WO2016140056A1 - Bague d'étanchéité - Google Patents

Bague d'étanchéité Download PDF

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Publication number
WO2016140056A1
WO2016140056A1 PCT/JP2016/054451 JP2016054451W WO2016140056A1 WO 2016140056 A1 WO2016140056 A1 WO 2016140056A1 JP 2016054451 W JP2016054451 W JP 2016054451W WO 2016140056 A1 WO2016140056 A1 WO 2016140056A1
Authority
WO
WIPO (PCT)
Prior art keywords
groove
seal ring
peripheral surface
shaft
housing
Prior art date
Application number
PCT/JP2016/054451
Other languages
English (en)
Japanese (ja)
Inventor
渉 ▲徳▼永
Original Assignee
Nok株式会社
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 Nok株式会社 filed Critical Nok株式会社
Priority to JP2017503401A priority Critical patent/JP6170271B2/ja
Publication of WO2016140056A1 publication Critical patent/WO2016140056A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings

Definitions

  • the present invention relates to a seal ring that seals an annular gap between a shaft and a shaft hole of a housing.
  • a seal ring that seals the annular gap between the relatively rotating shaft and the housing in order to maintain the hydraulic pressure.
  • This seal ring is mounted in an annular groove provided on the outer periphery of the shaft, and seals against the side wall surface of the annular groove and the inner peripheral surface of the shaft hole provided in the housing, thereby sealing the annular gap. Stop.
  • An object of the present invention is to provide a seal ring that is not affected by the eccentricity of the shaft relative to the housing and that reduces the rotational torque.
  • the present invention employs the following means in order to solve the above problems.
  • the seal ring of the present invention is Fluid pressure in a region to be sealed, which is mounted in an annular groove provided on the outer periphery of the shaft, and is configured to seal the annular gap between the shaft and the housing that rotate relatively to change the fluid pressure.
  • a dynamic pressure generating groove having a groove is provided.
  • the fluid to be sealed is guided into the dynamic pressure generating groove, the fluid pressure acting on the seal ring from the inner peripheral surface side in the range where the dynamic pressure generating groove is provided The fluid pressure acting on the seal ring from the outer peripheral surface side is canceled out. Thereby, the pressure receiving area of the fluid pressure with respect to the seal ring can be reduced. Further, when the seal ring slides on the inner peripheral surface of the shaft hole provided in the housing, dynamic pressure is generated when the fluid to be sealed flows from the first groove to the sliding portion. Thereby, the force of the direction away from the inner peripheral surface of a shaft hole generate
  • the dynamic pressure generating groove includes a first groove and a second groove extending from the center position in the circumferential direction of the first groove to the side surface on the sealing target region side. Accordingly, the dynamic pressure is generated regardless of the rotation direction of the seal ring with respect to the housing.
  • the dynamic pressure generating groove is provided on the outer peripheral surface side of the seal ring, it is not affected by the eccentricity of the shaft with respect to the housing. Accordingly, the design flexibility is greater when the dynamic pressure generating groove is formed on the outer peripheral surface side of the seal ring than when the dynamic pressure generating groove is formed on the side surface side of the seal ring.
  • the first groove may be configured to have a constant groove width and extend in the circumferential direction.
  • the groove bottom of the first groove is configured so that both ends are shallower than the center in the circumferential direction.
  • the rotational torque can be reduced without being affected by the eccentricity of the shaft with respect to the housing.
  • FIG. 1 is a side view of a seal ring according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged view of a side view of the seal ring according to the embodiment of the present invention.
  • FIG. 3 is a partially enlarged view of a side view of the seal ring according to the embodiment of the present invention.
  • FIG. 4 is a partially enlarged view of the seal ring according to the embodiment of the present invention as viewed from the outer peripheral surface side.
  • FIG. 5 is a partially enlarged view of the seal ring according to the embodiment of the present invention as viewed from the inner peripheral surface side.
  • FIG. 6 is a partially enlarged view of the seal ring according to the embodiment of the present invention as viewed from the outer peripheral surface side.
  • FIG. 1 is a side view of a seal ring according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged view of a side view of the seal ring according to the embodiment of the present invention.
  • FIG. 3 is a
  • FIG. 7 is a schematic cross-sectional view of a seal ring according to an embodiment of the present invention.
  • FIG. 8 is a schematic cross-sectional view showing a state in use of the seal ring according to the embodiment of the present invention.
  • FIG. 9 is a schematic cross-sectional view showing a state in use of the seal ring according to the embodiment of the present invention.
  • FIG. 10 is a schematic cross-sectional view of a seal ring according to Modification 1 of the present invention.
  • FIG. 11 is a schematic cross-sectional view of a seal ring according to Modification 2 of the present invention.
  • FIG. 12 is a schematic cross-sectional view of a seal ring according to Modification 3 of the present invention.
  • the seal ring according to the present embodiment is used for sealing an annular gap between a relatively rotating shaft and a housing in order to maintain hydraulic pressure in a transmission such as an AT or CVT for automobiles. It is used.
  • high pressure side means a side that becomes high when differential pressure occurs on both sides of the seal ring
  • low pressure side means that differential pressure occurs on both sides of the seal ring. This means the side that is at low pressure.
  • FIG. 1 is a side view of a seal ring according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged view of a side view of the seal ring according to the embodiment of the present invention, and is an enlarged view of a circled portion in FIG.
  • FIG. 3 is a partially enlarged view of a side view of the seal ring according to the embodiment of the present invention, and is an enlarged view of a circled portion in FIG. 1 as viewed from the opposite side.
  • 4 is a partially enlarged view of the seal ring according to the embodiment of the present invention as viewed from the outer peripheral surface side, and is an enlarged view of the circled portion in FIG.
  • FIG. 5 is a partially enlarged view of the seal ring according to the embodiment of the present invention as viewed from the inner peripheral surface side.
  • FIG. 5 is an enlarged view of the circled portion in FIG. 1 as viewed from the inner peripheral surface side.
  • 6 is a partially enlarged view of the seal ring according to the embodiment of the present invention as seen from the outer peripheral surface side.
  • FIG. 1 is an enlarged view of the portion other than the circled portion in FIG. is there.
  • FIG. 7 is a schematic cross-sectional view of a seal ring according to an embodiment of the present invention, and is a cross-sectional view taken along AA in FIG.
  • FIG. 8 and 9 are schematic cross-sectional views showing a state in use of the seal ring according to the embodiment of the present invention.
  • 8 shows a no-load state
  • FIG. 9 shows a state where a differential pressure is generated.
  • 8 and 9 corresponds to the BB cross-sectional view in FIG. 10 to 12 are schematic cross-sectional views of seal rings according to modifications of the present invention, showing examples in which the shape of the dynamic pressure generating groove is different.
  • the seal ring 100 is mounted in an annular groove 210 provided on the outer periphery of the shaft 200, and rotates relative to the shaft 200 and the housing 300 (the inner periphery of the shaft hole through which the shaft 200 in the housing 300 is inserted.
  • the annular gap between the first and second surfaces is sealed.
  • the seal ring 100 maintains the fluid pressure in the region to be sealed configured so that the fluid pressure (hydraulic pressure in this embodiment) changes.
  • the fluid pressure in the region on the right side in FIGS. 8 and 9 is configured to change, and the seal ring 100 serves to maintain the fluid pressure in the region to be sealed on the right side in the drawings. Is responsible.
  • FIG. 9 shows a state in which the fluid pressure on the right side in the drawing is higher than the fluid pressure on the left side.
  • the right side in FIG. 9 is referred to as a high pressure side (H)
  • the left side is referred to as a low pressure side (L).
  • the seal ring 100 is made of a resin material such as polyetheretherketone (PEEK), polyphenylene sulfide (PPS), polytetrafluoroethylene (PTFE). Further, the peripheral length of the outer peripheral surface of the seal ring 100 is configured to be shorter than the peripheral length of the inner peripheral surface of the shaft hole of the housing 300 and is configured not to have a tightening allowance. Therefore, when the fluid pressure is not acting, the outer peripheral surface of the seal ring 100 can be separated from the inner peripheral surface of the shaft hole of the housing 300.
  • PEEK polyetheretherketone
  • PPS polyphenylene sulfide
  • PTFE polytetrafluoroethylene
  • the seal ring 100 is provided with an abutment portion 110 at one place in the circumferential direction.
  • a dynamic pressure generating groove 120 is provided on the outer peripheral surface side of the seal ring 100.
  • the seal ring 100 according to the present embodiment has a configuration in which the above-described joint portion 110 and a plurality of dynamic pressure generating grooves 120 are formed on an annular member having a rectangular cross section.
  • this is merely an explanation of the shape, and does not necessarily mean that the annular member having a rectangular cross section is used as a material, and the joint portion 110 and the plurality of dynamic pressure generating grooves 120 are formed. .
  • a plurality of dynamic pressure generating grooves 120 may be obtained by cutting after forming a joint portion 110 in advance, and the manufacturing method is not particularly limited.
  • the configuration of the abutment portion 110 according to the present embodiment will be described with reference to FIGS. 2 to 5 in particular.
  • the joint part 110 according to the present embodiment employs a special step cut cut in a step shape when viewed from either the outer peripheral surface side or both side wall surfaces.
  • the first fitting convex portion 111 and the first fitting concave portion 114 are provided on the outer peripheral surface side on one side via the cutting portion, and the outer peripheral surface side on the other side is provided.
  • a second fitting concave portion 113 into which the first fitting convex portion 111 is fitted and a second fitting convex portion 112 to be fitted into the first fitting concave portion 114 are provided.
  • the end surface 115 on the inner peripheral surface side on one side and the end surface 116 on the inner peripheral side on the other side face each other through the cutting portion.
  • the “cutting portion” includes not only the case of being cut by cutting, but also the case of being obtained by molding.
  • the case of the special step cut is shown as an example of the abutment portion 110, but the abutment portion 110 is not limited to this, and a straight cut, a bias cut, a step cut, or the like may be employed.
  • a low-elasticity material such as PTFE
  • the end portion may be provided without providing the joint portion 110.
  • a plurality of dynamic pressure generating grooves 120 are provided at equal intervals over the entire circumference except for the vicinity of the joint 110 on the outer circumferential surface of the seal ring 100.
  • the plurality of dynamic pressure generating grooves 120 are provided to generate dynamic pressure when the seal ring 100 slides with respect to the inner peripheral surface of the shaft hole provided in the housing 300.
  • the dynamic pressure generating groove 120 has a groove width (axial direction (vertical direction in FIG. 6)) constant and extends in the circumferential direction, and is sealed from the circumferential center position of the first groove 121.
  • the second groove 122 extends to the side of the region side (the high pressure side (H) in FIG. 9) and guides the fluid to be sealed into the first groove 121.
  • the groove depth of the first groove 121 is configured to be constant in the axial direction (see FIGS. 8 and 9). And about the groove depth of the 1st groove
  • the groove bottom surface of the first groove 121 is configured by a flat inclined surface that is inclined so as to gradually become shallower from the center in the circumferential direction toward the end. .
  • various configurations can be adopted for the shape of the groove bottom surface of the first groove 121. For example, as shown in FIG.
  • the groove bottom surface of the first groove 121 can be configured by a curved inclined surface that is inclined so as to gradually become shallower from the center in the circumferential direction toward the end.
  • channel 121 can also be comprised so that it may become shallow toward an edge part in the step shape from the center of the circumferential direction.
  • the groove bottom of the first groove 121 may become shallower from the center in the circumferential direction toward the end in a stepped manner, and the stepped portion may be formed by an inclined surface.
  • the groove bottom of the first groove 121 is configured such that both ends are shallower than the center in the circumferential direction, so that dynamic pressure can be generated more effectively by the wedge effect.
  • FIG. 9 shows a state in which the engine is started and a differential pressure is generated via the seal ring 100 (a state in which the pressure on the right side in the figure is higher than the pressure on the left side).
  • the seal ring 100 is in close contact with the low-pressure side (L) side wall surface 211 of the annular groove 210 and the inner peripheral surface of the shaft hole of the housing 300.
  • the annular gap between the relatively rotating shaft 200 and the housing 300 is sealed, and the fluid pressure in the region to be sealed (the region on the high pressure side (H)) configured to change the fluid pressure.
  • the shaft 200 and the housing 300 rotate relatively, the shaft 200 slides between the inner peripheral surface of the shaft hole of the housing 300 and the outer peripheral surface of the seal ring 100.
  • dynamic pressure is generated when the fluid to be sealed flows out from the dynamic pressure generating groove 120 provided on the outer peripheral surface of the seal ring 100 to the sliding portion.
  • the seal ring 100 rotates in the clockwise direction in FIG. 7 with respect to the annular groove 210
  • the fluid to be sealed flows out from the end portion of the first groove 121 on the counterclockwise direction side to the sliding portion.
  • the seal ring 100 rotates counterclockwise in FIG. 7 with respect to the annular groove 210, the fluid to be sealed flows out from the end portion on the clockwise direction side of the first groove 121 to the sliding portion.
  • a combination of the decrease in the pressure receiving area and the generation of a force in the direction away from the inner peripheral surface of the shaft hole due to the dynamic pressure causes the rotational torque (sliding torque).
  • the reduction in rotational torque (sliding torque) can be realized, so that heat generated by sliding can be suppressed, and the seal ring 100 according to the present embodiment can be suitably used even under high-speed and high-pressure environmental conditions. It becomes possible. Accordingly, a soft material such as aluminum can be used as the material of the shaft 200.
  • the dynamic pressure generating groove 120 includes a first groove 121 and a second groove 122 extending from the center position in the circumferential direction of the first groove 121 to the side surface on the sealing target region side. Accordingly, the dynamic pressure is generated regardless of the rotation direction of the seal ring 100 with respect to the housing 300.
  • the dynamic pressure generating groove 120 is provided on the outer peripheral surface side of the seal ring 100, it is not affected by the eccentricity of the shaft 200 with respect to the housing 300. Accordingly, compared to the case where the dynamic pressure generating groove 120 is formed on the side surface side of the seal ring 100, the design flexibility is greater when the dynamic pressure generating groove 120 is formed on the outer peripheral surface side of the seal ring 100. large. That is, when the dynamic pressure generating groove is formed on the side surface side of the seal ring 100, the dynamic pressure generating groove is provided on the outer peripheral surface of the shaft 200 (the annular groove 210 is provided in consideration of the eccentricity of the shaft 200.
  • the outer peripheral surface of the non-exposed portion) and the inner peripheral surface of the shaft hole of the housing 300 must be prevented from jumping out.
  • the dynamic pressure generating groove 120 is formed on the outer peripheral surface side of the seal ring 100, such a consideration is not necessary. Thereby, the groove width of the 1st groove
  • the first groove 121 is configured to have a constant groove width and extend in the circumferential direction.
  • the effect of reducing the pressure receiving area described above can be enhanced, and the range of the fluid to be sealed that flows out from the first groove 121 to the sliding portion can be widened.
  • the groove width of the first groove 121 is tapered from the center in the circumferential direction toward both ends.
  • there is little effect of reducing the pressure receiving area and there is a concern that the range of the fluid to be sealed that flows out from the first groove 121 to the sliding portion becomes narrow.
  • the groove bottom of the first groove 121 is configured to be shallower at both ends compared to the center in the circumferential direction. By doing so, the dynamic pressure can be effectively generated by the wedge effect.
  • the second groove 122 is configured to reach one side surface of the seal ring 100 for all the dynamic pressure generating grooves 120.
  • a dynamic pressure generating groove having a second groove configured to reach one side surface of the seal ring 100 and a dynamic pressure generating having a second groove configured to reach the other side surface of the seal ring 100 are provided.
  • a configuration in which the grooves are alternately provided in the circumferential direction may be employed. Further, in this case, there is an advantage that the effect of the dynamic pressure generating groove is exhibited even in an environment in which the high pressure side (H) and the low pressure side (L) are alternately switched left and right in FIGS. is there.

Abstract

L'invention concerne une bague d'étanchéité qui n'est pas perturbée par l'excentricité d'un arbre par rapport à une enveloppe et qui réduit le couple de rotation. L'invention concerne une bague d'étanchéité montée dans une gorge annulaire située dans la périphérie extérieure d'un arbre, la bague d'étanchéité fermant hermétiquement l'espace annulaire entre l'arbre et une enveloppe, qui tournent l'un par rapport à l'autre, et maintenant la pression de fluide dans une région devant être enfermée hermétiquement, la région étant configurée de sorte que la pression de fluide change. La bague d'étanchéité est configurée de sorte que la bague d'étanchéité coulisse sur la surface périphérique intérieure d'un trou d'arbre qui est situé dans l'enveloppe et au travers duquel passe l'arbre. La bague d'étanchéité est caractérisée par le fait que la surface périphérique extérieure de la bague d'étanchéité est pourvue d'une gorge de production de pression dynamique comportant une première gorge s'étendant circonférentiellement (121) et une deuxième gorge (122) qui s'étend à partir du centre circonférentiel de la première gorge (121) jusqu'à une surface latérale sur le côté de la région à enfermer hermétiquement et qui conduit le fluide à enfermer hermétiquement, dans la première gorge (121).
PCT/JP2016/054451 2015-03-03 2016-02-16 Bague d'étanchéité WO2016140056A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2017503401A JP6170271B2 (ja) 2015-03-03 2016-02-16 シールリング

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015041145 2015-03-03
JP2015-041145 2015-03-03

Publications (1)

Publication Number Publication Date
WO2016140056A1 true WO2016140056A1 (fr) 2016-09-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/054451 WO2016140056A1 (fr) 2015-03-03 2016-02-16 Bague d'étanchéité

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JP (1) JP6170271B2 (fr)
WO (1) WO2016140056A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3299681A4 (fr) * 2015-10-15 2019-02-27 Kabushiki Kaisha Riken Bague d'étanchéité

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10318375A (ja) * 1997-05-15 1998-12-04 Ntn Corp 回転体用シールリング
JPH11336900A (ja) * 1998-05-27 1999-12-07 Toyota Motor Corp ピストンリング
JP5545420B1 (ja) * 2012-08-21 2014-07-09 Ｎｏｋ株式会社 シールリング

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10318375A (ja) * 1997-05-15 1998-12-04 Ntn Corp 回転体用シールリング
JPH11336900A (ja) * 1998-05-27 1999-12-07 Toyota Motor Corp ピストンリング
JP5545420B1 (ja) * 2012-08-21 2014-07-09 Ｎｏｋ株式会社 シールリング

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3299681A4 (fr) * 2015-10-15 2019-02-27 Kabushiki Kaisha Riken Bague d'étanchéité
US11028925B2 (en) 2015-10-15 2021-06-08 Kabushiki Kaisha Riken Seal ring

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Publication number Publication date
JPWO2016140056A1 (ja) 2017-06-15
JP6170271B2 (ja) 2017-07-26

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