DOWNHILL-SLIDING APPARATUS

CROSS-REFERENCE TO RELATED APPLICATION

The present patent application claims priority on United States Provisional Patent Application No. 60/806,566, filed on July 5, 2006.

FIELD OF THE APPLICATION

The present application relates to downhill- sliding sports and, more particularly, to an apparatus for such sports.

BACKGROUND ART

It has been over two decades since snowboarding gained mainstream popularity, and it has been even longer since BMX entered that realm. Today, many forms of downhill-sliding sports or activities are practiced, such as skiing, snowboarding, sledding, skibiking, monoskiing.

Up until today, a few apparatuses claim to combine the carving capabilities of expert snowboarders and the BMX-like feel and steering capabilities. These apparatuses fail to apply the proper technique used in snowboarding to initiate the so-called carve turn. The carve turn involves the ability to initiate g-force turns (e.g., like a roller coaster) with limited sliding, which sliding is usually present with the known BMX-snowboard hybrids.

Advanced snowboarders initiate turns by approaching their two knees together, which allows the board to deflect, enabling optimal edge contact with the snow. As the perimeter of contact between the board edge and the snow is increased enabling to use the full

arc of the board, the rider may lean more toward the slope and turn sharply, i.e., carve.

Accordingly, the knee motion performed by snowboarders is the vital part of initiating a carve turn. The knees and upper body of a snowboarder function as separate entities from the hips downwards. In other words, the upper body plays a passive role and the knees are constantly active. In addition to initiating carve turns, the knees act like absorbers while maintaining complete independence from one another, like a car with independent suspension or a motocross .

Numerous other devices have claimed to imitate the snowboard but have failed, like the monoski or the parabolic ski. The monoski places the skier at the center of one ski, and the parabolic ski tries to emulate the snowboard by having the same sort of sidecut. Both systems do not factor in the importance of the stance of a snowboarder and his/her ability to actually deform the board by moving his/her knees inwards or outwards while initiating a turn, or to get more of a spring-like effect after a turn. The snowboarder ' s pressure is spread out over the entire pressured edge of the board, with one leg being on the back half, and the other leg being on the front half. This gives the ability for the board edge to have excellent contact perimeter with the snow.

The prior art revolves around standing platforms or peg-like devices separated by one or two skis supported by shocks. The standing platforms are neither practical nor safe, as the full motion of the terrain is directly fed back to the rider on the platform, whether it be front or back, like a springboard. These platforms also prohibit the rotational movement found in a peg- like design (motocross) .

Over rough terrain, the lower and upper body- parts of the rider act independently from on another, with the feet and legs resting on a peg that keeps the rider standing during rough terrain. The rear and front wheels act independently from one another, thus giving the rider the ability to use his/her arms to maintain the level of the bike, since the rider is standing at the center of gravity of the bike.

Known sliding equipment does not factor in how a snowboard turn is executed. These designs propose shock absorbers on each end connected to a bike-like frame. Where all these designs differ from a board is in the pressure exerted on the board by a snowboarder when he/she brings his/her knees together in order to create a flex in the board or enable the natural curvature of the board to take place, resulting in a carve turn .

Snowboard, ski or monoski designs have a so- called side cut. The side cut, once deflected by the rider, permits the full contact of the board edge to touch the snow. This is achieved because, at standstill, the board is narrower at its center (i.e., waist) than the front (tip) or back (tail) . Once the board is inclined and deformed, the whole edge of the board is able to optimally contact the snow. It is therefore important for the knees of a snowboarder to be completely active in order to achieve optimal edge contact and allow full board deflection.

Looking closer at a snowboarder ' s side stance, it can be seen that an active triangle is formed from the hips downwards, which triangle the rider controls by absorbing, bending, opening or bringing the knees together. This is an active system area that permits a rider to deform his/her board in a way that allows him/her to not only control the board but to permit him/her to carve. The reason why a carve turn can be

accomplished is attributed to the fact that the rider is taking an active role in deflecting or deforming the board with the knees, and not just counting on gravitational forces to accomplish such.

SUMMARY OF THE APPLICATION

It is therefore an aim of the present invention to provide a downhill- sliding apparatus that addresses issues associated with the prior art.

Therefore, in accordance with the present invention, there is provided a downhill-sliding apparatus comprising: a board having an undersurface adapted to contact the ground during use of the apparatus, and an upper surface opposite the undersurface, and a longitudinal dimension; and a linkage configuration having a pair of legs separately mounted to the upper surface and spaced apart along the longitudinal dimension of the board, and a link assembly- interconnecting the legs so as to allow relative movement of free ends of the legs with respect to one another so as to cause a flexion of the board.

BRIEF DESCRIPTION OF DRAWINGS

Fig. 1 is a schematic view of a downhill- sliding apparatus having a link configuration constructed in accordance with an embodiment of the present invention, with a board being generally flat;

Fig. 2 is a schematic view of the downhill- sliding apparatus of Fig. 1, with the board fully bent;

Fig. 3 is a schematic view of the downhill- sliding apparatus of Fig. 1, with a rear end of the board being bent;

Fig. 4 is a schematic view of the downhill- sliding apparatus of Fig. 1, with the front end of the board being bent;

Fig. 5 is a front perspective view of the downhill-sliding apparatus in a bike configuration in accordance with another embodiment of the present invention; Fig. 6 is a rear perspective view of the apparatus of Fig. 5;

Fig. 7 is a rear elevation view of a relief interface for the downhill-sliding apparatus of Fig. 5;

Fig. 8A is a side elevation view, partly sectioned, of the relief interface for the downhill- sliding apparatus of Fig. 5, in a manual-release configuration;

Fig. 8B is a side elevation view, partly- sectioned, of the relief interface for the downhill- sliding apparatus of Fig. 5, in a automatic-release configuration;

Fig. 9 is a side elevation view of a handlebar system for the downhill-sliding apparatus of Fig. 5;

Fig. 10 is a front elevation view of the handlebar system for the downhill-sliding apparatus of Fig. 5;

Fig. 11 is a sectional view of a lock of the handlebar system for downhill-sliding apparatus of Fig. 5; Fig. 12 is a front sectional view of the handlebar system for the downhill-sliding apparatus of Fig. 5;

Fig. 13 is a side sectional view of the handlebar system for the downhill-sliding apparatus of Fig. 5;

Fig. 14 is a front perspective view of the downhill-sliding apparatus in a bike configuration in accordance with yet another embodiment of the present invention, having a brake system,- Fig. 15 is a rear elevation view of the brake system for the downhill-sliding apparatus of Fig. 14;

Fig. 16 is a side sectional view of the brake system for the downhill-sliding apparatus of Fig. 14;

Fig. 17 is a rear sectional view of the brake system for the downhill-sliding apparatus of Fig. 14; Fig. 18 is a side elevation view of an alternative brake system for the downhill-sliding apparatus of Fig. 14;

Fig. 19 is a side sectional view of the downhill-sliding apparatus in a ski configuration in accordance with yet another embodiment of the present invention,-

Fig. 20 is an enlarged sectional view of a front portion of the downhill-sliding apparatus of Fig. 19; Fig. 21 is an enlarged sectional view of a central portion of the downhill-sliding apparatus of Fig. 19; and

Fig. 22 is a side elevation view of the downhill-sliding apparatus of Fig. 19.

DESCRIPTION OF EMBODIMENTS

Referring now to the drawings, and more particularly to Fig. 1, a downhill-sliding apparatus according to a preferred embodiment is generally shown at 10. The apparatus 10 has a board 12 of the type having an undersurface of suitable material so as to slide on sliding surfaces (e.g., snow-covered slope), and lateral edges on opposites sides of the undersurface to carve into the sliding surfaces. The board 12 has a front end A and a rear end B. When used, the apparatus 10 usually has the front end A leading and the rear end B trailing, but some riding/skiing maneuvers can be performed with the rear end B leading. In the following description and figures, letters "A" and "B" will be affixed to a same reference numeral to indicate whether

a duplicated part is at the front end "A" or the rear end "B" of the apparatus 10.

The apparatus 10 has a linkage configuration 13 secured to the board 12 so as to actively cause bending in the board 12. The linkage configuration 13 of the apparatus 10 has a pair of legs 14, illustrated as a front leg 14A and a rear leg 14B. The legs 14 are rigidly fixed to an upper surface of the board 12.

Link members 16A and 16B are respectively connected at a first end to the front leg 14A and the rear leg 14B, by way of pivot joints 18A and 18B, respectively. Accordingly, the link members 16A and 16B respectively have a rotational degree of freedom illustrated as Al and Bl, respectively. The link members 16A and 16B are pivotally interconnected to one another by pivot joint 20. In a preferred embodiment, the axes of rotation of the pivot joints 18A, 18B and 20 are parallel to one another.

Referring to Fig. 2, it is shown that a downward pressure Pl on the pivot joint 20 will cause the joints 18A and 18B to move toward one another. As the legs 14 are connected to the board 12 (e.g., rigidly or in a swivel configuration) , this results in the board 12 bending, as is clearly visible in Fig. 2. This bending of the board 12 is induced to carve with the apparatus 10, whereby the linkage configuration 13 enables an active control of the board bending.

In order to absorb a portion of the pressure applied to the joint 20, it is contemplated to provide a shock 22 between the joint 20 and the board 12, as illustrated in Fig. 4, or between the link members 16 (or any other suitable member of the linkage configuration 13) and the board 12. The presence of the shock 22 between the joint 20 and the board 12 allows to apply additional pressure at the center of the board 12 to increase flexion. The additional pressure results

from the fact that a portion of the weight of the user is transmitted from the linkage configuration 13 to the board 12 enabling a better camber effect on the board 12 when the joint 20 is moving downwardly. Alternatively, a solid link could be provided between the joint 20 and the board 12 to enhance flexion in the board 12. In such a case, a release mechanism is provided to allow separation of the solid link from the joint 20 if so desired for optimal performance. Alternatively, a solid link could be connected to the linkage configuration 13 and separated from the board 12, to come in contact with the board 12 when pressure is applied on the linkage configuration 13 to enhance flexion of the board. The solid link is not restricted to joint 20 and can be connected to other members of the linkage configuration 13.

Referring to Fig. 3, pressure P2 is applied only to the pivot joint 18B. The linkage configuration 13 therefore causes the rear end B of the board 12 from the leg 14B to bend. Similarly, in Fig. 4, pressure P3 is applied to the pivot joint 18A, so as to cause the front end A to bend from the leg 14A.

Therefore, as seen in Figs. 1 to 4 and as described above, the linkage configuration 13 reproduces the leg movements performed by a rider of a snowboard in using the board to carve. The motion illustrated in Fig. 2 is essentially similar to the rider bringing his/her knees together. The motion depicted in Fig. 3 is equivalent to the rider bringing his/her rear knee forward, and the motion of Fig. 4 is equivalent to the rider bringing his/her front knee rearward.

The apparatus 10 has, in addition to the linkage configuration 13, interfaces for the rider to drive the board 12. Referring to Figs. 5 and 6, one embodiment involves a bike configuration involving the use of a pair of foot pegs 30 positioned at the pivot

joint 20. As will be illustrated hereinafter, the pegs 30 are provided in combination with a seat system and a handlebar system, and the rider pushes on the pegs 30 with his/her feet to bend the board 12, as illustrated in Fig. 2. The pegs 30 allow the rider to be fully supported by the linkage configuration 13, whereby the feet of the user do not interfere with the flexion of the board 12.

Also shown in Figs. 5 and 6 are the legs 14, which each consist of a pair of beam members 32 spaced apart so as to define a clearance 34 therebetween. This combination accommodates an end of the link member 16, which is pivotally supported by pivot shaft 36A.

A pair of connector plates 38 are provided on the link member 16A to accommodate an end of the link member 16B, at the pivot 20. Alternative configurations are also considered to enable the rotational degrees of freedom between the legs 14 and link members 16. For instance, single beam members, as opposed to paired up beams, can be used as long as the structural integrity required from the linkage configuration 13 to support a rider is respected.

Referring to Figs. 5 and 6, a seat system 40 is illustrated. The seat system 40 is provided to support the user of the apparatus 10 in the bike configuration. The seat system 40 has a seat tube 41 that is secured to the link member 16A. It is also considered to position the seat tube 41 on other parts of the apparatus 10. A seat (not shown) is mounted to a seat post 42. The seat post 42 is telescopically related to the seat tube 41, such that a position of the seat is adjustable according to the stance desired by the user of the apparatus 10. The seat tube 41 and seat post 42 preferably form a prismatic joint, such that the seat is always in a central vertical plane of the apparatus 10. It is considered to provide a blade (not

shown) on the seat post 42, which blade is received in a slot of the seat tube 41. Moreover, the blade provides the additional feature of preventing accidental pull out of the seat post 42 from the seat tube 41, while ensuring the alignment of the seat in relation to seat tube 41.

The seat is typically retracted when a chair lift is used. Accordingly, a quick-setting mechanism is considered to facilitate the retraction and subsequent extension of the seat system 40. One contemplated configuration involves holes 43 that cooperate with spring-biased pins (not shown) that lock the seat post 42 to the seat tube 41. Such a mechanism is manually released by the user to adjust the position of the seat post 42 with respect to the seat tube 41. Other quick setting mechanisms are considered as well.

Referring to Fig. 6, a suspension 45 is provided between the link members 16A and 16B. The suspension 45 is pivotally mounted at 46 to the respective link members 16. The suspension 45 is of the type having a damper combined with a spring. In Fig. 6, the damper is a gas damper and has a gas reservoir 47. The pressure in the gas reservoir 47 is controlled to adjust the shock absorption performed by the suspension 47. Other types of suspensions and positions for the suspension on the linkage configuration 13 are considered as well.

Referring to Figs. 5 to 8B, relief interfaces are shown at 50 on the front and rear ends of the apparatus 10. The relief interfaces 50 are provided as an additional rotational degree of freedom between the board and the legs 14, in the event that a substantial impact is exerted on the apparatus 10. The relief interfaces 50 can be in a manual-release configuration (Fig. 8A) , or in an automatic-release configuration (Fig. 8B) . For instance, if the apparatus 10 is used to

perform an aerial maneuver (i.e., jump), the load exerted on the legs 14 and board when landing is substantially high and could potentially damage the apparatus 10 over time, or else require a sturdy construction for the apparatus 10.

The relief interfaces 50 each have a pivot 51 relating a connection plate 52 to the respective leg 14. The connection plate 52 is anchored to the board 12 (Fig. 1) by bolts or like fasteners. A release mechanism 53 is provided on the leg 14 and interacts with a blade 54. The blade 54 is secured to the connection plate 52. A blocking mechanism 55 is provided adjacent to the release mechanism 53A, but is not directly related to the operation of the relief interface 5OA. The blocking mechanism 55 is provided to lock the leg 14A and the link member 16A in a given orientation, for limiting carving of the board to a rear portion thereof. The blocking mechanism 55 illustrates how the apparatus 10 could be built using one piece leg system up to the pivot 20. Alternatively, a similar blocking mechanism could be used for the rear portion of the linkage configuration 13.

The release mechanism 53A has an optional cable system 56, and a spring 57 biasing a latch 58, as best seen in Figs. 7, 8A and 8B. In the automatic- release configuration of the release interface 50 (Fig. 8B), the tip of the latch 58 is rounded and is accommodated in a corresponding groove in the blade 54, so as to lock the rotational degree of freedom between the leg 14 and the board 12 (Fig. 1), and is biased to this position by the spring 57. The tip of the latch 58 and the groove in the blade 54 are shaped, such that an impact of a given force will cause the latch 58 to slide out of engagement with the blade 54, thereby releasing the locked rotational degree of freedom to relieve the connection plate 52 from a full impact. Before the latch

58 slides out of engagement with the blade 54, friction between the tip and the groove will allow restricted pivoting movement of the leg 14 until the latch 58 is fully out of the blade 54. Referring to Fig. 8A, the manual-release configuration of the relief interface 50 is illustrated, and features flat contact surfaces between the tip of the latch 58 and the groove of the blade 54. Accordingly, it is required that the latch 58 be retracted using the cable system 56 to allow the pivoting of the leg 14 with respect to the board 12. The cable system 56 can be used to retract the tip of the latch 58 from the groove of the blade 54, in combination with a brake lever (not shown) as commonly used for bicycles.

Other types of relief/blocking or blocking mechanisms or configurations can be used as well. For instance, a constrained rotational degree of freedom using material deformations (e.g., a rubber bushing, springs) and the like could be used as well. It is also contemplated to use the apparatus 10 with the relief interfaces 50 opened, to allow a pivoting motion of the legs 14 with respect to the board 12. In such a configuration, the free rotational degrees of freedom between the legs 14 and the board 12 allow for a smoother ride with some movement of the linkage configuration 13 to lessen the impact of rough terrain on the user of the apparatus 10 and/or maintain optimal board flatness. The use of the shock 22 between the pivot 20 and the board 12 used in combination with the pivoting movement of the legs 14 is particularly suited for rough terrain.

Referring concurrently to Figs. 5, 6 and 9-13, a handlebar system is illustrated at 60. The handlebar of the handlebar system 60 has been omitted from the figures for simplicity purposes. The handlebar system

60 is provided as an arm interface for the user, and preferably features a suspension system to lessen the impact of rough terrain on the arms of the user of the apparatus 10. The handlebar system 60 is optionally provided with a rotational degree of freedom to allow aerial maneuvers such as a tailspin.

Accordingly, the handlebar system 60 has a mount supporting a stem tube 61. The mount is supported by an upper portion of the leg 14A. The stem tube 61 supports a handlebar (not shown) via a headset 62. The headset 62 is rotationally mounted to the stem tube 61, such that the handlebar is rotatable about the stem tube 61.

A release mechanism 63 is provided on the headset 62 so as to rotate therewith, and cooperates with the stem tube 61. The release mechanism 63 has a cable system 64, a spring 65 and a piston 66 biased by the spring 65. The piston 66 is biased against a locking plate 67 that is integrally fixed to the leg 14. The locking plate 67 features a groove as seen in Figs. 9 and 12, to accommodate the piston 66. When the piston 66 is in the groove of the locking plate 67, the handlebar is square with respect to the board.

In order to use the handlebar system 60 to perform maneuvers involving a rotation of the handlebar, a lever mechanism (e.g., a brake lever) on the handlebar is used to retract the piston 66 from engagement with the groove of the locking plate 67. By doing so, the rotational degree of freedom between the stem tube 61 and the headset 62 is released, allowing rotation of the handlebar with respect to a remainder of the board. It is contemplated to provide the piston 66 with an indexing mechanism such that the piston 66 remains retracted until the lever mechanism is actuated another time. Similarly, an indexing mechanism can be provided for the latch 58 of the relief interfaces 50 as

described previously.or other locking devices that could benefit from the presence of an indexing mechanism.

In an alternative embodiment, the biasing action of the spring 65 ensures that the piston 66 is reinserted into the groove of the locking plate 67 when the piston 66 and groove are in register.

Referring to Fig. 13, it is contemplated to provide a suspension between the stem tube 61 and the mount (i.e., leg 14A of the apparatus 10). As is shown in Fig. 13, the stem tube 61 is accommodated in a cavity of the mount and a spring is provided between the stem tube 61 and the cavity to act as a suspension. The spring biases the stem tube 61 upwardly.

Accordingly, with this suspension, it is considered to use the piston 66 (i.e., the release mechanism 63) in the following manner: the piston 66 is normally out of the groove in the locking plate 67. When downward pressure is applied to the handlebars, the piston 66 enters the groove, thereby locking the handlebars in rotation about the stem tube 61. This configuration allow the handlebar to always remain unlocked or free spinning as long as pressure is not applied to the handlebars. Other blocking mechanisms can be used. Referring to Figs. 14 to 17, a brake system 70 is provided on an alternative embodiment of the apparatus 10. The brake system 70 is positioned between the rear end B of the board 12 (Fig. 1) and the leg 14B. The brake system 70 has a cable system 71 that is related to a brake lever on the handlebar (not shown) . The brake system 70 also has a pinion 72, a rack 73 and fingers 74. Actuation of the brake lever will cause a rotational motion of the pinion 72 through the cable system 71. The rack 73 and the fingers 74 are connected, whereby rotation of the pinion 72 will cause a translation of the rack 73 and fingers 74.

In an embodiment, he fingers 74 are biased outwardly when the rack 73 reaches a given point, , such that the fingers 74 move laterally beyond an edge of the board 12 and downwardly below an undersurface of the board 12 (Fig. 1) to plunge into the snow and therefore induce friction that will slow down the slide of the board 12 (Fig. 1) . The fingers 74 must therefore consist of a resistant material, such as a metal, that will generally maintain its shape through repeated braking.

The fingers 74 can be manually removed and interchanged with other fingers of different proportions in order to vary ends for varying snow conditions requiring more or less penetrating power. Moreover, it is considered to provide the fingers 74 with springs that allow for little rear movement in relation to a forward sliding motion of the apparatus 10 in case the fingers 74 accidentally come into contact with a rock or the like. This allows for the fingers to slightly bend back in order to prevent damage .

As an alternative embodiment, a brake system 70' is illustrated in Fig. 18. The brake system 70' has an arm 75 that is pivotalIy mounted at one end to the link member 16A or 16B, to the foot pegs 30, or to the pivot joint 20 in order to not interfere with board and system deflection (Fig. 5), as illustrated by pivot 76. The arm 75 is biased upwardly by a spring, and features a plunger 77 at its rear end. The fingers 74 are at an end of the plunger 77 and are integrally related to the plunger 77 so as to extend below the surface of the board 12 (Fig. 1) during the braking action. The foot of the user is used to actuate the brake system 70', with downward pressure being applied on the arm 75, via peg 78 mounted to the arm 75. In an embodiment, a pair of pegs 78 a biased toward the pivot 76 by way of spring 79. The biasing system provides for various force

transmission since more or less leverage can be applied on the fly depending on where the user places the pegs 78 since the pegs 78 can slide along arm 75 against the action of the spring 79. The pegs 78 are returned to their initial position when released, by way of the biasing action of the spring 79. It is contemplated to use the arm 75 to activate the rack 73 and fingers 74 of the brake system 70. In such a case, the fingers 74 can move laterally and downwardly, in similar fashion to operation of the brake system 70.

Referring to Figs. 19 to 22, the downhill- sliding apparatus is shown in a ski configuration, wherein the board 12 is a ski. The apparatus 10 serves as an interface between the ski and the binding (not shown) and is used to allow a curvature of the ski under the binding.

A binding plate 80 is mounted on top of the link configuration, which features legs 14A and 14B, link members 16A and 16B and pivots 18A, 18B and 20. A guide 81 (i.e., open or closed-ring type) has a channel 82 that accommodates the pivot 20 to ensure that the movements of the link members 16A and 16B result in a translation motion at the pivot 20 and that the plate 80 stays in alignement with pivot 20 allowing for central location of the plate 80 with respect to a center line of the ski. The guide 81 is connected to the ski and is used in combination with a guide 85 that is part of plate 80 and projects downwardly therefrom to cooperate with the pivot 20. A spring-loaded piston 83 is optionally positioned above the guide 81 to exert downward pressure on the ski. The ski is pivotally mounted to the plate 80 via the joints 18A and 18B, whereby the ski can bend under the binding plate 80. The joints 18A and 18B are movable in translation along the plate 80.

In order to allow the skis to compress or bend even further below the binding plate 80, the link members 16A and 16B are each provided with a translational joint (i.e., in the form of shocks), as is shown by 84. Therefore, the translational joints 84 permit compression/extension of the link members 16A and 16B, thereby allowing further movement of the joints 18 toward one another or further movement of the pivots 18 in the guide 81. Accordingly, when the ski sustains pressure as a result of carving motion initiated by the user, the pressure on the ski will cause a translation motion at the pivot 20, allowing a curvature of the ski 12. The guides 81 and 85 ensure that the binding plate 80 remains centered with respect to the ski. The guides 81 and 85 can be used on the bicycle configuration of Fig . 5 as well .

The spring-loaded piston 83 is used as an alternative to the arms 84 is optionally provided to add additional pressure during a turn and can be manually adjusted to provide further pressure if required. The piston 83 also helps in reducing vibrations when the ski is curved. On the other hand, the translational joints 84 allow for optimal movements of the joints 18 towards one another to follow the ski arc, and it is clearly shown in Fig. 22 that the joints 84 can translate with respect to the binding plate.

It is considered to provide different link assemblies in alternative to the link configuration 13, to provide interrelated movement between the legs 14A and 14B . For instance, the blocking mechanism 55 locks the leg 14A to the link member 16A, thereby forming an integral leg with the rotational degree of freedom about the pivot 18A being blocked. In this configuration, the degrees of freedom are at the pivots 18B and 20. In such a case, there is relative movement between the

pivots 18B and 20, causing flexion in the board 12. This embodiment essentially forms a linkage configuration in which there are three structural members for two joints. Various other linkage configurations are contemplated to aid the board 12 in deflecting.