WO2023053964A1 - 摺動部品 - Google Patents

摺動部品 Download PDF

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Publication number
WO2023053964A1
WO2023053964A1 PCT/JP2022/034390 JP2022034390W WO2023053964A1 WO 2023053964 A1 WO2023053964 A1 WO 2023053964A1 JP 2022034390 W JP2022034390 W JP 2022034390W WO 2023053964 A1 WO2023053964 A1 WO 2023053964A1
Authority
WO
WIPO (PCT)
Prior art keywords
groove
fluid
leakage
reverse
leak
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2022/034390
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
忠継 井村
啓志 鈴木
翔悟 福田
健太 内田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eagle Industry Co Ltd
Original Assignee
Eagle Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eagle Industry Co Ltd filed Critical Eagle Industry Co Ltd
Priority to EP22875835.5A priority Critical patent/EP4411182A4/en
Priority to CN202280063523.3A priority patent/CN117980636A/zh
Priority to US18/695,302 priority patent/US12404936B2/en
Priority to KR1020247010305A priority patent/KR20240052031A/ko
Priority to JP2023551293A priority patent/JP7846126B2/ja
Publication of WO2023053964A1 publication Critical patent/WO2023053964A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking 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
    • 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
    • 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
    • F16J15/342—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 means for feeding fluid directly to the face
    • 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

Definitions

  • the present invention relates to sliding parts used for shaft seals and bearings.
  • a mechanical seal consisting of a pair of annular sliding rings that rotate relative to each other and whose sliding surfaces slide against each other is known as a sliding part that prevents leakage of the sealed fluid around the rotating shaft in a rotating machine.
  • a sliding part that prevents leakage of the sealed fluid around the rotating shaft in a rotating machine.
  • a plurality of spiral grooves on the inner diameter side and a plurality of spiral grooves on the outer diameter side are provided on the sliding surface of one of the sliding rings.
  • the spiral groove on the inner diameter side communicates with the space on the leakage side, which is on the inner diameter side of the sliding surface, and extends in the outer diameter direction while being inclined in one direction in the circumferential direction.
  • the spiral groove on the outer diameter side communicates with the space on the sealed fluid side, which is the outer diameter side of the sliding surface, and extends in the inner diameter direction while being inclined in the other circumferential direction. Since the spiral groove extends in the radial direction while being inclined in the circumferential direction in this way, it is possible to obtain a higher dynamic pressure generation capability than recesses or grooves such as dimples or Rayleigh steps extending along the radial direction.
  • the fluid to be sealed flows into the space between the slide surfaces through the spiral groove on the outer diameter side, forming a liquid film.
  • gas on the leakage side is sucked in from the starting end on the inner diameter side of the spiral groove on the inner diameter side, and dynamic pressure is generated at the terminal end.
  • the lubricity between the sliding surfaces is improved.
  • the spiral groove on the outer diameter side sucks in the sealed fluid between the sliding surfaces and discharges it to the outer diameter side, which prevents the sealed fluid from leaking into the space on the leakage side. It is designed to be
  • the present invention has been devised with a focus on such problems, and it is possible to allow the sliding surfaces to slide smoothly from a low speed state to a high speed state regardless of whether the direction of relative rotation is positive or reverse.
  • An object of the present invention is to provide a sliding part that can
  • the sliding component of the present invention is A sliding component provided with a pair of sliding surfaces arranged to face a portion that rotates relative to each other when a rotary machine is driven, and partitioning a fluid-side space and a leakage-side space, On one sliding surface, a fluid side groove communicating with the fluid side space and extending in the positive direction of relative rotation; a fluid-side reverse groove communicating with the fluid-side space and extending in a direction opposite to the relative rotation; a leakage side groove having at least one end disposed closer to the leakage side space than the fluid side groove and the fluid side reverse groove, and extending from the end toward the fluid side space in the positive direction of relative rotation; a leak-side reverse groove having at least one end disposed closer to the leak-side space than the fluid-side groove and the fluid-side reverse groove, and extending from the end toward the fluid-side space in a direction opposite to the relative rotation; A deep groove partitions a fluid side area where the fluid side groove and the fluid side reverse groove are provided and
  • the lubricity between the sliding surfaces is improved mainly by the sealed fluid supplied between the sliding surfaces from the closed end of the fluid side groove.
  • the sealed fluid supplied between the sliding surfaces from the fluid side groove is collected in the deep groove, so the positive pressure in the fluid side groove is suppressed.
  • the lubricity between the sliding surfaces is improved mainly by the sealed fluid supplied between the sliding surfaces from the closed end of the fluid-side reverse groove.
  • the sealed fluid supplied between the sliding surfaces from the fluid-side reverse groove is collected in the deep groove, so positive pressure in the fluid-side reverse groove is suppressed.
  • the leakage side groove or the leakage side reverse groove prevents the sealed fluid from leaking into the leak side space.
  • the deep groove may communicate with the fluid side space. According to this, since the fluid enters and exits the deep groove from the fluid side space, the amount of the sealed fluid in the deep groove is stabilized.
  • Each leakage side end of the leakage side groove and the leakage side reverse groove may communicate with the leakage side space. According to this, the leakage side fluid can be efficiently introduced from the leakage side space into the leakage side groove during relative rotation in the forward direction, and the leakage side fluid can be efficiently introduced from the leakage side space into the leakage side reverse groove during relative rotation in the reverse direction. can be introduced.
  • the one sliding surface may be provided with a communication groove that communicates the leak side end portions of the leak side groove and the leak side reverse groove. According to this, during relative rotation in the positive direction, the fluid collected in the leakage side reverse groove can be guided to the leakage side groove through the communication groove, and during relative rotation in the reverse direction, the fluid collected in the leakage side groove can be guided to the communication groove. can be led to the reverse groove on the leakage side through
  • the communication groove may be annular. According to this, the fluid sucked into the leakage side groove or the leakage side reverse groove can be recovered by the annular communication groove, and the fluid in the annular communication groove can be guided to the leakage side groove or the leakage side reverse groove. Furthermore, since the land is formed on the leakage side of the deep annular groove, the fluid recovered in the communication groove is less likely to leak into the leakage side space.
  • the terminal end portions of the leakage side groove and the leakage side reverse groove may be arranged closer to the fluid side space than the terminal end portions of the fluid side groove and the fluid side reverse groove. According to this, the length of each groove can be sufficiently secured.
  • the deep groove has a first inclined portion extending along the fluid side groove and the leakage side reverse groove, and a second inclined portion extending along the fluid side reverse groove and the leakage side groove.
  • FIG. 1 is a longitudinal sectional view showing an example of a mechanical seal in Example 1 of the present invention
  • FIG. FIG. 4 is a view of the sliding surface of the stationary seal ring in Example 1 as seen from the axial direction; 4 is an enlarged view of the sliding surface of the stationary seal ring when the rotary seal ring rotates forward at low speed in Embodiment 1, as seen from the axial direction.
  • FIG. 4 is an enlarged view of the sliding surface of the stationary seal ring when the rotary seal ring rotates forward at high speed in Embodiment 1, viewed from the axial direction.
  • FIG. It is the figure which looked at the sliding surface of the stationary seal ring in Example 2 of this invention from the axial direction.
  • FIG. 11 is a view of the sliding surface of the stationary seal ring in Example 3 of the present invention as seen from the axial direction;
  • FIG. 11 is a view of the sliding surface of the stationary seal ring in Example 4 of the present invention, viewed from the axial direction;
  • FIG. 11 is a view of the sliding surface of the stationary seal ring in Example 5 of the present invention as seen from the axial direction; It is the schematic which shows the modification of a fluid side groove
  • FIG. 1 A sliding component according to Example 1 will be described with reference to FIGS. 1 to 4.
  • FIG. 1 a mechanical seal will be described as an example of a sliding component.
  • the atmosphere A exists in the inner space S1
  • the sealed fluid F exists in the outer space S2.
  • the outer diameter side will be described as the sealed fluid side (high pressure side).
  • dots may be attached to grooves formed on the sliding surface in the drawings.
  • the mechanical seal shown in FIG. 1 seals a sealed fluid F in an outer space S2 as a fluid-side space that tends to leak from the outer diameter side to the inner diameter side of the sliding surface, and seals the sealed fluid F in an inner space S1 as a leakage side space.
  • the sealed fluid F is a high-pressure liquid
  • the atmosphere A is a gas with a pressure lower than that of the sealed fluid F.
  • a mechanical seal is mainly composed of a stationary seal ring 10 and a rotary seal ring 20.
  • the stationary seal ring 10 has an annular shape and is provided in a non-rotating and axially movable state on a seal cover 5 fixed to a housing 4 of a device to which it is attached.
  • the rotary seal ring 20 has an annular shape and is provided on the rotary shaft 1 via the sleeve 2 so as to be rotatable together with the rotary shaft 1 .
  • the stationary seal ring 10 is urged in the axial direction by the elastic member 7, so that the sliding surface 11 of the stationary seal ring 10 and the sliding surface 21 of the rotary seal ring 20 closely slide against each other. .
  • the sliding surface 21 of the rotary seal ring 20 is a flat surface, and this flat surface is not provided with recesses such as grooves.
  • the stationary seal ring 10 and the rotary seal ring 20 are typically made of a combination of SiC (hard material) or SiC (hard material) and carbon (soft material). Any material that is used as a sliding material for mechanical seals can be applied.
  • SiC include sintered bodies using boron, aluminum, carbon, etc. as sintering aids, and materials composed of two or more phases with different components and compositions, such as SiC and SiC in which graphite particles are dispersed.
  • Metal materials, resin materials, surface modification materials (coating materials), composite materials, etc. are also applicable in addition to the sliding materials described above.
  • the rotating seal ring 20 which is the mating seal ring, rotates relative to the stationary seal ring 10 clockwise as indicated by solid arrows or counterclockwise as indicated by dashed arrows. It is designed to slide.
  • the direction indicated by the solid line arrow is the forward rotation direction of the rotary seal ring 20
  • the direction indicated by the broken line arrow is the reverse rotation direction of the rotary seal ring 20.
  • the sliding surface 11 of the stationary seal ring 10 has a plurality of fluid side spiral grooves 13 as fluid side grooves, a plurality of fluid side reverse spiral grooves 14 as fluid side reverse grooves, and a plurality of leakage side spiral grooves as leakage side grooves.
  • Grooves 15a to 15c, a plurality of leakage side reverse spiral grooves 16a to 16c as leakage side reverse grooves, and a plurality of deep grooves 17 are provided.
  • the spiral groove means that the extending direction of the groove has both a radial component and a circumferential component.
  • a plurality (three in this embodiment) of the fluid-side spiral grooves 13 are arranged in the circumferential direction on the outer diameter side of the sliding surface 11 .
  • the fluid-side spiral groove 13 communicates with the outer space S2 at its outer diameter side end portion 13A, and extends in the forward rotation direction of the rotary seal ring 20, that is, in one circumferential direction, based on the communication point.
  • the fluid-side spiral groove 13 is a spiral groove that extends in an arcuate shape from the outer diameter side toward the inner diameter side while being inclined with a clockwise component.
  • the end portion 13B on the inner diameter side of the fluid-side spiral groove 13 has a closed shape, that is, a closed end portion.
  • the fluid-side spiral groove 13 has a constant depth in the extending direction.
  • a plurality (three in this embodiment) of the fluid-side reverse spiral grooves 14 are arranged in the circumferential direction on the outer diameter side of the sliding surface 11 .
  • the fluid-side reverse spiral groove 14 communicates with the outer space S2 at its outer diameter side end portion 14A, and extends in the opposite direction of rotation of the rotary seal ring 20, that is, in the other circumferential direction, based on the communication point.
  • the fluid-side reverse spiral groove 14 is a spiral groove that extends in an arcuate shape while being inclined with a counterclockwise component from the outer diameter side to the inner diameter side.
  • the end portion 14B on the inner diameter side of the fluid-side reverse spiral groove 14 has a closed shape, that is, a closed end portion.
  • the fluid-side reverse spiral groove 14 has a constant depth in the extending direction.
  • the fluid-side spiral groove 13 and the fluid-side reverse spiral groove 14 have the same depth.
  • the fluid-side reverse spiral groove 14 is circumferentially symmetrical with the fluid-side spiral groove 13 .
  • a plurality of leak side spiral grooves 15a to 15c are arranged in the inner diameter side of the sliding surface 11 in the circumferential direction.
  • the leak-side ends of the leak-side spiral grooves 15a to 15c that is, the inner diameter-side end 15A, communicate with the inner space S1.
  • the leak-side spiral grooves 15a-15c extend substantially parallel to the fluid-side spiral groove 13. As shown in FIG.
  • the leak-side spiral grooves 15a to 15c are spiral grooves that extend in an arcuate direction from the inner diameter side to the outer diameter side while being inclined with a clockwise component. Further, the ends 15B on the outer diameter side of the leak side spiral grooves 15a to 15c are in a closed shape, that is, closed ends.
  • the leak side spiral grooves 15a to 15c have a constant depth in the extending direction.
  • the lengths of the three leak-side spiral grooves 15a to 15c are different.
  • the leak-side spiral groove 15a is longer than the leak-side spiral groove 15b, and the leak-side spiral groove 15b is longer than the leak-side spiral groove 15c.
  • the ends 15B of the leak side spiral grooves 15a to 15c are arranged side by side in the radial direction.
  • each end 15B of the leak-side spiral grooves 15a to 15c is arranged on the outer diameter side of the end 13B of the fluid-side spiral groove 13 and the end 14B of the fluid-side reverse spiral groove .
  • a plurality of leakage-side reverse spiral grooves 16a to 16c are arranged on the inner diameter side of the sliding surface 11 in the circumferential direction.
  • the leak-side reverse spiral grooves 16a to 16c communicate with the inner space S1 at their leak-side ends, ie, the inner diameter side end 16A, and rotate in the reverse rotation direction, ie, the circumferential direction, etc. extending in the direction
  • the leak-side reverse spiral grooves 16 a - 16 c extend substantially parallel to the fluid-side reverse spiral groove 14 .
  • the leak-side reverse spiral grooves 16a to 16c are spiral grooves extending in an arcuate direction from the inner diameter side to the outer diameter side while being inclined with a counterclockwise component. Further, the ends 16B on the outer diameter side of the leak-side reverse spiral grooves 16a to 16c are in a closed shape, that is, closed ends. In other words, the leak-side reverse spiral grooves 16a-16c and the leak-side spiral grooves 15a-15c are circumferentially symmetrical.
  • the leak-side reverse spiral grooves 16a to 16c have a constant depth in the extending direction.
  • the leakage side spiral grooves 15a to 15c and the leakage side reverse spiral grooves 16a to 16c have the same depth, and the leakage side spiral grooves 15a to 15c and the leakage side reverse spiral grooves 16a to 16c have the same depth. It is deeper than the spiral groove 13 and the reverse spiral groove 14 on the fluid side.
  • the capacities of the leak-side spiral grooves 15a-15c and the leak-side reverse spiral grooves 16a-16c are larger than the capacities of the fluid-side spiral groove 13 and the fluid-side reverse spiral groove .
  • the lengths of the leak-side reverse spiral grooves 16a to 16c are different.
  • the leak-side reverse spiral groove 16a is longer than the leak-side reverse spiral groove 16b, and the leak-side reverse spiral groove 16b is longer than the leak-side reverse spiral groove 16c.
  • the ends 16B of the leak-side reverse spiral grooves 16a-16c are arranged radially side by side.
  • each end 16B of the leak-side reverse spiral grooves 16a to 16c is arranged radially outside the end 13B of the fluid-side spiral groove 13 and the end 14B of the fluid-side reverse spiral groove 14.
  • the fluid-side spiral groove 13 and the fluid-side reverse spiral groove 14 facing each other so that the ends 13B and 14B approach each other in the circumferential direction are regarded as one set, and the respective ends 15B and 16B face each other in the circumferential direction as leakage-side spiral grooves.
  • the grooves 15a to 15c and the reverse spiral grooves 16a to 16c on the leak side are described as one set.
  • One set of leakage side spiral grooves 15a to 15c and leakage side reverse spiral grooves 16a to 16c are arranged between one set of fluid side spiral grooves 13 and another set of adjacent fluid side reverse spiral grooves 14 in the circumferential direction. are arranged.
  • a plurality of (three in this embodiment) deep grooves 17 are arranged in the sliding surface 11 in the circumferential direction.
  • the deep groove 17 has a constant depth in the extending direction.
  • the deep groove 17 is deeper than the leakage side spiral grooves 15a to 15c and the leakage side reverse spiral grooves 16a to 16c.
  • the depth of the deep groove 17 is such that the relative rotation between the stationary seal ring 10 and the rotary seal ring 20 causes almost no dynamic pressure.
  • the deep groove 17 communicates with the outer space S2 at both ends 17A and 17B in the circumferential direction, and extends so as to surround a pair of the fluid-side spiral groove 13 and the fluid-side reverse spiral groove 14 .
  • the deep groove 17 has a first portion 171 as a first inclined portion, a second portion 172 as a second inclined portion, and a third portion 173 .
  • the first portion 171 is a portion that extends between and substantially parallel to the fluid side spiral groove 13 and the leakage side reverse spiral grooves 16a to 16c.
  • the second portion 172 is a portion that extends substantially parallel between the fluid side reverse spiral groove 14 and the leakage side spiral grooves 15a to 15c.
  • the third portion 173 extends concentrically with the stationary seal ring 10 and connects the inner diameter ends of the first portion 171 and the second portion 172 .
  • the land 12 has a flat surface.
  • the flat surface of the land 12 functions as a sliding surface that substantially slides on the sliding surface 21 of the rotary seal ring 20 .
  • the sliding surface 11 is divided into a fluid side area A1 and a leakage side area A2 by a deep groove 17.
  • a set of fluid-side spiral grooves 13 and fluid-side reverse spiral grooves 14, and lands 12 partitioning them are provided in the fluid-side region A1.
  • the leak side area A2 is provided with all the leak side spiral grooves 15a to 15c and the leak side reverse spiral grooves 16a to 16c, and the land 12 that partitions them.
  • the leak side area A2 is an area of the sliding surface 11 other than the fluid side area A1.
  • the sealed fluid F moves to the end portion 13B, and positive pressure is generated at the end portion 13B and its vicinity.
  • the sealed fluid F moves to the end portion 14A, and a relative negative pressure is generated at and near the end portion 14B.
  • the air A moves to each end 15B, and positive pressure is generated at each end 15B and its vicinity.
  • the leak-side reverse spiral grooves 16a to 16c the air A moves to each end 16A, and a relative negative pressure is generated at each end 16B and its vicinity.
  • relative negative pressure refers to a state in which the pressure is lower than the ambient pressure, not in a vacuum state.
  • FIG. 3 the case where the rotary seal ring 20 rotates in the normal direction will be described as an example, and the explanation when the rotary seal ring 20 rotates in the reverse direction will be omitted.
  • FIGS. 3 and 4 for convenience of explanation, the range of positive pressure generated in each spiral groove is illustrated so as to be surrounded by a one-dot chain line.
  • the sealed fluid F flows into the fluid-side spiral groove 13 and the fluid-side reverse spiral groove 14 through the openings of the ends 13A and 14A. Further, the sealed fluid F flows into the deep groove 17 from the openings of the end portions 17A and 17B. Also, the atmosphere A flows into the leakage side spiral grooves 15a to 15c and the leakage side reverse spiral grooves 16a to 16c from the openings of the ends 15A and 16A. Since the stationary seal ring 10 is urged toward the rotary seal ring 20 by the elastic member 7, the sliding surfaces 11 and 21 are in contact with each other, and the fluid F to be sealed between the sliding surfaces 11 and 21 is kept in contact with each other. There is almost no amount of leaking into the inner space S1.
  • the fluid-side spiral groove 13 is filled with a sealed fluid F whose pressure is higher than the atmosphere A flowing into the leak-side spiral grooves 15a to 15c, and the fluid-side spiral groove 13 is a leak-side spiral groove. Since the capacities are smaller than those of 15a-15c, the first force due to the positive pressure generated at the end 13B of the fluid side spiral groove 13 is due to the positive pressure generated at each end 15B of the leak side spiral grooves 15a-15c. greater than the second force. Therefore, when the rotary seal ring 20 rotates at a low speed, the first force mainly acts to separate the sliding surfaces 11 and 21 from each other.
  • the sealed fluid F is supplied between the sliding surfaces 11 and 21 from the fluid-side spiral groove 13, and the sliding surfaces 11 and 21 are slightly spaced apart, so that lubricity is maintained even during low-speed rotation. is improved, and wear between the sliding surfaces 11 and 21 can be suppressed.
  • the sealed fluid F supplied to the fluid side area A1 on the sliding surface 11 is mainly sucked into the fluid side reverse spiral groove 14 as indicated by the arrow H1, and is partially sucked as indicated by the arrow H2. is collected in the deep groove 17. Further, since the floating distance between the sliding surfaces 11 and 21 is small, the sealed fluid F hardly flows into the leak side area A2 of the sliding surface 11 . Therefore, the sealed fluid F is suppressed from leaking into the inner space S1. In addition, when the amount of the sealed fluid F that can be stored in the deep groove 17 is recovered, the excess sealed fluid F is returned to the outer space S2.
  • the negative pressure generated at each end 16B of the leakage side reverse spiral grooves 16a to 16c and its vicinity is relatively small, and the leakage side spiral grooves 15a to 15c facing each other are
  • the positive pressure generated at each end 15B acts to push out most of the sealed fluid F flowing from the outer diameter side of the leak side area A2 to the outer space S2.
  • the sliding surfaces 11 and 21 are separated by the sealed fluid F supplied between the sliding surfaces 11 and 21 mainly from the end portion 13B of the fluid-side spiral groove 13 . lubricity is improved. Further, when the relative rotation of the mechanical seal is forward rotation at high speed, the sealed fluid F supplied between the sliding surfaces 11 and 21 from the fluid-side spiral groove 13 is collected in the deep groove 17. The positive pressure is suppressed, and the positive pressure generated mainly at the ends 15B of the leak-side spiral grooves 15a to 15c separates the sliding surfaces 11 and 21 from each other, thereby improving lubricity.
  • the sliding surface 11 also has a fluid-side reverse spiral groove 14 circumferentially symmetrical with the fluid-side spiral groove 13 and a leak-side reverse spiral groove circumferentially symmetrical with the leak-side spiral grooves 15a to 15c. Since 16a to 16c are provided, when the relative rotation of the mechanical seals is reversed, the same function as above is exhibited.
  • the sealed fluid F can be taken in and out between the deep groove 17 and the outer space S2, and the amount of the sealed fluid F in the deep groove 17 is stabilized. . That is, the sealed fluid F supplied between the sliding surfaces 11 and 21 from the fluid-side spiral groove 13 or the fluid-side reverse spiral groove 14 can be reliably recovered in the deep groove 17 .
  • the ends 15A, 16A of the leak-side spiral grooves 15a-15c and the leak-side reverse spiral grooves 16a-16c communicate with the inner space S1. According to this, when the mechanical seal rotates relative to the normal direction, the atmosphere A can be introduced from the inner space S1 into the leakage side spiral grooves 15a to 15c, and when the mechanical seal rotates in the opposite direction, the leakage side reverse spiral grooves 15a to 15c can be introduced from the inner space S1. Since the atmosphere A can be introduced into the grooves 16a to 16c, positive pressure can be stably generated in the leak side spiral grooves 15a to 15c and the leak side reverse spiral grooves 16a to 16c.
  • each end 15B of the leakage side spiral grooves 15a to 15c and each end 16B of the leakage side reverse spiral grooves 16a to 16c are connected to the end 13B of the fluid side spiral groove 13 and the end 14B of the fluid side reverse spiral groove 14. It is arranged on the outer diameter side, that is, on the outer space S2 side. According to this, the length of each spiral groove can be sufficiently secured.
  • the deep groove 17 has a first portion 171 extending along the fluid side spiral groove 13 and the leakage side reverse spiral grooves 16a to 16c, and a first portion 171 extending along the fluid side reverse spiral groove 14 and the leakage side spiral grooves 15a to 15c.
  • the spiral grooves can be efficiently arranged in the circumferential direction.
  • An annular land 18 is provided on the inner diameter side edge of the sliding surface 111 of the stationary seal ring 100 of the second embodiment.
  • An annular deep groove 117 as a communication groove is formed concentrically with the stationary seal ring 100 on the outer diameter side of the annular land 18 .
  • the annular deep groove 117 and the third portion 173 of the deep groove 17 are separated by the land 112 forming the leak side area A20.
  • the annular deep groove 117 is formed to a depth that hardly generates dynamic pressure due to the relative rotation of the mechanical seal.
  • leakage side spiral grooves 151a to 151c and leakage side reverse spiral grooves 161a to 161c are provided on the outer diameter side of this annular deep groove 117.
  • Each end 151A of the leakage side spiral grooves 151a to 151c and each end 161A of the leakage side reverse spiral grooves 161a to 161c communicate with the annular deep groove 117.
  • the configuration other than the above is the same as that of the first embodiment.
  • the sealed fluid F collected in the leakage side reverse spiral grooves 161a to 161c can be guided to the leakage side spiral grooves 151a to 151c through the annular deep groove 117. Further, when the mechanical seal rotates in the reverse direction, the sealed fluid F collected in the leak-side spiral grooves 151a-151c can be led through the annular deep groove 117 to the leak-side reverse spiral grooves 161a-161c. Therefore, the sealed fluid F collected in the leakage side spiral grooves 151a to 151c and the leakage side reverse spiral grooves 161a to 161c hardly leaks into the inner space S1.
  • annular deep groove 117 can recover the sealed fluid F from portions other than the leakage side spiral grooves 151a to 151c and the leakage side reverse spiral grooves 161a to 161c, that is, the lands 112 forming the leakage side area A20.
  • annular land 18 is formed on the inner diameter side of the annular deep groove 117 .
  • the sealed fluid F collected in the annular deep groove 117 is less likely to leak into the inner space S1.
  • the deep groove and the annular communication groove are partitioned by the land, but the deep groove and the annular communication groove may communicate with each other.
  • Two fluid-side spiral grooves 213a and 213b and two fluid-side reverse spiral grooves 214a and 214b are provided in the fluid-side region A10 of the sliding surface 211 of the stationary seal ring 200 of the third embodiment. ing.
  • the fluid-side spiral groove 213a is longer than the fluid-side spiral groove 213b.
  • the fluid-side spiral groove 213a is arranged side by side in the reverse rotation direction of the rotary seal ring 20 of the fluid-side spiral groove 213b.
  • the fluid-side reverse spiral groove 214a is longer than the fluid-side reverse spiral groove 214b and has the same length as the fluid-side spiral groove 213a.
  • the fluid-side reverse spiral groove 214a is arranged side by side in the forward rotation direction of the rotary seal ring 20 of the fluid-side reverse spiral groove 214b.
  • fluid-side spiral groove 213b and the fluid-side reverse spiral groove 214b have the same length.
  • the configuration other than the above is the same as that of the second embodiment.
  • the sliding surface 311 of the stationary seal ring 300 of Embodiment 4 is provided with a deep groove 317 continuous in the circumferential direction.
  • the deep groove 317 has a first portion 317a, a second portion 317b, a third portion 317c, and a fourth portion 317d.
  • the first portion 317a is a portion extending substantially parallel between the fluid side spiral groove 13 and the leakage side reverse spiral grooves 161a to 161c.
  • the outer diameter end of the first portion 317a does not communicate with the outer space S2.
  • the second portion 317b is a portion extending substantially parallel between the fluid side reverse spiral groove 14 and the leak side spiral grooves 151a to 151c.
  • the outer diameter end of the second portion 317b does not communicate with the outer space S2.
  • the third portion 317c extends concentrically with the stationary seal ring 300 and connects the inner diameter ends of the first portion 317a and the second portion 317b.
  • the fourth portion 317d extends concentrically with the stationary seal ring 300 and connects the outer diameter ends of the first portion 317a and the second portion 317b.
  • the endless deep groove 317 is arranged between the leak side area A20′ and the outer space S2, the amount of the sealed fluid F flowing into the leak side area A20′ is small. Leakage of the sealed fluid F to S1 can be reduced as much as possible.
  • the mechanical seal of the fifth embodiment is of an outside type in which the sealed fluid F in the inner space S1 is sealed and the outer space S2 communicates with the atmosphere A. That is, in the fifth embodiment, the inner space S1 functions as a fluid side space, and the outer space S2 functions as a leak side space.
  • the sliding surface 411 of the stationary seal ring 400 of the fifth embodiment is provided with an annular land 18' on its outer diameter side edge.
  • An annular deep groove 117' is formed as a communication groove on the inner diameter side of the annular land 18'.
  • Four deep grooves 417 having both ends communicating with the inner space S1 are provided in the circumferential direction on the inner diameter side of the annular deep groove 117'.
  • the deep groove 417 does not communicate with the outer space S2.
  • a fluid-side spiral groove 413 and a fluid-side reverse spiral groove 414 are provided in the fluid-side region A100.
  • the leakage side region A200 is provided with leakage side spiral grooves 451a to 451c and leakage side reverse spiral grooves 461a to 461c.
  • the leak-side spiral grooves 451a-451c and the leak-side reverse spiral grooves 461a-461c communicate with the annular deep groove 117' and extend radially inward.
  • the fluid side groove and the fluid side reverse groove are directly connected to the fluid side space.
  • a fluid side groove 513 extends from the first portion 171 in one circumferential direction concentrically with the stationary seal ring 500, and a fluid side reverse groove 514 extends from the second portion 172 of the deep groove 17 in the other circumferential direction concentrically with the stationary seal ring 500. May be extended.
  • the fluid side groove 513 and the fluid side reverse groove 514 may communicate with the outer space S2, that is, the fluid side space through the deep groove 17 .
  • the fluid side groove 513 and the fluid side reverse groove 514 may not have a radial component, that is, they may not be spiral grooves.
  • Example 1 to 5 the fluid side groove and the fluid side reverse groove are symmetrical, and the leakage side groove and the leakage side reverse groove are symmetrical.
  • the form in which negative pressure is generated has been exemplified, it is not limited to this, and each groove is made asymmetrical so that positive pressure and relative negative pressure are generated differently in the positive direction and the reverse direction of relative rotation. good too.
  • the communication grooves communicating the leakage side ends of the leakage side groove and the leakage side reverse groove are deep grooves. It may be a shallow groove having a depth of
  • the form in which the communicating groove is annular was exemplified. good.
  • the communication groove is not limited to an arc shape, and may extend in a sine wave shape or in a straight line shape.
  • each groove and deep groove may be freely changed.
  • the fluid side groove and the leakage side reverse groove, and the fluid side reverse groove and the leakage side groove have substantially the same degree of inclination in the circumferential direction when viewed from the axial direction. may have different degrees of inclination to .
  • the grooves are provided in the stationary seal ring, but the grooves may be provided in the rotary seal ring.
  • each groove has a constant depth in the extending direction, but a step or an inclined surface may be formed on the bottom surface of the groove.
  • the fluid side groove and the fluid side reverse groove are shallower than the leakage side groove and the leakage side reverse groove, and the capacity is small.
  • the capacity may be formed to the same extent as the depth and capacity of the leakage side groove and the leakage side reverse groove.
  • the sealed fluid side is assumed to be the high pressure side and the leakage side is assumed to be the low pressure side, the sealed fluid side may be the low pressure side and the leakage side may be the high pressure side. It may be the same pressure.
  • the sealed fluid F is described as a high-pressure liquid, but it is not limited to this, and may be a gas or a low-pressure liquid. good too.
  • the fluid on the leak side is explained to be the atmosphere A, which is a low-pressure gas. It may be in the form of a mist.
  • stationary seal ring 11 sliding surface 12 land 13 fluid side spiral groove (fluid side groove) 13A end 13B end (terminal) 14 fluid side reverse spiral groove (fluid side reverse groove) 14A end 14B end (terminal) 15A end 15B end (terminal end, leak side end) 15a to 15c leak side spiral groove (leak side groove) 16A end 16B end (terminal) 16a to 16c Leakage side reverse spiral groove (leakage side reverse groove) 17 deep groove 18 annular land 20 rotary seal ring 21 sliding surface 117 annular deep groove A atmosphere A1 fluid side area A2 leak side area F sealed fluid S1 inner space (leak side space) S2 outer space (fluid side space)

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Sealing (AREA)
PCT/JP2022/034390 2021-09-28 2022-09-14 摺動部品 Ceased WO2023053964A1 (ja)

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EP22875835.5A EP4411182A4 (en) 2021-09-28 2022-09-14 SLIDING COMPONENT
CN202280063523.3A CN117980636A (zh) 2021-09-28 2022-09-14 滑动部件
US18/695,302 US12404936B2 (en) 2021-09-28 2022-09-14 Sliding component
KR1020247010305A KR20240052031A (ko) 2021-09-28 2022-09-14 슬라이딩 부품
JP2023551293A JP7846126B2 (ja) 2021-09-28 2022-09-14 摺動部品

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WO2026083929A1 (ja) * 2024-10-18 2026-04-23 イーグル工業株式会社 摺動部品

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