WO2023027102A1 - 摺動部品 - Google Patents

摺動部品 Download PDF

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Publication number
WO2023027102A1
WO2023027102A1 PCT/JP2022/031862 JP2022031862W WO2023027102A1 WO 2023027102 A1 WO2023027102 A1 WO 2023027102A1 JP 2022031862 W JP2022031862 W JP 2022031862W WO 2023027102 A1 WO2023027102 A1 WO 2023027102A1
Authority
WO
WIPO (PCT)
Prior art keywords
dynamic pressure
pressure generating
generating groove
groove
sliding
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2022/031862
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
忠継 井村
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eagle Industry Co Ltd
Original Assignee
Eagle Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eagle Industry Co Ltd filed Critical Eagle Industry Co Ltd
Priority to JP2023543950A priority Critical patent/JP7842769B2/ja
Priority to US18/685,161 priority patent/US20240344555A1/en
Priority to EP22861390.7A priority patent/EP4394217A4/en
Priority to KR1020247008518A priority patent/KR20240046244A/ko
Priority to CN202280057538.9A priority patent/CN117836546A/zh
Publication of WO2023027102A1 publication Critical patent/WO2023027102A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • 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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • 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
    • 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
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • 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
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • 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
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/42—Groove sizes

Definitions

  • the present invention relates to sliding parts used for shaft seals and bearings.
  • a mechanical seal consisting of a pair of annular sliding rings that rotate relative to each other and whose sliding surfaces slide against each other is known as a sliding part that prevents leakage of the sealed fluid around the rotating shaft in a rotating machine.
  • mechanical seals in recent years, there has been a desire to reduce the energy lost due to sliding for environmental measures, etc., and some mechanical seals are provided with positive pressure generating grooves on the sliding surface of the sliding ring.
  • a plurality of dynamic pressure generating mechanisms are provided in the circumferential direction on the sliding surface of one of the sliding rings.
  • This dynamic pressure generating mechanism includes a first dynamic pressure generating groove extending obliquely with respect to the relative rotation direction and closed at both ends, and a first dynamic pressure generating groove extending obliquely in the direction opposite to the first dynamic pressure generating groove with respect to the relative rotation direction. and a second dynamic pressure generating groove having both ends closed.
  • the first dynamic pressure generating groove and the second dynamic pressure generating groove are arranged side by side in the radial direction on the sliding surface.
  • a pressure generating groove is arranged on the inner diameter side (leakage side). Further, the entire grooves of the first dynamic pressure generating groove and the second dynamic pressure generating groove have a constant depth.
  • the sealed fluid present in the first dynamic pressure generating groove moves toward the end on the downstream side (inner diameter side) of the relative rotation, and the sealed fluid concentrates on the end.
  • the sliding surfaces are separated from each other, and a fluid film of the sealed fluid is formed on the sliding surfaces, thereby improving lubricity and realizing low friction.
  • the second dynamic pressure generating groove a relative negative pressure is generated in the vicinity of the end on the relative rotation upstream side (inner diameter side), and the sealed fluid flowing out to the sliding surface flows into the second dynamic pressure generating groove. Since it is sucked, leakage of the sealed fluid to the space on the leakage side can be reduced.
  • the present invention has been made with a focus on such problems, and an object of the present invention is to provide a sliding component that has excellent lubricity by separating the sliding surfaces against relative rotation in both directions.
  • the sliding component of the present invention is A first dynamic pressure generating groove extending obliquely with respect to the direction of relative rotation and a first dynamic pressure generating groove disposed on either one of the pair of sliding surfaces so as to face a portion of the rotating machine that rotates relatively, and the pair of sliding surfaces.
  • the bottom surfaces of the first dynamic pressure generating groove and the second dynamic pressure generating groove are inclined in the same radial direction. According to this, the first dynamic pressure generating groove becomes shallower toward the end on the downstream side of the relative rotation.
  • the second dynamic pressure generating groove becomes deeper toward the downstream end of the relative rotation.
  • positive pressure is likely to be generated in the first dynamic pressure generating grooves and negative pressure is less likely to be generated in the second dynamic pressure generating grooves with respect to relative rotation in the forward direction.
  • negative pressure is less likely to be generated in the first dynamic pressure generating grooves, and positive pressure is more likely to be generated in the second dynamic pressure generating grooves. Therefore, against relative rotation in both directions, positive pressure is reliably generated in the entirety of the first and second dynamic pressure generating grooves provided on the sliding surfaces, and the sliding surfaces are separated from each other, so that the sliding parts Excellent lubricity.
  • the deep end of the first dynamic pressure generating groove may communicate with either the space on the sealed fluid side or the leakage side. According to this, with respect to the relative rotation in the forward direction, the sealed fluid or the fluid on the leakage side is easily supplied into the first dynamic pressure generating groove, so the positive pressure is easily increased. Further, with respect to the relative rotation in the opposite direction, since the fluid is easily discharged from the first dynamic pressure generating groove to the sealed fluid side or the leak side space, negative pressure is less likely to occur.
  • the second dynamic pressure generating groove is a closed groove, and the length of the first dynamic pressure generating groove in the tilting direction of the first dynamic pressure generating groove is longer than the tilting direction of the second dynamic pressure generating groove.
  • the length of the second hydrodynamic groove may be formed long. According to this, with respect to relative rotation in the opposite direction, the positive pressure generating capability of the second dynamic pressure generating groove, which does not communicate with either the space on the sealed fluid side or the leakage side, is enhanced. Therefore, the same degree of positive pressure is generated by the first and second dynamic pressure generating grooves with respect to relative rotation in both directions.
  • the first dynamic pressure generating groove and the second dynamic pressure generating groove may be connected. According to this, the fluid is easily supplied between the first dynamic pressure generating groove and the second dynamic pressure generating groove.
  • the first dynamic pressure generating groove and the second dynamic pressure generating groove may be arranged side by side in the radial direction. According to this, since dynamic pressures having different magnitudes are generated on the sliding surface in the radial direction, the dynamic pressure tends to be generated uniformly over the circumferential direction of the sliding surface.
  • the first dynamic pressure generating groove and the second dynamic pressure generating groove may be provided on the sliding surface of one of the sliding parts. According to this, it is easy to adjust the balance of dynamic pressure generated in the entirety of the first and second dynamic pressure generating grooves.
  • FIG. 1 is a longitudinal sectional view showing an example of a mechanical seal in Example 1 of the present invention
  • FIG. FIG. 4 is a view of the sliding surface of the stationary seal ring in Example 1 as seen from the axial direction
  • 4 is an enlarged view of the sliding surface of the stationary seal ring in Example 1 as seen from the axial direction
  • FIG. FIG. 4 is a cross-sectional view taken along the line AA of FIG. 3
  • 5 is a diagram showing radial depth distributions of first dynamic pressure generating grooves and second dynamic pressure generating grooves in Example 1.
  • FIG. 4 is an enlarged view of the sliding surface of the stationary seal ring in Example 1 as seen from the axial direction;
  • FIG. 8 is an enlarged view of the sliding surface of the stationary seal ring in Example 2 of the present invention, viewed from the axial direction;
  • FIG. 11 is an enlarged view of the sliding surface of the stationary seal ring in Example 3 of the present invention as seen from the axial direction;
  • FIG. 11 is an enlarged view of the sliding surface of the stationary seal ring in Example 4 of the present invention as seen from the axial direction;
  • FIG. 10 is a cross-sectional view taken along the line BB of FIG. 9;
  • FIG. 12 is an enlarged view of the sliding surface of the stationary seal ring in Example 5 of the present invention, viewed from the axial direction;
  • 8 is an enlarged view of the sliding surface of the stationary seal ring in Modification 1 as seen from the axial direction;
  • FIG. 11 is an enlarged view of the sliding surface of the stationary seal ring in Modification 2 as seen from the axial direction;
  • FIG. 11 is a view of the sliding surface of the stationary seal ring in Modification 3 as seen from the axial direction;
  • FIG. 11 is a view of the sliding surface of the stationary seal ring in Modification 4 as seen from the axial direction;
  • FIG. 1 A mechanical seal as a sliding component according to Example 1 will be described with reference to FIGS. 1 to 6.
  • the sealed fluid F exists in the inner space S1 of the mechanical seal, and the atmosphere A exists in the outer space S2. side (high pressure side) and the outer diameter side as the leakage side (low pressure side).
  • grooves formed on the sliding surface may be given a gradation indicating shallowness and depth.
  • the automotive mechanical seal shown in FIG. 1 seals the sealed fluid F in the inner space S1 that is about to leak from the inner diameter side of the sliding surface toward the outer diameter side, and the outer space S2 communicates with the atmosphere A. It has a side shape.
  • the sealed fluid F is a high-pressure gas
  • the atmosphere A is a gas with a lower pressure than the sealed fluid F.
  • a mechanical seal is mainly composed of a rotary seal ring 20 as a sliding component and a stationary seal ring 10 as a sliding component.
  • the rotary seal ring 20 has an annular shape and is provided on the rotary shaft 1 via the sleeve 2 so as to be rotatable together with the rotary shaft 1 .
  • the stationary seal ring 10 has an annular shape and is provided in a non-rotating and axially movable state on a seal cover 5 fixed to a housing 4 of a device to which it is attached.
  • the stationary seal ring 10 is urged in the axial direction by the elastic member 7, so that the sliding surface 11 of the stationary seal ring 10 and the sliding surface 21 of the rotary seal ring 20 closely slide against each other.
  • the sliding surface 21 of the rotary seal ring 20 is a flat surface, and this flat surface is not provided with recesses such as grooves.
  • the stationary seal ring 10 and the rotary seal ring 20 are typically made of a combination of SiC (hard material) or SiC (hard material) and carbon (soft material). Any material that is used as a sliding material for mechanical seals can be applied.
  • SiC include sintered bodies using boron, aluminum, carbon, etc. as sintering aids, and materials composed of two or more phases with different components and compositions, such as SiC and SiC in which graphite particles are dispersed.
  • Metal materials, resin materials, surface modification materials (coating materials), composite materials, etc. are also applicable in addition to the sliding materials described above.
  • the rotary seal ring 20 which is the mating seal ring, slides counterclockwise relative to the stationary seal ring 10 as indicated by the solid line arrow.
  • this state will be described as forward relative rotation between the stationary seal ring 10 and the rotary seal ring 20 .
  • the sliding surface 11 of the stationary seal ring 10 is provided with a plurality of dynamic pressure generating mechanisms 13 on the inner diameter side and a plurality of dynamic pressure generating mechanisms 16 on the outer diameter side.
  • the dynamic pressure generating mechanisms 13 are evenly arranged in the circumferential direction (12 in this embodiment) on the inner diameter side of the sliding surface 11 .
  • the dynamic pressure generating mechanisms 16 are evenly arranged in the circumferential direction (12 in this embodiment) on the outer diameter side of the sliding surface 11 .
  • the dynamic pressure generating mechanisms 13 and 16 are arranged side by side in the radial direction. good.
  • the portion of the sliding surface 11 other than the dynamic pressure generating mechanisms 13 and 16 is a land 12 having a flat surface arranged on the same plane.
  • the flat surface of the land 12 functions as a sliding surface that substantially slides against the sliding surface 21 of the rotary seal ring 20 .
  • the dynamic pressure generating mechanism 13 on the inner diameter side is composed of a first dynamic pressure generating groove 14 and a second dynamic pressure generating groove 15 .
  • the first dynamic pressure generating groove 14 communicates with the inner space S1 and linearly extends radially outward from the inner peripheral surface 10g of the stationary seal ring 10 while being inclined with respect to the relative rotation direction.
  • the second dynamic pressure generating grooves 15 are inclined in the direction opposite to the first dynamic pressure generating grooves 14 with respect to the relative rotation direction from the radially outer end of the first dynamic pressure generating grooves 14 and extend linearly in the outer radial direction. extended.
  • the term "tilting" of the groove means that the groove does not extend in the longitudinal direction parallel to the direction of relative rotation (i.e., the circumferential direction) and does not extend perpendicularly to the direction of relative rotation. .
  • Part of the groove may be parallel or perpendicular to the direction of relative rotation (that is, the circumferential direction).
  • first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 are arranged side by side in the radial direction, and are connected to each other at their ends.
  • the second dynamic pressure generating groove 15 is longer than the first dynamic pressure generating groove 14 in the extension direction of the groove, in other words, the length of the groove in the longitudinal direction of the groove, or the length of the groove in the inclination direction of the groove.
  • the length is long, and more specifically, the circumferential component in the extending direction of the groove is long.
  • the first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 have substantially the same length in the radial direction component in the extension direction of the groove.
  • the ends of the adjacent second dynamic pressure generating grooves 15 are arranged so as to overlap each other in the radial direction.
  • the end of the second dynamic pressure generating groove 15 on the upstream side of the relative rotation that is, the end having the edge 15f, is the downstream end of the relatively rotationally adjacent second dynamic pressure generating groove 15' in the circumferential direction. That is, they are arranged so as to radially overlap on the outer diameter side of the end having the edge 15e'.
  • the first dynamic pressure generating groove 14 is composed of a bottom surface 14a and side surfaces 14b and 14c.
  • the bottom surface 14 a extends linearly while being inclined with respect to the flat surface of the land 12 .
  • the side surfaces 14b and 14c rise from both circumferential edges of the bottom surface 14a.
  • An opening 14A communicating with the inner space S1 is formed at the inner diameter side end of the first dynamic pressure generating groove 14. As shown in FIG.
  • the first dynamic pressure generating groove 14 has the deepest edge 14d on the inner diameter side of the bottom surface 14a located in the opening 14A communicating with the inner space S1, and the edge 14d on the outer diameter side of the bottom surface 14a is the deepest. 14e is inclined in the radial direction with respect to the flat surface of the land 12 so as to be the shallowest. That is, the first dynamic pressure generating groove 14 is formed so that the depth becomes shallower from the inner diameter side edge 14d of the bottom surface 14a toward the outer diameter side edge 14e.
  • the first dynamic pressure generating groove 14 is formed so that it is deeper on the upstream side of relative rotation and shallower on the downstream side of relative rotation with respect to forward relative rotation indicated by solid arrows in FIGS.
  • the second dynamic pressure generating groove 15 is composed of a bottom surface 15a, side surfaces 15b and 15c, and an inner diameter side end surface 15d.
  • the bottom surface 15 a extends linearly while being inclined with respect to the flat surface of the land 12 .
  • the side surfaces 15b and 15c rise from both circumferential edges of the bottom surface 15a.
  • An end surface 15d on the inner diameter side rises from the inner diameter end of the bottom surface 15a and is orthogonally connected to the side surfaces 15b and 15c.
  • the second dynamic pressure generating groove 15 is flattened so that the edge 15e on the inner diameter side of the bottom surface 15a is the deepest and the edge 15f on the outer diameter side of the bottom surface 15a is the shallowest. It is inclined in its radial direction with respect to the plane. That is, the second dynamic pressure generating groove 15 is formed so that the depth becomes shallower from the inner diameter side edge 15e of the bottom surface 15a toward the outer diameter side edge 15f.
  • the second dynamic pressure generating groove 15 is shallow on the upstream side of relative rotation and deep on the downstream side of relative rotation with respect to forward relative rotation indicated by solid arrows in FIGS.
  • first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 constituting the dynamic pressure generating mechanism 13 have opposite depth relationships with respect to the relative rotation direction.
  • the deepest portions of the first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 have the same depth.
  • the depths D1 and D2 of the first dynamic pressure generating grooves 14 and the second dynamic pressure generating grooves 15 are shown deeper than they actually are for convenience of explanation.
  • the radially outer edge 14e of the bottom surface 14a of the first dynamic pressure generating groove 14 and the radially outer edge 15f of the bottom surface 15a of the second dynamic pressure generating groove 15 It is coplanar with the flat surface and has substantially no depth.
  • FIG. in FIG. is expressed to be larger than the radial inclination with respect to 4 is a cross-sectional view taken along line AA in FIG. 3.
  • the second dynamic pressure generating grooves 15 are longer than the first dynamic pressure generating grooves 14 in the extending direction of the grooves. Specifically, this is because the circumferential component in the extending direction of the groove is formed to be long.
  • the first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 are formed so that the depth distribution in the radial direction has the same degree of inclination. .
  • the dynamic pressure generating mechanism 16 on the outer diameter side is composed of a first dynamic pressure generating groove 17 and a second dynamic pressure generating groove 18 .
  • the first dynamic pressure generating groove 17 communicates with the outer space S2 and linearly extends radially inward from the outer peripheral surface 10h of the stationary seal ring 10 while being inclined with respect to the relative rotation direction.
  • the second dynamic pressure generating groove 18 extends linearly in the radial direction from the radially inner end of the first dynamic pressure generating groove 17 while being inclined in the direction opposite to the first dynamic pressure generating groove 17 with respect to the relative rotation direction.
  • first dynamic pressure generating groove 17 and the second dynamic pressure generating groove 18 are arranged side by side in the radial direction, and are connected to each other at their ends.
  • the second dynamic pressure generating groove 18 has a longer groove length in the groove extending direction than the first dynamic pressure generating groove 17, and more specifically, has a longer circumferential component in the groove extending direction.
  • the first dynamic pressure generating groove 17 and the second dynamic pressure generating groove 18 have substantially the same length in the radial direction component in the extension direction of the groove.
  • the ends of the adjacent second dynamic pressure generating grooves 18 are arranged so as to overlap each other in the radial direction.
  • the end of the second dynamic pressure generating groove 18 on the relative rotation upstream side that is, the end having the edge 18f
  • the relative rotation downstream end of the second dynamic pressure generating groove 18' adjacent in the circumferential direction that is, they are arranged so as to radially overlap on the inner diameter side of the end having the edge 18e'.
  • the first dynamic pressure generating groove 17 is composed of a bottom surface 17a and side surfaces 17b and 17c.
  • the bottom surface 17 a extends linearly while being inclined with respect to the flat surface of the land 12 .
  • the side surfaces 17b and 17c rise from both circumferential edges of the bottom surface 17a.
  • An opening 17A communicating with the outer space S2 is formed at the outer diameter side end of the first dynamic pressure generating groove 17. As shown in FIG.
  • the first dynamic pressure generating groove 17 has the deepest edge 17d on the inner diameter side of the bottom surface 17a located in the opening 17A communicating with the outer space S2, and the outer edge 17d on the outer diameter side of the bottom surface 17a.
  • the edge 17e is inclined in the radial direction with respect to the flat surface of the land 12 so as to be the shallowest. That is, the first dynamic pressure generating groove 17 is formed so that the depth of the bottom surface 17a decreases from an inner diameter side edge 17d toward an outer diameter side edge 17e. 2 and 3, the first dynamic pressure generating groove 17 is formed so that it is deeper on the upstream side of relative rotation and shallower on the downstream side of relative rotation with respect to forward relative rotation indicated by solid arrows in FIGS.
  • the second dynamic pressure generating groove 18 is composed of a bottom surface 18a, side surfaces 18b and 18c, and an outer diameter side end surface 18d.
  • the bottom surface 18 a extends linearly while being inclined with respect to the flat surface of the land 12 .
  • the side surfaces 18b and 18c rise from both circumferential edges of the bottom surface 18a.
  • An outer diameter side end surface 18d rises from the inner diameter end of the bottom surface 18a and is orthogonally connected to the side surfaces 18b and 18c.
  • the second dynamic pressure generating groove 18 is arranged such that the edge 18e on the inner diameter side of the bottom surface 18a is the deepest and the edge 18f on the outer diameter side of the bottom surface 18a is the shallowest. radially inclined with respect to the flat surface of the That is, the second dynamic pressure generating groove 18 is formed so that the depth decreases from the inner diameter side edge 18e of the bottom surface 18a toward the outer diameter side edge 18f of the bottom surface 18a.
  • the second dynamic pressure generating groove 18 is shallow on the upstream side of relative rotation and deep on the downstream side of relative rotation with respect to forward relative rotation indicated by solid arrows in FIGS.
  • the first dynamic pressure generating groove 17 and the second dynamic pressure generating groove 18 that constitute the dynamic pressure generating mechanism 16 have opposite depth relationships with respect to the relative rotation direction. Further, the dynamic pressure generating mechanism 16 has the first dynamic pressure generating groove 17 and the second dynamic pressure generating groove 17 so as to form a so-called mirror image relationship with respect to the dynamic pressure generating mechanism 13 with respect to the center line (not shown) in the radial direction of the sliding surface. A dynamic pressure generating groove 18 is formed.
  • FIG. 3 the flow of the sealed fluid F is indicated by black arrows, and the flow of atmosphere A is indicated by white arrows.
  • the sealed fluid F flows into the first dynamic pressure generating groove 14 from the opening 14A, and the sealed fluid F flowing into the first dynamic pressure generating groove 14 also slightly flows into the second dynamic pressure generating groove 15 which crosses over the edge 14e on the outer diameter side of the bottom surface 14a and is connected to the outer diameter side.
  • the air A flows into the first dynamic pressure generating groove 17 from the opening 17A, and the air A flowing into the first dynamic pressure generating groove 17 crosses the edge 17e on the outer diameter side of the bottom surface 17a and moves to the inner diameter side. It also slightly flows into the connected second dynamic pressure generating grooves 18 .
  • the sealed fluid F in the first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 is It follows the rotation direction of the rotary seal ring 20 by shearing with the sliding surface 21 .
  • the sealed fluid F moves from the vicinity of the opening 14A toward the outer edge 14e as indicated by the arrow F1.
  • the fluid pressure near the opening 14A is relatively lower than the surrounding fluid pressure.
  • a relative negative pressure is generated in the vicinity of the opening 14A, and the sealed fluid F in the inner space S1 is sucked into the first dynamic pressure generating groove 14 as indicated by the arrow F2.
  • the depth D1 of the inner diameter side edge 14d positioned at the opening 14A is the deepest (see FIG. 4). can bring in a lot of
  • the sealed fluid F moves along the side surface 14b toward the edge 14e on the outer diameter side as indicated by the arrow F3.
  • the pressure of the sealed fluid F moving toward the edge 14e is increased at and near the corner 14B formed by the edge 14e and the side surface 14b. That is, a positive pressure is generated at the corner portion 14B of the first hydrodynamic groove 14 and its vicinity.
  • the sealed fluid F since the depth of the first dynamic pressure generating groove 14 becomes shallower from the inner diameter side edge 14d toward the outer diameter side edge 14e, the sealed fluid F The pressure is likely to be increased even in the process of moving toward the corner 14B. Further, even if the amount of movement of the fluid F to be sealed is small because the rotation speed of the rotary seal ring 20 is low, positive pressure is likely to be generated at the corner portion 14B of the first hydrodynamic groove 14 and its vicinity.
  • the sliding surfaces 11 and 21 are slightly separated from each other by the force generated by the positive pressure generated at the corner 14B of the first dynamic pressure generating groove 14 and its vicinity (not shown).
  • the sealed fluid F in the first hydrodynamic groove 14 flows out between the sliding surfaces 11 and 21 as indicated by arrow F4.
  • the sealed fluid F moves from the outer diameter side edge 15f toward the inner diameter side edge 15e as indicated by the arrow F5. Since the depth of the second dynamic pressure generating groove 15 increases from the outer diameter side edge 15f toward the inner diameter side edge 15e, almost no dynamic pressure is generated in the second dynamic pressure generating groove 15. .
  • a relative negative pressure is generated in the vicinity of the outer edge 15f of the second dynamic pressure generating groove 15, and a relative positive pressure is generated in the vicinity of the inner diameter edge 15e.
  • the absolute value of the positive pressure is extremely small. Therefore, as described above, dynamic pressure is much more difficult to generate in the second dynamic pressure generating grooves 15 than in the first dynamic pressure generating grooves 14 .
  • the sealed fluid flowed out between the sliding surfaces 11 and 21 from the first dynamic pressure generating groove 14' of the dynamic pressure generating mechanism 13' adjacent to the relative rotation upstream side in the circumferential direction.
  • the fluid F is sucked into the second dynamic pressure generating grooves 15 as indicated by arrow F6.
  • part of the sealed fluid F that has crossed over the edge 14 e of the first dynamic pressure generating groove 14 of the same dynamic pressure generating mechanism 13 flows into the second dynamic pressure generating groove 15 . This also makes it difficult for the second dynamic pressure generating grooves 15 to generate dynamic pressure.
  • the bottom surfaces 14a and 15a of the first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 are inclined so that the depth distribution in the radial direction has the same linear inclination degree.
  • positive pressure is more easily generated in the first dynamic pressure generating grooves 14 and negative pressure is less likely to be generated in the second dynamic pressure generating grooves 15 .
  • these inclinations may be curved rather than linear.
  • the inclination of the first dynamic pressure generating groove 14 and the inclination of the second dynamic pressure generating groove 15 in the depth distribution in the radial direction may not be the same.
  • the sealed fluid F in the first dynamic pressure generating groove 14 and the second dynamic pressure generating groove 15 is It follows the rotation direction of the rotary seal ring 20 by shearing with the sliding surface 21 .
  • the sealed fluid F moves from the outer edge 14e toward the opening 14A as indicated by an arrow F11. Since the depth of the first dynamic pressure generating groove 14 increases from the edge 14e on the outer diameter side toward the edge 14d on the inner diameter side, almost no dynamic pressure is generated in the first dynamic pressure generating groove 14. .
  • a relative negative pressure is generated near the outer edge 14e of the first dynamic pressure generating groove 14, and a relative positive pressure is generated near the inner diameter edge 14d.
  • the absolute value of the positive pressure is extremely small. Therefore, as described above, in the first dynamic pressure generating grooves 14 , dynamic pressure is much more difficult to generate than in the second dynamic pressure generating grooves 15 .
  • the first dynamic pressure generating groove 14 communicates with the inner space S1 through the opening 14A, almost no dynamic pressure is generated in the first dynamic pressure generating groove 14. Therefore, the sealed fluid F is hardly sucked into the first dynamic pressure generating groove 14 from between the sliding surfaces 11 and 21 .
  • the sealed fluid F moves from the inner diameter side edge 15e toward the outer diameter side edge 15f as indicated by the arrow F12.
  • the fluid pressure at the inner diameter side edge 15e is relatively lower than the surrounding fluid pressure.
  • a relative negative pressure is generated in the vicinity of the inner diameter side edge 15e, and the second dynamic pressure generating groove 15' of the dynamic pressure generating mechanism 13' adjacent to the upstream side in the relative rotation direction in the circumferential direction and the sliding surface.
  • the sealed fluid F that has flowed out between 11 and 21 is sucked into the second dynamic pressure generating groove 15 as indicated by an arrow F13.
  • the fluid pressure at the edge 15e on the inner diameter side of the second dynamic pressure generating groove 15 14 is relatively lower than the fluid pressure at the edge 14e on the outer diameter side. Therefore, the sealed fluid F between the sliding surfaces 11 and 21 is more easily sucked into the second dynamic pressure generating grooves 15 than into the first dynamic pressure generating grooves 14 .
  • the sealed fluid F moves along the side surface 15b toward the outer edge 15f as indicated by the arrow F14.
  • the pressure of the sealed fluid F that has moved toward the edge 15f is increased at and near the corner 15B formed by the edge 15e and the side surface 15b. That is, a positive pressure is generated at the corner portion 15B of the second dynamic pressure generating groove 15 and its vicinity.
  • the sealed fluid F since the depth of the second dynamic pressure generating groove 15 decreases from the inner diameter side edge 15e toward the outer diameter side edge 15f, the sealed fluid F The pressure is likely to be increased even in the process of moving toward the corner 15B. Further, even if the amount of movement of the fluid to be sealed F is small because the rotation speed of the rotary seal ring 20 is low, positive pressure is likely to be generated at the corner portion 15B of the second dynamic pressure generating groove 15 and its vicinity.
  • the second dynamic pressure generating groove 15 is longer in the extending direction than the first dynamic pressure generating groove 14, and more specifically, the circumferential component in the extending direction of the groove is longer. The pressure is likely to be further increased in the process of moving toward the corner 15B.
  • the sliding surfaces 11 and 21 are slightly separated from each other by the force of the positive pressure generated at the corner 15B of the second dynamic pressure generating groove 15 and its vicinity (not shown).
  • the sealed fluid F in the second dynamic pressure generating groove 15 flows out between the sliding surfaces 11 and 21 as indicated by an arrow F15.
  • the radially outer edge 15f of the second dynamic pressure generating groove 15 is arranged on the same plane as the flat surface of the land 12, the radially outer edge 15f of the second hydrodynamic groove 15 can be A positive pressure is generated over a wide range.
  • positive pressure of the same degree is generated in the entire dynamic pressure generating mechanisms 13 and 16 during relative rotation in the forward direction shown in FIG. 3 and relative rotation in the reverse direction shown in FIG. occur.
  • the bottom surfaces of the first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18 constituting the dynamic pressure generating mechanisms 13, 16 are inclined in the same radial direction.
  • the depth relationship with respect to the direction of relative rotation is reversed.
  • the first dynamic pressure generating grooves 14 and 17 are located at the downstream end of the relative rotation, that is, the end having the edges 14e and 17e. It gets shallower as you go.
  • the second hydrodynamic grooves 15 and 18 become deeper toward the downstream end of the relative rotation, that is, the end having the edges 15e and 18e.
  • the first dynamic pressure generating groove 14 that constitutes the dynamic pressure generating mechanism 13 communicates with the inner space S1, which is the space on the side of the sealed fluid F, at the deep end, that is, the end having the edge 14d.
  • the first dynamic pressure generating groove 17 constituting the dynamic pressure generating mechanism 16 communicates with the outer space S2, which is a space on the atmosphere A side, at the deep end, that is, the end having the edge 17d.
  • the sealed fluid F or the atmosphere A is easily supplied into the first dynamic pressure generating grooves 14 and 17 with respect to the relative rotation in the forward direction, so the positive pressure is easily increased.
  • the fluid is more likely to be discharged from inside the first dynamic pressure generating grooves 14 and 17 to the inner space S1 or the outer space S2, so negative pressure is less likely to occur.
  • the second dynamic pressure generating grooves 15 and 18 are closed grooves and have a longer groove length in the extension direction than the first dynamic pressure generating grooves 14 and 17. A circumferential component in the direction is formed long. According to this, the positive pressure generating capability of the second dynamic pressure generating grooves 15 and 18, which are not in communication with the inner space S1 and the outer space S2, is enhanced with respect to the relative rotation in the opposite direction. Therefore, the same degree of positive pressure is generated by the first dynamic pressure generating grooves 14 and 17 and the second dynamic pressure generating grooves 15 and 18 with respect to relative rotation in both directions.
  • first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18 are connected substantially without the land 12 interposed therebetween, the first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 14, 17 Fluid is easily supplied between the dynamic pressure generating grooves 15 and 18 .
  • the fluid is supplied from the dynamic pressure generating groove in which positive pressure is generated to the dynamic pressure generating groove in which negative pressure is difficult to generate, regardless of the direction of relative rotation. Negative pressure is more difficult to generate.
  • first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18 are arranged side by side in the radial direction. According to this, since dynamic pressures having different magnitudes are generated on the sliding surface 11 in the radial direction, the dynamic pressure tends to be generated uniformly over the circumferential direction of the sliding surface 11 . Also, the dynamic pressure generating mechanisms 13 and 16 can be efficiently arranged in the circumferential direction of the sliding surface 11 .
  • the sliding surface 21 of the rotary seal ring 20 is a flat surface, and the sliding surface 11 of the stationary seal ring 10 is provided with the first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18. there is According to this, it is easy to adjust the balance of the dynamic pressure generated in the first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18 as a whole.
  • first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18 are formed such that the depths of the deepest and shallowest portions are the same (see FIG. 4), so that It is easy to adjust the balance of the dynamic pressure generated in the first dynamic pressure generating grooves 14, 17 and the second dynamic pressure generating grooves 15, 18 as a whole to the same extent with respect to the relative rotation.
  • the stationary seal ring 210 of the second embodiment constitutes a first dynamic pressure generating groove 214 and a second dynamic pressure generating groove 215 constituting a dynamic pressure generating mechanism 213, and a dynamic pressure generating mechanism 216.
  • the first dynamic pressure generating groove 217 and the second dynamic pressure generating groove 218 are separated from each other in the radial direction and are not connected to each other.
  • the first dynamic pressure generating grooves 214, 217 and the second dynamic pressure generating grooves 215, 218 are radially separated from each other. That is, the first dynamic pressure generating groove 217 is located between the outer diameter side edge 214 e of the bottom surface 214 a of the first dynamic pressure generating groove 214 and the inner diameter side edge 215 e of the bottom surface 215 a of the second dynamic pressure generating groove 215 .
  • An edge 217e on the inner diameter side of the bottom surface 217a and an edge 218e on the outer diameter side of the bottom surface 218a of the second dynamic pressure generating groove 218 are substantially parallel and spaced apart from each other. ing. Note that the strip-shaped land 212 a is part of the land 212 .
  • the edge 214e on the outer diameter side of the first dynamic pressure generating groove 214 and the edge 217e on the inner diameter side of the first dynamic pressure generating groove 217 are different from those of the embodiment 1. Since the sealed fluid F or the atmosphere A can flow out between the sliding surfaces 211 and 21 along the , positive pressure can be generated in a wider range.
  • the stationary seal ring 310 of the third embodiment includes a second dynamic pressure generating groove 315 forming a dynamic pressure generating mechanism 313 and a second dynamic pressure generating groove 318 forming a dynamic pressure generating mechanism 316. are longer than those of the first dynamic pressure generating grooves 314 and 317 in the radial direction, and the lengths of the circumferential components in the extending direction of the grooves are substantially the same. It has the same configuration as the first embodiment.
  • the second dynamic pressure generating grooves 315 and 318 are radially wider than the first dynamic pressure generating grooves 314 and 317. It is formed such that the depth distribution has a gentle slope.
  • the second dynamic pressure generating grooves 315 and 318 have a longer radial component in the extending direction than the first dynamic pressure generating grooves 314 and 317, respectively, and have a longer circumference in the extending direction of the grooves. Since the directional components are formed to have substantially the same length, more dynamic pressure generating mechanisms 313 and 316 can be arranged in the circumferential direction than in the first embodiment, and the sliding surface 311 is balanced over the circumferential direction. A positive pressure can often be generated.
  • the stationary seal ring 410 of the fourth embodiment constitutes a first dynamic pressure generating groove 414 and a second dynamic pressure generating groove 415 that constitute a dynamic pressure generating mechanism 413, and a dynamic pressure generating mechanism 416.
  • the first dynamic pressure generating groove 417 and the second dynamic pressure generating groove 418 are formed so that the radial component and the circumferential component in the extending direction of the grooves have substantially the same length.
  • the first dynamic pressure generating groove 414 is flattened on the land 12 so that an edge 414d on the inner diameter side of the bottom surface 414a is the shallowest and an edge 414e on the outer diameter side of the bottom surface 414a is the deepest. It is radially inclined with respect to the plane. That is, the first dynamic pressure generating groove 414 is formed so that the depth decreases from the inner diameter side edge 414d of the bottom surface 414a toward the outer diameter side edge 414e.
  • the first dynamic pressure generating groove 414 is formed so that it is shallow on the upstream side of the relative rotation and deep on the downstream side of the relative rotation with respect to the forward relative rotation indicated by the solid arrow in FIG.
  • the second dynamic pressure generating groove 415 is radially inclined so that the inner diameter side edge 415e of the bottom surface 415a is the shallowest and the outer diameter side edge 415f of the bottom surface 415a is the deepest. That is, the second dynamic pressure generating groove 415 is formed so that the depth thereof increases from the inner diameter side edge 415e of the bottom surface 415a toward the outer diameter side edge 415f.
  • the second dynamic pressure generating groove 415 is formed so that it is deep on the upstream side of the relative rotation and shallow on the downstream side of the relative rotation with respect to the forward relative rotation indicated by the solid arrow in FIG.
  • the radial depth distribution of the first dynamic pressure generating grooves 414 and 417 and the second dynamic pressure generating grooves 415 and 418 is similar to that of the first embodiment. It is formed so as to have a reverse inclination.
  • the first dynamic pressure generating groove 414 and the second dynamic pressure generating groove 415 that constitute the dynamic pressure generating mechanism 413 have opposite depth relationships with respect to the relative rotation direction.
  • the dynamic pressure generating mechanism 416 is arranged in a first direction so as to have a so-called mirror image relationship with respect to the dynamic pressure generating mechanism 413 with respect to the center line (not shown) in the radial direction of the sliding surface.
  • a dynamic pressure generating groove 417 and a second dynamic pressure generating groove 418 are formed.
  • the first dynamic pressure generating grooves 414, 417 are separated from the inner space S1 or the outer space S2 by linear edges 414d, 417d. Therefore, the first dynamic pressure generating groove 414 and the second dynamic pressure generating groove 415 constituting the dynamic pressure generating mechanism 413, and the first dynamic pressure generating groove 417 and the second dynamic pressure generating groove 418 constituting the dynamic pressure generating mechanism 416 are formed.
  • the grooves so that the radial component and the circumferential component in the extending direction of the grooves have approximately the same length, it is possible to generate the same degree of positive pressure with respect to the relative rotation in both directions.
  • the stationary seal ring 510 of the fifth embodiment includes a first dynamic pressure generating groove 514 constituting a dynamic pressure generating mechanism 513 and a first dynamic pressure generating groove 517 constituting a dynamic pressure generating mechanism 516. are not in communication with the inner space S1 or the outer space S2, respectively, and the circumferential component in the extending direction of the grooves is longer than the second dynamic pressure generating grooves 515 and 518; A plurality of (three in the fifth embodiment) second dynamic pressure generating grooves 515 and 518 are arranged for the pressure generating grooves 514 and 517, respectively, and the groove width of the first dynamic pressure generating grooves 514 and 517 are formed larger than the second dynamic pressure generating grooves 515 and 518, respectively.
  • the circumferential component in the extension direction of the groove is long and the groove width is large.
  • Examples 1 to 5 examples were described in which the first dynamic pressure generating groove and the second dynamic pressure generating groove, which constitute the dynamic pressure generating mechanism, were provided in the stationary seal ring.
  • the two dynamic pressure generating grooves may be provided on the rotary seal ring, or one or both of the first dynamic pressure generating groove and the second dynamic pressure generating groove may be provided on the stationary seal ring and the rotary seal ring.
  • the sliding component of the present invention may be a stationary seal ring or a rotating seal ring.
  • the sealed fluid side is assumed to be the high pressure side and the leak side is assumed to be the low pressure side, but the sealed fluid side and the leak side may have substantially the same pressure.
  • the inner diameter side is the sealed fluid side and the outer diameter side is the leak side, but the outer diameter side may be the sealed fluid side and the inner diameter side may be the leak side.
  • the sealed fluid F is described as a high-pressure gas, but it is not limited to this, and may be a liquid or a low-pressure gas, or may be a mist mixture of liquid and gas. good too.
  • the fluid on the leak side is explained to be the atmosphere A which is a low-pressure gas, but it is not limited to this and may be a liquid or a high-pressure gas, or a mixture of liquid and gas. It may be in the form of a mist.
  • the first dynamic pressure generating groove and the second dynamic pressure generating groove are linearly extended, but the first dynamic pressure generating groove and the second dynamic pressure generating groove It may extend curvedly. That is, when the groove is viewed in the axial direction, the groove may be narrowed on at least one side in the circumferential direction of the groove.
  • the bottom surfaces of the first dynamic pressure generating groove and the second dynamic pressure generating groove are slanted with respect to the flat surface of the land and extend linearly.
  • the bottom surfaces of the dynamic pressure generating grooves and the second dynamic pressure generating grooves may be curved or stepped deep as long as the bottom surfaces become deeper or shallower in the extending direction of the grooves. may vary.
  • the shallowest edges of the bottom surfaces of the first dynamic pressure generating groove and the second dynamic pressure generating groove are arranged on the same plane as the flat surface of the land.
  • the shallowest edges of the bottom surfaces of the first dynamic pressure generating groove and the second dynamic pressure generating groove may have a predetermined depth as long as they are deep enough to generate a sufficient positive pressure. good.
  • Example 1 to 5 even if the first dynamic pressure generating groove and the second dynamic pressure generating groove are displaced in the circumferential direction like the stationary seal ring 610 of Modification 1 shown in FIG. good. Note that the first dynamic pressure generating groove and the second dynamic pressure generating groove may be partially connected to each other while being displaced in the circumferential direction.
  • Examples 1 to 5 like the stationary seal ring 710 of Modification 2 shown in FIG. may be formed in the opposite direction.
  • the dynamic pressure generating mechanisms are formed on the inner diameter side and the outer diameter side of the sliding surface. 15 may be formed only on the inner diameter side of the sliding surface like the static seal ring 810 of Modification 3 shown in FIG. may be formed only on the outer diameter side of the Also, three or more dynamic pressure generating mechanisms may be formed in the radial direction of the sliding surface.
  • the first dynamic pressure generating groove and the second dynamic pressure generating groove are arranged side by side in the radial direction. and the second hydrodynamic groove may be arranged side by side in the circumferential direction.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Sealing (AREA)
PCT/JP2022/031862 2021-08-26 2022-08-24 摺動部品 Ceased WO2023027102A1 (ja)

Priority Applications (5)

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JP2023543950A JP7842769B2 (ja) 2021-08-26 2022-08-24 摺動部品
US18/685,161 US20240344555A1 (en) 2021-08-26 2022-08-24 Sliding parts
EP22861390.7A EP4394217A4 (en) 2021-08-26 2022-08-24 SLIDING COMPONENT
KR1020247008518A KR20240046244A (ko) 2021-08-26 2022-08-24 슬라이딩 부품
CN202280057538.9A CN117836546A (zh) 2021-08-26 2022-08-24 滑动部件

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JP2021138020 2021-08-26
JP2021-138020 2021-08-26

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EP (1) EP4394217A4 (https=)
JP (1) JP7842769B2 (https=)
KR (1) KR20240046244A (https=)
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EP4394217A4 (en) 2025-08-27
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US20240344555A1 (en) 2024-10-17
JP7842769B2 (ja) 2026-04-08
JPWO2023027102A1 (https=) 2023-03-02
KR20240046244A (ko) 2024-04-08

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