Abstract
A braking system for a wheeled apparatus and an improved wheeled apparatus, such as a skateboard, are described where the braking system allows for easy, quick and universal mounting onto the deck of a typical board.
Claims
1. A brake system for a wheeled riding apparatus, the riding apparatus having a deck with at least one truck coupled to a bottom of the deck through a plurality of mounting holes in the deck, and at least one wheel mounted to the truck, the brake system comprising: a base structure having a plurality of fastener openings corresponding to at least one of the plurality of mounting holes, the base mountable on a top of the deck to the at least one truck through at least one of the plurality of mounting holes; a brake arm having a center section and a first lateral section with a first brake surface, the center section pivotably coupled to the base structure and the first lateral section extending over a first edge of the deck such that the brake surface is positioned adjacent to at least one wheel: a brake lever pivotally coupled to the base structure and the brake arm; and a force transmitting, component coupled between the brake arm and brake lever, where the force transmitting component is resilient and compressible such that the force transmitting component maintains the brake lever in a disengaged state and application of a force to the brake lever causes the force transmitting component to transfer a portion of the force to the brake arm to move the brake surface towards the at least one wheel until the brake surface engages the at least one wheel.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0034] Each of the following figures diagrammatically illustrates aspects and variation to better understand the invention. Variation of the invention from the aspects shown in the figures is contemplated.
[0035] FIG. 1 is an isometric view of a conventional longboard (100) with the brake system (102) described in this invention.
[0036] FIG. 2 is an isometric view of the brake system (102) above a conventional longboard (100) illustrating how it is attached.
[0037] FIG. 3 is an exploded view of the brake system (102) shown in FIG. 1.
[0038] FIG. 4 is a close up isometric top view of the brake actuator shell (106) of the brake in FIGS. 1, 2, and 3.
[0039] FIG. 5 is a close up isometric: bottom view of the brake actuator shell (106) of the brake (102) shown in FIG. 4.
[0040] FIG. 6 is an isometric top-side w of the braking arm (114) of the brake system (102) shown in FIG. 1.
[0041] FIG. 7 is an isometric bottom-side view of the braking arm (114) of the brake system (102) shown in FIG. 1.
[0042] FIG. 8 is a side view of the longboard (100) and brake (102) shown in Figure
[0043] FIG. 9 is a top view of the longboard (100) and brake (102) shown in FIG. 1.
[0044] FIG. 10 is a front view of the longboard (100) and brake (102) shown in FIG. 1.
[0045] FIG. 11 is a rear view of the longboard (100) and brake (102) shown FIG. 1.
[0046] FIG. 12 is a top view of the brake arm (114) and mounting plate (118) brake assembly (102) shown in FIG. 1 with the actuator shell (106) removed for clarity.
[0047] FIG. 13 is an isometric view of the brake arm (114) and mounting plate (118) brake assembly (102) shown in FIG. 12, with the actuator shell (106) removed for clarity.
[0048] FIG. 14 is a side view cross section from front to back through the longboard (100) and brake (102) shown in FIG. 1, when the brake (102) is in the fully disengaged state.
[0049] FIG. 15 is a close up view of the brake (102) shown in FIG. 1 illustrating the stroke multiplier mechanism.
[0050] FIG. 16 is a side view of the brake (102), with the actuator shell (106) sectioned, to better illustrate the positions of the actuator shell pivot hole (128), the brake arm pivot hole (140), and the cam surface (130) for the force transmission spring.
[0051] FIG. 17 is a table summarizing the details of the 2 stage braking system.
[0052] FIG. 18 is a close up view of the brake area shown in FIG. 14.
[0053] FIG. 19 is a cross-sectional side view of the brake area of the longboard (100) and brake (102) shown in FIG. 1 in which the brake's second stage begins to be engaged for braking with the brake actuator shell (106) pressing directly on the brake arm (114).
[0054] FIG. 20 is a side view of the brake area shown in FIG. 19.
[0055] FIG. 21 is a cross-sectional side view of the brake area of the longboard (100) and brake (102) shown in which the brake's second stage is fully engaged for braking with the brake actuator shell (106) pressing the brake arm (114) engaging the brake surface (116) fully into the wheel (144).
[0056] FIG. 22 is a side view of the brake area shown in FIG. 21.
[0057] FIG. 23 is an isometric view of the board (100) and brake (102) with the board in a full maximum turn and when the brake is not actuated, showing the brake surface (116) clearance with the wheel (144) during a maximum turn state of the board (100).
[0058] FIG. 24 is a close up view of the board (100), brake (102) and wheel (144) shown FIG. 23.
[0059] FIG. 25 is a top view of the board (100) and brake (102) shown in FIG. 23.
[0060] FIG. 26 is a close up isometric view of the brake (102) when in the disengaged position.
[0061] FIG. 27 is an exploded view of the brake system (102) with a pivoting brake pad (162) mechanism that also can be detachable.
[0062] FIG. 28 Shows the initial contact of the pivoting brake pad (162) to the wheel (144).
[0063] FIG. 29 shows the brake pad (162) pivoting into its final contact position with the wheel (144).
[0064] FIG. 30 shows the pivoting brake pad (162) with force concentration bumps or ribs (170).
[0065] FIG. 31 shows the pivoting brake pad (162) detached from the brake system (102), illustrating the force concentration bumps or ribs (170).
[0066] FIG. 32 shows the pivoting brake pad (162) detached from the brake system (102), illustrating replaceable force concentration plugs (174).
[0067] FIG. 33 shows the replaceable force concentration plugs (174) being inserted into mounting holes (176).
[0068] FIG. 34 is the brake system (102) mounted to a skateboard (100), with pivoting brake pads (162) that also have heat sink fins (180).
[0069] FIG. 35 is the pivoting brake pad (162) with the heat sink fins (180).
[0070] FIG. 36 is the pivoting brake pad (162) with the heat sink fins (180), force concentration ribs (182), aluminum or metal rims (184), and high melt temperature rubber tires (186).
[0071] FIG. 37 shows the brake system (102) with the pivoting brake pad (162) attached to the brake arm (114) with a shoulder bolt (166) secured with a cotter pin (188).
[0072] FIG. 38 is a close up view of the pivoting brake pad (162) attached and secured with a shoulder bolt (166) and a cotter pin (188) shown in FIG. 37.
[0073] FIG. 39 is an exploded view of the brake system shown in FIG. 37.
[0074] FIG. 40 is an exploded view of the close up view in FIG. 38.
[0075] FIG. 41 is a view isolating the shoulder bolt (166) and the cotter pin (188).
[0076] FIGS. 42 and 43 show an example of the shoulder bolt (166) and cotter pin (188) shown in FIG. 41.
[0077] FIGS. 44 and 45 show an example an irregular break surface.
DETAILED DESCRIPTION
[0078] The present invention describes a brake system which is foot actuated, is attached to the board with a single attachment, is compatible with existing longboard decks, is compatible with existing longboard wheels, applies brakes to both the left and right wheel, is mounted at or near the centerline of the deck to maintain a balanced foot position on the deck, and includes a duel stage large range adjustable braking stroke and braking force. As will be explained subsequently, these criteria are simultaneously accomplished by unique and novel solutions to the technical challenges.
[0079] In the devices described herein, interference between the brake and wheel when the brake is not engaged is prevented, however, the distance between the brake and wheel when the brake is not engaged is kept to a minimum by using a stroke multiplier in the brake actuator mechanism, thereby creating a low-to-the-deck brake foot actuator. This allows the rider in the present invention to not compromise their stable, balanced foot position. The devices described herein also provide a dual stage braking capability giving the rider a larger range of braking force, with a range of increasing force versus stroke in the first stage and a greater direct force in the second stage.
[0080] The brake system can be added to the board without modification of the board and without switching out any of the board's components, making it conveniently universal, versatile and affordable. The universality also makes it manageable in the work flow and economics of a retail shop, or for a realistic home installation. The brake system also permits optimal rider balance when using the brake, making it simple and safe to use, and usable by novice to advanced users. The brake system also permits maximal turning without inadvertent brake engagement by virtue of some additional unique aspects of the invention. The invention is especially useful for longboards and is also useful for other types of boards.
[0081] In FIG. 1 a conventional longboard (100) is shown with the brake system (102) described in this invention. The longboard deck (142) shown is a flat deck, although the invention is contemplated to be compatible with a drop deck. The brake assembly (102) is affixed to the rear of the board (100) in the location of the rear truck assembly (146) attachment to the deck (142). The style of the longboard (100) shown is that in which the longboard deck (142) is not above the wheels (144)the axles extend laterally beyond the sides of the deck (142). This exposes the top of the wheels (144) for the brake assembly (102) brake arm (114) and braking surface (116). However, it is contemplated by this invention that in cases in which the deck (142) is over the wheel (144), the brake arm (114) can be shaped with the necessary bends to reach the wheel (144) under the deck (142). As can be seen the brake assembly (102) is mounted in the center of the board (100) which affords the rider the ability to press on the brake (102) with his or her foot in the center of the board (100).As will be shown in subsequent figures, the brake (102) is uniquely, easily, safely, reliably and universally mountable onto a standard longboard (100), and easily removable. Also as will be shown, the brake (102) uniquely solves the problem of wheel (144) clearance when turning when the brake (102) is not engaged.
[0082] In FIG. 2, the brake (102) is shown above the longboard (100) with the truck mounting bolts (104) loosened. To assemble the brake (102) to the longboard (100), the truck mounting bolts (104) are loosened but not removed. For convenience, it is not necessary to completely remove the mounting bolts from the longboard (100). The brake (102) can be attached by utilizing a keyhole slot (150) in the base plate (118), and inserting it over the loosened mounting bolts (104), theme-tightening the mounting bolts (104). A close up view of the keyhole slots (150) can be seen in FIG. 12. It should be noted that this mounting method is possible also due to the fact that the keyhole slots (150) match up with the standard bolt-hole pattern used in longboard trucks (144) and decks (142).
[0083] In FIG. 3 an exploded view of the brake system (102) is shown. Typically, the brake assembly (102) is provided pre-assembled, with the actuator shell (106), brake arm (114), force transmission spring (112), return spring (108) and base mounting plate (118) joined together in an assembly with the dowel pins (124) attaching the brake arm (114) and a dowel pin or shoulder bolt (122) attaching the actuator shell (106) to the base plate (118) respectively. Optionally, removable, attachable brake pads may be attached to the ends of the brake arm (114). When attaching to the board, the installer simply loosens the existing truck mounting bolts (104), places the brake assembly (102) over the truck plate (146), and attaches the brake assembly (102) to the truck (146) and deck (142) by re-tightening the original truck mounting bolts (104). The base plate or mounting plate (118) has keyhole slots (150) which make it attachable to a standard truck assembly (146). The brake assembly (102) can be easily attached without mortification to the board (100), deck (142) or truck assembly (146). Any skate board shop installer, enthusiast or typical user can easily perform this attachment, making widespread commercial deployment of the system possible. The assembly process may take less than five minutes, require only a simple wrench and screwdriver, or similar, and can be therefore performed in a skate shop with negligible overhead costs, making it attractive to a retailer to offer the assembly service free of charge without impacting the shop's profit. In addition, the truck (146), deck (142) or wheels (144) do not have to be changed to a proprietary component in order for the brake assembly (102) to be attached, rendering this invention attractive to the typical consumer. Optionally, an alternative brake base plate adaptor can be provided which mounts to the top of the truck (146) and which includes a quick connect feature to attach the rest of the brake assembly (102) with a very simple attachment such as a spring loaded pin. With this option, an end user can easily remove and attach the brake assembly (102) whenever needed.
[0084] FIG. 4 is a close up isometric top view of the actuator shell (102) of the brake in FIG. 3. The actuator shell (106) includes slots (126), typically four slots, through which the screwdriver or hex wrench can be inserted to screw the base plate (118) to the truck (146) and deck (142), thereby attaching the brake assembly (102) to the board (100).
[0085] FIG. 5 is a close up isometric bottom view of the actuator shell (106) of the brake (102) shown in FIG. 3. The bottom of the actuator shell (106) includes a cam (130) where the upper end of the force transmission spring (112) is positioned. The left and right side of bottom side of the actuator shell (106) include a notch or contact surface (132) which contacts the brake arm (114) for deflecting the brake arm (114) downward to the wheels (144). In the rear section of the actuator shell (106), pivot holes (128) are shown which line up with the rear pivot holes on the base plate (118), and through which the actuator shell's pivot pins (122) attach the actuator shell (106) to the base plate (118). The distance of the pivot axes, along with the cam (130) and contact surface (132) serve to multiply the stroke angle displacement of the brake arm (114) as will be explained subsequently.
[0086] FIG. 6 is an isometric top-side view of the braking arm (114) of the brake system (102) shown in FIG. 1. A pocket (134) is provided to position the bottom end of the force transmission spring (112), which is pinched between the actuator shell (106) and brake arm (114). When the actuator shell (106) is depressed downward toward the deck (142), the force transmission spring (112) is compressed, transferring a spring force to the brake arm (114), and thereby pivoting the brake arm (114) downward toward the deck (142) and wheels (144). A mounting feature, such as a mount hole (136) as shown, is included for attachment of a return spring (108) in the rear of the brake arm (114). This return spring (108) is responsible for raising the brake arm (114) and brake surface (116) to their fully up disengaged free state position, which is the position when the brake surface (116) is not depressed to actuate the brake (102). At the lateral ends of the brake arm (114) the brake surfaces (116) can be found, which impinge on the wheel (144) to transmit the slowing and stopping force.
[0087] FIG. 7 is an isometric bottom-side view of the braking arm (114) of the brake system (102) shown in FIG. 1, providing a view of the curved brake surface (116). The anti-binding features such as a rib, rounded surface, lead in feature, groove or rib are not shown for brevity.
[0088] FIGS. 8 through 11 show the longboard (100) and brake (102) shown in FIG. 1, with the brake system (102) in its free state, fully disengaged position. As can be seen in a side view in FIG. 7, there is substantial clearance between the brake surface (116) and the wheel (144) when in the disengaged state. As will be explained in the following description, this clearance is exaggerated which is required to allow turning in order for the brake (102) to not make contact with the wheels (144). And, as will also be explained in the following description, in order for this exaggerated clearance to be compatible with a braking motion when braking is desired, a stroke multiplier mechanism has been utilized so as to not require a large actuation motion from the rider. A large actuation motion may lead to instability during riding.
[0089] As shown in the top view in FIG. 8 the brake arm (110) extends beyond the sides of the deck (142) to the areas above the wheels (144) and forward of the center point of the wheel (144). Typically the brake surfaces (116) engage the wheels (144) in the top forward quadrant of the wheel (144) which optimizes the smoothness of the braking action. As can be seen in FIG. 8, the brake actuator shell (102) is positioned in the midline of the deck (142) to maximize the riders balance when using the brake. In this manner, switching back and forth from a non-braking stance to a braking stance is easy, intuitive, repeatable, centered, and requires minimal leg and foot motion, for example the rider's foot needs to move only minimally so that the heal can engage with the actuator shell (102), and therefore the system does not disturb the rider's balance. Conversely for example, if the rider is required to apply the braking force to the side of the board, the board can be inadvertently turned or the rider could lose his or her balance. The front and rear views in FIGS. 9 and 10 respectively also show the center symmetry of the brake (102) compared to the deck (142).
[0090] FIG. 12 shows a top view of the brake system assembly however with the brake actuator shell (106) removed for the purposes of describing some of the mounting hardware. The brake arm (114) is pivotably attached to the base plate (118) with the use of a pivot pin (124). The brake arm (114) is attached to the base plate (118) also with two return springs (104) which brings the brake arm (114) upward to its resting state whenever the brake surface (116) is not being actuated. The base plate (118) is attached to the deck (142) and truck (146) with four bolts (104) of the exact pattern typical of an existing truck (146) attachment bolt pattern. The bolt holes can be slotted or larger than the bolts (104), or there may be an array of bolts in order to accommodate different truck (146) styles, making the mounting to the board truly universal, and without requiring board modification. The configuration in FIG. 12 shows keyhole slots (150) that have a hole larger than the mounting bolt head, and a slot larger than the mounting bolt shaft, but the slot is smaller than the mounting bolt head. This allows the bolt head to slip through, then slide over the bolt shaft. Assembly with this configuration would entail loosening the mounting bolts (104), placing the brake system (102) over the mounting bolt heads through the hole portion of the keyhole slot (150), sliding the brake system (102) backward to engage the slot portion, then tightening the mounting bolts (104). Complete removal of the mourning bolts (104) is not necessary and in most cases, the standard mounting bolts (104) that hold the truck (146) to the deck (142) should be compatible with this brake system (102) and do not need to be replaced. This exemplifies the ease of assembly and connection to the board (100).
[0091] FIG. 13 is an isometric view of the brake system without the actuator shell (106) shown in FIG. 12. The actuator shell (106) has been removed to show the mechanisms inside. The return spring (108) was previously mentioned and in FIGS. 12, and 13, there are two. One or two can be used to accomplish the same function. In FIGS. 12 and 13, the mounting of these return springs to the brake arm is done with integrated retention features (152) off of the brake arm (114) versus the return spring mounting screws (110) mentioned before. Similarly, there are return spring retention features on the base mounting plate (154). These features make assembly easier and reduce overall cost of manufacturing.
[0092] Clearance is required between the brake surface. (116) and the wheel (144) in order to not compromise the turning capabilities of the trucks (146) and longboard (100). When turning, the longboard deck (142) gets closer to the wheels (144) on the inside part of the turn. Turning also brings the wheels (144) closer to the deck (142). This can be seen in FIGS. 19-21. Because of this, the brake surface (116) must be high above the wheels (144), when not engaged, to allow clearance during the turning maneuver. This large, required, clearance distance is counter to the desired actuation stroke for the brake system (102). The ideal actuation stroke is small so as to allow the rider to keep their foot on the board (100) during operation. If the actuation stroke is large, it may require lifting the operator's foot off of the board (100) during riding which would lead to instability. Riding with both feet on the board (100) is more stable. The invention described in this patent allows for a small enough actuation stroke to allow the operator to leave both feet on the deck (142), resulting in stability, but still provides adequate wheel (144) clearance for turning. This is due to the stroke multiplier mechanism. The stroke multiplier mechanism is comprised of the actuator shell (106) and its pivot axis, the brake arm (114) and its pivot axis, and the cam (130) contact surface of the actuator shell (106) and the force transmission spring (112). Because the pivot hole (128) of the actuator shell (106) is well behind the pivot hole (140) of the brake arm (114), and the actuator shell cam surface (130) contacts the force transmission spring (112) in front of the brake arm pivot hole (140), angular displacement of the brake arm (114) is a multiple of the angular displacement of the actuator shell (106). For a given angular displacement for the actuator shell (106), the brake arm (114) is displaced a larger angle of . This is represented in FIGS. 15 and 16.
[0093] FIG. 17 shows a table that summarizes the dual stage braking feature of the brake system invention. On the left column, there are the different stages of braking, including stage 0 which is at rest, no braking. The furthest right column lists out the associated types of braking for each braking stage. The second, third, and fourth columns describe the different states of the mechanisms for each of the braking stages. At stage 0, the actuator shell (106) is not depressed, the braking surface (116) is at its maximum distance from the wheels (144), the force transmission spring (112) is not compressed, so there is no braking force. This is shown in as a cross-section in FIG. 18. At stage 1, the actuator shell (106) is depressed and the braking surface (116) is contacting the wheels (144) but the actuator shell (106) is not at its maximum actuation state. Instead, it is depressed based on the preference of the rider. The more it is depressed, the more it compresses the force transmission spring (112), and the more braking force is generated. In stage 1, the actuator shell (106) contacts the force transmission spring (112) which contacts the brake arm (114) which drives the brake surface (116) to the wheels (144). The braking force is governed by the compression of the force transmission spring (112) in stage 1 which allows a great deal of braking force adjustability. FIGS. 19 and 20 show the brake system (102) in stage 1. One other characteristic of stage 1 braking is the gap (156) between the actuator shell (106) and the brake arm (114). If there is a gap (156) between the actuator shell (106) and the brake arm (114), and the braking surface (116) is contacting the wheels (144), then the brake system (102) is in stage 1. In stage 2, the actuator shell (106) is fully depressed, the braking surface (116) is contacting the wheels, the force transmission spring (112) is compressed such that the actuator shell (106) contacts the brake arm (114) directly, and the maximum brake force is achieved. In stage 2, there is no gap (156) between the actuator shell (106) and the brake arm (114). FIGS. 21 and 22 show the brake system (102) in stage 2. The braking force adjustability found in stage 1 is beneficial because it allows the rider to decelerate slowly if desired. If a maximum deceleration rate is desired, the rider continues to depress the actuator shell (106) into stage 2 which provides the maximum braking force. It should also be noted that an alternative configuration for the force transmission spring (112) can come in various form factors such as the helical wire form shown or a compliant elastomeric component.
[0094] FIG. 19 is a close up cross sectional view of the brake system (102) in the partially engaged condition, or stage 1. FIG. 20 is a side view of the brake system (102) in the same state, stage 1. The actuator shell (106) is pivoted downward compressing the force transmission spring (112), which is deflecting the brake arm (114) to pivot downward and causing the braking surface (116) part of the brake arm (114) to swing or pivot downward and rearward ultimately to contact the wheels (144). In this braking state, the actuator shell (106) is not directly transmitting force to the brake arm (114), and the braking force is that which is dictated by the compression of the force transmission spring (112). FIG. 20 shows the gap (156) that exists between the actuator shell (106) and the brake arm (114) highlighting that those two components are not contacting and not directly transmitting force.
[0095] FIG. 21 is a close up cross sectional view of the brake system (102) and FIG. 22 is a side view of the brake system (102) however with the actuator shell (106) making direct contact with the brake arm (114), thereby beginning to emit force directly to the brake arm (114) and thus increase the brake force beyond that that is exerted by the force transmission spring (112) to a greater force that is exerted by the rider's weight or pressing force. FIGS. 21 and 22 show the brake system (102) in stage 2 of braking.
[0096] FIG. 23 is an isometric view of the board (100) and brake (102) shown during a turn, and FIG. 24 shows a close up view of the same. As can be seen, during a maximal turn in which the board deck (142) is maximally tilted and the truck (146) is maximally pivoted, which is the basic design principle of turning a board (100), there is still clearance between the brake surface (116) and wheel (144), thus preventing inadvertent engagement of the brake during a turn. It is this embodiment that further separates this invention from the prior art. In order for this invention to achieve this aspect of performance, the clearance of the brake surface (116) with respect to the wheel (144) is exaggerated when the board is unturned, and in order to accommodate this exaggerated clearance a stroke multiplier is preferred such that the rider can reasonably actuate the brake with reasonable amounts of deflection. Otherwise, either (a) the brake would undesirably bind up with the wheel (144) during a turn, and/or (b) the rider would be required to deflect the brake mechanism with unreasonable amounts of deflection and motion causing the rider to lose balance during braking. FIG. 25 is a top view of the board and brake (102) shown in FIGS. 23 and 24, also showing the position of the brake (102) and wheels (144) during a maximal turn, when the brake (102) is not engaged.
[0097] FIG. 26 shows a front-side isometric view of the brake system (102), with the board (100) in an unturned state, and the brake (102) in a fully disengaged position. This view shows clearance between the actuator shell (106) and brake arm (114), and clearance between the actuator shell (106) and deck (142), and clearance between the brake surface (116) and wheel (144). In addition replaceable brake surfaces (148) are shown, with a quick connect feature (138).
[0098] FIG. 27 shows the same brake shown in FIG. 26 with one of the replaceable brake surface (148) detached and the other attached. The replaceable brake surface (148) slides on to the brake arm (114) and attaches with a snap detest feature (138) allowing for easy attachment and detachment. The replaceable brake surfaces (148) may be comprised of a material that doesn't bind when pressed against the wheel (144), yet a softer material than the wheel (144) itself such that the replaceable brake surface (148) wears rather than the wheel (144) wearing as a result of repeated braking over time. The replaceable brake surface (148) can be curved to match the curvature of the wheel (144), and can have features to prevent binding, such as a rounded surface, groove or rib.
[0099] With a non-pivoting brake surface (116), as described earlier with the one piece braking arm (114), a unique position of the wheel (144) relative to the board exists for optimal braking. Because the braking surface (116) is a fixed feature of the braking arm (114), to achieve the maximum contact to the wheel (144), this unique position of the wheel (144) relative to the truck base (146) is required. If it is not in this unique position, a maximum contact of the brake surface (116) to the wheel (144) will not result. It is preferred to maximize the contact area of the brake surface (116) on to the wheel (144). The braking force is distributed over the contact area so if the area is maximized, distribution of the force is spread out over a large area. A small contact area will result in a concentration of the force in a localized spot which may generate a large amount of heat. This heat may melt and damage the skateboard wheels (144). There are several reasons why the wheels (144) may not be in this unique. One reason is that skateboard trucks (146) are designed to he adjustable depending on the style of riding chosen by the rider. This adjustability stiffens the turning capability of the truck (146) but also varies the height of the wheel (144) relative to the truck base (146). This continuum of adjustability leads to a continuum of deck (142) positions relative to the wheel (144). Another reason is that different truck (146) manufacturers may have various designs in which the position of the wheel (144) to the truck base (146) is different. Yet another reason that the position may not be optimal is that the wheel (144) diameters may vary. Skateboard wheels (144) come in various diameters and this variation may cause the position to be suboptimal. A solution to the problem stated above is to add a pivoting feature (160) to the brake arm (114). FIG. 28 shows an exploded view of the brake system (102) with a braking arm (114) that has the pivoting brake pads (162) as separate pieces. If the pivoting brake pads (162) are allowed to pivot about an axis (160) on the brake arm (114), it can allow for different positions relative to the truck base (146). It can also allow for different wheel (144) sizes. As the rider actuates the brake (102), the brake pad(162) automatically adjusts to the position and wheel (144) size by pivoting. FIG. 28 shows the braking arm (114) with pivoting brake pads (162) that pivot about an axis (160), held together with a shoulder bolt (170) and a spring washer (172). Because the pivoting brake pad (162) can move relative to the brake arm (114), clearance is required between the brake pads (160) and the brake arm (114). This clearance may result in an undesirable rattle during riding. This clearance can be taken up or absorbed with a compressible component such as a spring washer (172). The compressible component or spring washer (172) would be assembled in between the brake pad (162) and the brake arm (114) such that it is under compression. This compressed spring washer (172) would result in a light force between the parts that will prevent undesirable rattling during riding but will allow the necessary pivoting. This pivot hinge (160) mechanism also has features to prevent over rotation of the pivoting brake pad (162). The pad (162) should be positioned in a zone that allows it to re-position itself as it makes contact with the wheel (144). If the pad is over rotated, re-positioning may not be possible. These over rotation stopping features (164) keep the pad (162) inside of this zone, allowing it to re-position itself properly during contact with the wheel (144). They consist of hard stops (164) where the pivoting brake pad (162) collides into the brake arm (114) providing limits of rotation.
[0100] FIG. 29 shows the initial contact of the pivoting brake pad (162) to the wheel (144). This illustrates that if the wheel (144) is in a suboptimal position relative to the deck (142) or if the wheel (144) is of a size that is not ideal, the initial contact will also be suboptimal. FIG. 30 shows that with further actuation of the actuator shell (106), the pivoting brake pad (162) automatically conforms to the optimal position allowing for proper and optimal engagement of the pivoting brake pads (162) to the wheels (144).
[0101] The invention herein applies to high performance braking systems and recreational braking systems. The recreational braking systems typically includes maximum brake surface (116) contact which will not damage typical skateboard wheels (144) and will provide adequate braking performance. When high performance braking is required, the same invention can be utilized with an additional feature to the brake pads (162). FIGS. 31 and 32 show an alternative embodiment to the pivoting brake pad (162) previously described that could provide higher performance. Higher braking performance can be defined as the ability to decelerate at higher speeds and/or the ability to decelerate in less distance. It can also be defined as requiring less actuation force. This can be accomplished by increasing the deceleration force. The deceleration force is defined as Fd=N where is the coefficient of friction and N is the braking force applied to the wheel. By adding bumps or ribs (170) to the brake surface (416), the contact area is minimized which concentrates the braking force to those areas versus distributing the force over a larger contact area. These raised elements (170) act as gripping features by minimizing the contact area which concentrates the braking force which increases N which increases the deceleration force. The brake force is distributed over the contact area. Minimizing the contact area will concentrate the braking force because the area in which the brake force is distributed is smaller. However, as stated previously, concentrating the force on a smaller area can also generate high heat Which may melt and damage the skateboard wheels (144). In this embodiment, it may also be necessary to accompany this type of brake pad (162) with high melt temperature rubber skateboard wheels or tires (186). It is believed that this higher braking performance may be advantageous enough to warrant the requirement of specific and non-typical skateboard wheels
[0102] FIGS. 33 and 34 shows a pivoting brake pad (162) with disposable force concentration plugs (174). These inserts (174) have a snapping feature (172) that engage into mating cavities (176) of the brake pad (162). The head of the plug (174) have the raised geometry necessary to concentrate the braking force. As the force concentration plug (174) wears, it is easily replaced by disengaging the remnants from the brake pad (162). The removable approach would allow them to wear out and then be replaced more economically than replacing the whole brake pad (162). These inserts can be made of different materials including steel, aluminum, and various plastic polymers. The variation in materials can provide different types of braking performance and wear resistance.
[0103] FIGS. 35 and 36 show a pivoting brake pad (162) with heat sink fins (180). The heat sink fins (180) are intended to dissipate the heat generated from general braking and/or the heat from the force concentration features (170). Aluminum, because of its thermal conductivity, would be a good brake pad (162) material choice for heat dissipation. The heat sink fins (180) increase the surface area of the pivoting brake pad (162) and in combination with the air flow would allow heat to be dissipated preventing damage to the skateboard wheels (144).
[0104] FIG. 37 shows the underside of the pivoting brake pad (162) with force concentration ribs (170) along with the skateboard with aluminum rims (184) and high melt temperature rubber tires (186). One way to manufacture this high temperature rubber wheel would be to first machine or cast the rim out of aluminum. The next step would be to take the rim and over mold the high temperature rubber (186) on to the rim (184). The standard skateboard wheels (144) have plastic rims with polyurethane wheels. The proposed aluminum rim (184) would have sufficient strength and high melt temperature and would lend it itself to be over molded with the high temperature rubber. It's also conceivable that the tire (186) be molded separately then assembled on to the rim (184).
[0105] Attachment of the pivoting brake pad (162) can be accomplished with a shoulder bolt (166) as described above. To prevent inadvertent unthreading and detachment due to normal vibration during riding, a threadlock can be used. This can be accomplished with a plastic patch such as nylon applied to the thread of the shoulder bolt (166) or an adhesive threadlock placed on the thread during assembly of the brake pad (162). Both are commonly used to prevent screws from inadvertent unthreading during vibration. In both cases, it should be considered that high heat can be a factor during braking so the exact compound used for threadlocking should withstand these high temperatures. An alternative method to secure the shoulder bolt (166) is to use a cotter phi (188) as shown in FIGS. 38 through 41. In these Figures, the shoulder bolt (190) has an extension which a cross-hole (190) is drilled to allow for a cotter pin (188). After the shoulder bolt (166) is assembled to the brake pad (162) and brake arm (114), a cotter pin (188) is placed through the cotter pin hole (190), securing the shoulder bolt (166), preventing inadvertent unthreading. This too is common practice in securing pins and bolts to vibrating assemblies. This method can be advantageous over the plastic or adhesive threadlock because a metal cotter pin (188) along with a metal shoulder bolt (166) are capable of handling the high temperatures during braking. It also allows for easy attachment and detachment of the brake pads (162) if the rider wants to upgrade the pads (162) for high performance ones.
[0106] FIGS. 42 and 43 show the cotter pin (188) locking with shoulder bolt (166) locking mechanism without any other components for clarity. FIG. 42 shows the cotter pin (188) locking to the shoulder bolt (166) while FIG. 43 show the two components in an exploded view.
[0107] FIGS. 44 and 45 show an example of where the brake surface 170 comprises an irregular surface, which can include lines, a V-shape ridge, raised bumps, or any surface to modify the brake surface 170 from being a smooth surface.
[0108] The invention also contemplates a hand brake cable system coupled to the brake actuator pad, for example a push-pull rod mounted between the front bottom of the actuator pad and deck. In this case the length of the mounting plate is extended in the forward direction for connection of the bottom of the rod. Actuation of the handbrake will compress the push rod to deflect the brake actuator pad downward, and releasing of the handbrake will allow the actuator pad to return to the up position. The invention also applies to non-wheeled conveyances, such as a snowboard, in which case the brake shoes dig into the snow when braking.
