WO2023147938A1 - Joint d'étanchéité de train de roulement à dispositif anti-rotation et ses composants - Google Patents

Joint d'étanchéité de train de roulement à dispositif anti-rotation et ses composants Download PDF

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Publication number
WO2023147938A1
WO2023147938A1 PCT/EP2022/087956 EP2022087956W WO2023147938A1 WO 2023147938 A1 WO2023147938 A1 WO 2023147938A1 EP 2022087956 W EP2022087956 W EP 2022087956W WO 2023147938 A1 WO2023147938 A1 WO 2023147938A1
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WO
WIPO (PCT)
Prior art keywords
ring
housing
locking elements
locking
circumferential direction
Prior art date
Application number
PCT/EP2022/087956
Other languages
German (de)
English (en)
Inventor
Fabian Goedde
Original Assignee
Federal-Mogul Friedberg Gmbh
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 Federal-Mogul Friedberg Gmbh filed Critical Federal-Mogul Friedberg Gmbh
Publication of WO2023147938A1 publication Critical patent/WO2023147938A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/344—Pressing means the pressing force being applied by means of an elastic ring supporting the slip-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
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3452—Pressing means the pressing force resulting from the action of a spring
    • 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
    • F16J15/3464—Mounting of the seal
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/18—Freewheels or freewheel clutches with non-hinged detent
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/18—Freewheels or freewheel clutches with non-hinged detent
    • F16D41/185—Freewheels or freewheel clutches with non-hinged detent the engaging movement having an axial component
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/2028—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving radially between engagement and disengagement

Definitions

  • the present invention relates to drive seals and components of drive seals as well as a housing for accommodating a drive seal or a shape of a seat for a drive seal in a housing.
  • Undercarriage seals are usually used on drive axles or rollers of earth-working machines that are operated at relatively low speeds under harsh operating conditions.
  • Common areas of application are the chain drives of crawler vehicles, bulldozers, chain excavators or axle seals of wheel drives of wheel excavators, loaders, graders and other machines that are used in earthworking and under comparable conditions. For example, they protect the bearing points on the rollers of the chain drive on construction machinery or excavators from foreign bodies such as sand and dust.
  • Running gear seals are rotary seals and represent a special design of mechanical seals.
  • the running gear seals consist of two geometrically identical sliding rings that are installed opposite one another in separate housings. One slip ring remains static while another rotates.
  • Asymmetrical designs, i.e. sliding rings with unequal geometries, are also known.
  • the sliding rings are prestressed against each other by respective elastomer elements and seal the respective sliding ring against the respective housing.
  • the actual sealing takes place at the contact surface of the lapped running surfaces of the sliding rings that are in contact with one another.
  • Mechanical seals are usually operated at a relative speed of less than 2 to 3 m/s and with oil lubrication of a maximum of 10m/s, which means that they cannot be used in fast-moving vehicles and rapidly rotating shafts or axles.
  • the seal rings are made rotationally symmetrical, with static friction between the elastomer elements and the respective housing or seal ring preventing the seal rings from twisting relative to the respective housings.
  • the mechanical seal and the mounting via elastomer elements ensure that deformations that occur on the axles, housings or the drive are decoupled from the sliding rings, thus preventing leakage at the sealing gap between the sliding rings.
  • the present invention therefore relates to a carriage seal and the parts of a carriage seal that enable simple anti-rotation protection between a sliding ring and an associated housing or also a housing, shaft or axle flange.
  • a housing and a housing flange no distinction is made between a housing and a housing flange.
  • a sliding ring for a drive seal or a drive seal comprising a sliding surface and at least one contact surface for an elastomer ring.
  • the sliding ring is provided with at least two projecting resilient locking elements arranged in the circumferential direction, which can be designed in particular as locking pawls or locking springs, and which are set up to engage in corresponding engagement structures running in the circumferential direction in a housing or an axle or shaft flange.
  • the locking elements provide a kind of free wheel, whereby each of the locking elements allows movement in one direction but prevents movement in an opposite direction directly or after a certain angle of rotation.
  • the present invention thus enables a simpler installation in which it is not necessary to pay attention to a mutual alignment of a slide ring with respect to a housing. Even during a trial run, the slide rings can move with respect to their housing parts to be sealed until one or the blocking elements engage in one or a respective engagement structure and prevent further rotation. As a result, the maximum path of the rotational movement of the sliding ring relative to a housing or a flange is limited, so that no significant wear can occur.
  • the blocking elements each point in the same circumferential direction.
  • the blocking elements form a kind of freewheel, whereby this design can be used if the carriage has only one direction of rotation.
  • an even number of locking elements is provided, with one half of the locking elements in one Have circumferential direction, and another half of the locking elements are aligned opposite to the circumferential direction.
  • the blocking elements form freewheels connected in opposite directions, so that the slide ring is fixed in both directions of rotation.
  • a certain freedom of movement can be provided here, which allows smaller rotary movements of the slide ring relative to the housing / flange, but a longer movement that would cause greater wear of the elastomer ring is excluded.
  • An additional embodiment of the present invention relates to an embodiment in which half of the locking elements that point in the circumferential direction are spaced radially and/or axially from the other half of the locking elements that are oriented opposite to the circumferential direction. In this way, two freewheels connected in opposite directions are realized, which can act locally independently of one another and can thus prevent any major movement both in one and in the other circumferential direction.
  • the blocking elements extend in the axial direction, in the radial direction, in the radial and axial direction and/or at an angle of between 15° and 60° to an axial direction. It should be made clear here that different arrangements and orientations of the blocking elements are possible.
  • the blocking elements are arranged regularly in the circumferential direction. In an additional embodiment of the sliding ring, pairs of two blocking elements directed towards one another are regularly arranged in the circumferential direction. In another additional embodiment of the sliding ring, the blocking elements are arranged in the circumferential direction with a rotational symmetry of between 1° and 180°, preferably between 2° and 60° and more preferably between 1° and 30°.
  • the contact surface for an elastomer ring forms a conical surface, which is preferably rounded and broadened at a base.
  • a contact surface for an elastomer ring that is essentially circular or oval in cross section is described here, as is known in the case of running gear seals.
  • the blocking elements are arranged either inside the conical surface or outside of the conical surface. The blocking elements are preferably provided within the conical surface since they are protected there from external influences such as dirt and damage.
  • the blocking elements can also be provided radially outside of the elastomer ring if this is advantageous because of the media to be sealed or because of the mechanical design, such as in a countersunk arrangement of the drive seal in a housing.
  • the contact surface can be set up for contact with an elastomer ring with a trapezoidal or rhombic profile.
  • the geometry can be selected appropriately, with a radial outer ring surface and an axial ring surface being conventionally combined, it also being possible, for example, to combine two cone-shaped ring surfaces.
  • a combined radial and axial support with two mutually perpendicular cut surfaces in the profile is preferred.
  • the blocking elements are designed as blocking springs or blocking leaf springs, which are set up to engage in corresponding depressions on a flange.
  • the blocking elements are designed as spring-loaded, essentially straight rods which can resiliently engage in corresponding recesses in a flange or housing in the axial and/or radial direction and are not or not significantly subjected to bending when loaded in the blocking direction .
  • a rod-shaped blocking element can be designed as a screw which can be deflected in the radial and axial direction via a ball joint and an elastomer element.
  • Such a locking bar can absorb much higher forces than a spring, even if the load is uneven.
  • a housing or a shaft or axle flange which is set up to accommodate an elastomer ring and a slide ring as described above.
  • the housing or the shaft or axle flange includes at least one contact surface for an elastomer ring.
  • the housing or shaft or axle flange is provided with a circumferential engagement structure adapted to engage or engage at least one resilient locking member of a slip ring. If the sliding ring includes pawls, for example, the counterpart is provided with a corresponding structure in which the pawls can engage.
  • a rectangular structure is provided here, which allows it to serve as an abutment for pawls in both directions.
  • This has the advantage that, depending on the application, pawls can engage in both directions.
  • a freewheel or a pawl can serve as a freewheel in both directions with a rectangular, trapezoidal or symmetrical triangular structure, depending on whether the pawls are arranged in one direction, against one direction or in the opposite direction.
  • a drive profile as known from screw heads and wrenches, it is not intended here that the structure of the housing / flange engages directly.
  • the engagement structure running in the circumferential direction is regular and/or has a rotational symmetry of between 1° and 90°, preferably between 2° and 45° and more preferably between 1° and 30° on.
  • a regular rotational symmetry with a maximum of a quarter turn, an eighth turn or a twelfth turn is described here.
  • the circumferential engagement structure extends in the axial direction, in the radial direction, in the radial and axial direction, or at an angle of between 15° and 60° to an axial direction.
  • Pockets are described here which extend in the axial direction and/or in the radial direction and preferably run obliquely so that straight locking elements can also engage in the pockets of the structures.
  • the contact surface for an elastomer ring forms a conical surface.
  • a contact surface for an elastomer ring that is essentially circular in cross section described with a transition to a stop in the axial direction is usually rounded.
  • the contact surface is designed for an elastomer ring with a trapezoidal or rhombic profile.
  • a combination of at least one sliding ring described above with at least one elastomer ring and a housing described above and/or a shaft or axle flange described above is also provided. So at least half a running gear seal and at most a complete running gear seal is provided, with the two sliding rings preferably being of the same design in relation to the anti-twist device or the blocking elements in the case of the complete running gear seal.
  • two slip rings as described above and two associated elastomeric rings are provided.
  • This version relates to two half running gear seals and thus a set of parts to replace a running gear seal whose running surfaces or sealing surfaces are damaged.
  • a sliding ring for a drive seal having a sliding surface and at least one abutment surface for an elastomeric ring, which is additionally provided with a circumferentially extending engagement structure.
  • the engagement structure forms pockets in which corresponding locking elements that are arranged on a housing or on a shaft or axle flange can engage.
  • the engagement structure running in the circumferential direction is regular.
  • the engagement structure running in the circumferential direction has a rotational symmetry of between 1° and 45°, preferably between 2° and 30° and more preferably between 1° and 15°.
  • a uniform distribution of the engagement structures or an arrangement of engagement structures that repeats itself at least in the circumferential direction is described.
  • the engagement structures arranged in the circumferential direction extend in the axial direction and/or in the radial direction, in the radial and axial direction or at an angle of between 15° and 60° to an axial direction. Pockets or cutouts are described here that allow a locking element to engage in different directions.
  • a resilient engagement is provided in an axial direction, so that the sliding ring enables an axial displacement of the locking element or elements in the axial direction without having to carry out a corresponding orientation in the circumferential direction.
  • the resilient locking elements can spring into and engage in the engagement structures when the slide ring rotates with respect to the housing or an associated flange, and thus prevent rotational movement of the slide ring.
  • the contact surface for an elastomer ring forms a conical surface.
  • a contact surface is provided for an elastomer ring with a substantially circular or oval-round cross-section, which exerts a radial 5 and axial force component on the seal ring in order to press the running surface of two seal rings together.
  • the contact surface is designed for an elastomer ring with a trapezoidal or rhombic profile.
  • the engagement structure is set up for engagement with at least one resilient locking element, in particular a pawl or locking spring. It is also contemplated that the pawl will be a locking pin extending in multiple directions at a point of attachment
  • a housing or shaft or axle flange or also a housing flange with at least one contact surface for an elastomer ring is provided, wherein at least two projecting resilient locking elements are provided which are arranged in the circumferential direction and are set up in corresponding 25 running in the circumferential direction Engagement structures in a slide ring for a
  • the locking elements can be designed as pawls or locking springs.
  • the term pawl is not only limited to known pawls that can only pivot in one direction, but should also include rods that are pivoted in two dimensions.
  • This embodiment 30 is the counterpart to the sliding rings with those arranged in the circumferential direction
  • the blocking elements each point in the same circumferential direction.
  • the blocking elements act like a freewheel, with such an embodiment only being intended for areas of application in which the shaft or the axle which is provided with the running gear seal only has one direction of rotation.
  • Vehicles that are only moved in one direction such as tunnel boring machines, pipeline laying machines and the like, can dispense with a separate locking device for a reverse direction.
  • housing or shaft or axle flange there is a symmetrical number of locking elements, with half of the locking elements each pointing in a circumferential direction and another half of the locking elements being oriented opposite to the circumferential direction.
  • the blocking elements form ⁇ 45 each against each other connected freewheels, with a movement of the slip rings
  • the blocking elements extend in the axial direction, in the radial direction, in the radial and axial direction or at an angle of between 15° and 60° to an axial direction.
  • the locking elements are arranged essentially tangentially
  • a slide ring can thus be used without the blocking elements interfering with assembly, regardless of whether they are currently engaged with the engagement structures or are spring-backed. During operation, the blocking elements can then engage in a next engagement structure during a rotary movement of the slide rings and thus fix the slide ring. Depending on the possible mutual movement of the
  • the locking elements and the engagement structures should be able to compensate for slight axial and radial movements and bearing play of the shaft in the housing. Rigid guidance of the blocking elements could lead to jamming. It is therefore envisaged that the blocking elements in preferred embodiments can either move in 2 dimensions or be sufficiently elastic,
  • the blocking elements are arranged regularly in the circumferential direction. It can also be provided that in a further embodiment, the arrangement of the blocking elements
  • housing, shaft or axle flange is designed in such a way that the contact surface for an elastomer ring forms a conical surface.
  • contact surface for an elastomer ring forms a conical surface.
  • the contact surface is on an elastomer ring with a trapezoidal or rhombic profile
  • the blocking elements can be designed as blocking springs or blocking leaf springs or as rod elements which can yield resiliently in the axial and radial directions.
  • the rotational symmetry of the arrangement of the locking elements differs from the rotational symmetry of the engagement structure.
  • an embodiment is provided in which only one or 2 blocking elements are engaged, whereby the dead travel of the sliding ring
  • FIG. 1 shows a section through a conventional running gear seal as is known from the prior art.
  • FIG. 2 shows a possible embodiment of the present invention in a partial view, which already shows all relevant aspects.
  • FIG. 3 shows an engagement structure as can be used on a running gear seal according to the invention.
  • FIG. 4 shows six locking springs as can be used on a drive seal according to the invention.
  • Figures 5A through 5I are plan and side sectional views showing an exemplary latch and the use of the latch in a drive seal.
  • Figure 6 illustrates the engagement structure of Figure 3 with locking members of Figure 4 engaged therewith.
  • FIG. 7 shows a further embodiment of an engagement structure as can be used according to the invention on a running gear seal.
  • FIG. 8 illustrates twenty-four locking elements as may be employed on a carriage seal in accordance with the invention along with the engagement structure of FIG.
  • Figure 9 shows the engagement structure of Figure 7 with locking members of Figure 8 engaged therewith.
  • Figures 10 and 11 are sectional views, respectively, of embodiments of drive seals in an installed condition with locking members engaged with engagement structures, respectively.
  • Figure 12 shows an embodiment of a blocking element in a solid construction.
  • Figures 13 and 14 represent a sliding ring and a special embodiment of a locking element in a perspective partial view.
  • FIG. 1 shows a section through a conventional running gear seal 40 as is known from the prior art.
  • the associated housing and shaft or axle flanges are not shown.
  • the running gear seal 40 includes two sliding rings 44 which are shown here in the same way, but can also be designed differently.
  • Each of the sliding rings includes a sliding or running surface 46, the two running surfaces 46 of the sliding rings 44 touching.
  • an elastomer ring 24 is arranged on each of the slide rings 44, with which it rests sealingly on the slide ring 44 and on the other hand rests against a housing or housing, shaft or axle flange, not shown.
  • the seal only acts between the sliding surfaces 46 between the sliding rings 44, with the elastomer rings supporting the sliding rings in relation to their respective associated housings, shaft flanges or axle flanges and fixing them by frictional engagement.
  • a frictional connection between the elastomer rings 42 and the housing/the flanges and the slide rings 44 is greater than between the two sliding or running surfaces, no problems are to be expected.
  • the slip rings 44 are conventionally in contact only with each other and with the elastomeric rings to allow some radial, axial, and also minimal canting of the slip rings relative to an axle, shaft, or housing.
  • FIG. 1 not only serves to show the state of the art here, but also has the task of determining and showing the essential areas, which are referred to in more detail below.
  • the surface 52 corresponds to an inner surface of a slide ring.
  • the slide ring back 48 corresponds to a surface of the slide ring facing a flange or a housing, which surface can be flat or can represent part of a conical surface.
  • the surface 50 designates part of a lateral surface 50 of the slide ring 44 which is located outside of a contact surface 54 for an elastomeric ring 42 .
  • the corresponding surfaces can be or can be correspondingly modified for special applications.
  • FIG. 2 shows a possible embodiment of the present invention in a partial sectional view.
  • a sectional view of the slide ring 44 is shown at the top in FIG recognize.
  • the section is nearly tangent to and through the edge of the slip ring 44 with the plane of the section being parallel to an axial direction (a shaft being sealed by the drive seal).
  • the circumferential elastomer ring 42 can be seen on the left and right edge of the section.
  • the outer surface 50 of the sliding ring 44 is shown on the right-hand edge of the sealing ring.
  • a housing/a housing, axle or shaft flange 60 is shown in FIG. On which the slide ring 44 is directly or indirectly connected via the elastomer ring 42 .
  • the term flange 60 is used to refer to a housing/a housing, axle or shaft flange.
  • the flange 60 has a flange face 62 with a distance of
  • a pocket or a recess 33 for a blocking element 8 is let into the downward-pointing slide ring back 48 of the slide ring 44 .
  • the section runs through the recess 33 so that the rear wall of the recess can be seen.
  • a blocking element 10 is arranged in the recess 33 .
  • the blocking element 10 comprises a U-shaped bracket section which is open at the bottom and serves as a fastening section 8 .
  • Rod elements extend from the attachment section 8 and are designed here as leaf springs, with which the blocking element 10 engages in a corresponding engagement structure 6 on an opposite flange 60 .
  • the engagement structure 6 comprises indentations which are arranged in the flange 60 at equal angular intervals in the circumferential direction.
  • the indentations as well as the locking elements 10 are designed symmetrically.
  • the locking members 10 are each obliquely engaged with the engaging structures so that the left rod member of the locking member 10 prevents twisting to the left and the right rod member of the locking member 10 prevents twisting to the left. Due to the same angular distances of the depressions of the engagement structure 6, the slide ring 44 could be shifted so far to the right that the rod element now arranged on the right engages in the depression now arranged on the left. The bar element now shown on the left will then engage in a recess that is arranged on the left outside of the image detail. Engagement and mating are illustrated in more detail in Figures 5A-5I.
  • FIG. 3 shows a plan view of an annular section of a flange 60 or a slide ring 44. Only the flange face 62 or the slide ring back 48 is shown. The end face is provided with engagement structures 6 in the form of pockets or indentations extending into the plane of the figure.
  • the engagement structure 6 forms a total of twelve indentations, the engagement structure 6 having a rotational symmetry of 30°.
  • Other forms of depressions or elevations or projections are also conceivable as an engagement structure. It is also possible to use other rotational symmetries.
  • FIG. 4 shows a plan view of one possible embodiment of an annular section of a sliding ring 44 or flange 60 which fits the engagement structure 6 of FIG.
  • the slide ring back 48 / the flange face 62 is provided with six locking elements 10, each of which includes a fastening section 8 .
  • the blocking elements 10 are screwed to the slide ring back 48/the flange face 62 by means of two screws 25, with other types of fastening such as welding, adhesive, riveting or form-fitting connections also being possible.
  • the blocking elements 10 each comprise two bar elements which protrude upwards from the plane of the drawing and are designed so elastically that they can spring perpendicularly to the plane of the drawing.
  • the blocking elements 10 can be made of sheet metal, in which case the bar elements then serve as leaf springs which are biased obliquely upwards.
  • the rod elements run here essentially tangentially to the fastening section 8 of the locking elements 10.
  • FIG. 4 shows a dashed line which corresponds to the sectional line to which the sectional view of FIG. 5B corresponds.
  • FIG. 5A shows one of the six blocking elements 10 of FIG. 4 in a top view. Since the locking element 10 is shown alone, no heads of the screws 25 are shown in the fastening section 8, but only the holes 26 are present, through which these fastening elements can be inserted.
  • FIG. 5B shows a side view of the blocking element 10 in a position in which it is fastened to the slide ring back 48 of the slide ring 44 or the flange face 62 of the flange 60.
  • the heads of the screws 25 are also shown in the side view.
  • the section runs perpendicularly through FIG. 4, corresponding to the bar elements of the blocking element, as shown there by the dashed line.
  • the blocking element 10 comprises two rod elements or arms which protrude slightly obliquely upwards. Given the dimensions of the locking member 10, it is clear that the arms can be pushed down towards the slip ring back 48/flange face 62.
  • Figure 5C shows the view of Figure 5B in combination with a sectional view of an associated flange 60 or an associated slide ring 44.
  • the associated slide ring back 60/the associated flange face 48 is provided with the engagement structure 6, which in the sectional view as two rectangular cross-section depressions are executed.
  • the locking elements 10 are not yet engaged with the engagement structure 6 .
  • FIG. 5C shows a situation during the assembly of a sliding ring 44 in relation to a flange 60, both aligned with one another but still spaced apart from one another in the axial direction.
  • FIG. 5D the flange 60 and the slide ring 44 are brought together in the axial direction to such an extent that the rod elements of the blocking element 10 are in contact with the opposite end face which has the engagement structure 6 .
  • the rod elements of the locking element are elastically deformed in the axial direction and press against the back of the slide ring 62/the flange face 48. However, the rod elements of the locking element 10 are not yet in engagement with the engagement structure 6.
  • FIG. 5D shows that it is not necessary to align the sliding ring in the circumferential direction with respect to the flange for the assembly of the sliding ring. It is therefore not necessary to bring the locking elements 10 into engagement with the engagement structure 6 .
  • FIG. 5E the back of the slide ring 62/the flange face 48 has moved to the left in the circumferential direction, so that the right-hand bar element of the locking element 10 could lower into the right-hand recess of the engagement structure 6.
  • the left-hand bar element of the locking element 10 springs or snaps into the left-hand recess of the engagement structure 6 .
  • the right-hand bar element of the locking element 10 abuts against the right-hand flank of the right-hand depression of the engagement structure 6 and prevents further movement of the flange face 62/seal ring back 48 in the circumferential direction to the left.
  • the flange and the sliding ring are locked against further movement of the flange face 62/of the sliding ring back 48 in the circumferential direction to the left.
  • FIG. 5F shows a load case in the blocking direction of the right rod element of the blocking element 10, under the load.
  • the end of the right bar element is caught in the upper right corner of the right indentation and cannot slip out of this corner without deformation.
  • the load in the direction of the rod causes an increased contact pressure on the running surface of the associated slide ring, which improves the sealing effect.
  • FIG. 5G a load in the opposite direction, with a corresponding movement of the in the other direction being prevented here.
  • a slight circumferential deviation between the states of Figures 5E and 5F an unavoidable play which is essential for positive engagement of the locking elements 10 in the engagement structure.
  • the play in the circumferential direction is less than a movement that is possible through elastic deformation of the elastomer ring.
  • FIG. 5H shows an operating situation in which the drive seal is subjected to pressure in the axial direction, with both rod elements of the blocking element 10 being supported in the axial direction on the bottom of the depressions in the engagement structure 6 and thus counteracting further deformation of the elastomer ring.
  • FIG. 51 shows an operating situation in which the running gear seal is subjected to a pull in the axial direction.
  • the rod element of the locking element 10 remains in engagement with the recess and increases the pressure on the slide ring.
  • the rod elements contribute to maintaining the pressure between the sealing surfaces of the slip rings, even if a load situation occurs that would reduce the sealing surface pressure of the slip rings.
  • FIG. 6 shows a combination of the engagement structure 6 and the locking elements 10 in a plan view in the axial direction, with the sliding ring back 48/the flange face 62 of the component to which the locking elements 10 are attached being indicated only by a light dotted line.
  • the member with the engaging structure is the same as that shown in FIG.
  • the locking elements 10 correspond to those of FIG. 4.
  • One bar element of the locking elements 10 is assigned to a recess of the engagement structure and engages with it. Even if the arrangement of the locking elements only has a rotational symmetry of 60°, the flange and the slide ring can only move by less than 30° at most until all locking elements 10 engage in the engagement structure 6, since the engagement structure 6 already has rotational symmetry of 30°. Only 6 bar elements are available for each direction of rotation to block mutual rotation.
  • FIG. 7 largely corresponds to FIG. 3 and shows a further embodiment of an engagement structure such as can be used on a running gear seal according to the invention.
  • FIG. 73 shows a top view of an annular section of a flange 60 or a slide ring 44. Only the flange face 62 or the slide ring back 48 is shown, the other components of a slide ring or flange have been omitted for the sake of simplicity.
  • Figure 7 shows a flange face 62/slip ring back 48 of a flange 60 or slip ring 44 with a different engagement structure 6. The indentations of the engagement structure 6 are enlarged clockwise on the inside. This engagement structure 6 is compatible with the locking elements of FIG.
  • FIG. 8 shows a top view of one possible embodiment of an annular section of a sliding ring 44 or flange 60 which fits the engagement structure 6 of FIG.
  • the slide ring back 48 / the flange face 62 is provided with twenty-four locking elements 10, each comprising a fastening section 8.
  • the locking elements 10 are screwed to the slide ring back 48/the flange end face 62 by means of two screws 25.
  • other types of fastening such as welding, adhesive, riveting or form-fitting connections can also be used.
  • the blocking elements 10 each comprise a rod element which protrudes upwards from the plane of the drawing and is designed so elastically that it can spring perpendicularly to the plane of the drawing.
  • Twelve blocking elements 10 each form an outer ring, in which the rod elements of the blocking elements 10 extend clockwise from the plane of the image in the plan view of the end face 68/62. Twelve blocking elements 10 each form an inner ring, in which the rod elements of the blocking elements 10 extend counterclockwise from the plane of the image in the plan view of the end face 68/62.
  • the rings each form a kind of freewheel, with the two freewheels facing each other and always blocking each other, with a small amount of return movement or small play being possible.
  • Figure 9 shows a combination of the engagement structure 6 and the locking elements 10 of Figures 7 and 8 in a plan view in the axial direction, with the sliding ring back 48/the flange face 62 of the component to which the locking elements 10 are attached being indicated only by a light dotted line.
  • the component with the engaging structure is the same as shown in FIG.
  • the blocking elements 10 correspond to those of FIG. 8, the orientation of the outer and inner bar elements being reversed due to the opposite viewing direction, and the bar elements each extending obliquely into the plane of the image.
  • one rod element of two locking elements 10 is assigned to a depression in the engagement structure 6 and engages with it.
  • both the engagement structure 6 and the locking elements 10 have a rotational symmetry of 30°.
  • 12 rod elements are available for each direction of rotation to block mutual rotation, which is why this embodiment is secured against twisting at least twice as much as the embodiment in FIG.
  • Figures 10 and 11 each show sectional views of embodiments of drive seals in an installed condition, with latching elements engaged with engagement structures, respectively.
  • FIG. 10 shows the principle of the anti-twist devices from FIGS. 2 to 9 in a technical drawing, in which two locking elements 10 are used between a flange 60 and a slide ring 44 .
  • the flange 60 which has a through-opening, is arranged on the left-hand side in section.
  • Two blocking elements are attached to the through-opening on one end face of the flange 60 by means of rivets. Only one blocking element 10 can be seen through the section.
  • the blocking element comprises two bar elements.
  • the sliding ring 44 is elastically mounted in the flange via an elastomeric ring having a polygonal cross section, and can easily move in the axial direction and perpendicularly to the axial direction with deformation of the elastomeric ring. It is also possible to slightly tilt the slide ring relative to the flange.
  • the two rod elements of the locking element 10 are each engaged with depressions in the engagement structure 6 of the sliding ring 44.
  • the locking elements 10 which engage in the depressions in the engagement structure 6 mean that the sliding ring 44 can no longer be twisted relative to the flange 60. It can thus be ruled out that there can be considerable wear of the elastomer ring on the contact surfaces with the flange or the slide ring.
  • a leak in the contact surface between the elastomer ring and the flange 40 or the sliding ring 44 can also be avoided by reduced wear.
  • the inner surface 52 of the slide ring 44 is clearly visible.
  • the sliding surface 46 is arranged to run on a corresponding counterpart.
  • FIG. 11 shows an embodiment which largely corresponds to that of FIG. 10, a total of five locking elements 10 with a total of ten rod elements being used in FIG.
  • the locking element 10 arranged below lies exactly halfway on the sectional plane.
  • the embodiment of FIG. 11 has a torsional strength that is increased by a factor of 2.5 due to the blocking elements 10 .
  • FIG. 12 shows a further embodiment of a blocking element 10.
  • the blocking element 10 has a fastening section 8 which is provided with a thread with which the blocking element can be screwed into a corresponding threaded hole.
  • a rod element of the blocking element 10 is pivotably connected to the fastening section 8 via a ball joint and an elastomer jacket.
  • This version is only intended to be able to transmit large forces with a few blocking elements.
  • a massive, rigid, pivotably mounted rod element will not buckle even under high loads and thus reliable self-locking anti-rotation protection is possible with only two locking elements per direction of rotation.
  • Figure 13 shows a view of one edge of a sealing ring 44.
  • An outer lateral surface 50 of the sliding ring 44 faces the viewer.
  • the middle part of the outer lateral surface 50 of the sliding ring 44 is closer to the viewer than the two parts to the left and right of the middle which are towards curve backwards.
  • the slide ring back 48 of the slide ring 44 can be seen at the top and forms an edge with the lateral surface 50.
  • a depression or an incision is made in the lateral surface.
  • the projection of the circumferential direction is essentially horizontal to the viewer in the image plane and the projection of the axial direction is essentially perpendicular to the viewer in the plane of the drawing.
  • the image detail roughly corresponds to part of an edge of a pipe end.
  • the recess here does not represent an indentation of an engagement structure, but is only intended to enable the viewer to orientate himself in relation to FIG. 1, since this is essential for understanding FIG.
  • FIG. 14 shows the same section of the edge of the slide ring 44 of FIG. 13, with a locking element being inserted into the depression.
  • the locking element 10 comprises a fastening section 8, a part of the fastening section 8 resting on the bottom of the indentation/incision.
  • a tab extends downwards from this part in the direction of the viewer and rests on the lateral surface 50 .
  • Another tab which cannot be seen, runs to the rear, away from the viewer and rests on the lateral surface 50 on the inner surface of the slide ring 44 .
  • the locking element 10 is clamped onto the edge of the slide ring by the two tabs and fixed in the radial direction. Two projections of the blocking element 10 run from the fastening section 8 in the axial direction to the back of the sliding ring 48 of the sliding ring 44.
  • the projections of the blocking element 10 run obliquely above the sliding ring back 48 and almost tangentially to the lateral surface 50 of the sliding ring and form elastically resilient rod elements which can be brought into engagement with corresponding recesses or projections of an engagement structure of an opposite flange.

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

Abstract

L'invention concerne une bague de glissement (44) pour un joint d'étanchéité de train de roulement (40), comprenant une surface de glissement (46) et au moins une surface de contact (54) pour une bague à base d'élastomère (42). L'invention est caractérisée par au moins deux éléments de verrouillage (10) qui sont agencés dans le sens circonférentiel et qui ont d'excellentes propriétés élastiques, en particulier au moins deux éléments de verrouillage (10) comportant des cliquets ou des ressorts de verrouillage, qui sont conçus pour venir en prise dans au moins une structure de mise en prise correspondante (6) qui s'étend dans le sens circonférentiel sur la bague de glissement (44) ou sur un boîtier (60).
PCT/EP2022/087956 2022-02-03 2022-12-28 Joint d'étanchéité de train de roulement à dispositif anti-rotation et ses composants WO2023147938A1 (fr)

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DE102022102571.3 2022-02-03
DE102022102571.3A DE102022102571A1 (de) 2022-02-03 2022-02-03 Laufwerkdichtung mit Verdrehsicherung und Komponenten davon

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EP4311958A1 (fr) * 2022-07-27 2024-01-31 Fluiten Italia S.p.A. Joint mécanique

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US3452994A (en) * 1966-08-01 1969-07-01 Borg Warner Mechanical face seal
US20060022413A1 (en) * 2004-07-30 2006-02-02 Federal Mogul Friedberg Gmbh Slide ring packing
US20070267819A1 (en) * 2006-05-17 2007-11-22 A.W. Chesterton Company Mechanical seal assembly
US10352457B2 (en) * 2012-12-07 2019-07-16 A.W. Chesterton Company Self aligning split mechanical seal employing a rotary seal ring having non-flat end faces
US11052509B2 (en) * 2016-04-29 2021-07-06 Cnh Industrial America Llc System and method for manufacturing a face seal with controlled load tolerance
US20210381603A1 (en) * 2020-06-05 2021-12-09 A.W. Chesterton Company Externally energized secondary seals in split mechanical seals

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DE1750565U (de) 1956-06-30 1957-08-14 Andre Ayat Kuechenherd.
DE29521734U1 (de) 1995-01-27 1998-06-10 AE Goetze GmbH, 51399 Burscheid Gleitringdichtung
US6398223B1 (en) 2000-08-21 2002-06-04 John Crane Inc. Mechanical face seal
DE10104788C2 (de) 2001-02-02 2003-06-26 Federal Mogul Friedberg Gmbh Gleitringdichtung mit radialer Verdrehsicherung
DE10148929C2 (de) 2001-10-04 2003-11-27 Federal Mogul Friedberg Gmbh Gleitringdichtung mit axialem Spielausgleich
DE102006011620B3 (de) 2006-03-14 2007-09-06 Federal-Mogul Burscheid Gmbh Gleitringdichtung

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US3452994A (en) * 1966-08-01 1969-07-01 Borg Warner Mechanical face seal
US20060022413A1 (en) * 2004-07-30 2006-02-02 Federal Mogul Friedberg Gmbh Slide ring packing
US20070267819A1 (en) * 2006-05-17 2007-11-22 A.W. Chesterton Company Mechanical seal assembly
US10352457B2 (en) * 2012-12-07 2019-07-16 A.W. Chesterton Company Self aligning split mechanical seal employing a rotary seal ring having non-flat end faces
US11052509B2 (en) * 2016-04-29 2021-07-06 Cnh Industrial America Llc System and method for manufacturing a face seal with controlled load tolerance
US20210381603A1 (en) * 2020-06-05 2021-12-09 A.W. Chesterton Company Externally energized secondary seals in split mechanical seals

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4311958A1 (fr) * 2022-07-27 2024-01-31 Fluiten Italia S.p.A. Joint mécanique

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