WO1991019920A1 - Dispositif d'etancheite - Google Patents

Dispositif d'etancheite Download PDF

Info

Publication number
WO1991019920A1
WO1991019920A1 PCT/DE1991/000423 DE9100423W WO9119920A1 WO 1991019920 A1 WO1991019920 A1 WO 1991019920A1 DE 9100423 W DE9100423 W DE 9100423W WO 9119920 A1 WO9119920 A1 WO 9119920A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
sealing
groove
sealing arrangement
machine part
Prior art date
Application number
PCT/DE1991/000423
Other languages
German (de)
English (en)
Inventor
Wolfgang Böhler
Original Assignee
Busak + Luyken Gmbh & Co.
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 Busak + Luyken Gmbh & Co. filed Critical Busak + Luyken Gmbh & Co.
Publication of WO1991019920A1 publication Critical patent/WO1991019920A1/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
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic 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
    • F16J15/56—Other sealings for reciprocating rods

Definitions

  • the invention relates to an arrangement for sealing a gap between two mutually concentric, mutually movable machine parts, of which the first machine part has a groove and the second machine part has a smooth contact surface opposite the groove, with an inserted in the groove of the first machine part
  • Sealing ring made of tough-elastic plastic, which has a ring-shaped section and a web projecting radially therefrom, at its end a web forming a pointed cross-section, and an elastic clamping ring which directly adjoins a ring with a higher modulus of elasticity than the sealing ring .
  • the known sealing arrangement for shafts comprises a sealing ring made of a viscoplastic material, in particular glass fiber reinforced polytetrafluoroethylene, and a rubber-elastic clamping ring resting on the side of the sealing ring facing away from the sealing surface.
  • the sealing ring has a cylindrical section and a web projecting radially therefrom, which forms the sealing surface at its end.
  • a spacer ring on the low-pressure side is arranged in the groove, which determines the axial position of the clamping ring in relation to the sealing ring. The spacer ring prevents the clamping ring from being deformed and displaced too far towards the low-pressure side in the pressure-loaded state of the known sealing arrangement.
  • the contact pressure on the sealing surface of the web depends on the shape and position of the clamping ring.
  • the contact pressure resulting from the more elastic clamping ring can be transferred to the sealing ring, so that the maximum force resultant of this contact pressure is directed more or less directly at the sealing edge of the sealing ring.
  • the sealing ring cannot be relieved of the elastomeric contact pressure via the pressure of the medium in contact with the known sealing arrangement.
  • the invention is therefore based on the object of developing a sealing arrangement of the known type such that the sealing ring can also be relieved of the contact pressure of the tensioning ring by the pressure of the medium present on the sealing arrangement.
  • the ring is designed as a support ring for the clamping ring and that the clamping ring rests more or less on the support ring with direct pressure loading by a medium.
  • the sealing arrangement according to the invention thus has the essential advantage that, with increased pressure of the medium, the force with which the sealing surface of the sealing ring is pressed against the contact surface of the moving machine part is essentially determined by the hydraulic pressure of the medium itself.
  • the clamping ring can slide completely onto the supporting ring and the supporting ring can be designed in such a way that it absorbs the entire biasing force of the clamping ring without deformation and does not transmit it to the sealing ring.
  • This has the advantage that the contact pressure of the sealing edge against the rotating contact surface can be kept largely constant even at high pressures.
  • the force with which the sealing surface increases generally increases with increasing medium pressure the contact surface is pressed. If, on the other hand, the elastomer contact pressure increases with increasing medium pressure, the actually increasing contact pressure with which the sealing surface is pressed against the contact surface can be reduced. This means that longer running times can be achieved with the sealing arrangement according to the invention.
  • the support ring is arranged in the groove as a body spaced from the sealing ring and one side of it rests on a groove flank.
  • the support ring has a surface that extends obliquely to the base of the groove.
  • the support ring when the sealing arrangement is depressurized, the support ring is embedded stress-free in a recess on the side of the sealing ring which adjoins the clamping ring.
  • the support ring together with the sealing ring can be introduced into the groove and that no structural designs of the groove are particularly to be taken into account. While in the first embodiment the support ring must be adapted to the groove size and the position of the support ring relative to the sealing ring must also be taken into account and the inclination and length of the inclined surface of the support ring must also be specified exactly, in the second embodiment the support ring can be detached from the groove shape and the groove size and only be matched to the sealing ring itself.
  • sealing arrangement preference is given to using O-rings, rectangular rings, four-lip sealing rings or else half-O-rings as the clamping ring or clamping rings.
  • the sealing arrangement can be used with reciprocating machine parts as well as with rotating machine parts.
  • trapezoidal support rings can also be used in cross section.
  • the invention is shown in the drawing and is based on
  • FIG. 1 shows a sealing arrangement according to the invention in cross section with a support ring spaced from the sealing ring; the sealing arrangement is shown in the figure in the depressurized state;
  • FIG. 2 shows a sealing arrangement according to the invention in cross section with a support ring which is arranged in a recess in the sealing ring; the sealing arrangement according to the invention is shown in the figure in the depressurized state;
  • FIG. 3 shows a sealing arrangement according to the invention in cross section with a clamping ring which has been displaced from the medium in the groove onto the inclined surface of the support ring;
  • FIG. 4 shows a sealing arrangement according to the invention in cross section with a clamping ring which has been displaced by the medium in the groove via a support ring embedded in the sealing ring.
  • FIG. 1 shows a sealing arrangement 1 which seals two machine parts which are concentric with one another and movable with respect to one another.
  • the machine parts are composed of a first machine part 2 and a second machine part 3.
  • a groove 4 is excluded in the first machine part 2.
  • ER SA TZBLATT has a rectangular cross section in FIG.
  • a sealing ring 5 which is composed of an annular section 6 and a web 7 which projects radially from the annular section 6.
  • the web 7 is formed towards the second machine element 3 and ends in a sealing surface 8 which . is formed in the figure as a sealing edge.
  • the sealing surface 8 rests on a contact surface 9 of the second machine part 3.
  • a clamping ring 11 is arranged on the surface of the sealing ring 5 facing away from the contact surface 9 and a support ring 12 is placed in the groove 4 next to it.
  • the clamping ring 11 consists of an elastomer.
  • the support ring 12 has a higher modulus of elasticity than the sealing ring 5, which is made for example of glass fiber reinforced polytetrafluoroethylene.
  • a pressurized medium can flow into the groove 4 via the gap 10, which presses the sealing ring 5 against a groove flank 14 on the low-pressure side.
  • a groove flank 15 of the groove 4 is then spaced from the sealing ring 5.
  • the clamping ring 11 is arranged between the sealing ring 5 and a groove base 16.
  • the clamping ring 11 is preferably preloaded in the groove 4 and presses the sealing ring 5 with the sealing surface 8 with the preselected prestressing force against the contact surface 9 of the second machine part 3.
  • the support ring 12 On the low-pressure side, the support ring 12 is arranged in the groove 4 next to the clamping ring 11.
  • the support ring 12 has a triangular cross section and is arranged at a distance from the sealing ring 5 in the groove 4. With one side surface, the support ring 12 lies against the groove flank 14 and an inclined surface 17 of the support ring 12 lies against the clamping ring 11 across from.
  • the support ring 12 is made of a hard material, for example metal, and is largely dimensionally stable against forces acting on it.
  • FIG. 2 shows a further sealing arrangement 20 which is installed between a first machine part 21 and a second machine part 22.
  • the seal arrangement 20 seals a gap 23 between the first machine part 21 and the second machine part 22.
  • the sealing arrangement 20 is inserted into a groove 24 in the first machine part 21.
  • a sealing ring 25 made of tough elastic material has a recess 26 on its circumferential surface pointing away from the second machine part 22, which recess receives a support ring 27.
  • the outer diameter of the support ring 27 points to a groove base 28 of the groove 24.
  • a clamping ring 29 is arranged on the sealing ring 25.
  • the groove 24 has groove flanks 30, 31 which limit an axial displacement of the sealing arrangement 20.
  • the sealing ring 25 With a sealing edge 32, the sealing ring 25 bears against a bearing surface 33 of the second machine part 22. The sealing ring 25 is pressed against the bearing surface 33 with the biasing force exerted on the sealing ring 25 by the clamping ring 29. If medium under pressure flows through the gap 23 into the groove 24 in the direction of the arrow 34, the sealing arrangement 20 is spaced from the groove flank 31 and has one end against the groove flank 30 of the groove 24. If the hydraulic pressure becomes greater, the clamping ring 29 can shift towards the low-pressure side and covers the supporting ring 27 in sections or over the entire surface.
  • FIG. 3 shows a further sealing arrangement 40 in the pressure-loaded state, which is installed between a first machine part 41 and a second machine part 42.
  • medium under pressure flows into a gap 44, which has a groove 45 in the first machine part 41 in Connection is established.
  • the gap 44 existing between the first and second machine parts 41, 42 is sealed by the sealing arrangement 40, which consists of a sealing ring 46 which abuts an end face 47 against a groove flank 48.
  • a further groove flank 49 which is connected to the groove flank 48 via a groove bottom 50, delimits the rectangular groove 45 in the first machine part 41.
  • a support ring 51 with a triangular cross section is arranged above the sealing ring 46 on the low-pressure side of the sealing arrangement 40.
  • the support ring 51 With a side 52 running parallel to the groove flank 48, the support ring 51 bears against the groove flank 48.
  • a surface 53 of the support ring 51 which is inclined to the groove base 50 is largely occupied by a clamping ring 54 which has been pushed by the pressurized medium in the groove 45 onto the inclined surface 43 of the support ring 51.
  • the support ring 51 is spaced apart from the sealing ring 46 in the pressureless state and in the pressurized state.
  • the forces acting on the support ring 51 via the tension ring 54 cannot deform the support ring 51 or shift it from its position in the groove 45.
  • a sealing edge 55 of the sealing ring 46 is pressed more or less strongly against a contact surface 56 of the second machine part 42 or it is only exposed to the hydraulic pressure.
  • FIG. 4 shows a further pressure-loaded sealing arrangement 60 which is installed between a first machine part 61 and a second machine part 62.
  • medium under pressure can flow through a gap 64 between the first machine part 61 and the second machine part 62 into a groove 65 of the first machine part 61.
  • a sealing ring 66 of the sealing arrangement 60 is then pressed towards the low-pressure side with an end face 67 against a groove flank 68 of the groove 65.
  • a groove flank 69 of the groove 65 is then spaced apart from the sealing arrangement 60.
  • the sealing ring 66 has in its outer circumferential surface a recess 70 which is suitable for receiving a support ring 71.
  • the support ring 71 In the unpressurized state of the sealing arrangement 60, the support ring 71 is inserted loosely, ie radially displaceably, in the recess 70, and in the pressurized state the support ring 71 transmits no or only slightly forces acting on the sealing ring 66. Between a groove base
  • the clamping ring 73 is shifted to the low-pressure side via the medium under pressure and, as shown in the figure, completely covers the support ring 71.
  • the force acting on the support ring 71 from the tension ring 73 is not or only insignificantly passed on to the sealing ring 66 by the support ring 71.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)

Abstract

Un dispositif d'étanchéité présente, entre deux éléments de machine concentriques (41, 42) se déplaçant l'un par rapport à l'autre, des moyens d'étanchéité (40) comprenant un joint d'étanchéité (46), une bague-support (51) et une bague de tension (54). Le joint (46) est en un matériau élastique résistant, la bague-support (51) présente un module d'élasticité plus élevé que le joint (46), la bague de tension (54) étant constituée par un élastomère. La bague-support (51) est disposée, par rapport à la bague de tension (54), dans une rainure (45) d'un premier élément de machine (41), de telle façon que lorsque le dispositif d'étanchéité (40) est sollicité à la pression, un fluide s'écoulant à l'intérieur de la rainure (45), dans le sens de la flèche (43), applique la bague de tension (54) sur une face oblique (53) de la bague-support (51). La force de pression exercée par le joint (46), à cause de la bague de tension (54), sur une face d'appui (56) peut ainsi être déplacée en grande partie sur la bague-support (51) placée à distance du joint (46), cette distance étant conservée, même sous une sollicitation à la pression.
PCT/DE1991/000423 1990-06-12 1991-05-22 Dispositif d'etancheite WO1991019920A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4018741 1990-06-12
DEP4018741.1 1990-06-12

Publications (1)

Publication Number Publication Date
WO1991019920A1 true WO1991019920A1 (fr) 1991-12-26

Family

ID=6408237

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1991/000423 WO1991019920A1 (fr) 1990-06-12 1991-05-22 Dispositif d'etancheite

Country Status (2)

Country Link
EP (1) EP0533696A1 (fr)
WO (1) WO1991019920A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19734497A1 (de) * 1997-08-08 1999-03-04 Daimler Benz Ag Dichtungsanordnung zur Abdichtung einer Kolbenstange
WO2017041464A1 (fr) * 2015-09-08 2017-03-16 刘付日叁 Nouveau joint d'étanchéité à ultra-haute pression
CN108050129A (zh) * 2017-12-28 2018-05-18 佛山市达曼森密封科技有限公司 一种组合密封结构

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2846896A1 (de) * 1977-10-27 1979-05-03 Caterpillar Tractor Co Dichtungsanordnung
GB2050534A (en) * 1979-04-23 1981-01-07 Shamban & Co W S Seals
US4560174A (en) * 1983-12-02 1985-12-24 Berco S.P.A. Multi lip seal
EP0231673A1 (fr) * 1985-11-25 1987-08-12 Societe Nationale D'etude Et De Construction De Moteurs D'aviation "Snecma" Dispositif composite d'étanchéité
DE3709320A1 (de) * 1987-03-21 1988-09-29 Danfoss As Hydraulische dichtvorrichtung zum abdichten eines ringspalts
DE3739179C1 (de) * 1987-11-19 1989-05-18 Busak & Luyken Gmbh & Co Dichtungsanordnung
DE3906775A1 (de) * 1989-03-03 1990-09-13 Busak & Luyken Gmbh & Co Dichtungsanordnung fuer wellen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2846896A1 (de) * 1977-10-27 1979-05-03 Caterpillar Tractor Co Dichtungsanordnung
GB2050534A (en) * 1979-04-23 1981-01-07 Shamban & Co W S Seals
US4560174A (en) * 1983-12-02 1985-12-24 Berco S.P.A. Multi lip seal
EP0231673A1 (fr) * 1985-11-25 1987-08-12 Societe Nationale D'etude Et De Construction De Moteurs D'aviation "Snecma" Dispositif composite d'étanchéité
DE3709320A1 (de) * 1987-03-21 1988-09-29 Danfoss As Hydraulische dichtvorrichtung zum abdichten eines ringspalts
DE3739179C1 (de) * 1987-11-19 1989-05-18 Busak & Luyken Gmbh & Co Dichtungsanordnung
DE3906775A1 (de) * 1989-03-03 1990-09-13 Busak & Luyken Gmbh & Co Dichtungsanordnung fuer wellen

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19734497A1 (de) * 1997-08-08 1999-03-04 Daimler Benz Ag Dichtungsanordnung zur Abdichtung einer Kolbenstange
DE19734497C2 (de) * 1997-08-08 1999-06-10 Daimler Chrysler Ag Dichtungsanordnung zur Abdichtung einer Kolbenstange
US6217029B1 (en) 1997-08-08 2001-04-17 Daimlerchrysler Ag Seal arrangement for a piston rod
WO2017041464A1 (fr) * 2015-09-08 2017-03-16 刘付日叁 Nouveau joint d'étanchéité à ultra-haute pression
CN108050129A (zh) * 2017-12-28 2018-05-18 佛山市达曼森密封科技有限公司 一种组合密封结构

Also Published As

Publication number Publication date
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