EP1651890A2 - Dispositif d'etancheification axiale d'arbre - Google Patents

Dispositif d'etancheification axiale d'arbre

Info

Publication number
EP1651890A2
EP1651890A2 EP04763447A EP04763447A EP1651890A2 EP 1651890 A2 EP1651890 A2 EP 1651890A2 EP 04763447 A EP04763447 A EP 04763447A EP 04763447 A EP04763447 A EP 04763447A EP 1651890 A2 EP1651890 A2 EP 1651890A2
Authority
EP
European Patent Office
Prior art keywords
shaft seal
sliding partner
axial shaft
seal according
sealing element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP04763447A
Other languages
German (de)
English (en)
Inventor
Gerd Meier
Klaus-Jürgen Uhrner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ceramtec GmbH
Kaco GmbH and Co KG
Original Assignee
Ceramtec GmbH
Kaco GmbH and Co KG
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 DE102004035658.0A external-priority patent/DE102004035658B4/de
Application filed by Ceramtec GmbH, Kaco GmbH and Co KG filed Critical Ceramtec GmbH
Publication of EP1651890A2 publication Critical patent/EP1651890A2/fr
Ceased legal-status Critical Current

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
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • 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
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • F16J15/3264—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals the elements being separable from each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3456—Pressing means without external means for pressing the ring against the face, e.g. slip-ring with a resilient lip

Definitions

  • the invention relates to an axial shaft seal with a counter surface on which at least one sealing surface of a primary seal bears under prestress, a sealing ring for use in such an axial shaft seal and the use of the axial shaft seal.
  • Sealing a shaft bushing with a mechanical seal (GIRD) or with a radial shaft seal (RWDR) is common state of the art.
  • a mechanical seal a spring-loaded, stationary slide ring usually runs against a rotating counter ring. The treads of the rings pressed against one another seal the housing, for example a pump chamber, from the environment.
  • pre-assembled seals in cassette design. Such a preassembled seal is pressed or shrunk onto a shaft, for example, and also seals against the housing after it has been inserted into the housing. Seals of this type have a complex structure and consist of numerous individual parts.
  • Radial shaft seals run, as the name suggests, radially on the shaft to be sealed.
  • the housing is sealed with a static seal.
  • the main seal with respect to the pressure chamber is provided via a generally pre-tensioned radial sealing lip, sometimes with downstream side seals, which can also form a storage space for lubricants or sealants.
  • the sliding / rubbing of the sealing edge on the shaft creates running tracks on the shaft which, after replacing the radial shaft sealing ring, have a disruptive or even destructive effect on the sealing edge of the new seal.
  • the Axial shaft seal consists of an outer ring, which can be inserted into the housing wall in a stationary and sealing manner, with a radially inward-facing sleeve made of a polymeric material in the form of a bellows, which has one or more axially aligned sealing surfaces on its inner edge, and a torsion-proof and sealing element with the shaft connectable inner ring with a radially outwardly directed ring flange designed as an axial counter-sealing surface. Due to its design, this seal is only suitable for sealing large gaps.
  • this seal is only suitable for sealing against unpressurized rooms or rooms with low pressure, since the contact pressure is exerted by the bellows from the surrounding side. If the pressure of the medium to be sealed is greater than the contact pressure of the bellows, the seal leaks.
  • EP 1 239 710 A2 presents an axially acting sealing ring for sealing a shaft against a housing.
  • the sealing ring comprises a metal housing on which a seal is formed, which is oriented in the direction of the housing, and an axial sliding ring made of PTFE, which has a substantially rectangular profile, with a radially inward and a radially outward Circumferential surface extending substantially parallel to the axis of the sealing ring.
  • the slide ring is elastically accommodated by means of a plastic which is molded onto the metal housing, and is non-positively and positively connected.
  • the contact pressure of the seal must be applied against the pressure of the medium to be sealed.
  • the components of this seal are not combined to form a unit that can be installed.
  • the invention has for its object to provide an axial shaft seal with a structurally simple structure that seals securely even when exposed to high pressures, and sealing elements for use in such an axial shaft seal.
  • the object is achieved with the aid of the characterizing features of claim 1 and claim 21.
  • Advantageous embodiments of the invention are claimed in the further claims, possible areas of application of the axial shaft seal according to the invention are claimed in claims 38 to 42.
  • the axial shaft seal according to the invention can be constructed in different versions:
  • the axial shaft seal consists of a stationary and a rotating housing part, both housing parts enclosing a sliding partner, usually a ring, as a counter surface.
  • the counter-running surface can also be a surface of a housing part coated with hard material.
  • At least one sealing surface of a sealing element seals between the sliding partner with its counter surface and a housing part.
  • the sliding partner can be firmly connected to the rotating or the stationary housing part. However, it can also be arranged in the housing in a freely rotatable manner and thus execute a relative movement with respect to the housing parts. In this case, the sliding partner can be arranged between two sealing elements, one that is arranged on the stationary and one that is arranged on the rotating housing part.
  • Composites based on metal-ceramic compounds are one group.
  • the basic composition of a preferably used metal-ceramic composite material consists of one or more metallic phases with a proportion of 30 to 75 vol .-%, preferably aluminum and its alloys, and one or more non-metallic inorganic components with a share of 25 to 75 vol .-% as ceramic materials, preferably silicon carbides, aluminum oxides, titanium oxides and silicates.
  • Oxidic materials based on aluminum oxide, zirconium oxide or titanium oxide and silicate materials are also suitable.
  • metallic materials preference is given to using materials based on corrosion-resistant steels. Materials based on non-ferrous metals are also used. Due to their porosity, metallic sintered materials can be impregnated with oils, wax or fats.
  • composite materials have a base of carbon compounds, with and without impregnation, or plastic compounds, with and without fiber reinforcement.
  • Sintered silicon carbide bodies which preferably have a defined porosity of 2 to 15% by volume, are particularly suitable for difficult tribological uses, the pores being closed and not connected.
  • the inorganic component of the material consists of 80 to 98 wt .-% silicon carbide, 0.5 to 5 wt .-% carbon, 0.3 to 5 wt .-% boron and 0 to about 20 wt .-% of a hard material from the Group of the borides and / or silicides. It is possible to store carbon particles up to 200 ⁇ m in size.
  • Silicon carbide can also be sintered with another component, preferably zirconium diboride in a proportion of 6% by volume. Silicon carbide can also be infiltrated, for example with metallic silicon, preferably with 12 to 19% by volume.
  • these housing parts which form the counter surface, can be made of a material suitable for this purpose and / or coated.
  • the coating can for example, hard metal, carbide or diamond-like carbon deposited from the plasma phase.
  • PTFE materials are particularly suitable as the material for the sealing element because of their wear resistance and their resistance to hot and aggressive media.
  • the sealing elements can be subjected to plasma activation and receive a reinforcement component.
  • a sliding component such as graphite can be added.
  • the sealing elements can be glued, riveted or screwed to their holder or carrier or clamped between two holders.
  • At least one further sealing element can additionally seal the sliding partner in a radial direction with respect to the stationary housing.
  • the space between the sliding partner, the sealing element and the rotating housing can be used as a reservoir for sealing and / or lubricants or blocking agents.
  • the invention reduces the number of components compared to the prior art, and it results in a simple design. Due to the inherent preload, additional pressure elements, such as springs, are not necessary. It is advantageous if the medium to be sealed exerts a force on the sealing part of the primary seal, so that this sealing part is additionally loaded by its own preload and by the medium pressure in the direction of its sealing position.
  • a cassette design enables easy assembly and interchangeability of the axial shaft seal. The installation space is significantly shorter compared to a mechanical seal. Compensation of manufacturing and assembly tolerances is possible. It is also possible to compensate for system faults in operation. When using appropriate sliding partners tribologically and thermally optimal conditions possible. There is also the option of one-time lubrication against dry running.
  • the shaft and housing bore can e.g. in tolerance class IT7 with roundness IT7 and surface Rz 10 ⁇ m.
  • FIGS. 1 to 11 exemplary embodiments of the axial shaft seal according to the invention are shown in section in schematic form.
  • an axial shaft seal in the form of a cassette seal 1 is shown in FIG. 1, which is arranged between a shaft 2, on which it is shrunk, and a housing 3, for example a pump housing.
  • the cassette seal 1 seals between the medium space 4 and the surroundings 5. It is inserted into a recess 6 as the installation space of the housing 3.
  • the cassette seal 1 consists of two housing parts, the stationary housing part 7 and the rotating housing part 8 shrunk onto the shaft 2, both of which look L-shaped in section.
  • the peripheral wall 9 of the stationary housing part 7 is supported on the end face in the recess 6 on the housing 3 and is sealed off from the installation space 6 by a static sealing element 10.
  • the radial end wall 11 facing the environment 5 carries a sealing element 12, the primary seal, which bears with its sealing surface 12a on the counter surface of the sliding partner 13.
  • the sealing element 12 is elastically bent in an approximately U- or V-shape in axial section.
  • the sliding partner 13 can be made of metal, non-ferrous metal, hard metal, plastic, ceramic, glass, glass fiber or composite materials to produce optimal tribological conditions.
  • the sliding partner 13 is a ring in the present exemplary embodiment. In the present exemplary embodiment, it is connected to the radial end wall 14 of the rotating housing part 8, the opposite side of the end wall 14 facing the medium space 4.
  • the sliding partner 13 can also be arranged so that it can move freely Can perform relative movements to the end wall 14.
  • the peripheral wall 15 of the housing part 8 is shrunk onto the shaft 2. With a conical extension 16 pointing away from the shaft 2, the stationary housing part 7 is held in position, which is overlapped by the extension 16.
  • the end wall 14 of the housing part 8 ends at a distance from the cylindrical peripheral wall 9 of the housing part 7, so that the interior 17 of the cassette seal 1 is open to the medium space 4.
  • the sliding partner 13 is radially opposite the end face of the end wall 14 of the rotating housing part 8.
  • the space 17 in the cassette seal 1 between the sealing element 12 and the two housing parts 7 and 8 can be used as a reservoir for sealants and / or lubricants or blocking agents. This means that special requirements such as dry running or odor tightness can also be mastered.
  • the advantage over the prior art is furthermore that the sealing element 12 is loaded from the pressure side in such a way that it is additionally pressed against the sliding partner 13, which supports the seal.
  • Figures 2 and 3 differ from Figure 1 in the arrangement of the sliding partner 13 with its counter surface and the arrangement of the sealing elements. Matching features are identified by the same reference numbers.
  • the sliding partner 13 is arranged in the form of a ring between two sealing elements 18 and 19 freely movable.
  • Sealing element 18 as the primary seal is fastened to the end wall 11 of the stationary housing part 7 and presses with its sealing surface 20 against the mating surface of the sliding partner 13, while sealing element 19 is fastened as a further primary seal to the end wall 14 of the rotating housing part 8 and with its sealing surface 21 against the Sliding partner 13 presses.
  • a freely movable sliding partner 13 the friction with one of the housing walls is thus avoided.
  • two usable reservoirs 17 are formed under the respective sealing elements 18 and 19. Furthermore there is a relative movement between the sliding partner 13 and the two sealing elements.
  • the sealing element 19 tries to take the ring 13 with it and on the other hand the sealing element 18 inhibits this movement on the fixed housing.
  • Such axial shaft seals are advantageously suitable for high speeds, such as those that occur in turbochargers.
  • the radially inner end of the annular sliding partner 13 engages in a groove 60 of a ring 61 which surrounds the cylindrical peripheral wall 15 of the rotating housing part 8 at a distance. Otherwise, this embodiment has the same design as the embodiment according to FIG. 1.
  • Figure 3 differs from Figure 2 in that an additional sealing element 22 is provided which, in addition to the two primary seals 18 and 19, is fastened on the inside to the peripheral wall 9 of the stationary housing part 7, concentrically surrounds the sliding partner 13 and presses against its peripheral side 23.
  • the sealing element 23 lies flat against the peripheral wall 9 and has in the center a radially projecting, circumferential rib 62 with which the sealing element 22 bears against the peripheral side 23 of the sliding partner 13.
  • the rib 62 advantageously has a partially round cross section.
  • FIG. 4 shows an axial shaft seal 100 constructed differently from the concept.
  • the sealing element 24 is the primary seal on the rotating one Fastened housing part 8 and rests with its sealing surface 25 on the mating surface of the sliding partner 13, which is fastened to the stationary housing part 7.
  • the dashed contours of the sealing surface 25 and the sliding partner 13 indicate the possibility of axial displacement.
  • the centrifugal force of the rotating sealing surface supports the system on the sliding partner. If the medium 4 is under pressure, the installation of the sealing element is also supported.
  • the stationary housing part 7 is provided with a conical narrowing 63 at the free end of the peripheral wall 9.
  • the sliding partner 13 bears against the radially inwardly projecting end wall 11 of the housing part 7.
  • the rotating housing part 8 which is seated in a rotationally fixed manner on the shaft 2, has the radially outwardly projecting end wall 14, the free end of which is bent by 180 ° and encompassed by the sealing element 24. It has a small radial distance from the peripheral wall 9 of the housing part 7.
  • the end wall 11 of the housing part 7, the sliding partner 13 and the sealing element 24 have a radial distance from the peripheral wall 15 of the housing part 8.
  • the exemplary embodiment according to FIG. 5 differs from the previous exemplary embodiment by the arrangement and mounting of the sealing element 26, which is fastened to the leg 14 of the rotating housing part 8 with a holding element 27.
  • the holding element 27 is a clamping disk, which sits on the shaft 2 in a rotationally fixed manner and lies in a radial plane.
  • the sealing element 26 is clamped between the holding element 27 and the radial end wall 14 of the rotating housing part 8.
  • the free end 28 of the holding element 27, which is at a distance from the peripheral wall 9 of the stationary housing part 7, is curved in an arcuate cross section. With the bent end part 28, the sealing element 26 is deflected against the sliding partner 13.
  • the pressing of the sealing surface 29 against the mating surface of the sliding partner 13 is supported by a plate spring or finger spring 30. Since the end wall 11 of the housing part 7 and the sliding partner 13 have a distance from the peripheral wall 15 of the housing part 8, the Medium space 4 is connected to the space 64 accommodating the spring 30, so that the pressure acting in the medium space 4 supports the pressing of the sealing surface 29 of the sealing element 26 against the mating surface of the sliding partner 13.
  • the design of the exemplary embodiment according to FIG. 6 again corresponds to the exemplary embodiments according to FIGS. 1 to 3, in which the sealing element 31 is fastened to the stationary housing part 7.
  • the sealing element 31 as the primary seal of the axial shaft seal 1 is clamped between the leg 11 of the stationary housing part 7 and a holding element 32.
  • the stationary housing part 7 has the peripheral wall 9, the free end 65 of which extends radially outwards.
  • the peripheral wall 5 merges into the end wall 11 which, in contrast to the previous exemplary embodiment, converges with respect to the end wall 14 of the rotating housing part 8.
  • the free end 34 of the end wall 11 is bent in the direction of the end wall 14 of the housing part 8, so that the deflection of the sealing element 31 is facilitated.
  • With the sealing surface 33 the sealing element 31 bears against the mating surface of the sliding partner 13, which bears against the end wall 14 of the rotating housing part 8.
  • the annular holding element 32 is V-shaped in axial section and bears with a cylindrical jacket 66 on the inside of the peripheral wall 9 of the housing part 7.
  • the sloping leg 67 of the holding element 32 presses the sealing element 31 against the end wall 11 of the housing part 7.
  • the end wall 14 of the housing part 8 and the sliding partner 13 lie axially in front of the free end 65 of the housing part 7.
  • the interior of the seal 1 is connected to the medium space 4, so that the medium pressure can support the sealing effect in the manner described.
  • An axial play in the bearing can also be compensated for.
  • the stationary housing part 7 has a Z-shaped shape in axial section.
  • the cylindrical peripheral wall 9 that is Housing part 7 on the wall of the receiving space of the housing 3.
  • the free end 65 of the housing part 7 is angled radially outwards and lies against the end face of the housing 3.
  • the radially inner cylindrical wall 11 of the housing part 7 surrounds the shaft 2 at a distance.
  • the sealing element 35 is fastened to the inside of the wall 11. It has an outwardly curved leg 80 which rests on the sliding partner 13 in a sealing manner under elastic deformation. For its part, it bears against the end wall 14 of the rotating housing part 8. It sits with the peripheral wall 15 on the shaft 2 in a rotationally fixed manner.
  • the peripheral wall 15 extends axially outward and thus does not protrude into the seal 1. It is open to the medium side 4, so that the medium pressure can act on the sealing surface 36.
  • the dashed contour of the sealing surface 36 and the sliding partner 13 show that an equalization of axial play is also possible here.
  • the exemplary embodiment according to FIG. 8 differs from the previous exemplary embodiment in that the leg 14 of the rotating housing part 8 itself forms the sliding partner.
  • the leg 14 is inclined at an angle 37 of 45 ° against the shaft 2 in the present embodiment. Its sliding surface 39 facing the sealing element 38 can be provided with a wear-preventing coating 40, against which the sealing surface 41 of the sealing element 38 bears.
  • the leg 14 is advantageously parallel to the opposite web 68 of the housing part 7 and ends at a distance from the circumferential wall 9. This in turn creates a connection between the medium side 4 and the interior 17 of the seal 1.
  • FIG. 9 shows an exemplary embodiment for a double seal.
  • the rotating housing part 8 shrunk on the shaft 2 is U-shaped in axial section. Extending perpendicularly to the shaft 2 from the peripheral wall 15 seated on the shaft 2 are two legs 141 and 142, on the inside of which the sealing surfaces 431 and 432 bear from the curved sealing element 42 which projects into the profile of the housing part 8 in a U-shaped manner in axial section.
  • the stationary housing part 7 has the on the inner wall of the receiving space of the housing 3rd adjacent peripheral wall 9, which has the radially inwardly projecting fleece 69 at the free end.
  • the peripheral wall 9 merges into the radially inward end wall 11, the free end 44 of which is bent somewhat semicircularly in the direction of the flange 69.
  • the sealing element 42 is fastened to this end 44.
  • the end 44 lies centrally between the two legs 141, 142 of the rotating housing part 8, which are preferably of equal length.
  • the leg 142 is at a small axial distance from the flange 69, which overlaps it slightly in the radial direction.
  • the leg 142 also ends at a distance from the peripheral wall 9 of the stationary housing part 7.
  • the other leg 141 lies at a distance from the end wall 11 of the housing part 7.
  • the sealing element 42 is fastened to the arcuate end 44 of the leg 11 of the stationary housing part 7 by that it is pressed into the U-profile of the rotating housing part 8.
  • the legs 141 and 142 can be provided with a wear-reducing coating 45 on the sliding surface.
  • the area between the sealing element 42 and the housing part 7 or the wall of the housing receiving space is open to the medium or to the surrounding side 4, 5.
  • the function of the embodiment according to FIG. 10 corresponds to the embodiment according to FIG. 1.
  • the stationary housing part 7 lies with its cylindrical peripheral wall 9 against the wall of the receiving space of the housing 3.
  • the end of the peripheral wall 9 facing away from the air side 5 merges into the radially inwardly extending end wall 11.
  • the end wall 11 merges into a cylindrical circumferential wall 46 surrounding the shaft 2, which extends from the end wall 11 in the same direction as the radially outer circumferential wall 9.
  • the sealing element 48 used as the primary seal is between the circumferential wall 46 of the housing part 7 and a cylindrical part 70 of the holding element 47 inserted, for example glued.
  • the end wall of the peripheral wall 46 of the housing part 7 bears against a radially outward leg 71 of the holding element 47.
  • the part of the sealing element 48 projecting in the direction of the sliding partner 13 is elastically bent radially outwards and, with its sealing surface 49, lies sealingly against the counter-running surface of the sliding partner 13.
  • the sliding partner 13 is axially supported on the radially outwardly directed end wall 14 of the housing part 8, which is seated in a rotationally fixed manner on the shaft 2, and projects radially beyond the end wall 14. Between the sliding partner 13 and the wall of the receiving space of the seal 1, there is a passage from the medium side 4 to the interior of the seal 1. Because of the flexibility of the sealing material, the sealing element 48 can compensate for slight axial displacements.
  • FIG. 11 shows a cassette seal in a multi-lip design. It is particularly suitable for sealing abrasive media.
  • the stationary housing part has the radial end wall 11, which merges radially on the inside into a cylindrical extension 50 surrounding the sealing shaft 2 at a distance. With the radially outer peripheral wall 9, the stationary housing part 7 bears against the inner wall of the receiving space of the housing 3.
  • the peripheral wall 9 merges into the loop 65, which is angled outwards at right angles and with which the housing part 7 bears against the housing 3.
  • a profile ring 51 which is U-shaped in axial section is inserted. With it, two annular sealing elements 52, 53 are clamped.
  • the sealing element 52 is clamped with its cylindrical jacket 72 between the peripheral wall 9 and the cylindrical jacket 73 of the profile piece 51 and the sealing element 53 with its cylindrical jacket 74 between the extension 50 and the radially inner cylindrical jacket 75 of the profile piece 51.
  • the sealing elements 52, 53 can be glued.
  • the jacket 72, 74 of the sealing elements 52, 53 and the two jacket sections 73, 75 of the profile piece 51 are coaxial to the shaft 2, which surround them at a distance.
  • the ends 76, 77 of the sealing elements 52, 53 projecting beyond the profile piece 51 are elastically bent in the direction of one another and lie with their radial ones Sealing surfaces 54, 55 in a sealing manner on the radial end wall 14 of the housing part 8 seated in a rotationally fixed manner on the shaft 2.
  • It is U-shaped in axial section and has the peripheral wall 15 with which the housing part 8 sits on the shaft 2.
  • the peripheral wall 15 is connected via the end wall 14 to a cylindrical jacket 56 which lies approximately at the level of the jacket 72 of the sealing element 52.
  • Another sealing element 57 with a cylindrical sealing surface 58 rests on the jacket 56.
  • the annular sealing element 57 is fastened to the radially outwardly directed flange 65 of the housing part 7.
  • the sealing element 57 is glued to the stationary housing part 7.
  • the jacket 56 can be coated against wear, but can also wear a ceramic ring as a sliding partner.
  • the abrasive medium 4 can lead to premature wear of the sealing surface 58 before the other sealing surfaces 54 and 55 wear out.
  • the sealing element 57 can still act as a labyrinth in the state of wear.
  • a grease filling 59 can be provided in the profile piece 51, which is enclosed by the sealing elements 52 and 53.
  • the radially outer sealing element 52 prevents the grease 59 from escaping, so that the radially inner sealing element 53 can work under optimal tribological conditions and a long service life with an optimal seal is thereby ensured.
  • the sealing elements are installed in such a way that they are elastically deformed as much as possible in the form of an annular disk and thus rest under their own tension with their sealing surface on the mating surface of the sliding partner. Furthermore, due to the arrangement described, the sealing element is additionally subjected to pressure by the medium, so that its sealing surface is pressed against the mating surface of the sliding partner. The sealing effect is supported in an advantageous manner.

Landscapes

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

Abstract

L'invention concerne un dispositif d'étanchéification axiale d'arbre comprenant une surface antagoniste de roulement d'un élément de glissement correspondant, contre laquelle la surface d'étanchéité d'au moins un élément d'étanchéité primaire repose de façon à être précontrainte. Cette invention se rapporte en outre à des éléments d'étanchéité destinés à être utilisés dans ledit dispositif d'étanchéification axiale d'arbre. L'objectif de cette invention est de créer un dispositif d'étanchéification axiale d'arbre présentant une structure simple et assurant une étanchéité fiable même lorsqu'il est soumis à des pressions élevées. A cet effet, l'étanchéification axiale est assurée par précontrainte propre d'un élément d'étanchéité primaire (12) à déformation élastique qui présente une forme annulaire au moins dans la zone d'étanchéité.
EP04763447A 2003-07-25 2004-07-23 Dispositif d'etancheification axiale d'arbre Ceased EP1651890A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10334268 2003-07-25
DE102004035658.0A DE102004035658B4 (de) 2003-07-25 2004-07-22 Axialwellendichtung
PCT/EP2004/008273 WO2005010412A2 (fr) 2003-07-25 2004-07-23 Dispositif d'etancheification axiale d'arbre

Publications (1)

Publication Number Publication Date
EP1651890A2 true EP1651890A2 (fr) 2006-05-03

Family

ID=34105480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04763447A Ceased EP1651890A2 (fr) 2003-07-25 2004-07-23 Dispositif d'etancheification axiale d'arbre

Country Status (2)

Country Link
EP (1) EP1651890A2 (fr)
WO (1) WO2005010412A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101913398B (zh) * 2010-08-30 2012-09-26 重庆隆鑫机车有限公司 一种计速装置
US20160069457A1 (en) 2013-04-22 2016-03-10 Carl Freudenberg Kg Slide ring seal
DE112014004893T5 (de) * 2013-10-23 2016-07-14 Borgwarner Inc. Drehbetätigungswellen-Gleitringdichtung mit U-Dichtung
DE102017204374A1 (de) * 2017-03-16 2018-09-20 Trelleborg Sealing Solutions Germany Gmbh Dichtungsanordnung
DE102019219765A1 (de) * 2019-12-16 2021-06-17 Volkswagen Aktiengesellschaft Anordnung zur Abdichtung einer Dichtzone

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB499729A (en) * 1937-07-12 1939-01-27 Warman Charles Harold Improvements in sealing devices for rotational members
DE1239710B (de) 1964-04-06 1967-05-03 Eastman Kodak Co Blatt-Tastvorrichtung
IT950581B (it) * 1971-01-15 1973-06-20 Mecanique Ind Int Dispositivo di tenuta tra un ele meto fisso ed un elemento rotante
JPS54133256A (en) * 1977-12-08 1979-10-16 Taiho Kogyo Co Ltd Slider material for shaft sealing
JPS5670169A (en) * 1979-11-13 1981-06-11 Taiho Kogyo Co Ltd Mechanical seal
US4484752A (en) * 1984-03-08 1984-11-27 Federal-Mogul Corporation Rotating-lip bidirectional hydrodynamic oil seal
DE3733730C1 (de) * 1987-10-06 1988-10-27 Feldmuehle Ag Gleit- oder Dichtelementepaarung und Verfahren zu deren Herstellung
US4765632A (en) * 1987-11-23 1988-08-23 Alterio Joseph C D Lubricated rotary shaft seal
DE3833690A1 (de) * 1988-10-04 1990-04-12 Acla Werke Gmbh Radialwellendichtung
US5395807A (en) * 1992-07-08 1995-03-07 The Carborundum Company Process for making silicon carbide with controlled porosity
US6338906B1 (en) * 1992-09-17 2002-01-15 Coorstek, Inc. Metal-infiltrated ceramic seal
DE4401567C1 (de) * 1994-01-20 1995-02-23 Heinz Konrad Prof Dr I Mueller Wellendichtung
DE19922842A1 (de) * 1999-05-19 2000-11-23 Kaco Gmbh Co Radialwellendichtring
DE19947007A1 (de) * 1999-09-30 2001-07-26 Zexel Valeo Compressor Europe Wellenabdichtung, insbesondere für Axialkolbenverdichter
DE10047701A1 (de) * 2000-09-25 2002-04-25 Freudenberg Carl Kg Dichtmanschette
DE10203751A1 (de) * 2001-02-16 2002-08-29 Ceram Tec Ag Innovative Cerami Keramischer Werkstoff auf der Basis von Aluminiumoxid und daraus hergestellte Sinterformkörper
DE20105558U1 (de) * 2001-03-29 2001-07-12 Bode GmbH, 22549 Hamburg Dichtung für Wellen
DE10228621B4 (de) 2002-06-26 2020-02-27 Carl Freudenberg Kg Axialwellendichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005010412A2 *

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