WO2019004268A1 - シールリング - Google Patents
シールリング Download PDFInfo
- Publication number
- WO2019004268A1 WO2019004268A1 PCT/JP2018/024323 JP2018024323W WO2019004268A1 WO 2019004268 A1 WO2019004268 A1 WO 2019004268A1 JP 2018024323 W JP2018024323 W JP 2018024323W WO 2019004268 A1 WO2019004268 A1 WO 2019004268A1
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- WO
- WIPO (PCT)
- Prior art keywords
- seal ring
- dynamic pressure
- housing
- groove
- pressure
- Prior art date
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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
- F16J15/44—Free-space packings
- F16J15/441—Free-space packings with floating ring
-
- 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
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
-
- 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
- F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
- F16J15/48—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings influenced by the pressure within the member to be sealed
-
- 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
-
- 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
- F16J15/26—Sealings between relatively-moving surfaces with stuffing-boxes for rigid sealing rings
-
- 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
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3244—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with hydrodynamic pumping action
-
- 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
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3268—Mounting of sealing rings
- F16J15/3272—Mounting of sealing rings the rings having a break or opening, e.g. to enable mounting on a shaft otherwise than from a shaft end
Definitions
- the present invention relates to a seal ring for sealing an annular gap between a shaft and a shaft hole of a housing.
- a seal ring is provided to seal an annular gap between the relatively rotating shaft and the housing in order to hold the hydraulic pressure.
- fuel efficiency has been promoted as a countermeasure against environmental problems, and in the above-mentioned seal ring, there is an increasing demand to reduce rotational torque. Therefore, conventionally, measures have been taken to reduce the contact area of the sliding portion between the side surface of the annular groove to which the seal ring is mounted and the seal ring.
- a seal ring according to such a conventional example will be described with reference to FIG.
- FIG. 10 is a schematic cross-sectional view showing a state of use of a seal ring according to a conventional example.
- the seal ring 300 according to the conventional example is mounted in an annular groove 510 provided on the outer periphery of the shaft 500.
- the seal ring 300 is in close contact with the inner peripheral surface 610 of the shaft hole of the housing 600 into which the shaft 500 is inserted, and is slidably in contact with the side wall surface of the annular groove 510.
- An annular gap between the shaft and the bore is sealed.
- a pair of recessed portions 311 and 312 extending in the circumferential direction are provided on the inner peripheral surface side of both side surfaces.
- the seal ring 300 is axially directed from the high pressure side (in the illustrated example, the area (P) side) to the low pressure side (in the illustrated example, the area (Q) side) by the fluid to be sealed.
- the effective pressure receiving area at the time of being pressed is the area shown by T0 in FIG. That is, in the side surface of the seal ring 300, the radial area of the portion where the concave portions 311 and 312 are not provided is the effective pressure receiving area T0.
- an effective pressure receiving area when the seal ring 300 is pressed radially outward from the inner peripheral surface toward the outer peripheral surface by the fluid to be sealed is an area indicated by H0 in FIG. That is, the thickness in the axial direction of the seal ring 300 is an effective pressure receiving area H0. The area over the entire circumference of the pressure receiving area H0 is the pressure receiving area in the radial direction.
- the contact area of seal ring 300 with the side wall surface of annular groove 510 is the area indicated by U 0 in FIG.
- seal ring 300 is a side surface on the low pressure side, and among the portions where recess 312 is not provided, only the portion excluding the portion exposed to the gap between shaft 500 and housing 600 is annular groove 510.
- the contact area U 0 in the seal ring 300 is influenced by the dimension of the gap between the shaft 500 and the housing 600 and the dimension of the chamfer provided in the annular groove 510. Therefore, depending on the use environment, the contact area of the seal ring 300 with the side wall surface of the annular groove 510 may be excessively reduced, and the sealing performance may be reduced. In addition, there is a problem that the contact area changes depending on the use environment, and the sealing property is not stable.
- An object of the present invention is to provide a seal ring in which the sealing property is stabilized while reducing the rotational torque.
- the present invention adopts the following means in order to solve the above problems.
- the seal ring of the present invention is A fluid pressure of a seal target area which is attached to an annular groove provided on an outer periphery of a shaft and seals an annular gap between the relatively rotating shaft and the housing to change a fluid pressure.
- the seal ring that holds A seal ring which is in close contact with the side wall surface on the low pressure side of the annular groove and slides on the inner peripheral surface of an axial hole through which the shaft in the housing is inserted
- a first dynamic pressure is provided extending from the center of the axial width to the side surface on one side to the side surface on one side, and generating a dynamic pressure as the housing and the seal ring rotate relative to each other Generation groove
- a second dynamic pressure which is provided so as to extend from the center of the axial width to the side surface on the other side to the side surface on the other side, and generates a dynamic pressure as the housing and the seal ring relatively rotate.
- a plurality of generating grooves are provided at intervals in the circumferential direction.
- the seal ring is in close contact with the side wall surface on the low pressure side of the annular groove and configured to slide relative to the inner peripheral surface of the axial hole of the housing.
- the area of the sliding portion can be stabilized regardless of the size of the annular gap. Therefore, the sealing performance can be stabilized.
- the first dynamic pressure generating groove and the second dynamic pressure generating groove are provided on the outer peripheral surface side of the seal ring, it is possible to reduce the sliding resistance and to reduce the rotational torque.
- the side surface on the upstream side in the relative rotational direction of the seal ring with respect to the housing is constituted by an inclined surface whose depth gradually decreases toward the upstream side
- the side surface on the upstream side in the relative rotational direction of the seal ring with respect to the housing may also be formed by an inclined surface whose depth gradually decreases toward the upstream side.
- a plurality of projections projecting radially inward may be provided on the inner peripheral surface side of the seal ring at intervals in the circumferential direction.
- the sealing performance can be stabilized while reducing the rotational torque.
- FIG. 1 is a side view of a seal ring according to an embodiment of the present invention.
- FIG. 2 is a part of a view seen from the outer peripheral surface side of the seal ring according to the embodiment of the present invention.
- FIG. 3 is a partially enlarged view of the side view of the seal ring according to the embodiment of the present invention.
- FIG. 4 is a schematic sectional view showing a use state of the seal ring according to the embodiment of the present invention.
- FIG. 5 is a schematic cross-sectional view showing a use state of the seal ring according to the embodiment of the present invention.
- FIG. 6 is a schematic cross-sectional view showing a use state of the seal ring according to the embodiment of the present invention.
- FIG. 1 is a side view of a seal ring according to an embodiment of the present invention.
- FIG. 2 is a part of a view seen from the outer peripheral surface side of the seal ring according to the embodiment of the present invention.
- FIG. 3 is a partially enlarged
- FIG. 7 is a partially enlarged view of a side view of a seal ring according to a first modification of the present invention.
- FIG. 8 is a partially enlarged view of a side view of a seal ring according to a second modification of the present invention.
- FIG. 9 is a partially enlarged view of a side view of a seal ring according to a third modification of the present invention.
- FIG. 10 is a schematic cross-sectional view showing a state of use of a seal ring according to a conventional example.
- FIG. 1 is a side view of a seal ring according to an embodiment of the present invention.
- FIG. 2 is a part of a view from the outer peripheral surface side of the seal ring according to the embodiment of the present invention, and is a view showing the vicinity of a joint portion provided on the seal ring.
- FIG. 3 is a partially enlarged view of the side view of the seal ring according to the embodiment of the present invention.
- 4 to 6 are schematic cross-sectional views showing the state of use of the seal ring according to the embodiment of the present invention.
- the seal ring in FIGS. 4 and 5 corresponds to the BB cross-sectional view in FIG.
- the seal ring in FIG. 6 corresponds to the AA cross section in FIG.
- the “axial direction” means the direction in which the central axis of the shaft 500 or the seal ring 100 extends.
- the seal ring 100 is mounted in an annular groove 510 provided on the outer periphery of the shaft 500, and the shaft 500 and the housing 600 that rotate relative to each other Seal the annular gap between the surface 610). That is, as shown, for example, in FIG. 5, the annular gap between the shaft 500 and the inner circumferential surface 610 of the axial hole of the housing 600 is separated by the seal ring 100 into the area (P) and the area (Q). Thereby, the seal ring 100 holds the fluid pressure of the area to be sealed, which is configured to change the fluid pressure (in the present embodiment, the hydraulic pressure).
- the seal ring 100 is a fluid in the area (P) that is the sealing target area. It plays the role of holding the pressure.
- P the fluid pressure in the area to be sealed
- the fluid pressure in the area to be sealed becomes high.
- the seal ring 100 is made of a resin material such as polyetheretherketone (PEEK), polyphenylene sulfide (PPS), polytetrafluoroethylene (PTFE) or the like. Further, the peripheral length of the outer peripheral surface of seal ring 100 is shorter than the peripheral length of the inner peripheral surface of the axial hole of housing 600, and is configured so as not to have an interference.
- PEEK polyetheretherketone
- PPS polyphenylene sulfide
- PTFE polytetrafluoroethylene
- the seal ring 100 is provided with an abutment 110 at one location in the circumferential direction. Further, on the outer peripheral surface side of the seal ring 100, a plurality of first dynamic pressure generation grooves 131 and a plurality of second dynamic pressure generation grooves 132 are provided at intervals in the circumferential direction. Furthermore, on the inner peripheral surface side of the seal ring 100, a plurality of protrusions 150 that protrude inward in the radial direction are provided at intervals in the circumferential direction. Thus, by providing the plurality of projections 150, the seal ring 100 is mounted from the outer peripheral surface of the shaft 500 in a state before the seal ring 100 is attached to the annular groove 510 and assembled into the shaft hole of the housing 600.
- the projection 150 is formed.
- each portion can be obtained by cutting.
- the first dynamic pressure generating groove 131 and the second dynamic pressure generating groove 132 may be obtained by cutting after forming the joint portion 110 and the plurality of protrusions 150 in advance, or the manufacturing method Is not particularly limited.
- the abutment section 110 adopts a so-called special step cut which is cut in a step shape as viewed from either the outer peripheral surface side or the both side wall surface side.
- seal ring 100 the 1st fitting convex part 111a and the 1st fitting recess 112a are provided in the peripheral face side of one side via a cutting part, and the peripheral face side of the other side is provided.
- a second fitting recess 112b in which the first fitting protrusion 111a is fitted and a second fitting protrusion 111b in which the first fitting recess 112a is fitted are provided.
- a gap S is formed between the surface 113a on the inner peripheral surface side on one side and the surface 113b on the inner peripheral surface side on the other side via the cutting portion (see FIG. 1).
- the special step cut is a well-known technology, its detailed description is omitted, but it has the property of maintaining stable seal performance even if the circumferential length of the seal ring 100 changes due to thermal expansion and contraction.
- a special step cut was shown as an example of the abutment part 110 here, not only this but a straight cut, a bias cut, a step cut, etc. may be employ
- FIG. When a low elasticity material (PTFE or the like) is employed as the material of the seal ring 100, the joint portion 110 may not be provided, and may be endless.
- the first dynamic pressure generating groove 131 is provided so as to extend from the center (refer to L in FIG. 2) of the axial width of the seal ring 100 to a side surface 100A on one side from a position biased to the side 100A on one side. .
- the side surfaces 131a and 131b on both sides in the circumferential direction are each formed by an inclined surface whose depth gradually decreases toward both sides. More specifically, the said inclined surface is comprised by the surface (what is called R surface) curved seeing from the side of seal ring 100 side.
- the side surface (the side surface 131a or the side surface 131b) on the upstream side in the rotation direction is the same regardless of the relative rotation direction of the shaft 500 with respect to the housing 600. It can be said that it is configured by an inclined surface whose depth gradually decreases toward the upstream side.
- the second dynamic pressure generation groove 132 is provided so as to extend from the center of the axial width of the seal ring 100 toward the other side surface 100B to the other side surface 100B.
- the side surfaces on both sides in the circumferential direction are each formed by an inclined surface whose depth gradually becomes shallow toward both sides. More specifically, the said inclined surface is comprised by the surface (what is called R surface) curved seeing from the side of seal ring 100 side.
- the upstream side surface in the rotational direction has a depth toward the upstream side regardless of the relative rotational direction of the shaft 500 with respect to the housing 600. It can be said that is constituted by the inclined surface which becomes shallow gradually. Since the shapes of the second dynamic pressure generation groove 132 and the first dynamic pressure generation groove 131 are the same, the view from the side of the second dynamic pressure generation groove 132 is omitted.
- a plurality of first dynamic pressure generation grooves 131 and second dynamic pressure generation grooves 132 are provided at intervals in the circumferential direction over the entire circumference excluding the vicinity of the joint portion 110.
- the first dynamic pressure generation groove 131 is provided so as to extend from the center of the axial width of the seal ring 100 to the side surface 100A on one side to the side surface 100A on one side.
- the second dynamic pressure generating groove 132 is provided so as to extend from the center of the width in the axial direction of the seal ring 100 to a side surface 100B on the other side from a position biased to the side surface 100B on the other side.
- the annular convex part 120 is formed in the part which passes along the center of the width of an axial direction among the outer peripheral surfaces of the seal ring 100.
- rib-shaped first rib portions 141 are formed between the adjacent first dynamic pressure generating grooves 131, respectively.
- rib-like second rib portions 142 are respectively formed between the adjacent second dynamic pressure generating grooves 132.
- the outer peripheral surface near the abutment 110, the outer peripheral surface of the convex portion 120, the outer peripheral surfaces of the plurality of first rib portions 141, and the outer peripheral surfaces of the plurality of second rib portions 142 are located on the same plane. As a result, an annular continuous seal surface (cylindrical seal surface) on the outer peripheral surface side of the seal ring 100 is formed.
- the width of the convex portion 120 although the torque can be reduced as the width becomes narrower, if the width is made too narrow, the sealing performance and the durability deteriorate. Therefore, it is desirable to make the width as narrow as possible according to the use environment, etc., to the extent that the sealing performance and the durability can be maintained.
- the width of the convex portion 120 may be set to about 0.3 mm or more and 0.7 mm or less.
- the distance from the side surface on one side of the convex portion 120 to the side surface 100B on the other side of the seal ring 100 (corresponding to the length of the region H1 in FIG. 5)
- the distance from the side surface on the other side in portion 120 to the side surface 100A on one side in seal ring 100 is the distance from the inner peripheral surface of seal ring 100 to the outer peripheral surface of convex portion 120 (in FIG. It is set shorter than equivalent).
- the distance from the side surface on one side in the convex portion 120 to the side surface 100B on the other side in the seal ring 100 and the distance from the side surface on the other side in the convex portion 120 to the side surface 100A on one side in the seal ring 100 are equal.
- the region H1 can also be referred to as a region from the side on the high pressure side of the convex portion 120 to the side on the low pressure side of the seal ring 100 when the seal ring 100 is used.
- the effective pressure receiving area from the inner peripheral surface side contributing to the force with which the seal ring 100 is pressed against the inner peripheral surface 610 of the shaft hole by fluid pressure Is smaller than the effective pressure receiving area from the side that contributes to the force that is pressed against the low-pressure side wall surface of the annular groove 510 by the fluid pressure.
- FIG. 4 shows a state (no-load state) in which the engine is stopped and the fluid pressure on the area (P) side and the fluid pressure on the area (Q) side are equal via the seal ring 100.
- FIGS. 5 and 6 the engine is engaged and the fluid pressure on the region (P) side is higher than the fluid pressure on the region (Q) side in the state where the differential pressure is generated via the seal ring 100 ) Is shown.
- the seal ring 100 In the no-load state, there is no differential pressure between the area (P) and the area (Q), and no fluid pressure from the inner circumferential surface acts, so the seal ring 100 is the left side in FIG. It can be in a state of being separated from the inner circumferential surface 610 of the wall surface and the shaft hole.
- seal ring 100 When the engine is applied and a differential pressure is generated, seal ring 100 is in close contact with the side wall surface of annular groove 510 on the low pressure side (in the example shown, the area (Q) side), and the axial hole Sliding with respect to the inner circumferential surface 610 (see FIGS. 5 and 6).
- the seal ring 100 according to the present embodiment is in close contact with the side wall surface on the low pressure side of the annular groove 510 and is configured to slide on the inner circumferential surface 610 of the axial hole of the housing 600. This point will be described in more detail.
- the length of the region H1 shown in FIG. 5 is set shorter than the length of the region T1.
- the effective pressure receiving area from the inner circumferential surface side which contributes to the force by which seal ring 100 is pressed against inner circumferential surface 610 of the axial hole by the fluid pressure is the low pressure side of annular groove 510 by the fluid pressure. It becomes narrower than the effective pressure receiving area from the side which contributes to the force pressed against the side wall surface.
- the region T1 is an effective pressure receiving region when the seal ring 100 is axially pressed from the high pressure side to the low pressure side by the fluid to be sealed. Further, the area over the entire circumference of the pressure receiving region T1 is an effective pressure receiving area in the axial direction.
- the area H1 is an effective pressure receiving area when the seal ring 100 is pressed radially outward from the inner peripheral surface toward the outer peripheral surface by the fluid to be sealed. This is because, in the region where the high-pressure-side dynamic pressure generation groove (in the case of the present embodiment, the first dynamic-pressure generation groove 131 on the region (P) side) is provided, fluid pressure is applied from both sides in the radial direction. This is because the force applied to the seal ring 100 in the radial direction is offset.
- the area over the entire circumference of the pressure receiving area H1 is an effective pressure receiving area in the radial direction.
- the effective pressure receiving area (pressure receiving area) for the seal ring 100 is smaller in the radially outward direction than in the axial direction. Therefore, the seal ring 100 can be prevented from sliding relative to the annular groove 510, and the outer peripheral surface of the seal ring 100 can be more reliably slid relative to the inner peripheral surface 610 of the shaft hole. Thereby, regardless of the size of the annular gap between the shaft 500 and the housing 600, the area of the sliding portion can be stabilized. Therefore, the sealing performance can be stabilized.
- a lubricating film here, an oil film
- the sliding torque can be further reduced. This is because, when sliding between the outer peripheral surface of the seal ring 100 and the inner peripheral surface of the shaft hole, the wedge effect is exhibited in the minute gap portion between them.
- the seal ring 100 when a differential pressure is generated on both sides via the seal ring 100, the dynamic pressure generation groove on the high pressure side of the pair of dynamic pressure generation grooves (this embodiment In this case, the fluid to be sealed is introduced into the first dynamic pressure generating groove 131). Therefore, even if the fluid pressure increases, fluid pressure acts on seal ring 100 both from the outer peripheral surface side and from the inner peripheral surface side in the region where first dynamic pressure generation groove 131 is provided. , These fluid pressure can be offset.
- the arrows in FIG. 5 indicate that the fluid pressure acts on the seal ring 100.
- first dynamic pressure generation grooves 131 and second dynamic pressure generation grooves 132 are formed circumferentially at intervals along the entire circumference excluding the vicinity of the joint portion 110.
- first dynamic pressure generation groove 131 and the second dynamic pressure generation groove 132 are provided over a wide area of the outer peripheral surface of the seal ring 100.
- the sliding area with the inner circumferential surface 610 of the hole can be made as narrow as possible, and the sliding torque can be extremely reduced.
- the first dynamic pressure generation groove 131 and the second dynamic pressure generation groove 132 generate a dynamic pressure as the housing 600 and the seal ring 100 rotate relative to each other.
- the upstream side surface (side surface 131a or side surface 131b) of the seal ring 100 in the relative rotational direction with respect to the housing 600 has a gradually shallower depth toward the upstream side. It is comprised by the inclined surface which becomes. Therefore, when the housing 600 and the seal ring 100 relatively rotate, the fluid to be sealed in the first dynamic pressure generation groove 131 flows from the inside of the groove to the outer peripheral surface of the seal ring 100 so that a dynamic pressure is generated. Do.
- the mechanism of the dynamic pressure generation by the second dynamic pressure generation groove 132 is also the same.
- a dynamic pressure is a force in a direction in which the outer peripheral surface of the seal ring 100 is separated from the inner peripheral surface 610 of the axial hole of the housing 600.
- the film thickness of the fluid to be sealed which is formed between the outer peripheral surface of the seal ring 100 and the inner peripheral surface 610 of the axial hole of the housing 600, can be increased. Therefore, the sliding torque (rotational torque) can be further reduced.
- the seal ring 100 according to the present embodiment can be suitably used even under high-speed and high-pressure environmental conditions. Further, by not sliding on the side surface of the annular groove 510, a soft material such as aluminum can also be used as a material of the shaft 500.
- the seal ring 100 since the plurality of first rib portions 141 and the second rib portions 142 are provided, the rigidity of the seal ring 100 is increased, and in particular, the strength in the twisting direction is high. can do. Therefore, deformation of the seal ring 100 is suppressed even under an environment where the differential pressure increases, and the sealing performance is stably exhibited. In addition, the seal ring 100 can be prevented from being inclined with respect to the annular groove 510.
- the first dynamic pressure generation groove 131 and the second dynamic pressure generation groove 132 according to the above embodiment, the case where the side surfaces on both sides in the circumferential direction are formed by so-called R surfaces is shown.
- the first dynamic pressure generating groove and the second dynamic pressure generating groove in the present invention are not limited to such a configuration, and the dynamic pressure may be generated with relative rotation between the housing 600 and the seal ring 100.
- various known techniques can be adopted.
- the side surfaces 131Xa and 131Xb on both sides in the circumferential direction are configured by planar inclined surfaces whose depths gradually become smaller toward both sides. It may be done. It goes without saying that the same effect as that of the first embodiment can be obtained also in the first modification.
- the side surface 131Ya on one side in the circumferential direction may be configured by an R surface as in the case of the first embodiment.
- the upstream side surface 131Ya of the seal ring 100 in the relative rotational direction with respect to the housing 600 has a gradually increasing depth toward the upstream side. It is necessary to constitute by the inclined surface (R surface) which becomes shallow.
- an arrow R ⁇ b> 1 is the relative rotational direction of the seal ring 100 with respect to the housing 600. Therefore, when the shaft 500 (and the seal ring 100) is relatively rotated with respect to the housing 600, the fluid to be sealed flows in the direction of the arrow R2 with respect to the seal ring 100 in the figure.
- the side surface 131Za on one side in the circumferential direction can be configured as a flat inclined surface as in the first modification.
- the side surface 131Za can also be referred to as a groove bottom surface.
- the upstream side surface 131Za of the seal ring 100 in the relative rotational direction with respect to the housing 600 has a gradually shallower depth toward the upstream side. It is necessary to comprise by the inclined surface which becomes.
- an arrow R ⁇ b> 1 is the relative rotational direction of the seal ring 100 with respect to the housing 600. Therefore, when the shaft 500 (and the seal ring 100) is relatively rotated with respect to the housing 600, the fluid to be sealed flows in the direction of the arrow R2 with respect to the seal ring 100 in the figure.
Abstract
Description
軸の外周に設けられた環状溝に装着され、相対的に回転する前記軸とハウジングとの間の環状隙間を封止して、流体圧力が変化するように構成されたシール対象領域の流体圧力を保持するシールリングにおいて、
前記環状溝における低圧側の側壁面に密着し、かつ前記ハウジングにおける前記軸が挿通される軸孔の内周面に対して摺動するシールリングであって、
外周面側には、
軸線方向の幅の中心から一方側の側面に偏った位置から一方側の側面に至るように設けられ、前記ハウジングとシールリングとの相対的な回転に伴って動圧を発生する第1動圧発生溝と、
軸線方向の幅の中心から他方側の側面に偏った位置から他方側の側面に至るように設けられ、前記ハウジングとシールリングとの相対的な回転に伴って動圧を発生する第2動圧発生溝と、がそれぞれ周方向に間隔を空けて複数設けられていることを特徴とする。
第2動圧発生溝において、前記ハウジングに対するシールリングの相対的な回転方向の上流側の側面も、該上流側に向かって深さが徐々に浅くなる傾斜面により構成されているとよい。
図1~図6を参照して、本発明の実施例に係るシールリングについて説明する。図1は本発明の実施例に係るシールリングの側面図である。図2は本発明の実施例に係るシールリングの外周面側から見た図の一部であり、シールリングに設けられた合口部付近を示した図である。図3は本発明の実施例に係るシールリングの側面図の一部拡大図である。図4~図6は本発明の実施例に係るシールリングの使用状態を示す模式的断面図である。なお、図4,5中のシールリングは、図3中のBB断面図に相当する。図6中のシールリングは、図3中のAA断面図に相当する。なお、以下の説明において、「軸線方向」とは、軸500やシールリング100の中心軸線が伸びる方向を意味する。
本実施例に係るシールリング100は、軸500の外周に設けられた環状溝510に装着され、相対的に回転する軸500とハウジング600(ハウジング600における軸500が挿通される軸孔の内周面610)との間の環状隙間を封止する。つまり、シールリング100によって、例えば図5に示すように、軸500とハウジング600の軸孔の内周面610との間の環状隙間が領域(P)と領域(Q)に隔てられる。これにより、シールリング100は、流体圧力(本実施例では油圧)が変化するように構成されたシール対象領域の流体圧力を保持する。ここで、本実施例においては、図4~図6中の右側の領域(P)の流体圧力が変化するように構成されており、シールリング100はシール対象領域である領域(P)の流体圧力を保持する役割を担っている。なお、自動車のエンジンが停止した状態においては、シール対象領域の流体圧力は低く、無負荷の状態となっており、エンジンをかけるとシール対象領域の流体圧力は高くなる。
特に、図4~図6を参照して、本実施例に係るシールリング100の使用時のメカニズムについて説明する。図4は、エンジンが停止しており、シールリング100を介して領域(P)側の流体圧力と領域(Q)側の流体圧力が等しい状態(無負荷状態)を示している。図5及び図6は、エンジンがかかり、シールリング100を介して、差圧が生じている状態(領域(P)側の流体圧力が領域(Q)側の流体圧力に比べて高くなった状態)を示している。
本実施例に係るシールリング100は、環状溝510の低圧側の側壁面に密着し、ハウジング600の軸孔の内周面610に対して摺動するように構成されている。この点について、より詳細に説明する。本実施例に係るシールリング100においては、図5に示す領域H1の長さは領域T1の長さよりも短く設定されている。これにより、シールリング100が、流体圧力により軸孔の内周面610に対して押し付けられる力に寄与する内周面側からの有効受圧面積の方が、流体圧力により環状溝510における低圧側の側壁面に対して押し付けられる力に寄与する側面側からの有効受圧面積よりも狭くなる。
上記実施例に係る第1動圧発生溝131及び第2動圧発生溝132においては、周方向の両側の側面が、いわゆるR面で構成される場合を示した。しかしながら、本発明における第1動圧発生溝及び第2動圧発生溝は、そのような構成に限らず、ハウジング600とシールリング100との相対的な回転に伴って動圧が発生しさえすれば、各種公知技術を採用することができる。例えば、図7の変形例1に示す動圧発生溝131Xのように、周方向の両側の側面131Xa,131Xbが、いずれも両側に向かって深さが徐々に浅くなる平面状の傾斜面によって構成されるようにしてもよい。この変形例1の場合においても、上記実施例1の場合と同様の効果を得ることができることは言うまでもない。
100A 一方側の側面
100B 他方側の側面
110 合口部
111a 第1嵌合凸部
111b 第2嵌合凸部
112a 第1嵌合凹部
112b 第2嵌合凹部
120 凸部
131 第1動圧発生溝
132 第2動圧発生溝
131X,131Y,131Z 動圧発生溝
131a,131b,131Xa,131Xb,131Ya,131Za 側面
141 第1リブ部
142 第2リブ部
150 突起
500 軸
510 環状溝
600 ハウジング
610 内周面
Claims (3)
- 軸の外周に設けられた環状溝に装着され、相対的に回転する前記軸とハウジングとの間の環状隙間を封止して、流体圧力が変化するように構成されたシール対象領域の流体圧力を保持するシールリングにおいて、
前記環状溝における低圧側の側壁面に密着し、かつ前記ハウジングにおける前記軸が挿通される軸孔の内周面に対して摺動するシールリングであって、
外周面側には、
軸線方向の幅の中心から一方側の側面に偏った位置から一方側の側面に至るように設けられ、前記ハウジングとシールリングとの相対的な回転に伴って動圧を発生する第1動圧発生溝と、
軸線方向の幅の中心から他方側の側面に偏った位置から他方側の側面に至るように設けられ、前記ハウジングとシールリングとの相対的な回転に伴って動圧を発生する第2動圧発生溝と、がそれぞれ周方向に間隔を空けて複数設けられていることを特徴とするシールリング。 - 第1動圧発生溝において、前記ハウジングに対するシールリングの相対的な回転方向の上流側の側面が、該上流側に向かって深さが徐々に浅くなる傾斜面により構成されており、
第2動圧発生溝において、前記ハウジングに対するシールリングの相対的な回転方向の上流側の側面も、該上流側に向かって深さが徐々に浅くなる傾斜面により構成されていることを特徴とする請求項1に記載のシールリング。 - 内周面側には、径方向内側に向かって突出する突起が、周方向に間隔を空けて複数設けられていることを特徴とする請求項1または2に記載のシールリング。
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