WO2021182168A1 - 摺動部品 - Google Patents
摺動部品 Download PDFInfo
- Publication number
- WO2021182168A1 WO2021182168A1 PCT/JP2021/007813 JP2021007813W WO2021182168A1 WO 2021182168 A1 WO2021182168 A1 WO 2021182168A1 JP 2021007813 W JP2021007813 W JP 2021007813W WO 2021182168 A1 WO2021182168 A1 WO 2021182168A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shallow groove
- groove
- sliding
- sliding component
- end portion
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 158
- 238000007789 sealing Methods 0.000 description 68
- 230000003068 static effect Effects 0.000 description 40
- 230000007246 mechanism Effects 0.000 description 15
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 9
- 239000000463 material Substances 0.000 description 9
- 230000004048 modification Effects 0.000 description 8
- 238000012986 modification Methods 0.000 description 8
- 229910052799 carbon Inorganic materials 0.000 description 7
- 239000007788 liquid Substances 0.000 description 7
- 230000007423 decrease Effects 0.000 description 3
- 230000006698 induction Effects 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 239000006185 dispersion Substances 0.000 description 2
- 229910002804 graphite Inorganic materials 0.000 description 2
- 239000010439 graphite Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000000638 solvent extraction Methods 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
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 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
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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
- 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
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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
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/0633—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being retained in a gap
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/74—Sealings of sliding-contact bearings
- F16C33/741—Sealings of sliding-contact bearings by means of a fluid
-
- 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
-
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure
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 fields, or an automobile or a general industrial machine. Or other sliding parts used for 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.
- the sliding surface of the sliding component is provided with a positive pressure generating groove that communicates with the outer diameter side, which is the high-pressure sealed fluid side, and closes one end on the sliding surface.
- the mechanical seal shown in Patent Document 1 is provided with a Rayleigh step and a reverse Rayleigh step communicating with the fluid to be sealed in one of the sliding parts. According to this, when the sliding parts rotate relative to each other, a positive pressure is generated between the sliding surfaces by the Rayleigh step, the sliding surfaces are separated from each other, and the sealed fluid is interposed between the sliding surfaces to provide lubricity. Is improved.
- the reverse Rayleigh step a relatively negative pressure is generated, and since the reverse Rayleigh step is arranged on the leakage side of the Rayleigh step, the high-pressure sealed fluid flowing out from the Rayleigh step between the sliding surfaces is reverse-Rayleigh. Can be inhaled into the step. Further, a deep groove having a larger volume than that of the reverse Rayleigh step is provided on the relative rotation end side of the reverse Rayleigh step, and the sealed fluid recovered in the reverse Rayleigh step is moved to the sealed fluid side via the deep groove. It is supposed to be returned. In this way, the sealed fluid between the pair of sliding parts is prevented from leaking to the leak side, and the sealing property is improved.
- the sealed fluid in the reverse rayry step provided on one sliding component reverses the sealed fluid due to the relative rotation of the other sliding component facing each other. It is designed to move from the Rayleigh step toward the deep groove.
- the flow path cross-sectional area of the reverse Rayleigh step is constant in the circumferential direction, the amount of movement of the sealed fluid from the reverse Rayleigh step to the deep groove depends on the relative rotation speed of the sliding component.
- the fluid to be sealed on the upper side in the reverse rayy step follows the movement of the sliding component on the other side, but the fluid to be sealed on the bottom side slides on the other. It became difficult to follow the movement of the parts, the amount of movement of the sealed fluid in the reverse Rayleigh step did not increase as the relative rotation speed increased, and there was a risk that sufficient negative pressure would not be generated in the reverse Rayleigh step.
- the present invention has been made by paying attention to such a problem, and provides a sliding component capable of reliably generating a negative pressure in a shallow groove regardless of the relative rotation speed of the other sliding component.
- the purpose is to do.
- the sliding parts of the present invention are An annular sliding component that is placed in a relative rotating part of a rotating machine and slides relative to other sliding components.
- the sliding surface of the sliding component is provided with a shallow groove for generating negative pressure extending in the circumferential direction and a deep groove deeper than the shallow groove for collecting the fluid to be sealed in the shallow groove.
- the shallow groove has a terminal portion in which the cross-sectional area of the flow path narrows toward the deep groove. According to this, since the flow path cross-sectional area of the shallow groove is narrowed toward the deep groove, the pressure of the fluid to be sealed in the shallow groove is increased at the end during the relative rotation of the sliding parts.
- the deep groove is arranged on the downstream side, the sealed fluid at the end portion easily flows into the deep groove. In this way, a negative pressure can be reliably generated in the shallow groove regardless of the rotation speed of the sliding component. Further, since the sealed fluid at the end of the shallow groove flows into the deep groove, it is possible to suppress the generation of positive pressure between the sliding surfaces due to the shallow groove.
- the shallow groove may have its end portion gradually shallowed toward the deep groove. According to this, since the sealed fluid aggregates in the shallow groove from the end to the deep groove from the bottom surface of the shallow groove toward the sliding surface, it is easily affected by the flow of the sliding surface, so that the sealed fluid is deeply grooved. Can be made to flow in a large amount.
- the bottom surface of the end portion of the shallow groove may be curved so as to be recessed toward the deep groove side. According to this, the region where the pressure of the sealed fluid increases at the terminal portion can be reduced.
- the deep groove may communicate with the fluid to be sealed. According to this, the sealed fluid collected in the deep groove can be returned to the sealed fluid side.
- the shallow groove may have a start end portion extending over the entire circumference of the sliding surface of the sliding component and continuing in the circumferential direction with respect to the deep groove. According to this, a negative pressure can be generated over the entire circumference of the sliding surface of the sliding component.
- the shallow groove and the deep groove are equally arranged in the circumferential direction of the sliding surface of the sliding component, and the shallow groove has a symmetrical shape with reference to a line extending in the radial direction passing through the deep groove. May be good. According to this, it can be used not limited to the relative rotation direction of the sliding component. Further, since the sealed fluid is less likely to flow into the shallow groove on the relative rotation end side than the deep groove, a negative pressure can be generated in the shallow groove on the relative rotation end side as well.
- the shallow groove of the sliding component according to the present invention extends in the circumferential direction as long as the shallow groove extends with at least a component in the circumferential direction, preferably a component along the circumferential direction rather than the radial direction. It suffices if it is extended so that Further, the fact that the deep groove extends in the radial direction means that the deep groove may extend with at least a radial component, and preferably the deep groove extends so that the component along the radial direction is larger than that in the circumferential direction. Just do it.
- 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 cross-sectional view which shows an example of the mechanical seal in Example 1 of this invention. It is the figure which looked at the sliding surface of the static sealing ring from the axial direction. It is a cross-sectional view of AA. It is explanatory drawing which looked at the vicinity of the liquid guide groove part in a negative pressure generation mechanism from the axial direction. It is the schematic cross-sectional view which cut in the vicinity of the liquid guide groove part by the plane orthogonal to the liquid guide groove part. It is explanatory drawing which shows the modification 1 of the static sealing ring of Example 1. FIG. It is explanatory drawing which shows the modification 2 of the static sealing ring of Example 1. FIG. It is explanatory drawing which shows the modification 3 of the static sealing ring of Example 1. FIG.
- FIG. It is explanatory drawing which shows the modification 4 of the static sealing ring of Example 1.
- FIG. It is explanatory drawing which shows the modification 5 of the static sealing ring of Example 1.
- FIG. It is explanatory drawing which shows the modification 6 of the static sealing ring of Example 1.
- FIG. It is a figure which looked at the sliding surface of the static sealing ring in Example 2 of this invention from the axial direction.
- the sliding parts according to the first embodiment will be described with reference to FIGS. 1 to 5.
- a mode in which the sliding component is a mechanical seal will be described as an example.
- the outer diameter side of the sliding parts constituting the mechanical seal will be described as the sealed fluid side (high pressure side), and the inner diameter side will be described as the atmosphere side (low pressure side) as the leakage side.
- dots may be added to the grooves and the like formed on the sliding surface in the drawings.
- the mechanical seal for general industrial machinery shown in FIG. 1 is an inside type that seals the sealed fluid F that tends to leak from the outer diameter side to the inner diameter side of the sliding surface.
- a mode in which the sealed fluid F is a high-pressure gas is illustrated.
- the mechanical seal is a rotary seal ring 20 which is an annular sliding component provided on the rotary shaft 1 so as to be rotatable together with the rotary shaft 1 via a sleeve 2, and a seal fixed to the housing 4 of the attached device.
- the cover 5 is mainly composed of an annular static sealing ring 10 as a sliding component provided on the cover 5 in a non-rotating state and an axially movable state, and the bellows 7 urges the static sealing ring 10 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.
- the sliding surface 21 of the rotary sealing ring 20 is a flat surface, and the flat surface is not provided with a recessed portion.
- 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 using 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.
- carbon in which carbon and graphite are mixed.
- metal materials, resin materials, surface modification materials (coating materials), composite materials and the like can also be applied.
- a negative pressure generating mechanism 14 is provided on the sliding surface 11 of the static sealing ring 10.
- the negative pressure generating mechanism 14 includes a fluid guide groove portion 15 as a deep groove that communicates with the sealed fluid F side and extends in the inner diameter direction, and a static sealing ring 10 from a circumferential end portion on the downstream side of the fluid guide groove portion 15 on the inner diameter side. It is provided with a shallow groove 9 for generating negative pressure, which extends concentrically in the circumferential direction and is continuously provided at the peripheral end portion on the upstream side of the inner diameter side of the fluid guide groove portion 15.
- the portion of the sliding surface 11 other than the negative pressure generating mechanism 14 is a land 12 forming a flat end surface. Further, although not shown, a positive pressure generating mechanism such as dimples is formed on the land 12 located on the outer diameter side of the shallow groove 9.
- the end portion of the shallow groove 9 connected to the left side of the paper surface of the fluid guide groove portion 15 is the starting end portion 9a of the relative rotation of the shallow groove 9, that is, the sealed fluid F flowing in the shallow groove 9.
- the end portion of the shallow groove 9 connected to the right side of the paper surface of the fluid guide groove portion 15 is described as the upstream side as the end portion 9b of the relative rotation of the shallow groove 9, that is, the downstream side of the sealed fluid F flowing in the shallow groove 9. do.
- the depth of the shallow groove 9 is shown deeper than it actually is.
- the fluid guide groove portion 15 of the first embodiment extends in the radial direction of the static sealing ring 10. Further, the fluid guide groove portion 15, the start end portion 9a and the end portion 9b of the shallow groove 9 are connected in series, that is, arranged side by side in the circumferential direction.
- the shallow groove 9 includes a bottom surface 9c, an outer surface 9d erected from the outer diameter side of the bottom surface 9c, and an inner side surface 9e erected from the inner diameter side of the bottom surface 9c.
- the outer side surface 9d and the inner side surface 9e are parallel to each other and orthogonal to the flat surface of the land 12.
- the bottom surface 9k near the start end portion 9a of the shallow groove 9 extends in an arc shape that is convex toward the side opposite to the sliding surface 11, and the shallow groove The depth of 9 gradually becomes shallower toward the starting end side of the shallow groove 9. That is, the cross section (the cross section shown in FIG. 3, that is, the peripheral cross section) cut in the vicinity of the starting end portion 9a of the shallow groove 9 on the plane orthogonal to the fluid guiding groove portion 15 is curved so as to be recessed toward the fluid guiding groove portion 15.
- a wall portion 9f for partitioning the shallow groove 9 and the fluid guide groove portion 15 is formed at the starting end portion 9a of the shallow groove 9.
- the top portion 9g of the wall portion 9f has a linear shape extending in the radial direction, and is arranged on the flat end surface of the land 12, that is, a position slightly deeper than the upper surface in FIG. 3, that is, the bottom surface 9c side.
- the shallow groove 9 and the fluid guide groove portion 15 communicate with each other in the space G1 on the flat end surface side of the land 12 at the top portion 9 g.
- the flow path cross-sectional area of the start end portion 9a of the shallow groove 9 gradually decreases toward the fluid guide groove portion 15.
- the bottom surface 9m near the end portion 9b of the shallow groove 9 extends in an arc shape that is convex toward the side opposite to the sliding surface 11, and the depth of the shallow groove 9 is shallow. It gradually becomes shallower toward the end of the groove 9. That is, the cross section obtained by cutting the vicinity of the end portion 9b of the shallow groove 9 on the plane orthogonal to the fluid guide groove portion 15 is curved so as to be recessed toward the fluid guide groove portion 15.
- a wall portion 9h for partitioning the shallow groove 9 and the fluid guide groove portion 15 is formed at the terminal portion 9b of the shallow groove 9. Further, the top portion 9j of the wall portion 9h is arranged at a position slightly deeper than the flat end surface of the land 12, that is, on the bottom surface 9c side.
- the shallow groove 9 and the fluid guide groove portion 15 communicate with each other in the space G2 on the flat end surface side of the land 12 at the top portion 9j. As described above, the flow path cross-sectional area of the end portion 9b of the shallow groove 9 gradually decreases toward the fluid guide groove portion 15.
- the bottom surface 9n between the bottom surface 9k near the start end portion 9a and the bottom surface 9m near the end end portion 9b is a flat surface parallel to the flat end surface of the land 12, and is the deepest portion in the shallow groove 9. It has become.
- the vicinity of the start end portion 9a of the shallow groove 9 and the vicinity of the end portion 9b of the shallow groove 9 form a symmetrical shape with reference to a line LN (see FIG. 2) extending in the radial direction along the fluid guide groove portion 15. ..
- the depth dimension L10 of the fluid guide groove portion 15 is deeper than the deepest portion in the shallow groove 9, that is, the depth dimension L20 between the flat end surface of the land 12 and the bottom surface 9n of the shallow groove 9 (). L10> L20).
- the depth dimension L10 of the fluid guide groove portion 15 in the first embodiment is formed to 100 ⁇ m, and the depth dimension L20 of the shallow groove 9 is formed to 1 ⁇ m. If the depth dimension of the fluid guide groove portion 15 is formed deeper than the depth dimension of the shallow groove 9, the depth dimension of the fluid guide groove portion 15 and the shallow groove 9 can be freely changed, preferably the dimension L10. It is 5 times or more the dimension L20.
- the sealed fluid F on the outer diameter side of the sliding surfaces 11 and 21 is drawn between the sliding surfaces 11 and 21, and the above-mentioned illustration is omitted. Due to the positive pressure generated by the positive pressure generation mechanism, the sliding surfaces 11 and 21 are slightly separated from each other. Further, as shown in FIGS. 4 and 5, the sealed fluid F flowing into the shallow groove 9 follows the rotation direction of the rotary sealing ring 20 due to friction with the sliding surface 21 as shown by the arrow L1. ..
- the fluid guide groove portion 15 Since the flow path cross-sectional area of the end portion 9b of the shallow groove 9 is gradually reduced toward the fluid guide groove portion 15, the fluid is aggregated, whereby the pressure is highest in the vicinity of the end portion 9b and the pressure is increased. As shown by the arrow L2, the sealed fluid F flows into the fluid guide groove portion 15 through the space surrounded by the outer surface 9d, the inner surface 9e, the top portion 9j, and the sliding surface 21 of the rotary sealing ring 20. Since the fluid guide groove portion 15 has a space for dispersing the fluid, the agglomerated fluid is dispersed, and the increased pressure is reduced by the dispersion of the fluid, and the shallow groove 9 on the downstream side, that is, the starting end portion.
- the high pressure sealed fluid F is prevented from flowing into the 9a side.
- the volume of the shallow groove 9 on the downstream side of the top 9g suddenly increases, so that a negative pressure is generated due to the dispersion of the fluid, and the negative pressure is the shallow groove 9. It covers the whole area.
- the sealed fluid F in the fluid guide groove portion 15 is caused by the sealed fluid F flowing in from the terminal portion 9b of the shallow groove 9 to be arrowed L3. It is extruded to the outer diameter side as shown in. Further, during the relative rotation of the static sealing ring 10 and the rotary sealing ring 20, the sealed fluid F flows in between the sliding surfaces 11 and 21 from the outer diameter side thereof and the fluid guide groove portion 15 at any time, and has lubricity. Is excellent.
- the sealed fluid F around the portion other than the terminal portion 9b of the shallow groove 9 is sucked into the shallow groove 9 by the negative pressure generated in the shallow groove 9 as shown by the arrow H1.
- the sealed fluid F in the vicinity of the terminal portion 9b of the shallow groove 9 has a high pressure as described above, as shown by the arrow H2, it remains located at the land 12 and almost enters the shallow groove 9. do not.
- the sealed fluid F in the vicinity of the fluid guide groove portion 15 enters the fluid guide groove portion 15 as shown by the arrow H3, and a part of the sealed fluid F in the fluid guide groove portion 15 is shown by the arrow H4.
- the fluid flows out between the sliding surfaces 11 and 21 due to friction with the sliding surface 21 and the like.
- the shallow groove 9 is shallow when the static sealing ring 10 and the rotary sealing ring 20 are relatively rotated. It is difficult to increase the pressure of the sealed fluid F in the groove 9, the shallow groove 9 can be easily maintained at a negative pressure, and the sealed fluid F that tends to leak to the atmosphere can be recovered.
- the sealed fluid F whose pressure is increased in the vicinity of the end portion 9b is arranged on the relative rotation downstream side of the end portion 9b of the shallow groove 9, the sealed fluid F whose pressure is increased in the vicinity of the end portion 9b is , The sealed fluid F whose pressure has been increased is dispersed in the fluid guide groove portion 15 so as to flow into the fluid guide groove portion 15, and the outflow between the sliding surfaces 11 and 21 is suppressed. It is possible to suppress the generation of positive pressure between the moving surfaces 11 and 21. As a result, it is possible to prevent the shallow groove 9 from decreasing in its ability to generate negative pressure. Further, since the sealed fluid F whose pressure has been increased is dispersed in the fluid guide groove portion 15, negative pressure is suitably generated in the shallow groove 9 on the downstream side without flowing into the shallow groove 9 on the downstream side. Can be done.
- the end portion 9b of the shallow groove 9 communicates with the fluid guide groove portion 15, the sealed fluid F whose pressure has been increased is suppressed from flowing out between the sliding surfaces 11 and 21, and the sliding surface 11 , 21 The generation of positive pressure is suppressed.
- the bottom surface 9c near the end portion 9b of the shallow groove 9 gradually becomes shallower toward the fluid guide groove portion 15. According to this, the sealed fluid F aggregates from the end portion 9b of the shallow groove 9 toward the fluid guide groove portion 15 from the bottom surface 9n of the shallow groove 9 toward the sliding surface, so that the sealed fluid F slides. It becomes easily affected by the flow of the surface, and a large amount can flow into the fluid guide groove portion 15 on the downstream side.
- the bottom surface 9c of the end portion 9b of the shallow groove 9 is curved so as to be recessed toward the fluid guide groove portion 15, and the top portion 9j, which is the end of the end portion 9b, is on the opposite sliding surface 21 side, that is, statically sealed. Since the ring 10 faces the axial direction, the region where the pressure of the sealed fluid F increases at the terminal portion 9b can be reduced in the circumferential direction. That is, a large negative pressure generation region of the shallow groove 9 can be secured. Further, the pressure of the sealed fluid F in the shallow groove 9 is maintained so as not to increase until just before the upstream side of the fluid guide groove portion 15, and the portion where the pressure is increased is arranged near the boundary between the end portion 9b and the fluid guide groove portion 15. Therefore, the sealed fluid F whose pressure has been increased is unlikely to return to the shallow groove 9, and the shallow groove 9 can be easily maintained at a negative pressure.
- the bottom surface 9c of the end portion 9b of the shallow groove 9 is curved so as to be recessed toward the fluid guide groove portion 15, the flow of the sealed fluid F in the shallow groove 9 is less likely to be disturbed, and the sealed fluid F is less likely to be disturbed. Flow becomes smooth.
- the sealed fluid F recovered from the shallow groove 9 can be returned to the sealed fluid F side on the outer diameter side. Further, when the static sealing ring 10 and the rotary sealing ring 20 are relatively rotated, the sealed fluid F is easily returned to the sealed fluid F side on the outer diameter side by centrifugal force, and the sealed fluid F is more easily returned than the sliding surfaces 11 and 21. Leakage to the low pressure side on the inner diameter side can be reduced.
- the shallow groove 9 extends concentrically over the entire circumference of the sliding surface 11 and communicates with one fluid guide groove portion 15 at the start end portion 9a and the end portion 9b in the circumferential direction, the shallow groove 9 slides. A negative pressure of the shallow groove 9 can be generated over the entire circumference of the surface 11.
- the starting end portion 9a of the shallow groove 9 communicates with the fluid guide groove portion 15 via the space G1, and when the static sealing ring 10 and the rotary sealing ring 20 rotate relative to each other, the fluid guiding groove portion 15 to the shallow groove 9 Since it is difficult for the sealed fluid F to enter the start end portion 9a side, a large negative pressure can be generated in the shallow groove 9.
- start end portion 9a and the end portion 9b of the shallow groove 9 have a symmetrical shape with reference to the line LN extending in the radial direction along the fluid guide groove portion 15, the static sealing ring 10 and the rotary sealing ring 20 are formed. It can be used regardless of the relative rotation direction with.
- the mode in which the fluid guide groove portion 15 as the deep groove communicates with the sealed fluid F side on the outer diameter side is illustrated, but the present invention is not limited to this, and for example, the modified example shown in FIG.
- the fluid induction groove portion 151 as a deep groove may not communicate with the atmosphere A side and the sealed fluid F side of the static sealing ring 10.
- the fluid guide groove portion 152 as a deep groove may communicate with the atmosphere A side on the inner diameter side of the static sealing ring 101.
- the deep groove has a size as long as the sealed fluid F flowing out from the end portion 9b of the shallow groove 9 can be recovered to the extent that no positive pressure is generated between the sliding surfaces 11 and 21 or the positive pressure can be suppressed.
- the shape may be freely changed.
- the bottom surface 9c of the start end portion 9a and the end portion 9b of the shallow groove 9 is curved so as to be recessed toward the fluid guide groove portion 15
- the present invention is not limited to this, and for example,
- the bottom surface 90c of the start end portion 90a of the shallow groove 90 extends so as to linearly incline toward the end surface 90g of the wall portion 90f, and the end portion 90b
- the bottom surface 90c' may extend so as to incline linearly with respect to the end face 90j at the wall portion 90h. According to this, the flow of the sealed fluid F flowing from the shallow groove 90 toward the fluid guide groove portion 15 can be smoothed.
- the bottom surface 91c of the start end portion 91a of the shallow groove 91 and the bottom surface 91c'of the end end portion 91b are in the circumferential direction of the fluid guide groove portion 15. It may be curved so as to bulge to the opposite side.
- the cross-sectional shape may be freely changed.
- the relative rotation direction of the sliding component is only one direction, at least the end portion of the shallow groove may be gradually shallowed toward the deep groove.
- the terminal portion 9b of the shallow groove 9 gradually becomes shallower toward the fluid guide groove portion 15, and the radial width of the shallow groove 9 is constant over the circumferential direction.
- the present invention is not limited to this, and for example, the radial width of the end portion of the shallow groove may be gradually narrowed. That is, the end portion of the shallow groove may be formed so that the cross-sectional area of the flow path narrows toward the deep groove.
- the embodiment in which the start end portion 9a and the end portion 9b of the shallow groove 9 communicate with the fluid guide groove portion 15 is illustrated, but it is similar to the static sealing ring 104 of the modified example 5 shown in FIG.
- a land 121 may be formed between the start end portion 92a and the end portion 92b of the shallow groove 92 and the fluid guide groove portion 15. That is, the fluid guide groove portion 15 may be arranged adjacent to the downstream side of the terminal portion 9b.
- the embodiment in which the top portion 9g of the wall portion 9f and the top portion 9j of the wall portion 9h in the shallow groove 9 are arranged slightly on the bottom surface 9c side of the flat end surface of the land 12 is illustrated.
- the present invention is not limited to this, and the top 9g'and the top 9j' in the shallow groove 9 are arranged in the same plane as the flat end surface of the land 12, as in the static sealing ring 106 of the modified example 6 shown in FIG. You may. That is, if it is possible to prevent a positive pressure exceeding an allowable value from being generated between the sliding surfaces of the sliding parts, the start end portion and the end portion of the shallow groove do not have to communicate with the deep groove.
- a plurality of negative pressure generating mechanisms 145 are formed on the sliding surface 115 of the static sealing ring 105 of the second embodiment so as to be separated from each other in the circumferential direction, and three in the present embodiment.
- the negative pressure generation mechanism 145 has a fluid guide groove portion 153 extending from the outer diameter side to the inner diameter side, and an axially arcuate arc-shaped portion extending from the inner diameter side end portion of the fluid guide groove portion 153 to the relative rotation end side, that is, counterclockwise on the paper surface. It is provided with one shallow groove 95 and a second shallow groove 96 having an axially arcuate shape extending from the inner diameter side end portion of the fluid guide groove portion 153 to the relative rotation start end side, that is, clockwise on the paper surface.
- the start end portion 95a of the first shallow groove 95 is formed so as to be shallower than the intermediate portion 95c and the end portion 95b of the first shallow groove 95, and the intermediate portion 95c and the end portion 95b are parallel to the flat end surface of the land 122. It extends to and is formed at the same depth.
- the end portion 96b of the second shallow groove 96 is formed so as to be shallower than the start end portion 96a and the intermediate portion 96c of the second shallow groove 96, and the start end portion 96a and the intermediate portion 96c are flat end surfaces of the land 122. It extends parallel to and is formed at the same depth. That is, the start end portion 95a of the first shallow groove 95 and the end portion 96b of the second shallow groove 96 are formed so as to gradually become shallower toward the fluid guide groove portion 153 side.
- first shallow groove 95 and the second shallow groove 96 have a symmetrical shape with reference to the line LN extending in the radial direction along the fluid guide groove portion 153, the static sealing ring 105 and the rotary sealing ring 20 are used. Can be used regardless of the relative rotation direction of.
- the fluid guide groove portion 153 is arranged on the downstream side of the second shallow groove 96, so that the sealed fluid F in the second shallow groove 96 is the starting end portion. It moves from 96a to the intermediate portion 96c and the terminal portion 96b side, and even if the pressure is increased at the terminal portion 96b, it easily flows into the fluid guide groove portion 153. Further, since the starting end portion 95a of the first shallow groove 95 has a small communication port with the fluid guide groove portion 153 side, it is difficult for the sealed fluid F to flow into the first shallow groove 95 from the fluid guide groove portion 153. Negative pressure can also be generated in the first shallow groove 95.
- the sealed fluid F flowing out from the end portion 95b of the first shallow groove 95 to the sliding surface 115 can be sucked from the start end portion 96a of the second shallow groove 96 of the negative pressure generating mechanism 145 adjacent to the downstream side. , It is possible to suppress the leakage of the sealed fluid F to the atmosphere A side.
- end portion 95b of the first shallow groove 95 adjacent in the circumferential direction and the start end portion 96a of the second shallow groove 96 may be continuous in the circumferential direction.
- the mechanical seal for general industrial machines has been described as an example as the sliding component, but other mechanical seals for automobiles, water pumps, etc. 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 negative pressure generating mechanism may be provided only on the static sealing ring, but the negative pressure generating mechanism may be provided only on the rotary sealing ring, and the negative pressure generating mechanism may be provided on both the static sealing ring and the rotary sealing ring. You may.
- 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.
- the pressure may be the same.
- the present invention is not limited to this, and sliding is not limited to this. It may be an outside type that seals the sealed fluid F that leaks from the inner diameter side to the outer diameter side of the surface.
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- 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する環状の摺動部品であって、
前記摺動部品の摺動面には、周方向に延びる負圧発生用の浅溝と、前記浅溝内の被密封流体を回収する前記浅溝よりも深い深溝と、が備えられており、
前記浅溝は、前記深溝に向かって流路断面積が狭まる終端部を有している。
これによれば、浅溝の終端部は、深溝に向かって流路断面積が狭まっていることから、摺動部品の相対回転時には、浅溝内の被密封流体の圧力が終端部で高められ、該終端部の被密封流体は下流側に深溝が配置されていることにより深溝に流入しやすくなっている。このようにして、摺動部品の回転速度によらずに浅溝内に負圧を確実に発生させることができる。また、浅溝の終端部の被密封流体が深溝に流入するので該浅溝によって摺動面間に正圧が発生することを抑制できる。
これによれば、浅溝は終端部から深溝にかけて浅溝の底面から摺動面に向かうように被密封流体が凝集するため、摺動面の流れの影響を受け易くなるので被密封流体を深溝に多く流入させることができる。
これによれば、終端部において被密封流体の圧力が高まる領域を小さくすることができる。
これによれば、深溝に回収された被密封流体を被密封流体側に戻すことができる。
これによれば、摺動部品の摺動面の全周に亘って負圧を発生させることができる。
これによれば、摺動部品の相対回転方向に限られず使用できる。また、深溝よりも相対回転終端側の浅溝には被密封流体が流入し難くなっているため、相対回転終端側の浅溝にも負圧を発生させることができる。
9a 始端部
9b 終端部
9c 底面
10 静止密封環(摺動部品)
11 摺動面
14 負圧発生機構
15 液体誘導溝部(深溝)
20 回転密封環(摺動部品)
21 摺動面
90 浅溝
90a 始端部
90b 終端部
91 浅溝
91a 始端部
91b 終端部
92 浅溝
92a 始端部
92b 終端部
95 第1浅溝(浅溝)
95a 始端部
95b 終端部
96 第2浅溝(浅溝)
96a 始端部
96b 終端部
100~105 静止密封環
145 負圧発生機構
151,152,153 液体誘導溝部(深溝)
A 大気
F 被密封流体
Claims (6)
- 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する環状の摺動部品であって、
前記摺動部品の摺動面には、周方向に延びる負圧発生用の浅溝と、前記浅溝内の被密封流体を回収する前記浅溝よりも深い深溝と、が備えられており、
前記浅溝は、前記深溝に向かって流路断面積が狭まる終端部を有している摺動部品。 - 前記浅溝は、前記終端部が前記深溝に向けて漸次浅くなっている請求項1に記載の摺動部品。
- 前記浅溝の前記終端部の底面が、前記深溝側に凹むように湾曲している請求項2に記載の摺動部品。
- 前記深溝は被密封流体側に連通している請求項1ないし3のいずれかに記載の摺動部品。
- 前記浅溝は前記摺動部品の摺動面の全周に亘って延び、前記深溝に対して周方向に連なる始端部を備えている請求項1ないし4のいずれかに記載の摺動部品。
- 前記浅溝及び前記深溝は前記摺動部品の摺動面の周方向に等配されており、前記浅溝は前記深溝を通る径方向に延びる線を基準として対称形状を成している請求項1ないし4のいずれかに記載の摺動部品。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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US17/908,515 US20230118633A1 (en) | 2020-03-09 | 2021-03-02 | Sliding component |
EP21767086.8A EP4119807A4 (en) | 2020-03-09 | 2021-03-02 | SLIDING COMPONENT |
JP2022505934A JPWO2021182168A1 (ja) | 2020-03-09 | 2021-03-02 | |
KR1020227031184A KR20220139957A (ko) | 2020-03-09 | 2021-03-02 | 슬라이딩 부품 |
CN202180017508.0A CN115210488A (zh) | 2020-03-09 | 2021-03-02 | 滑动部件 |
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JP2020-040352 | 2020-03-09 | ||
JP2020040352 | 2020-03-09 |
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WO2021182168A1 true WO2021182168A1 (ja) | 2021-09-16 |
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PCT/JP2021/007813 WO2021182168A1 (ja) | 2020-03-09 | 2021-03-02 | 摺動部品 |
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US (1) | US20230118633A1 (ja) |
EP (1) | EP4119807A4 (ja) |
JP (1) | JPWO2021182168A1 (ja) |
KR (1) | KR20220139957A (ja) |
CN (1) | CN115210488A (ja) |
WO (1) | WO2021182168A1 (ja) |
Cited By (1)
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WO2023182056A1 (ja) * | 2022-03-24 | 2023-09-28 | イーグル工業株式会社 | 摺動部品 |
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WO2012046749A1 (ja) | 2010-10-06 | 2012-04-12 | イーグル工業株式会社 | 摺動部品 |
WO2014148317A1 (ja) * | 2013-03-17 | 2014-09-25 | イーグル工業株式会社 | 摺動部品 |
WO2015087800A1 (ja) * | 2013-12-09 | 2015-06-18 | イーグル工業株式会社 | 摺動部品 |
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WO2020162349A1 (ja) * | 2019-02-04 | 2020-08-13 | イーグル工業株式会社 | 摺動部品 |
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Publication number | Priority date | Publication date | Assignee | Title |
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US11293553B2 (en) * | 2018-05-17 | 2022-04-05 | Eagle Industry Co., Ltd. | Seal ring |
WO2020110922A1 (ja) * | 2018-11-30 | 2020-06-04 | イーグル工業株式会社 | 摺動部品 |
US11852241B2 (en) * | 2019-02-04 | 2023-12-26 | Eagle Industry Co., Ltd. | Sliding component |
KR102647265B1 (ko) * | 2019-02-04 | 2024-03-14 | 이구루코교 가부시기가이샤 | 슬라이딩 부품 |
KR102651943B1 (ko) * | 2019-03-22 | 2024-03-29 | 이구루코교 가부시기가이샤 | 슬라이딩 부품 |
JPWO2022009767A1 (ja) * | 2020-07-06 | 2022-01-13 | ||
US20230296176A1 (en) * | 2020-07-06 | 2023-09-21 | Eagle Industry Co., Ltd. | Sliding component |
-
2021
- 2021-03-02 EP EP21767086.8A patent/EP4119807A4/en active Pending
- 2021-03-02 CN CN202180017508.0A patent/CN115210488A/zh active Pending
- 2021-03-02 US US17/908,515 patent/US20230118633A1/en active Pending
- 2021-03-02 KR KR1020227031184A patent/KR20220139957A/ko not_active Application Discontinuation
- 2021-03-02 WO PCT/JP2021/007813 patent/WO2021182168A1/ja unknown
- 2021-03-02 JP JP2022505934A patent/JPWO2021182168A1/ja active Pending
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WO2014148317A1 (ja) * | 2013-03-17 | 2014-09-25 | イーグル工業株式会社 | 摺動部品 |
WO2015087800A1 (ja) * | 2013-12-09 | 2015-06-18 | イーグル工業株式会社 | 摺動部品 |
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WO2023182056A1 (ja) * | 2022-03-24 | 2023-09-28 | イーグル工業株式会社 | 摺動部品 |
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KR20220139957A (ko) | 2022-10-17 |
EP4119807A4 (en) | 2024-04-24 |
CN115210488A (zh) | 2022-10-18 |
EP4119807A1 (en) | 2023-01-18 |
US20230118633A1 (en) | 2023-04-20 |
JPWO2021182168A1 (ja) | 2021-09-16 |
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