WO2022009768A1 - 摺動部品 - Google Patents
摺動部品 Download PDFInfo
- Publication number
- WO2022009768A1 WO2022009768A1 PCT/JP2021/024941 JP2021024941W WO2022009768A1 WO 2022009768 A1 WO2022009768 A1 WO 2022009768A1 JP 2021024941 W JP2021024941 W JP 2021024941W WO 2022009768 A1 WO2022009768 A1 WO 2022009768A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure groove
- pressure
- low
- sliding
- groove
- Prior art date
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- 239000012530 fluid Substances 0.000 claims abstract description 51
- 239000003507 refrigerant Substances 0.000 description 18
- 230000006835 compression Effects 0.000 description 16
- 238000007906 compression Methods 0.000 description 16
- 239000010687 lubricating oil Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 239000002184 metal Substances 0.000 description 4
- 239000003921 oil Substances 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 238000009751 slip forming Methods 0.000 description 2
- 238000007792 addition Methods 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
-
- 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
- F04C29/0021—Systems for the equilibration of forces acting on the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/18—Eccentric-shafts
-
- 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
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/001—Radial sealings for working fluid
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/22—Cranks; Eccentrics
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
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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
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- 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
- F04C2240/50—Bearings
- F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/801—Wear plates
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/42—Pumps with cylinders or pistons
Definitions
- the present invention relates to a sliding component used in a rotating machine including an eccentric mechanism.
- Machines with rotary drive used in various industrial fields include not only rotary machines that rotate while the central axis is held in place, but also rotary machines that rotate with eccentricity.
- One of the rotating machines that rotates with eccentricity is a scroll compressor, etc.
- This type of compressor has a fixed scroll with a spiral wrap on the surface of the end plate, and a spiral wrap on the surface of the end plate. It is equipped with a scroll compression mechanism consisting of a movable scroll, an eccentric mechanism that rotates the rotation axis eccentrically, etc., and by rotating the movable scroll relative to the fixed scroll with eccentric rotation, both scrolls can be used. It is a mechanism that pressurizes the fluid supplied from the low pressure chamber on the outer diameter side and discharges the high pressure fluid from the discharge hole formed in the center of the fixed scroll.
- the scroll compressor shown in Patent Document 1 includes a thrust plate that slides relative to the movable scroll on the back side of the movable scroll, and is compressed by a scroll compression mechanism in a back pressure chamber formed on the back side of the thrust plate.
- the present invention has been made focusing on such a problem, and an object of the present invention is to provide a sliding component capable of stably reducing the frictional resistance of a sliding surface accompanied by eccentric rotation.
- the sliding parts of the present invention are It is a sliding component that has an annular shape with high-pressure and low-pressure fluids facing inside and outside, and has a sliding surface that slides relative to each other with eccentric rotation.
- the sliding surface is provided with a plurality of high-pressure grooves that open in a space where a high-pressure fluid exists and a low-pressure groove that opens in a space where a low-pressure fluid exists, respectively, in the circumferential direction.
- the fluid existing in the space inside and outside the sliding component is used to be provided in one of the high-pressure grooves and in the circumferential direction. Dynamic pressure is generated in the low-pressure groove, and the sliding surfaces are slightly separated from each other to form a fluid film. As a result, the lubricity during sliding is improved, and the frictional resistance of the sliding surface can be stably reduced.
- the low-pressure groove may have a larger area in the direction parallel to the sliding surface than the high-pressure groove. According to this, it is easy to balance the dynamic pressure generated in the low pressure groove and the dynamic pressure generated in the high pressure groove according to the direction of the relative movement of the high pressure groove and the low pressure groove due to the eccentric rotation. Therefore, the sliding parts are suppressed from vibrating and tilting due to the generation of dynamic pressure.
- the high-pressure groove and the low-pressure groove may be arranged alternately inside and outside. According to this, dynamic pressure is generated in either the high-pressure groove or the low-pressure groove alternately arranged inside and outside regardless of the direction of the relative movement of the high-pressure groove and the low-pressure groove due to the eccentric rotation. The dynamic pressure generated over the circumferential direction is well-balanced.
- the high-pressure groove and the low-pressure groove may be equally arranged in the circumferential direction. According to this, the sliding surfaces can be separated from each other substantially evenly in the circumferential direction by the dynamic pressure generated in the high pressure groove and the low pressure groove respectively.
- the high-pressure groove and the low-pressure groove may have a shape formed from a part of a circle. According to this, stable dynamic pressure can be generated along the arcuate wall surface of the high pressure groove and the low pressure groove according to the relative movement direction of the high pressure groove and the low pressure groove due to the eccentric rotation.
- the space in which the low-pressure fluid exists may be a space on the outer diameter side of the sliding surface. According to this, since the low pressure groove is formed on the outer diameter side of the sliding surface, it is easy to secure a large area in the direction parallel to the opening of the low pressure groove and the sliding surface.
- FIG. 1 It is a schematic block diagram which shows the scroll compressor to which the side seal as the sliding component of Example 1 which concerns on this invention is applied. It is a figure which shows the sliding surface of the side seal of Example 1 of this invention. It is a partially enlarged view which shows the high pressure groove and the low pressure groove in a sliding surface. It is a figure which shows the relative sliding of the sliding surface of the side seal of Example 1 of this invention, and the sliding surface of a thrust plate. With (a) as the starting position, (b) is 90 degrees, (c) is 180 degrees, and (d) is the sliding surface of the side seal that slides relative to each other when the rotation axis rotates eccentrically up to 270 degrees. The positional relationship with the sliding surface of the thrust plate is shown. FIG.
- FIG. 4 is a diagram showing the distribution of pressure generated in a plurality of grooves due to the relative movement of the grooves due to the eccentric rotation of the rotating shaft on the sliding surface of the side seal shown in FIG. 4 (a). It is a figure which shows the distribution of the pressure generated in a plurality of grooves by the relative movement of a groove with the eccentric rotation of a rotation shaft on the sliding surface of the side seal shown in FIG. 4 (b).
- FIG. 3 is a diagram showing the distribution of pressure generated in a plurality of grooves due to the relative movement of the grooves due to the eccentric rotation of the rotating shaft on the sliding surface of the side seal shown in FIG. 4 (c).
- FIG. 4 is a diagram showing the distribution of pressure generated in a plurality of grooves due to the relative movement of the grooves due to the eccentric rotation of the rotating shaft on the sliding surface of the side seal shown in FIG. 4 (d). It is a figure which shows the sliding surface of the side seal of Example 2 which concerns on this invention. It is a figure which shows the sliding surface of the side seal of Example 3 which concerns on this invention. It is a figure which shows the sliding surface of the side seal of Example 4 which concerns on this invention.
- the sliding component of the present invention is applied to a rotating machine including an eccentric mechanism, for example, a scroll compressor C that sucks, compresses, and discharges a refrigerant as a fluid used in an air conditioning system of an automobile or the like.
- the refrigerant is a gas, and a mist-like lubricating oil is mixed therewith.
- the scroll compressor C As shown in FIG. 1, the scroll compressor C is driven by a housing 1, a rotary shaft 2, an inner casing 3, a scroll compression mechanism 4, a side seal 7 as a sliding component, and a thrust plate 8. It is mainly composed of a motor M and.
- the housing 1 is composed of a cylindrical casing 11 and a cover 12 that closes one opening of the casing 11.
- a low pressure chamber 20, a high pressure chamber 30, and a back pressure chamber 50 are formed inside the casing 11.
- a low-pressure refrigerant is supplied to the low-pressure chamber 20 from a refrigerant circuit (not shown) through a suction port 10.
- a high-pressure refrigerant compressed by the scroll compression mechanism 4 is discharged to the high-pressure chamber 30.
- a part of the refrigerant compressed by the scroll compression mechanism 4 is supplied to the back pressure chamber 50 together with the lubricating oil.
- the back pressure chamber 50 is formed inside the cylindrical inner casing 3 housed inside the casing 11.
- the cover 12 is formed with a discharge communication passage 13.
- the discharge communication passage 13 communicates a refrigerant circuit (not shown) with the high pressure chamber 30.
- the cover 12 is formed with a part of the back pressure communication passage 14 connecting the high pressure chamber 30 and the back pressure chamber 50, which is branched from the discharge communication passage 13.
- the discharge communication passage 13 is provided with an oil separator 6 that separates the lubricating oil from the refrigerant.
- the inner casing 3 is fixed in a state where one end thereof is in contact with the end plate 41a of the fixed scroll 41 constituting the scroll compression mechanism 4. Further, a suction communication passage 15 penetrating in the radial direction is formed at one end of the inner casing 3. That is, the low pressure chamber 20 is formed from the outside of the inner casing 3 to the inside of the inner casing 3 via the suction communication passage 15. The refrigerant supplied to the inside of the inner casing 3 through the suction communication passage 15 is sucked into the scroll compression mechanism 4.
- the scroll compression mechanism 4 is mainly composed of a fixed scroll 41 and a movable scroll 42.
- the fixed scroll 41 is fixed to the cover 12 in a substantially sealed shape.
- the movable scroll 42 is housed inside the inner casing 3.
- the fixed scroll 41 is made of metal and has a spiral wrap 41b.
- the spiral wrap 41b is projected from the surface of the disk-shaped end plate 41a, that is, one end surface of the end plate 41a.
- the fixed scroll 41 is formed with a recess 41c that is recessed on the back surface of the end plate 41a, that is, on the inner diameter side of the other end surface of the end plate 41a.
- the high pressure chamber 30 is defined from the recess 41c and the end surface of the cover 12.
- the movable scroll 42 is made of metal and has a spiral wrap 42b.
- the spiral wrap 42b is projected from the surface of the disk-shaped end plate 42a, that is, one end surface of the end plate 42a.
- the movable scroll 42 is formed with a boss 42c protruding from the back surface of the end plate 42a, that is, the center of the other end surface of the end plate 42a.
- An eccentric portion 2a formed at one end of the rotating shaft 2 is fitted into the boss 42c so as to be relatively rotatable.
- an eccentric mechanism for eccentric rotation of the rotary shaft 2 is configured by an eccentric portion 2a of the rotary shaft 2 and a counterweight portion 2b protruding in the outer diameter direction from one end of the rotary shaft 2. Has been done.
- the side seal 7 as a sliding component in this embodiment will be described.
- the side seal 7 is made of resin and has a rectangular cross section and an annular shape in the axial direction. Further, the side seal 7 is fixed to the back surface of the end plate 42a of the movable scroll 42 (see FIG. 1). In addition, in FIGS. 2 and 3, the sliding surface 7a of the side seal 7 is shown.
- a sliding surface 7a that abuts on the sliding surface 8a of the thrust plate 8 is formed on one side surface of the side seal 7.
- the sliding surface 7a of the side seal 7 is composed of a land 79, a plurality of high-pressure grooves 71, and a plurality of low-pressure grooves 72.
- the high-pressure groove 71 is formed by opening into a back pressure chamber 50 (see FIG. 1), which is a space recessed from the flat surface 79a of the land 79 and in which a high-pressure fluid exists on the inner diameter side thereof.
- the low pressure groove 72 is formed by opening into a low pressure chamber 20 (see FIG. 1), which is a space recessed from the flat surface 79a of the land 79 and in which a low pressure fluid exists on the outer diameter side of the sliding surface 7a. ing.
- the high-pressure groove 71 and the low-pressure groove 72 are arranged alternately inside and outside in the circumferential direction of the sliding surface 7a and are arranged substantially equally.
- the high-pressure groove 71 is formed in a substantially semicircular shape having a center P1 at the innermost inner diameter of the sliding surface 7a.
- the low pressure groove 72 is formed in a substantially semicircular shape having a center P2 at the outermost diameter of the sliding surface 7a.
- the high pressure groove 71 and the low pressure groove 72 are formed from a part of a circle in a direction parallel to the sliding surface 7a, that is, in an axial view.
- the high pressure groove 71 is formed from a wall surface 71a and a bottom surface 71b.
- the wall surface 71a extends substantially orthogonal to the surface 79a of the land 79, has a constant radius of curvature, and is continuously formed in a substantially semicircular arc shape.
- the bottom surface 71b extends substantially perpendicular to the end of the wall surface 71a and substantially parallel to the surface 79a of the land 79, and is formed in a planar shape.
- the high-pressure grooves 71 have the same size, but the sizes may be different.
- the low pressure groove 72 is formed from a wall surface 72a and a bottom surface 72b.
- the wall surface 72a extends substantially orthogonal to the surface 79a of the land 79, has a constant radius of curvature, and is continuously formed in a substantially semicircular arc shape.
- the bottom surface 72b extends substantially perpendicular to the end of the wall surface 72a and substantially parallel to the surface 79a of the land 79, and is formed in a planar shape.
- the low pressure grooves 72 have the same size, but the sizes may be different.
- the bottom surface 71b of the high pressure groove 71 and the bottom surface 72b of the low pressure groove 72 are not limited to those formed in a plane extending substantially parallel to the sliding surface 7a, and may be formed as, for example, an inclined surface or a curved surface.
- the depth dimension of the high pressure groove 71 which is the dimension from the surface 79a of the land 79 to the bottom surface 71b of the high pressure groove 71 and the depth of the low pressure groove 72 which is the dimension from the surface 79a of the land 79 to the bottom surface 72b of the low pressure groove 72.
- the vertical dimensions are substantially the same, and are formed to a depth at which dynamic pressure that separates the sliding surfaces 7a and 8a from each other as the thrust plate 8 slides relative to the sliding surface 8a can be generated.
- the depth dimensions of the high-pressure groove 71 and the low-pressure groove 72 are not limited to those formed to be substantially the same.
- the low pressure groove 72 is formed to have a larger area in the direction parallel to the sliding surface 7a (that is, an axial viewing area) than the high pressure groove 71.
- the radius R2 of the low pressure groove 72 which is the dimension from the center P2 to the wall surface 72a in the low pressure groove 72, is longer than the radius R1 of the high pressure groove 71, which is the dimension from the center P1 to the wall surface 71a in the high pressure groove 71 (R1). It is ⁇ R2).
- the circumferential dimension L2 of the low pressure groove 72 is longer (L2> L4) than the circumferential dimension L4 of the land portion between the adjacent low pressure grooves 72. That is, a plurality of low pressure grooves 72 are densely formed along the circumferential direction of the sliding surface 7a, and the opening area of the low pressure groove 72 into which the fluid flows from the space on the outer diameter side of the sliding surface 7a becomes large. There is.
- the wall surface 72a extends to a position on the inner diameter side of the center of the sliding surface 7a in the radial direction. As a result, the capacity for holding the fluid in the low pressure groove 72 is increased.
- the circumferential dimension L2 of the low pressure groove 72 is shorter (L2 ⁇ L3) than the circumferential dimension L3 of the land portion between the adjacent high pressure grooves 71, and the circumferential dimension L1 of the high pressure groove 71 is The land portion between the adjacent low-voltage grooves 72 is shorter than the circumferential dimension L4 (L1 ⁇ L4).
- the thrust plate 8 is made of metal and has an annular shape.
- a seal ring 43 is fixed to one end surface of the thrust plate 8. Further, the seal ring 43 is in contact with the inner side surface of the inner casing 3.
- the thrust plate 8 functions as a thrust bearing that receives an axial load of the movable scroll 42 via the side seal 7.
- the side seal 7 and the seal ring 43 partition the low pressure chamber 20 formed on the outer diameter side of the movable scroll 42 and the back pressure chamber 50 formed on the back side of the movable scroll 42 inside the inner casing 3. is doing.
- the back pressure chamber 50 is a closed section formed between the inner casing 3 and the rotating shaft 2.
- the seal ring 44 is fixed to the inner circumference of the through hole 3a provided in the center of the other end of the inner casing 3 and is slidably in contact with the rotating shaft 2 inserted through the through hole 3a in a sealed manner.
- the back pressure communication passage 14 that connects the high pressure chamber 30 and the back pressure chamber 50 is formed over the cover 12, the fixed scroll 41, and the inner casing 3.
- the back pressure communication passage 14 is provided with an orifice (not shown) so that the refrigerant of the high pressure chamber 30 whose pressure reduction is adjusted by the orifice is supplied to the back pressure chamber 50 together with the lubricating oil separated by the oil separator 6. It has become.
- the pressure in the back pressure chamber 50 is adjusted to be higher than the pressure in the low pressure chamber 20.
- the inner casing 3 is formed with a pressure relief hole 16 that penetrates in the radial direction and communicates the low pressure chamber 20 and the back pressure chamber 50.
- a pressure adjusting valve 45 is provided in the pressure release hole 16. The pressure adjusting valve 45 is opened when the pressure in the back pressure chamber 50 exceeds a set value.
- the boss 42c of the movable scroll 42 is inserted through the through hole 8b in the center of the thrust plate 8.
- the through hole 8b is formed to have a diameter that allows eccentric rotation by the eccentric portion 2a of the rotating shaft 2 that is inserted into the boss 42c. That is, the sliding surface 7a of the side seal 7 can slide relative to the sliding surface 8a of the thrust plate 8 by the eccentric rotation of the rotating shaft 2 (see FIG. 4).
- FIGS. 4 (a) to 4 (d) show FIG. 4 (a) indicated by a black arrow among the rotation loci of the boss 42c when viewed from the fixed scroll 41 side (see FIG. 1).
- the boss 42c is rotated by 90 degrees, 180 degrees, and 270 degrees, respectively.
- the sliding region between the sliding surface 7a of the side seal 7 and the sliding surface 8a of the thrust plate 8 is schematically shown by dots.
- the rotating shaft 2 only the eccentric portion 2a inserted into the boss 42c is shown, and the counterweight portion 2b and the like constituting the eccentric mechanism are not shown.
- the side seal 7 is a sliding component having a sliding surface 7a that slides relative to the sliding surface 8a of the thrust plate 8 with eccentric rotation.
- FIGS. 5 to 8 A fluid containing a refrigerant, lubricating oil, and the like flows into the high-pressure groove 71 and the low-pressure groove 72 even when the rotation is stopped.
- FIGS. 5 to 8 the side seals 7 when viewed from the drive motor M side (see FIG. 1) are shown, respectively, and the circles shown on the wall surface 71a of the high pressure groove 71 and the wall surface 72a of the low pressure groove 72 are shown. The mark indicates the place where the pressure is highest in each high pressure groove 71 and each low pressure groove 72.
- the fluid in the high pressure groove 71 and the low pressure groove 72 is on the side. It receives a shearing force in a direction substantially opposite to the moving direction of the seal 7 and moves in that direction.
- the pressure of the fluid is increased on the wall surface 71a of the high pressure groove 71 and the wall surface 72a of the low pressure groove 72, and a positive dynamic pressure is generated.
- the dynamic pressure of positive pressure may be simply described as dynamic pressure.
- the sliding surfaces 7a and 8a are slightly separated from each other, and a fluid film is formed by the fluid flowing between the sliding surfaces 7a and 8a. As a result, the lubricity between the sliding surfaces 7a and 8a is improved, so that the frictional resistance between the sliding surfaces 7a and 8a is reduced.
- each high pressure groove 71 formed in a range of about 180 degrees on the inner diameter side of the sliding surface 7a from the right side of the paper surface to the upper side of the paper surface, and the sliding surface 7a is generated from the left side of the paper surface to the lower side of the paper surface.
- Dynamic pressure is generated in each low pressure groove 72 formed in the range of about 180 degrees on the outer diameter side of the above.
- each high pressure groove 71 formed in a range of about 180 degrees on the inner diameter side of the sliding surface 7a from the upper side of the paper surface to the left side of the paper surface, and the sliding surface 7a is generated from the lower side of the paper surface to the right side of the paper surface.
- Dynamic pressure is generated in each low pressure groove 72 formed in the range of about 180 degrees on the outer diameter side of the above.
- each high pressure groove 71 formed in a range of about 180 degrees on the inner diameter side of the sliding surface 7a from the left side of the paper surface to the lower side of the paper surface, and the sliding surface 7a is generated from the right side of the paper surface to the upper side of the paper surface.
- Dynamic pressure is generated in each low pressure groove 72 formed in the range of about 180 degrees on the outer diameter side of the above.
- each high pressure groove 71 formed in a range of about 180 degrees on the inner diameter side of the sliding surface 7a from the lower side of the paper surface to the right side of the paper surface, and the sliding surface 7a is generated from the upper side of the paper surface to the left side of the paper surface.
- Dynamic pressure is generated in each low pressure groove 72 formed in the range of about 180 degrees on the outer diameter side of the above.
- the side seal 7 in which the high pressure groove 71 and the low pressure groove 72 are formed on the sliding surface 7a has a narrower radial width than the relative sliding thrust plate 8 (see FIGS. 1 and 4). .. According to this, between the sliding surfaces 7a and 8a that slide relative to each other with eccentric rotation, the entire sliding surface 7a of the side seal 7 is always in the sliding region with the sliding surface 8a of the thrust plate 8 (FIG. 4). As a result, the high pressure groove 71 and the low pressure groove 72 can surely generate dynamic pressure.
- the wall surfaces 71a and 72a are formed in a substantially semi-arc shape in the axial direction, in each high-pressure groove 71 and each low-pressure groove 72, depending on the rotation angle of the boss 42c.
- the pressure points generated on the wall surfaces 71a and 72a gradually move along the wall surfaces 71a and 72a within a range of about 180 degrees (see FIGS. 5 to 8).
- the high-pressure groove 71 and the low-pressure groove 72 have substantially semicircular arc-shaped wall surfaces 71a and 72a continuous with the same radius of curvature, they are generated in each of the high-pressure groove 71 and the low-pressure groove 72 regardless of the eccentric rotation angle. The pressure to be applied is almost the same. As a result, the dynamic pressure generated in the high-pressure groove 71 and the low-pressure groove 72 between the sliding surfaces 7a and 8a is unlikely to change suddenly, and the generated dynamic pressure is stable.
- the low pressure groove 72 is formed to have a larger axial viewing area than the high pressure groove 71, and the pressure generated in the high pressure groove 71 and the pressure generated in the low pressure groove 72 are substantially the same. It is balanced so that it becomes.
- the high-pressure groove 71 and the low-pressure groove 72 are arranged alternately inside and outside in the circumferential direction of the sliding surface 7a and are arranged substantially equally. Therefore, dynamic pressure is generated in each high-pressure groove 71 formed in a range of about 180 degrees on the inner diameter side of the sliding surface 7a according to the relative movement direction of the high-pressure groove 71 and the low-pressure groove 72 due to the eccentric rotation. At the same time, dynamic pressure is generated in each low pressure groove 72 formed in a range of about 180 degrees deviated by half in the circumferential direction on the outer diameter side of the sliding surface 7a from the relevant range (see FIGS. 5 to 8). That is, substantially the same dynamic pressure is generated in the circumferential direction by each high pressure groove 71 and each low pressure groove 72 between the sliding surfaces 7a and 8a.
- the side seal 7 is provided in the circumferential direction by utilizing the fluid existing in the space inside and outside the side seal 7 according to the direction of the relative movement of the high pressure groove 71 and the low pressure groove 72 due to the eccentric rotation.
- the sliding surfaces 7a and 8a are slightly separated from each other to form a fluid film, thereby lubricating the sliding surfaces 7a and 8a. Since the property can be improved, the frictional resistance of the sliding surfaces 7a and 8a can be stably reduced.
- the low pressure groove 72 is formed to have a larger axial viewing area than the high pressure groove 71, the dynamic pressure generated in the low pressure groove 72 according to the direction of the relative movement of the sliding surface 7a due to the eccentric rotation. Since the dynamic pressure generated in the high-pressure groove 71 can be balanced so as to be substantially the same, the sliding surfaces 7a and 8a can be separated from each other substantially evenly in the circumferential direction, and the dynamic pressure is generated. Vibration, tilt, and the like of the side seal 7 can be suppressed.
- the high-pressure groove 71 and the low-pressure groove 72 are arranged alternately inside and outside on the sliding surface 7a, so that the high-pressure groove 71 and the low-pressure groove 72 are arranged inside and outside the high-pressure groove 71 regardless of the relative movement direction of the high-pressure groove 71 and the low-pressure groove 72 due to the eccentric rotation. Since the dynamic pressure is generated in any of the low pressure grooves 72, the dynamic pressure generated in the circumferential direction of the sliding surface 7a is well balanced. Further, since the formed regions of the high pressure groove 71 and the low pressure groove 72 on the sliding surface 7a are unlikely to interfere with each other, the high pressure groove 71 and the low pressure groove 72 can be effectively formed on the sliding surface 7a.
- the high pressure groove 171 and the low pressure groove 172 are formed in a substantially rectangular shape.
- the high-pressure groove 171 is formed of a wall surface 171a, side wall surfaces 171c and 171d, and a bottom surface 171b.
- the wall surface 171a extends substantially orthogonal to the surface 179a of the land 179 and extends linearly in the circumferential direction.
- the side wall surfaces 171c and 171d extend substantially orthogonal to the surface 179a of the land 179 and extend linearly in the radial direction.
- the bottom surface 171b is substantially orthogonal to the ends of the wall surface 171a and the side wall surfaces 171c and 171d, respectively, and extends substantially parallel to the surface 179a of the land 179 to form a flat surface.
- the low pressure groove 172 is formed of a wall surface 172a, side wall surfaces 172c and 172d, and a bottom surface 172b.
- the wall surface 172a extends substantially orthogonal to the surface 179a of the land 179 and extends linearly in the circumferential direction.
- the side wall surfaces 172c and 172d extend substantially orthogonal to the surface 179a of the land 179 and extend linearly in the radial direction.
- the bottom surface 172b is substantially orthogonal to the ends of the wall surface 172a and the side wall surfaces 172c and 172d, respectively, and extends substantially parallel to the surface 179a of the land 179 to form a flat surface.
- the radial dimension L14 of the low pressure groove 172 is longer (L13 ⁇ L14) than the radial dimension L13 of the high pressure groove 171. That is, the low-pressure groove 172 is formed to have a larger axial viewing area than the high-pressure groove 171.
- the low pressure groove 172 extends to a position on the inner diameter side of the center of the sliding surface 107a in the radial direction. As a result, the capacity for holding the fluid in the low pressure groove 172 is increased.
- the fluid in the high pressure groove 171 and the low pressure groove 172 is the wall surface 171a and the side wall surfaces 171c, 171d constituting the high pressure groove 171. It concentrates on the corner portion formed by either one of the above, the wall surface 172a constituting the low pressure groove 172, and the corner portion formed by any one of the side wall surfaces 172c and 172d. Therefore, high dynamic pressure is generated in the high pressure groove 171 and the low pressure groove 172.
- the high pressure groove 271 and the low pressure groove 272 are formed in a substantially rectangular shape.
- the circumferential dimension L22 of the low pressure groove 272 is longer (L21 ⁇ L22) than the circumferential dimension L21 of the high pressure groove 271. As a result, the opening area of the low pressure groove 172 into which the fluid flows from the space on the outer diameter side of the sliding surface 207a is increased.
- the high pressure groove 271 extends to a position on the outer diameter side of the center of the sliding surface 207a in the radial direction
- the low pressure groove 272 extends to a position on the inner diameter side of the center of the sliding surface 207a in the radial direction. .. That is, the high-pressure groove 271 and the low-pressure groove 272 are formed so that most of them overlap in the circumferential direction.
- the fluid flowing out from the high-pressure groove 271 or low-pressure groove 272 upstream in the circumferential direction due to the generation of dynamic pressure between the sliding surfaces 207a and 8a flows into the adjacent high-pressure groove 271 or low-pressure groove 272 on the downstream side at that time. It is easy to flow in. Not only is it easy for a fluid film to be formed by the fluid over the circumferential direction between the sliding surfaces 207a and 8a, but also the fluid on the land 279 is likely to be supplied into the high pressure groove 271 or the low pressure groove 272.
- the high-pressure groove 371 and the low-pressure groove 372 are formed in a substantially isosceles trapezoidal shape, and the low-pressure groove 372 has a larger axial viewing area than the high-pressure groove 371.
- the high-pressure groove 371 and the low-pressure groove 372 are each formed in a substantially isosceles trapezoidal shape having the largest circumferential dimension in the inner and outer openings. As a result, a large axial viewing area of the land portion between the high-pressure groove 371 and the low-pressure groove 372 adjacent to each other in the circumferential direction is secured.
- the fluid flowing out from the high-pressure groove 371 or the low-pressure groove 372 between the sliding surfaces 307a and 8a due to the generation of dynamic pressure tends to stay in the land portion. Therefore, it is possible to improve the sealing property while ensuring the lubricity between the sliding surfaces 307a and 8a during sliding.
- the present invention is not limited to this, and any rotary machine including an eccentric mechanism, for example. It may be applied to a scroll expansion compressor or the like equipped with an expander and a compressor integrally.
- the fluid existing in the space inside and outside the sliding surface of the sliding component may be a gas, a liquid, or a mixed state of a gas and a liquid, respectively.
- the high-pressure groove 71 has been described as being formed in a circular shape having a center P1 at the innermost inner diameter of the sliding surface 7a, and the wall surface 71a is formed in a substantially semi-arc shape, but the present invention is not limited to this.
- the high-pressure groove may be any as long as the wall surface is continuous in an arc shape.
- the high-pressure groove may be formed in a semi-elliptical shape and the wall surface may be in an arc shape. The same applies to the low pressure groove 72.
- the low-pressure groove is described as having a larger axial viewing area than the high-pressure groove, but the low-pressure groove is not limited to this, and the low-pressure groove has the same axial viewing area as the high-pressure groove. It may be present, or the axial viewing area may be smaller than that of the high-pressure groove.
- a balance is achieved so that substantially the same dynamic pressure is generated in a range of 360 degrees in the circumferential direction between the sliding surfaces. You may.
- the sliding component of the present invention has a sliding surface that slides relative to each other with eccentric rotation, it is not limited to an environment where there is a pressure difference between the inside and outside of the sliding surface, and the inside and outside of the sliding surface. It may be used in an environment where the pressures are substantially the same. Further, the sliding component of the present invention does not need to function as a seal, and may be any as long as it can stably reduce the frictional resistance of the sliding surface.
- the side seal having the sliding surface that slides relative to each other is described as being made of resin and the thrust plate is made of metal, but the material of the sliding parts can be freely selected according to the usage environment and the like. You can do it.
- the present invention is not limited to this, and sliding having a sliding surface that slides relative to each other with eccentric rotation.
- a groove may be formed in the sliding region (see FIG. 4) of the sliding surface of the thrust plate which is a component. Further, a groove may be formed on both the sliding surface of the side seal and the sliding surface of the thrust plate.
- a groove may be formed on a sliding surface that includes only one of the thrust plates and slides relative to each other with eccentric rotation.
- a groove may be formed on either or both of the sliding surface of the thrust plate as a sliding component and the back surface of the end plate of the movable scroll.
- a groove may be formed on the sliding surface of the side seal as a sliding component. In this case, the side seal abuts on the inner peripheral surface of the inner casing and also functions as a thrust bearing that receives an axial load of the movable scroll.
- the movable scroll does not have a side seal and a thrust plate, and the back surface of the end plate of the movable scroll abuts on the inner peripheral surface of the inner casing and functions as a thrust bearing that receives an axial load of the movable scroll, the movable scroll A groove may be formed on the sliding surface formed on the back surface of the end plate.
- the side seal has been described as having an axial viewing ring, but the present invention is not limited to this, and the side seal may be formed in the shape of an axial viewing disk.
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
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- Ocean & Marine Engineering (AREA)
- Rotary Pumps (AREA)
Abstract
Description
内外に高圧と低圧の流体が面する円環形状を成し、偏心回転を伴って相対摺動する摺動面を有する摺動部品であって、
前記摺動面には、高圧の流体が存在する空間に開口する高圧溝と、低圧の流体が存在する空間に開口する低圧溝と、がそれぞれ周方向に複数設けられている。
これによれば、偏心回転に伴う高圧溝および低圧溝の相対移動の方向に応じて、摺動部品の内外の空間に存在する流体を利用して周方向に設けられるいずれかの高圧溝内および低圧溝内で動圧が発生し、摺動面同士がわずかに離間し流体膜が形成される。これにより摺動時における潤滑性が向上し、摺動面の摩擦抵抗を安定して低減することが可能となる。
これによれば、偏心回転に伴う高圧溝および低圧溝の相対移動の方向に応じて、低圧溝内で発生する動圧と、高圧溝内で発生する動圧とのバランスを取りやすい。そのため、摺動部品は動圧発生による振動や傾き等が抑制されている。
これによれば、偏心回転に伴う高圧溝および低圧溝の相対移動の方向によらず、内外交互に配置される高圧溝内および低圧溝内のいずれかで動圧が発生するため、摺動面の周方向に亘って発生する動圧のバランスがよい。
これによれば、高圧溝内および低圧溝内でそれぞれ発生する動圧により、摺動面同士を周方向に略均等に離間させることができる。
これによれば、偏心回転に伴う高圧溝および低圧溝の相対移動の方向に応じて、高圧溝と低圧溝の円弧形状の壁面に沿ってそれぞれ安定した動圧を発生させることができる。
これによれば、摺動面の外径側に低圧溝が形成されるため、低圧溝の開口や摺動面と平行な方向の面積を大きく確保しやすい。
2 回転軸
2a 偏心部
3 インナーケーシング
4 スクロール圧縮機構
6 オイルセパレータ
7 サイドシール(摺動部品)
7a 摺動面
8 スラストプレート
8a 摺動面
10 吸入口
13 吐出連通路
14 背圧連通路
15 吸入連通路
20 低圧室
30 高圧室
40 圧縮室
41 固定スクロール
42 可動スクロール
50 背圧室
71 高圧溝
72 低圧溝
79 ランド
107 サイドシール(摺動部品)
171 高圧溝
172 低圧溝
207 サイドシール(摺動部品)
271 高圧溝
272 低圧溝
307 サイドシール(摺動部品)
371 高圧溝
372 低圧溝
C スクロール圧縮機
M 駆動モータ
P1 高圧溝の中心
P2 低圧溝の中心
Claims (6)
- 内外に高圧と低圧の流体が面する円環形状を成し、偏心回転を伴って相対摺動する摺動面を有する摺動部品であって、
前記摺動面には、高圧の流体が存在する空間に開口する高圧溝と、低圧の流体が存在する空間に開口する低圧溝と、がそれぞれ周方向に複数設けられている摺動部品。 - 前記低圧溝は、前記高圧溝よりも前記摺動面と平行な方向の面積が大きい請求項1に記載の摺動部品。
- 前記高圧溝と前記低圧溝は、内外交互に配置されている請求項1または2に記載の摺動部品。
- 前記高圧溝と前記低圧溝は、周方向にそれぞれ等配されている請求項1ないし3のいずれかに記載の摺動部品。
- 前記高圧溝と前記低圧溝は、円の一部から形成された形状である請求項1ないし4のいずれかに記載の摺動部品。
- 前記低圧の流体が存在する空間は、前記摺動面の外径側の空間である請求項1ないし5のいずれかに記載の摺動部品。
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KR1020237000902A KR20230022987A (ko) | 2020-07-06 | 2021-07-01 | 슬라이딩 부품 |
US18/012,856 US20230258181A1 (en) | 2020-07-06 | 2021-07-01 | Sliding component |
JP2022535277A JP7475801B2 (ja) | 2020-07-06 | 2021-07-01 | 摺動部品 |
CN202180044576.6A CN115917171A (zh) | 2020-07-06 | 2021-07-01 | 滑动部件 |
EP21836928.8A EP4177485A4 (en) | 2020-07-06 | 2021-07-01 | SLIDING ELEMENT |
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JP2020-116357 | 2020-07-06 | ||
JP2020116357 | 2020-07-06 |
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US (1) | US20230258181A1 (ja) |
EP (1) | EP4177485A4 (ja) |
JP (1) | JP7475801B2 (ja) |
KR (1) | KR20230022987A (ja) |
CN (1) | CN115917171A (ja) |
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2021
- 2021-07-01 US US18/012,856 patent/US20230258181A1/en active Pending
- 2021-07-01 EP EP21836928.8A patent/EP4177485A4/en active Pending
- 2021-07-01 CN CN202180044576.6A patent/CN115917171A/zh active Pending
- 2021-07-01 WO PCT/JP2021/024941 patent/WO2022009768A1/ja unknown
- 2021-07-01 KR KR1020237000902A patent/KR20230022987A/ko unknown
- 2021-07-01 JP JP2022535277A patent/JP7475801B2/ja active Active
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EP4177485A1 (en) | 2023-05-10 |
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