WO2021246372A1 - 摺動部品 - Google Patents
摺動部品 Download PDFInfo
- Publication number
- WO2021246372A1 WO2021246372A1 PCT/JP2021/020703 JP2021020703W WO2021246372A1 WO 2021246372 A1 WO2021246372 A1 WO 2021246372A1 JP 2021020703 W JP2021020703 W JP 2021020703W WO 2021246372 A1 WO2021246372 A1 WO 2021246372A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- groove
- inclined groove
- fluid
- sealed fluid
- sliding
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 294
- 238000007789 sealing Methods 0.000 description 127
- 230000001154 acute effect Effects 0.000 description 63
- 230000003068 static effect Effects 0.000 description 50
- 239000007788 liquid Substances 0.000 description 44
- 238000010008 shearing Methods 0.000 description 10
- 239000000463 material Substances 0.000 description 9
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 7
- 229910052799 carbon Inorganic materials 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 238000011144 upstream manufacturing Methods 0.000 description 6
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 238000009751 slip forming Methods 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 3
- 239000012141 concentrate Substances 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- 239000000203 mixture 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
- 239000007787 solid Substances 0.000 description 2
- ZOXJGFHDIHLPTG-UHFFFAOYSA-N Boron Chemical compound [B] ZOXJGFHDIHLPTG-UHFFFAOYSA-N 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052796 boron Inorganic materials 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 229910002804 graphite Inorganic materials 0.000 description 1
- 239000010439 graphite Substances 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000005245 sintering Methods 0.000 description 1
- 239000007779 soft material Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- 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
- F16C17/028—Sliding-contact bearings for exclusively rotary movement for radial load only with fixed wedges to generate hydrodynamic pressure, e.g. multi-lobe 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
- F16J15/3424—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 microcavities
-
- 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
- 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
- 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
- F16J15/3416—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 with at least one continuous groove
Definitions
- the present invention relates to sliding parts that rotate relative to each other, for example, sliding parts used in a shaft sealing device for shaft-sealing the rotating shaft of a rotating machine in an automobile, a general industrial machine, or other sealing field, or an automobile or a general industrial machine. Or other sliding parts used in the bearings of machines in the bearing field.
- a mechanical seal is provided with a pair of annular sliding parts that rotate relative to each other and slide between sliding surfaces.
- it has been desired to reduce the energy lost due to sliding for environmental measures and the like.
- a pair of annular sliding parts are configured to be relatively rotatable, a sealed fluid exists in the outer space, and a low-pressure fluid exists in the inner space.
- One of the sliding parts is provided with a fluid introduction groove that communicates with the outer space where the sealed fluid exists and the inner diameter end is closed, and at the same time, communicates with the inner space where the low pressure fluid exists and communicates from the inner diameter end.
- An inclined groove is provided that extends in an arc shape while inclining in the circumferential direction toward the outer diameter side, and the outer diameter end is closed downstream in the relative rotation direction.
- the sealed fluid existing in the outer space is introduced into the fluid introduction groove to lubricate the sliding surfaces of the pair of sliding parts.
- a low-pressure fluid existing in the inner space is introduced into the inclined groove, so that positive pressure is generated at the outer diameter end and its vicinity, and the pair of sliding parts slide. Low friction is achieved by slightly separating the surfaces from each other.
- the sealed fluid that flows from the outer space between the sliding surfaces and heads toward the inner diameter side of the sliding surface is sucked by the inclined groove, so that the sealed fluid flows from between the pair of sliding parts into the low-pressure inner space. Can be prevented from leaking to.
- the inclined groove is arranged on the leak side of one of the sliding components, and the outer diameter is from the inner diameter end so that the fluid on the leak side is introduced during normal rotation. Since it is configured to extend to the side, it is possible to reduce wear and suppress leakage, but during reverse rotation, the sealed fluid flows out from the fluid introduction groove between the sliding surfaces, which is excellent in lubricity. There is a problem that the sealed fluid leaks into the inner space from between the pair of sliding parts.
- the present invention has been made by paying attention to such a problem, and wear between sliding surfaces during both forward rotation and reverse rotation (hereinafter, may be referred to as both rotations). It is an object of the present invention to provide a sliding component which can suppress the leakage of the sealed fluid and can suppress the leakage of the sealed fluid.
- the sliding parts of the present invention are Multiple fluid introduction grooves that are placed in the relative rotating part of the rotating machine and slide relative to other sliding parts, communicate with the space on the sealed fluid side on the sliding surface, and introduce the sealed fluid, and from the leak side.
- An annular sliding component comprising a plurality of inclined grooves extending toward the sealed fluid side to generate dynamic pressure.
- the sliding surface of the sliding component is provided with a recess arranged at least between the fluid introduction grooves adjacent in the circumferential direction.
- the recess may be a reverse inclined groove provided on the sealed fluid side of the inclined groove and extending in the opposite direction to the inclined groove to generate dynamic pressure.
- the sealed fluid flowing out from the fluid introduction groove between the sliding surfaces is captured by the reverse inclined groove on the downstream side of the relative rotation of the fluid introduction groove, and is captured in the reverse inclined groove.
- the sealing fluid moves following the sliding surface of other sliding parts due to shearing, and is returned between the sliding surfaces from the end of the reverse inclined groove on the sealed fluid side toward the sealed fluid side, so that the leak side Leakage of the sealed fluid into the space can be further reduced.
- the recess may be provided only between the adjacent fluid introduction grooves. According to this, there is no recess in the position where it overlaps in the radial direction with the inclined groove arranged on the leak side of the fluid introduction groove, and the extending distance of the inclined groove arranged on the leak side of the fluid introduction groove is long. can do. Therefore, at the time of forward rotation, a high positive pressure is likely to be generated by the fluid on the leak side in the inclined groove, and the dynamic pressure effect can be enhanced.
- the fluid introduction groove may have a Rayleigh step.
- the Rayleigh step can generate dynamic pressure to slightly separate the sliding surfaces and introduce the sealed fluid between the sliding surfaces, thereby improving the lubricity between the sliding surfaces. Can be done.
- the fluid introduction groove may have Rayleigh steps extending on both sides in the circumferential direction. According to this, at both rotations, the Rayleigh step can generate dynamic pressure to slightly separate the sliding surfaces and introduce the sealed fluid between the sliding surfaces, so that the sliding surfaces can be introduced to each other. Lubricity can be improved.
- the reverse inclined groove may have a shorter extension distance than the inclined groove. According to this, it is possible to generate a positive pressure at an early stage in the reverse inclined groove at the time of reverse rotation.
- the inclined groove and the reverse inclined groove may be continuous grooves. According to this, during reverse rotation, the sealed fluid that tends to move toward the leak side through the inclined groove can be returned to the sealed fluid side by the reverse inclined groove, so that the space on the leak side is covered. Leakage of the sealing fluid can be reduced.
- An annular land portion that is continuous in the circumferential direction and has a width equal to or larger than a predetermined value in the radial direction may be provided between the inclined groove and the reverse inclined groove on the sealed fluid side of the inclined groove. According to this, since the sealed fluid is captured in the reverse inclined groove on the sealed fluid side of the annular land portion at the time of reverse rotation, it is possible to prevent the sealed fluid from entering the inclined groove. In addition, since the inclined groove and the reverse inclined groove are separated by the annular land portion, the inclined groove and the reverse inclined groove do not interfere with each other's dynamic pressure generation at the time of both rotations, so that the dynamic pressure effect is exhibited. It's easy to do.
- the inclined groove may have both a radial component and a circumferential component in the extending direction of the inclined groove.
- the reverse inclined groove has both a radial component and a circumferential component in the extending direction of the reverse inclined groove, and the circumferential direction extending from the upstream to the downstream at the time of relative rotation is the inclined groove. The opposite is true.
- the sealed fluid may be a gas or a liquid, or may be a mist in which a liquid and a gas are mixed.
- FIG. 1 It is a vertical sectional view which shows an example of the mechanical seal in Example 1 of this invention. It is a figure which looked at the sliding surface of the static sealing ring in Example 1 from the axial direction. It is an enlarged view which looked at the sliding surface of the static sealing ring in Example 1 from the axial direction. It is explanatory drawing which looked at the movement of the fluid of the inclined groove and the reverse inclined groove at the time of the forward rotation about the sliding surface of the static sealing ring in Example 1 from the axial direction. It is explanatory drawing which looked at the movement of the fluid of the inclined groove and the reverse inclined groove at the time of the reverse forward rotation about the sliding surface of the static sealing ring in Example 1 from the axial direction.
- the sliding parts according to the first embodiment will be described with reference to FIGS. 1 to 6.
- a mode in which the sliding component is a mechanical seal will be described as an example.
- the sealed fluid exists in the outer space of the mechanical seal, and the atmosphere exists in the inner space.
- the outer diameter side of the sliding parts constituting the mechanical seal is the sealed fluid side (high pressure side), and the inner diameter side is This will be described as the leak side (low pressure side).
- dots may be added to the grooves and the like formed on the sliding surface in the drawings.
- the mechanical seal for an automobile shown in FIG. 1 is an inside type that seals a sealed fluid F that tends to leak from the outer diameter side to the inner diameter side of the sliding surface and allows the inner space S1 to pass through the atmosphere A. ..
- a mode in which the sealed fluid F is a high-pressure liquid and the atmosphere A is a gas having a lower pressure than the sealed fluid F is illustrated.
- the mechanical seal is fixed to the rotary seal ring 20 as another sliding component of the annular shape provided on the rotary shaft 1 so as to be rotatable together with the rotary shaft 1 via the sleeve 2, and to the housing 4 of the attached device.
- the seal cover 5 is mainly composed of an annular static sealing ring 10 as a sliding component provided on the seal cover 5 in a non-rotating state and in a state of being movable in the axial direction.
- the sliding surface 11 of the static sealing ring 10 and the sliding surface 21 of the rotary sealing ring 20 slide closely with each other by being urged to.
- the sliding surface 21 of the rotary sealing ring 20 is a flat surface, and the flat surface is not provided with a recess such as a groove.
- the static sealing ring 10 and the rotary sealing ring 20 are typically formed of SiC (hard material) or a combination of SiC (hard material) and carbon (soft material), but the sliding material is not limited to this. It can be applied as long as it is used as a sliding material for mechanical seals.
- the SiC includes a sintered body containing boron, aluminum, carbon and the like as a sintering aid, and materials composed of two or more types of phases having different components and compositions, for example, SiC and SiC in which graphite particles are dispersed.
- resin molded carbon, sintered carbon and the like can be used, including carbon in which carbonaceous and graphitic are mixed.
- metal materials, resin materials, surface modification materials (coating materials), composite materials and the like can also be applied.
- the rotary sealing ring 20 slides relative to the static sealing ring 10 in a counterclockwise direction as indicated by a solid arrow or clockwise as indicated by a dotted arrow.
- a plurality of dynamic pressure generating grooves 13 and inclined grooves 13' are evenly arranged in the circumferential direction on the inner diameter side, and a plurality of fluid introduction grooves 16 on the outer diameter side. are evenly arranged in the circumferential direction.
- the counterclockwise rotation direction of the rotary sealing ring 20 indicated by the solid arrow will be described as a forward rotation direction
- the clockwise rotation direction of the rotary sealing ring 20 indicated by the dotted arrow will be described as a reverse rotation direction. ..
- the portion of the sliding surface 11 other than the dynamic pressure generating groove 13, the inclined groove 13'and the fluid introduction groove 16 is a land 12 forming a flat surface.
- the dynamic pressure generating groove 13 extends from the inner diameter side to the outer diameter side, and the outer diameter end 13B extends to the land portion 12b between the fluid introduction grooves 16 adjacent in the circumferential direction. It is composed of an inclined groove 14 for generating dynamic pressure and a reverse inclined groove 15 as a recess which is continuously formed on the outer diameter side of the inclined groove 14 and extends in the opposite direction to the inclined groove 14 to generate dynamic pressure. It has an L-shape.
- the reverse inclined groove 15 as a recess is arranged between the fluid introduction grooves 16 adjacent to each other in the circumferential direction.
- the reverse inclined groove 15 is on the inner diameter side with respect to the inclined groove 14 extending while having a component in the forward rotation direction from the inner diameter side to the outer diameter side. It means that it extends from to the outer diameter side while tilting with a component in the reverse rotation direction.
- the inner diameter end 13A that is, the inner diameter end of the inclined groove 14 communicates with the inner space S1 and is inclined in the forward rotation direction of the rotary sealing ring 20 from the inner diameter end 13A toward the outer diameter side.
- a reverse inclined groove 15 extending in the direction opposite to the inclined groove 14 is continuously formed at the end portion of the inclined groove 14 on the outer diameter side.
- the reverse inclined groove 15 extends linearly from the end on the inner diameter side toward the outer diameter side while being inclined in the reverse rotation direction of the rotary sealing ring 20, and the end on the outer diameter side, that is, the dynamic pressure generating groove 13.
- the outer diameter end 13B of the above is closed so as not to communicate with the outer space S2.
- the reverse inclined groove 15 is not limited to the one extending linearly while being inclined, and may be one extending in an arc shape.
- the inclined groove 14 has a bottom surface 14a that is flat and parallel to the flat surface of the land 12 in the extending direction, and a side wall that extends vertically from both side edges of the bottom surface 14a toward the sliding surface 11. It is composed of parts 14c and 14d.
- the reverse inclined groove 15 has a bottom surface 15a that is flat and parallel to the flat surface of the land 12 in the extending direction, and a wall portion that extends vertically from the edge of the bottom surface 15a on the outer diameter end 13B side toward the sliding surface 11. It is composed of 15b and side wall portions 15c and 15d extending vertically from both side edges of the bottom surface 15a toward the sliding surface 11.
- the dynamic pressure generating groove 13 has an acute angle portion 13C formed by the side wall portion 14d of the inclined groove 14 and the side wall portion 15d of the reverse inclined groove 15, and an acute angle formed by the wall portion 15b and the side wall portion 15c of the reverse inclined groove 15.
- the portion 13D and the obtuse angle portion 13E formed by the wall portion 15b and the side wall portion 15d of the reverse inclined groove 15 are formed, and the acute angle portion 13D is on the outer diameter side of the acute angle portion 13C and is the reverse of the rotary sealing ring 20. It is located on the downstream side in the direction of rotation. Further, the acute angle portion 13D has a smaller angle than the acute angle portion 13C.
- the acute-angled portion 13C is formed at a radial position substantially the same as the peripheral wall portion 17a on the inner diameter side of the liquid guide groove portion 17 of the fluid introduction groove 16 described later, and the acute-angled portion 13D is a Rayleigh step of the fluid introduction groove 16 described later. It is formed at substantially the same radial position as the peripheral wall portion 18a on the outer diameter side of 18.
- the extending distance of the inverted inclined groove 15 is shorter than the extending distance of the inclined groove 14. That is, the lengths of the side wall portions 15c and 15d of the reverse inclined groove 15 are shorter than the lengths of the side wall portions 14c and 14d of the continuous inclined groove 14, respectively.
- the depth of the inverted inclined groove 15 is the same as the depth of the inclined groove 14. That is, the bottom surface 15a of the reverse inclined groove 15 is arranged in the same plane as the bottom surface 14a of the continuous inclined groove 14 to form a flat surface.
- the bottom surface 14a of the inclined groove 14 and the bottom surface 15a of the reverse inclined groove 15 are not limited to those forming a flat surface, and may have an inclination or unevenness.
- the outer diameter end 13B' is arranged on the inner diameter side of the fluid introduction groove 16 and extends from the inner diameter side toward the outer diameter side to generate dynamic pressure.
- the inner diameter end 13A' communicates with the inner space S1 and extends in an arc shape from the inner diameter end 13A' toward the outer diameter side while inclining in the forward rotation direction of the rotary sealing ring 20.
- the outer diameter end 13B' is closed so as not to communicate with the fluid introduction groove 16.
- the inclined groove 13' slides from the bottom surface 13a' which is flat in the extending direction and parallel to the flat surface of the land 12 and the edge of the bottom surface 13a' on the outer diameter end 13B' side. It is composed of a wall portion 13b'that extends vertically toward the moving surface 11 and side wall portions 13c'and 13d' that extend vertically from both side edges of the bottom surface 13a' toward the sliding surface 11.
- the inclined groove 13' is formed with an acute-angled portion 13C'formed by the wall portion 13b'and the side wall portion 13d', and an obtuse-angled portion 13D' formed by the wall portion 13b'and the side wall portion 13c'. ..
- the fluid introduction groove 16 includes a liquid guide groove portion 17 communicating with the outer space S2 and a static seal ring 10 from the inner diameter side of the liquid guide groove portion 17 toward the forward rotation direction of the rotary seal ring 20. It is composed of a Rayleigh step 18 that extends concentrically in the circumferential direction.
- the liquid guide groove portion 17 and the Rayleigh step 18 are formed to have substantially the same depth as the depth dimension of the dynamic pressure generation groove 13. Further, the Rayleigh step 18 is formed so that the length in the circumferential direction is longer than the length in the circumferential direction of the liquid guide groove portion 17 or the length in the circumferential direction of one dynamic pressure generating groove 13.
- the sealed fluid F in the Rayleigh step 18 is the sliding surface 21.
- the sealed fluid F in the outer space S2 is drawn into the liquid guide groove portion 17 by following the rotation sealing ring 20 in the forward rotation direction by shearing with. That is, in the fluid introduction groove 16, the sealed fluid F moves from the liquid guide groove portion 17 toward the downstream end portion 18A in the relative rotation direction in the Rayleigh step 18 as shown by the arrow H1.
- the flow of the sealed fluid F and the atmosphere A in FIG. 4 is shown schematically without specifying the relative rotation speed of the rotary sealing ring 20.
- the pressure of the sealed fluid F that has moved toward the end 18A of the Rayleigh step 18 is increased at or near the end 18A of the Rayleigh step 18. That is, positive pressure is generated at the end 18A of the Rayleigh step 18 and its vicinity.
- the sliding surfaces 11 and 21 are slightly separated from each other.
- the sealed fluid F in the fluid introduction groove 16 indicated by the arrow H2 mainly flows between the sliding surfaces 11 and 21.
- the lubricity is improved even during low-speed rotation, and wear between the sliding surfaces 11 and 21 can be suppressed.
- the floating distance between the sliding surfaces 11 and 21 is small, the amount of the sealed fluid F that the sealed fluid F leaks into the inner space S1 is small.
- the liquid guide groove portion 17 is provided, a large amount of the sealed fluid F can be held, and it is possible to avoid poor lubrication between the sliding surfaces 11 and 21 during low-speed rotation.
- the atmosphere A is sufficiently dense in the dynamic pressure generating groove 13 and the inclined groove 13'at the time of relative rotation low speed between the rotary sealing ring 20 and the static sealing ring 10.
- No high positive pressure is generated, and the force due to the positive pressure generated by the dynamic pressure generation groove 13 and the inclined groove 13'is relative to the force due to the positive pressure generated at the end 18A of the Rayleigh step 18 and its vicinity.
- Small. Therefore, when the rotary sealing ring 20 is rotated at a low speed, the sliding surfaces 11 and 21 are separated from each other mainly by the force due to the positive pressure generated at the end 18A of the Rayleigh step 18 and its vicinity.
- the pressure of the atmosphere A that has moved toward the end on the outer diameter side of the inclined groove 14 is increased in the acute angle portion 13C and its vicinity. That is, positive pressure is generated at the acute angle portion 13C and its vicinity. Further, the pressure of the atmosphere A that has moved toward the outer diameter end 13B'of the inclined groove 13'is increased in the acute angle portion 13C'and its vicinity. That is, positive pressure is generated at the acute angle portion 13C'and its vicinity.
- the atmosphere A in the dynamic pressure generating groove 13 and the inclined groove 13'indicated by the arrows L2 and L2' excludes the sealed fluid F in the vicinity of the acute angle portion 13C of the dynamic pressure generating groove 13 and the acute angle portion 13C' of the inclined groove 13'. Since it acts to push back to the space S2 side, the amount of the sealed fluid F leaking into the dynamic pressure generating groove 13 and the acute-angled groove 13'or the inner space S1 is small.
- the atmosphere A in the inclined groove 13'indicated by the arrow L2' introduces the fluid as shown by the arrow H3 by pushing the sealed fluid F near the acute angle portion 13C' of the inclined groove 13' to the outer space S2 side. Since it enters the Rayleigh step 18 of the groove 16, it is possible to prevent the sealed fluid F from leaking into the inner space S1.
- the positive pressure generation capacity of the entire inclined grooves 14 and 13' is the positive pressure generation capacity of the entire reverse inclined grooves 15 and the positive pressure generation capacity of the entire Rayleigh step 18 during high-speed rotation of the forward rotation. Since it is designed to be sufficiently larger than the capacity, the final state is that only the atmosphere A exists between the sliding surfaces 11 and 21, that is, gas lubrication.
- the sealed fluid F existing in the land portion 12b between the adjacent fluid introduction grooves 16 and the land portion 12c between the dynamic pressure generating groove 13 and the fluid introduction groove 16 separated in the radial direction is a Rayleigh step.
- the negative pressure generated in and near the end 18A of 18 is sucked into the fluid introduction groove 16 as shown by the arrow H2', and the tendency is remarkably shown in the vicinity of the end 18A.
- the sealed fluid F that has entered the reverse inclined groove 15 formed on the outer diameter side of the dynamic pressure generating groove 13 is with the sliding surface 21. Due to shearing, the rotary sealing ring 20 follows the reverse rotation direction. That is, in the dynamic pressure generation groove 13, the sealed fluid F moves in the reverse inclined groove 15 toward the acute angle portion 13D as shown by the arrow H3'.
- the pressure of the sealed fluid F that has moved toward the acute angle portion 13D is increased in the acute angle portion 13D and its vicinity. That is, positive pressure is generated at the acute angle portion 13D and its vicinity.
- the sliding surfaces 11 and 21 are slightly separated by the force due to the positive pressure generated in the acute angle portion 13D and its vicinity.
- the sealed fluid F in the fluid introduction groove 16 indicated by the arrow H4' flows mainly between the sliding surfaces 11 and 21.
- the amount of the sealed fluid F that leaks into the inside or the inner space S1 is small.
- the sealed fluid F existing around the acute angle portion 13C is sucked into the reverse inclined groove 15 as shown by the arrow H5'due to the negative pressure generated in the acute angle portion 13C and its vicinity.
- the sealed fluid F sucked into the reverse inclined groove 15 is returned from the acute angle portion 13D between the sliding surfaces 11 and 21.
- the sealed fluid F introduced into the fluid introduction groove 16 and flowing out from the vicinity of the liquid guide groove 17 between the sliding surfaces 11 and 21 is located on the downstream side in the relative rotation direction of the liquid guide groove 17 of the fluid introduction groove 16. It is captured by being sucked into the reversely inclined groove 15 of the dynamic pressure generating groove 13. At this time, since a negative pressure is generated in the acute angle portion 13C and its vicinity, the sealed fluid F flowing out between the sliding surfaces 11 and 21 is likely to be sucked into the reversely inclined groove 15 of the dynamic pressure generating groove 13. It has become.
- the sealed fluid returned between the sliding surfaces 11 and 21 from the acute angle portion 13D of the dynamic pressure generating groove 13 located on the upstream side of the Rayleigh step 18 of the fluid introduction groove 16 toward the outer diameter side.
- F is sucked into the fluid introduction groove 16 by the negative pressure generated at the end 18A of the Rayleigh step 18 and its vicinity thereof as shown by the arrow H2'.
- the sealed fluid F becomes the fluid introduction groove 16 by arranging the reversely inclined grooves 15 of the plurality of dynamic pressure generating grooves 13 between the fluid introduction grooves 16 adjacent to each other in the circumferential direction. Since it is passed between the fluid and the plurality of reversely inclined grooves 15 and fastened to the outer diameter side, the amount of the sealed fluid F leaking into the dynamic pressure generating groove 13 or the inner space S1 is small.
- the inner diameter end 13A of the inclined groove 14 is open to the inner space S1, the negative pressure generated in the inclined groove 14 at the time of reverse rotation of the rotary sealing ring 20 is small. Further, since the inclined groove 14 and the reverse inclined groove 15 are continuous grooves, the sealed fluid F that has entered the dynamic pressure generating groove 13 during the reverse rotation of the rotary sealing ring 20 is covered in the reverse inclined groove 15. Since the fluid is returned between the sliding surfaces 11 and 21 from the acute angle portion 13D toward the outer diameter side by the flow of the sealing fluid F, the sealed fluid F leaking to the inner space S1 through the inclined groove 14 can be reduced. ..
- the sliding surfaces 11 and 21 are lubricated by the sealed fluid F flowing out from the fluid introduction groove 16 between the sliding surfaces 11 and 21.
- the sliding surfaces 11 and 21 are separated from each other by the positive pressure generated by the atmosphere A in the dynamic pressure generation groove 13 and the inclined groove 13', and from the start of relative rotation to high-speed rotation. It is possible to suppress wear between the sliding surfaces 11 and 21.
- the sealed fluid F that has entered the reverse inclined groove 15 on the outer diameter side of the inclined groove 14 in the dynamic pressure generating groove 13 is with the sliding surface 21 of the rotary sealing ring 20.
- the dynamic pressure generating groove 13 includes the inclined groove 14 and the reverse inclined groove 15 having different rotation directions for the main dynamic pressure generation, the sliding surfaces 11 and 21 are connected to each other during both rotations. It is possible to suppress wear by separating them, and it is possible to suppress leakage of the sealed fluid F from between the sliding surfaces 11 and 21 to the inner space S1.
- the sealed fluid F introduced into the fluid introduction groove 16 and flowing out from the vicinity of the liquid guide groove 17 between the sliding surfaces 11 and 21 is in the relative rotation direction of the liquid guide groove 17 of the fluid introduction groove 16. It is captured by being sucked into the reverse inclined groove 15 of the dynamic pressure generating groove 13 by the negative pressure generated in the sharp corner portion 13C of the dynamic pressure generating groove 13 located on the downstream side and its vicinity, and is captured in the reverse inclined groove 15.
- the sealed fluid F moves following the sliding surface 21 of the rotary sealing ring 20 and is returned from the sharp angle portion 13D of the reverse inclined groove 15 to the outer diameter side between the sliding surfaces 11 and 21. Leakage of the sealed fluid F into the space S1 can be further reduced.
- the dynamic pressure generating groove 13 is L-shaped by the inclined groove 14 and the reverse inclined groove 15, the acute angle portion 13D is formed together with the atmosphere A sucked into the inclined groove 14 from the inner diameter end 13A at the time of forward rotation.
- the sealed fluid F sucked into the reverse inclined groove 15 can be collected at the acute angle portion 13C to generate a positive pressure.
- the sealed fluid F can be pushed back to the outer space S2 side by the dynamic pressure generated in the reverse inclined groove 15 at the time of reverse rotation, it is possible to suppress the intrusion of the sealed fluid F into the inclined groove 14. It is possible to suppress the leakage of the sealed fluid F into the inner space S1 through the inclined groove 14.
- the inverted inclined groove 15 has a shorter extending distance than the inclined groove 14. According to this, it is possible to generate a positive pressure at an early stage in the reverse inclined groove 15 at the time of reverse rotation.
- the reverse inclined groove 15 is a groove having an acute angle portion 13D whose end portion on the outer diameter side is tapered. According to this, at the time of reverse rotation, the sealed fluid F in the reverse inclined groove 15 is easily concentrated on the acute angle portion 13D to easily generate a positive pressure, so that the dynamic pressure effect can be enhanced.
- the reverse inclined groove 15 is provided only in the dynamic pressure generating groove 13 formed between the adjacent fluid introduction grooves 16. According to this, the reverse inclined groove 15 does not exist at the position overlapping in the radial direction with the inclined groove 13'arranged on the inner diameter side of the fluid introduction groove 16, and the inclination is arranged on the inner diameter side of the fluid introduction groove 16.
- the extending distance of the groove 13' can be lengthened. Therefore, at the time of forward rotation, it becomes easy to generate a higher positive pressure by the atmosphere A in the inclined groove 13', and the dynamic pressure effect can be enhanced.
- the inclined grooves 14, 13' communicate with the inner space S1. According to this, at the time of forward rotation, the atmosphere A of the inner space S1 is easily introduced into the inclined grooves 14, 13'from the inner diameter ends 13A, 13A', and the positive pressure is applied by the atmosphere A in the inclined grooves 14, 13'. Since it is easy to generate, the dynamic pressure effect can be enhanced.
- the fluid introduction groove 16 is provided with a Rayleigh step 18. According to this, at the time of forward rotation, the hydraulic pressure is generated by the Rayleigh step 18 to slightly separate the sliding surfaces 11 and 21 to introduce the sealed fluid F between the sliding surfaces 11 and 21. Therefore, the lubricity between the sliding surfaces 11 and 21 can be improved. Further, in the fluid introduction groove 16, since the liquid guide groove portion 17 communicates with the outer space S2, it is easy to introduce the sealed fluid F into the liquid guide groove portion 17, and a positive pressure can be generated at an early stage by the Rayleigh step 18. can.
- the Rayleigh step 18 can suck the sealed fluid F around the end portion 18A by a negative pressure and introduce it into the liquid guide groove portion 17 at the time of reverse rotation, the sealed fluid F can be introduced into the inner space S1. Leakage can be suppressed.
- a plurality of fluid introduction grooves 116 are uniformly formed in the circumferential direction on the inner diameter side of the sliding surface 111 as in the static sealing ring 110 as a sliding component shown in FIG.
- a plurality of dynamic pressure generating grooves 113 and inclined grooves 113' are evenly arranged in the circumferential direction on the outer diameter side so that the sliding surface 111 leaks from the inner diameter side toward the outer diameter side. It may be applicable to an outside type mechanical seal that seals the sealed fluid F.
- the dynamic pressure generation groove 113, the inclined groove 113'and the fluid introduction groove 116 are formed by reversing the dynamic pressure generation groove 13, the inclined groove 13'and the fluid introduction groove 16 in the first embodiment.
- the arrangement configuration of the dynamic pressure generation groove and the fluid introduction groove in this modification can be applied to the sliding surface of the sliding parts of each subsequent embodiment. That is, it can be applied to the outside type mechanical seal by exchanging the radial arrangement of the dynamic pressure generation groove and the fluid introduction groove in each of the following examples.
- the dynamic pressure generating groove 213 in which the outer diameter end 213B is arranged between the fluid introduction grooves 16 adjacent in the circumferential direction is It has the same configuration as the dynamic pressure generation groove 13 of the first embodiment.
- the dynamic pressure generating groove 213'in which the outer diameter end 213B'is arranged on the inner diameter side of the fluid introduction groove 16 extends from the inner diameter side toward the outer diameter side to generate the dynamic pressure, and the inclined groove 214'. It is composed of a reverse inclined groove 215'which is continuously formed on the outer diameter side of the groove 214' and extends in the opposite direction to the inclined groove 214' to generate dynamic pressure, and has an L shape.
- the extending distance of the inverted inclined groove 215' is shorter than the extending distance of the inclined groove 214'. Further, the extending distances of the inclined groove 214'and the reverse inclined groove 215' are shorter than the extending distances of the inclined groove 214 and the inverted inclined groove 215 constituting the dynamic pressure generating groove 213, respectively.
- the fluid is sucked into the dynamic pressure generating groove 213'around the inclined groove 214'and the reverse inclined groove 215'on the inner diameter side of the fluid introduction groove 16 as well as the dynamic pressure generating groove 213.
- the sealed fluid F is returned from the acute angle portion 213C'toward the outer diameter side between the sliding surfaces 211 and 21, and is pushed back to the outer space S2 side.
- the inclined groove 313'in which the outer diameter end 313B'is arranged on the inner diameter side of the fluid introduction groove 16 is the first embodiment. It has the same configuration as the inclined groove 13'of. Further, the dynamic pressure generating groove 313 extends from the inner diameter side toward the outer diameter side to generate the dynamic pressure, and the inclined groove 314 is separated in the radial direction on the outer diameter side of the inclined groove 314 with respect to the inclined groove 314. It is composed of a reverse inclined groove 315 as a recess extending in the opposite direction and generating dynamic pressure.
- the dynamic pressure generation groove 313 has a configuration in which the inclined groove 314 and the reverse inclined groove 315 are separated in the radial direction by the annular land portion 312d described later.
- the reverse inclined groove 315 is arranged in the land portion 312b between the fluid introduction grooves 16 adjacent to each other in the circumferential direction.
- the inclined groove 314 has an inner diameter end 314A communicating with the inner space S1 and extends in an arc shape from the inner diameter end 314A toward the outer diameter side while being inclined in the forward rotation direction of the rotary sealing ring 20.
- the linear outer diameter end 314B of the 314 is closed so as not to communicate with the reverse inclined groove 315.
- the reverse inclined groove 315 has a substantially parallelogram shape, and extends linearly from the inner diameter end 315A toward the outer diameter side while being inclined in the reverse rotation direction of the rotary sealing ring 20, and the outer diameter end 315B is formed. It is closed so as not to communicate with the outer space S2.
- annular land portion 312d that is continuous in the circumferential direction and has a width equal to or larger than a predetermined value in the radial direction is formed.
- the annular land portion 312d is also arranged in the same plane as the other land portions to form a flat surface of the land 312.
- the inclined groove 314 is formed with an acute-angled portion 314C formed by the wall portion 314b and the side wall portion 314d at the outer diameter end 314B, and an obtuse-angled portion 314D formed by the wall portion 314b and the side wall portion 314c.
- the reverse inclined groove 315 has an acute angle portion 315C formed by the wall portion 315b and the side wall portion 315d at the inner diameter end 315A, and an acute angle portion 315D formed by the wall portion 315e and the side wall portion 315c at the linear outer diameter end 315B. , Is formed, and the acute-angled portion 315D is located on the outer diameter side of the acute-angled portion 315C and on the downstream side in the reverse rotation direction of the rotary sealing ring 20.
- the extending distance of the inverted inclined groove 315 is shorter than the extending distance of the inclined groove 314.
- the depth of the reverse inclined groove 315 is the same as the depth of the inclined groove 314.
- the reverse inclined groove 315 may be formed at a depth different from that of the inclined groove 314.
- the outer diameter end 314B and the inner diameter end 315A are arranged at positions that are substantially parallel and have substantially the same length and overlap in the radial direction. From the viewpoint of preventing leakage, it is preferable that the inner diameter end 315A has a length equal to or larger than the outer diameter end 314B and is arranged at a position where the inner diameter end 315A overlaps in the radial direction.
- the pressure of the atmosphere A that has moved toward the outer diameter end 314B of the inclined groove 314 is increased in the acute angle portion 314C and its vicinity. That is, positive pressure is generated at the acute angle portion 314C and its vicinity.
- the atmosphere A in the inclined groove 314 indicated by the arrow L2 acts to push the sealed fluid F in the vicinity of the acute angle portion 314C back to the outer space S2 side, so that the sealed fluid leaks into the inclined groove 314 or the inner space S1.
- the fluid F is small.
- the sealed fluid F that has entered the reverse inclined groove 315 follows the rotation sealing ring 20 in the forward rotation direction due to shearing with the sliding surface 21, and is covered in the vicinity of the acute angle portion 315D.
- the sealing fluid F is drawn into the reverse tilt groove 315. That is, in the reverse inclined groove 315, the sealed fluid F moves from the acute angle portion 315D of the reverse inclined groove 315 toward the acute angle portion 315C as shown by the arrow H5, and the pressure is increased in the acute angle portion 315C and its vicinity. That is, positive pressure is generated at the acute angle portion 315C and its vicinity.
- the sealed fluid F in the reverse inclined groove 315 shown by the arrow H6 is pushed back to the outer space S2 side by the atmosphere A in the inclined groove 314 shown by the arrow L2 together with the sealed fluid F in the vicinity of the acute angle portion 315C.
- the sealed fluid F that has entered the reverse inclined groove 315 formed on the outer diameter side of the inclined groove 314 follows the reverse rotation direction of the rotary sealing ring 20 by shearing with the sliding surface 21.
- the sealed fluid F in the vicinity of the acute angle portion 315C is drawn into the reverse inclined groove 315. That is, in the reverse inclined groove 315, the sealed fluid F moves from the acute angle portion 315C of the reverse inclined groove 315 toward the acute angle portion 315D as shown by the arrow H3', and the pressure is increased in the acute angle portion 315D and its vicinity. .. That is, positive pressure is generated at the acute angle portion 315D and its vicinity.
- the amount of the sealed fluid F leaking into the space S1 is small.
- the sealed fluid F existing around the acute angle portion 315C is sucked into the reverse inclined groove 315 as shown by the arrow H5'due to the negative pressure generated in the acute angle portion 315C and its vicinity.
- the sealed fluid F sucked into the reverse inclined groove 315 is returned from the acute angle portion 315D between the sliding surfaces 31 and 21 toward the outer diameter side.
- the sealed fluid F introduced into the fluid introduction groove 16 and flowing out from the vicinity of the liquid guide groove 17 between the sliding surfaces 31 and 21 is located on the downstream side in the relative rotation direction of the liquid guide groove 17 of the fluid introduction groove 16. It is captured by being sucked into the reversely inclined groove 315 of the dynamic pressure generating groove 313. At this time, since a negative pressure is generated in the acute-angled portion 315C and its vicinity, the sealed fluid F flowing out between the sliding surfaces 311, 21 is likely to be sucked into the reversely inclined groove 315 of the dynamic pressure generating groove 313. It has become.
- the sealed fluid F is sucked into the fluid introduction groove 16 by the negative pressure generated at the end 18A of the Rayleigh step 18 and its vicinity as shown by the arrow H2'.
- the fluid introduction grooves 16 are adjacent to each other in the circumferential direction, and the reverse inclination grooves 315 of the plurality of dynamic pressure generation grooves 313 are arranged so that the sealed fluid F becomes the fluid introduction groove 16. Since it is passed between the fluid and the plurality of reversely inclined grooves 315 and fastened to the outer diameter side, the amount of the sealed fluid F leaking into the dynamic pressure generating groove 313 or the inner space S1 is small.
- the positive pressure generated in the inclined groove 314 and the reverse inclined groove 315 of the dynamic pressure generating groove 313 causes the space between the outer space S2 and the sliding surfaces 311, 21. Since the inflowed sealed fluid F is sucked in and pushed back to the outer space S2 side, it is suppressed that the sealed fluid F leaks from between the sliding surfaces 31 and 21 to the inner space S1.
- the sealed fluid F that has entered the reverse inclined groove 315 on the outer diameter side of the inclined groove 314 moves following the sliding surface 21 of the rotary sealing ring 20.
- the leakage of the sealed fluid F to the inner space S1 is reduced by returning the reverse inclined groove 315 between the sliding surfaces 31 and 21 toward the outer diameter side from the end portion on the sealed fluid F side, that is, the acute angle portion 315D. be able to.
- the dynamic pressure generation groove 313 includes the inclined groove 314 and the reverse inclined groove 315 whose main rotation directions for generating the dynamic pressure are different, the sliding surfaces 311, 21 are brought together during both rotations. It is possible to suppress wear by separating them, and it is possible to suppress leakage of the sealed fluid F from between the sliding surfaces 31 and 21 to the inner space S1.
- the sealed fluid F introduced into the fluid introduction groove 16 and flowing out from the vicinity of the liquid guide groove 17 between the sliding surfaces 31 and 21 is in the relative rotation direction of the liquid guide groove 17 of the fluid introduction groove 16. It is captured by being sucked into the reversely inclined groove 315 of the dynamic pressure generating groove 313 located on the downstream side.
- the sealed fluid F flowing out between the sliding surfaces 311, 21 is likely to be sucked into the reversely inclined groove 315 of the dynamic pressure generating groove 313. It has become.
- the sealed fluid F captured in the reverse inclined groove 315 moves following the sliding surface 21 of the rotary sealing ring 20 due to shearing, and the sliding surface from the acute angle portion 315D of the reverse inclined groove 315 toward the outer diameter side. By being returned between 31 and 21, the leakage of the sealed fluid F into the inner space S1 can be further reduced.
- annular land portion 312d that is continuous in the circumferential direction and has a width equal to or larger than a predetermined radial direction is formed, and the annular land portion 312d reverses the inclined groove 314. Since the inclined groove 315 is separated, the sealed fluid F is sucked into the inverted inclined groove 315 from the acute angle portion 315C on the outer diameter side of the annular land portion 312d during the reverse rotation of the rotary sealing ring 20. Therefore, the sealed fluid F is suppressed from entering the inclined groove 314 beyond the annular land portion 312d, and the sealed fluid F leaking to the inner space S1 through the inclined groove 314 can be further reduced. ..
- the inclined groove 314 and the reverse inclined groove 315 are separated by the annular land portion 312d, the inclined groove 314 and the reverse inclined groove 315 do not interfere with each other's dynamic pressure generation at the time of both rotations. It is easy to exert a dynamic pressure effect.
- the radial center of the annular land portion 312d that separates the inclined groove 314 and the reverse inclined groove 315 is arranged closer to the sealed fluid F side than the radial center of the sliding surface 311. According to this, the extending distance of the inclined groove 314 can be secured for a long time, and the inclined groove 314 becomes the main source of dynamic pressure more than the reverse inclined groove 315 at the time of forward rotation. Leakage can be further suppressed.
- the inclined groove 313' is not limited to the same configuration as the inclined groove 13'of the first embodiment, and may have the same configuration as the dynamic pressure generating groove 213'of the second embodiment, for example, and the dynamic pressure is generated. Similar to the groove 313, the inclined groove and the reverse inclined groove may be separated in the radial direction. Further, such a change in the configuration of the dynamic pressure generating groove can be applied to the sliding surface of the sliding component of each subsequent embodiment.
- the dynamic pressure generating groove 413 extends from the inner diameter side toward the outer diameter side and generates a dynamic pressure with the inclined groove 414. It is composed of a recess 415 that is radially separated on the outer diameter side of the inclined groove 414.
- the recess 415 has a substantially square shape, and is arranged substantially in the center of the outer diameter end 414B of the inclined groove 414 in the land portion 412b between the fluid introduction grooves 16 adjacent in the circumferential direction.
- the concave portion 415 has corners facing each other in the radial direction, that is, diagonal lines are arranged on the radial line of the static sealing ring 410.
- the sealed fluid F flowing out from the fluid introduction groove 16 between the sliding surfaces 411 and 21 is captured by the recess 415 on the relative rotation downstream side of the fluid introduction groove 16 so as to be inside. Leakage of the sealed fluid F into the space S1 can be reduced.
- the recess 415 is not limited to a substantially square shape, for example, unless it has a directionality in the circumferential direction extending from the upstream to the downstream during relative rotation, as in the case of the reverse inclined groove 315 of the third embodiment.
- the shape and the like may be freely configured such as a circle and a triangle.
- the fluid introduction groove 516 in the static sealing ring 510 of the fifth embodiment has a liquid guide groove portion 517 communicating with the outer space S2 and a positive rotation sealing ring 20 from the inner diameter side of the liquid guide groove portion 517. It is composed of Rayleigh steps 518 and 518'that extend concentrically in the circumferential direction with the static sealing ring 510 in the rotation direction and the reverse rotation direction, respectively.
- the sealed fluid F in the fluid introduction groove 516 moves following the rotary sealing ring 20 in the forward rotation direction by shearing with the sliding surface 21, so that the liquid is liquid. While moving from the guide groove portion 517 to the Rayleigh step 518 side, the sealed fluid F in the outer space S2 is drawn into the liquid guide groove portion 517. Further, even during reverse rotation, the sealed fluid F in the fluid introduction groove 516 moves following the rotation sealing ring 20 in the reverse rotation direction due to shearing with the sliding surface 21, and thus the Rayleigh step 518 from the liquid guide groove portion 517. As it moves to the'side, the sealed fluid F in the outer space S2 is drawn into the liquid guide groove portion 517.
- the fluid introduction groove 516 is covered between the sliding surfaces 511,21 by causing dynamic pressure to be slightly separated between the sliding surfaces 511,21 by the Rayleigh steps 518,518'during both rotations.
- the sealing fluid F By supplying the sealing fluid F, the lubricity between the sliding surfaces 511,21 can be improved.
- the fluid introduction groove 616 in the static sealing ring 610 of the sixth embodiment has the same configuration as the fluid introduction groove 516 of the fifth embodiment.
- the dynamic pressure generation groove 613 has the same configuration as the dynamic pressure generation groove 313 of the third embodiment.
- the fluid introduction groove 616 is a sliding surface 611 by slightly separating the sliding surfaces 611 and 21 and introducing the sealed fluid F between the sliding surfaces 611 and 21 at the time of both rotations. Wear between 21 and 21 can be further suppressed, and leakage of the sealed fluid F can be suppressed by the inclined groove 614 and the reverse inclined groove 615 separated in the radial direction in the dynamic pressure generation groove 613.
- the fluid introduction groove 716 in the static sealing ring 710 of the seventh embodiment is composed of a substantially trapezoidal groove communicating with the outer space S2.
- the side wall portion 716a on the downstream side in the forward rotation direction of the rotary sealing ring 20 extends linearly while inclining from the outer diameter side toward the inner diameter side in the reverse rotation direction, and is rotationally sealed.
- the side wall portion 716d on the upstream side in the forward rotation direction of the ring 20 extends linearly along the diameter line from the outer diameter side to the inner diameter side.
- the acute angle portion 716A formed by the wall portion 716c and the side wall portion 716b at the inner diameter end is arranged close to the acute angle portion 713C of the dynamic pressure generation groove 713 on the downstream side in the forward rotation direction in the circumferential direction. ing.
- the side wall portion 716a of the fluid introduction groove 716 is inclined along the circumferential direction, the relative rotation between the static sealing ring 710 and the rotary sealing ring 20 at the time of normal rotation of the rotary sealing ring 20 starts. Occasionally, the sealed fluid F is likely to be introduced into the fluid introduction groove 716.
- the sharp angle portion 716A of the fluid introduction groove 716 is formed during the reverse rotation of the rotary sealing ring 20. Since the sealed fluid F that leaks out in a concentrated manner can be sucked and recovered by the negative pressure generated at the sharp corner portion 713C of the dynamic pressure generation groove 713 and its vicinity, the leakage of the sealed fluid F to the inner space S1 is further suppressed. be able to.
- the fluid introduction groove 816 in the static sealing ring 810 of the present embodiment 8 is composed of a rectangular groove communicating with the outer space S2.
- the side wall portion 816a on the downstream side in the forward rotation direction and the side wall portion 816b on the upstream side in the forward rotation direction of the rotary sealing ring 20 are directed in the reverse rotation direction from the outer diameter side to the inner diameter side. It extends linearly while tilting.
- the acute angle portion 816A formed by the wall portion 816c and the side wall portion 816b at the inner diameter end is arranged close to the acute angle portion 813C of the dynamic pressure generating groove 813 on the downstream side in the forward rotation direction in the circumferential direction. ing.
- the fluid introduction groove 816 has a smaller acute angle portion 816A than that of the seventh embodiment and is closer to the acute angle portion 813C of the dynamic pressure generating groove 813 in the circumferential direction, the fluid sealing ring 20 is rotated in the reverse direction.
- the sealed fluid F tends to concentrate on the acute-angled portion 816A, and the sealed fluid F that concentrates and leaks out on the acute-angled portion 816A of the fluid introduction groove 816 is generated in the acute-angled portion 813C of the dynamic pressure generating groove 813 and its vicinity. Since it can be sucked and recovered by pressure, leakage of the sealed fluid F to the inner space S1 can be further suppressed.
- the fluid introduction groove 916 in the static sealing ring 910 of the present embodiment 9 is a liquid guiding groove portion 917 communicating with the outer space S2 and a rotary sealing ring 20 from the outer diameter side of the liquid guiding groove portion 917. It is composed of a stationary sealing ring 910 and a Rayleigh step 918 extending concentrically in the circumferential direction in the forward rotation direction.
- the liquid guide groove portion 917 has substantially the same shape as the fluid introduction groove 916 of the eighth embodiment.
- the Rayleigh step 918 causes dynamic pressure to be generated by the Rayleigh step 918 so that the sliding surfaces 911 and 21 are slightly separated from each other and slide.
- the fluid introduction groove 1016 in the static sealing ring 1010 of the present embodiment 10 has a liquid guide groove portion 1017 communicating with the outer space S2 and a positive rotation sealing ring 20 from the inner diameter side of the liquid guide groove portion 1017. It is composed of Rayleigh steps 1018 and 1018'that extend concentrically in the circumferential direction with the stationary sealing ring 1010 in the rotation direction and the reverse rotation direction, respectively.
- the liquid guide groove portion 1017 has substantially the same shape as the fluid introduction groove 816 of the eighth embodiment.
- the mechanical seal for automobiles has been described as an example as the sliding component, but other mechanical seals such as general industrial machines may be used.
- the present invention is not limited to the mechanical seal, and may be a sliding component other than the mechanical seal such as a slide bearing.
- the dynamic pressure generation groove and the fluid introduction groove are provided in the static sealing ring
- the dynamic pressure generation groove and the fluid introduction groove may be provided in the rotary sealing ring.
- the sealed fluid side has been described as the high pressure side and the leak side as the low pressure side, the sealed fluid side may be the low pressure side and the leak side may be the high pressure side, and the sealed fluid side and the leak side are abbreviated. It may be the same pressure.
- the inclined groove in the dynamic pressure generating groove communicates with the inner space S1
- the present invention is not limited to this, and if the dynamic pressure can be generated, it does not have to communicate.
- the dynamic pressure generating groove is not limited to the one in which the reverse inclined groove is continuously formed at the end on the outer diameter side of the inclined groove, and the reverse inclined groove branches from the substantially central portion in the extending direction of the inclined groove. May be formed.
- a plurality of reverse inclined grooves may be arranged for one inclined groove.
- the inclined groove is not limited to the one extending in an arc shape while inclining in the circumferential direction, and the shape may be simplified by forming the inclined groove in a straight line.
- the fluid introduction groove may be deeper than the dynamic pressure generation groove.
- the sealed fluid F has been described as a high-pressure liquid, but the sealed fluid F is not limited to this, and may be a gas or a low-pressure liquid, or may be in the form of a mist in which a liquid and a gas are mixed.
- the fluid on the leak side is the atmosphere A, which is a low-pressure gas, but the present invention is not limited to this, and may be a liquid or a high-pressure gas, or a mist-like mixture of a liquid and a gas. May be.
- Static sealing ring (sliding parts) 11 Sliding surface 12 Lands 12a to 12c Lands 13 Dynamic pressure generating grooves 13'Inclined grooves 13C, 13C', 13D Sharp corners 14 Inclined grooves 15 Reversely inclined grooves (recesses) 16 Fluid introduction groove 17 Liquid induction groove 18 Rayleigh step 20 Rotating sealing ring (other sliding parts) 21 Sliding surface 310 Static sealing ring (sliding parts) 311 Sliding surface 312d Circular land portion 313 Dynamic pressure generation groove 313'Inclined groove 314 Inclined groove 314C Acute angle portion 315 Reverse inclined groove (recess) 315C, 315D Acute angle part 410 Static sealing ring (sliding part) 411 Sliding surface 413 Dynamic pressure generation groove 414 Inclined groove 415 Recess A Atmosphere F Sealed fluid S1 Inner space S2 Outer space
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Sealing (AREA)
Abstract
Description
回転機械の相対回転する箇所に配置され他の摺動部品と相対摺動し、摺動面に被密封流体側の空間に連通し被密封流体を導入する複数の流体導入溝と、漏れ側から被密封流体側に延び動圧を発生させる複数の傾斜溝と、を備える環状の摺動部品であって、
前記摺動部品の摺動面には、少なくとも周方向に隣接する前記流体導入溝の間に配置される凹部が備えられている。
これによれば、逆回転時において、流体導入溝から摺動面間に流出する被密封流体が流体導入溝の相対回転下流側で凹部により捕捉されることにより、漏れ側の空間への被密封流体の漏れを減らすことができる。そのため、両回転時において摺動面同士を離間させて摩耗を抑制することができ、かつ一対の摺動部品間から被密封流体が漏れ側の空間に漏れることを抑制できる。
これによれば、逆回転時において、流体導入溝から摺動面間に流出する被密封流体が流体導入溝の相対回転下流側で逆傾斜溝により捕捉され、逆傾斜溝内に捕捉された被密封流体が他の摺動部品の摺動面とのせん断により追随移動し逆傾斜溝の被密封流体側の端部から被密封流体側に向けて摺動面間に戻されることにより漏れ側の空間への被密封流体の漏れをさらに減らすことができる。
これによれば、流体導入溝の漏れ側に配置される傾斜溝と径方向に重なる位置に凹部が存在しておらず、流体導入溝の漏れ側に配置される傾斜溝の延在距離を長くすることができる。そのため、正回転時において、当該傾斜溝内で漏れ側の流体により高い正圧を発生させやすくなり、動圧効果を高めることができる。
これによれば、レイリーステップにより、動圧を生じさせて摺動面間を僅かに離間させ摺動面間に被密封流体を導入することができるため、摺動面同士の潤滑性を高めることができる。
これによれば、両回転時において、レイリーステップにより、動圧を生じさせて摺動面間を僅かに離間させ摺動面間に被密封流体を導入することができるため、摺動面同士の潤滑性を高めることができる。
これによれば、逆回転時において、逆傾斜溝で正圧を早期に発生させることができる。
これによれば、逆回転時において、傾斜溝を通って漏れ側に向けて移動しようとする被密封流体を逆傾斜溝により被密封流体側に戻すことができるため、漏れ側の空間への被密封流体の漏れを減らすことができる。
これによれば、逆回転時において、環状ランド部の被密封流体側において逆傾斜溝に被密封流体が捕捉されるため、傾斜溝に被密封流体が進入することを抑制できる。また、環状ランド部により傾斜溝と逆傾斜溝が分離されていることにより、両回転時において、傾斜溝と逆傾斜溝が互いの動圧発生に干渉することがないため、動圧効果を発揮しやすい。
11 摺動面
12 ランド
12a~12c ランド部
13 動圧発生溝
13’ 傾斜溝
13C,13C’,13D 鋭角部
14 傾斜溝
15 逆傾斜溝(凹部)
16 流体導入溝
17 液体誘導溝部
18 レイリーステップ
20 回転密封環(他の摺動部品)
21 摺動面
310 静止密封環(摺動部品)
311 摺動面
312d 環状ランド部
313 動圧発生溝
313’ 傾斜溝
314 傾斜溝
314C 鋭角部
315 逆傾斜溝(凹部)
315C,315D 鋭角部
410 静止密封環(摺動部品)
411 摺動面
413 動圧発生溝
414 傾斜溝
415 凹部
A 大気
F 被密封流体
S1 内空間
S2 外空間
Claims (8)
- 回転機械の相対回転する箇所に配置され他の摺動部品と相対摺動し、摺動面に被密封流体側の空間に連通し被密封流体を導入する複数の流体導入溝と、漏れ側から被密封流体側に延び動圧を発生させる複数の傾斜溝と、を備える環状の摺動部品であって、
前記摺動部品の摺動面には、少なくとも周方向に隣接する前記流体導入溝の間に配置される凹部が備えられている摺動部品。 - 前記凹部は、前記傾斜溝の被密封流体側に設けられ前記傾斜溝に対して逆方向に延び動圧を発生させる逆傾斜溝である請求項1に記載の摺動部品。
- 前記凹部は、隣接する前記流体導入溝の間のみに設けられている請求項1または2に記載の摺動部品。
- 前記流体導入溝は、レイリーステップを有している請求項1ないし3のいずれかに記載の摺動部品。
- 前記流体導入溝は、周方向両側に延びるレイリーステップを有している請求項1ないし3のいずれかに記載の摺動部品。
- 前記逆傾斜溝は、前記傾斜溝と比べて延在距離が短い請求項2ないし5のいずれかに記載の摺動部品。
- 前記傾斜溝と前記逆傾斜溝は、連続する溝である請求項2ないし6のいずれかに記載の摺動部品。
- 前記傾斜溝と前記逆傾斜溝との間には、前記傾斜溝の被密封流体側で周方向に連続し径方向所定以上の幅を有する環状ランド部が設けられている請求項2ないし6のいずれかに記載の摺動部品。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2022528825A JPWO2021246372A1 (ja) | 2020-06-02 | 2021-05-31 | |
CN202180038568.0A CN115698566A (zh) | 2020-06-02 | 2021-05-31 | 滑动部件 |
KR1020227043002A KR20230008819A (ko) | 2020-06-02 | 2021-05-31 | 슬라이딩 부품 |
EP21818322.6A EP4160057A4 (en) | 2020-06-02 | 2021-05-31 | SLIDING COMPONENT |
US17/928,571 US20230228292A1 (en) | 2020-06-02 | 2021-05-31 | Sliding component |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2020-095900 | 2020-06-02 | ||
JP2020095900 | 2020-06-02 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2021246372A1 true WO2021246372A1 (ja) | 2021-12-09 |
Family
ID=78830299
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2021/020703 WO2021246372A1 (ja) | 2020-06-02 | 2021-05-31 | 摺動部品 |
Country Status (6)
Country | Link |
---|---|
US (1) | US20230228292A1 (ja) |
EP (1) | EP4160057A4 (ja) |
JP (1) | JPWO2021246372A1 (ja) |
KR (1) | KR20230008819A (ja) |
CN (1) | CN115698566A (ja) |
WO (1) | WO2021246372A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2023223914A1 (ja) * | 2022-05-19 | 2023-11-23 | イーグル工業株式会社 | 摺動部品 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20230008818A (ko) * | 2020-06-02 | 2023-01-16 | 이구루코교 가부시기가이샤 | 슬라이딩 부품 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0144492B2 (ja) | 1980-07-21 | 1989-09-28 | Dainippon Printing Co Ltd | |
JPH0666374A (ja) * | 1992-04-02 | 1994-03-08 | John Crane Inc | 二重螺旋溝を有する面シール |
JP2005180652A (ja) * | 2003-12-22 | 2005-07-07 | Eagle Ind Co Ltd | 摺動部品 |
WO2018088353A1 (ja) * | 2016-11-14 | 2018-05-17 | イーグル工業株式会社 | しゅう動部品 |
WO2019044671A1 (ja) * | 2017-08-28 | 2019-03-07 | イーグル工業株式会社 | 摺動部品 |
WO2019069887A1 (ja) * | 2017-10-03 | 2019-04-11 | イーグル工業株式会社 | 摺動部品 |
JP2019173953A (ja) * | 2018-03-29 | 2019-10-10 | 株式会社豊田自動織機 | 遠心圧縮機 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2881632B1 (en) * | 2012-08-04 | 2018-04-04 | Eagle Industry Co., Ltd. | Sliding component |
WO2016035860A1 (ja) * | 2014-09-04 | 2016-03-10 | イーグル工業株式会社 | メカニカルシール |
US10519966B2 (en) * | 2014-12-22 | 2019-12-31 | Eagle Industry Co., Ltd. | Plain bearing and pump |
US10704417B2 (en) | 2015-04-15 | 2020-07-07 | Eagle Industry Co., Ltd. | Sliding component having fluid introduction groove and dynamic pressure generation groove |
CN110832235B (zh) * | 2017-07-13 | 2022-07-12 | 伊格尔工业股份有限公司 | 滑动部件 |
CN112789434B (zh) * | 2018-10-24 | 2023-09-29 | 伊格尔工业股份有限公司 | 滑动部件 |
EP3926188B1 (en) * | 2019-02-15 | 2024-08-21 | Eagle Industry Co., Ltd. | Sliding components |
CN113508238B (zh) * | 2019-03-22 | 2023-07-25 | 伊格尔工业股份有限公司 | 滑动部件 |
-
2021
- 2021-05-31 JP JP2022528825A patent/JPWO2021246372A1/ja active Pending
- 2021-05-31 WO PCT/JP2021/020703 patent/WO2021246372A1/ja unknown
- 2021-05-31 KR KR1020227043002A patent/KR20230008819A/ko not_active Application Discontinuation
- 2021-05-31 CN CN202180038568.0A patent/CN115698566A/zh active Pending
- 2021-05-31 EP EP21818322.6A patent/EP4160057A4/en active Pending
- 2021-05-31 US US17/928,571 patent/US20230228292A1/en active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0144492B2 (ja) | 1980-07-21 | 1989-09-28 | Dainippon Printing Co Ltd | |
JPH0666374A (ja) * | 1992-04-02 | 1994-03-08 | John Crane Inc | 二重螺旋溝を有する面シール |
JP2005180652A (ja) * | 2003-12-22 | 2005-07-07 | Eagle Ind Co Ltd | 摺動部品 |
WO2018088353A1 (ja) * | 2016-11-14 | 2018-05-17 | イーグル工業株式会社 | しゅう動部品 |
WO2019044671A1 (ja) * | 2017-08-28 | 2019-03-07 | イーグル工業株式会社 | 摺動部品 |
WO2019069887A1 (ja) * | 2017-10-03 | 2019-04-11 | イーグル工業株式会社 | 摺動部品 |
JP2019173953A (ja) * | 2018-03-29 | 2019-10-10 | 株式会社豊田自動織機 | 遠心圧縮機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP4160057A4 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2023223914A1 (ja) * | 2022-05-19 | 2023-11-23 | イーグル工業株式会社 | 摺動部品 |
Also Published As
Publication number | Publication date |
---|---|
US20230228292A1 (en) | 2023-07-20 |
EP4160057A4 (en) | 2024-06-26 |
EP4160057A1 (en) | 2023-04-05 |
JPWO2021246372A1 (ja) | 2021-12-09 |
KR20230008819A (ko) | 2023-01-16 |
CN115698566A (zh) | 2023-02-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20220120313A1 (en) | Sliding components | |
WO2020196145A1 (ja) | 摺動部品 | |
WO2021246372A1 (ja) | 摺動部品 | |
KR102682943B1 (ko) | 슬라이딩 부품 | |
US20220275828A1 (en) | Sliding component | |
WO2021246371A1 (ja) | 摺動部品 | |
CN112334690A (zh) | 滑动组件 | |
JPWO2020162348A1 (ja) | 摺動部品 | |
JP2020173020A (ja) | 摺動部品 | |
US20220099138A1 (en) | Sliding components | |
JPWO2020162349A1 (ja) | 摺動部品 | |
JPWO2020162352A1 (ja) | 摺動部品 | |
WO2020209258A1 (ja) | 摺動部品 | |
WO2023199791A1 (ja) | 摺動部品 | |
WO2021193743A1 (ja) | 摺動部品 | |
US20230118633A1 (en) | Sliding component | |
WO2021230081A1 (ja) | 摺動部品 | |
WO2023026756A1 (ja) | 摺動部品 | |
WO2023095905A1 (ja) | 摺動要素 | |
WO2024004657A1 (ja) | 摺動部品 | |
US20240209891A1 (en) | Sliding component | |
JP2020153468A (ja) | 摺動部品 | |
KR20240019290A (ko) | 슬라이딩 부품 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 21818322 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2022528825 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 20227043002 Country of ref document: KR Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2021818322 Country of ref document: EP Effective date: 20230102 |