• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a gliding board binding (10) for holding a shoe on a gliding board (14), comprising a base (12) adapted for mounting on the gliding board (14), a binding body (16) which is adjustable between an engaged position for holding the shoe and a release position for releasing the shoe, and a pivot bearing assembly (46, 48, 50, 52) rotatably to the binding body (16) for adjustment between engagement position and release position about a vertical axis of rotation (V) extending vertically to a sliding board plane the base (12), the pivot bearing assembly (46, 48, 50, 52) having a hub (46) provided on a first one of the base (12) and binding body (16) and a receptacle (46). 48) which is provided on the other of the two elements of base (12) and binding body (16), wherein the hub (46) is rotatably inserted into the receptacle, wherein the pivot bearing arrangement (46 , 48, 50, 52) further comprises a thrust bearing (50, 52) with a first (50) and a second thrust bearing element (52) which are mutually rotatably mounted to each other about the vertical axis of rotation (V), wherein the first thrust bearing element (50) is arranged on the first element (12) and wherein the second thrust bearing element (52) is arranged on the second element (16).
    公开号:AT515186A2
    申请号:T871/2014
    申请日:2014-12-01
    公开日:2015-06-15
    发明作者:Edwin Lehner
    申请人:Salewa Sport Ag；
    IPC主号:
    专利说明:

    The present invention relates to a gliding board binding for holding a shoe to a gliding board, comprising a base adapted for mounting on the gliding board, a binding body which is adjustable between an engaged position for holding the shoe and a release position for releasing the shoe, and a rotary bearing assembly interposing the binding body for the adjustment Engagement position and release position rotatably supported on the base about a vertical axis of rotation perpendicular to a sliding board plane, the pivot bearing arrangement having a hub provided on a first one of the base and binding bodies and having a receptacle provided on the second of the two base and binding body elements; wherein the hub is rotatably inserted in the receptacle, wherein the pivot bearing assembly further comprises a thrust bearing with a first and a second thrust bearing member which are mutually about the vertical axis of rotation dr are mutually supported, wherein the first axial bearing element is arranged on the first element and wherein the second axial bearing element is arranged on the second element.
    Such a gliding board binding is known as a heel unit for touring ski binding of EP 2 545 966 A2. The conventional binding comprises a binding body having two coupling pins which are adapted to engage a heel portion of a shoe to hold the shoe firmly in a downhill position on the ski. The binding body is rotatably mounted about a vertical axis of rotation on a ski-solid base, so that the heel unit is rotatable from the said down position to a touring position in which the coupling pins are laterally oriented and instead a climbing aid attached to the binding body is oriented forwardly to move the shoe as it moves to support predetermined height above the ski. The rotation of the binding body about the vertical axis of rotation is further exploited for an Mz triggering mechanism by biasing the pivot bearing into the down position by a spring arrangement so that upon application of a force exceeding a predetermined release force from the shoe to the coupling pins of the binding body laterally (in the event of the shoe falling and twisting) vertical axis) the coupling pins against the force of the spring assembly can escape laterally to release the shoe in the heel section.
    The binding body pivot is subjected to heavy loads during use of the binding, which may be due to frequent adjustment of the binding between downhill and toe-up, and also to impact or pressure loads during walking or downhill. However, regardless of the actual use of the guideboard binding as a touring binding, guideboard bindings are subject to the conflicting demands for increased long-term stability on the one hand and low construction weight on the other.
    In particular, the pivot bearing arrangement of the heel unit known from EP2 545 966 A2 is realized by a Naber, which at its free end a
    An annular projection which engages a corresponding bearing ring on the binding body, to provide an axial fixation between hub and receptacle and to prevent a separation between the base and the binding body. Impact or compression forces introduced in the binding body in the in-axial direction or in the direction transverse to the axis of the hub are thus always introduced directly into the hub and could lead to damage or even breakage of the hub, especially during prolonged use.
    Against this background, it is an object of the present invention to provide a sliding board binding with a binding body rotatable about a vertical axis of rotation, which is characterized by increased stability, by reduced wear and by low weight.
    According to the invention, this object is achieved by a sliding board binding for holding a shoe on a sliding board, comprising a base adapted for mounting on the sliding board, a binding body which is adjustable between an engagement position for holding the shoe and a release position for releasing the shoe, and a pivot bearing arrangement, which is the binding body for adjusting between the engagement position and the release position, rotatably supported around a vertical pivot axis extending vertically to a slide board plane, the pivot bearing assembly having a hub provided on a first one of the base and the binding body and having a receptacle attached to the second one of the base and binding body wherein the hub is rotatably inserted into the receptacle, wherein the pivot bearing assembly further comprises a thrust bearing with a first and a second thrust bearing member which are mutually about the Ver wherein the first axial bearing member is disposed on the first member, and wherein the second axial bearing member is disposed on the second member, and wherein the first axial bearing member is disposed at a distance from the hub radially outside the hub on the first member.
    According to an important feature of the present invention, the sliding board binding comprises a thrust bearing, wherein a first thrust bearing member of the thrust bearing is disposed radially outside the hub on the first member. Thus, one idea of the present invention is to statically and spatially separate the axial bearing from the hub by connecting the first thrust bearing member and the hub to different portions of the first member, each independently connected to the first member. As a result, relief of the hub can be achieved because axial forces encountered during use, and in particular impact or compressive loads during a downhill run or during a hike in the event of a touring binding, are introduced directly into the first element from the thrust bearing. In this way, the long term strength of the gliding board binding is improved, wear can be reduced and, in particular, it can also be thought of using lighter materials for the binding body, the base and the bearing assembly, respectively.
    Preferably, at least one of the two axial bearing elements has an annular or partially annular shape
    Bearing surface with axial normal vector on, so that each other of the two thrust bearing elements on the annular or part-annular bearing surface is rotatable about the vertical axis of rotation but in the axial direction in at least one direction immovable. Such axial normal vector bearing surface allows uniform pivotal mounting over a predetermined angular range as well as stable axial support.
    One of the two axial bearing elements may have a projection which projects in the radial direction and engages behind a radial projection of the other of the two axial bearing elements. In this way, the axial support between binding body and base can be achieved with simple technical means and at the same time mechanically very stable by a positive engagement.
    In another preferred embodiment of the invention, the axial position of the first axial bearing member is closer to a root portion of the hub than to a head portion of the hub or the axial position of the first thrust bearing member is substantially equal to the axial position of the root portion of the hub. In such a variant, when the first thrust bearing member is approximately at the level of the root portion of the hub or in the vicinity of the root portion of the hub, the forces received by the thrust bearing can be reliably absorbed by a relatively substantial portion of the first member in a position relatively far away is from the protruding free end of the hub.
    The thrust bearing may have at least one interruption in the circumferential direction, at which the axial abutment of the two thrust bearing elements is canceled. Such an interruption of the bearing surface in the circumferential direction can be utilized for mounting or dismounting the thrust bearing. For this purpose, the two axial bearing elements can be adjusted relative to each other into a mounting rotational position, in which the bearing surface of one of the thrust bearing elements aligned with the interruption of the other thrust bearing element, so that the bearing surface can pass the interruption in the axial direction and the two thrust bearing elements can be separated from each other or attached to each other. In particular, the two axial bearing elements may be configured as a bayonet coupling such that they can be coaxially aligned with one another for assembly and disassembly and aligned with at least one predetermined mounting rotational position relative to each other, being rotatable and angularly non-rotatable in angular ranges other than the mounting rotational position are held.
    In a particularly preferred variant of the invention, it is provided that the first and the second axial bearing element each have a bearing surface which has a circumferential interruption, such that the thrust bearing elements can be brought into a mounting rotational position relative to each other, in which the bearing surface of the one axial bearing element in axial direction can occur due to an interruption of the other axial bearing element, if the two
    Axiallagerelemente be moved for assembly or disassembly in the axial direction relative to each other. It can be provided that over a full revolution of the two thrust bearing elements to each other (over 360 Gradhinweg) is exactly one mounting rotational position. In this way, the angular range effectively usable for the operation of the gliding board binding, in which a reliable axial coupling is made, is maximized. Further, preferably, when the axial bearing elements are set to the assembly rotational position, the binding body is adjusted to a position rotated about 180 degrees from the engaged position, such that the mounting rotational position is at a maximum distance from the engagement position and a function of the gliding board binding is not impaired by the presence of the interruption for the mounting rotational position, in particular in the shutdown position of the binding. The 180 degree twisted position of the binding body may also be a minimum required rotational position of the binding body for normal operation of the gliding board binding and the desired operational adjustment of the gliding board binding (for example, between touring and downhill positions).
    In the above embodiments, for the possibility of advantageous assembly or disassembly, the existence of at least one interruption of the bearing surface is accepted. Thus, it could be thought to minimize the number of interruptions or the length of the circumferential breaks. However, since the number and length of the
    Interruptions should correspond with a corresponding number and length of bearing surfaces of the other thrust bearing element, respectively, because these bearing surfaces must pass the corresponding interruptions for assembly / disassembly, the optimization of the number and length of interrupts or bearing surfaces is not a trivial task. The inventors have found that for the best possible distribution of axial forces that can act at various points in the circumferential direction of the thrust bearing, it is particularly advantageous if the bearing surface of the first and / or second thrust bearing elements has n interruptions, where n > 2. This means that the bearing surface is also divided into at least two partial bearing surfaces. In particular, the number of interruptions may be greater than the number of mounting rotational positions. Tilting moments can then be well initiated in binding bodies or bases. Particularly preferred is a value of n > 3 (in particular n = 3), which combines a good dissipation of tilting moments with an optimization of the length of the bearing surfaces.
    In addition, the centers of adjacent breaks (that is, the center of the breaks in the circumferential direction) should include an angle of α = 360 / n, that is, the centers should be evenly distributed in the circumferential direction. It is then ensured uniform stability of the Gleitbrettbindung regardless of the angle of rotation between the binding body and the base.
    Irrespective of the uniform distribution of the centers of the interruptions, it is preferred that at least two
    Interruptions have different lengths in the circumferential direction. These differences in length of the interruptions can be used in a structurally simple way to define at least one mounting rotational position in which the binding body and the base are to be aligned relative to one another in order to assemble or disassemble the axial bearing.
    In the manner described above, the present invention achieves stabilization or disassembly of the hub of the pivot bearing assembly. This may be exploited to use less resilient but lighter or / and less expensive materials for hub and / or receptacle manufacture. In particular, such components of the bearing assembly may be formed of a plastics material such that the weight of the board can be reduced.
    The invention will be explained in more detail below by means of a preferred embodiment with reference to the attached drawings. Show it:
    FIG. 1 is a perspective view of a heel unit according to the embodiment of the invention;
    Figure 2 is a plan view of the heel unit of the embodiment,
    FIG. 3 is a perspective view, partly in section, of the heel unit of the embodiment, including an enlarged detail in FIG
    Area of thrust bearing,
    FIG. 4 is a perspective view of a base of the heel unit of the embodiment;
    FIG. 5: a top view of the base shown in FIG. 4,
    Figure 6 is a perspective bottom view of a binding body of the heel unit of the embodiment, and
    Figure 7: a bottom view of the binding body shown in Figure 6.
    In the illustrated embodiment, a board binding of the present invention is a heel unit 10 of touring binding and includes a base 12 for attachment to a gliding board 14 and a binding body 16 held on the base 12 for supporting a shoe (not shown). For attachment to the gliding board 14, the base 12 has a mounting arrangement here formed by a plurality of mounting holes 18 through which screws 20 to be screwed into the gliding board 14 are passed.
    The mounting arrangement defines a sliding board plane E as the surface of the sliding board 14 to which the base 12 is to be attached, a sliding board longitudinal axis Lin traveling direction of the sliding board 14, and thus also a coordinate system of the heel unit 10 having an X-axis along the sliding board longitudinal axis L, a Z-axis orthogonal to the sliding board plane E and a Y-axis (laterally with respect to the sliding board) orthogonal to the X-axis and the Z-axis. As used herein, terms such as "forward," "backward," "top," "bottom," "side," "horizontal," "vertical," or similar, are understood to refer to that coordinate system 10 carrying gliding board 14 is located on a horizontal surface and the viewer looks in the direction of travel or along the longitudinal axis L of the carriage.
    By a rotary bearing arrangement to be described later, the binding body 16 is rotatably supported on the base 12 about a vertical rotation axis V extending in the Z direction. The binding body 16 may also be slidable with respect to the gliding board 14 along the longitudinal axis L of the girder, such as by the base 12 comprising a fastener 22 to be fixed to the gliding board 14 and having the attachment assembly 18 thereto, and further comprising a carriage 24 attached to the attachment member 22 in FIG X-direction is slidably guided and which has theDiehlageranordnung. Thus, in this embodiment, the binding body 16 is rotatably supported on the slidable slide 24 of the base 12 about the vertical axis of rotation V. The displaceability of the binding body 16 in the X-direction can be used to adjust the heel unit to fit a shoe size, and can also dynamically compensate for the distance between the heel unit 10 and a front unit during a downhill ride to provide the heel unit 10 also
    Always keep ski deflections in close contact with the shoe. To this end, the movement of the carriage 24 may be biased forwardly by a spring 26 (Figure 3), as is known in detail from EP 2 545 966 A2, the disclosure of which is herein incorporated by reference.
    By rotating the binding body 16 about the vertical axis of rotation V, the heel unit 10 is adjustable between a deployed position shown in Figs. 1 and 2 for holding a heel portion of a shoe and a touring position in which the heel portion of the shoe is released and can lift up. To hold the shoe in the deployed position, the heel unit 10 on the binding body 16 may comprise coupling means 28, in particular two parallel forwardly projecting coupling pins 281, 28r. In the touring position, in which the coupling means 28 are disengaged from the shoe so that the heel portion of the shoe can lift upwardly, the shoe is generally pivotally mounted to an unillustrated toe unit of the touring binding about a pivot axis in the Y direction. At each step the heel portion then slides away from the skid board 14 and then descends downwardly in the direction of the glide board 14. The height to which the shoe may descend in the touring position depends on the construction or adjustment of the heel unit 10, and may be dictated by the climbing aid 30 which supports the shoe at steeper terrain above the slide board plane E for steeper terrain can.
    In the illustrated embodiment, a toggle position is adjustable in which the binding body 16 is rotated about the vertical axis of rotation V so that the coupling means 28 faces sideways, that is, a rotational angle about the vertical axis of rotation V between exit position and tour position is between about 10 degrees and about 170 degrees, preferably between about 45 degrees and about 135 degrees (in the illustrated embodiment approximately at 90 degrees). In the tour position, a recess 32 may be provided on the tie body 16 in the forward direction, providing sufficient clearance for the shoe so that the shoe will pass the recess 32 to a relatively low height above the gliding board 14 can lower (walking in flat terrain). Further, in the touring position, the climbing aid 30 may be displaced from a passive position shown in Figs. 1 and 2 to an active position in which it projects beyond the recess 32 and projects into the pivoting area of the shoe. For example, the climbing aid 30 may be pivotally mounted on the binding body 16 about a pivot axis S. so that when the binding body 16 is turned to the towing position, it can be folded forward from the passive position to the active position.
    It is further shown in Figures 1 and 2 that the heel unit 10 may comprise a brake assembly which is adjustable between a braking position (Figures 1 and 2) in which a braking member 36 is lowered below the gliding board 14 for braking engagement with the ground. and a driving position in which the brake member 36 is raised up to the height of the slide board 14. By engaging a first
    Control portion 38 of the binding body 16 with a second control portion 40 of the brake assembly 34, the brake assembly 34 can be locked in the driving position when the binding body 16 is rotated in the tour position. In the downhill position, the first control section 38 is moved away from contact with the second control section 40, so that the brake assembly 34 automatically moves to the braking position by the force of a spring 42 when the shoe is released from the heel unit 10 in the event of a fall, and in a manner known per se Tread plate 44 relieved, which holds the brake assembly 34 in the down position normally against the force of the spring 42 in the driving position.
    Hereinafter, with reference also to FIGS. 3 to 6, the rotary bearing arrangement will be described, by which the binding body 16 is rotatably supported about the vertical axis of rotation V on the base 12.
    The pivot bearing assembly includes a hub 46 which is fixed to the base 12 (optionally on the slide 24) and projects coaxially with the vertical axis of rotation V from the base 12 upwardly. The hub is fitted into a receptacle 48 of the binding body 16 so that it can rotate in the receptacle 48. The receptacle 48 may be defined by a cylindrical opening in a housing of the binding body 16, so that it encloses the hub and leads tipping over a certain axial length. The hub 46 and optionally other parts of the base 12 and the carriage 24 may be made of a material of low weight, in particular a plastic material or
    Be made of aluminum. Also, the receptacle 48 of the binding body and optionally other parts of the binding body 16 may be made of a material of low weight, in particular of plastic material or of aluminum.
    The rotary bearing arrangement further comprises a thrust bearing which is constructed from a first axial bearing element 50 provided on the base 12 (optionally on the carriage 24) and a second axial bearing element 52 provided on the binding body 16. As can be seen in particular in FIGS. 4 and 5, the first axial bearing element 50 has an annular or partial annular shape and rotates the hub 46 radially outwardly at a distance d. In other words, the first thrust bearing member 50 is provided separately from the hub 46, or spaced from the hub 46.
    The first axial bearing element 50 may have an annular or annular first bearing surface 54, on which a second bearing surface 56 of the second axial bearing element 52 is mounted. The bearing surfaces 54, 56 may be directly displaceable contact or be supported by means of a rolling element to each other, for example in the form of a ball bearing.
    Since the thrust bearing members 50, 52 form a thrust bearing to prevent relative movement between the hub 46 and receptacle 48 in the axial direction, the bearing surfaces 54, 56 of the thrust bearing members 50, 52 have normal vectors oriented in the axial direction of the vertical axis of rotation V or obliquely therefrom. In the illustrated embodiment, the first bearing surface 54 faces downwardly or away from the bonding body (the normal vector of the first bearing surface 54 slopes down to the vertical axis of rotation V) and the second bearing surface 56 faces upward (the normal vector of the second bearing surface 56 slopes upward relative to the vertical axis of rotation V).
    The first bearing surface 54 of the base 12 and of the slide 24 is formed as a projection 58 projecting in a direction parallel to the slide board plane E, for example protruding radially inward. The second bearing surface 56 of the binding body 16 may also be provided on a projection 60 which extends in a direction parallel to the sliding board plane E, here radially outwardly. The axial fixation between base 12 and binding body 16 is then accomplished by mutual engagement of the two projections.
    As can be seen in particular in FIGS. 3 and 4, the first thrust bearing element 50 is at least at the level of a foot section 57 of the hub 46 with respect to the vertical axis of rotation V at which the hub 46 is connected to the base 12 or the carriage 24, but in any case closer the foot portion 57 as an upper head portion 59 of the hub. In the illustrated embodiment, the bearing surfaces 54, 56 are each not formed as solid rings but as a partial ring, in particular formed on part-annular projections 58, 60. Thus, the first thrust bearing element 50 has a plurality of protrusions 58 distributed in the circumferential direction, here a first protrusion 58-1, a second protrusion 58-2 and a third protrusion 58-3, each through interruptions 62, accordingly a first interrupt 62-1, a second Break 62-2 and a third break 62-3 are separated. Likewise, the second thrust bearing member 52 has a mating plurality of protrusions 60, here three protrusions 60-1, 60-2, and 60-3, which extend through intersections, three intersections 64-1, 64-2, and 64-3, in the circumferential direction are separated. Centers ZI, Z2, Z3 of the intersections 62-1, 62-2 and 62-3, respectively, measured in the circumferential direction preferably each enclose an angle of 120 degrees with each other.
    The lengths of the projections 58, 60 and the circumferences 62, 64 in the circumferential direction are coordinated so that in at least one mounting rotational position between the base 12 and the binding body 16, the projections and interruptions can pass each other in the axial direction, and thus the binding body 16 and base 12 in axial direction can be separated or attached to each other. In this way, the axial bearing elements 50, 52 form a bayonet coupling.
    Further, in the illustrated embodiment, the break 62-1 is longer than the other breaks 62-2 and 62-3, respectively, and the boss 60-1 is longer than each of the breaks 62-2 and 62-3, but shorter than the first break 62-1. The projection 60-1 may thus pass only through the first interrupt 62-1 but not through the other two intersections 62-2 and 62-6. In this way, the first protrusion 60-1 and the first interrupt 62-1 define a predetermined mounting rotational position in which the fastener body 16 is to be oriented relative to the base 12 to mount or disassemble the two thrust bearing members 50, 52, respectively. In the embodiment, only a single such mounting rotational position is defined along the full revolution of the binding body 16. It will be apparent to those skilled in the art that by appropriate arrangement and sizing of projections and discontinuities, if desired, a plurality of predetermined mounting rotational positions may be realized.
    At angular ranges other than the mounting rotational position, there is always at least a partial overlap in the circumferential direction between the protrusions 58, 60 of the first and second thrust bearing elements 50, 52, so that in these angular ranges the binding body 16 is rotatably but immovably axially fixed to the base 12. When the binding body 16 is subjected to impact or compression forces during use which stress the binding body 16 on a tilt or axial pull away from the base 12, such forces will be transmitted through the second thrust bearing member of the binding body 16 and the first thrust bearing member of the base 12 over a relatively large one (Because radially outboard of hub 46 lying) circumferential portion directly into the base 12 and the carriage 24 introduced without these forces lead to an excessive stress on the hub 46. The hub 46 is thus relieved. The greater the distance d between an outer circumference of the hub 46 and the first bearing surface 54 (or the projection 58) of the first, the greater the relief
    Axiallagerelements 50 is selected.
    In the illustrated embodiment, the arrangement of the projections 58, 60 and the breaks 62, 64, respectively, of the thrust bearing members 50, 52 is chosen such that a single mounting rotational position is such a position that the binding body 16 is about 180 degrees from the standoff position
    Vertical axis of rotation V is rotated, that is, a position in which the coupling means 28 have in the reverse direction. Since in this variant of binding a towing position is a rotational position of the binding body 16 in which the coupling means 28 are sideways or obliquely to the side, the mounting rotational position does not correspond to a position in an angular range suitable for the intended use of the heel unit 10 and in particular the adjustment between downhill and toe-up is needed. In other words, with respect to a full revolution of the binding body 16 around the vertical axis of rotation V at different angular ranges and angular intervals separated from each other at a safe distance, a downhill position, a tour position and a mounting rotational position are provided. The adjustment of the mounting rotational position may be protected by a locking arrangement (not shown) which prevents accidental disassembly of the binding body 16 during normal use of the heel unit 10.
    权利要求:
    Claims (13)
    [1]
    Claims 1. A gliding board binding (10) for holding a shoe on a gliding board (14), comprising a base (12) adapted for mounting on the gliding board (14), a binding body (16) which is adjustable between an engaged position for holding the shoe and a pivotal bearing assembly (46, 48, 50, 52) for rotatably holding the binding body (16) to the base (12) between an engaged position and an unlocked position about a vertical pivot axis (V) vertical to a sliding board plane, the pivot bearing assembly a hub (46) provided on a first one of the base (12) and binding body (16) and having a receptacle (48) provided on the other of the base (12) and binding body (16) with the hub (46) rotatably inserted into the receptacle (48), the pivot bearing assembly further comprising an axial bearing (50, 52) having a first A xiallagerelement (50) and a second thrust bearing member (52) which are mutually rotatable about the vertical axis of rotation (V) mounted together, wherein the first axial bearing element (50) on the first element (12) is arranged and wherein the second thrust bearing element (52) on the second member (16), characterized in that the first thrust bearing member (50) is spaced apart from the hub (46) radially outside the hub (46) on the first member (12).
    [2]
    A gliding board binding (10) according to claim 1, characterized in that at least one of the two axial bearing elements comprises an annular or partially annular bearing surface (54, 56) with an axial normal vector.
    [3]
    A gliding board binding (10) according to claim 1 or claim 2, characterized in that one of the two axial bearing elements has a projection (58) which projects in the radial direction and engages behind a projection (60) of the other of the two axial bearing elements.
    [4]
    A gliding board binding (10) according to any one of the preceding claims, characterized in that the axial position of the first thrust bearing member (50) is closer to, or substantially equal to, a root portion (57) of the hub (46) than at a head portion (59) of the hub (46) axial position of the foot portion of the hub.
    [5]
    A gliding board binding (10) according to any one of the preceding claims, characterized in that the thrust bearing in the circumferential direction has at least one interruption (62, 64) at which the axial abutment of the two abutment elements is canceled.
    [6]
    A gliding board binding (10) according to any one of the preceding claims, characterized in that the first axial bearing element (50) and the second axial bearing element (52) form a bayonet coupling with each other.
    [7]
    A gliding board binding (10) according to any one of the preceding claims, characterized in that the first and second thrust bearing elements each comprise a bearing surface (54, 56) which has a break (62, 64) in the circumferential direction, such that the axial bearing elements are placed in an assembly Rotary position can be brought relative to each other, in which the bearing surface of the one Axiallagerelements can pass in the axial direction by an interruption of the other thrust bearing element when the two thrust bearing elements for assembly or disassembly are moved in the axial direction relative to each other.
    [8]
    8. board binding (10) according to claim 7, characterized in that there is a complete rotation of the Axiallagerelemente each other exactly one mounting rotational position.
    [9]
    A gliding board binding (10) according to claim 7 or claim 8, characterized in that, when the axial bearing members are set in the assembly rotational position, the binding body (16) is set in a position rotated about 180 degrees from the engaged position.
    [10]
    A gliding board binding (10) according to any one of claims 7 to 9, characterized in that the bearing surface of the first or / and the second thrust bearing element has nintervals, where n> = 2, preferably n> = 3.
    [11]
    A gliding board binding (10) according to claim 10, characterized in that the centers (ZI, Z2, Z3) of adjacent breaks form an angle alpha = 360 / n.
    [12]
    A gliding board binding (10) according to claim 10 or claim 11, characterized in that at least two interruptions have different lengths in the circumferential direction.
    [13]
    A gliding board binding (10) according to any one of the preceding claims, characterized in that the hub and / or the receptacle are made of plastic material.
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    同族专利:
    公开号 | 公开日
    AT515186A3|2020-01-15|
    DE102013224576A1|2015-06-03|
    AT515186B1|2020-04-15|
    DE102013224576B4|2019-03-28|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1172172B|1959-04-07|1964-06-11|Jean Joseph Alfred Beyl|Safety bindings|
    DE1578957C3|1965-03-17|1980-09-18|Paul 8501 Oberasbach Unger|Ski binding|
    AT381458B|1985-03-25|1986-10-27|Barthel Fritz|TOURING SKI BINDING|
    DE202009019109U1|2008-02-29|2016-09-05|G3 Genuine Guide Gear Inc.|Heel unit for touring ski binding|
    DE102010028764A1|2010-05-07|2011-11-10|Salewa Sport Ag|Heel unit for a binding, in particular touring ski binding|
    DE102011079210A1|2011-07-14|2013-01-17|Salewa Sport Ag|Heel unit for a touring ski binding|
    DE202012002705U1|2012-03-14|2013-06-17|Salewa Sport Ag|Heel unit for a touring binding|US10315099B2|2017-10-31|2019-06-11|G3 Genuine Guide Gear Inc.|Lightweight touring binding heel unit|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102013224576.9A|DE102013224576B4|2013-11-29|2013-11-29|Slide board binding with pivot bearing|
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