WO2022211331A1 - 로터리 압축기 - Google Patents
로터리 압축기 Download PDFInfo
- Publication number
- WO2022211331A1 WO2022211331A1 PCT/KR2022/003801 KR2022003801W WO2022211331A1 WO 2022211331 A1 WO2022211331 A1 WO 2022211331A1 KR 2022003801 W KR2022003801 W KR 2022003801W WO 2022211331 A1 WO2022211331 A1 WO 2022211331A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- vane
- oil supply
- supply groove
- compression
- face
- Prior art date
Links
- 230000006835 compression Effects 0.000 claims abstract description 216
- 238000007906 compression Methods 0.000 claims abstract description 216
- 238000007789 sealing Methods 0.000 claims description 22
- 238000000034 method Methods 0.000 claims description 20
- 230000000149 penetrating effect Effects 0.000 claims 2
- 239000003921 oil Substances 0.000 description 399
- 230000002093 peripheral effect Effects 0.000 description 34
- 238000005461 lubrication Methods 0.000 description 22
- 239000003507 refrigerant Substances 0.000 description 22
- 230000000694 effects Effects 0.000 description 17
- 230000001965 increasing effect Effects 0.000 description 11
- 230000001050 lubricating effect Effects 0.000 description 6
- 230000004323 axial length Effects 0.000 description 4
- 230000000087 stabilizing effect Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 239000010726 refrigerant oil Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 206010000117 Abnormal behaviour Diseases 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 235000014676 Phragmites communis Nutrition 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
Images
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
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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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
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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
- F04C18/356—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 outer 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
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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
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
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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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
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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
- F04C2240/10—Stators
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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
- F04C2240/20—Rotors
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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
- F04C2240/30—Casings or housings
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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
- F04C2240/50—Bearings
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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
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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
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/10—Stators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/20—Rotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/50—Bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/60—Shafts
Definitions
- the present invention relates to a rotary compressor.
- the rotary compressor can be divided into a method in which a vane is slidably inserted into a cylinder and contacted with the roller, and a method in which a vane is slidably inserted into the roller and contacted with the cylinder.
- the former is called a roller eccentric rotary compressor (hereinafter referred to as a rotary compressor), and the latter is classified as a vane concentric rotary compressor (hereinafter, a vane rotary compressor).
- the vane inserted into the cylinder is drawn toward the roller by elastic force or back pressure, and comes into contact with the outer circumferential surface of the roller.
- the vane rotary compressor the vane inserted into the roller rotates together with the roller, and is drawn toward the cylinder by centrifugal force and back pressure, and comes into contact with the inner circumferential surface of the cylinder.
- the rotary compressor independently forms as many compression chambers as the number of vanes per rotation of the roller, so that each compression chamber simultaneously performs suction, compression, and discharge strokes.
- each compression chamber sequentially performs suction, compression, and discharge strokes. Therefore, the vane rotary compressor forms a higher compression ratio than the rotary compressor. Accordingly, the vane rotary compressor is more suitable for using high-pressure refrigerants with low ozone depletion potential (ODP) and global warming potential (GWP), such as R32, R410a, and CO 2 .
- ODP ozone depletion potential
- GWP global warming potential
- Patent Document 1 Japanese Laid-Open Patent Application: JP2013-213438A.
- the vane rotary compressor disclosed in Patent Document 1 is a low-pressure method in which the inner space of the motor chamber is filled with suction refrigerant, but a structure in which a plurality of vanes are slidably inserted into the rotating roller discloses the characteristics of the vane rotary compressor.
- a back pressure chamber is formed at the rear end of the vane, respectively, and the back pressure chamber is formed so that the back pressure pocket communicates.
- the back pressure pocket is divided into a first pocket forming an intermediate pressure and a second pocket forming a discharge pressure or an intermediate pressure close to the discharge pressure. Based on the direction from the suction side to the discharge side, the first pocket communicates with the back pressure chamber located on the upstream side, and the second pocket communicates with the back pressure chamber located on the downstream side.
- an object of the present invention is to provide a rotary compressor capable of reducing friction loss and wear by sufficiently supplying oil between the axial side of the vane and the main bearing or sub bearing facing the same.
- the present invention allows a certain amount of oil to be stored between the axial side of the vane and the main bearing or sub-bearing facing it, so that the oil is quickly transferred between the axial side of the vane and the main bearing or sub-bearing facing it when restarting.
- An object of the present invention is to provide a rotary compressor that can be easily supplied.
- Another object of the present invention is to provide a rotary compressor capable of reducing friction loss and wear between the vanes and the vane slots facing them.
- an object of the present invention is to provide a rotary compressor capable of suppressing friction loss and wear by reducing the friction area between the vanes and the vane slots facing them.
- an object of the present invention is to provide a rotary compressor capable of reducing friction loss between the rear edge of the vane and the vane slot facing the same.
- Another object of the present invention even when using a high-pressure refrigerant such as R32, R410a, CO 2 It is possible to suppress friction loss and wear between the vane and the main bearing or sub-bearing and between the vane and the vane slot. It is intended to provide a rotary compressor.
- a high-pressure refrigerant such as R32, R410a, CO 2
- a rotary compressor for achieving the object of the present invention includes a casing, a cylinder, a main bearing and a sub-bearing, a rotating shaft, a roller, and at least one or more vanes.
- the casing may have a sealed inner space.
- the cylinder may be provided inside the casing to form a compression space.
- the main bearing and the sub-bearing may be respectively provided on both sides of the cylinder in the axial direction to support the rotation shaft.
- the rotation shaft may be supported through the main bearing hole and the sub bearing hole.
- the roller may be provided on the rotation shaft to be eccentrically provided in the compression space.
- the vane may be slidably inserted into the vane slot provided in the roller or the cylinder to separate the compression space into a plurality of compression chambers.
- the vane may have an oil supply groove formed on at least one of both axial side surfaces facing the main bearing and the sub bearing.
- the oil supply groove may be formed longer in the longitudinal direction than in the width direction of the vane.
- the oil supply groove may extend in the longitudinal direction from the edge of the rear end face of the vane accommodated in the vane slot toward the end face of the vane opposite thereto. Through this, oil is supplied far along the longitudinal direction of the vane to secure a wide lubrication area, and friction loss and wear on the friction surface can be suppressed.
- the oil supply groove may be spaced apart from the first edge of the rear end face of the vane accommodated in the vane slot by a predetermined distance and extend in the longitudinal direction toward the end face of the vane opposite to that. Through this, the oil is preserved on the friction surface of the vane, so that it can be lubricated quickly when the compressor is restarted.
- sealing portions are formed on both sides of the oil supply groove in the width direction, and the both sealing portions may be formed to be greater than or equal to the width of the oil supply groove.
- the oil supply grooves are formed on both axial side surfaces of the vane, and the oil supply grooves formed on the both axial side surfaces may be formed symmetrically to each other. Through this, both axial side surfaces of the vane can be easily machined and effectively lubricated.
- the oil supply groove is formed on both axial side surfaces of the vane, respectively, and the oil supply groove formed on the both axial side surfaces may be formed asymmetrically with each other. Through this, it is possible to additionally supply oil to the surface that requires relatively more lubrication, thereby increasing the lubrication effect.
- a discharge port may be formed on one of the main bearing and the sub bearing.
- the length of the oil supply groove facing the bearing on the side where the discharge port is not formed may be longer than the length of the oil supply groove facing the bearing on the side where the discharge port is formed.
- the oil supply groove includes a first oil supply groove formed on the side of the rear end face of the vane accommodated in the vane slot, and a second oil supply groove that extends from the first oil supply groove toward the end surface of the vane that is opposite to the rear end of the vane. may include.
- the volume of the first oil supply groove may be formed wider than the volume of the second oil supply groove.
- the first oil supply groove may extend from the first edge of the rear end face of the vane so as to communicate with the end face after the vane. Through this, oil can be smoothly introduced into the oil supply groove to increase the lubrication effect.
- the first oil supply groove may be spaced apart by a predetermined distance from the first edge of the rear end face of the vane so as to be separated from the end face after the vane. Through this, the oil is preserved in the oil supply groove, so that oil can be quickly supplied to the friction surface during restart.
- the oil supply groove is formed on at least one of both circumferential side surfaces of the vane, and may extend from the second edge of the rear end face of the vane so as to communicate with the end face after the vane accommodated in the vane slot. Through this, friction loss and wear between the vane and the vane slot can be suppressed.
- the second corner each of which is provided on both sides of the axial direction of the oil supply groove may be formed with a support portion in contact with the inner surface of the vane slot.
- the support portion may extend from the rear end face of the vane so as to protrude than the oil supply groove.
- a plurality of the oil supply grooves may be formed at a predetermined interval along the axial direction from the second edge of the rear end face of the vane.
- the oil supply groove, the oil supply groove formed on the rotational direction side of the roller may be formed deeper in the width direction of the vane than the oil supply groove on the opposite side.
- the vane may have a vane front end face opposite to the vane rear end face accommodated in the vane slot inclined in the direction of rotation of the roller.
- the oil supply groove may be formed on both circumferential side surfaces of the vane, respectively.
- the oil supply groove on the rotational direction side of the vane may be formed longer toward the vane tip end surface opposite to the rear end surface of the vane than the oil supply groove on the opposite side.
- a rotary compressor for achieving the object of the present invention includes a casing, a cylinder, a main bearing and a sub-bearing, a rotating shaft, a roller, and at least one or more vanes.
- the casing may have a sealed inner space.
- the cylinder may be provided inside the casing to form a compression space.
- the main bearing and the sub-bearing may be respectively provided on both sides of the cylinder in the axial direction to support the rotation shaft.
- the rotation shaft may be supported through the main bearing hole and the sub bearing hole.
- the roller may be provided on the rotation shaft to be eccentrically provided in the compression space.
- the vane may be slidably inserted into the vane slot provided in the roller or the cylinder to separate the compression space into a plurality of compression chambers.
- the vane may have an oil supply groove formed on at least one of both circumferential side surfaces.
- the oil supply groove may extend from the second edge of the rear end face of the vane so as to communicate with the end face of the rear vane accommodated in the vane slot. Through this, friction loss and wear between the vane and the vane slot can be suppressed.
- the second corner each of which is provided on both sides of the axial direction of the oil supply groove may be formed with a support portion in contact with the inner surface of the vane slot.
- the support portion may extend from the rear end face of the vane so as to protrude than the oil supply groove.
- the oil supply groove may be formed in plurality at a predetermined interval along the axial direction at the second edge of the rear end face of the vane.
- the oil supply groove, the oil supply groove formed on the rotational direction side of the roller may be formed deeper in the width direction of the vane than the oil supply groove on the opposite side. Through this, it is possible to secure the rigidity of the vane while reducing friction loss and wear between the vane and the vane slot.
- the vane may be disposed so that a front end face of the vane opposite to a rear end face of the vane accommodated in the vane slot is inclined in the direction of rotation of the roller.
- the oil supply groove may be formed on both circumferential side surfaces of the vane, respectively.
- the oil supply groove on the rotational direction side of the vane may be formed longer toward the vane tip end surface than the oil supply groove on the opposite side.
- At least one vane slot is formed in the roller along the outer circumferential surface of the roller, and at least one back pressure chamber communicating with the vane slot in the roller may be formed through the axial direction.
- a back pressure pocket communicating with the back pressure chamber may be formed on at least one of the main bearing and the sub bearing. At least a portion of the oil supply groove may overlap the back pressure pocket in the axial direction.
- At least one of both axial side surfaces of the vanes facing the main bearing and the sub-bearing may be formed with an oil supply groove longer in the longitudinal direction than in the width direction of the vanes.
- an oil supply groove extending in the longitudinal direction from the edge of the rear end face of the vane accommodated in the vane slot toward the end face of the vane opposite to that may be formed.
- the rotary compressor according to this embodiment may be spaced apart by a predetermined interval from the first edge of the rear end face of the vane accommodated in the vane slot, and an oil supply groove extending in the longitudinal direction toward the end face of the vane opposite thereto may be formed. Through this, the oil is preserved on the friction surface of the vane, so that it can be lubricated quickly when the compressor is restarted.
- sealing portions are formed on both sides of the oil supply groove in the width direction, respectively, and both sealing portions may be formed to be greater than or equal to the width of the oil supply groove.
- oil supply grooves may be formed so as to be symmetrical or asymmetric to each other on both axial side surfaces of the vanes.
- a first oil supply groove is formed on the side of the rear end face of the vane accommodated in the vane slot, and extends from the first oil supply groove toward the end face of the vane opposite to the rear end of the vane and narrower than the first oil supply groove.
- a second oil supply groove may be formed.
- an oil supply groove is formed on at least one of both circumferential side surfaces of the vane, and the oil supply groove extends from the second edge of the rear end face of the vane so as to communicate with the end surface of the rear end of the vane accommodated in the vane slot.
- the rotary compressor according to the present embodiment may be formed with a support portion that protrudes from both sides of the axial direction of the oil supply groove and comes into contact with the inner surface of the vane slot. Through this, it is possible to lubricate the vane and the vane slot while stabilizing the behavior of the vane.
- a plurality of oil supply grooves may be formed at predetermined intervals along the axial direction at the second edge of the rear end face of the vane.
- the oil supply groove formed on the rotational direction side of the roller may be formed deeper in the width direction of the vane than the opposite oil supply groove.
- the rotary compressor according to this embodiment, R32, R410a even when using a high-pressure refrigerant such as CO 2 It is possible to form an oil supply groove on the friction surface of the vane. Through this, friction loss and wear between the vane and the main bearing or sub-bearing and between the vane and the vane slot can be suppressed.
- FIG. 1 is a cross-sectional view showing an embodiment of a vane rotary compressor according to the present invention
- FIG. 2 is an exploded perspective view of the compression unit in FIG. 1;
- Figure 4 is a perspective view showing the vane in Figure 1,
- FIG. 5 is a sectional view of "IV-IV" in FIG. 4;
- FIG. 6 is a cross-sectional view showing a process in which oil is introduced into the oil supply groove in FIG. 1;
- Figure 8 is a "V-V" front sectional view of Figure 7,
- FIG. 9 and 10 are perspective views showing another embodiment of the oil supply groove in FIG.
- FIG. 11 is a perspective view of another embodiment of the vane in FIG. 1;
- FIG. 12 is a front cross-sectional view of "VI-VI" in FIG. 11;
- FIG. 13 is a cross-sectional view showing another embodiment of the oil supply groove in FIG. 11;
- FIG. 14 is a perspective view showing another embodiment of the oil supply groove in FIG. 11;
- FIG. 15 is a sectional view of "VII-VII" of FIG. 14;
- FIG. 17 is a perspective view showing another embodiment of the vane in FIG. 1;
- the oil supply hole according to the present invention can be equally applied to the vane rotary compressor in which the vane is slidably inserted into the roller.
- the same may be applied to the case in which the vane slot is formed in a radial direction as well as an example in which the vane slot is inclined as in the present embodiment.
- an example in which the vane slot is inclined on the roller and the inner circumferential surface of the cylinder is an asymmetric oval shape will be described as a representative example.
- FIG. 1 is a cross-sectional view showing an embodiment of a vane rotary compressor according to the present invention
- FIG. 2 is an exploded perspective view of the compression unit in FIG. 1
- FIG. 3 is a plan view showing the compression unit of FIG. 2 assembled.
- the vane rotary compressor includes a casing 110 , a driving motor 120 , and a compression unit 130 .
- the drive motor 120 is installed in the upper inner space 110a of the casing 110
- the compression unit 130 is installed in the lower inner space 110a of the casing 110, respectively, and the drive motor 120 and the compression unit ( 130 is connected to the rotation shaft 123 .
- the casing 110 includes an intermediate shell 111 formed in a cylindrical shape, a lower shell 112 covering the lower end of the intermediate shell 111 , and an upper shell 113 covering the upper end of the intermediate shell 111 .
- the driving motor 120 and the compression unit 130 are inserted into the intermediate shell 111 to be fixedly coupled, and the suction pipe 115 may be penetrated to be directly connected to the compression unit 130 .
- the lower shell 112 is sealingly coupled to the lower end of the intermediate shell 111 , and a storage oil space 110b in which oil to be supplied to the compression unit 130 is stored may be formed below the compression unit 130 .
- the upper shell 113 is sealingly coupled to the upper end of the intermediate shell 111 , and an oil separation space 110c may be formed above the driving motor 120 to separate oil from the refrigerant discharged from the compression unit 130 . have.
- the driving motor 120 is a part constituting the electric part, and provides power to drive the compression part 130 .
- the driving motor 120 includes a stator 121 , a rotor 122 , and a rotation shaft 123 .
- the stator 121 is fixedly installed inside the casing 110 , and may be press-fitted to the inner circumferential surface of the casing 110 by shrink fit or the like.
- the stator 121 may be fixed by being press-fitted to the inner circumferential surface of the intermediate shell 110a.
- the rotor 122 is rotatably inserted into the stator 121 , and the rotation shaft 123 is press-fitted to the center of the rotor 122 . Accordingly, the rotating shaft 123 rotates concentrically with the rotor 122 .
- An oil pickup 127 may be installed in the middle or lower end of the oil passage 125 .
- the oil pickup 127 may be a gear pump, a viscous pump, or a centrifugal pump. This embodiment shows an example in which a centrifugal pump is applied. Accordingly, when the rotating shaft 123 rotates, the oil filled in the oil storage space 110b of the casing 110 is pumped by the oil pickup 127, and this oil is sucked along the oil passage 125 and then the second oil through hole. It may be supplied to the sub-bearing surface 1322b of the sub-bush part 1322 through the 126b and to the main bearing surface 1312b of the main bushing part 1312 through the first oil through-hole 126a.
- the compression unit 130 includes a main bearing 131 , a sub bearing 132 , a cylinder 133 , a roller 134 , and a plurality of vanes 1351 , 1352 , 1353 .
- the main bearing 131 and the sub bearing 132 are respectively provided on upper and lower sides of the cylinder 133 to form a compression space V together with the cylinder 133, and the roller 134 rotates in the compression space V Installed as possible, the vanes 1351, 1352, 1353 are slidably inserted into the roller 134 to divide the compression space V into a plurality of compression chambers.
- the main bearing 131 may be fixedly installed on the intermediate shell 111 of the casing 110 .
- the main bearing 131 may be inserted into the intermediate shell 111 and welded.
- the main bearing 131 may be closely coupled to the upper end of the cylinder 133 . Accordingly, the main bearing 131 forms the upper surface of the compression space V, supports the upper surface of the roller 134 in the axial direction, and at the same time supports the upper half of the rotary shaft 123 in the radial direction.
- the main bearing 131 may include a main plate part 1311 and a main bush part 1312 .
- the main plate part 1311 covers the upper side of the cylinder 133 and is coupled to the cylinder 133
- the main bush part 1312 is axially from the center of the main plate part 1311 toward the driving motor 120 . It extends to support the upper half of the rotation shaft 123 .
- the main plate part 1311 may be formed in a disk shape, and the outer peripheral surface of the main plate part 1311 may be fixed in close contact with the inner peripheral surface of the intermediate shell 111 .
- At least one or more outlets 1313a, 1313b, and 1313c are formed in the main plate portion 1311 , and a plurality of outlets 1313a, 1313b, and 1313c for opening and closing each of the outlets 1313a, 1313b, and 1313c are formed on the upper surface of the main plate portion 1311 .
- discharge valves 1361, 1362 and 1363 are installed, and the discharge ports 1313a, 1313b, 1313c and the discharge valves 1361, 1362, 1363 are provided on the upper side of the main plate 1311 to accommodate the A discharge muffler 137 having a discharge space (unsigned) may be installed.
- the discharge port will be described again later.
- a first main back pressure pocket 1315a and a second main back pressure pocket 1315b are formed on the lower surface of the main plate portion 1311 facing the upper surface of the roller 134 among both sides of the main plate portion 1311 in the axial direction.
- the first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be formed in an arc shape and may be formed at a predetermined interval along the circumferential direction.
- the inner peripheral surface of the first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be formed in a circular shape, and the outer peripheral surface may be formed in an elliptical shape in consideration of a vane slot to be described later.
- the first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be formed within the outer diameter range of the roller 134 . Accordingly, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b may be separated from the compression space (V). However, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b are both sides unless a separate sealing member is provided between the lower surface of the main plate part 1311 and the upper surface of the roller 134 facing it. Through the gap between the faces, it is possible to communicate finely.
- the second main back pressure pocket 1315b forms a pressure higher than that of the first main back pressure pocket 1315a, for example, a discharge pressure or an intermediate pressure between the suction pressure and the discharge pressure close to the discharge pressure.
- oil flowing into the main bearing hole 1312a of the main bearing 1312 through the first oil through hole 126a may be introduced into the second main back pressure pocket 1315b.
- the second main back pressure pocket 1315b may be formed within the range of the compression chamber forming the discharge pressure in the compression space V. Accordingly, the second main back pressure pocket 1315b maintains the discharge pressure.
- first main bearing protrusion 1316a surrounding the circumference of the first main back pressure pocket 1315a is formed around the first main back pressure pocket 1315a, and around the second main back pressure pocket 1315b is formed.
- a second main bearing protrusion 1316b surrounding the circumference of the second main back pressure pocket 1315b may be formed. Accordingly, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b are sealed to the outside, and the rotation shaft 123 can be stably supported.
- the first main bearing protrusion 1316a and the second main bearing protrusion 1316b may be formed separately to surround each of the main back pressure pockets 1315a and 1315b independently, and the main back pressure pockets 1315a and 1315b) It may be integrally connected and formed so as to enclose the .
- an example in which the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are integrally formed is shown.
- the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed at the same height, and an oil communication groove (not shown) or an oil communication hole (not shown) on the inner peripheral end surface of the second main bearing protrusion 1316b not shown) may be formed.
- the inner peripheral height of the second main bearing protrusion 1316b may be formed to be lower than the inner peripheral height of the first main bearing protrusion 1316a. Accordingly, high-pressure oil (refrigerant oil) flowing into the main bearing surface 1312b flows into the second main back pressure pocket 1315b, and the second main back pressure pocket 1315b is in the first main back pressure pocket 1315a. A high pressure (discharge pressure) is formed.
- the main bush portion 1312 is formed in the shape of a hollow bush, and a first oil groove (not shown) may be formed on the inner peripheral surface of the main bearing hole 1312a constituting the inner peripheral surface of the main bush part 1312 .
- the first oil groove (not shown) may be formed in a straight line or an oblique line between upper and lower ends of the main bush part 1312 to communicate with the first oil through hole 126a.
- the sub-bearing 132 may be closely coupled to the lower end of the cylinder 133 . Accordingly, the sub-bearing 132 forms the lower surface of the compression space V, supports the lower surface of the roller 134 in the axial direction and at the same time supports the lower half of the rotation shaft 123 in the radial direction.
- the sub-bearing 132 may include a sub-plate part 1321 and a sub-bush part 1322 .
- the sub-plate part 1321 covers the lower side of the cylinder 133 and is coupled to the cylinder 133, and the sub-bush part 1322 is axially from the center of the sub-plate part 1321 toward the lower shell 112. It extends to support the lower half of the rotating shaft 123 .
- the sub-plate part 1321 is formed in a disk shape like the main plate part 1311 , and the outer peripheral surface of the sub-plate part 1321 may be spaced apart from the inner peripheral surface of the intermediate shell 111 .
- a first sub back pressure pocket 1325a and a second sub back pressure pocket 1325b are formed on the upper surface of the sub plate portion 1321 facing the lower surface of the roller 134 among both sides of the sub plate portion 1321 in the axial direction.
- the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b are formed symmetrically around the roller 134 in the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, respectively.
- first sub back pressure pocket 1325a may be symmetrical with the first main back pressure pocket 1315a
- second sub back pressure pocket 1325b may be formed symmetrically with the second main back pressure pocket 1315b
- first sub bearing protrusion 1326a is formed around the first sub back pressure pocket 1325a
- second sub bearing protrusion 1326b is formed around the second sub back pressure pocket 1325b, respectively or connected to each other.
- the first main back pressure pocket 1315a and the second main back pressure with respect to the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b, the first sub bearing protrusion 1326a and the second sub bearing protrusion 1326b The description of the pocket (1315b), the first main bearing protrusion (1316a) and the second main bearing protrusion (1316b) is replaced.
- the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b are located in the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, respectively, centering on the roller 134. It may be formed asymmetrically.
- the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b may be formed to be deeper than the first main back pressure pocket 1315a and the second main back pressure pocket 1315b.
- the sub-bush portion 1322 is formed in a hollow bush shape, and an oil groove (not shown) may be formed on an inner peripheral surface of the sub-bearing hole 1322a constituting the inner peripheral surface of the sub-bush part 1322 .
- An oil groove (not shown) may be formed in a straight line or an oblique line between the upper and lower ends of the sub-bush part 1322 to communicate with the second oil through-hole 126b of the rotation shaft 123 .
- the back pressure pockets [(1315a, 1315b)] [(1325a, 1325b)] may be formed on only one of the main bearing 131 and the sub bearing 132 .
- the discharge port 1313 may be formed in the main bearing 131 as described above.
- the discharge port may be formed in the sub-bearing 132 , the main bearing 131 and the sub-bearing 132 , respectively, or may be formed through the inner peripheral surface and the outer peripheral surface of the cylinder 133 .
- This embodiment will be mainly described with respect to an example in which the discharge port 1313 is formed on the main bearing 131 .
- discharge port 1313 Only one discharge port 1313 may be formed. However, in the discharge port 1313 according to the present embodiment, a plurality of discharge ports 1313a, 1313b, and 1313c may be formed at predetermined intervals along the compression progress direction (or the rotation direction of the roller).
- the roller 134 is eccentrically disposed with respect to the compression space V, the proximal point that almost contacts between the outer circumferential surface 1341 of the roller 134 and the inner circumferential surface 1332 of the cylinder 133 (P1) is generated, and the discharge port 1313 is formed near the proximity point P1. Accordingly, as the compression space V approaches the proximity point P1, the distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134 becomes narrower, making it difficult to secure the discharge port area. do.
- the discharge port 1313 may be divided into a plurality of discharge ports 1313a, 1313b, and 1313c to be formed along the rotational direction (or compression progress direction) of the roller 134 .
- the plurality of outlets 1313a, 1313b, and 1313c may be formed individually, but may be formed in pairs of two as in the present embodiment.
- the outlets 1313 according to the present embodiment may be arranged in the order of the first outlet 1313a, the second outlet 1313b, and the third outlet 1313c from the outlet closest to the adjacent portion 1332a.
- the distance between the first outlet 1313a and the second outlet 1313b and/or the distance between the second outlet 1313b and the third outlet 1313c is the gap between the preceding vane and the following vane, that is, each compression. It may be formed approximately similar to the circumferential length of the yarn.
- the interval between the first discharge port 1313a and the second discharge port 1313b and the interval between the second discharge port 1313b and the third discharge port 1313c may be equal to each other.
- the first interval and the second interval may be formed to be substantially equal to the circumferential length of the first compression chamber V1, the circumferential length of the second compression chamber V2, and the circumferential length of the third compression chamber V3.
- the plurality of discharge ports 1313 communicate with one compression chamber or the plurality of compression chambers do not communicate with one discharge port 1313, and the first discharge port 1313a is connected to the first compression chamber V1 and the second
- the second discharge port 1313b may communicate with the compression chamber V2 and the third discharge port 1313c may communicate with the third compression chamber V3, respectively.
- each compression chamber V1, V2, and V3 is formed differently, and one A plurality of discharge ports may communicate with one compression chamber, or a plurality of compression chambers may communicate with one discharge port.
- a discharge groove 1314 may be formed to extend through the discharge port 1313 according to the present embodiment.
- the discharge groove 1314 may extend in an arc shape along the compression progress direction (rotation direction of the roller). Accordingly, the refrigerant not discharged from the preceding compression chamber may be guided to the discharge port 1313 communicating with the subsequent compression chamber through the discharge groove 1314 to be discharged together with the refrigerant compressed in the subsequent compression chamber.
- the compressor efficiency can be increased by minimizing the residual refrigerant in the compression space (V) to suppress overcompression.
- the discharge groove 1314 as described above may be formed to extend from the final discharge port (eg, the third discharge port) 1313 .
- the compression space V is divided into a suction chamber and a discharge chamber on both sides with a proximity portion (proximity point) 1332a interposed therebetween, when the sealing between the suction chamber and the discharge chamber is considered, the discharge port 1313 is located in the proximity portion. It cannot be superimposed on the proximity point P1 located at 1332a.
- a residual space S spaced apart between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134 is formed along the circumferential direction,
- the refrigerant is not discharged through the final discharge port (1313) and remains.
- Residual refrigerant may increase the pressure of the final compression chamber, thereby causing a decrease in compression efficiency due to overcompression.
- the discharge groove 1314 extends from the final discharge port 1313 to the residual space S, the refrigerant remaining in the remaining space S passes through the discharge groove 1314 to the final discharge port ( 1313) and additionally discharged, it is possible to effectively suppress a decrease in compression efficiency due to overcompression in the final compression chamber.
- a residual discharge hole may be formed in the remaining space S in addition to the discharge groove 1314 .
- the residual discharge hole may be formed to have a smaller inner diameter than the discharge hole, and unlike the discharge hole, the residual discharge hole may be formed to be always opened without being opened or closed by the discharge valve.
- the plurality of discharge ports 1313a, 1313b, and 1313c may be opened and closed by the respective discharge valves 1361, 1362, and 1363 described above.
- Each of the discharge valves 1361, 1362, 1363 may be formed of a cantilever-shaped reed valve having one end forming a fixed end and the other end forming a free end. Since each of these discharge valves 1361, 1362, 1363 is widely known in a conventional rotary compressor, a detailed description thereof will be omitted.
- the cylinder 133 may be in close contact with the lower surface of the main bearing 131 and may be bolted to the main bearing 131 together with the sub bearing 132 . Accordingly, the cylinder 133 may be fixedly coupled to the casing 110 by the main bearing 131 .
- the cylinder 133 may be formed in an annular shape having an empty space to form a compression space V in the center.
- the empty space portion is sealed by the main bearing 131 and the sub bearing 132 to form the above-described compression space V, and a roller 134 to be described later may be rotatably coupled to the compression space V.
- the cylinder 133 may be formed by passing the suction port 1331 from the outer circumferential surface to the inner circumferential surface.
- the suction port may be formed through the main bearing 131 or the sub bearing 132 .
- the suction port 1331 may be formed on one side in the circumferential direction around a proximity point P1 to be described later.
- the discharge port 1313 described above may be formed in the main bearing 131 at the other side in the circumferential direction opposite to the suction port 1331 around the proximity point P1 .
- the inner peripheral surface 1332 of the cylinder 133 may be formed in an elliptical shape.
- the inner circumferential surface 1332 of the cylinder 133 according to the present embodiment may be formed in an asymmetric oval shape by combining a plurality of ellipses, for example, four ellipses having different major and minor ratios to have two origins.
- the roller 134 according to the present embodiment has an outer peripheral surface 1341 formed in a circular shape, and the rotational shaft 123 is extended as a single unit at the rotation center Or of the roller 134 or Alternatively, it may be post-assembled and combined. Accordingly, the rotation center Or of the roller 134 is positioned on the same axis as the axis center (unsigned) of the rotation shaft 123 , and the roller 134 rotates concentrically with the rotation shaft 123 .
- the rotation center Or of the roller 134 is located at the outer diameter center Oc of the cylinder 133 . It can be arranged eccentrically. Accordingly, the roller 134, one side of the outer peripheral surface 1341 is almost in contact with the inner peripheral surface 1332 of the cylinder 133, precisely the proximity portion 1332a to form the proximity point (P1).
- the proximal point P1 may be formed in the proximal portion 1332a as described above. Accordingly, the imaginary line passing through the proximity point P1 may correspond to the short axis of the elliptic curve forming the inner circumferential surface 1332 of the cylinder 133 .
- roller 134 has a plurality of vane slots 1342a, 1342b, and 1342c formed at appropriate locations along the circumferential direction on its outer peripheral surface 1341, and each vane slot 1342a, 1342b, 1342c).
- a plurality of vanes 1351, 1352, 1353, which will be described later, may be slidably inserted and coupled to each.
- a plurality of vane slots 1342a, 1342b, and 1342c are defined as a first vane slot 1342a, a second vane slot 1342b, and a third vane slot 1342c along the compression progress direction (rotation direction of the roller).
- the first vane slot 1342a, the second vane slot 1342b, and the third vane slot 1342c may be formed to be identical to each other at equal or unequal intervals along the circumferential direction.
- the plurality of vane slots 1342a, 1342b, and 1342c are formed to be inclined by a predetermined angle with respect to the radial direction, respectively, so that the lengths of the vanes 1351, 1352 and 1353 can be sufficiently secured. Accordingly, when the inner peripheral surface 1332 of the cylinder 133 is formed in an asymmetric oval shape, even if the distance from the outer peripheral surface 1341 of the roller 134 to the inner peripheral surface 1332 of the cylinder 133 increases, the vane 1351 It is possible to suppress the separation of the 1352 and 1353 from the vane slots 1342a, 1342b, and 1342c, thereby increasing the degree of freedom in designing the inner circumferential surface 1332 of the cylinder 133.
- the direction in which the vane slots 1342a, 1342b, and 1342c are inclined is opposite to the rotational direction of the roller 134, that is, each vane tip end face 1351, 1352) ( It may be preferable to tilt the 1353 in the direction of rotation of the roller 134 so that the compression start angle can be pulled toward the direction of rotation of the roller 134 so that the compression can be started quickly.
- back pressure chambers 1343a, 1343b, and 1343c may be formed to communicate with each other at inner ends of the vane slots 1342a, 1342b, and 1342c.
- the back pressure chambers 1343a, 1343b, and 1343c have a discharge pressure or intermediate pressure oil (or refrigerant) toward the rear side of each vane 1351, 1352, 1353, that is, the rear end surfaces 1351c, 1352c, and 1353c.
- each vane 1351 , 1352 , 1353 moves through the inner circumferential surface of the cylinder 133 by the pressure of oil (or refrigerant) filled in the back pressure chambers 1343a, 1343b, and 1343c. can be pressed towards.
- the direction toward the cylinder 133 based on the movement directions of the vanes 1351, 1352 and 1353 may be described by defining the forward direction and the opposite side as the rear.
- the back pressure chambers 1343a, 1343b, and 1343c may be formed to be sealed by the main bearing 131 and the sub bearing 132 , respectively.
- the back pressure chambers 1343a, 1343b and 1343c may independently communicate with each of the back pressure pockets [(1315a, 1315b)] [(1325a, 1325b)], and the back pressure pockets [1315a, 1315b] ][(1325a, 1325b)] may be formed to communicate with each other.
- a plurality of vanes 1351 , 1352 , 1353 may be slidably inserted into the respective vane slots 1342a, 1342b, and 1342c. Accordingly, the plurality of vanes 1351, 1352, and 1353 may be formed to have substantially the same shape as the respective vane slots 1342a, 1342b, and 1342c.
- a plurality of vanes 1351, 1352 and 1353 are defined as a first vane 1351, a second vane 1352, and a third vane 1353 along the rotational direction of the roller 134,
- the first vane 1351 is to be inserted into the first vane slot 1342a
- the second vane 1352 is to be inserted into the second vane slot 1342b
- the third vane 1353 is to be inserted into the third vane slot 1342c, respectively.
- the plurality of vanes 1351, 1352, and 1353 may be formed to have substantially the same shape.
- the plurality of vanes 1351, 1352 and 1353 are each formed as a substantially rectangular parallelepiped, and the vane tip end surfaces 1351a, 1352a, 1353a in contact with the inner circumferential surface 1332 of the cylinder 133 are curved.
- the plurality of vanes 1351, 1352 and 1353 have back pressure chambers 1343a, 1343b, and 1343c facing the rear end surfaces 1351b, 1352b, 1353b, the main bearing 131 and the sub-bearing.
- Both axial sides facing (132) [(1351c) (1352c) (1353c)] [(1351d) (1352d) (1353d)]][( 1351f), 1352f, and 1353f] may be formed as straight surfaces, respectively.
- the surface facing the main bearing 131 among both axial side surfaces is referred to as the vane upper side surface 1351c, 1352c, 1353c
- the side facing the sub bearing 132 is the vane lower side surface 1351d (1351d) ( 1352d) and 1353d are respectively defined and described.
- the rotation direction side of the roller 134 is defined as the vane compression surfaces 1351e, 1352e, 1353e
- the opposite side is defined as the vane compression rear surfaces 1351f, 1352f and 1353f, respectively.
- the vanes 1351, 1352, and 1353 have an upper side oil supply groove 1355a on the vane upper side surfaces 1351c, 1352c, 1353c, and the vane lower side surface 1351d (1352d) (1352d) (1353d) On the lower side oil supply groove (1355b), the compression surface oil supply groove (1356a) on the vane compression surfaces (1351e), 1352e (1353e), the compression surface oil supply groove (1356a) on the compression rear surface (1351f) (1352f) (1353f) of the vane compression surface oil supply groove ( 1356b) may be formed respectively.
- the upper surface oil supply groove (1355a) and the lower surface oil supply groove (1355b), the compressed surface oil supply groove (1356a) and the compressed rear oil supply groove (1356b) may all be formed, the upper surface oil supply groove (1355a) and the lower side Only the oil supply groove (1355b) is formed, or only the compressed surface oil supply groove (1356a) and the compressed rear oil supply groove (1356b) may be formed, the upper surface oil supply groove (1355a) and the lower surface oil supply groove (1355b) and the compression surface oil supply groove Only one of the (1356a) and the compressed back oil supply groove (1356b) may be formed. These oil supply grooves will be described again later.
- the plurality of vanes 1351, 1352, and 1353 have centrifugal force generated by the rotation of the roller 134 and the rear end surfaces 1351b, 1351b, 1351c of the vanes 1351, 1352 and 1353. It is drawn out from each of the vane slots 1342a, 1342b and 1342c by the back pressure of the back pressure chambers 1343a, 1343b, and 1343c supporting the .
- the compression space (V) of the cylinder 133 is formed by the plurality of vanes 1351, 1352, 1353, and as many compression chambers (suction chambers or discharge chambers) as the number of the plurality of vanes 1351, 1352, 1353.
- the inner peripheral surface 1332 of the cylinder 133 while moving along the rotation of the roller 134, each of the compression chambers V1, V2, and V3
- the volume is changed by the shape and eccentricity of the rollers 134, and the refrigerant sucked into the respective compression chambers V1, V2, and V3 flows along the rollers 134 and the vanes 1351, 1352 and 1353.
- a series of processes of being compressed while moving and discharged into the inner space of the casing 110 are repeated.
- the vane rotary compressor according to the present embodiment slides in the radial direction while rotating with the roller in a state in which the vane is inserted into the vane slot of the roller.
- the vanes are rubbed against the main bearing and sub-bearing and also rub against the rollers. That is, the upper side of the vane and the lower side of the vane are in contact with the main bearing and the sub-bearing, respectively, and the compressed surface of the vane and the compressed rear of the vane are respectively contacted and rubbed against the inner surface of the vane slot. Friction loss and wear occur.
- friction loss between the axial side of the vane and the main bearing or/and sub-bearing facing it, and the circumferential side of the vane and the roller facing it by forming an oil supply groove on the axial side of the vane. Or it can suppress abrasion.
- the first to third vanes according to the present embodiment are formed in substantially the same shape, the first vane will be described below as a representative example.
- FIG. 4 is a perspective view showing the vane in FIG. 1
- FIG. 5 is a cross-sectional view “IV-IV” in FIG. 4
- FIG. 6 is a cross-sectional view showing a process in which oil is introduced into the oil supply groove in FIG. 1 .
- the first vane 1351 is formed in a substantially rectangular parallelepiped as described above, while the vane front end face 1351a is formed in a curved shape, while the other face, that is, the rear end face of the vane.
- 1351b, the vane upper side surface 1351c, the vane lower side surface 1351d, the vane compression surface 1351e, and the vane compression rear surface 1351f may each be formed as substantially straight surfaces.
- an upper side oil supply groove 1355a is formed on the vane upper side surface 1351c in contact with the main plate portion 1311 of the main bearing 131, and the sub bearing 132 ) of the lower side of the vane in contact with the sub-plate portion 1321 (1351d), the lower side oil supply groove (1355b) may be formed, respectively.
- the upper side oil supply groove (1355a) is a vane front end surface (1351a) at the edge (hereinafter the first corner) (1351g) where the vane upper side surface (1351c) and the rear vane end surface (1351b) of the first vane (1351) meet.
- the upper surface oil supply groove (1355a) may be formed with the same cross-sectional area or the same volume along the longitudinal direction of the upper surface oil supply groove (1355a). Accordingly, the upper oil supply groove 1355a communicates with the first back pressure chamber 1343a through the first vane slot 1342a into which the first vane 1351 is inserted, and the oil flows into the first back pressure chamber 1343a. It can be quickly and uniformly introduced into the upper side oil supply groove (1355a).
- the upper side oil supply groove (1355a) may be formed to be located in the middle of the width direction of the vane upper side (1351c). Accordingly, upper side sealing portions 1355c and 1355c may be formed on both sides of the width direction of the upper side oil supply groove 1355a, respectively.
- the width of the upper side oil supply groove (1355a) may be formed to be 1/2 or less than the width of the vane upper side surface (1351c).
- the width D11 of the upper surface oil supply groove 1355a is smaller than or equal to the width D12 of the upper surface sealing parts 1355c and 1355c located on both sides in the width direction of the upper surface oil supply groove 1355a.
- the width D12 of the upper side sealing portions 1355c and 1355c may be formed to be greater than or equal to the width D11 of the upper surface oil supply groove 1355a. Accordingly, the upper side sealing portions 1355c and 1355c may secure a sealing distance from the vane upper side surface 1351c to suppress leakage between compression chambers respectively formed on both sides of the first vane 1351 in the circumferential direction.
- the upper side oil supply groove (1355a) may be formed slightly eccentric toward the vane compression surface (1351e) or the vane compression rear surface (1351f) in the middle of the width direction of the vane upper side surface (1351c).
- the upper side oil supply groove (1355a) may be formed slightly eccentric toward the vane compression surface (1351e) in the middle of the width direction of the vane upper side surface (1351c). Accordingly, it is possible to suppress the leakage of the oil of the upper surface oil supply groove (1355a) constituting the substantially discharge pressure into the compression chamber on the side of the compression rear vane (1351f) forming a relatively low pressure.
- the upper side oil supply groove (1355a) may be formed as a single groove between the both ends communicate with each other. Accordingly, the oil flowing from the first back pressure chamber 1343a to the rear end of the upper side oil supply groove 1355a moves quickly to the tip of the upper side oil supply groove 1355a, and an oil film is formed on the entire vane upper side surface 1351c. It can be advantageous to
- the tip side end may be formed to such an extent that it does not communicate with the discharge ports (1313a, 1313b) (1313c).
- the tip end of the upper surface oil supply groove 1355a is the discharge port ( 1313a), 1313b, and 1313c may be formed in an imaginary circle C connecting the inner ends (points adjacent to the rotation axis).
- the lower side oil supply groove (1355b) may be formed symmetrically with the upper surface oil supply groove (1355a) described above. Accordingly, the lower surface oil supply groove (1355b) is formed in the center of the lower surface of the vane (1351d), the lower surface sealing portion (1355d) may be formed on both sides of the width direction of the lower surface oil supply groove (1355b).
- the configuration of the lower surface oil supply groove (1355b) and the lower surface sealing part (1355d) and the effect thereof are replaced with the description of the upper surface oil supply groove (1355a) and the upper surface sealing part (1355c).
- the first vane 1351 rotates in the circumferential direction together with the roller 134 and simultaneously reciprocates in the radial direction along the first vane slot 1342a.
- the first vane 1351 forms a friction surface with respect to the main bearing 131 , the sub bearing 132 , and the roller 134 .
- the upper surface oil supply groove 1355a and the lower surface oil supply groove 1355b are formed on the vane upper side surface 1351c and the vane lower side surface 1351d that form the friction surface, respectively.
- the oil of the back pressure chamber 1343a flows into the friction surface between the vane upper side surface 1351c and the main plate part 1311 and the vane lower side surface 1351d and the sub-plate part 1321 and flows into these friction surfaces.
- the sub-bearing 132 and the first vane 1351 may be generated between the lower vane side surface 1351d.
- Compression efficiency can be increased by suppressing friction loss.
- the upper surface oil supply groove and the lower surface oil supply groove are formed symmetrically to each other, but in some cases, the upper surface oil supply groove and the lower surface oil supply groove may be formed asymmetrically.
- Figure 7 is a perspective view showing another embodiment for the oil supply groove in Figure 4
- Figure 8 is a "V-V" front sectional view of Figure 7.
- the first vane 1351 according to this embodiment is formed in a rectangular parallelepiped shape as described above. (1351d), the lower side oil supply groove (1355b) may be formed, respectively.
- the upper side oil supply groove (1355a) and the lower surface oil supply groove (1355b) have a basic configuration and an effect thereof similar to the embodiment of FIG. 4 described above, so a detailed description thereof will be omitted.
- the length (L1) of the upper surface oil supply groove (1355a) and the length (L2) of the lower surface oil supply groove (1355b) may be formed to be different from each other.
- the discharge ports 1313a, 1313b, and 1313c are formed in the main bearing 131 , but the discharge ports are not formed in the sub bearing 132 .
- the upper oil supply groove 1355a facing the main bearing 131 is formed so as not to overlap the discharge ports 1313a, 1313b, and 1313c.
- the lower side oil supply groove 1355b facing the sub-bearing 132 may be formed up to a position close to the vane tip end surface 1351a because the limiting condition for the outlet is excluded.
- the length L1 of the upper oil supply groove 1355a is the lower side. It may be formed shorter than the length (L2) of the oil supply groove (1355b).
- the oil is supplied through the lower surface oil supply groove (1355b) to the lower surface of the vane (1355b). ) can supply a greater amount of oil to the friction surface formed further away, which is advantageous for uniform oil film formation. Furthermore, due to its own weight, friction loss or wear may occur more on the lower side of the vane (1351b) than on the upper side (1351a) of the vane due to its own weight, but the length (L2) of the lower side oil supply groove (1355b) is reduced to the upper side oil supply groove (1355a). ), as it is formed longer than the length L1, the friction loss and wear described above can be more effectively suppressed.
- the length (L2) of the lower surface oil supply groove (1355b) may be formed shorter than the length (L1) of the upper surface oil supply groove (1355a).
- it may be formed in only one of the upper surface oil supply groove (1355a) and the lower surface oil supply groove (1355b). In this case, it is preferable to be formed on the axial side of the bearing facing the bearing without the lower side oil supply groove (1355b) or the discharge port in which a relatively large amount of oil is stored.
- the oil supply groove is formed with the same volume toward the vane tip end face, but in some cases, the oil supply groove may be formed with a different volume toward the vane tip end surface.
- FIG. 9 and 10 are perspective views showing another embodiment of the oil supply groove in FIG.
- the upper surface oil supply groove (1355a) and the lower surface oil supply groove (1355b) may be formed in a plurality of sizes.
- the upper side oil supply groove (1355a) has a first oil supply groove (1355a1) is formed in the direction from the first edge (1351g) toward the vane tip end surface (1351a), and again at the end of the first oil supply groove (1355a1)
- the second oil supply groove (1355a2) may further extend in the direction toward the vane tip end surface (1351a).
- the radial width (hereinafter, width) D21 of the first oil supply groove 1355a1 may be formed larger than the width D22 of the second oil supply groove 1355a2. Accordingly, while reducing the friction area between the upper side surface of the vane 1351c and the main bearing 131 facing it, the lubrication area is expanded by that much to reduce friction loss or wear between the first vane 1351 and the main bearing 131. can be reduced.
- the width D21 of the first oil supply groove 1355a1 is larger than the width D22 of the second oil supply groove 1355a2
- the oil stored in the first back pressure chamber 1343a is stored in the first oil supply groove 1355a1. or a certain amount of oil is stored in the first oil supply groove (1355a1), so that the oil inflow into the second oil supply groove (1355a2) can proceed more quickly.
- the first oil supply groove (1355a1) may be spaced apart from the first edge (1351g). Since the second oil supply groove (1355a2) is the same as the second oil supply groove (1355a2) of the above-described embodiment, a description thereof will be omitted.
- the first oil supply groove (1355a1) when the first oil supply groove (1355a1) is spaced apart from the first edge (1351g), a kind of oil pocket may be formed on the vane upper side surface (1351c). Then, even when the compressor is stopped, a predetermined amount of oil may be filled in the first oil supply groove 1355a1 constituting the oil pocket and stored. Then, when the compressor is restarted, the oil stored in the first oil supply groove 1355a1 can be quickly supplied to the friction surface between the first vane 1351 and the main bearing 131, so that friction loss and wear can be more effectively suppressed. can
- the lower surface oil supply groove (1355b) may also be formed in the same manner as the upper surface oil supply groove (1355a), and the effect thereof may also be similar.
- the lower surface oil supply groove (1355b) may be excluded, the upper surface oil supply groove (1355a) is excluded, and only the lower surface oil supply groove (1355b) may be formed. Even in these cases, the composition and effect may be the same.
- the width D21 of the first oil supply groove 1355a1 and the width D22 of the second oil supply groove 1355a2 are the same or different from each other, and the depth of the first oil supply groove 1355a1 is the first. 2 may be formed deeper than the depth of the oil supply groove (1355a2). In this case, the effect may be the same as the embodiment described above, that is, the embodiment in which the width D21 of the first oil supply groove 1355a1 is larger than the width D22 of the second oil supply groove 1355a2.
- the oil supply groove is formed on the upper surface of the vane and/or the lower surface of the vane, but in some cases, the oil supply groove may be formed on the compressed surface of the vane and/or the rear surface of the vane.
- FIG. 11 is a perspective view of another embodiment of the vane in FIG. 1
- FIG. 12 is a front sectional view of “VI-VI” in FIG. 11 .
- the first vane 1351 according to the present embodiment is formed in a rectangular parallelepiped shape as described above, and both circumferential side surfaces, that is, the vane compression surface 1351e, have a compression surface oil supply groove 1356a. ), the compression rear oil supply groove (1356b) may be formed in the vane compression back (1351f), respectively.
- the compression surface oil supply groove 1356a may be formed to be stepped at the edge (hereinafter, second edge) 1351h where the vane compression surface 1351e and the rear end surface 1351b meet.
- the compression surface oil supply groove (1356a) may be recessed in a rectangular parallelepiped shape by a predetermined depth at the second edge (1351h) to be formed to be stepped.
- both ends in the axial direction of the second edge 1351h have a compressed surface support part excluded from the compression surface oil supply groove 1356a ( 1356c) may be formed respectively.
- both compression surface support parts 1356c is shorter than the axial length of the compression surface oil supply groove 1356a, respectively, and the total length including the axial length of both compression surface support parts 1356c is also compressed surface oil supply groove 1356a. It may be formed shorter than the axial length of Accordingly, the inner end of the compression surface side of the first vane 1351 is supported by the compression surface support part 1356c, so that the vane tip end surface 1351c of the first vane 1351 is excessively pushed in the reverse rotation direction of the roller 134. it can be prevented
- the compression surface oil supply groove (1356a) may be formed with the same depth and the same area along the axial direction. Accordingly, the back pressure by the oil accommodated in the compression surface oil supply groove 1356a is formed almost uniformly in the entire section along the axial direction, so that the behavior of the vane can be stabilized.
- the compression surface oil supply groove (1356a) is compressed according to the position of the first vane 1351 with respect to the roller 134 when the first vane 1351 reciprocates with respect to the roller 134 when the reciprocating motion is drawn in or out.
- the distance from the thread is variable. For this reason, when the compressed surface oil supply groove (1356a) is formed too long in the direction toward the vane tip end surface (1351a), that is, in the radial direction, the compressed surface oil supply groove (1356a) is compressed in the process of withdrawing the first vane (1351).
- the sealing distance with the seal V that is, an appropriate distance with the outer peripheral surface of the roller 134 may not be secured.
- the radial length L3 of the compression surface oil supply groove 1356a is a length located inside the first vane slot 1342a even when the first vane 1351 is maximally drawn out, for example,
- the compression surface oil supply groove 1356a at the time when the first vane 1351 is maximally drawn out It is preferable to properly secure a sealing distance defined as a distance (interval) between the outer peripheral surface of the roller 134 and the roller 134 .
- the minimum sealing distance varies according to the specifications of the compressor, it is desirable to secure approximately 1.0 to 2.0 mm.
- the compression surface oil supply groove 1356a and the compression rear oil supply groove ( 1356b) may be of different lengths.
- the length L3 of the compression surface oil supply groove 1356a is the compression rear oil supply groove ( 1356b) may be formed longer than the length L4.
- the minimum length from the outer peripheral surface of the roller 134 to the compression surface oil supply groove 1356a is the outer peripheral surface of the roller 134. It becomes longer than the minimum length from the compressed back oil supply groove (1356b).
- the compression back oil supply groove (1356b) may be formed symmetrically with the compression surface oil supply groove (1356a) described above. Accordingly, compression back support portions 1356d may be formed on both sides of the axial direction of the compression back oil supply groove 1356b, respectively.
- the compression back oil supply groove 1356b is similar to the compressed surface oil supply groove 1356a described above in its basic configuration and its effect, the description thereof is replaced with a description of the compression surface oil supply groove 1356a. .
- the compression surface oil supply groove (1356a) and the compression back oil supply groove (1356b) are respectively formed in both second corners (1351h) as in this embodiment, the compression surface oil supply groove (1356a) and the compression rear oil supply groove ( 1356b) by lubricating the friction surfaces between the compression surface 1351e and the compression rear surface 1351f of the first vane 1351 and both inner surfaces of the first vane slot 1342a facing them by lubricating these friction surfaces with the oil filled in 1356b). Friction loss and wear can be suppressed.
- both second corners 1351h is formed in a chamfer shape. Accordingly, friction loss and wear between the first vane 1351 and the vane slot 1342a by reducing the friction area between the inner surface of the first vane slot 1342a and both sides of the first vane 1351 facing it. can be suppressed.
- the width direction depth (hereinafter, the depth) (D31) of the compressed surface oil supply groove (1356a) and the depth (D32) of the compressed rear oil supply groove (1356b) may be formed to be the same as each other, but in some cases, they are different from each other may be formed.
- FIG. 13 is a cross-sectional view showing another embodiment of the oil supply groove in FIG.
- the width direction depth (hereinafter, the depth) (D32) of the compression back oil supply groove (1356b) may be formed shallow compared to the depth (D31) of the compression surface oil supply groove (1356a). Accordingly, it is possible to suppress friction loss and wear at the portion where the friction load is greatest, that is, the second edge 1351h where the vane compression surface 1351e and the rear vane end surface 1351b meet.
- the vane tip end face 1351a may be pushed in the reverse rotation direction of the roller 134 by the gas reaction force of the compression chamber. Then, the rear end face 1351b of the first vane 1351 is pushed in the opposite direction to the end face 1351a of the vane, that is, in the direction of rotation of the roller 134, so that the second edge 1351h is in the first vane slot 1342a. It can be the most closely attached.
- the depth (D31) of the compression surface oil supply groove (1356a) is formed to be deeper than the depth (D32) of the compression surface oil supply groove (1356b) on the opposite side as in this embodiment, the second edge (1351h) with a relatively large friction load. ), friction loss and wear can be suppressed.
- the compression surface oil supply groove and the compression rear oil supply groove are formed to be stepped, respectively, but in some cases, at least one of the compression surface oil supply groove and the compression rear oil supply groove may be formed to be inclined.
- Figure 14 is a perspective view showing another embodiment of the oil supply groove in Figure 11,
- Figure 15 is a "VII-VII" front sectional view of Figure 14.
- the first vane 1351 according to the present embodiment is formed in a rectangular parallelepiped as described above, so that the compression surface oil supply groove 1356a is formed on the vane compression surface 1351e, and the vane compression rear surface 1351f ) Compression back oil supply grooves (1356b) may be formed, respectively.
- the compression surface oil supply groove 1356a may be formed obliquely in the front and rear direction at the second edge 1351h where the vane compression surface 1351e and the rear end surface 1351b meet.
- the compression surface oil supply groove (1356a) may be formed to be inclined from the middle of the vane rear end surface (1351b) to the vane front end surface (1351a).
- the compression surface oil supply groove 1356a may be formed at the same inclination angle along the radial direction and the axial direction. Accordingly, the compression surface oil supply groove (1356a) may be formed in a triangular cross-sectional shape having the same depth and the same area along the axial direction, through which the back pressure by the oil accommodated in the compression surface oil supply groove (1356a) is in the axial direction. Accordingly, the same occurrence may occur, and thus the behavior of the vane may be stabilized.
- the compression back oil supply groove (1356b) may be formed symmetrically with the compression surface oil supply groove (1356a) described above.
- the basic configuration of the compressed rear oil supply groove (1356b) and the effect thereof are similar to the compressed surface oil supply groove (1356a) described above, so a description thereof is replaced with a description of the compressed surface oil supply groove (1356a).
- the length (L4) of the compressed back oil supply groove (1356b) may be formed shorter than the length (L3) of the compressed surface oil supply groove (1356a). Accordingly, the second edge 1351h on the side of the vane compression rear surface 1351f reduces the friction area in close contact with the inner surface of the vane slot 1342a facing it in the circumferential direction, while reducing the compression back surface oil supply groove 1356b. An appropriate sealing distance from the rear surface 1351f to the outer peripheral surface of the roller 134 may be secured.
- the compression surface oil supply groove and the compression rear oil supply groove are formed one by one, respectively, but in some cases, the compression surface oil supply groove and the compression surface oil supply groove may be formed in plurality.
- FIG. 16 is a perspective view showing another embodiment of the oil supply groove in FIG. 11 .
- the first vane 1351 has a second edge ( A compression surface oil supply groove (1356a) is formed in 1351h), and a compression rear oil supply groove (1356b) may be formed in the second edge (1351h) between the compressed rear surface of the vane (1351e) and the rear end surface (1351b) of the vane.
- the basic configuration of the compressed surface oil supply groove (1356a) and the compressed rear oil supply groove (1356b) and the effect thereof are similar to the above-described embodiments.
- the compressed surface oil supply groove (1356a) and the compressed rear oil supply groove (1356b) may be formed to be stepped, respectively, may be formed to be inclined.
- a step difference example will be mainly described.
- a plurality of compression surface oil supply grooves (1356a) and compressed rear oil supply grooves (1356b) according to this embodiment may be formed in plural, respectively.
- the compression surface oil supply groove (1356a) may be formed with a plurality of compression surface oil supply groove (1356a) at a predetermined interval along the axial direction.
- the oil can be divided and retained for each of the plurality of compression surface oil supply grooves 1356a, and through this, the oil of the upper half is concentrated to the lower half by its own weight while the compressed surface By suppressing escape from the oil supply groove (1356a), it can be uniformly lubricated between the vane 1351 and the roller 134 along the axial direction.
- a plurality of compression surface oil supply grooves (1356a) may be formed in the same standard along the axial direction, may be formed in different standards.
- the vane 1351 can be easily processed.
- the plurality of compressed surface oil supply grooves 1356a are formed in different sizes, the width or depth of the compressed surface oil supply groove 1356a located in the upper half is larger than that of the compressed surface oil supply groove 1356a located in the lower half. can be formed. Accordingly, even if the oil flows down by its own weight, it is possible to secure a certain amount of oil in the compression surface oil supply groove 1356a located in the upper half.
- the compressed surface oil supply groove (1356a) may be formed to have a larger width and depth than the compressed rear oil supply groove (1356b). Even in this case, even when the vane tip end surface 1351a of the vane is inserted inclined in the rotational direction of the roller 134, the sealing distance in the compressed rear oil supply groove 1356b can be secured. In addition, even if the inner end of the vane 1351 receives a force pressed in the rotational direction of the roller 134 due to the pressure difference in the compression chambers located on both sides of the vane 1351 , the second edge 1351h faces the vane slot. It is possible to reduce friction loss or wear by suppressing strong adhesion to the inner surface of the 1342a.
- the oil supply groove is formed on the upper and lower surfaces of the vane, or is formed on the compression surface and the compression rear surface, but in some cases, the oil supply groove is formed on the upper and lower surfaces of the vane, and the compression surface. and may be respectively formed on the compression back surface.
- FIG. 17 is a perspective view showing another embodiment of the vane in FIG. 1 .
- the first vane 1351 has an upper side oil supply groove 1355a and a lower side oil supply groove that form an axial oil supply groove on the vane upper side surface 1351c and the vane lower side surface 1351d.
- the compression surface lubrication groove (1356a) and the compression rear lubrication groove (1356b) constituting the circumferential direction oil supply groove in the vane compression surface (1351c) and the compression rear surface (1351d) may be formed, respectively.
- an axial oil supply groove is formed on the vane upper side surface 1351c and the vane lower side surface 1351d as described above, and the circumferential direction oil supply groove is formed on the vane compression surface 1351c and the vane compression rear surface 1351d. It is possible to suppress friction loss and wear on the axial friction surface, as well as suppress friction loss and wear on the circumferential friction surface.
- the vane rotary compressor according to the present embodiment may be more effective when using a high-pressure refrigerant such as R32, R410a, and CO 2 .
- a high-pressure refrigerant such as R32, R410a, and CO 2 .
- the pressure difference between the compression chambers is large, so that the vane and the bearing are in closer contact. This can increase friction loss and wear between the vane and the bearing.
- the oil supply grooves are respectively formed on the axial side surfaces of the vanes as in the present embodiment, friction loss and wear between the vanes and the main bearings and sub bearings facing them can be reduced.
- the same can be applied between vanes and rollers. That is, when a high-pressure refrigerant is applied, the gas reaction force acting on the vane in the circumferential direction may be further increased while the pressure of the compression chamber is increased. Due to this, the inner end edge of the vane may be in close contact with the vane slot, causing friction loss and wear. In this case, when the lubricating grooves are respectively formed on the circumferential side surfaces described above, friction loss and wear between the vanes and the vane slots can be reduced.
- oil supply groove in the above-described embodiments may be equally applied to other types of rotary compressors.
- an axial oil supply groove 235a and/or a circumferential oil supply groove may be formed in the vane 235 even in an eccentric rotary compressor in which the roller 234 is eccentric with respect to the cylinder 233 . have.
- the eccentric part 224 is provided on the rotating shaft 223 , and the roller 234 may be rotatably inserted into the eccentric part 224 .
- a vane slot 233a is formed in the cylinder 233 , and a vane 235 may be slidably inserted into the vane slot 233a.
- the vane 235 may be slidably contacted, rotatably coupled, or integrally formed on the outer peripheral surface of the roller 234 to partition the compression space into a plurality of compression chambers.
- the vane 235 shows an example of sliding contact with the outer peripheral surface of the roller (234).
- An axial lubrication groove (235a), a circumferential lubrication groove (not shown) may be formed on the axial side surface of the vane 235 in the circumferential direction.
- the basic configuration of the axial lubrication groove 235a and the circumferential lubrication groove (not shown) and the effect thereof are the same as those of the above-described embodiments, so a detailed description thereof replaces the description of the above-described embodiments. .
- an axial oil supply groove (335a) and/or a circumferential oil supply groove may be formed in the vane 335 .
- the concentric rotary compressor according to this embodiment is provided with a roller 334 on the rotating shaft 323, the roller 334 is formed in an elliptical shape so that both ends constituting the long axis are in contact with the inner circumferential surface of the cylinder 333
- the compression space may be partitioned into a plurality of compression chambers together with the plurality of vanes 335 provided in the vane slot 333a.
- An axial lubrication groove (335a), a circumferential lubrication groove (not shown) may be formed on the axial side surface of the vane 335 .
- the basic configuration of the axial lubrication groove (335a) and the circumferential lubrication groove (not shown) and the effect thereof are the same as those of the above-described embodiments, so a detailed description thereof replaces the description of the above-described embodiments. .
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Abstract
Description
Claims (21)
- 케이싱;상기 케이싱의 내부에 구비되어 압축공간을 형성하는 실린더;상기 실린더의 축방향 양쪽에 각각 구비되며, 축방향으로 관통되는 메인베어링구멍과 서브베어링구멍이 각각 구비되는 메인베어링 및 서브베어링;상기 메인베어링구멍과 상기 서브베어링구멍을 관통하여 지지되는 회전축;상기 회전축에 구비되어 상기 압축공간에 편심지게 구비되는 롤러; 및상기 롤러 또는 상기 실린더에 구비된 베인슬롯에 미끄러지게 삽입되어 상기 압축공간을 복수 개의 압축실로 분리하는 적어도 한 개 이상의 베인을 포함하며,상기 베인은,상기 메인베어링과 상기 서브베어링을 마주보는 양쪽 축방향측면 중에서 적어도 한 쪽에는 급유홈이 형성되며,상기 급유홈은,상기 베인의 폭방향보다 길이방향으로 길게 형성되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈은,상기 베인슬롯에 수용되는 베인후단면의 모서리에서 그 반대쪽인 베인선단면을 향해 길이방향으로 연장되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈은,상기 베인슬롯에 수용되는 베인후단면의 제1 모서리에서 기설정된 간격만큼 이격되어 그 반대쪽인 베인선단면을 향해 길이방향으로 연장되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈의 폭방향 양쪽에는 실링부가 각각 형성되고,상기 양쪽 실링부는 상기 급유홈의 폭보다 크거나 같게 형성되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈은,상기 베인의 양쪽 축방향측면에 각각 형성되고, 상기 양쪽 축방향측면에 형성되는 급유홈은 서로 대칭되게 형성되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈은,상기 베인의 양쪽 축방향측면에 각각 형성되고, 상기 양쪽 축방향측면에 형성되는 급유홈은 서로 비대칭되게 형성되는 로터리 압축기.
- 제1항에 있어서,상기 메인베어링과 상기 서브베어링 중에서 어느 한 쪽에 토출구가 형성되고,상기 급유홈은,상기 토출구가 형성된 쪽의 베어링을 마주보는 급유홈의 길이보다 상기 토출구가 형성되지 않은 쪽의 베어링을 마주보는 급유홈의 길이가 더 길게 형성되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈은,상기 베인슬롯에 수용되는 베인후단면쪽에 형성되는 제1 급유홈과, 상기 제1 급유홈에서 상기 베인후단면의 반대쪽인 베인선단면을 향해 연장되는 제2 급유홈을 포함하고,상기 제1 급유홈의 체적은 상기 제2 급유홈의 체적보다 넓게 형성되는 로터리 압축기.
- 제8항에 있어서,상기 제1 급유홈은,상기 베인후단면에 연통되도록 상기 베인후단면의 제1 모서리에서 연장되는 로터리 압축기.
- 제8항에 있어서,상기 제1 급유홈은,상기 베인후단면에서 분리되도록 상기 베인후단면의 제1 모서리에서 기설정된 간격만큼 이격되는 로터리 압축기.
- 제1항에 있어서,상기 급유홈은,상기 베인의 양쪽 원주방향측면 중에서 적어도 어느 한쪽에 형성되며, 상기 베인슬롯에 수용되는 베인후단면에 연통되도록 상기 베인후단면의 제2 모서리에서 연장되는 로터리 압축기.
- 제11항에 있어서,상기 제2 모서리에는,상기 급유홈의 축방향 양쪽에서 각각 구비되어 상기 베인슬롯의 내측면에 접하는 지지부가 형성되고,상기 지지부는 상기 급유홈보다 돌출되도록 상기 베인후단면에서 연장되는 로터리 압축기.
- 제11항에 있어서,상기 급유홈은,상기 베인후단면의 제2 모서리에서 축방향을 따라 기설정된 간격을 두고 복수 개가 형성되는 로터리 압축기.
- 제11항에 있어서,상기 급유홈은,상기 롤러의 회전방향쪽에 형성되는 급유홈이 반대쪽 급유홈보다 상기 베인의 폭방향으로 깊게 형성되는 로터리 압축기.
- 제11항에 있어서,상기 베인은 상기 베인슬롯에 수용되는 베인후단면보다 그 반대쪽인 베인선단면이 상기 롤러의 회전방향쪽으로 경사지게 배치되고,상기 급유홈은 상기 베인의 양쪽 원주방향측면에 각각 형성되며,상기 급유홈중에서 상기 베인의 회전방향쪽 급유홈은 그 반대쪽 급유홈보다 상기 베인후단면의 반대쪽인 베인선단면을 향해 더 길게 형성되는 로터리 압축기.
- 케이싱;상기 케이싱의 내부에 구비되어 압축공간을 형성하는 실린더;상기 실린더의 축방향 양쪽에 각각 구비되며, 축방향으로 관통되는 메인베어링구멍과 서브베어링구멍이 각각 구비되는 메인베어링 및 서브베어링;상기 메인베어링구멍과 상기 서브베어링구멍을 관통하여 지지되는 회전축;상기 회전축에 구비되어 상기 압축공간에 편심지게 구비되는 롤러; 및상기 롤러 또는 상기 실린더에 구비된 베인슬롯에 미끄러지게 삽입되어 상기 압축공간을 복수 개의 압축실로 분리하는 적어도 한 개 이상의 베인을 포함하며,상기 베인은 양쪽 원주방향측면 중에서 적어도 어느 한쪽에 급유홈이 형성되며,상기 급유홈은,상기 베인슬롯에 수용되는 베인후단면에 연통되도록 상기 베인후단면의 제2 모서리에서 연장되는 로터리 압축기.
- 제16항에 있어서,상기 제2 모서리에는,상기 급유홈의 축방향 양쪽에서 각각 구비되어 상기 베인슬롯의 내측면에 접하는 지지부가 형성되고,상기 지지부는 상기 급유홈보다 돌출되도록 상기 베인후단면에서 연장되는 로터리 압축기.
- 제16항에 있어서,상기 급유홈은,상기 베인후단면의 제2 모서리에서 축방향을 따라 기설정된 간격을 두고 복수 개가 형성되는 로터리 압축기.
- 제16항에 있어서,상기 급유홈은,상기 롤러의 회전방향쪽에 형성되는 급유홈이 반대쪽 급유홈보다 상기 베인의 폭방향으로 깊게 형성되는 로터리 압축기.
- 제16항에 있어서,상기 베인은 상기 베인슬롯에 수용되는 베인후단면보다 그 반대쪽인 베인선단면이 상기 롤러의 회전방향쪽으로 경사지게 배치되고,상기 급유홈은 상기 베인의 양쪽 원주방향측면에 각각 형성되며,상기 급유홈중에서 상기 베인의 회전방향쪽 급유홈은 그 반대쪽 급유홈보다 상기 베인선단면쪽으로 더 길게 형성되는 로터리 압축기.
- 제1항 내지 제20항 중 어느 한 항에 있어서,상기 롤러에는 상기 베인슬롯이 상기 롤러의 외주면을 따라 적어도 한 개 이상 형성되며, 상기 롤러의 내부에는 상기 베인슬롯에 각각 연통되는 적어도 한 개이 상의 배압챔버가 축방향을 관통하여 형성되고,상기 메인베어링과 상기 서브베어링 중에서 적어도 어느 한쪽에는 상기 배압챔버와 연통되는 배압포켓이 형성되며,상기 급유홈은,적어도 일부가 상기 배압포켓에 축방향으로 중첩되는 로터리 압축기.
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Citations (6)
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JPH10169583A (ja) * | 1996-12-06 | 1998-06-23 | Daikin Ind Ltd | ロータリー圧縮機 |
JPH1137072A (ja) * | 1997-07-15 | 1999-02-09 | Seiko Seiki Co Ltd | 気体圧縮機 |
CN2528971Y (zh) * | 2001-12-28 | 2003-01-01 | 上海日立电器有限公司 | 一种叶片上带油槽的一体化活塞 |
JP2006077597A (ja) * | 2004-09-07 | 2006-03-23 | Calsonic Compressor Inc | 気体圧縮機 |
JP2013213438A (ja) | 2012-04-02 | 2013-10-17 | Calsonic Kansei Corp | 気体圧縮機 |
JP2017066889A (ja) * | 2015-09-28 | 2017-04-06 | 東芝キヤリア株式会社 | 回転式圧縮機及び冷凍サイクル装置 |
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2021
- 2021-03-30 KR KR1020210041370A patent/KR102508196B1/ko active IP Right Grant
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2022
- 2022-03-18 EP EP22781451.4A patent/EP4317693A1/en active Pending
- 2022-03-18 WO PCT/KR2022/003801 patent/WO2022211331A1/ko active Application Filing
- 2022-03-18 CN CN202280025505.6A patent/CN117083460A/zh active Pending
- 2022-03-18 US US18/283,057 patent/US20240167476A1/en active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH10169583A (ja) * | 1996-12-06 | 1998-06-23 | Daikin Ind Ltd | ロータリー圧縮機 |
JPH1137072A (ja) * | 1997-07-15 | 1999-02-09 | Seiko Seiki Co Ltd | 気体圧縮機 |
CN2528971Y (zh) * | 2001-12-28 | 2003-01-01 | 上海日立电器有限公司 | 一种叶片上带油槽的一体化活塞 |
JP2006077597A (ja) * | 2004-09-07 | 2006-03-23 | Calsonic Compressor Inc | 気体圧縮機 |
JP2013213438A (ja) | 2012-04-02 | 2013-10-17 | Calsonic Kansei Corp | 気体圧縮機 |
JP2017066889A (ja) * | 2015-09-28 | 2017-04-06 | 東芝キヤリア株式会社 | 回転式圧縮機及び冷凍サイクル装置 |
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CN117083460A (zh) | 2023-11-17 |
EP4317693A1 (en) | 2024-02-07 |
KR20220136551A (ko) | 2022-10-11 |
US20240167476A1 (en) | 2024-05-23 |
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