WO2014183542A1 - Composant d'étanchéité par rapport à un mouvement de va-et-vient - Google Patents

Composant d'étanchéité par rapport à un mouvement de va-et-vient Download PDF

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Publication number
WO2014183542A1
WO2014183542A1 PCT/CN2014/075952 CN2014075952W WO2014183542A1 WO 2014183542 A1 WO2014183542 A1 WO 2014183542A1 CN 2014075952 W CN2014075952 W CN 2014075952W WO 2014183542 A1 WO2014183542 A1 WO 2014183542A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing
reciprocating seal
reciprocating
annular
seal
Prior art date
Application number
PCT/CN2014/075952
Other languages
English (en)
Chinese (zh)
Inventor
杜杰
王景林
李玉胜
梁延忠
Original Assignee
烟台润蚨祥油封有限公司
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
Priority claimed from CN201310182418.4A external-priority patent/CN103244686B/zh
Priority claimed from CN201410042652.1A external-priority patent/CN103742651B/zh
Application filed by 烟台润蚨祥油封有限公司 filed Critical 烟台润蚨祥油封有限公司
Publication of WO2014183542A1 publication Critical patent/WO2014183542A1/fr

Links

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
    • F16J15/56—Other sealings for reciprocating rods
    • 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
    • F16J15/324—Arrangements for lubrication or cooling of the sealing itself
    • 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

Definitions

  • the present invention relates to a seal, and more particularly to a reciprocating seal. Background technique
  • Reciprocating hydraulic structures such as shock absorbers are commonly used components in modern vehicles and construction machinery.
  • the reciprocating shaft seal lip structure and wear resistance generally have a large impact on the service life of the reciprocating hydraulic structure.
  • the sealing ability of the seal depends on the thickness of the oil film on the sealing surface.
  • the thickness of the oil film between the sealing lip and the shaft is too large, and the seal is prone to leakage; if the thickness is too small, dry friction may occur, resulting in wear of the seal and the shaft.
  • the shock absorber of a motor vehicle often has problems such as oil leakage, abnormal noise, and poor durability of the reciprocating hydraulic structure during use.
  • the sealing member must have the ability to maintain sufficient radial force on the shaft (e.g., the damper shaft).
  • the radial force required for the seal must first be met.
  • the theory that the friction coefficient is equal to the product of the radial force and the friction coefficient.
  • the radial force design value is large, under the condition that the friction coefficient remains unchanged, a large axial friction force is inevitable, in the axial direction.
  • the hydraulic structure of the seal and the reciprocating hydraulic structure is liable to cause dry grinding, abnormal sound or even reciprocating hydraulic structure failure, which affects the service life of the moving body such as automobile and construction machinery. Then, how to ensure proper radial sealing force and minimize the axial friction between the sealing body and the reciprocating hydraulic structure becomes critical. Summary of the invention
  • the present invention is directed to the above-mentioned deficiencies of the prior art, and provides a reciprocating seal capable of reducing the axial friction between the sealing body and the reciprocating hydraulic structure while maintaining the radial sealing pressure, thereby extending the sealing body. Even the reciprocating hydraulic structure such as the life of the shock absorber.
  • the technical solution of the present invention to solve the above technical problems is as follows: a reciprocating seal having an annular elastic sealing body, the annular elastic sealing body comprising at least one sealing lip, characterized by a ring formed by the sealing lip An uneven surface band is provided on the sealing surface.
  • the invention has the beneficial effects that on the one hand, since the annular sealing surface formed on the sealing lip is provided with the concave-convex surface band, this not only reduces the contact area between the sealing surface and the reciprocating hydraulic structure, but also facilitates A critical lubricating oil film is formed between the sealing surface and the reciprocating hydraulic structure; on the other hand, since the surface of the concave-convex surface belt is concave and convex, the lubricating oil can be better stored, and the sealing lip and the reciprocating hydraulic structure are lowered.
  • the friction coefficient achieves the purpose of reducing the friction between the seal and the reciprocating hydraulic structure while maintaining the radial force of the reciprocating hydraulic structure.
  • the uneven surface band is provided with a plurality of protrusions or dimples.
  • These protrusions or dimples form longitudinal and lateral grooves on the concave and convex ring belts, so that the oil can be stored in these grooves and can obtain a labyrinth sealing effect, and also contribute to long-term preservation of the lubricating oil film, thereby improving The service life of the seal.
  • a single raised or recessed structure is more flexible and followable. Compared with the conventional seal, the axial friction of the invention can be reduced by 10% to 37%, and the service life of the seal is extended by 20% - 40%.
  • the shape of the protrusion or the pit is a hemispherical shape, a tetragonal shape, a truncated cone shape or a polygonal prism shape.
  • the use of different structures of protrusions or dimples can better adapt to different working conditions to reduce the axial friction under the premise of ensuring the sealing performance: by adjusting the shape and density of the concave and convex structures and between the protrusions or pits The spacing can be adjusted to the sealing performance of the seal or to the pressure of different sealed media.
  • the projections or depressions are hooked or randomly distributed on the annular sealing surface.
  • the uniform or irregular distribution can be selected, and the irregular distribution can ensure the formation of the labyrinth oil storage groove, so that the service life of the seal is longer.
  • the height of the protrusion or the depth of the pit is 0.02 0.3 mm.
  • the height of the protrusions may be appropriately selected according to the diameter of the seal, the thickness of the seal, the thickness of the oil film required, and other operating conditions. The depth of the pit.
  • the annular sealing surface between adjacent ones of said protrusions or adjacent said pits is planar, concavely curved or convexly curved.
  • the uneven surface band is provided with an axial parallel pattern.
  • an axial groove is formed on the above-mentioned annular sealing surface, which infiltrates the lubricating oil or the grease into the sealing member and the reciprocating motion by the reciprocating motion of the reciprocating hydraulic structure such as the damper shaft.
  • the hydraulic structure has the largest contact stress and the easiest dry-grinding lip lip portion to form a critical lubricating oil film; the sealing member does not closely contact the reciprocating hydraulic structure at least in the axial groove formed by the adjacent axial parallel lines, The contact area of the sealing member and the reciprocating hydraulic structure is reduced, and the heat dissipation is reduced while reducing friction heat generation; the axial groove formed by the axial parallel pattern facilitates the storage of the lubricating oil and the long-term lubrication of the lip tip portion. And can form an axial guiding effect on the reciprocating hydraulic structure.
  • the axial parallel pattern has a continuous straight line shape, a wave shape, or an intermittent straight line shape in the axial direction.
  • the axial parallelogram has a wavy, circular arc, triangular or trapezoidal shape in the radial direction. This arrangement effectively reduces the contact area between the seal lip and the damper shaft and reduces manufacturing costs.
  • the at least one sealing lip may include a first sealing lip and a second sealing lip, and a ring formed by each of the first sealing lip and the second sealing lip
  • a first concave-convex surface belt and a second concave-convex surface belt are respectively disposed on the sealing surface.
  • the annular elastic sealing body may further include a dust lip, and a third concave-convex surface band is further provided on the annular sealing surface formed by the dust lip. Designed by ammonium third concave-convex surface band It can reduce the axial friction of the seal while effectively blocking the dust.
  • the reciprocating seal described above may be a shock absorber oil seal.
  • the reciprocating seal described above may also include an annular support frame.
  • the material shield of the above annular elastic sealing body is polyurethane or rubber, and the rubber may be nitrile rubber, hydrogenated nitrile rubber or fluororubber. Depending on the application, the required cost may vary and a suitable sealing material may be used.
  • Figure 1 is a schematic view showing the structure of a reciprocating seal according to a first embodiment of the present invention
  • FIG. 2 is a schematic view showing the structure of a reciprocating seal according to a second embodiment of the present invention.
  • Figure 3 is a schematic view showing the structure of a reciprocating seal according to a third embodiment of the present invention.
  • Figure 4 is a schematic view showing the structure of a reciprocating seal according to a fourth embodiment of the present invention.
  • Figure 5 is a partial cross-sectional view in the radial direction of a concave-convex annular band of a reciprocating seal according to a fifth embodiment of the present invention, wherein a hemispherical projection is schematically shown;
  • Figure 6 is a reciprocating motion shown in Figure 1.
  • Figure 1 a partial cross-sectional view of the concavo-convex annulus of the seal in the radial direction, wherein the multi-segment-shaped projection is schematically shown;
  • Figure 7 is a partial cross-sectional view of the 1HJ convex annulus of the reciprocating seal of Figure 2 in a radial direction, wherein the irregularly distributed projections are schematically illustrated;
  • Figure 8 is a partial cross-sectional view, in the radial direction, of the concave-convex annular band of the reciprocating seal of Figure 3, wherein the pits are schematically shown;
  • Figure 9 is a cross-sectional view along line AA of the reciprocating seal of Figure 4, schematically showing a quadrangular projection;
  • Figure 10 is a schematic view showing the structure of a reciprocating seal according to a sixth embodiment of the present invention.
  • Figure 11 is a schematic view showing the structure of a reciprocating seal according to a seventh embodiment of the present invention.
  • Figure 12 is a schematic view showing the structure of a reciprocating seal according to an eighth embodiment of the present invention.
  • Figure 13 is a cross-sectional view of the axial parallel pattern of the reciprocating seal shown in Figures 10 through 12 in the radial direction.
  • the reciprocating seal comprises an annular support frame 1 And an annular elastic sealing body 2, wherein the annular elastic sealing body 2 comprises at least one sealing lip, and an annular sealing surface formed on the annular sealing surface formed by the sealing lip is provided.
  • the annular sealing surface formed on the sealing lip is provided with a concave-convex surface band, this not only reduces the contact area between the sealing surface and the reciprocating hydraulic structure, but also facilitates the sealing surface.
  • a critical lubricating oil film is formed between the reciprocating hydraulic structure; on the other hand, since the surface of the concave-convex surface band is concave and convex, the lubricating oil can be better stored, and the friction coefficient between the sealing lip and the reciprocating hydraulic structure is reduced.
  • the hydraulic structure may be a hydraulic cylinder and a piston structure, so that the seal according to the embodiment of the present invention may be fitted, for example, on a reciprocating piston or shaft.
  • the annular elastic sealing body 2 includes two sealing lips, i.e., the first sealing lip 3 and the second sealing lip 4.
  • a first uneven surface band 6 and a second uneven surface band 7 are respectively provided on the annular sealing faces formed by the first sealing lip 3 and the second sealing lip 4.
  • the annular elastic sealing body 2 further includes a dust lip 5, and a third uneven surface band 8 is further provided on the annular sealing surface formed by the dust lip 5.
  • the above-mentioned uneven surface ring and belt are provided with a plurality of projections 10 (see Figs. 5 to ⁇ and Fig. 9) or pits 11 (see Fig. 8).
  • the shape of the protrusion 10 or the pit 11 may be a hemispherical shape (see FIG. 5), a tetragonal shape (see FIG. 9), a truncated cone shape or a polygonal prism shape (see FIG. 6) on which the annular sealing surface is formed. Hook distribution or irregular distribution (see Figure 7).
  • the height of the projections 10 or the depth of the dimples is 0.02 - 0.3 mm.
  • the sealing faces between adjacent projections 10 or between adjacent dimples 1 1 may be planar, concavely curved or convexly curved.
  • each of the first concavo-convex surface band 6, the second concavo-convex ring band 7, and the third concavo-convex ring band 8 A plurality of protrusions 10 are provided on the top, and the protrusions 10 have a polygonal shape, and the height of the protrusions 10 is 0.02 mm.
  • a plurality of protrusions 10 are also provided on each of the concave and convex surface band 6, the second concave and convex surface band 7, and the third concave and convex surface band 8, and the protrusions 10 are irregularly distributed on the annular sealing surface.
  • the height is 0.10 mm.
  • each of the first uneven surface band 6, the second uneven surface band 7, and the third uneven ring band 8 are provided.
  • each of the first uneven surface band 6, the second uneven surface band 7, and the third uneven surface band 8 are also A plurality of protrusions 10 are provided, and the protrusions 10 have a quadrangular shape.
  • a grid-like lubricating oil storage groove is formed on the annular sealing surface, wherein the height of the protrusions 10 It is 0.20 mil.
  • the reciprocating seal is embodied as a damper oil seal comprising an annular support frame 1 and an annular elastic seal 2 as an oil seal.
  • the annular elastic sealing body 2 also includes at least one sealing lip, and a toroidal sealing surface is formed on the annular sealing surface formed by the sealing lip.
  • the at least one sealing lip is actually two sealing lips, namely a first sealing lip 3 and a second sealing lip 4, wherein the first sealing lip 3 and the second sealing lip 4, the annular sealing surface formed is provided with a first concave-convex surface belt 6 and a second concave-convex surface belt 7 respectively.
  • the annular elastic sealing body 2 further includes a dust lip 5, and a third uneven surface band 8 is provided on the annular sealing surface formed by the dust lip 5.
  • the axially parallel strips are provided on the uneven surface band.
  • the first concave-convex surface band 6 is provided with a first axial parallel pattern 60, and the first axial parallel lines 60 are continuous in a straight line shape in the axial direction, as shown in FIG. 10;
  • the annular belt 7 is provided with a second axial parallel pattern 70, and the second axial parallel lines 70 are axially A wave-bending shape, as shown in FIG. 11;
  • a third axial parallel pattern 80 is disposed on the third concave-convex surface band 8, and the third axial parallel lines 80 are intermittently linear along the axial direction, as shown in the figure. 12 is shown.
  • the axial parallel lines 60, 70 and 80 are wavy (see Figure 13), circular, triangular or trapezoidal in cross section.
  • the material shield of the annular elastic sealing body 2 in the above first to eighth embodiments may be polyurethane or rubber, wherein the rubber is preferably a nitrile rubber, a hydrogenated nitrile rubber or a fluororubber.
  • annular support frame 1 is shown in the above first to eighth embodiments, it is not a necessary component for the reciprocating seal, and in a specific application, the seal may not provide a skeleton, but only It is composed of an annular elastic sealing body 2, for example, the sealing member may be a one-piece annular elastic sealing body.
  • annular elastic sealing body 2 shown in the above embodiment is provided with a tightening spring for increasing the followability of the lip of the sealing member and ensuring that the sealing member maintains the necessary radial force after the lip is worn.
  • the tightening spring 9 is not essential to the invention as long as the annular elastic sealing body 2 itself has sufficient radial force.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

La présente invention concerne un composant d'étanchéité par rapport à un mouvement de va-et-vient comprenant un corps de joint (2) élastique annulaire. Le corps de joint (2) élastique annulaire comprend au moins une lèvre de joint (3, 4) et une surface de joint annulaire formée par la lèvre de joint (3, 4) est pourvue d'une gaine (6, 7) concave-convexe. Le frottement entre le corps de joint et un arbre est réduit tout en garantissant que le corps de joint présente une pression de joint radiale suffisante, de façon à réduire le frottement du mécanisme de va-et-vient et de prolonger la durée de vie du corps de joint et de l'arbre de déplacement tout en garantissant l'obtention d'un effet de joint.
PCT/CN2014/075952 2013-05-16 2014-04-22 Composant d'étanchéité par rapport à un mouvement de va-et-vient WO2014183542A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201310182418.4 2013-05-16
CN201310182418.4A CN103244686B (zh) 2013-05-16 2013-05-16 一种低摩擦减振器油封
CN201410042652.1A CN103742651B (zh) 2014-01-29 2014-01-29 一种低摩擦往复运动密封件
CN201410042652.1 2014-01-29

Publications (1)

Publication Number Publication Date
WO2014183542A1 true WO2014183542A1 (fr) 2014-11-20

Family

ID=51897687

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/075952 WO2014183542A1 (fr) 2013-05-16 2014-04-22 Composant d'étanchéité par rapport à un mouvement de va-et-vient

Country Status (1)

Country Link
WO (1) WO2014183542A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5044642A (en) * 1988-03-30 1991-09-03 Firma Carl Freudenberg Annular seal
JP2001355740A (ja) * 2000-06-15 2001-12-26 Nok Corp オイルシール
JP2004138091A (ja) * 2002-10-15 2004-05-13 Nok Corp 往復動シール
JP2006009928A (ja) * 2004-06-25 2006-01-12 Nok Corp 密封装置
JP2006242373A (ja) * 2004-09-24 2006-09-14 Nok Corp 密封装置
CN101000097A (zh) * 2006-01-13 2007-07-18 昆山茂顺密封件工业有限公司 密封元件
CN202251628U (zh) * 2011-09-09 2012-05-30 浙江强广剑工贸有限公司 减震器油封
CN202381618U (zh) * 2011-11-11 2012-08-15 青岛开世密封工业有限公司 减震器油封
CN103244686A (zh) * 2013-05-16 2013-08-14 烟台润蚨祥油封有限公司 一种低摩擦减振器油封
CN203322272U (zh) * 2013-05-16 2013-12-04 烟台润蚨祥油封有限公司 一种低摩擦减振器油封

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5044642A (en) * 1988-03-30 1991-09-03 Firma Carl Freudenberg Annular seal
JP2001355740A (ja) * 2000-06-15 2001-12-26 Nok Corp オイルシール
JP2004138091A (ja) * 2002-10-15 2004-05-13 Nok Corp 往復動シール
JP2006009928A (ja) * 2004-06-25 2006-01-12 Nok Corp 密封装置
JP2006242373A (ja) * 2004-09-24 2006-09-14 Nok Corp 密封装置
CN101000097A (zh) * 2006-01-13 2007-07-18 昆山茂顺密封件工业有限公司 密封元件
CN202251628U (zh) * 2011-09-09 2012-05-30 浙江强广剑工贸有限公司 减震器油封
CN202381618U (zh) * 2011-11-11 2012-08-15 青岛开世密封工业有限公司 减震器油封
CN103244686A (zh) * 2013-05-16 2013-08-14 烟台润蚨祥油封有限公司 一种低摩擦减振器油封
CN203322272U (zh) * 2013-05-16 2013-12-04 烟台润蚨祥油封有限公司 一种低摩擦减振器油封

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