WO2013105131A1 - ベーン型圧縮機 - Google Patents
ベーン型圧縮機 Download PDFInfo
- Publication number
- WO2013105131A1 WO2013105131A1 PCT/JP2012/000114 JP2012000114W WO2013105131A1 WO 2013105131 A1 WO2013105131 A1 WO 2013105131A1 JP 2012000114 W JP2012000114 W JP 2012000114W WO 2013105131 A1 WO2013105131 A1 WO 2013105131A1
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- WIPO (PCT)
- Prior art keywords
- vane
- peripheral surface
- cylinder
- inner peripheral
- rotor
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
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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
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/321—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/352—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 vanes being pivoted on the axis of 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
- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
-
- 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
Definitions
- the present invention relates to a vane type compressor.
- one or a plurality of portions are formed in the rotor portion of a rotor shaft (a rotor portion in which a cylindrical rotor portion that rotates in a cylinder and a shaft that transmits rotational force to the rotor portion are integrated).
- a general vane type compressor having a configuration in which a vane is fitted into a vane groove and the tip of the vane slides while contacting the inner peripheral surface of the cylinder (for example, see Patent Document 1).
- the rotor shaft has a hollow interior and a vane fixed shaft disposed therein.
- the vane is rotatably attached to the fixed shaft, and a pair of semicircular rods is formed near the outer periphery of the rotor portion.
- a vane type compressor in which a vane is rotatably held with respect to a rotor part via a clamping member (bush) (see, for example, Patent Document 2).
- the oil film is not formed between the inner circumferential surface of the cylinder and the vane tip. It is not formed, and it becomes a boundary lubrication state without entering a fluid lubrication state.
- the friction coefficient in the lubrication state is about 0.001 to 0.005 in the fluid lubrication state, but becomes very large in the boundary lubrication state, and is generally about 0.05 or more.
- the interior of the rotor part is made hollow, and a vane is rotatably supported at the center of the inner peripheral surface of the cylinder, and the vane is a rotor.
- a method of holding a vane via a pinching member in the vicinity of the outer peripheral portion of the rotor portion so as to be rotatable with respect to the portion has been proposed.
- the vane is rotatably supported at the center of the inner peripheral surface of the cylinder.
- the tip of the vane rotates along the inner peripheral surface of the cylinder. For this reason, a minute gap is maintained between the vane tip and the inner peripheral surface of the cylinder, and it is possible to operate without contact, no loss due to sliding at the vane tip occurs, A vane type compressor in which the inner peripheral surface of the cylinder is not worn can be obtained.
- the end plate is provided in the both end surfaces of the rotor part.
- the end plate on one side has a disk shape because it is necessary to transmit power from the rotating shaft, and the rotating shaft is connected to the center of the end plate.
- it is necessary to comprise the end plate of the other side so that it may not interfere with the rotation range of a vane fixed axis
- the outer diameter and the rotation center portion of the rotor portion are required to have high accuracy.
- the rotor part and the end plate are composed of separate parts, the outer diameter of the rotor part, such as the distortion generated by the fastening of the rotor part and the end plate, and the coaxial displacement between the rotor part and the end plate, etc. There is also a problem that the accuracy of the rotation center is deteriorated.
- the present invention has been made in order to solve the above-described problems, and can suppress wear of the tip of the vane, reduce the bearing sliding loss by being able to support the rotating shaft portion with a small diameter, and reduce the rotor portion.
- An object of the present invention is to obtain a vane type compressor that improves the accuracy of the outer diameter and the rotation center.
- the compression element for compressing the refrigerant is displaced by a predetermined distance from the center axis of the inner peripheral surface in the cylinder in which the cylindrical inner peripheral surface is formed and the cylinder.
- a cylindrical rotor portion that rotates about a rotation axis, a rotor shaft having a rotation shaft portion that transmits a rotational force from the outside to the rotor portion, and one opening portion of the inner peripheral surface of the cylinder
- a frame that closes and supports the rotating shaft portion by the main bearing portion, a cylinder head that closes the other opening of the inner peripheral surface of the cylinder and supports the rotating shaft portion by the main bearing portion, and the rotor
- the vane Surrounded by the vane, the outer peripheral part of the rotor part, and the inner peripheral part of the cylinder in a state where the normal line of the arc shape of the end part and the normal line of the inner peripheral surface of the cylinder are almost coincident with each other.
- the vane is supported so as to compress the refrigerant in a space to be supported, the vane is supported to be swingable and movable with respect to the rotor portion, and the tip end portion of the vane is located on the inner peripheral surface side of the cylinder.
- Vane support means for holding the tip portion and the inner peripheral surface so as to have a predetermined gap when moved to the maximum is provided, and the rotor shaft and the rotating shaft portion are integrally formed with the rotor shaft.
- the vane includes a pair of partial rings provided on an end surface on the frame side and the center side of the rotor portion, and an end surface on the cylinder head side and the center side of the rotor portion.
- a concave portion concentric with the inner peripheral surface of the cylinder is formed on the cylinder side end surface of the frame and the cylinder head, and the vane aligner portion is fitted into the concave portion,
- a stopper that is supported by a vane aligner bearing portion that is an outer peripheral surface of the recess, is formed inside the recess of the frame and / or the cylinder head, and restricts movement of the vane aligner portion inward of the rotor portion. It is equipped with.
- the compressor efficiency due to an increase in mechanical loss while suppressing the leakage of the refrigerant from the tip portion. can be suppressed, and wear at the tip can be suppressed.
- the mechanism that the vane necessary to perform the compression operation so that the arc shape of the tip of the vane and the normal line of the inner peripheral surface of the cylinder always coincide substantially rotates around the center of the inner peripheral surface of the cylinder.
- FIG. 2 is a cross-sectional view taken along the line II of FIG. 1 in the vane type compressor 200 according to the first embodiment of the present invention.
- FIG. 5 is a cross-sectional view taken along the line JJ in FIG. 4 showing the rotation operation of the vane aligner portions 5c and 6c of the vane type compressor 200 according to Embodiment 1 of the present invention. It is principal part sectional drawing around the vane part 5a of the 1st vane 5 of the vane type compressor 200 which concerns on Embodiment 1 of this invention. 5 is a cross-sectional view taken along the line JJ in FIG. 4 and an enlarged view of the cross-sectional view at a rotation angle of 0 ° in FIG. 7 in the vane type compressor 200 according to Embodiment 1 of the present invention.
- FIG. 6 is a structural diagram around a vane aligner bearing portion 2b of a vane compressor 200 according to a third embodiment of the present invention. It is a structural diagram of the periphery of the vane aligner bearing portion 2b of the vane type compressor 200 according to the fourth embodiment of the present invention.
- FIG. 1 is a longitudinal sectional view of a vane type compressor 200 according to Embodiment 1 of the present invention
- FIG. 2 is an exploded perspective view of a compression element 101 of the vane type compressor 200
- 3 is a plan view and a front view of the first vane 5 and the second vane 6 of the vane type compressor 200
- FIG. 4 is a longitudinal section around the vane aligner bearing portion 2b of the vane type compressor 200.
- FIGS the structure of the vane type compressor 200 will be described with reference to FIGS.
- a vane type compressor 200 is located in a hermetic container 103 forming an outer shape, a compression element 101 accommodated in the hermetic container 103, and an upper part of the compression element 101, and drives the compression element 101.
- the electric element 102 and an oil sump 104 that stores the refrigerating machine oil 25 are provided at the bottom in the sealed container 103.
- the sealed container 103 forms the outer shape of the vane type compressor 200, houses the compression element 101 and the electric element 102 therein, and seals the refrigerant and the refrigerating machine oil.
- a suction pipe 26 for sucking the refrigerant into the sealed container 103 is installed on the side surface of the sealed container 103, and a discharge pipe 24 for discharging the compressed refrigerant to the outside is installed on the upper surface of the sealed container 103. Yes.
- the compression element 101 compresses the refrigerant sucked into the sealed container 103 from the suction pipe 26, and includes the cylinder 1, the frame 2, the cylinder head 3, the rotor shaft 4, the first vane 5, the second vane 6, and , Bushes 7 and 8.
- the cylinder 1 has a substantially cylindrical shape as a whole, and a substantially circular penetrating portion 1f is formed so as to be centered at a position eccentric from the center of the cylindrical circle in the axial direction. Further, a notch 1c that is wound in an R shape from the center of the penetrating portion 1f to the outside is provided on a part of the cylinder inner peripheral surface 1b that is the inner peripheral surface of the penetrating portion 1f. A suction port 1a is opened at 1c. The suction port 1a communicates with the suction pipe 26, and the refrigerant is sucked into the through portion 1f from the suction port 1a.
- a discharge port 1d is cut out and provided on the opposite side of the suction port 1a with a nearest contact point 32, which will be described later, between the nearest contact point 32 and the side facing the frame 2 described later ( (See FIG. 2).
- two oil return holes 1e are provided in the outer peripheral portion of the cylinder 1 in the axial direction and at positions symmetrical to the center of the through portion 1f.
- the frame 2 has a substantially T-shaped vertical cross section, and a portion in contact with the cylinder 1 has a substantially disk shape, and closes one opening (upper side in FIG. 2) of the through portion 1f of the cylinder 1. .
- the central portion of the frame 2 has a cylindrical shape.
- the cylindrical portion is hollow, and a main bearing portion 2c is formed here. Further, the end surface of the frame 2 on the cylinder 1 side and the main bearing portion 2c are formed with a recess 2a whose outer peripheral surface is formed concentrically with the cylinder inner peripheral surface 1b.
- the concave portion 2a is provided with a step between the outer peripheral side and the inner peripheral side, and an annular groove portion 2e is formed deeper toward the outer peripheral side, and a first vane 5 described later is formed in the groove portion 2e.
- the vane aligner portion 5c and the vane aligner portion 6c of the second vane 6 are fitted. At this time, the vane aligner portions 5c and 6c are supported by the vane aligner bearing portion 2b which is the outer peripheral surface of the recess 2a.
- the frame 2 is provided with a discharge port 2d that communicates with a discharge port 1d provided in the cylinder 1 and penetrates in the axial direction.
- a discharge valve 2d is provided at an opening on the opposite side of the cylinder 1 from the discharge port 2d. 27 and a discharge valve presser 28 for restricting the opening degree of the discharge valve 27 are attached.
- the cylinder head 3 has a substantially T-shaped longitudinal cross-section, and the portion in contact with the cylinder 1 has a substantially disk shape, and closes the other opening (the lower side in FIG. 2) of the penetrating portion 1f of the cylinder 1. It is. Further, the central portion of the cylinder head 3 has a cylindrical shape, and this cylindrical shape is hollow, and a main bearing portion 3c is formed here. Further, a concave portion 3a having an outer peripheral surface concentrically formed with the cylinder inner peripheral surface 1b is formed in the end surface of the cylinder head 3 on the cylinder 1 side and the main bearing portion 3c.
- the concave portion 3a is provided with a step between the outer peripheral side and the inner peripheral side, and an annular groove portion 3e is formed deeper toward the outer peripheral side, and a first vane 5 described later is formed in the groove portion 3e.
- the vane aligner portion 5d and the vane aligner portion 6d of the second vane 6 are fitted. At this time, the vane aligner portions 5d and 6d are supported by the vane aligner bearing portion 3b which is the outer peripheral surface of the recess 3a.
- the rotor shaft 4 is a substantially cylindrical rotor portion 4a that rotates on a central axis that is eccentric from the central axis of the through-hole 1f of the cylinder 1 in the cylinder 1, and from the center of a circle that is the upper surface of the rotor portion 4a.
- the rotating shaft portion 4b extending vertically upward on the upper surface and the rotating shaft portion 4c extending vertically downward on the lower surface from the center of the circle that is the lower surface of the rotor portion 4a are integrated. ing.
- the rotation shaft portion 4 b is inserted and supported by the main bearing portion 2 c of the frame 2, and the rotation shaft portion 4 c is inserted and supported by the main bearing portion 3 c of the cylinder head 3.
- the rotor portion 4a has a substantially circular cross section perpendicular to the axial direction of the cylindrical rotor portion 4a and penetrates in the axial direction to form bush holding portions 4d and 4e and vane relief portions 4f and 4g.
- the bush holding portions 4d and 4e are formed at positions symmetrical to the rotor portion 4a, and vane relief portions 4f and 4g are formed on the outer sides of the bush holding portions 4d and 4e, respectively. That is, the centers of the rotor portion 4a, the bush holding portions 4d and 4e, and the vane relief portions 4f and 4g are formed so as to be substantially linearly arranged.
- the bush holding portion 4d and the vane escape portion 4f communicate with each other, and the bush holding portion 4e and the vane escape portion 4g communicate with each other. Further, the axial end portions of the vane relief portions 4 f and 4 g communicate with the concave portion 2 a of the frame 2 and the concave portion 3 a of the cylinder head 3.
- an oil pump 31 using the centrifugal force of the rotor shaft 4 as described in, for example, Japanese Patent Application Laid-Open No. 2009-62820 is provided at the lower end portion of the rotating shaft portion 4c of the rotor shaft 4.
- the oil pump 31 is provided at the shaft center portion at the lower end of the rotating shaft portion 4c of the rotor shaft 4 and extends upward from the lower end of the rotating shaft portion 4c to the inside of the rotor portion 4a and the rotating shaft portion 4b. It communicates with 4h. Further, the rotary shaft portion 4b is provided with an oil supply passage 4i for connecting the oil supply passage 4h and the recess 2a, and the rotary shaft portion 4c is provided with an oil supply passage 4j for connecting the oil supply passage 4h and the recess 3a. Furthermore, an oil drain hole 4k that communicates with the internal space of the sealed container 103 is provided at a position above the main bearing portion 2c of the rotary shaft portion 4b.
- the first vane 5 has a vane portion 5a, which is a substantially square plate-shaped member, an arc shape provided on the upper end surface of the vane portion 5a on the frame 2 side and the rotating shaft portion 4b side, that is, a partial ring shape.
- the vane aligner portion 5c and the vane aligner portion 5d having a circular arc shape, that is, a partial ring shape, provided on the lower end surface of the vane portion 5a on the cylinder head 3 side and the rotating shaft portion 4c side.
- the vane tip 5b which is the end surface of the vane portion 5a on the cylinder inner peripheral surface 1b side, is formed in an arc shape that protrudes outward, and the radius of curvature of the arc shape is the same as the radius of curvature of the cylinder inner peripheral surface 1b. It is formed so as to be substantially the same.
- the first vane 5 has the length direction of the vane portion 5a and the normal direction of the arc of the vane tip portion 5b passing through the center of the arc of the vane aligner portions 5c and 5d. Is formed. Further, as shown in FIG.
- the radial width of the arc shape of the vane aligner portion 5c is formed to be smaller than the groove width of the groove portion 2e of the frame 2 into which the vane aligner portion 5c is fitted.
- the radial width of the arc shape of the vane aligner portion 5d is formed to be smaller than the groove width of the groove portion 3e of the cylinder head 3 into which the vane aligner portion 5d is fitted.
- the second vane 6 has a vane portion 6a, which is a substantially square plate-shaped member, an arc shape provided on the upper end surface of the vane portion 6a on the frame 2 side and the rotating shaft portion 4b side, that is, a partial ring shape.
- the vane aligner portion 6c and the vane aligner portion 6d having an arc shape, that is, a partial ring shape, provided on the lower end surface of the vane portion 6a on the cylinder head 3 side and the rotating shaft portion 4c side.
- the vane tip 6b which is the end surface of the vane portion 6a on the cylinder inner peripheral surface 1b side, is formed in an outwardly convex arc shape, and the radius of curvature of the arc shape is substantially the same as the radius of curvature of the cylinder inner peripheral surface 1b. It is formed to be the same.
- the second vane 6 has a length direction of the vane portion 6a and a normal direction of the arc of the vane tip portion 6b passing through the centers of the arcs of the vane aligner portions 6c and 6d. Is formed. Further, as shown in FIG.
- the radial width of the arc shape of the vane aligner portion 6c is formed to be smaller than the groove width of the groove portion 2e of the frame 2 into which the vane aligner portion 6c is fitted.
- the radial width of the arc shape of the vane aligner portion 6d is formed to be smaller than the groove width of the groove portion 3e of the cylinder head 3 into which the vane aligner portion 6d is fitted.
- the bushes 7 and 8 are each composed of a pair of objects formed in a substantially semi-cylindrical shape.
- the bush 7 is fitted into the bush holding portion 4 d of the rotor shaft 4, and a plate-shaped vane portion 5 a is sandwiched between the pair of bushes 7. At this time, the vane portion 5a is held so as to be rotatable with respect to the rotor portion 4a and movable in the length direction thereof.
- the bush 8 is fitted into the bush holding portion 4 e of the rotor shaft 4, and a plate-shaped vane portion 6 a is sandwiched between the pair of bushes 8. At this time, the vane portion 6a is held so as to be rotatable with respect to the rotor portion 4a and movable in the length direction thereof.
- the bush holding portions 4d and 4e, the vane relief portions 4f and 4g, the bushes 7 and 8, and the vane aligner bearing portions 2b and 3b correspond to the “vane support means” of the present invention.
- the electric element 102 is composed of, for example, a brushless DC motor, and as shown in FIG. 1, the stator 21 fixed to the inner periphery of the hermetic container 103 and the inner side of the stator 21. It is comprised by the rotor 22 formed by these. Electric power is supplied to the stator 21 from a glass terminal 23 fixed to the upper surface of the hermetic container 103, and the rotor 22 is rotationally driven by this electric power.
- the rotor 22 is fixed with the rotating shaft portion 4b of the rotor shaft 4 described above. The rotating force of the rotor 22 is transmitted to the rotating shaft portion 4b when the rotor 22 is rotated. The entire shaft 4 is rotationally driven.
- FIG. 5 is a cross-sectional view taken along the line II of FIG. 1 in the vane compressor 200 according to Embodiment 1 of the present invention
- FIG. 6 is a diagram illustrating a compression operation of the vane compressor 200.
- the compression operation of the vane type compressor 200 will be described with reference to FIGS. 5 and 6.
- FIG. 5 shows a state where the rotor portion 4a of the rotor shaft 4 is in closest contact with one place (the closest contact point 32) of the cylinder inner peripheral surface 1b.
- the radius of the vane aligner bearing portions 2b and 3b is ra (see FIG. 7 described later) and the radius of the cylinder inner peripheral surface 1b is rc
- a distance rv (see FIG. 3) between the side and the vane tip 5b is expressed by the following equation (1).
- ⁇ represents the gap between the vane tip 5b and the cylinder inner peripheral surface 1b.
- the vane tip 5b of the first vane 5 is It will rotate without contacting the cylinder inner peripheral surface 1b.
- rv is set so that ⁇ is as small as possible, refrigerant leakage from the vane tip 5b is minimized.
- the relationship of the expression (1) is the same for the second vane 6, and the second vane 6 rotates while maintaining a narrow gap between the vane tip 6 b of the second vane 6 and the cylinder inner peripheral surface 1 b. Will be.
- the penetrating portion 1f of the cylinder 1 is formed by the closest contact 32 adjacent to the cylinder inner peripheral surface 1b, the vane tip 5b of the first vane 5, and the vane tip 6b of the second vane 6. Three spaces (a suction chamber 9, an intermediate chamber 10, and a compression chamber 11) are formed inside.
- the refrigerant sucked from the suction pipe 26 enters the suction chamber 9 through the suction port 1a of the notch 1c.
- the notch 1c is formed from the vicinity of the closest point 32 to the vane tip 5b of the first vane 5 and the inside of the cylinder.
- the compression chamber 11 communicates with the discharge port 2d provided in the frame 2 that is closed by the discharge valve 27 through the discharge port 1d of the cylinder 1 except when the refrigerant is discharged. Accordingly, the intermediate chamber 10 is a space formed in a rotation angle range that communicates with the suction port 1a up to a rotation angle of 90 °, but does not communicate with either the suction port 1a or the discharge port 1d, and thereafter the discharge port.
- the compression chamber 11 is communicated with 1d.
- bush centers 7a and 8a are the rotation centers of the bushes 7 and 8 and the rotation centers of the vanes 5a and 6a, respectively.
- the rotating shaft portion 4 b of the rotor shaft 4 receives the rotational force from the rotor 22 of the electric element 102, and the rotor portion 4 a rotates within the through portion 1 f of the cylinder 1.
- the bush holding portions 4d and 4e of the rotor portion 4a move on the circumference around the rotor shaft 4.
- the vane part 6a of the 2nd vane 6 also rotates with rotation of the rotor part 4a.
- the first vane 5 and the second vane 6 receive a centrifugal force generated by the rotation of the rotor portion 4a, and the vane aligner portions 5c and 6c and the vane aligner portions 5d and 6d are pressed against the vane aligner bearing portions 2b and 3b, respectively.
- the vane aligner bearing portions 2b and 3b rotate around the center of rotation.
- the vane aligner bearing portions 2b and 3b and the cylinder inner peripheral surface 1b are concentric, the first vane 5 and the second vane 6 rotate around the center of the cylinder inner peripheral surface 1b.
- the bushes 7 and 8 are respectively in the bush holding portions 4d and 4e so that the length directions of the vane portion 5a of the first vane 5 and the vane portion 6a of the second vane 6 pass through the center of the cylinder inner peripheral surface 1b.
- the bush centers 7a and 8a are rotated about the rotation center. That is, the rotor portion 4a rotates in a state in which the arc shape of the vane tip portions 5b and 6b and the normal line of the cylinder inner peripheral surface 1b are always substantially matched.
- FIG. 6 for the sake of simplicity, the illustration of the suction port 1a, the notch 1c, and the discharge port 1d is omitted, and the suction port 1a and the discharge port 1d are indicated by the arrows as suction and discharge, respectively.
- FIG. 6 is the closest point 32 where the rotor portion 4a of the rotor shaft 4 and the cylinder inner peripheral surface 1b are closest to each other, and one location where the vane portion 5a and the cylinder inner peripheral surface 1b face each other.
- angle 0 ° In FIG. 6, the positions of the vane portion 5 a and the vane portion 6 a in the case of “angle 0 °”, “angle 45 °”, “angle 90 °”, and “angle 135 °”, and the suction chamber 9 in each case, The state of the intermediate chamber 10 and the compression chamber 11 is shown. Further, in the “angle 0 °” diagram of FIG. 6, the rotation direction of the rotor shaft 4 (clockwise in FIG. 6) is indicated by an arrow.
- the right space partitioned by the closest contact point 32 and the vane portion 6a of the second vane 6 is the intermediate chamber 10, and communicates with the suction port 1a via the notch portion 1c. And inhales the gas refrigerant.
- the left space partitioned by the closest contact 32 and the vane portion 6a of the second vane 6 becomes the compression chamber 11 communicating with the discharge port 1d.
- the space partitioned by the vane portion 5a of the first vane 5 and the closest point 32 becomes the suction chamber 9 at an “angle of 45 °”.
- the intermediate chamber 10 partitioned by the vane portion 5a of the first vane 5 and the vane portion 6a of the second vane 6 communicates with the suction port 1a through the notch portion 1c, and the volume of the intermediate chamber 10 is “ Since the angle is larger than that at “0 °”, the suction of the gas refrigerant is continued.
- the space partitioned by the vane portion 6a of the second vane 6 and the nearest contact point 32 is the compression chamber 11, and the volume of the compression chamber 11 is smaller than that at the “angle 0 °”, and the gas refrigerant is compressed. The pressure gradually increases.
- the vane tip 5b of the first vane 5 overlaps with the point A on the cylinder inner peripheral surface 1b, so that the intermediate chamber 10 does not communicate with the suction port 1a. Thereby, the suction of the gas refrigerant into the intermediate chamber 10 is completed.
- the volume of the intermediate chamber 10 is substantially maximum.
- the volume of the compression chamber 11 becomes even smaller than when the angle is 45 °, and the pressure of the gas refrigerant increases.
- the volume of the suction chamber 9 is larger than that at the “angle 45 °” and communicates with the suction port 1a through the notch 1c to suck the gas refrigerant.
- the volume of the intermediate chamber 10 becomes smaller than that at “angle 90 °”, and the pressure of the refrigerant increases. Further, the volume of the compression chamber 11 becomes smaller than that at the “angle 90 °”, and the pressure of the refrigerant rises. Since the volume of the suction chamber 9 becomes larger than that at the “angle of 90 °”, the suction of the gas refrigerant is continued.
- the vane portion 6a of the second vane 6 approaches the discharge port 1d, but when the pressure of the gas refrigerant in the compression chamber 11 exceeds the high pressure of the refrigeration cycle (including the pressure necessary to open the discharge valve 27).
- the discharge valve 27 is opened.
- the gas refrigerant in the compression chamber 11 passes through the discharge port 1 and the discharge port 2d and is discharged into the sealed container 103 as shown in FIG.
- the gas refrigerant discharged into the sealed container 103 passes through the electric element 102 and is discharged to the outside (the high pressure side of the refrigeration cycle) through the discharge pipe 24 fixed to the upper part of the sealed container 103. Therefore, the pressure in the sealed container 103 is a high discharge pressure.
- the volume of the suction chamber 9 gradually increases due to the rotation of the rotor portion 4a of the rotor shaft 4, and the suction of the gas refrigerant is continued. Thereafter, the suction chamber 9 moves to the intermediate chamber 10, but the volume gradually increases until halfway (until the vane portion (the vane portion 5 a or the vane portion 6 a) separating the suction chamber 9 and the intermediate chamber 10 faces the point A). The volume increases and the suction of the gas refrigerant is continued. In the middle of the process, the volume of the intermediate chamber 10 becomes maximum, and the communication with the suction port 1a is lost. Thus, the suction of the gas refrigerant is finished here.
- the volume of the intermediate chamber 10 gradually decreases, and the gas refrigerant is compressed. Thereafter, the intermediate chamber 10 moves to the compression chamber 11 and the compression of the gas refrigerant is continued.
- the gas refrigerant compressed to a predetermined pressure pushes up the discharge valve 27 through the discharge port 1d and the discharge port 2d, and is discharged into the sealed container 103.
- FIG. 7 is a cross-sectional view taken along the line JJ in FIG. 4 showing the rotational operation of the vane aligner portions 5c and 6c of the vane compressor 200 according to Embodiment 1 of the present invention.
- the rotation direction of the vane aligner portions 5 c and 6 c (clockwise in FIG. 7) is indicated by an arrow.
- the arrows indicating the rotation directions of the vane aligner portions 5c and 6c are omitted.
- the rotation of the rotor shaft 4 causes the vane portion 5a of the first vane 5 and the vane portion 6a of the second vane 6 to rotate about the center of the cylinder inner peripheral surface 1b.
- the vane aligner portions 5c and 6c are supported by the vane aligner bearing portion 2b in the groove portion 2e formed in the concave portion 2a, with the center of the cylinder inner peripheral surface 1b as the center of rotation. Rotate.
- the vane aligner portions 5d and 6d are supported by the vane aligner bearing portion 3b in the groove portion 3e formed in the recess 3a and rotate around the center of the cylinder inner peripheral surface 1b.
- the refrigerating machine oil 25 is sucked up from the oil sump 104 by the oil pump 31 by the rotation of the rotor shaft 4, and sent out to the oil supply path 4h.
- the refrigerating machine oil 25 sent out to the oil supply passage 4h is sent out to the recess 2a of the frame 2 through the oil supply passage 4i and to the recess 3a of the cylinder head 3 through the oil supply passage 4j.
- a part of the refrigerating machine oil 25 sent to the recesses 2a and 3a is sent to the grooves 2e and 3e, respectively, to lubricate the vane aligner bearings 2b and 3b, and also to vane relief parts 4f and 4g communicating with the recesses 2a and 3a To be supplied.
- the pressure in the sealed container 103 is a high discharge pressure
- the pressures in the recesses 2a and 3a and the vane relief portions 4f and 4g are also discharge pressures.
- a part of the refrigerating machine oil 25 fed to the recesses 2a and 3a is supplied to the main bearing portion 2c of the frame 2 and the main bearing portion 3c of the cylinder head 3 to be lubricated.
- FIG. 8 is a cross-sectional view of the main part around the vane portion 5a of the first vane 5 of the vane type compressor 200 according to Embodiment 1 of the present invention.
- the solid line arrows indicate the flow of the refrigerating machine oil 25. Since the pressure in the vane relief portion 4f is a discharge pressure and is higher than the pressure in the suction chamber 9 and the intermediate chamber 10, the refrigerating machine oil 25 lubricates the sliding portion between the side surface of the vane portion 5a and the bush 7. However, it is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force.
- the refrigerating machine oil 25 is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force while lubricating the sliding portion between the bush 7 and the bush holding portion 4d of the rotor shaft 4. Further, a part of the refrigerating machine oil 25 sent out to the intermediate chamber 10 flows into the suction chamber 9 while sealing the gap between the vane tip 5b and the cylinder inner peripheral surface 1b.
- the space partitioned by the vane portion 5a of the first vane 5 is the suction chamber 9 and the intermediate chamber 10.
- the rotation of the rotor shaft 4 proceeds and the vane portion 5a of the first vane 5 is advanced.
- the space partitioned by is the intermediate chamber 10 and the compression chamber 11. That is, even when the pressure in the compression chamber 11 reaches the same discharge pressure as the pressure of the vane escape portion 4f, the refrigerating machine oil 25 is sent out toward the compression chamber 11 by centrifugal force.
- the refrigerating machine oil 25 supplied to the main bearing portion 2 c is discharged into the space above the frame 2 through the gap between the main bearing portion 2 c and the rotating shaft portion 4 b.
- the oil is returned to the oil sump 104 through the oil return hole 1 e provided in the outer peripheral portion of the cylinder 1.
- the refrigerating machine oil 25 supplied to the main bearing portion 3c is returned to the oil sump 104 through the gap between the main bearing portion 3c and the rotating shaft portion 4c.
- the refrigerating machine oil 25 sent to the suction chamber 9, the intermediate chamber 10 and the compression chamber 11 through the vane relief portions 4f and 4g is finally discharged together with the gas refrigerant into the space above the frame 2 from the discharge port 2d.
- the oil is returned to the oil sump 104 through the oil return hole 1 e formed in the outer peripheral portion of the cylinder 1.
- the surplus refrigerating machine oil 25 is discharged into the space above the frame 2 from the oil drain hole 4 k above the rotor shaft 4.
- the oil is returned to the oil sump 104 through the oil return hole 1 e formed in the outer peripheral portion of the cylinder 1.
- FIG. 9 is a cross-sectional view taken along the line JJ in FIG. 4 and an enlarged view of the cross-sectional view at a rotation angle of 0 ° in FIG. 7 in the vane type compressor 200 according to Embodiment 1 of the present invention.
- FIG. 9A and FIG. 9B are diagrams showing a case in which no step is provided in the recess 2a, that is, no groove 2e is provided
- FIG. 9C is the present embodiment.
- the behavior of the first vane 5 and the second vane 6 when the pressure is abnormally increased by compressing the liquid refrigerant in the suction chamber 9, the intermediate chamber 10, or the compression chamber 11 will be described with reference to FIG. 9. To do.
- the first vane 5 moves a distance f ⁇ b> 1 until the vane aligner portion 5 c comes into contact with the rotating shaft portion 4 b of the rotor shaft 4.
- the second vane 6 has a distance f2 until the vane aligner portion 6c comes into contact with the rotating shaft portion 4b of the rotor shaft 4, and until the vane aligner portion 6c comes into contact with the vane aligner portion 5c at the circumferential ends. Therefore, the shorter one of the distances f3-f1 is moved.
- the moving distance of the second vane 6 is longer than the moving distance of the first vane 5.
- FIG. 9B shows the vane aligner bearing portion 2b with a reduced diameter so as to shorten the moving distance.
- the distance f1 which is the moving distance of the vane aligner portion 5c
- the distance f2 or the distance f3-f1 that is the movement distance of the second vane 6 is considerably longer than the distance f1 that is the movement distance of the first vane 5.
- the moving distance of the second vane 6 is long, the return to the original state is delayed, or the inertial force acting on the second vane 6 is increased, so that the vane aligner portion 6c is connected to the rotor shaft 4.
- the rotating shaft portion 4b or the vane aligner portion 5c may collide with a large force and cause damage.
- the pressure in the compression chamber 11 increases abnormally, and the force that pushes the first vane 5 and the second vane 6 toward the center of the cylinder inner peripheral surface 1b is the first vane 5 and the second vane. If it becomes larger than the centrifugal force which acts on 6, the 1st vane 5 and the 2nd vane 6 will be pushed and moved to the center direction of the cylinder internal peripheral surface 1b. At this time, since the vane aligner portions 5c and 6c are in contact with the inner diameter side of the groove portion 2e, the movement is restricted.
- the difference f0 between the groove width of the groove portion 2e and the radial width of the vane aligner portions 5c and 6c is the moving distance of the first vane 5 and the second vane 6.
- FIG. 9 shows a case where the rotation angle of the rotor shaft 4 is 0 °.
- the movement distances of the first vane 5 and the second vane 6 are the difference f0 even at other rotation angles. Accordingly, if the difference f0 is set to an appropriate amount, the first vane 5 and the second vane 6 are not delayed in returning to the original state, and the gap between the vane aligner portions 5c, 6c and the groove portion 2e is not delayed.
- the arc-shaped curvature radii of the vane tip 5b of the first vane 5 and the vane tip 6b of the second vane 6 are formed so as to be substantially the same as the curvature radius of the cylinder inner peripheral surface 1b.
- a fluid lubrication state can be formed between the portions 5b and 6b and the cylinder inner peripheral surface 1b, and sliding resistance can be suppressed and mechanical loss can be reduced.
- the radial width of the arc shape of the vane aligner portions 5c and 6c is made smaller than the groove width of the groove portion 2e, and the radial width of the arc shape of the vane aligner portions 5d and 6d is made larger than the groove width of the groove portion 3e.
- the difference between these widths is set to a predetermined appropriate amount.
- the vane aligner portions 5c and 6c are in contact with the inner diameter side of the groove portion 2e, and the vane aligner portions 5d and 6d are in contact with the inner diameter side of the groove portion 3e to restrict movement. Accordingly, the first vane 5 and the second vane 6 are not delayed in returning to the original state, and when the vane aligner portions 5c and 6c come into contact with the groove portion 2e, and the vane aligner portion 5d. , 6d and the groove 3e do not increase in force, so that the first vane 5 and the second vane 6 can be prevented from being damaged, and high reliability can be obtained.
- the recesses 2a and 3a are provided with steps to form the groove portions 2e and 3e, and the inner diameter sides of the groove portions 2e and 3e are in contact with the first vane 5 and the second vane 6.
- the force acting on the first vane 5 and the second vane 6 at the time of contact can be handled by both the grooves 2e and 3e.
- the present invention is not limited to this configuration, and any one of the grooves 2e and 3e can be used as long as the force acting upon the contact of the first vane 5 and the second vane 6 can be handled by any one of the grooves 2e and 3e. Only one of them may be formed.
- the recesses 2a and 3a are respectively provided with steps to form the groove portions 2e and 3e, thereby restricting the movement of the first vane 5 and the second vane 6 toward the center of the cylinder inner peripheral surface 1b.
- the present invention is not limited to this, and other stoppers may be provided in place of forming the grooves 2e and 3e as long as the movement of the cylinder inner peripheral surface 1b in the center direction can be restricted. Good.
- vanes necessary for performing the compression operation so that the arc shapes of the vane tip portions 5b and 6b and the normal line of the cylinder inner peripheral surface 1b almost always coincide with each other in the cylinder.
- a mechanism that rotates around the center of the peripheral surface 1b as a rotation center can be realized by a configuration in which the rotor portion 4a and the rotating shaft portions 4b and 4c are integrated.
- the rotation shaft portions 4b and 4c can be supported with a small diameter, so that the bearing sliding loss can be reduced, and the accuracy of the outer diameter and the rotation center of the rotor portion 4a can be improved. Leakage loss can be reduced by forming a narrow gap with 1b.
- the vanes installed on the rotor portion 4a of the rotor shaft 4 are the first vane 5 and the second vane 6.
- the present invention is not limited to this, and one or three vanes are not limited to this. It is good also as a structure by which the vane of a sheet or more is installed.
- Embodiment 2 FIG. The vane compressor 200 according to the present embodiment will be described focusing on differences from the vane compressor 200 according to the first embodiment.
- FIG. 10 is a plan view of the first vane 5 and the second vane 6 of the vane compressor 200 according to Embodiment 2 of the present invention
- FIG. 11 is a diagram illustrating the compression operation of the vane compressor 200. It is. As shown in FIG. 10, B is a line indicating the length direction of the vane portions 5a and 6a, and C is an arcuate normal line of the vane tip portions 5b and 6b. Therefore, the vane portions 5a and 6a are attached to the vane aligner portions 5c, 5d, 6c, and 6d so as to be inclined in the B direction.
- the normal C of the arc of the vane tip portions 5b and 6b is inclined with respect to the vane longitudinal direction B, and is formed so as to pass through the center of the arc forming the vane aligner portions 5c, 5d, 6c, and 6d. Yes.
- the centers of the rotor portion 4a and the bush holding portions 4d and 4e are formed so as to be arranged in a substantially straight line, but as shown in the “angle 0 °” diagram of FIG.
- the vane relief portion 4f is formed on the right side of the straight line
- the vane relief portion 4g is formed on the left side of the straight line.
- Embodiment 3 FIG.
- the vane compressor 200 according to the present embodiment will be described focusing on differences from the vane compressor 200 according to the first embodiment.
- FIG. 12 is a structural diagram around the vane aligner bearing portion 2b of the vane type compressor 200 according to Embodiment 3 of the present invention.
- 12A is a longitudinal sectional view around the vane aligner bearing portion 2b
- FIG. 12B is a KK sectional view in FIG. 12B.
- a partial ring-shaped stopper 2 f is formed integrally with the frame 2 inside the recess 2 a.
- This stopper 2f is formed so that the outer peripheral surface is substantially concentric with the vane aligner bearing portion 2b which is the outer peripheral surface of the recess 2a, and interferes with the rotating shaft portion 4b as shown in FIG. 12 (a). It has a partial ring shape with a cut part.
- the radius of curvature of the outer peripheral surface of the stopper 2f is set to be substantially the same as the maximum distance between the outer periphery of the rotating shaft portion 4b and the center of the cylinder inner peripheral surface 1b, as indicated by a broken line in FIG. Has been.
- the radius of curvature of the outer peripheral surface of the stopper 2f may not be completely the same as the above maximum distance.
- the pressure in the compression chamber 11 increases abnormally, and the force that pushes the first vane 5 and the second vane 6 toward the center of the cylinder inner peripheral surface 1b is greater than the centrifugal force acting on the first vane 5 and the second vane 6. If it becomes larger, the first vane 5 and the second vane 6 are pushed and moved toward the center of the cylinder inner peripheral surface 1b.
- the difference between the curvature radius of the inner peripheral surface of the vane aligner portions 5c and 6c and the curvature radius of the outer peripheral surface of the stopper 2f is f0, the curvature radius of the outer peripheral surface of the stopper 2f is equal to the outer periphery of the rotary shaft portion 4b and the cylinder.
- the vane aligner portion 5c of the first vane 5 moves by the difference f0 in the center direction of the cylinder inner peripheral surface 1b and comes into contact with the outer periphery of the stopper 2f or the rotating shaft portion 4b.
- the vane aligner portion 6c of the second vane 6 moves by a difference f0 toward the center of the cylinder inner peripheral surface 1b and comes into contact with the stopper 2f. Therefore, both the first vane 5 and the second vane 6 always have the same moving distance (difference f0). If the difference f0, which is the movement distance, is set to an appropriate amount, the same effect as in the first embodiment can be obtained.
- the difference f0 that is the movement distance of the first vane 5 and the second vane 6 is used.
- the diameter of the vane aligner bearing portions 2b and 3b is made larger. It can be made smaller.
- the diameter of the vane aligner bearing portions 2b and 3b can be reduced, the sliding loss in the vane aligner bearing portions 2b and 3b can be reduced. The effect that loss can be further reduced as compared with the first mode can be obtained.
- a partial ring-shaped stopper 3f similar to the stopper 2f is also formed integrally with the cylinder head 3 inside the recess 3a of the cylinder head 3 (not shown). May be. Accordingly, since the force acting on the first vane 5 or the second vane 6 can be handled by both the stoppers 2f and 3f, the movement of the first vane 5 or the second vane 6 can be more reliably regulated. .
- the radius of curvature of the outer peripheral surface of the stopper 2f is substantially the same as the maximum distance between the outer periphery of the rotating shaft 4b and the center of the cylinder inner peripheral surface 1b, as shown in FIG.
- the present invention is not limited to this. That is, if it is not desired to contact the vane aligner portions 5c and 6c with the rotating shaft portion 4b, the radius of curvature of the outer peripheral surface of the stopper 2f is set larger than the maximum distance between the outer periphery of the rotating shaft portion 4b and the center of the cylinder inner peripheral surface 1b. If it is slightly increased, the first vane 5 and the second vane 6 can be brought into contact only with the stopper 2f.
- Embodiment 4 FIG.
- the vane type compressor 200 according to the present embodiment will be described focusing on differences from the vane type compressor 200 according to the third embodiment.
- FIG. 13 is a structural diagram around the vane aligner bearing portion 2b of the vane type compressor 200 according to Embodiment 4 of the present invention.
- 13A is a longitudinal sectional view around the vane aligner bearing portion 2b
- FIG. 13B is an LL sectional view in FIG. 13B.
- a plurality (three in FIG. 13) of cylindrical stoppers 2g are provided. It is formed so as to be integrated with the frame 2 inside the recess 2a. As shown in FIG. 13B, the maximum distance between the outer periphery of each cylindrical stopper 2g and the center of the cylinder inner peripheral surface 1b is the maximum distance between the outer periphery of the rotating shaft portion 4b and the center of the cylinder inner peripheral surface 1b. It is set to be almost the same as the distance. Moreover, each cylindrical stopper 2g and the rotating shaft part 4b are arrange
- each cylindrical stopper 2g and the center of the cylinder inner peripheral surface 1b is not completely the same as the maximum distance between the outer periphery of the rotary shaft portion 4b and the center of the cylinder inner peripheral surface 1b. Also good.
- the pressure in the compression chamber 11 increases abnormally, and the first vane 5 and the second vane 6 are formed on the cylinder inner peripheral surface 1 b.
- the vane aligner portion 5c of the first vane 5 is in contact with the stopper 2g or the rotating shaft portion 4b, and the vane aligner portion 6c of the second vane 6 is in contact with the stopper 2g.
- the difference f0 is the first difference. This is the moving distance of the vane 5 and the second vane 6. If the difference f0, which is the moving distance, is set to an appropriate amount, the same effect as in the third embodiment can be obtained.
- a plurality of cylindrical stoppers 3g similar to the stopper 2g are formed integrally with the cylinder head 3 inside the recess 3a of the cylinder head 3 (not shown). ) Accordingly, since the force acting on the first vane 5 or the second vane 6 can be handled by both the stoppers 2g and 3g, the movement of the first vane 5 or the second vane 6 can be more reliably regulated. .
- the maximum distance between the outer periphery of each stopper 2g and the center of the cylinder inner peripheral surface 1b is set to the rotating shaft portion 4b. If it is made slightly larger than the maximum distance between the outer periphery of the cylinder and the center of the cylinder inner peripheral surface 1b, the first vane 5 and the second vane 6 can be brought into contact only with the stopper 2g.
- each cylindrical stopper 2g and the rotating shaft portion 4b are arranged at substantially equal intervals.
- any one of the stoppers 2g is surely provided. If it can contact, it does not need to arrange at equal intervals.
- the stopper 2g has a cylindrical shape.
- the stopper 2g does not have to be a cylindrical shape as long as the moving distance of the first vane 5 and the second vane 6 can be appropriately set. .
- the oil pump 31 using the centrifugal force of the rotor shaft 4 has been described.
- any form of the oil pump 31 may be used, for example, in Japanese Patent Application Laid-Open No. 2009-62820.
- the positive displacement pump described may be used as the oil pump 31.
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Abstract
Description
(ベーン型圧縮機200の構造)
図1は、本発明の実施の形態1に係るベーン型圧縮機200の縦断面図であり、図2は、同ベーン型圧縮機200の圧縮要素101の分解斜視図である。また、図3は、同ベーン型圧縮機200の第1ベーン5及び第2ベーン6の平面図及び正面図であり、図4は、同ベーン型圧縮機200のベーンアライナー軸受部2b周辺の縦断面図である。このうち、図1において、実線で示す矢印はガス(冷媒)の流れ、そして、破線で示す矢印は冷凍機油25の流れを示している。以下、図1~図4を参照しながら、ベーン型圧縮機200の構造ついて説明する。
図5は、本発明の実施の形態1に係るベーン型圧縮機200において図1のI-I断面図であり、図6は、同ベーン型圧縮機200の圧縮動作を示す図である。以下、図5及び図6を参照しながら、ベーン型圧縮機200の圧縮動作について説明する。
ローターシャフト4の回転軸部4bが電動要素102の回転子22からの回転力を受け、ローター部4aは、シリンダー1の貫通部1f内で回転する。このローター部4aの回転に伴い、ローター部4aのブッシュ保持部4d、4eは、ローターシャフト4を中心とした円周上を移動する。そして、ブッシュ保持部4d、4e内にそれぞれ保持されている一対のブッシュ7、8、及び、その一対のブッシュ7、8それぞれの間に回転可能に挟持されている第1ベーン5のベーン部5a、及び、第2ベーン6のベーン部6aもローター部4aの回転と共に回転する。第1ベーン5及び第2ベーン6は、ローター部4aの回転による遠心力を受け、ベーンアライナー部5c、6c及びベーンアライナー部5d、6dは、ベーンアライナー軸受部2b、3bにそれぞれ押し付けられて摺動しながら、ベーンアライナー軸受部2b、3bの中心を回転中心として回転する。ここで、ベーンアライナー軸受部2b、3bとシリンダー内周面1bとは同心であるため、第1ベーン5及び第2ベーン6はシリンダー内周面1bの中心を回転中心として回転することになる。そうすると、第1ベーン5のベーン部5a、第2ベーン6のベーン部6aの長さ方向がシリンダー内周面1bの中心を通るように、ブッシュ7、8が、それぞれブッシュ保持部4d、4e内で、ブッシュ中心7a、8aを回転中心として回転することになる。すなわち、ベーン先端部5b、6bの円弧形状及びシリンダー内周面1bの法線が常にほぼ一致する状態で、ローター部4aが回転することになる。
図7の「角度0°」の図においては、ベーンアライナー部5c、6cの回転方向(図7では時計方向)を矢印で示している。ただし、他の角度の図においては、ベーンアライナー部5c、6cの回転方向を示す矢印は略している。ローターシャフト4の回転により、第1ベーン5のベーン部5a及び第2ベーン6のベーン部6aがシリンダー内周面1bの中心を回転中心として回転する。これによって、ベーンアライナー部5c、6cは、図4で示されるように、凹部2aに形成された溝部2e内を、ベーンアライナー軸受部2bに支持されてシリンダー内周面1bの中心を回転中心として回転する。また、同様に、ベーンアライナー部5d、6dは、凹部3aに形成された溝部3e内を、ベーンアライナー軸受部3bに支持されてシリンダー内周面1bの中心を回転中心として回転する。
以上の動作において、図1で示されるように、ローターシャフト4の回転によって、油ポンプ31により油溜め104から冷凍機油25が吸い上げられ、給油路4hに送り出される。この給油路4hに送り出された冷凍機油25は、給油路4iを通ってフレーム2の凹部2aに、かつ、給油路4jを通ってシリンダーヘッド3の凹部3aに送り出される。凹部2a、3aに送り出された冷凍機油25の一部は、それぞれ溝部2e、3eに送られ、ベーンアライナー軸受部2b、3bを潤滑すると共に、凹部2a、3aと連通したベーン逃がし部4f、4gに供給される。ここで、密閉容器103内の圧力は高圧である吐出圧力になっているため、凹部2a、3a及びベーン逃がし部4f、4g内の圧力も吐出圧力となる。また、凹部2a、3aに送り出された冷凍機油25の一部は、フレーム2の主軸受部2c及びシリンダーヘッド3の主軸受部3cに供給され潤滑する。
図8で示されるように、実線の矢印は冷凍機油25の流れを示している。ベーン逃がし部4f内の圧力は吐出圧力であり、吸入室9及び中間室10内の圧力よりも高いため、冷凍機油25は、ベーン部5aの側面とブッシュ7と間の摺動部を潤滑しながら、圧力差及び遠心力によって吸入室9及び中間室10に送り出される。また、冷凍機油25は、ブッシュ7とローターシャフト4のブッシュ保持部4dとの間の摺動部を潤滑しながら、圧力差及び遠心力によって吸入室9及び中間室10に送り出される。また、中間室10に送り出された冷凍機油25の一部は、ベーン先端部5bとシリンダー内周面1bとの間の隙間をシールしながら吸入室9に流入する。
なお、以上の動作は第1ベーン5に対して示したが、第2ベーン6においても同様である。
図9は、本発明の実施の形態1に係るベーン型圧縮機200において図4におけるJ-J断面図、かつ、図7における回転角度0°における断面図の拡大図である。このうち、図9(a)及び図9(b)は、凹部2aに段差を設けない、すなわち、溝部2eを設けない場合を示した図であり、図9(c)は、本実施の形態を示す図である。以下、図9を参照しながら、吸入室9、中間室10又は圧縮室11内において液冷媒を圧縮する等により異常に圧力が増加した場合における第1ベーン5及び第2ベーン6の挙動について説明する。
以上の構成のように、上記の式(1)の関係を有するように、ベーン先端部5b、6bとシリンダー内周面1bとの間に所定の適正な隙間δを設けることによって、ベーン先端部5b、6bからの冷媒の漏れを抑制しつつ、機械損失の増大による圧縮機効率の低下を抑制し、かつ、ベーン先端部5b、6bの摩耗を抑制できる。
本実施の形態に係るベーン型圧縮機200について、実施の形態1に係るベーン型圧縮機200と相違する点を中心に説明する。
図10は、本発明の実施の形態2に係るベーン型圧縮機200の第1ベーン5及び第2ベーン6の平面図であり、図11は、同ベーン型圧縮機200の圧縮動作を示す図である。
図10で示されるように、Bは、ベーン部5a、6aの長さ方向を示す線であり、Cは、ベーン先端部5b、6bの円弧形状の法線である。したがって、ベーンアライナー部5c、5d、6c、6dに対して、ベーン部5a、6aは、Bの方向に傾いて取り付けられている。また、ベーン先端部5b、6bの円弧の法線Cは、ベーン長手方向Bに対して傾いており、ベーンアライナー部5c、5d、6c、6dを形成する円弧の中心を通るように形成されている。
以上のような構成においても、図6に示す実施の形態1と同様に、ベーン先端部5b、6bの円弧形状及びシリンダー内周面1bの法線が常にほぼ一致する状態で圧縮動作を行うことができ、ベーン先端部5b、6bとシリンダー内周面1bとは常に微小な隙間を保ちつつ、非接触で回転することが可能である。
本実施の形態においても、フレーム2の凹部2a、シリンダーヘッド3の凹部3aに段差を設けて溝部2e、3eを形成すれば、吸入室9、中間室10又は圧縮室11内の圧力が異常に増加した場合における第1ベーン5及び第2ベーン6の動作は実施の形態1と同様であり、実施の形態1と同様の効果が得られる。また、実施の形態1におけるその他の効果も、本実施の形態においても得られる。
本実施の形態に係るベーン型圧縮機200について、実施の形態1に係るベーン型圧縮機200と相違する点を中心に説明する。
図12は、本発明の実施の形態3に係るベーン型圧縮機200のベーンアライナー軸受部2b周辺の構造図である。このうち、図12(a)は、ベーンアライナー軸受部2b周辺の縦断面図であり、図12(b)は、図12(b)におけるK-K断面図である。
なお、このストッパー2fの外周面の曲率半径は、上記の最大距離と、完全に同一でなくてもよい。
次に、図12を参照しながら、吸入室9、中間室10又は圧縮室11内において異常に圧力が増加した場合における第1ベーン5及び第2ベーン6の挙動について説明する。
本実施の形態においては、第1ベーン5又は第2ベーン6が回転軸部4b、4cと接触してもよい構成としたので、第1ベーン5及び第2ベーン6の移動距離である差f0が同じであるとすると、実施の形態1で示した第1ベーン5又は第2ベーン6が溝部2e、3eの内周面と接触する場合と比べて、ベーンアライナー軸受部2b、3bの直径を小さくすることが可能となる。このように、ベーンアライナー軸受部2b、3bの径を小さくすることが可能になると、ベーンアライナー軸受部2b、3bにおける摺動損失を小さくすることができるため、実施の形態3においては、実施の形態1よりも損失をより低減できるという効果を得ることができる。
本実施の形態に係るベーン型圧縮機200について、実施の形態3に係るベーン型圧縮機200と相違する点を中心に説明する。
図13は、本発明の実施の形態4に係るベーン型圧縮機200のベーンアライナー軸受部2b周辺の構造図である。このうち、図13(a)は、ベーンアライナー軸受部2b周辺の縦断面図であり、図13(b)は、図13(b)におけるL-L断面図である。
なお、各円柱状のストッパー2gの外周とシリンダー内周面1bの中心との最大距離は、回転軸部4bの外周とシリンダー内周面1bの中心との最大距離と、完全に同一でなくてもよい。
次に、図13を参照しながら、吸入室9、中間室10又は圧縮室11内において異常に圧力が増加した場合における第1ベーン5及び第2ベーン6の挙動について説明する。
Claims (7)
- 冷媒を圧縮する圧縮要素が、
円筒状の内周面が形成されたシリンダーと、
該シリンダーの内部において、前記内周面の中心軸と所定の距離ずれた回転軸を中心に回転する円筒形状のローター部、及び、該ローター部に外部からの回転力を伝達する回転軸部を有したローターシャフトと、
前記シリンダーの前記内周面の一方の開口部を閉塞し、主軸受部によって前記回転軸部を支承するフレームと、
前記シリンダーの前記内周面の他方の開口部を閉塞し、主軸受部によって前記回転軸部を支承するシリンダーヘッドと、
前記ローター部に設けられ、前記ローター部内から突出する先端部が外側に凸となる円弧形状に形成された少なくとも1枚のベーンと、
を備えたベーン型圧縮機において、
前記ベーンの前記先端部の前記円弧形状の法線と、前記シリンダーの前記内周面の法線とが常にほぼ一致する状態で、前記ベーン、前記ローター部の外周部、及び前記シリンダーの前記内周部によって囲まれる空間で冷媒を圧縮するように前記ベーンを支持し、前記ベーンを前記ローター部に対して揺動可能かつ移動可能に支持し、前記ベーンの前記先端部が前記シリンダーの前記内周面側に最大限移動した場合に、該先端部と該内周面との所定の間隙を有するように保持するベーン支持手段を備え、
前記ローターシャフトは、前記ローター部と前記回転軸部とが一体に形成されて構成され、
前記ベーンは、前記フレーム側かつ前記ローター部の中心側の端面、及び、前記シリンダーヘッド側かつ前記ローター部の中心側の端面に設けられた一対の部分リング形状のベーンアライナー部を有し、
前記フレーム及び前記シリンダーヘッドの前記シリンダー側端面に、前記シリンダーの前記内周面と同心の凹部が形成され、
前記ベーンアライナー部は、前記凹部内に嵌入され、該凹部の外周面であるベーンアライナー軸受部で支承され、
前記フレーム及び/又は前記シリンダーヘッドの前記凹部の内側に形成され、前記ベーンアライナー部の前記ローター部の内側方向への移動を規制するストッパーを備えた
ことを特徴とするベーン型圧縮機。 - 前記ストッパーは、前記凹部内において、該凹部の外周側の深さを深くして形成された環状の溝部における内周部であり、
前記溝部は、その溝幅を前記ベーンアライナー部の径方向の幅よりも大きくなるように形成され、
前記ベーンアライナー軸受部は、前記溝部の外周面であり、
前記ベーンアライナー部は、前記溝部に嵌入された
ことを特徴とする請求項1記載のベーン型圧縮機。 - 前記ストッパーは、前記凹部内に形成され、外周面が前記ベーンアライナー軸受部と同心であり、前記回転軸部と干渉する箇所が切れた部分リング形状物であり、
前記ベーンアライナー部は、前記ストッパーの外周面と前記ベーンアライナー軸受部との間に嵌入された
ことを特徴とする請求項1記載のベーン型圧縮機。 - 前記ストッパーの外周面の曲率半径は、前記回転軸部の外周と前記シリンダーの前記内周面の中心との最大距離と略同一である
ことを特徴とする請求項3記載のベーン型圧縮機。 - 前記ストッパーは、前記凹部内に形成され、中心軸が前記ベーンアライナー軸受部の同心円上に配置された複数の円柱形状物であり、
前記ベーンアライナー部は、前記同心円と前記ベーンアライナー軸受部との間に嵌入された
ことを特徴とする請求項1記載のベーン型圧縮機。 - 前記各円柱形状物の外周と前記シリンダーの前記内周面の中心との最大距離は、前記回転軸部の外周と前記シリンダーの前記内周面の中心との最大距離と略同一である
ことを特徴とする請求項5記載のベーン型圧縮機。 - 前記ベーンの前記先端部の前記円弧形状の曲率半径は、前記シリンダーの前記内周面の曲率半径と略同一である
ことを特徴とする請求項1~請求項6のいずれか一項に記載のベーン型圧縮機。
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JP2013553081A JP5657144B2 (ja) | 2012-01-11 | 2012-01-11 | ベーン型圧縮機 |
CN201280060099.3A CN103975163B (zh) | 2012-01-11 | 2012-01-11 | 叶片型压缩机 |
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- 2012-01-11 CN CN201280060099.3A patent/CN103975163B/zh active Active
- 2012-01-11 JP JP2013553081A patent/JP5657144B2/ja active Active
- 2012-01-11 US US14/350,937 patent/US9458849B2/en active Active
- 2012-01-11 WO PCT/JP2012/000114 patent/WO2013105131A1/ja active Application Filing
- 2012-01-11 EP EP12865406.8A patent/EP2803864B1/en active Active
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Also Published As
Publication number | Publication date |
---|---|
US9458849B2 (en) | 2016-10-04 |
EP2803864A1 (en) | 2014-11-19 |
EP2803864B1 (en) | 2020-08-12 |
CN103975163A (zh) | 2014-08-06 |
EP2803864A4 (en) | 2015-10-21 |
JP5657144B2 (ja) | 2015-01-21 |
CN103975163B (zh) | 2015-12-02 |
JPWO2013105131A1 (ja) | 2015-05-11 |
US20140294642A1 (en) | 2014-10-02 |
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