Toe piece of a gliding board binding

Description

TECHNICAL FIELD

[0001] The present invention relates to the field of shoe bindings on a sliding board. It relates more particularly to a binding stop, as well as a binding or a sliding board equipped with such a stop. It finds a particularly advantageous application in the field of skiing. STATE OF THE ART

[0002] A binding for a boot on a sliding board, such as a ski or a snowboard, generally comprises a front retaining device, called a toe piece, and a rear retaining device, called a rear toe piece or "heel piece". The boot is inserted between the toe piece and the heel piece, these elements being fixed to the sliding board. The toe piece and the heel piece are each equipped with stopping means acting on the boot so as to block the movement of the boot relative to the sliding board in the three longitudinal, vertical and transverse directions. Thus, the joint action of these two retaining devices makes it possible to secure the boot to the sliding board, when the boot is engaged with the binding.

[0003] There are various solutions for producing a front toe piece or a heel piece. For example, documents EP-A-0 241 360, EP-A-1 151 765, US4298213 A and EP-A-2 174 695 describe various embodiments of toes. In these illustrations, the front toe piece incorporates a sole clamp comprising two wings forming a "V" whose branches partially cover a front extension of the shoe, in a vertical direction. Furthermore, the sole of the shoe, i.e. the lower face of the shoe, presses on a support plate fixed to the sliding board. Consequently, the vertical immobilization of the shoe at the toe piece is achieved by a double contact between, on the one hand, the upper face of the front extension of the shoe and the wings of the toe piece and, on the other hand, the sole of the shoe and the support plate.

[0004] For safety reasons, the toe piece and the heel piece often incorporate a safety mechanism to release the binding if necessary. This mechanism allows the release of the user's foot to avoid injury during an accidental transverse and / or vertical movement of the foot. This may be during a fall or generally, to prevent the user from injuring themselves when the forces exerted on the shoe exceed previously determined values. Safety mechanisms for the toe piece are also described in the documents cited above.

[0005] There are several types of ski boots, including alpine ski boots and ski touring boots. These two categories of boots are characterized by the NF ISO 5355 and NF ISO 9523 standards, respectively. These categories are distinguished in particular by the dimensions of the parts that interface with the binding elements. The dimensions of the interface parts vary from one category to another, and as a result, bindings are generally designed or configurable to accommodate a single category of boot.

[0006] Some toe stops include a mechanism allowing elastic adjustment of the height, or vertical positioning, of their wings. This elastic means is used to compensate for small dimensional variations related to the tolerances of the production of a boot of the same category. However, these toe stops do not allow sufficient height adjustment to make the binding automatically compatible (without user adjustment) with alpine ski boots and with ski touring boots.

[0007] Similarly, there are bindings whose support plate serving as an interface with the sole of the boot is mounted on an elastic means in order to compensate for the dimensional variations intrinsic to a particular category of boot. These stops also do not make the binding automatically compatible (without user adjustment) with alpine ski boots and with ski touring boots.

[0008] Other stops are divided into two parts, the part integrating the wings being adjustable in height, via an adjustment screw, relative to the other part fixed to the ski. This type of stop allows the binding to be configured alternately for alpine ski boots and for ski touring boots. However, this type of stop is complex, expensive and is difficult to compatible with a mechanism to compensate for the dimensional variations intrinsic to a category. This design does not allow to cover large dimensional variations. Furthermore, adjusting the height of the wings to be compatible with a category of boot is not easy because the adjustment is done continuously and without reference, via the screwing of the screw. It is therefore not easy to correctly adjust the height of the wings for a particular category of boot.Furthermore, this type of adjustment to adapt to a shoe category is not convenient for the user because it is necessary to move the part integrating the wings over a large stroke, which involves several turns of the screwdriver.

[0009] Alternatively, other stops, also in two parts, allow the vertical position of the support plate to be changed in relation to the part incorporating the wings. The disadvantages are similar to the previous constructions where it is the part incorporating the wings that is movable.

[0010] For these two-part stops, adjustment is generally done with the shoes and often in several operations to adjust the tightness.

[0011] An object of the present invention is therefore to propose a solution, simple and reliable to use, to make the binding automatically compatible, without adjustment by the user, with shoes having different dimensions concerning their interface with the binding.

[0012] Another object of the present invention is to propose a solution, simple and reliable to use, to allow the use of alpine ski boots and ski touring boots on the same binding.

[0013] Another aim of the invention is to propose a binding automatically compatible with several categories of shoe without significantly disrupting the operation of the lateral release mechanism.

[0014] Other objects, features, and advantages of the present invention will become apparent from the following description and accompanying drawings. It is understood that other advantages may be incorporated. SUMMARY

[0015] To achieve this objective, according to one embodiment, a stop is provided, for example a front stop, for a binding of a shoe on a sliding board comprising the characteristics of claim 1.

[0016] Thanks to this construction, the clamping force exerted by the sole clamp on the boot remains controlled regardless of the dimensions of the part of the boot forming the interface with the binding. For example, if an interface with a greater thickness, taken in a vertical direction, is used, as is the case for ski touring boots, the cam makes it possible to control the clamping force and reduce the friction forces between the sole clamp and the boot during lateral release. This makes it possible to improve the reliability of lateral release. The invention thus makes it possible to considerably improve the safety of the user of a self-configuring binding.

[0017] It is then possible to use, with a binding equipped with this stop, boots having variable dimensions of interfaces with the binding. Typically, the present invention makes it possible to use with the same binding, alpine ski boots and ski touring boots, these two categories being distinguished in particular by the dimensions of the parts making the interface with the front stop, parts which will subsequently be called sole for the sake of brevity. Whatever the type of boots used, the lateral release force remains controlled.

[0018] For this type of stop where the movement of the sole clamp is energized, the distance of the sole clamp from the gliding board causes an increase in the compression of the second elastic means and thus causes an increase in the return force generated by this second elastic means. In the absence of the cam, this increase in the return force would cause a very significant increase in the pressing force that the sole clamp exerts on the shoe. This pressing force would generate friction between the sole clamp and the shoe. This friction would oppose the mobility of the sole clamp relative to the body and would thus oppose the lateral release and, ultimately, the release of the shoe. The release of the shoe would therefore not be controlled and the user's safety would be significantly degraded, in a configuration where the sole clamp would be far from the gliding board.

[0019] The claimed construction adds a cam that tends to reduce the increase in the pressing force when the sole clamp is moved away from the board. In other words, this allows, for example, to have little variation in pressing force, or at least a controlled variation, regardless of the position of the sole clamp.

[0020] Depending on the configuration of the stop and in particular the shape of the cam and the dimensioning of the second elastic means, it can be expected that the pressing force remains constant regardless of the position of the sole clamp relative to the sliding board. Thus, regardless of the type of shoes used, it is possible to obtain a lateral release force which remains substantially constant.

[0021] Optionally, the stop may further have at least any one of the following features which may be taken separately or in combination.

[0022] According to one example, the body is pivotally mounted on the chassis about an axis of rotation substantially transverse to a longitudinal axis of the chassis, the cam being dimensioned so as to modify the direction of the return force exerted by the second elastic means on the body so that the distance between the direction of the return force and the axis of rotation of the body differs depending on the angle of inclination of the body relative to the chassis. The inclination of the body relative to the chassis is measured in a vertical plane passing through the longitudinal axis of the chassis.

[0023] In one example, the rotation axis of the body is positioned at the upper part of the body, above the first elastic means of the lateral trigger mechanism.

[0024] According to one example, the cam and the vertical holding mechanism are shaped so that the pressing force Fp does not vary by more than 20%, preferably does not vary by more than 10%, regardless of the position of the sole clamp relative to the body. This makes it possible to avoid significantly increasing the intensity of the lateral release force that must be exerted on the sole clamp, i.e. the threshold value allowing the stop to be tilted into the release configuration in order to release the shoe.

[0025] According to one example, the second elastic means is arranged so as to act continuously on the body, regardless of the position of the sole clamp relative to the body.

[0026] According to one example, the sole clamp exerts on the first elastic means of the lateral release mechanism an action opposite to that exerted by the first elastic means on the sole clamp. The second elastic means is arranged so as to act on the body independently of the action of the sole clamp on the first elastic means of the lateral release mechanism. The movement of the sole clamp relative to the body does not act on the second elastic means. Thus, the first elastic means and the second elastic means operate independently.

[0027] According to one example, the first elastic means is configured to be alternately compressed and relaxed along a first working axis, the second elastic means is configured to be alternately compressed and relaxed along a second working axis, said second working axis being misaligned relative to said first working axis. According to one example embodiment, the first and second working axes are contained in the same vertical plane. However, they are not parallel.

[0028] In one example, the sole clamp includes two wings, each wing being pivotally mounted on the body. In one example, each wing pivots on the body independently of the other wing.

[0029] According to one example, the cam is dimensioned so that the return torque exerted on the body, and characterized by the product of the intensity of the return force by the distance between the direction of the return force and the axis of rotation of the body, is, when the sole clamp is distant from the sliding board, identical, to within 20%, preferably to within 10%, to this return torque when the sole clamp is close to the lower face of the chassis.

[0030] According to one example, the lateral release mechanism comprises an adjustment device configured to adjust a threshold value of a release force to be applied by the shoe to the lateral release mechanism to cause the sole clamp to move from a latching configuration to a release configuration. According to one example, the toe piece also comprises a compensation mechanism configured to exert an additional return force on the body, the intensity of the additional return force being a function of said adjustment. The pressing force is then a function of the return force exerted by the second elastic means and the additional return force exerted by the compensation mechanism. According to one example, the compensation mechanism is configured to increase the pressing force when said adjustment increases the threshold value of the release force.Thus, if the user wishes to be more firmly held laterally, he will adjust the adjustment device accordingly. This will automatically increase the force of the sole clamp on his shoe. This further improves the safety provided by the stop. Thus, the proposed stop allows: . both to maintain a constant pressing force regardless of the shoe used when the user wishes to maintain the setting of the threshold value of the trigger force, and at the same time to vary this pressing force according to the trigger threshold value set by the user, typically by increasing the pressing force when the user increases the lateral trigger threshold value.

[0031] Another aspect relates to a binding for a shoe on a sliding board, comprising a toe piece as described above and a complementary toe piece, said toe piece being one of a front toe piece and a heel piece and said complementary toe piece being the other of a front toe piece and a heel piece.

[0032] Another aspect concerns a sliding board equipped with at least one stop according to the preceding paragraphs. BRIEF DESCRIPTION OF THE FIGURES

[0033] The aims, objects, as well as the characteristics and advantages of the invention will emerge more clearly from the detailed description of an embodiment thereof which is illustrated by the following accompanying drawings in which: [ Fig. 1 ] There Figure 1 is a perspective view of a stop according to an exemplary embodiment of the present invention and of a portion of a sliding board equipped with such a stop. Fig. 2 ] There Figure 2is another perspective view of the stop illustrated in Figure 1 and part of a shoe. Fig. 3 ] There Figure 3 is an exploded perspective view of the stop illustrated in Figure 1 . [ Fig. 4 ] there Figure 4 is another exploded perspective view of the stop illustrated in Figure 1 . [ Fig. 5 ] There Figure 5 is a horizontal sectional view of the stop illustrated in Figure 1 . [ Fig. 6 ] There Figure 6 is a view of the stop illustrated in Figure 1 , in vertical section and passing through a median axis of the stop. The stop is shown in the low position, that is to say in a position in which it is not stressed by a shoe. Fig. 7 ] There Figure 7 corresponds to the Figure 6 , a part of a first category of shoe being illustrated in engagement with the toe piece. Fig. 8 ] There figure 8 corresponds to the Figure 6, a part of a second category of shoe, different from the first category of shoe, being illustrated in engagement with the toe piece. Fig. 9A ] There Figure 9A is a graph illustrating the plating force as a function of the body's inclination angle relative to the chassis for several lateral release threshold setting values. Fig. 9B ] There Figure 9B is a graph showing the lateral release force as a function of the body's lean angle relative to the chassis for several lateral release threshold setting values. Fig. 10 ] There Figure 10 is a view of a stop according to another embodiment, which is not part of the claimed invention, in vertical section and passing through a median axis of the stop. The stop is shown in a low position, that is to say in a position in which it is stressed by a first category of shoe. Fig. 11 ] There Figure 11is a view identical to that of the Figure 10 , but in which the stop is in a high position, that is to say in a position in which it is stressed by a second category of shoe. The drawings are given as examples and are not limiting of the invention. They constitute schematic representations of principle intended to facilitate the understanding of the invention and are not necessarily to the scale of practical applications. DETAILED DESCRIPTION

[0034] In the following detailed description, terms such as "horizontal", "vertical", "longitudinal", "transverse", "upper", "lower", "top", "bottom", "front", "back", "inside", "outside" may be used. These terms must be interpreted relatively in relation to the normal position of the binding / boot / sliding board assembly, and the normal direction of advancement of the user of the assembly. For example, the notions "horizontal" and "longitudinal" correspond to the main direction of extension of the sliding board. The face of the sliding board intended to receive the binding is oriented "upwards" and the face of the sliding board intended to rest on the snow is oriented "downwards". For illustrative and non-limiting purposes, reference may be made hereinafter to a ski as a sliding board or to a skier as a user.

[0035] We will also use a reference whose longitudinal or back / front direction corresponds to the X axis, the transverse or right / left direction corresponds to the Y axis and the vertical or down / up direction corresponds to the Z axis.

[0036] Furthermore, "engagement" refers to the attachment of the shoe to the binding and "release" refers to the detachment of the shoe from the binding. More specifically, "lateral release" corresponds to the release of the binding by a lateral force of the shoe on the binding. In the embodiments described below, the lateral release is achieved at the front stop, by a lateral movement of the front of the shoe. Typically, this lateral movement is caused by the user falling. An engagement configuration corresponds to an engagement configuration for which the shoe is engaged with the binding.

[0037] Binding release level is a measure of the amount of force required by the boot to exert on a binding element in order to release the boot from the binding via the release mechanism. This value may be marked on the binding in accordance with ISO 9462 or one of its later editions. It may correspond to a setting value or a pre-setting value of the associated binding. For the release level to be effective, the spacing of the binding elements must be appropriate for the boot intended to be engaged with the binding in order to ensure proper engagement of the binding.

[0038] The term "DIN setting" or "DIN value" when referring to release refers to the setting or value set by a German standards body (DIN for "Deutsches Institut für Normung"). A DIN-certified binding therefore meets certain standards. In particular, all DIN-certified bindings have equivalent settings. In particular, the release level of a binding of one brand set to a DIN value equal to 6 will be the same as that of a binding of another brand set to the same DIN value, if both bindings are DIN-certified.

[0039] In the remainder of the description, the term "on" does not necessarily mean "directly on". Thus, when it is indicated that a part or member A is supported "on" a part or member B, this does not mean that the parts or members A and B are necessarily in direct contact with each other. These parts or members A and B may be either in direct contact or be supported on each other by means of one or more other parts. The same applies to other expressions such as, for example, the expression "A acts on B", which may mean "A acts directly on B" or "A acts on B by means of one or more other parts".

[0040] In the context of the present patent application, the expression "kinematically interposed between" does not necessarily mean not in "contact with". Thus, if a part A is kinematically interposed between a part B and a part C, this does not mean that A and B are necessarily in direct contact or that A and C are necessarily in direct contact. It means that a movement or a force of the part B, respectively of the part C, can be at least partly transmitted to the part C, respectively to the part B, via the part A.

[0041] In this patent application, the term mobile corresponds to a rotational movement or a translational movement or even to a combination of movements, for example the combination of a rotation and a translation.

[0042] In this patent application, the term "mitigate" is equivalent to the term reduce. It can mean to reduce partially or entirely, that is, to cancel.

[0043] In this patent application, when two parts are indicated as distinct, this means that these parts are separate. They are: positioned at a distance from each other, and / or movable relative to each other and / or secured to each other by being fixed by added elements, this fixing being removable or not.

[0044] A single piece cannot therefore be made up of two separate pieces.

[0045] In this patent application, the term "integral" used to qualify the connection between two parts means that the two parts are linked / fixed relative to each other, according to all degrees of freedom, at least for a usage configuration, unless explicitly specified differently. For example, if it is indicated that two parts are integral in translation in an X direction, this means that the parts can be movable, possibly according to several degrees of freedom, excluding the freedom in translation in the X direction. In other words, if one part is moved in the X direction, the other part performs the same movement.

[0046] In the present patent application, an elastic means may for example be a spring, such as a coil spring, elastic washers such as Belleville washers, an elastomer, a rubber.

[0047] In the present patent application, the term cam device corresponds to a device comprising at least: a first surface, called a guide surface, also called a cam profile, carried by a first part, a second surface, carried by a second part. One of the first and second parts is movable, at least in rotation relative to a chassis around an axis of rotation. The first and second surfaces are configured so that, when the movable part is rotated relative to the chassis, the projected distance (D1, D2) between the axis of rotation (Y122) and the normal direction (Fr1, Fr2) at the point of contact between these two surfaces varies.

[0048] A non-limiting example of a stop according to the present invention will now be described in detail with reference to figures 1 to 9 .

[0049] As indicated in the section relating to the state of the art, a binding usually comprises two stops, one front and one rear, to hold a boot on a sliding board. In the non-limiting example which will be described subsequently, the stop considered is a front stop. Alternatively or in combination, the invention can also be applied to a rear stop.

[0050] The stop 1 comprises in particular a frame 11, a body 12, and a sole clamp 13. These elements will be described in detail later. Chassis 11

[0051] The frame 11 has a lower face 111 intended to be placed opposite an upper face 31 of a sliding board 3. The latter also has a lower face 32 intended to be in contact with a substrate such as snow. The lower face 111 of the frame 11 can be fixed to the upper face 31 of the sliding board 3 by being either directly in contact with the latter, or by being fixed to the sliding board 3 by means of another element.

[0052] This attachment can remove any degree of freedom between the frame 11 and the sliding board 3. To this end, and as can be seen in figures 1 , 3 And 4 , the frame 11 comprises fixing means, typically screws 113, which engage with a thread formed in the sliding board 3.

[0053] According to an alternative example, it can be provided that this attachment of the frame 11 to the sliding board 3 allows at least one degree of freedom, for example in translation, of the frame 11 relative to the sliding board 3. According to this alternative example, it can then be provided that the frame 11 is mounted on a slide which slides along a longitudinal axis of the sliding board 3. This allows an adjustment of its longitudinal position. Once the stop is positioned longitudinally, the frame is blocked so that it can no longer move in all directions. The frame is then integral with the sliding board according to all degrees of freedom in this usage configuration.

[0054] The chassis 11 also carries a support plate 112, an upper face of which is intended to come into contact with a part of a shoe 2. In the example illustrated, the support plate 112 is configured to receive a front part 21 of a shoe 2. More precisely, the lower surface 213 of a sole 22 of the shoe 2 comes to bear on the upper face of this support plate 112.

[0055] In this example, the frame 11 is defined by a median longitudinal axis X115 extending in a direction parallel to the X axis. The longitudinal axis X115 of the frame corresponds to the longitudinal axis of the stop. The longitudinal axis X115 of the frame, the longitudinal axis of the slide board 3 and the X axis are substantially parallel. Body 12

[0056] The body 12 of the stop 1 is mounted movably on the frame 11 and carries the sole clamp 13. In the example illustrated, this mobility is a rotational mobility. Alternatively, translational mobility or mobility combining rotational and translational movements can be provided.

[0057] In the illustrated example, the body 12 is mounted in rotation around an axis of rotation Y122 transverse to the longitudinal axis X115 of the chassis 11. These axes X115, X122 are referenced in particular in Figure 6 . They are respectively parallel to the X axis and the Y axis of the orthogonal XYZ reference frame illustrated in figures 5 And 6. Thus, the body 12 can tilt relative to the chassis 11 and, consequently, relative to the sliding board 3, according to an angle α which can be measured between the longitudinal axis X115 of the chassis 11 and a median longitudinal axis X121 of the body 12. The median axis X121 of the body 12 is contained in a plane parallel or identical to the plane ZX and the angle α is measured in this same plane passing through the median axis X121 of the body 12. The inclination of the body relative to the chassis is therefore measured in a vertical plane passing through the longitudinal axis of the chassis. According to a non-limiting example, the longitudinal axis X115 of the chassis 11 and the median axis X121 of the body 12 are included in the same plane, preferably the same vertical plane, preferably the plane ZX.

[0058] On the Figure 7 , the longitudinal axis X115 of the chassis 11 is parallel, or even coincident, with the median axis X121 of the body 12. The angle α is then zero. On the figures 7 And 8the median axis X121 of the body is inclined at an angle α (noted αa in Figure 7 and αb in figure 8 ) relative to the longitudinal axis X115 of the chassis 11. This angle α increases when the body 12, at the level of the sole clamp 13, moves away from the board 3.

[0059] The chassis comprises a yoke having two cheeks 114 carrying a shaft 1221 materializing the axis of rotation Y122. The shaft 1221 can be fixed relative to the yoke of the chassis 11, the body 12 then rotating around this shaft 1221. Alternatively, it can be provided that the shaft 1221 is fixed relative to the body 12 and that it is mounted in rotation in the yoke.

[0060] In this example, as seen on the figures 6 to 8, the rotation axis Y122 of the body 12 is positioned at the level of the upper part of the body. The yoke thus allows such positioning of the rotation axis, at a certain height of the upper face 31 of the sliding board 3. The body 12 can thus pivot mainly below this rotation axis Y122. Sole clamp 13

[0061] The stop 1 comprises a sole clamp 13. As indicated previously in the section relating to the state of the art, the sole clamp 13 has the function of keeping a part of the shoe 2 secured to the sliding board 3, at least in the vertical and transverse directions. For this, the sole clamp exerts a pressing force Fp on the part of the shoe 2 in order to keep it in contact with the support plate 112. This pressing force Fp is vertical or has a vertical component.

[0062] In this example, the sole clamp 13 has a lower bearing surface 131 and rollers 135 configured to come into contact with the shoe 2. When the stop 1 is a front stop, the part of the shoe 2 on which the sole clamp 13 exerts a pressing force is a front part. Preferably, the sole clamp 13 is configured so that the lower bearing surface 131 comes into contact with an upper surface 211 of the front part 21 of the shoe 2. Preferably, the sole clamp is also configured so that each roller 135 and more precisely a part of the external cylindrical surface of a roller 135 comes into contact with a lateral surface 212 of this front part 21 of the shoe 2. In the example illustrated for example in Figure 2, the front part 21 of the shoe 2 is an integral part or is at least partly formed by a sole 22 of the shoe 2. Alternatively, the front part of the shoe may be part of a separate insert, attached to the shoe.

[0063] According to another variant, the sole clamp acts on a part of the shoe 2 which is distinct from the sole 22 of the shoe 2. The term sole clamp 13 therefore does not necessarily imply contact of the sole clamp 13 at the level of a sole of the shoe 2. Indeed, the part of the shoe 2 on which the sole clamp 13 can exert the pressing force Fp may belong to a portion of the shoe located above the sole 22.

[0064] In the example illustrated, the sole clamp 13 of the stop comprises two wings 132 arranged on either side of the median axis X121 of the body 12. As illustrated in Figure 5, each wing 132 carries a roller 135 intended to come into contact with a lateral surface 212 of the front part of the shoe. Each wing 132 is mounted in rotation on the body 12 around an axis of rotation Z133. This axis of rotation Z133 is substantially vertical, in particular when the median axis X121 of the body 12 is aligned with the longitudinal axis X115 of the chassis 11. Naturally, this axis of rotation Z133 tilts relative to the chassis 11 and therefore relative to the vertical when the body 12 pivots around the axis Y122.

[0065] In an engagement configuration of the shoe 2, each wing 132 of the sole clamp 13 exerts a pressing force Fp on the shoe 2, via the lower support surface 131. This pressing force Fp tends to constrain the shoe 2 between the wing 132 and the support plate 112.

[0066] In a variant, the sole clamp 13 is a single-piece unit having two arms, each arm being intended to cover an upper surface and a lateral surface of an edge of the front part of the shoe. The sole clamp is also rotatably mounted on the body 12 around an axis of rotation Z, substantially perpendicular to the median axis X121 of the body 12. Side release mechanism

[0067] The body 12 also includes a side trigger mechanism configured: to retain or return each wing 132 into an engagement configuration with the shoe 3, allow the rotation of each wing 132 around its axis of rotation Z133 to move into a release configuration when the force Fd exerted by the shoe 2 on the binding is sufficient. This force, designated the release force, is referenced Fd in Figure 5 .

[0068] More precisely, the triggering force Fd exerted by the shoe 2 on the sole clamp 13 has at least one component perpendicular to the axis of rotation Z133 of the wing 132. When this component is sufficient, at least one of the wings 132 rotates around its axis of rotation Z133. This allows a movement of the front part of the shoe 2 relative to the chassis 11 in a substantially lateral direction, that is to say in a direction having a horizontal component (Y axis) and perpendicular to the longitudinal axis X115 of the chassis 11. In the triggering configuration, the wing 132 is no longer engaged with the front part of the shoe 2. The latter can then be released from the toe piece 1 and the binding. Typically, it is during a fall phase of the user that this force Fd allows a transition to the triggering configuration. The shoe can then separate from the sliding board.

[0069] The side release mechanism appears in particular on the figures 5 And 6 This mechanism comprises a tie rod 146 having a drive surface 147 which cooperates with a shaft 134 carried by a wing 132 of the sole clamp 13. In the example illustrated, the tie rod 146 has two drive surfaces 147 which each cooperate with a shaft 134 carried by one of the two wings 132. The movement of the tie rod 146, along its main direction of extension, causes the movement of the shaft 134 which causes the rotation of the wing 132 around its axis of rotation Z133. Preferably, the main direction of extension of the tie rod 146 is coaxial with the median axis X121 of the body 12.

[0070] The release mechanism also comprises at least one first elastic means 141 configured to return the tie rod 146 to a position by which the tie rod 146 brings the wing 132 into the engagement configuration. In the illustrated example, the first elastic means 141 tends to pull the tie rod 146 toward the front of the body 12 which tends to rotate the shaft 134 about the axis of rotation Z133 so that the roller 135 of the wing 132 approaches, in a horizontal plane, the longitudinal axis X115 of the chassis 11. The roller 135 is then maintained or is returned to the engagement configuration. When the boot is engaged with the binding, the roller of the left wing presses against the left lateral surface of the front portion of the boot and the roller of the right wing presses against the right lateral surface of the front portion of the boot.

[0071] For the transmission of the force between the first elastic means 141 and the tie rod 146, it can be provided that the body 12 has a housing 123 to receive at least part of the first elastic means 141. The first elastic means 141 has: a first end 1411 bearing, by direct contact or by means of an additional part such as a rocker 161 for example, on the body 12. In the example illustrated, the first end 1411 bears on a wall 124 of the bottom of the housing 123 by means of a rocker 161 which will be described in detail later. a second end 1412 bearing on the tie rod 146 or on a part integral with the tie rod 146.

[0072] Preferably, the first elastic means 141 is a spring that works in compression. It may be a coil spring. The first elastic means 141 compresses as the wings open or, in other words, as the rollers 135 of the wing 132 move away from the median axis X121 of the body 12 in a direction transverse to this median axis X121. This compression takes place along a working axis X142. This working axis X142 is preferably parallel or coincident with the median axis X121 of the body 12.

[0073] In the example illustrated, the tie rod 146 is secured to a sleeve 148 inside which the first elastic means 141 is housed at least in part. The sleeve 148 has a bottom wall 1481 on which the second end 1412 of the first elastic means 141 bears. Advantageously, an adjustment member 149 is provided which makes it possible to vary the distance between the shafts 134 and the second end 1412 of the first elastic means 141. This adjustment member 149 makes it possible to adjust the compression ratio of the first elastic means 141 when the wings 132 are in the engagement configuration. It therefore makes it possible to adjust the force that the user must exert to spread the wings and move into the release configuration. Typically, this adjustment member 149 makes it possible to adjust the “DIN value” as defined previously. This adjustment member 149 can be manipulated by the user using a tool.In the illustrated example, the adjustment member 149 has an imprint for cooperating with a tool and can form a screw head.

[0074] In this example, as seen on the figures 6 to 8 , the rotation axis Y122 of the body 12 is positioned at the upper part of the body, above the first elastic means 141 of the lateral trigger mechanism 14. Vertical holding mechanism

[0075] As indicated above, to vertically secure the shoe 2 to the sliding board, the shoe will be clamped between the support surface 131 of the sole clamp 13, that is to say, the combination of the support surfaces of the wings, and the support plate 112 of the chassis 12. Thus, the sole clamp 13 exerts a pressing force Fp on the shoe 2 via the sole clamp. The paragraphs below detail the kinematics for controlling this plating force Fp regardless of the angle α that the body 12 forms relative to the chassis 11. Subsequently, the position of the sole clamp 13 relative to the support plate 112 corresponds to the vertical position (along a Z axis) of the support surfaces 131 of the wings 132 of the sole clamp 13 relative to the horizontal surface tangent to the upper face of the support plate 112. This position is directly linked to the inclination α of the body 12 carrying the sole clamp.The distance of the sole clamp 13 from the support plate 112 therefore corresponds to an increase in the vertical distance H, projection on an axis Z, between the support surfaces 131 and the support plate.

[0076] For this purpose, the stop 1 comprises a vertical holding mechanism. This mechanism comprises at least one second elastic means 151 configured to exert a return force Fr1 on the body 12. This return force Fr1 tends to bring the bearing surfaces 131 of the wings 132 of the sole clamp 13 back towards the sliding board 3, more precisely towards the support plate 112 resting on the sliding board 3. In more detail, this return force Fr1 is exerted in a direction, substantially vertical, which makes it possible to generate a torque M on the body 12 around its axis of rotation Y122. This torque generates at the level of the bearing surface 131 of the sole clamp 13 the pressing force Fp on the shoe 2.

[0077] The second elastic means 151 can be carried either by the body 12, as is the case in the embodiment of the figures 1 to 9 , either by the chassis 11, as is the case in the embodiment illustrated in Figure 10 , , which is not part of the claimed invention. In these two embodiments, the second elastic means 151 is configured so that the chassis 11 generates a return force Fr1 on the body 12.

[0078] In the example illustrated in Figure 7, the median axis X121 of the body 12 is inclined at an angle αa relative to the longitudinal axis X115 of the chassis 11 and the return force is denoted Fr1a. The product of the intensity of this force Fr1a multiplied by the distance D1a between the direction of this force Fr1a and the axis of rotation Y122 is equal to the value of the torque Ma generated by this force Fr1a on the body 12. Thus, Ma = Fr1a x D1a. In the absence of compensation means, compensation means which will be described later, the intensity of the pressing force Fpa exerted by the sole clamp 13 on the shoe 2 is equal to this torque Ma divided by the distance Dp between the direction of this pressing force Fpa and the axis of rotation Y122. Thus, Fpa = Ma / Dp = Fr1a / (D1a x Dp).

[0079] There Figure 7 illustrates the references Fr1a, D1a, Ma, Fpa, Dp.

[0080] The second elastic means 151 is configured so that the intensity of the return force Fr1 resulting from the action of the second elastic means increases when the sole clamp 13 moves away from the support plate 112. Preferably, the second elastic means 151 is a spring that works in compression. It may be a coil spring. It compresses as the sole clamp 13 moves away from the support plate 112. This compression takes place along a working axis X152. According to one example, this working axis X152 is parallel to the median axis X121 of the body 12. Preferably, this working axis X152 is parallel but not coaxial to the working axis X142 of the first elastic means 141. These two axes are for example included in the same vertical plane ZX.

[0081] On the non-limiting example illustrated in figures 1 to 9, the body has a housing 127 shaped to accommodate a part, acting as a piston 155, capable of translating in the housing 127. This piston has a head 158 and a body 156. The body forms a sleeve 156, open at one of its ends and having an internal support wall 157 at the other of its ends. The second elastic means 151 is housed partly inside the sleeve 156. A first end 1511 of the second elastic means 151 bears on a wall 128 of a housing 127 carried by the body 12. A second end 1512 of the second elastic means 151 bears on the bearing wall 157 of the piston 155. The force exerted by the compression of the second elastic means 151 therefore tends to move the head 158 of the piston 155 away from the wall 128 of the body 12. The head 158 of the piston 155 has an external face intended to come into contact with an extension 116 of the chassis 11 or a part carried by the chassis.

[0082] The return force Fr1 resulting from the action of the second elastic means 151, between the chassis 11 and the body 12, is applied at the level of the contact between the head 158 of the piston 155 and the extension 116.

[0083] Furthermore, this extension 116 and the head 158 of the piston 155 are configured so that when the body 12 pivots around the axis of rotation Y122 the piston 155 moves in the housing 127 thus causing a variation in the compression of the second elastic means 151. Consequently, depending on the inclination of the body 12 relative to the frame 11 the intensity of the return force Fr1 varies. More precisely, in this case, when the body 12 pivots so as to increase the angle α, the extension 116 compresses the second elastic means 151 which increases the intensity of the return force Fr1 imposed by the frame 11 on the body 12 via the piston 155. Mitigation device

[0084] Particularly advantageously, the stop 1 comprises an attenuation device configured so as to reduce the increase in the intensity of the plating force Fp1 caused by a distance of the sole clamp 13 from the support plate 112.

[0085] Typically, the attenuation device makes it possible to limit to a maximum of 20%, preferably to a maximum of 10% and preferably to a maximum of 5%, the variation in the intensity of the plating force Fp1, over the entire travel of the body 12 relative to the chassis 11.

[0086] According to one embodiment, the variation in the intensity of the plating force Fp1 varies in an interval between -20% and +10%, preferably in an interval between -15% and +5%.

[0087] According to an exemplary embodiment, the intensity of the pressing force Fp1 remains constant whatever the position of the body 12 relative to the chassis 11, in this example whatever the value of the angle α formed between the median axis X121 of the body 12 and the longitudinal axis X115 of the chassis 11. For this exemplary embodiment, as the distance Dp between the point of application of the pressing force Fp of the sole clamp 13 on the shoe 2 and the axis of rotation Y122 of the body 12 is substantially constant, the intensity of the torque Ma, Mb is substantially constant whatever the position of the body 12 relative to the chassis 11.

[0088] The angle α is dictated by the distance H, in projection along the vertical direction Z and in the engagement configuration, between the upper face of the support plate 112 and the point of application of the pressing force Fp of the sole clamp 13 on the shoe 2. This distance is noted: H0 in Figure 6and corresponds to the configuration of the stop in the absence of a shoe; Ha in Figure 7 and corresponds to the distance imposed by a shoe of a first type, for example an alpine ski boot and; Hb in figure 8 and corresponds to the distance imposed by a shoe of a second type, for example a ski touring shoe.

[0089] In this example, the front stop is configured so that: When no boot is engaged with the toe piece, the angle α is equal to 0°, and the clamping height corresponds to the reference height H0. When a boot of a first type, for example an alpine ski boot, is engaged with the toe piece, the angle α is equal to 1.5°, and the clamping height Ha corresponds to the reference height H0 + 1.3 mm. When a boot of a second type, for example a ski touring boot, is engaged with the toe piece, the angle α is equal to 5.5°, and the clamping height Hb corresponds to the reference height H0 + 5.7 mm.

[0090] Furthermore, the front stop comprises a stop device which makes it possible to limit the inclination of the body 12. Thus, in this example, at most, the angle α is equal to 8°, and the clamping height Hm corresponds to the reference height H0 + 8.2 mm.

[0091] The stop is therefore designed so that the body 12 can tilt by a maximum angle α of 15°, preferably a maximum angle of 10°. In other words, the stop is designed so that the body 12 can tilt so that the maximum clamping height Hm corresponds to the reference height H0 + 15 mm, preferably a maximum height corresponding to the reference height H0 + 10 mm.

[0092] Thus, whatever the dimensions of the shoe part 1, intended to be inserted into the stop 1, the torque M as well as the pressing force Fp exerted by the sole clamp 13 on this shoe part 2 remain constant or within a small interval. Thus, during a lateral release, the variation in the friction exerted by the sole clamp 13 on the shoe 2 also remains constant or within a small interval. The threshold value of the release force Fd necessary for switching to the release configuration therefore also remains constant or within a small interval whatever these shoe dimensions. The safety of the user is therefore preserved whatever the shoes he uses with this same stop 1.

[0093] To achieve a reduction in the increase in the intensity of the plating force Fp1 caused by a distance of the sole clamp 13 from the support plate 112, the attenuation device is configured to modify the distance D1 between the direction of application of the restoring force Fr1 and the axis of rotation Y122 of the body 12. In this example, the distance D1 decreases at the same time as the restoring force Fr1 increases and the sole clamp 13 moves away from the support plate 112.

[0094] For this purpose, the attenuation device comprises a cam, also called a cam device, arranged on one of the parts allowing the transfer of the return force Fr1 from the chassis 11 to the body 12. This cam is shaped to vary the distance D1.

[0095] In the example illustrated in figures 1 to 9, this cam is kinematically arranged between the second elastic means 151 and the chassis 11. The cam may be arranged at other locations. For example, in an embodiment which is not part of the claimed invention and which will be described in detail with reference to the Figure 10 , the cam can be arranged between the second elastic means 151 and the body 12.

[0096] In the example illustrated in figures 1 to 9, the cam device is formed by the cooperation of the extension 116 secured to the frame 11 and the external face of the piston 155. These parts 116, 155 are shaped so that the distance D1, as defined previously, is reduced as the angle α formed by the inclination of the body 12 relative to the frame 11 increases. In this example, the external face of the head 158 of the piston 155 forms a first cam profile 153. Furthermore, the extension 116 forms a second cam profile 154 intended to cooperate with the first cam profile 153. Variants are naturally conceivable. For example, one could provide that one of the extension 116 and the external face of the piston 155 has a continuous surface and that only the other of the extension 116 and the external face of the piston 155 has a cam profile.

[0097] According to this embodiment, the cam therefore has a first cam profile 153 secured to the body 12 rotating around the axis of rotation Y122, and a second cam profile 154 secured to the chassis 11.

[0098] The cam profiles 153, 154 are shaped so that the direction of the return force Fr1 approaches the axis of rotation Y122 as the distance H imposed by the shoe 2 on the stop 1 increases.

[0099] THE figures 7 And 8 illustrate in a particularly clear manner the operation of this mitigation device.

[0100] On the Figure 7, the shoe 2 used imposes a distance Ha between the support plate 112 of the chassis 11 and the support surface 131 of the sole clamp 13. It follows that the body 12 has an inclination αa relative to the chassis 11. The chassis 11, by means of the extension 116, exerts on the body 12 a return force Fr1a, thanks to the second elastic means 151. The relative position of the first and second cam profiles 153, 154 of the cam device dictates the direction in which this return force Fr1a is exerted. This cam device therefore dictates the distance D1a between the direction of this return force Fr1a and the center of rotation Y122 of the body 12. Consequently, this cam device impacts the intensity of the pressing force Fpa exerted by the sole clamp 13 on the shoe 2, since, as indicated previously, Fpa = Ma / Dp = Fr1a / (D1a x Dp).

[0101] On the figure 8, the shoe 2 used imposes a distance Hb, with Hb > Ha, between the support plate 112 of the chassis 11 and the support surface 131 of the sole clamp 13. It follows that the body 12 has an inclination αb, with αb > αa, relative to the chassis 11. The chassis 11, by means of the extension 116, exerts on the body 12 a return force Fr1b, thanks to the second elastic means 151. The relative position of the first and second cam profiles 153, 154 of the cam device dictates the direction in which this return force Fr1b is exerted. This cam device therefore dictates the distance D1b between the direction of this return force Fr1b and the center of rotation 122 of the body 12. As is clearly shown in the figures 7 And 8 , D1b < D1a. The intensity of the restoring force Fpb exerted by the sole clamp 13 on the shoe 2 is such that Fpb = Mb / Dp = Fr1b / (D1b x Dp).

[0102] The second elastic means 151 and the cam device are configured so that the difference between D1b and D1a on the one hand and the difference between Fr1b and Fr1a on the other hand are such that the intensities of the return forces Fpb and Fpa are identical to within 20% preferably, to within 10%, preferably to within 5%. According to one embodiment, the intensities of the return forces Fpb and Fpa vary in an interval between -20% and +10%, preferably in an interval between -15% and +5%. Compensation mechanism

[0103] According to an optional but particularly advantageous embodiment, the stop 1 comprises a compensation mechanism. This compensation mechanism is configured to adapt the plating force Fp according to the adjustment made on the lateral trigger mechanism 14. More precisely, this compensation mechanism makes it possible to automatically increase the value of the plating force Fp when the user adjusts the lateral trigger mechanism 14 to increase the lateral trigger threshold value.

[0104] Thus, according to one embodiment: thanks to the attenuation device described above, for the same setting value of the lateral trigger threshold, typically the same DIN value, the plating force Fp remains constant whatever the angle α, therefore whatever the dimension H of the shoe 2. This scenario is illustrated in Figure 9A: at constant DIN, Fp remains constant whatever the inclination of the body 12, whatever the value of the angle α, thanks to the compensation device, for two adjustment values ​​of the lateral triggering threshold, typically for two DIN values, the plating force Fp varies and this for the same inclination of the body 12, or for the same value of the angle α. This scenario is also illustrated in Figure 9A: if the DIN value increases, then Fp increases. Indeed, when the user increases the DIN value, he may wish to have a firmer hold of his boot in the binding and seek to obtain both the threshold value of the release force Fd and the greater engagement force Fp. In the absence of the compensation mechanism, an increase in the threshold value of the release force Fd, an increase desired by the user, is not accompanied by an increase in the engagement force Fp. The compensation mechanism makes it possible to overcome this drawback.

[0105] At the same time, as illustrated in Figure 9B, the lateral trigger threshold value Fd, increases slightly the more the body is tilted, that is, when the angle α increases, but the value of the DIN setting remains constant. Furthermore, the lateral trigger threshold value Fd, increases significantly when the user increases the value of the DIN setting, in this example by going from DIN setting 11 to DIN setting 16.

[0106] As illustrated in figure 8, the compensation mechanism exerts on the body 12 an additional restoring force Fr2b, which generates a torque M2b on the body 12, around its axis of rotation Y122. The distance between the direction of this additional restoring force Fr2b and the axis of rotation Y122 is denoted D2b. Thus, the torque M2b is: M2b = Fr2b x D2b. Furthermore, as we have seen previously, the second elastic means 151 also exerts a restoring force Fr1b on the body 12, which results in a torque M1b equal to M1b = Fr1b x D1b. Thus, the torque exerted on the body is the sum of the two previous torques and is: Mb = M1b + M2b. The plating force Fpb is directly proportional to the torque Mb and is: Frp = Mb / Dp. We then deduce the value of the clamping force Fpb exerted by the sole clamp 13 on the shoe 2 which is: Fpb = Fr1b / (D1b x Dp) + Fr2b / (D2b x Dp).

[0107] The compensation mechanism comprises a rocker 161 shown in perspective on the figures 3 And 4 . This rocker 161 is configured to be housed partly in the housing 123 of the body 12 receiving the first elastic means 141. The rocker 161 is configured to rotate inside the body 12, around a direction substantially perpendicular to the working axis X142 of the first elastic means 141. Typically, the rocker 161 is configured to rotate, over a small angular sector, around a direction transverse to the median axis X121 of the body 12. For this, the rocker preferably comprises a pivot portion 1611 configured to be housed in a seat 125 formed in the wall 124 of the housing 123.

[0108] In this construction, as mentioned previously, the rocker is interposed between the first end 1411 of the first elastic means 141 and the body 12. The first elastic means therefore bears on the rocker. Thus, when the rocker is pivoted, the first elastic means is acted on, compressing it, for example, when the rocker pivots in one direction.

[0109] The rocker 161 also comprises a support portion 1612 interposed between the second end 1412 of the first elastic means 141 and the wall 124 of the bottom of the housing 123 of the body 12. Thus, the first elastic means 141 bears in particular on this support portion 1612.

[0110] Preferably, the pivot portion 1611 and the support portion 1612 are located on either side of the working axis X142. For this purpose, the rocker 161 comprises an opening 1615 shaped to be crossed by the tie rod 144.

[0111] The rocker 161 also includes an extension 1616 which extends beyond the body 12 to come into contact with a portion 117 of the chassis 11 or a part carried by the chassis.

[0112] At least one of the rocker 161 and the part 117 of the chassis has a cam profile. In the illustrated example, the extension 1616 carries a cam profile 1613 which cooperates with a profile 1614, having a general slope shape, carried by the part 117 of the chassis.

[0113] As illustrated in Figure 7, that is to say with a shoe 2 which causes an inclination of the body 12 relative to the chassis 11 by a small angle αa (shoe 2 “low”), the cooperation between the cam surface 1613 and the profile 114 allows the support portion 1612 to be maintained in its seat 126, that is to say, in a position in which this support portion 1612 does not or only slightly constrains the first elastic means 141. In this example, with the angle αa the cam profile 1613 keeps the support portion 1612 pressed into a seat 126 formed in the wall 124 of the body 12. The rocker 161 does not compress the first elastic means 141.

[0114] On the contrary, as illustrated in figure 8, that is to say with a shoe 2 which causes an inclination of the body 12 relative to the chassis 11 by a high angle αb (shoe 2 “high”), the cooperation between the cam surface 1613 and the profile 114 causes the support portion 1612 to move away from its seat 126. This results in the compression of the first elastic means 141. This results in a return force Fr2b which, with the return force Fr1b, contributes to the generation of a torque Mb on the body 12, around its axis of rotation Y122. This torque Mb induces the pressing force Fpb of the sole clamp 13 on the shoe 2. Furthermore, since the first elastic means 141 is more strongly compressed, the threshold value of the triggering force Fd increases as illustrated in Figure 9B .

[0115] So, these figures 7 And 8illustrate the contribution of the return force Fr2 exerted by the compensation mechanism on the plating force Fp. These figures also clearly illustrate the compression imposed by this compensation mechanism on the first elastic means 141 and therefore on the threshold value of the triggering force Fd (typically the DIN value).

[0116] As stated above, this compensation mechanism is optional and the stop can function perfectly well without such a mechanism. Alternative embodiment

[0117] An alternative embodiment, which is not part of the claimed invention, will now be described with reference to figures 10 And 11 . Except for the details which will be given below, all the characteristics as well as all the advantages and technical effects mentioned above concerning the method of realizing the figures 1 to 9are perfectly transposable and combinable with the embodiment which is described with reference to the figures 10 And 11 .

[0118] The hatching used for the figures 10 And 11 may vary without this implying structural differences. Furthermore, on the Figure 10 a thread 1461 is shown on a portion of the tie rod 146, this thread 1461 cooperating with the adjustment member 149 described with reference to the embodiment illustrated in the figures 1 to 9 .

[0119] In this embodiment, the second elastic means 151 is carried by the chassis 11, unlike the first embodiment where the second elastic means 151 is carried by the body 12. More precisely, this first elastic means has one end bearing on a bearing wall 119 secured to the chassis 11 and another end bearing on a bearing wall 157 carried by a piston 155 mounted to slide in translation on the chassis 11. This translation is carried out along an axis parallel to the longitudinal axis X115 of the chassis 11. Thus, the body 12 is rotating relative to the second elastic means 151.

[0120] This piston 155 has a surface 154 which slides relative to the frame 11 and relative to the axis of rotation Y122 of the body 12. The body 12 has a surface 153 shaped to remain in contact with the surface 154. The return force Fr1a exerted by the second elastic means 151 is applied to the body 12 at the level of contact between the surfaces 153 and 154. Thus, these surfaces 153, 154 are kinematically interposed between the second elastic means 151 and the body 12.

[0121] There Figure 10 illustrates the stop in the low position, that is to say in a position in which it is stressed by a first category of shoe. The median axis X121 of the body is therefore inclined relative to the longitudinal axis X115 of the chassis 11 by a non-zero angle of inclination αa.

[0122] There Figure 11illustrates the stop in the high position, that is to say in a position in which it is stressed by a second category of shoe. The median axis X121 of the body is therefore inclined relative to the longitudinal axis X115 of the chassis 11 by a non-zero angle of inclination αb.

[0123] According to this alternative embodiment, the cam has a first cam profile 153 secured to the body 12, and a second cam profile 154 carried by the chassis 11 and preferably being slidably mounted on the chassis 11.

[0124] These surfaces 153 and 154 are configured to form the cam device of the attenuation device described above. At least one of these surfaces 153, 154 has a cam profile such that an increase in the inclination of the body 12 relative to the chassis 11 (so as to move the sole clamp 13 away from the support plate 112), causes both: a greater compression of the second elastic means 151, a variation in the direction of application of the return force Fr1a, Fr1b exerted on the body 12, thanks to the second elastic means 151, by means of the cooperation between the surfaces 153 and 154, this variation in direction tending to reduce the distance D1 (D1b < D1a) between this direction and the axis of rotation Y122 of the body 12.

[0125] Thus, for this embodiment as for that described with reference to the figures 1 to 9, the attenuation device makes it possible to limit, or even cancel, the variation in the intensity of the plating force Fp when the body 12 tilts relative to the chassis 11. Without an attenuation device according to the invention, the intensity of the plating force Fp tends to vary proportionally depending on the inclination of the body relative to the chassis. Consequently, the attenuation device makes it possible to control the plating force Fp according to the inclination of the body and in particular, to avoid having a significant plating force Fp at the end of the body's travel.

[0126] With the configurations of the non-limiting examples described above, it is noted that the second elastic means 151 is arranged so as to act on the body 12, that is to say to exert on the latter a return force Fr1, whatever the position of the sole clamp 13 relative to the body 12. Furthermore, it will be noted that the second elastic means 151 acts on the body 12 independently of the action that the sole clamp 13 exerts on the first elastic means. Thus, the first elastic means and the second elastic means act in a perfectly independent manner. Examples of possible variants

[0127] The invention is not limited to the embodiments previously described but extends to all embodiments covered by the claims.

[0128] According to a variant, the first elastic means extends transversely, in a Y direction.

[0129] For example, although in the detailed description and the figures the stop incorporating the cam is a front binding stop, the invention also extends to a rear stop, also referred to as a binding heel piece.

[0130] Furthermore, although in the detailed description the mobility of the body 12 relative to the chassis 11 is a mobility in rotation around the axis of rotation 122, the invention also extends to a configuration in which the body 12 is movable in translation relative to the chassis 11, or is movable according to a combination of a rotational and translational movement relative to the chassis 11.

[0131] In the foregoing description, the non-limiting examples may relate to a sliding board forming a ski and a ski boot. The invention extends to sliding boards other than skis and for example to snowboards and boots adapted to snowboards.

[0132] Furthermore, in the preceding example, the retaining device, also referred to as a sole clamp 13, comprises two wings 132 pivotally mounted on the body, each pivoting about an axis of rotation specific to them. It is nevertheless possible to provide for the two wings to be integral in rotation. They may, for example, form a single-piece part in the general shape of a “U” or a “V” mounted in rotation on the body 12 about a single axis.

[0133] Furthermore, in the preceding example, the vertical holding mechanism comprises a single second elastic means. It is nevertheless possible to provide for this vertical holding mechanism to comprise two or more second elastic means. For example, two springs may be provided, arranged on either side of the median axis X121 of the body 12, and each cooperating with a cam profile.

Claims

1. Retaining piece (1) for a binding for binding a boot (2) to a gliding board (3), comprising: - a chassis (11) having a lower face (111) configured to be secured to the gliding board (3), - a body (12) movably mounted on the chassis (11), - a sole clamp (13) movably mounted on the body (12) and adapted to come into contact with an upper surface (211) and at least one lateral part (212) of a front or rear part of the boot (2) when the boot (2) is engaged with the binding, - a lateral release mechanism comprising at least a first elastic means (141) acting on the sole clamp (13) to return it to a configuration of engagement with the boot (2), - a vertical-retention mechanism comprising a second elastic means (151), distinct from the first elastic means (141), and arranged so as to continuously exert a return force (Fr1a, Fr1b) on the body (12) to return the sole clamp (13) towards the lower face (111) of the chassis (11), this return force producing a pressing force (Fp)that presses the sole clamp (13) intimately against the boot (2) when the boot (2) is engaged with the binding, wherein the retaining piece (1) comprises at least one cam (153, 154), kinematically interposed between the second elastic means (151) and one of either the chassis (11) or the body (12), the cam (153, 154) being shaped to modify, depending on the position of the body (12) relative to the chassis (11), the direction of the return force (Fr1a, Fr1b) exerted by the second elastic means (151) on the body (12) so as to lessen any variation in the pressing force (Fp) when the sole clamp (13) is moved away from the lower face (111) of the chassis (11), and characterized in that a first profile (153) of the cam is translationally mounted on the body (12), and the second elastic means (151) acts directly on a piston (155) capable of translational movement in a housing (127) of the body (12), a part of the piston forming the first cam profile (153).

2. Retaining piece (1) according to the preceding claim, wherein the body (12) is mounted so as to pivot on the chassis (11) about an axis of rotation (Y122) substantially transverse to a longitudinal axis (X115) of the chassis (11), the cam (153, 154) being dimensioned so as to modify the direction of the return force (Fr) exerted by the second elastic means (151) on the body (12) so that the distance (Da, Db) between the direction of the return force (Fr) and the axis of rotation (Y122) of the body (12) differs as a function of the angle (α) of inclination of the body (12) with respect to the chassis (11).

3. Retaining piece (1) according to the preceding claim, wherein the axis of rotation (Y122) of the body (12) is positioned at the upper part of the body, above the first elastic means (141) of the lateral release mechanism.

4. Retaining piece (1) according to any one of the preceding claims, wherein the second elastic means (151) is borne by the body (12).

5. Retaining piece (1) according to any one of the preceding claims, wherein the cam (153, 154) and the vertical-retention mechanism are shaped such that the pressing force (Fp) does not vary by more than 20%, and preferably does not vary by more than 10%, whatever the position of the sole clamp (13) relative to the body (12).

6. Retaining piece (1) according to any one of the preceding claims, wherein the second elastic means (151) is arranged to act continuously on the body (12) whatever the position of the sole clamp (13) relative to the body (12).

7. Retaining piece (1) according to any one of the preceding claims, wherein the second elastic means (151) is arranged to act on the body (12) independently of the action of the sole clamp (13) on the first elastic means (141) of the lateral release mechanism (14).

8. Retaining piece (1) according to any one of the preceding claims, wherein the first elastic means (141) is configured to be alternately compressed and relaxed along a first working axis (X142), the second elastic means (151) is configured to be alternately compressed and relaxed along a second working axis (X152), said second working axis (X152) being misaligned with respect to said first working axis (X142).

9. Retaining piece (1) according to any one of the preceding claims, wherein the sole clamp (13) comprises two wings (132), each wing (132) being pivotably mounted to the body (12).

10. Retaining piece (1) according to any one of the preceding claims, wherein the cam (153, 154) is dimensioned so that the return moment (Ma, Mb) exerted on the body (12), and characterized by the product of the intensity of the return force (Frla, Fr1b) multiplied by the distance (Da, Db) between the direction of the return force (Frla, Fr1b) and the axis of rotation (Y122) of the body (12), is, when the at least one sole clamp (13) is moved away from the gliding board (3), identical, to within 20% and preferably to within 10%, to this return moment (Ma, Mb) when the sole clamp (13) is close to the lower face (111) of the chassis (11).

11. Retaining piece (1) according to any one of the preceding claims, wherein the lateral release mechanism comprises an adjusting device configured to allow the setting of a threshold value of a release force that has to be applied to the lateral release mechanism in order to cause the sole clamp (13) to move into a lateral release configuration, the retaining piece also comprising a compensation mechanism configured to exert an additional return force (Fr2) on the body (12), the intensity of the additional return force (Fr2) being dependent on said setting, the pressing force (Fp) being a dependent on the return force (Fr1) exerted by the second elastic means (151) and on the additional return force (Fr2) exerted by the compensation mechanism.

12. Gliding board (3) equipped with at least one retaining piece according to one of the preceding claims.