47a and 47b constitute the compression mechanism 13 (see FIG. 1).
- Two compression chambers 50a and 50b are formed by the front surface of the cylinder chamber 31, the inner peripheral surface of the cylinder chamber 31, the rear surface of the cylinder chamber 31, the outer peripheral surface of the rotor 45, and the vanes 47a and 47b.
- annular groove 4 b is recessed around the axis O on the rear surface of the first side plate 4. Further, an annular groove 5p that faces the annular groove 4b in the front-rear direction is recessed around the axis O on the front surface of the second side plate 5.
- a discharge chamber 9 a that is a discharge pressure region is formed between the cover 9 and the second side plate 5.
- the cover 9 is formed with a discharge port 9b that communicates the outside with the discharge chamber 9a.
- a condenser 6c of a vehicle air conditioner is connected to the discharge port 9b by a pipe.
- a block 35 is fixed to the second side plate 5.
- the block 35 is formed with an oil separation portion 35a that has a cylindrical shape and extends in a direction intersecting the axis O.
- a cylindrical tube member 53 is fixed to the oil separation portion 35a.
- the upper end of the cylindrical member 53 is opened to the discharge chamber 9a, and the lower end of the oil separation part 35a is opened to the discharge chamber 9a by the oil discharge port 35b.
- the oil separator is constituted by the oil separation portion 35a and the cylindrical member 53.
- the lower part of the discharge chamber 9a is an oil storage part 35c that stores the lubricating oil separated by the oil separation part 35a.
- discharge passages 5b and 35e that connect the discharge space 37 to the oil separation portion 35a are formed.
- the second side plate 5 is formed with a first passage 5d that communicates with the oil groove 9c and extends upward so as to approach the axis O. Further, the second side plate 5 is formed with a second passage 5e that connects the oil supply chamber 55 and the upper end of the first passage 5d, and a third passage 5f that connects the oil supply chamber 55 and the annular groove 5p. Yes.
- the first passage 5d is formed in a cylindrical shape.
- the first passage 5d corresponds to the oil supply hole of the present invention.
- An insertion member 57 is inserted into the first passage 5d by press fitting or gap fitting. In the case of gap fitting, the gap between the insertion member 57 and the inner peripheral surface of the first passage 5d is sealed with lubricating oil.
- the insertion member 57 is prevented from coming off by a circlip 58 with its distal end in contact with the upper end of the first passage 5 d.
- the insertion member 57 is a screw member for a ball screw having a male screw thread 57a and a male screw groove 57b.
- the top surface of the screw thread 57a of the insertion member 57 abuts against the inner peripheral surface of the first passage 5d, and the screw groove 57b of the insertion member 57 and the first groove 57b A gap 57c is secured between the inner peripheral surface of the passage 5d.
- the male screw groove 57b corresponds to the oil supply groove of the present invention.
- the cut of the circlip 58 allows the gap 57c to communicate with the oil storage part 35c.
- the gap 57c, the second passage 5e, the oil supply chamber 55, and the third passage 5f in the first passage 5d correspond to the back pressure passage of the present invention.
- each compression chamber 50a, 50b repeats expansion and contraction of the volume.
- each compression chamber 50a, 50b performs a suction stroke for sucking low-pressure refrigerant gas from the motor chamber 1c through the suction passages 33a, 33b and the suction port 33c.
- a compression stroke is performed in which the refrigerant gas is compressed in the compression chambers 50a and 50b.
- a discharge stroke is performed in which high-pressure refrigerant gas in the compression chambers 50a and 50b is discharged to the discharge chamber 9a through the discharge port 37a, the discharge space 37, and the discharge passages 5b and 35e.
- the air conditioning of the passenger compartment is performed.
- the lubricating oil is separated from the high-pressure refrigerant gas discharged from the discharge passages 5b and 35e into the oil separation portion 35a by centrifugal force.
- the lubricating oil is stored in an oil storage part 35c below the discharge chamber 9a. Since the inside of the discharge chamber 9a has a high pressure, the lubricating oil is supplied to the annular groove 5p through the oil groove 9c, the gap 57c of the first passage 5d, the second passage 5e, the oil supply chamber 55, and the third passage 5f. . Since the annular groove 5p communicates with the back pressure chambers 49a and 49b, it applies a back pressure to the vanes 47a and 47b. For this reason, the vanes 47a and 47b are suitably biased to the inner peripheral surface of the cylinder chamber 31, and work is performed with high compression efficiency.
- the back pressure flow path connecting the discharge chamber 9a and the back pressure chambers 49a, 49b has a gap 57c, and the gap 57c is spiral. Is formed.
- the gap 57c between the first passage 5d and the insertion member 57 is easier and more stable than a check valve, a pressure regulating valve, or a small back pressure flow passage formed in a plug in a known compressor. Can be produced in large quantities.
- the compressor when the compressor is started after being stopped for a long time, the refrigerant circuit of the vehicle air conditioner connected to the compressor by the pipe 6 is equalized, and the lubricating oil is exhausted from the oil storage portion 35c.
- the refrigerant gas having the discharge pressure quickly passes through the spiral gap 57c to quickly increase the pressure in the back pressure chambers 49a and 49b, thereby preventing chattering.
- the lubricating oil in the refrigerant circuit After startup, the lubricating oil in the refrigerant circuit is sucked together with the refrigerant gas and reaches the discharge chamber 9a.
- the spiral gap 57c is filled with the lubricating oil, and the discharge pressure is reduced by the viscosity of the lubricating oil in the gap 57c.
- the back pressure chambers 49a and 49b are pressurized. For this reason, it is possible to omit the conventional mechanism for preventing chattering. Further, since the spiral gap 57c can form a long-distance passage while keeping the communication area small, it can quickly pass through the refrigerant gas and also functions as a throttle for the lubricating oil. It is the best to let you.
- this compressor can realize a reduction in manufacturing cost while reliably reducing power loss.
- the compressor since the thickness of the 2nd side plate 5 which forms an oil supply hole can be made thin, it is not necessary to change the shapes of the motor housing 1, the cover 9, etc. significantly, and a compressor enlarges. Nor. For this reason, the compressor can be reduced in size and can be mounted on a vehicle or the like.
- the first passage 5d is formed in a columnar shape and the insertion member 57 is a screw member, it is easy to form an oil supply hole, and the manufacturing cost can be further reduced.
- the insertion member 57 is a screw member for a ball screw
- the male screw groove 57b has a highly accurate cylindrical shape. For this reason, it is difficult for foreign matter to be clogged in the gap 57c, and the compressor can exhibit high durability.
- Example 2 In the compressor according to the second embodiment, as illustrated in FIG. 5, the gap 257 c is formed by the first passage 5 d and the outer peripheral surface of the insertion member 257.
- the insertion member 257 is a fastening screw member having a male thread 257a and a male thread groove 257b.
- a linear groove 257d extending in the diametrical direction is recessed in the lower end surface of the insertion member 257.
- the groove 257d allows the gap 257c to communicate with the oil storage part 35c.
- Other configurations are the same as those of the first embodiment. Also in this compressor, the same effect as Example 1 can be produced.
- Example 3 In the compressor of the third embodiment, as shown in FIG. 6, an insertion member 357 having a male thread 357a and a male thread groove 357b is screwed into the first passage 35d having the female thread groove 5g.
- the insertion member 357 is also a fastening screw member.
- the gap 357c is formed by the first passage 35d and the male thread 357b of the insertion member 357.
- Other configurations are the same as those of the first embodiment. Also in this compressor, the same effect as Example 1 can be produced.
- Example 4 In the compressor of the fourth embodiment, as shown in FIG. 7, an insertion member 457 having a male thread 457a and a male thread groove 457b is screwed into the first passage 45d having the female thread groove 5h.
- the insertion member 457 is also a fastening screw member.
- the gap 457c is formed by the first passage 45d and the male thread 457b of the insertion member 457.
- Other configurations are the same as those of the first embodiment. Also in this compressor, the same effect as Example 1 can be produced.
- Example 5 In the compressor of the fifth embodiment, as shown in FIG. 8, the insertion member 557 having the male thread 557a and the male thread groove 557b is screwed into the first passage 55d having the female thread 5i and the female thread groove 5j. is doing.
- the insertion member 557 is also a fastening screw member.
- the gap 557c is formed by the female thread groove 5j of the first passage 55d and the female thread 557a of the insertion member 557.
- Other configurations are the same as those of the first embodiment. Also in this compressor, the same effect as Example 1 can be produced.
- Example 6 In the compressor of the sixth embodiment, as shown in FIG. 9, the insertion member 657 having the male thread 657a and the female thread groove 657b is screwed into the first passage 65d having the female thread 5k and the female thread groove 5l. is doing.
- the insertion member 657 is also a fastening screw member.
- the gap 657c is formed by the female thread 5l of the first passage 65d and the thread 657a of the insertion member 657
- the gap 657d is formed by the thread 5k of the first passage 65d and the thread 657b of the insertion member 657.
- Other configurations are the same as those of the first embodiment. Also in this compressor, the same effect as Example 1 can be produced.
- Example 7 In the compressor of Example 7, the second side plate 61 is employed as shown in FIG.
- the second side plate 61 includes a first plate 62 that forms the cylinder chamber 31 and a second plate 63 that comes into contact with the first plate 62.
- the first plate 62 is for forming the cylinder chamber 31 and is therefore harder than the second plate 63. Plating is formed on the front surface of the first plate 62.
- the second plate 63 is formed with a columnar hole forming portion 63a extending upward from the lower end. Grooves 63b and 63c extending upward from the lower end are formed on both sides of the hole forming portion 63a, and the hole forming portion 63a entirely protrudes into the discharge chamber 9a except for the front surface thereof.
- the hole forming portion 63a is formed with a columnar first passage 5s that communicates with the oil groove 9c and extends upward so as to approach the axis O. Since the second plate 63 is soft, it is easy to form the first passage 5s.
- the first passage 5s is formed slightly behind the front surface.
- an insertion member 57 is inserted by a clearance fit.
- the thermal expansion coefficient of the insertion member 57 is larger than the thermal expansion coefficient of the hole forming portion 63a.
- the second plate 63 is formed with an oil separation part 35a, which also functions as the block 35 of the first embodiment.
- Other configurations are the same as those of the compressor of the first embodiment.
- the refrigerant gas at the discharge pressure can quickly pass through the gap 57c and prevent chattering when starting up. it can.
- the second plate 63 is soft, the diameter of the hole forming portion 63a is easily reduced by a high pressure.
- the first passage 5s is formed slightly behind the front surface, the thickness between the discharge chamber 9a and the first passage 5s in the hole forming portion 63a depends on the pressure of the refrigerant gas in the discharge chamber 9a. The first passage 5s surely has a small diameter.
- the second plate 64 is employed in the compressor of the eighth embodiment, as shown in FIG. 12, the second plate 64 is employed.
- the second plate 64 is formed with a hole forming portion 64a extending in a cylindrical shape from the lower end to the upper side.
- the hole forming portion 64 a is formed away from the rear end surface of the first plate 62.
- Other configurations are the same as those of the seventh embodiment.
- This compressor can achieve the same effects as those of the seventh embodiment. Furthermore, since the pressure of the refrigerant gas in the discharge chamber 9a can be evenly received over the entire circumference of the cylindrical hole forming portion 64a, the first passage 5s can be reduced in diameter without deviation, and stable quality can be ensured. it can.
- Example 9 In the compressor of the ninth embodiment, the second plate 66 is adopted as shown in FIG.
- the second plate 66 is formed with a hole forming portion 66a extending in a quadrangular prism shape upward from the lower end.
- Other configurations are the same as those of the seventh embodiment. Also in this compressor, the same effect as Example 7 can be produced.
- the grooves 63a and 63b on both sides of the hole forming portion 66a may or may not be present. If the grooves 63a and 63b are provided, the pressure of the refrigerant gas in the discharge chamber 9a acts from the rear surface and both side surfaces, and the first passage 5s can be more preferably reduced in diameter.
- a cylindrical gap adjusting member 67 is provided between the first passage 5 s and the insertion member 57.
- the gap adjusting member 67 has a thermal expansion coefficient larger than that of the hole forming portion 63a.
- Other configurations are the same as those of the seventh embodiment.
- the gap adjusting member 67 is provided between the first passage 5s and the insertion member 57, the discharge adjusting chamber 9a gradually increases in temperature as the operation continues, so that the gap adjusting member 67 becomes a hole. It is possible to expand the forming portion 63a and the insertion member 57, and to make the gap 57c between the gap adjustment member 67 and the insertion member 57 in the first passage 5s smaller than at the time of activation. Other functions and effects are the same as those of the seventh embodiment.
- the present invention has been described with reference to the first to tenth embodiments.
- the present invention is not limited to the first to tenth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.
- Example 1 a screw member for a ball screw manufactured by rolling is used as the insertion member 57, but a screw member for a ball screw manufactured by cutting or the like can also be used.
- the insertion member and the screw member are not limited to metal, and may be made of resin or the like.
- the first passages 5d, 35d, 45d, 55d, 65d, and 5s are used as oil supply holes.
- the second and third passages 5e and 5f are used as oil supply holes to form an oil supply groove. Is also possible.
- a sliding bearing or a rolling bearing can be adopted between the rotating shaft 19 and the shaft holes 4a and 5a in addition to plating.
- the cross-sectional shape orthogonal to the axial direction of the cylinder chamber 31 is not limited to a perfect circle.
- the present invention can be used for an air conditioner for vehicles.
- Cylinder chamber 9a Discharge pressure area (discharge chamber) 1, 4, 7, 5, 9 ... housing (1 ... motor housing, 4 ... first side plate, 7 ... cylinder block, 5, 61 ... second side plate, 9 ... cover) O ... Axis center 19 ... Rotating shaft 45a, 45b ... Vane groove 45 ... Rotor 47a, 47b ... Vane 50a, 50b ... Compression chamber 49a, 49b ... Back pressure chamber 5d, 57c, 5e, 5f ... Back pressure channel (5d, 35d) 45d, 55d, 65d, 5s ... first passage, oil supply holes, 57c, 257c, 357c, 457c, 557c, 657c, 657d ...
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Abstract
Description
前記ハウジング内にサイドプレートによって区画されたシリンダ室と、
前記ハウジング内に回転可能に設けられた回転軸と、
前記シリンダ室内で前記回転軸と回転可能に設けられ、複数個のベーン溝が形成されたロータと、
前記各ベーン溝に各々出没可能に設けられるベーンとを備え、
前記シリンダ室の一面、前記シリンダ室の内周面、前記シリンダ室の他面、前記ロータの外周面及び前記各ベーンによって複数個の圧縮室が形成され、
前記各ベーンの底面と前記各ベーン溝との間が背圧室とされ、
前記吐出圧領域内には、前記圧縮室から吐出される冷媒ガスから潤滑油を分離する油分離部と、分離された潤滑油を貯留する貯油部とが形成され、
前記ハウジングには、前記貯油部と前記各背圧室とを連通する背圧流路が形成されたベーン型圧縮機において、
前記背圧流路は、前記サイドプレートに直線状に形成されて前記貯油部に開口する給油孔と、前記給油孔に挿入される挿入部材との間隙からなり、前記給油孔の内周面及び前記挿入部材の外周面の少なくとも一方に設けられた給油溝によって螺旋状に形成されていることを特徴とする。 The vane type compressor of the present invention includes a housing in which a discharge pressure region is formed,
A cylinder chamber defined by a side plate in the housing;
A rotating shaft rotatably provided in the housing;
A rotor provided rotatably with the rotary shaft in the cylinder chamber, and formed with a plurality of vane grooves;
A vane provided in each vane groove so as to be able to appear and disappear,
A plurality of compression chambers are formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and the vanes.
A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
In the discharge pressure region, an oil separation part that separates the lubricating oil from the refrigerant gas discharged from the compression chamber, and an oil storage part that stores the separated lubricating oil are formed,
In the housing, in the vane type compressor in which a back pressure flow path communicating the oil storage part and the back pressure chambers is formed,
The back pressure flow path is formed by a gap between an oil supply hole that is linearly formed on the side plate and opens in the oil storage portion, and an insertion member that is inserted into the oil supply hole. The insertion member is formed in a spiral shape by an oil supply groove provided on at least one of the outer peripheral surfaces of the insertion member.
実施例1の電動ベーン型圧縮機(以下、単に圧縮機という。)は、図1に示すように、モータハウジング1と、モータ機構3と、第1、2サイドプレート4、5と、シリンダブロック7と、カバー9と、圧縮機構13とを備えている。以下、図1において、モータハウジング1側を前方とし、カバー9側を後方とする。 (Example 1)
As shown in FIG. 1, an electric vane type compressor (hereinafter simply referred to as a compressor) of
実施例2の圧縮機では、図5に示すように、間隙257cは第1通路5dと挿入部材257の外周面とにより形成されている。挿入部材257はおねじ山257aとおねじ溝257bとを有する締結用のねじ部材である。挿入部材257の下端面には、直径方向に延びる直線状の溝257dが凹設されている。溝257dは間隙257cを貯油部35cに連通させている。他の構成は実施例1と同様である。この圧縮機においても、実施例1と同様の作用効果を奏することができる。 (Example 2)
In the compressor according to the second embodiment, as illustrated in FIG. 5, the
実施例3の圧縮機では、図6に示すように、めねじ溝5gを有する第1通路35dに対し、おねじ山357aとおねじ溝357bとを有する挿入部材357を螺合している。挿入部材357も締結用のねじ部材である。間隙357cは第1通路35dと挿入部材357のおねじ溝357bとにより形成されている。他の構成は実施例1と同様である。この圧縮機においても、実施例1と同様の作用効果を奏することができる。 (Example 3)
In the compressor of the third embodiment, as shown in FIG. 6, an
実施例4の圧縮機では、図7に示すように、めねじ溝5hを有する第1通路45dに対し、おねじ山457aとおねじ溝457bとを有する挿入部材457を螺合している。挿入部材457も締結用のねじ部材である。間隙457cは第1通路45dと挿入部材457のおねじ溝457bとにより形成されている。他の構成は実施例1と同様である。この圧縮機においても、実施例1と同様の作用効果を奏することができる。 Example 4
In the compressor of the fourth embodiment, as shown in FIG. 7, an
実施例5の圧縮機では、図8に示すように、めねじ山5i及びめねじ溝5jを有する第1通路55dに対し、おねじ山557aとおねじ溝557bとを有する挿入部材557を螺合している。挿入部材557も締結用のねじ部材である。間隙557cは第1通路55dのめねじ溝5jと挿入部材557のおねじ山557aとにより形成されている。他の構成は実施例1と同様である。この圧縮機においても、実施例1と同様の作用効果を奏することができる。 (Example 5)
In the compressor of the fifth embodiment, as shown in FIG. 8, the
実施例6の圧縮機では、図9に示すように、めねじ山5k及びめねじ溝5lを有する第1通路65dに対し、おねじ山657aとおねじ溝657bとを有する挿入部材657を螺合している。挿入部材657も締結用のねじ部材である。間隙657cは第1通路65dのめねじ溝5lと挿入部材657のおねじ山657aとにより形成され、間隙657dは第1通路65dのおねじ山5kと挿入部材657のおねじ溝657bとにより形成されている。他の構成は実施例1と同様である。この圧縮機においても、実施例1と同様の作用効果を奏することができる。 (Example 6)
In the compressor of the sixth embodiment, as shown in FIG. 9, the
実施例7の圧縮機では、図10に示すように、第2サイドプレート61を採用している。第2サイドプレート61は、シリンダ室31を形成する第1プレート62と、第1プレート62と当接される第2プレート63とからなる。 (Example 7)
In the compressor of Example 7, the
実施例8の圧縮機では、図12に示すように、第2プレート64を採用している。第2プレート64には、下端から上方に向かって円柱状に延びる孔形成部64aが形成されている。孔形成部64aは第1プレート62の後端面と離間して形成されている。他の構成は実施例7と同様である。 (Example 8)
In the compressor of the eighth embodiment, as shown in FIG. 12, the
実施例9の圧縮機では、図13に示すように、第2プレート66を採用している。第2プレート66には、下端から上方に向かって四角柱状に延びる孔形成部66aが形成されている。他の構成は実施例7と同様である。この圧縮機においても、実施例7と同様の作用効果を奏することができる。 Example 9
In the compressor of the ninth embodiment, the
実施例10の圧縮機では、図14に示すように、第1通路5sと挿入部材57との間に円筒状の間隙調整部材67が設けられている。間隙調整部材67は、孔形成部63aの熱膨張係数よりも熱膨張係数が大きい。他の構成は実施例7と同様である。 (Example 10)
In the compressor according to the tenth embodiment, as illustrated in FIG. 14, a cylindrical
9a…吐出圧領域(吐出室)
1、4、7、5、9…ハウジング(1…モータハウジング、4…第1サイドプレート、7…シリンダブロック、5、61…第2サイドプレート、9…カバー)
O…軸心
19…回転軸
45a、45b…ベーン溝
45…ロータ
47a、47b…ベーン
50a、50b…圧縮室
49a、49b…背圧室
5d、57c、5e、5f…背圧流路(5d、35d、45d、55d、65d、5s…第1通路、給油孔、57c、257c、357c、457c、557c、657c、657d…間隙、給油溝、5e…第2通路、5f…第3通路)
57…挿入部材
35a…油分離部
57a、257a、357a、457a、557a、657a…おねじ山
57b、257b、357b、457b、557b、657b…おねじ溝
62…第1プレート
63、64、66…第2プレート
63a、64a66a…孔形成部
67…間隙調整部材 31 ...
1, 4, 7, 5, 9 ... housing (1 ... motor housing, 4 ... first side plate, 7 ... cylinder block, 5, 61 ... second side plate, 9 ... cover)
O ...
57 ...
Claims (10)
- 吐出圧領域が形成されたハウジングと、
前記ハウジング内にサイドプレートによって区画されたシリンダ室と、
前記ハウジング内に回転可能に設けられた回転軸と、
前記シリンダ室内で前記回転軸と回転可能に設けられ、複数個のベーン溝が形成されたロータと、
前記各ベーン溝に各々出没可能に設けられるベーンとを備え、
前記シリンダ室の一面、前記シリンダ室の内周面、前記シリンダ室の他面、前記ロータの外周面及び前記各ベーンによって複数個の圧縮室が形成され、
前記各ベーンの底面と前記各ベーン溝との間が背圧室とされ、
前記吐出圧領域内には、前記圧縮室から吐出される冷媒ガスから潤滑油を分離する油分離部と、分離された潤滑油を貯留する貯油部とが形成され、
前記ハウジングには、前記貯油部と前記各背圧室とを連通する背圧流路が形成されたベーン型圧縮機において、
前記背圧流路は、前記サイドプレートに直線状に形成されて前記貯油部に開口する給油孔と、前記給油孔に挿入される挿入部材との間隙からなり、前記給油孔の内周面及び前記挿入部材の外周面の少なくとも一方に設けられた給油溝によって螺旋状に形成されていることを特徴とするベーン型圧縮機。 A housing in which a discharge pressure region is formed;
A cylinder chamber defined by a side plate in the housing;
A rotating shaft rotatably provided in the housing;
A rotor provided rotatably with the rotary shaft in the cylinder chamber, and formed with a plurality of vane grooves;
A vane provided in each vane groove so as to be able to appear and disappear,
A plurality of compression chambers are formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and the vanes.
A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
In the discharge pressure region, an oil separation part that separates the lubricating oil from the refrigerant gas discharged from the compression chamber, and an oil storage part that stores the separated lubricating oil are formed,
In the housing, in the vane type compressor in which a back pressure flow path communicating the oil storage part and the back pressure chambers is formed,
The back pressure flow path is formed by a gap between an oil supply hole that is linearly formed on the side plate and opens in the oil storage portion, and an insertion member that is inserted into the oil supply hole. A vane type compressor characterized in that it is formed in a spiral shape by an oil supply groove provided on at least one of the outer peripheral surfaces of the insertion member. - 前記給油孔は円柱状に形成され、
前記挿入部材は、おねじ山とおねじ溝とを有するねじ部材であり、
前記給油溝は、前記給油孔の内周面と前記おねじ溝との前記間隙である請求項1記載のベーン型圧縮機。 The oil supply hole is formed in a cylindrical shape,
The insertion member is a screw member having a male thread and a male thread groove,
The vane type compressor according to claim 1, wherein the oil supply groove is the gap between an inner peripheral surface of the oil supply hole and the male screw groove. - 前記サイドプレートは、前記シリンダ室を形成する第1プレートと、前記第1プレートと当接され、前記給油孔が形成された第2プレートとからなる請求項1又は2記載のベーン型圧縮機。 3. The vane type compressor according to claim 1, wherein the side plate includes a first plate that forms the cylinder chamber, and a second plate that is in contact with the first plate and has the oil supply hole.
- 前記ねじ部材はボールねじ用のものである請求項2記載のベーン型圧縮機。 The vane compressor according to claim 2, wherein the screw member is for a ball screw.
- 前記サイドプレートは前記給油孔が形成された孔形成部を有し、
前記孔形成部は前記吐出圧領域内に突出している請求項1又は2記載のベーン型圧縮機。 The side plate has a hole forming portion in which the oil supply hole is formed,
The vane compressor according to claim 1 or 2, wherein the hole forming portion projects into the discharge pressure region. - 前記サイドプレートは、前記シリンダ室を形成する第1プレートと、前記第1プレートと当接され、前記給油孔が形成された第2プレートとからなり、
前記第2プレートが前記孔形成部を有する請求項4記載のベーン型圧縮機。 The side plate includes a first plate that forms the cylinder chamber, and a second plate that is in contact with the first plate and in which the oil supply hole is formed.
The vane type compressor according to claim 4, wherein the second plate has the hole forming portion. - 前記サイドプレートは前記給油孔が形成された孔形成部を有し、
前記挿入部材の熱膨張係数は前記孔形成部の熱膨張係数よりも大きい請求項1又は2記載のベーン型圧縮機。 The side plate has a hole forming portion in which the oil supply hole is formed,
The vane type compressor according to claim 1 or 2, wherein a thermal expansion coefficient of the insertion member is larger than a thermal expansion coefficient of the hole forming portion. - 前記サイドプレートは、前記シリンダ室を形成する第1プレートと、前記第1プレートと当接され、前記給油孔が形成された第2プレートとからなり、
前記第2プレートが前記孔形成部を有する請求項7記載のベーン型圧縮機。 The side plate includes a first plate that forms the cylinder chamber, and a second plate that is in contact with the first plate and in which the oil supply hole is formed.
The vane type compressor according to claim 7, wherein the second plate has the hole forming portion. - 前記サイドプレートは前記給油孔が形成された孔形成部を有し、
前記給油孔と前記挿入部材との間には、前記孔形成部の熱膨張係数よりも熱膨張係数が大きい間隙調整部材が設けられている請求項1又は2記載のベーン型圧縮機。 The side plate has a hole forming portion in which the oil supply hole is formed,
The vane type compressor according to claim 1 or 2, wherein a gap adjusting member having a thermal expansion coefficient larger than a thermal expansion coefficient of the hole forming portion is provided between the oil supply hole and the insertion member. - 前記サイドプレートは、前記シリンダ室を形成する第1プレートと、前記第1プレートと当接され、前記給油孔が形成された第2プレートとからなり、
前記第2プレートが前記孔形成部を有する請求項9記載のベーン型圧縮機。 The side plate includes a first plate that forms the cylinder chamber, and a second plate that is in contact with the first plate and in which the oil supply hole is formed.
The vane type compressor according to claim 9, wherein the second plate has the hole forming portion.
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CN201580064566.3A CN107002677A (en) | 2014-11-28 | 2015-11-26 | Blade-tape compressor |
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---|---|---|---|---|
WO2018008553A1 (en) * | 2016-07-07 | 2018-01-11 | カルソニックカンセイ株式会社 | Electric compressor |
WO2018123860A1 (en) * | 2016-12-27 | 2018-07-05 | 株式会社ヴァレオジャパン | Oil supply structure for vane compressor |
US20230137074A1 (en) * | 2021-10-28 | 2023-05-04 | Lg Electronics Inc. | Vane rotary compressor |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR102454723B1 (en) * | 2021-03-19 | 2022-10-14 | 엘지전자 주식회사 | Rotary compressor |
Citations (4)
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JPS58158185U (en) * | 1982-04-16 | 1983-10-21 | 株式会社日立製作所 | Rotary vane compressor |
JPS5954793A (en) * | 1982-09-21 | 1984-03-29 | Matsushita Electric Ind Co Ltd | Compressor |
JPS60107384U (en) * | 1983-12-22 | 1985-07-22 | 株式会社豊田自動織機製作所 | vane compressor |
JP2014125957A (en) * | 2012-12-26 | 2014-07-07 | Toyota Industries Corp | Scroll type compressor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006226117A (en) * | 2005-02-15 | 2006-08-31 | Calsonic Compressor Inc | Gas compressor |
CN101469705A (en) * | 2007-12-26 | 2009-07-01 | 上海三电贝洱汽车空调有限公司 | Rotary vane type compressor |
-
2015
- 2015-11-26 DE DE112015005352.2T patent/DE112015005352T5/en not_active Withdrawn
- 2015-11-26 KR KR1020177017502A patent/KR20170091666A/en active Search and Examination
- 2015-11-26 JP JP2016561930A patent/JPWO2016084874A1/en active Pending
- 2015-11-26 WO PCT/JP2015/083162 patent/WO2016084874A1/en active Application Filing
- 2015-11-26 CN CN201580064566.3A patent/CN107002677A/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58158185U (en) * | 1982-04-16 | 1983-10-21 | 株式会社日立製作所 | Rotary vane compressor |
JPS5954793A (en) * | 1982-09-21 | 1984-03-29 | Matsushita Electric Ind Co Ltd | Compressor |
JPS60107384U (en) * | 1983-12-22 | 1985-07-22 | 株式会社豊田自動織機製作所 | vane compressor |
JP2014125957A (en) * | 2012-12-26 | 2014-07-07 | Toyota Industries Corp | Scroll type compressor |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018008553A1 (en) * | 2016-07-07 | 2018-01-11 | カルソニックカンセイ株式会社 | Electric compressor |
WO2018123860A1 (en) * | 2016-12-27 | 2018-07-05 | 株式会社ヴァレオジャパン | Oil supply structure for vane compressor |
US20230137074A1 (en) * | 2021-10-28 | 2023-05-04 | Lg Electronics Inc. | Vane rotary compressor |
US11644035B1 (en) * | 2021-10-28 | 2023-05-09 | Lg Electronics Inc. | Vane rotary compressor |
Also Published As
Publication number | Publication date |
---|---|
KR20170091666A (en) | 2017-08-09 |
DE112015005352T5 (en) | 2017-08-10 |
CN107002677A (en) | 2017-08-01 |
JPWO2016084874A1 (en) | 2017-04-27 |
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