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HYDRAULICALLY ACTUATED DAMPING ADJUSTMENT / LOCKOUT

FIELD OF THE INVENTION

[0001] The present invention relates to suspension mechanisms and, more particularly, relates to systems and methods of adjusting a suspension system.

CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims the benefit of U.S. provisional patent application no. 61/049,425 entitled "Hydraulically actuated remote damping adjustment/lockout" and filed on April 30 ^th , 2008, which is hereby incorporated by reference herein.

BACKGROUND OF THE INVENTION

[0003] Conventional bicycle forks connect a front wheel of a bicycle to a bicycle frame so that a rider can rotate or turn the bicycle fork and therefore, the front wheel axially with respect to the frame to steer the bicycle. The bicycle fork typically includes a fork steerer (or steering) tube that is easily rotated by handlebars. The steerer tube is coupled to a fork crown that extends across the top of the bicycle wheel. Two blades extend from opposing ends of the fork crown on opposite sides of the wheel to securely attach the crown to opposite sides of an axle of the front bicycle wheel. [0004] Telescoping bicycle forks are not only used to steer bicycles, but they are also used to absorb various loads that are experienced by a front wheel of the bicycles. In rough terrain, however, these telescoping bicycle forks often rebound too rapidly after hitting a large bump. Some bicycle riders have also found that traditional telescoping bicycle forks compress too rapidly upon hitting small bumps. Therefore, manufacturers of bicycle forks have developed damping apparatuses that have damping mechanisms for controlling the relative movement between the telescoping members. [0005] Conventional remote actuation damping apparatuses utilize a cable or electrical system to facilitate damping adjustment. However, cables stretch over time and require periodic adjustment to maintain their damping adjustment setting. It would therefore be advantageous to provide a damping system that maintains, or at least substantially maintains, the damping adjustment setting. It would additionally be advantageous if such a system could operate with minimal, if any, adjustment by a user over a substantial

3 period of time. Further, it would be beneficial if such a system could be provided at a relatively lower cost.

BRIEF SUMMARY OF THE INVENTION

[0006] In at least some embodiments, the present invention relates to a hydraulically actuated suspension system, the system including a remote actuator assembly having (i) an actuator body; (ii) an actuator piston, the actuator piston positioned within the actuator body; and (iii) an actuator, positioned within the actuator body and coupled at least indirectly with the actuator piston. The system further includes a suspension fork assembly having (i) a fork housing; (ii) a slave piston assembly with a slave piston, the slave piston assembly being positioned within the fork housing, where actuation of the actuator causes the actuator piston to move from a first position to a second position resulting in movement of working fluid from within the actuator body into the fork housing, and wherein the movement of the working fluid in the fork housing causes the slave piston to translate from a first position to a second position resulting in an adjustment of the suspension system.

[0007] In other embodiments, the present invention relates to a remote actuator assembly for use in a suspension system, the remote actuator assembly including an actuator body, an actuator assembly at least partially disposed within the actuator body, and an actuator piston assembly having an actuator piston. Where the actuator piston assembly is disposed within the actuator body and coupled to the actuator, and actuation of the actuator assembly causes the actuator piston to move from a first position to a second position resulting in an adjustment of the suspension system.

[0008] In yet some other embodiments, the present invention relates to a suspension fork for use in a suspension system, the suspension fork including a fork housing, a slave piston assembly substantially disposed within the fork housing, and a compression piston assembly disposed within the fork housing and coupled at least indirectly with the slave piston assembly. Where the movement of working fluid in the suspension fork causes the slave piston assembly to translate from a first position to a second position resulting in an adjustment of the suspension system.

[0009] In yet still some other embodiments, the present invention relates to a method of using a hydraulically actuated suspension system, the method includes providing a remote actuator assembly having (i) an actuator body; (ii) an actuator piston assembly with an

4 actuator piston, the actuator piston assembly positioned within the actuator body, and (iii) an actuator assembly positioned within the actuator body and coupled at least indirectly with the actuator piston assembly. The method further includes providing a suspension fork assembly having a fork housing and a slave piston assembly with a slave piston, the slave piston assembly positioned within the fork housing. Where the actuator assembly is actuated causing the actuator piston to move from a first position to a second position resulting in movement of working fluid from within the actuator body into the suspension fork, and where the movement of the working fluid in the suspension fork causes the slave piston to translate from a first position to a second position resulting in an adjustment of the suspension system.

[0010] In still additional other embodiments, the present invention relates to a hydraulically actuated damping assembly that includes a slave piston assembly having a slave piston, wherein translation of the slave piston provides a damping adjustment and/or lock-out.

[0011] Other embodiments, aspects, features, objectives and advantages of the present invention will be understood and appreciated upon a full reading of the detailed description and the claims that follow.

BRIEF DESCRIPTION OF THE DRAWINGS

[0012] Features of the present invention which are believed to be novel are set forth with particularity in the appended claims. Embodiments of the invention are disclosed with reference to the accompanying drawings and are for illustrative purposes only. The invention is not limited in its application to the details of construction or the arrangement of the components illustrated in the drawings. Rather, the invention is capable of other embodiments or of being practiced or carried out in other various ways. The drawings illustrate a best mode presently contemplated for carrying out the invention. Like reference numerals are used to indicate like components. In the drawings: [0013] FIGS. IA, IB, 1C and ID illustrate front, side, front cross-sectional and front views, respectively, of a suspension system having a suspension fork assembly in operational association with a handlebar actuator assembly employed in conjunction with, or as part of a bicycle, in accordance with at least some embodiments of the present invention.

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[0014] FIGS. 2A-2C illustrate, in cut-away, first, second and third cross-sectional views, respectively, of the suspension fork assembly of FIG. IA- 1C in greater detail, in accordance with at least some embodiments of the present invention. [0015] FIG. 3A-3C illustrate a turret assembly for use in conjunction with the suspension fork assembly of FIGS. 2A-2C, with FIG. 3 A specifically illustrating a top view of the turret assembly, and FIGS. 3B and 3C illustrating respective cross-sectional views along lines B-B and C-C of FIG. 3 A, in accordance with at least some embodiments of the present invention;

[0016] FIGS. 4A-4J illustrate a first embodiment of the handlebar actuator assembly of FIGS. 1A-1C, with FIG 4B illustrating an exploded view of FIG. 4A, and FIGS. 4C-4J illustrating the steps of operation of the handlebar actuator assembly, in accordance with at least some embodiments of the present invention;

[0017] FIG. 5 illustrates a second embodiment of the handlebar actuator assembly of FIGS. 1A-1C, in accordance with at least some embodiments of the present invention; [0018] FIG. 6 illustrates a third embodiment of the handlebar actuator assembly of FIGS. IA- 1C, in accordance with at least some embodiments of the present invention; [0019] FIG. 7A and 7B illustrate a fourth embodiment of the handlebar actuator assembly of FIGS. 1 A-IC, with FIG. 7B illustrating an enlarged cross-sectional view of a portion of FIG. 7 A, in accordance with at least some embodiments of the present invention; and [0020] FIGS. 8A-8E illustrates a fifth embodiment of the handlebar actuator assembly of FIGS. IA- 1C, in accordance with at least some embodiments of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0021] Referring to FIGS. IA, IB, 1C and ID, a suspension system 100 for mounting in a bicycle 110 is illustrated, in accordance with at least some embodiments of the present invention. Notwithstanding the fact that the suspension system 100 of the present embodiment is described for use in the bicycle 110, it is contemplated that at least some other embodiments employ the suspension system in other types of vehicles, and preferably vehicles having handlebars, such as a motorcycle and moped. As shown, the suspension system 100 includes a suspension fork assembly 102 and a handlebar actuator assembly 103 (shown in FIGS. 1 A-IC). As described with regard to FIGS. 1 A-ID, as well as FIGS. 2A-8E below, a suspension fork assembly 102, is also referred to herein as

6 a suspension fork, and the handlebar actuator assembly 103 is also referred to herein as a handlebar actuator or a remote actuator.

[0022] In at least one embodiment, the suspension fork 102 includes a steerer (or steering) tube 104 connected at one end to a crown 106, which in turn is connected to two parallel spaced apart fork legs 108. The other end (e.g., the end opposite the crown end) of the steerer tube 104 is connected to the handlebars 124 (FIG. ID) of the bicycle 110. Each of the fork legs 108 further includes an upper leg portion 112, an upper end of which is connected to the crown 106 and a lower end of which is slidingly connected at a flange portion 114 to a lower leg portion 116. The flange portion 114 is connected to a fork arch 117. The upper end of the upper leg portion 112 (e.g., adjacent the crown 106) is also connected to the handlebar actuator 103, the handlebar actuator 103 is employed for damping adjustment, as described herein. Further, the lower end of the lower leg portion 116 forms a dropout 120 having an axle catching portion 122 for receiving an axle of a wheel 126 of the bicycle 110. Although not shown, additional components can be provided as part of the suspension system. Further, additional components may be shown but are not described in detail as their application would be apparent to a person skilled in the art.

[0023] Turning now to FIGS. 2A-2C, first, second and third cross-sectional views, respectively, are shown in cutaway, of the fork legs 108 of the suspension fork 102, in accordance with at least some embodiments of the present invention. The suspension fork 102 of FIG. 2 A includes an exemplary stanchion damping assembly 200. The stanchion damping assembly 200, in turn, includes a slave piston assembly 201 and a compression piston assembly 259 in operational association therewith, via a coupling mechanism 203. When assembled, the stanchion damping assembly 200 is positioned substantially within a hollow stanchion tube 208, which can be included as part of a fork housing. The hollow stanchion tube 208 can make up a portion of the upper leg portion 112 (see FIG. IA) of the suspension fork 102.

[0024] In at least one embodiment, the slave piston assembly 201 includes a slave piston 210 is positioned within a slave bore 214 of a sleeve member 212. More particularly, the slave piston 210 has a receive end 209 and a transfer end 211, wherein the receive end 209 defines at least a portion of a slave chamber 216. An annular leak-proof sealing mechanism(s) 218 (e.g., a rubber O-ring) positioned between an outer surface of the slave piston 210 and an inner surface of the slave bore 214 provides a seal for the slave

7 chamber 216. The slave piston assembly 201 further includes a top cap member 220 that is secured to the upper portion of the sleeve member 212 to further bound the slave chamber 216. In at least one embodiment, the top cap member 220 is secured to the sleeve member 212 using a threaded engagement, although the securing can be accomplished in another manner, such as welding or press-fit. [0025] The coupling mechanism 203 is secured to the bottom portion of the sleeve member 212. In at least one embodiment, the coupling mechanism 203 includes a preload spring 204, a cartridge tube 205, a hollow tube housing 206, and a pushrod 242. The transfer end 211 of the slave piston 210 extends into the tube housing 206, wherein the tube housing 206 is secured to the sleeve member 212 by mating threads at securing point 219, although the securing can accomplished in another manner, for example, by welding or press-fit. The pushrod 242 and the preload spring 204 are abuttingly positioned within the tube housing 206, such that transfer end 211 of the slave piston 210 abuts the pushrod 242, which in turn communicates a spring force to the valve piston 241. [0026] With regard to valve piston 241, the valve piston 241 includes an actuating end 228 and a valve end 229, and is positioned with the valve end 229 substantially within an annular support sleeve 232, and the actuating end 228 substantially inside the tube housing 206. A compression piston 262 is secured to the support sleeve 232 opposite the tube housing 206. The compression piston 262 includes a top end 215 that is positioned substantially inside the support sleeve 232 and a bottom end 233 situated opposite the top end 215 and substantially outside the support sleeve 232. A relief chamber 237 situated inside the cartridge tube 205, is substantially bounded on the outside by the cartridge tube 205 and on the inside by the compression piston 262, support sleeve 232 and tube housing 206. The cartridge tube 205 extends from the bottom portion of the sleeve member 212 into the lower leg portion 116 (see FIG. IA). As shown, the top end 215 of compression piston 262 is situated inside the tube housing 206. The positioning of the compression piston 262 within the cartridge tube 205, along with a sealing mechanism 266, provides a separation between a damping chamber 240 and the relief chamber 237. The compression piston 262 includes one or more communication passages 238 extending therethrough, the communication passages 238 leading to a communication passage opening 207. Damping fluid is communicated from the damping chamber 240 to the relief chamber 237 via the communication passages 238. In addition, a flow chamber 236 is substantially defined by the top end 215, the valve end 229, and the support sleeve 232,

8 wherein damping fluid passes through the flow chamber 236 when the valve end 229 is not pressed against the communication passage opening 207. In addition, the support sleeve 232 includes one or more openings 239 that allow damping fluid to pass between the flow chamber 236 and the relief chamber 237. The relief chamber 237 is positioned to at least temporarily store damping fluid passed from the damping chamber 240 through the flow chamber 236.

[0027] In a static position, the preload spring 204 sufficiently presses the valve end 229 of the valve piston 241 against the opening 207, such that damping fluid is at least one of limited and substantially prevented from passing from the communication passages 238 into the flow chamber 236. As the lower leg portion 116 (see FIG. IA) is raised towards the upper leg portion 112, damping fluid situated in the cartridge tube 205 is compressed, thereby increasing the fluid pressure in the damping chamber 240. At such point when the fluid pressure is high enough to overcome the preload spring 204 and thereby move the valve end 229 off the opening 207, damping fluid flows into the flow chamber 236 and subsequently into the relief chamber 237.

[0028] A turret assembly 244 is provided that communicates hydraulic pressure remotely from the handlebar actuator 103 to the suspension fork 102. More particularly, to the slave chamber 216 of the slave piston assembly 201. The turret assembly 244 is rotatably secured to and freely rotatable with the aforementioned top cap member 220 by a connector such as a snap ring 250. More particularly, the turret assembly 244 includes a turret 246 retained circumferentially in the top cap member 220 by the snap ring 250. A longitudinal passage 252 formed within the turret 246 communicates working fluid from the handlebar actuator 103 to the slave piston chamber 216 to lock-out (discussed below), dampen or otherwise modify the damping characteristics of the suspension fork 102, this more generally provides a lock-out, damping or modification of the damping characteristics of the suspension system 100. Specifically, by movement of the working fluid, the preload tension of the preload spring 204 can be adjusted to achieve a desired level of lock-out or damping of the suspension system. In addition, the tension of the preload spring 204 (and hence, the level of fluid flow resistance) can also be adjusted to accommodate a variety of rider weights. Additional details about the turret assembly 244 are provided with reference to FIGS. 3A-3C, as discussed below. Typically, damping as used herein refers to slowing translation in the compression direction of the suspension

9 fork 102, while lock-out refers to disabling the suspension mechanism to render the suspension system substantially rigid.

[0029] Further, a variety of sealing mechanisms can be provided within the suspension fork 102. For example, the sealing mechanism 248 for creating a leak-proof seal, can be provided between the turret 246 and the top cap member 220. Further, an annular sealing mechanism 222 can be provided between an outer surface of the sleeve member 212 and an inner surface of the cartridge tube 205. A sleeve sealing mechanism 224 provides a seal between the outer surface of the sleeve member 212 and the inner surface of the top cap member 220, while a similar top cap sealing mechanism 226 provides a seal between an outer surface of the top cap member 220 and an inner surface of the stanchion tube 208. In addition, one or more sealing mechanisms 266 can be provided between the damping chamber 240 and the relief chamber 237. Further, an annular sealing mechanism 234 positioned between an outer diameter of the valve end 229 and an inner surface of the support sleeve 232 creates a leak-proof sealing surface. As discussed above, the sealing mechanism can include such elements as a rubber o-ring, although other types of sealing structures can be employed in other embodiments.

[0030] In accordance with at least some embodiments, to assemble at least a portion of the suspension fork 102, the valve piston 241 is placed at least partially into the tube housing bottom portion 243 and the support sleeve 232 is secured to the tube housing 206 at the securing point 247. In at least some embodiments, the securing point 247 includes a threaded mating connection between the support sleeve 232 and the tube housing 206. The preloaded spring 204 is then inserted into the tube housing upper portion 245 such that a lower end portion of the preload spring 204 is in contact the actuating end 228 of the valve piston 241, while an upper end of the preload spring 204 is in contact with a lower portion of a pushrod 242 that is installed in the tube housing 206 on top of the preload spring 204. The slave piston assembly 201 is then secured at the tube housing upper portion 245 such that the slave piston 210 is at least partially situated within the tube housing 206 and in operational association with the upper portion of the pushrod 242. The cartridge tube 205 is then secured to the sleeve member bottom portion 251, and the top cap member 220 is secured to the sleeve member. The stanchion damping assembly 200 and a portion of the top cap member 220 are inserted into the stanchion tube 208 and then removably secured thereto at securing point 253. The turret assembly

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244 is then secured in place at least partially in the top cap member 220 and over the stanchion damping assembly 200, thereby completing the slave piston chamber 216. [0031] In operation, hydraulic fluid from the handlebar actuator 103 (see FIGS. IA- 1C), discussed further below, enters the slave piston assembly 201 via the turret assembly 244. Specifically, hydraulic fluid enters the slave piston chamber 216 resulting in translation of that piston downwardly in the direction of the compression piston 262. By virtue of piston translation, the pushrod 242 exerts a force on the preloaded spring 204, which in turn preloads the valve piston 241 against the opening 207. As a result, the damping fluid in the damping chamber 240 must reach a specific pressure to overcome the force of the valve piston 241 before the fluid can flow into the flow chamber 236 and relief chamber 237. In other words, damping is not provided until an impact provides enough pressure to overcome the preloaded spring 204.

[0032] Turning now to FIG. 2B, a cross-sectional view is shown in cut-away, of the suspension fork 102' of FIG. 1C, in accordance with at least some other embodiments of the present invention. As shown, the suspension fork 102' includes a stanchion damping assembly 200'. The stanchion damping assembly 200' in turn, includes a slave piston assembly 201'. The slave piston assembly 201' is provided with a slave piston 210' integrally formed with a pushrod 242' and a valve piston 241', and positioned within a tube housing 206'. Notwithstanding the fact that the slave piston 210', the pushrod 242' and the valve piston 241' are integrally formed in the present embodiment, it is understood that in other embodiments, these components can be separate components that can be connected or otherwise positioned together in operational association. The stanchion damping assembly 200' is positioned substantially within a hollow stanchion tube 208', which can be included as part of a fork housing. A top cap member 220' is threadingly engaged with a threaded upper inner portion of the stanchion tube 208' at securing point 253' to secure the stanchion damping assembly 200' inside the stanchion tube 208'. The tube housing 206' is threadingly engaged with the top cap member 220' at securing point 258'. A slave chamber 216' is formed by the tube housing 206', the slave piston 210' and the top cap member 220'.

[0033] The suspension fork 102' is coupled to the handlebar actuator 103 (see FIG. IA), at least in part, by the top cap member 220'. In addition, a hydraulic fitting 260' can be threadingly engaged with the top cap member 220' to further facilitate the coupling. The hydraulic fitting 260' and the top cap member 220' include passages 261', 263',

11 respectively therethrough for the transfer of fluid from the handlebar actuator 103 to the slave chamber 216'. In at least some embodiments, a sealant is applied to the threaded tube housing upper portion 245' prior to engaging the top cap member 220' for holding pressure created by the remote actuator 103. Various sealing mechanisms, such as seals 226' and 218' can be provided between the top cap member 220' and the stanchion tube 208', and the slave piston 210' and the tube housing 206', respectively. Additional sealing surfaces and sealing mechanisms can be provided in other embodiments as may be deemed necessary to provide leak-proof seals for the proper operation of the suspension system.

[0034] The stanchion damping assembly 200' further includes a compression piston assembly 259' having a compression piston 262'. The compression piston 262' includes a top end 215' and a bottom end 233', wherein the top end 215' is engaged (e.g., threadingly engaged) with and situated therein, the tube housing 206', as shown in FIG. 2B. A communication passage 238' extends from the top end 215' to the bottom end 233' of the compression piston 262', through which damping fluid enters the tube housing 206' from a damping chamber 240'. A damping chamber 240' is situated inside the stanchion tube 208' and adjacent the bottom end 233' of the compression piston 262'. A communication passage opening 207' of the communication passage 238' is substantially funnel shaped for complementarily receiving therein a tapered needle valve portion 257' of the valve piston 241'. In other embodiments, other shapes and configurations for the communication passage 238' and needle valve portion 257' are contemplated and considered within the scope of the invention. A sealing mechanism 266' is provided between the inner surface of the stanchion tube 208' and an outer diameter of the compression piston 262' for creating a leak-proof surface. An additional sealing mechanism 268' can be provided between the surface of the tube housing 206' and the valve piston 241'.

[0035] A flow chamber 236' is formed by the space substantially bounded by the tube housing 206', the needle valve portion 257' and the opening 207'. The flow chamber 236' can pass damping fluid between the damping chamber 240' and a relief chamber 237', wherein the relief chamber 237' is bounded by the stanchion tube 208', the top cap member 220', the tube housing 206' and the compression piston 262'. In addition, the flow chamber 236' includes a return spring 270' that is in contact with the valve piston 241' and the compression piston 262'. The return spring 270' provides a stabilizing back-pressure

12 on the valve piston 241' to hold the needle valve portion 257' in an unseated position when the force induced by the remote actuator 103 is insufficient to overcome the spring force.

[0036] In operation, as the remote actuator 103 (See FIG. IA) is applied, fluid enters the slave chamber 216' causing the slave piston 210', pushrod 242', and the valve piston 241' to translate, against the bias of the return spring 270', towards the compression piston 262', such that the cross-sectional area of the communication passage 238' is reduced about the opening 207', thereby restricting the flow rate of damping fluid into chambers 236' and 237'. When the lower leg portion 116 is translated upwards toward the upper leg portion 112, the damping chamber 240' is compressed and therefore damping fluid is pushed through the communication passage 238', past the opening 207', and into chambers 236' and 237'. The rate of fluid transfer from the damping chamber 240' to the chambers 236' and 237' translates into the amount of damping provided. Thus, the reduction in the area about the opening 207' results in an increase of the damping level of the fork. In contrast, reversing the actuation of the remote actuator 103 causes a rising of the needle valve portion 257' out of the opening 207' (increasing the area about the opening 207'), thereby reducing the damping level. Further, in contrast to preloading a spring as in the embodiment of FIG. 2A in which a pressure force overcomes the return force of the spring, in the present embodiment changing the area of the communication passage opening 207' causes a change in the damping rate of the suspension fork 102'. [0037] Turning now to FIG. 2C, a cross-sectional view of a third embodiment of the suspension fork 102" including the stanchion damping assembly 200", is shown in cutaway, in accordance with at least some embodiments of the present invention. The suspension fork 102" is similar in construction, design and operation to the embodiment of FIG. 2B, with the exception that the present embodiment employs a preloaded circular spring plate (also known as shim) 278" in association with a compression piston assembly 259", to facilitate flow resistance of the damping fluid. The stanchion damping assembly 200" is positioned substantially within a hollow stanchion tube 208", which can be included as part of a fork housing. The stanchion damping assembly 200" includes a tube housing 206", the compression piston assembly 259", and a slave piston assembly 201". The slave piston assembly 201" having a slave piston 210" integrally formed with a pushrod 242" and a valve piston 241". The slave piston 210" and the pushrod 242" are positioned within the tube housing 206", wherein the tube housing 206" includes a

13 threaded tube housing upper portion 245" to which a sealant has been applied thereto prior to securing to a top cap member 220" at securing point 258". [0038] The stanchion damping assembly 200" further includes a support sleeve 232" secured to a tube housing bottom portion 243". The compression piston assembly 259" includes a compression piston 262" that is secured to the support sleeve 232" opposite the tube housing bottom portion 243". A chamber 236" is substantially bounded by the valve piston 241", the support sleeve 232", and the compression piston 262". In addition, a relief chamber 237" is substantially bounded by the stanchion tube 208", the tube housing 206" and the support sleeve 232". The relief chamber 237" is capable of communicating with the flow chamber 236" by way of a path 276" situated through the support sleeve 232". Further, the compression piston 262" includes a communication passage 238" having a communication passage opening 207". The communication passage 238" is capable of communicating working fluid between a damping chamber 240", situated below the compression piston 262" and the flow chamber 236".

[0039] The aforementioned pre-loaded circular spring plate 278" is secured to the valve piston 241" by a retainer 280 and is situated adjacent to the communication passage opening 207". In at least some embodiments, the spring plate 278" has a thickness and shape that is capable of at least partially closing off the communication passage opening 207" to limit the flow of fluid from the damping chamber 240" into the flow chamber 236" situated above the communication passage opening 207". As shown, the circular spring plate 278" comprises a substantially flat circular metal plate having a thickness and shape that allows a pre-selected level of resistance to bending under the influence of fluid pressure. Additionally, although only one spring plate 278" is shown in FIG. 2C, it should be understood that in alternate embodiments, the spring plate 278" can consist of multiple flexible members formed from one or more of various materials in a variety of shapes and sizes.

[0040] Similar to the embodiment shown in FIG. 2B, the top cap member 220" is threadingly engaged with the threaded upper portion of the stanchion tube 208" (at securing point 253") to secure the stanchion damping assembly 200" inside the stanchion tube 208". Li addition, the top cap member 220", along with a hydraulic fitting 260", serve to couple the remote actuator assembly 103 (see FIG. IA) to the suspension fork 102". The hydraulic fitting 260" and the top cap member 220" include passages 261", 263" respectively therethrough, for the transfer of working fluid from the remote actuator

14 assembly 103 to the slave chamber 216" of the stanchion damping assembly 200" (more particularly the slave piston 210"). Additionally, a turret assembly (not shown), alone or in combination with the hydraulic fitting 260", can be engaged to the top cap member 220" for coupling the remote actuator assembly 103 to the suspension fork 102". Various sealing mechanisms and hydraulic fittings as discussed above can also be provided. [0041] Upon application of the remote actuator 103, hydraulic fluid from the handlebar actuator 103 enters the slave chamber 216" resulting in translation of the slave piston 210". Translation of the slave piston 210" translates the valve piston 241" downwards towards the compression piston 262", thereby depressing the spring plate 278" at about the mating region of the two portions of the spring plate 278". By virtue of depressing the spring plate 278", the spring plate 278" is pre-loaded against the compression piston 262". Thus, the more the spring plate 278" is deflected, the higher the force it has, such that a higher pressure is required to pass through the circumferentially closed area of the mating edges of the spring plate 278". In some ways, actuation of the spring plate 278" is similar to the actuation of the damping assembly 200 of FIG. 2A, in that a certain pressure is needed to initiate flow of the damping fluid. This is in contrast to the embodiment of the valve piston having a needle valve portion, in which the damping fluid is continuously flowing (except during lock-out) depending upon the area of the communication passage opening.

[0042] Thus, any of the embodiments of FIGS. 2A-2C can be employed depending upon the application and the type of bicycle (or other vehicle) employing the suspension system. Notwithstanding the fact that a particular structure and arrangement of the various components have been described, it is contemplated that various refinements to features above are considered within the scope of the invention. For example, one or more of the slave piston, push-rod and/or valve piston can be integrally formed, or alternatively, as separate components connected in operational association. Further, despite a specific shape, geometry and configuration of the valve piston 241' and the spring plate 278" being described, other shapes, geometries and configurations as may be deemed necessary for the proper operation of the suspension system, are contemplated in other embodiments.

[0043] Referring now to FIGS. 3A-3C, a turret assembly 300 is shown in accordance with at least some embodiments of the present invention. Specifically, FIG. 3 A illustrates a top view of the turret assembly 300, while FTGS. 3B and 3C illustrate cross-sectional

15 views along lines B-B and C-C of FIG. 3A, respectively. Typically, the turret assembly 300 is employed in conjunction with the handlebar actuator 103 (See. FIG. IA- 1C) and an exemplary suspension fork 102 such as shown in FIGS. 2A-2C, and serves as an interface therebetween to facilitate damping adjustment of the suspension system 100. For instructional purposes, the turret assembly 300 is described below as being used in conjunction with the suspension fork 102 of FIG. 2 A.

[0044] As shown, the turret assembly 300 includes a turret body 302 having a brake hose sub-assembly 304, which is connected with a turret bore 306 formed in the top cap upper portion 307 of the top cap member 308. The top cap member 308 is connected to sleeve member 212, inside which the slave piston 210 is inserted. Typically, the turret assembly 300 is assembled by assembling a turret seal 310 in a turret gland 312. Thereafter, a bleed screw 315 is screwed onto the turret body 302 for creating a temporary opening in the otherwise closed working fluid path 313. The turret body 302 is then inserted into the turret bore 306 and an internal retaining ring 314 is fitted into retaining groove 316 formed in the turret bore 306 to secure the turret body 302 therein. Finally, the brake hose sub-assembly 304 is threadingly engaged into the turret body 302. [0045] Typically, the brake hose sub-assembly 304 includes a crimp fitting 318, a brake hose 322 and a compression nut 320, each of which are arranged in operational association such that the brake hose 322 (also known as hydraulic hose) is sealed to the crimp fitting 318 to form a hydraulic inlet 326. Hydraulic fluid is conveyed through the hydraulic inlet 326 for actuation of the stanchion damping assembly 200. Various seal mechanisms, such as a seals 332, can be provided for creating a leak-proof sealing surface. Thus, the design of the turret assembly 300 allows full rotation about the top cap member 308. In addition, the turret assembly 300 provides the ease of the bleed screw 315 being integrated into the turret body 302.

[0046] Referring now to FIGS. 4A and 4B, a first embodiment of a handlebar actuator 400 is shown, (previously described as handlebar actuator 103 in FIGS. IA- 1C) in accordance with at least some embodiments of the present invention. Specifically, FIG. 4A shows a cross-sectional view of the handlebar actuator 400, while FIG. 4B shows an exploded view thereof. The handlebar actuator 400 is typically employed for facilitating damping adjustment and/or lock-out of the suspension system 100 (see FIG. IA- 1C) in the suspension fork 102 via the turret assembly 300 (see FIGS. 3A-3C). As shown, the handlebar actuator 400 includes an actuator assembly 401, an actuator body 402, an

16 actuator piston assembly 403, and a handlebar clamp 404. The handlebar clamp 404 is first connected to the actuator body 402 via bolts 406, and is then clamped to a handlebar of the bicycle (not shown). Notwithstanding the fact that the handlebar clamp 404 is a separate component that is connected to the actuator body 402, it is contemplated that in at least some embodiments the clamp is integrally formed with the actuator body. The size, shape and diameter of the clamp 404 can vary depending upon the size, shape and diameter of the handlebar upon which the clamp is mounted, hi addition, other securing mechanisms to secure the actuator body 402 to a handlebar have been contemplated. [0047] With respect to the actuator body 402, it includes a front end portion 408 that is in fluid communication with the brake hose sub-assembly 304 (see FIGS. 3A-3C) for conveying working fluid therethrough to facilitate a damping adjustment and/or lock-out. Working fluid is typically stored in a piston bore/working fluid chamber 409 situated inside the actuator body 402 and adjacent to a front-end portion 410. The actuator body is configured to substantially house the actuating assembly 401 wherein when a knob 412 of the actuating assembly 401 is depressed, it translates working fluid in the fluid chamber 409 via the actuator piston assembly 403, through the front-end portion 408, through the brake house 322, through the turret assembly 300 (see FIGS. 3A-3C), and into the slave chamber 216 (see FIGS. 2A-2C), as further described below. [0048] The actuating assembly 401 includes a cam actuator 414 that is connected in operational association with the knob 412. More particularly, the knob 412 is connected to an actuator knob end 421 of the cam actuator 414. The cam actuator 414 includes a key outer surface portion 416, which in turn is mounted in operational association with a threaded adjuster sleeve 418. The key outer surface portion 416 serves to substantially limit rotation of the adjuster sleeve 418 relative to the adjuster dial 440. In general, the adjuster sleeve 418 is keyed to the cam actuator 414 which in turn is keyed to slot 428 in the cam guide 426 by first cams 424 A, wherein the cam guide 426 is fixed to the actuator body 402. In one embodiment, the cam actuator 414 is A cylindrical rod that is shaped to complementarily fit the adjuster sleeve 418, although in other embodiments the actuator 414 can have another shape, such as square or triangular, to accommodate various adjuster sleeve shapes. In addition, the threaded adjuster sleeve 418 is mounted through an end cap 420. An actuator bushing 422 for reducing friction between the cam actuator 414 and the end cap 420 can also be provided.

17

[0049] The actuating assembly 401 further includes a cam guide 426 having a plurality of longitudinal cam guide grooves (or slots) 428. The cam actuator 414 includes a plurality of first cams 424, of which one or more are engaged with the cam guide grooves 428. The cam guide 426 in turn is threadingly engaged with the actuator body 402 to prevent rotation thereof. The piston assembly 403 also includes a second plurality of cams 434 situated about the piston 432, which are operatively associated to a front end 430 and the cam guide grooves 428 of the cam guide 426. Additionally, the cams 434 interact with the plurality of first cams 424 of the cam actuator 414. The plurality of first cams 424 further includes a plurality of protruding first cams 424A and a plurality of flush second cams 424B. Relatedly, the second plurality of cams 434 includes a plurality of protruding second cams 434 A and a plurality of flush second cams 434B, wherein the protruding second cams 434A interact with a plurality of cam slots 435 situated at the front end 430. The first plurality of cams 424 can also be referred to as a plurality of cam actuator cams 424, while the second plurality of cams 434 can also be referred to as a plurality of second cams 434. The other end (e.g., the end opposite the second plurality of cams 434) of the piston 432 is slidingly engaged with the actuator body 402. [0050] Further, the actuator assembly 401 includes a position adjuster dial 440 for adjusting a first position of the piston 432 that is threadingly engaged with the threaded adjuster sleeve 418, and a ball detent 442, a ball 443 and a spring 444 are employed for holding the position of the adjuster dial 440 and the adjuster sleeve 418 relative to the end cap 420. Typically, the first position can be varied by rotation of the position adjuster dial 440, which translates the adjuster sleeve 418 whose end provides a stop for the cam actuator 414. Further, the first position of the piston 432 can be modified from continuous locations to discrete locations and additionally fixed and variable locations using one or more adjuster dial mechanisms.

[0051] A piston seal 436 can be provided between the piston 432 and the actuator body 402 to provide a leak-proof seal. A bleed screw 438 can additionally be installed in the front end portion 408 of the actuator body 402 for creating a temporary opening in the otherwise closed working fluid flow path 437 (path 437 is discussed further below). In particular, the bleed screw 438 can be actuated to facilitate the removal of air from the handlebar actuator 400. In other embodiments, the positioning of the bleed screw 438 within the handlebar actuator 400 can vary. Additionally, any of a variety of commonly

18 employed and available mechanisms for removal of air/air bubbles can be used instead of or in conjunction with the bleed screw.

[0052] The operation of the handlebar actuator 400 can be understood by looking at FIGS. 4C-4J. Specifically, a second position of the piston 432 is shown in FIG. 4C in which one of the plurality of protruding first cams 424A (of the first plurality of cams 424, shown in FIG. 4B) is shown to be captured at the bottom of the cam guide groove 428, and one of the plurality of protruding second cams 434 A (of the plurality of second cams 434, shown in FIG. 4B) of the piston 432 is shown in a resting position in a cam slot 435 at the front end 430 of the cam guide 426. The cam slots 435 are configured to secure the protruding second cams 434A from rotating out of the resting position, wherein rotation of the piston 432 in one direction is substantially limited and rotation in the opposite direction is only partially limited.

[0053] Typically, damping adjustment and/or lock-out can be achieved by depressing the knob 412 (see FIG. 4A). By virtue of depressing the knob 412, the cam actuator 414 translates towards the piston 432, and particularly, the protruding first cam 424A travels down the cam guide groove 428 to contact the piston 432, as shown in FIG. 4D. Specifically, in this position, the protruding second cam 434A of the piston 432 is still situated in its resting position in a cam slot 435, and one or more of the first plurality of cams 424 is initiating contact with one or more of the second plurality of cams 434. It should be noted that when the first and the second plurality of cams 424 and 434, respectively, initiate contact, the toothed surfaces of the cams are offset from one another by the protruding first cam 424 A, protruding second cam 434 A, and the cam guide 426. The offset toothed surfaces of the cams can be seen in greater detail in FIG. 4E. It is the offsetting of the first and the second cam surfaces that causes the piston 432 to rotate. As further shown in FIG. 4F, the plurality of protruding first cams 424A is shown lifting the plurality of cams 434 above the tip portion 439 of the cam guide grooves 428 thus rotationally advancing the protruding second cam 434A over the tip portion 439. [0054] Next, as the knob 412 is released, the first plurality of cams 424 descends and the protruding second cams 434A of the piston 432 advance toward the longitudinal portion of the cam guide grooves 428. A close-up view of the protruding second cams 434A starting to slide down the cam guide 426 is shown in FIGS. 4G-4I. The translation of the piston 432 (towards the rear end portion 410) allows the working fluid to exit the slave chamber 216 through the turret assembly 300 and into the actuator bore 409. As the

19 piston 432 translation continues, the first and second cams 424, 434 continue to slide down the cam guide grooves 428 as shown in FIG. 41, thereby returning the piston 432 to the first position, as shown in FIG. 4J.

[0055] Starting at the piston 432 first position shown in FIG. 4J, depressing the knob 412 causes the protruding first cams 424A and the protruding second cams 434A to travel along the cam guide groove 428 towards the front end 430 of the cam guide 426. When the protruding second cams 434A reach the end of the cam guide groove 428, the offset surfaces of the cams 424, 434 cause the piston 432 to rotate. The protruding second cams 434A then leave the cam guide groove 428 and interact with the cam slots 435 of the cam guide 426. As the knob 412 is released, the piston 432 comes to rest in the second position as shown in FIG. 4C. As the piston 432 is advanced from the first position to the second position, the piston 432 pushes working fluid along the working fluid flow path 437 (as shown in FIG. 4A) and into the slave bore 214 (see FIGS. 2A-2C) via a connection, such as a turret assembly 300 or a hydraulic fitting 260. The working fluid thereby provides a translation of the slave piston 210 and therefore provides increased damping of the suspension fork 102 (see FIGS. 1A-2C).

[0056] Further, the first position of the piston 432 can be modified from continuous locations to discrete locations and additionally fixed and variable locations. Typically, the first position can be varied by rotation of the position adjuster dial 440, which translates the adjuster sleeve 418, whose end provides a stop for the cam actuator 414. [0057] Referring now to FIG. 5, a second embodiment of a mechanically advantageous continuously advancing linearly actuated handlebar actuator 500 is shown, in accordance with at least some other embodiments of the present invention. Generally speaking, the handlebar actuator 500 is similar (or substantially similar) in construction and operation to the handlebar actuator 400 of FIGS. 4A-4B, with the exception that a lever 502 is employed in lieu of the knob 412 to facilitate damping adjustment and/or lock-out. Specifically, the handlebar actuator 500 includes an actuator body 504 having front and rear end portions 506 and 508, respectively. Working fluid stored in a working fluid chamber 510 is conveyed through the front-end portion 506 to the turret assembly 300 (see Figs. 3A-3C) and subsequently to the slave chamber 216 (see FIG. 2A) by the actuation of the lever 502 connected to the rear end 508 of the actuator body 504. Additionally, similar to the handlebar actuator 400, a handlebar clamp 512 mounts the

20 handlebar actuator 500 to the handlebar of the bicycle. A bleed screw 514 creates a temporary opening along the working fluid flow path 515.

[0058] Also provided is a piston 516, which at one end is inserted into the actuator body 504 via a sealing mechanism 518, while a camming end 520 is engaged with a cam guide 522. The other end of the cam guide 522 (e.g., the end opposite to the one engaging the piston 516) is engaged with a cam actuator 524, which in turn is connected to a pushrod 526 connected to the lever 502. With respect to the lever in particular, it includes a lever attachment bracket 528, which connects the lever 502, via pivot pin 530, to the actuator body 504. A lever stop feature 532 about the pivot pin 530 limits or constrains movement of the lever 502 beyond a particular point by facilitating contact of the stop feature 532 with the lever surface 533. An adjuster mechanism 534 for adjusting the lever 502 can additionally be provided in a manner commonly known to one skilled in the art. The adjuster mechanism 534 can typically be employed in lieu of the threaded adjuster sleeve 418 and dial 440 (see FIGS. 4A-4B) for adjusting the first position. Additional sealing, retaining springs, structures and mechanisms can be employed to reduce friction and provide smooth connections.

[0059] In operation, activating the lever 502 results in translation and/or rotation of the cam actuator 524 and the piston 516 within the cam guide 522 in a manner previously described, so as to force working fluid from the front end portion 506 of the handlebar actuator 500. The working fluid is then communicated through an interconnected turret assembly 300 (see FIGS. 3A-3C) and slave chamber 216 (see FIG. 2A), which in turn results in translation of slave piston 210 to facilitate damping adjustment and/or lock-out. By virtue of employing the lever 502 to actuate the handlebar actuator 500, the overall force required to achieve piston translation is reduced, while also reducing the overall piston travel/stroke (by converting the mechanical advantage supplied by the lever to a larger diameter piston bore chamber 510) to hydraulically actuate the working fluid from the working fluid chamber 510 through the turret assembly 300 and to the slave chamber 216.

[0060] Turning now to FIG. 6, a third embodiment of a handlebar actuator 600 is shown in accordance with at least some alternate embodiments of the present invention. The handlebar actuator 600 is substantially similar to the handlebar actuator 400 of FIG. 4, except that the handlebar actuator of the present embodiment employs a pawl and rack system 602 instead of the cam guide and cam actuator system for facilitating damping

21 adjustment and/or lock-out. Specifically, the handlebar actuator 600 includes an actuator body 604 having a handlebar clamp 606, a bleed fitting 608 and a working fluid chamber/piston bore 610 for conveying working fluid to the suspension fork 102 (See FIG. 1 A-IC). Also provided is a knob 612 connected to an actuator 614, which in turn is in operational association with a piston 616. In some embodiments, the actuator 614 can be mounted to an end cap 622 via an actuator bushing 624 to provide an anti-rotational arrangement of the actuator 614 relative to the actuator body 604. The piston 616 translates in the piston bore 610 to force working fluid along the working fluid path 617 to the suspension fork 102. A piston sealing mechanism 620 can additionally be provided between the piston 616 and the piston bore 610 to create a leak proof seal. [0061] As additionally shown in FIG. 6, the actuator 614 has integrally formed therein a plurality of ratchet teeth 626 along an edge thereof for interacting with a pawl 628. The pawl 628 is formed as part of a release lever 630, which is capable of pivoting about pivot pin 632. A compression spring 634 biases the pawl 628 into engagement with the ratchet teeth 626. Specifically, in operation, actuation (e.g., depression) of the knob 612 causes translation of the actuator 614 (along with ratchet teeth 626) towards the piston 616, which in turn causes the piston 616 to translate within the piston bore 610 to move the working fluid. Working fluid from the piston bore 610 is caused to move along the working fluid path 617 and subsequently, through the fluid column 618, and then through the turret assembly 300 and to the slave chamber 216 to facilitate damping adjustment and/or lock-out. Additionally, as the actuator 614 translates towards the piston 616 for damping adjustment and/or lock-out, the pawl 628 follows the ratchet teeth 626 and falls into one of the spaces between two adjacent teeth 626. Specifically, the compression spring 634 forces the pawl 628 towards the ratchet teeth 626 for engagement. To return to the first position, the release lever 630 can be actuated (e.g., by pushing the lever towards the actuator body 604) causing the pawl 628 to lift free of the ratchet teeth 626. By virtue of freeing the pawl 628 from the ratchet teeth 626, the pressure of the working fluid causes the actuator 614 to return to its first position. Although the present embodiment does not have a first position adjustment feature similar to the first position adjustment features of FIGS. 4 and 5, the first position can be adjusted by selecting the ratchet tooth 626 to which the pawl 628 can engage.

[0062] Referring now to FIGS. 7 A and 7B, a fourth embodiment of the handlebar actuator 700 is shown in accordance with some further embodiments of the present

22 invention. Specifically, the handlebar actuator 700 is a screw type actuator employing an actuator screw 702 and a ball and detent system 704 for facilitating damping adjustment and/or lock-out, as explained below. As shown, the handlebar actuator 700 has an actuator body 706 and a bleed fitting 708 and a handlebar clamp 710 connected thereto in operational association as explained above. Also provided is a piston 712 situated inside the actuator body 706, the piston 712 having threads on its internal surface 713, which mate in threading engagement with the actuator screw 702. Anti-rotational pins 714 and a sealing mechanism 716 can be provided between the outer surface of the piston 712 and the inner surface of the actuator body 706 for preventing rotation of the piston and providing leak-proof seals respectively. Further, a top cap 732 containing one or more ball and spring pockets 724 is fixed to the actuator body 706.

[0063] A compression spring 718 is positioned beneath the piston 712 to provide a bias to maintain the position of the piston 712 in the fluid chamber 720 during assembly. A lever 723 is coupled to the actuator screw 702, as discussed below. The lever 723 is capable of rotating the actuator screw 702 about the internal surface 713, anti-rotational pins 714 are provided to substantially limit any rotation of the piston 712 thereby causing the piston 712 to translate downwards towards the working fluid chamber 720. Translation of the piston 712 in this manner, results in displacement of working fluid from the working fluid chamber 720 into the fluid column 722 and subsequently into the suspension fork 102 to facilitate damping adjustment and/or lock-out. Similarly, rotation of the lever 723 in a reverse direction causes rotation of the actuator screw 702 and translation of the piston 712 in the reverse direction, thereby providing reduced damping and/or unlocking. Typically, the lever 723 can be rotated continuously in both directions depending upon the level of damping adjustment and/or lock-out desired. Alternatively, the rotation of the lever 723 can by pre-designed to only rotate in discrete positions. [0064] To facilitate rotation (and anti-rotation) of the lever 723 in a constrained manner, the lever 723 is designed with a detent system configuration similar to the one discussed with regard to handlebar actuator 400. The detent system 704 includes one or more ball and spring pockets 724. Inside at least one of the ball and spring pockets 724, a ball 726, and spring 727 is operationally positioned to engage the ball detent 728 of the lever 723 and also to facilitate discrete rotation thereof. Notwithstanding the fact that only one of the ball and detent systems 704 has been shown in detail in the present embodiment, it is contemplated that a similar or substantially similar ball and detent system 704 can be

23 provided in multiple and/or alternate locations. A screw and washer 730 can additionally be employed for securing the actuator screw 702 to the lever 723. Thus, as described above, rotation of the lever 723 results in rotation of the actuator screw 702, which in turn translates the piston 712 to facilitate damping adjustment and/or lock-out. [0065] Referring now to FIGS. 8A-8E, a fifth embodiment of a handlebar actuator 800 is shown in accordance with at least some embodiments of the present invention. As shown in FIG. 8B, the handlebar actuator 800 includes an actuator body 802, a lever 804, a rotor 806 and a bleed screw 808. Although a handlebar clamp is not shown, it is understood that such a clamp can be provided and connected to the actuator body 802 at adjacent surface 810 discussed previously. The lever 804 and the rotor 806 are mounted in a top cap 816, wherein the top cap 816 is engaged (e.g., threadingly, welded, friction-fitted, etc.) to the actuator body 802. The lever 804 is rotatably mounted in the top cap 816 and includes a ball and detent system 812 situated between at least a portion of the lever 804 and top cap 816. The ball and detent system 812 is similar to the previously discussed system with regard to FIG. 7A. The lever 804 is also rotatably engaged with the rotor 806 such that rotation of the lever 804 causes rotation of the rotor 806. A piston/stator 818 is additionally provided about the rotor 806. The piston 818 and the rotor 806 are typically positioned within a piston bore 820 of the actuator body 802 for translation. Further the piston 818 and the piston bore 820 are keyed together (e.g., by employing an elliptical profile) to prevent piston rotation. In other embodiments, other types of anti- rotation structures and mechanisms can be employed as well to prevent piston rotation. A sealing mechanism 822 can additionally be provided to create leak-proof seals. [0066] Also provided is a ball ramp actuating mechanism 815 (FIG. 8D) situated between the piston 818 and the rotor 806. The mechanism 815 includes three ball bearings 824 (only one is shown in FIGS. 8C and 8D and none shown in 8 A and 8B) and three sets of upper and lower ramps 826, 828, respectively. The upper ramps 826 are formed in a bottom portion 829 of the rotor 806 and the lower ramps 828 are formed in the upper portion 831 of the piston 818. The ball bearings 824 are positioned in the ramps 828, 826 such that rotation of the rotor 806 by lever 804 causes the ball bearings to ride up (or down) the ramps 828, 826 to facilitate piston translation. An exemplary ball bearing and ramp configuration is illustrated in FIG. 8D, which is an unfolded view of the handlebar actuator 800 about the ramp centerline 833 taken along line W-W of FIG. 8E, in accordance with some embodiments of the present invention. Thus, counter-clockwise

24 rotation of the rotor 806, by the lever 804, causes the ball bearings 824 to ride up their respective ramps 828, 826 thereby translating the piston 818 downward against the bias of the compression spring 819 towards the fluid column 830. The downward piston translation moves the working fluid from the fluid chamber 832 situated in the piston bore 820, through the fluid column 830 (FIG. 8C) and into the suspension fork 102, to facilitate damping adjustment and/or lock-out. Relatedly, clock-wise rotation of the lever 804 causes the ball bearings 824 to ride down their respective ramps 828, 826, which results in translation of the piston 818 upwards towards the lever 804 under the bias of the compression spring 819. The upward piston translation allows the working fluid to return back to the fluid chamber 832 through the fluid column 830. Although the use of three ball bearings and three associated ramp assemblies have been discussed, the ball ramp actuating mechanism 815 should be understood to not be limited to these quantities. [0067] Thus, as described above, embodiments of the present invention provide a remotely actuable hydraulic adjustment system in which the remote actuator can be actuated to facilitate or accomplish damping adjustment and/or lockout at the suspension fork. Advantageously, use of the aforementioned suspension system results in a smoother actuation, longer periods of setting retention, and the capability to exert higher forces through imroved efficiency. Additionally, the actuation direction is not limited to pull (for example, as referenced from a bicycle wheel to a handlebar), thereby improving the feel and function of the remotely actuated damping adjuster/lockout. [0068] Although the suspension system, inlcuding the handelbar actuator assembly and damping assembly for example, have been disclosed for use with a front suspension fork assembly, the suspension system 100 or one or more of its sub-assemblies can be used in alternate embodiments to improve existing fork dampers. Further, in alternate embodiments, one or more of the various assemblies as described herein could also be utilized in, incorporated for use, and/or assembled as part of, a rear shock assembly and can be linked to both the front fork and a rear shock.

[0069] Notwithstanding the embodiments described above in relation to FIGS. 1 A-8D, it is nevertheless contemplated that various refinements to the features described above, including addition of various features and components that are commonly employed in conjunction with, or as part of suspension systems, are included. For example, various other sealing structures and mechanisms, anti-rotational rings and mechanisms and various friction-reducing devices can be employed. Furthermore, notwithstanding the

25 embodiments of the suspension fork and the handlebar actuator described above, it is contemplated that other embodiments for hydraulically adjusting the suspension fork can be employed as well.

[0070] Further, despite any methods being outlined in a step-by-step sequence, the completion of acts or steps in a particular chronological order is not necessarily mandatory. Modification, rearrangement, combination, reordering, or the like, of acts or steps where such changes are appropriate for and maintain proper functioning of the invention in one or more of its various embodiments is contemplated and considered within the scope of the description and claims.

[0071] Accordingly, it is specifically intended that the present invention not be limited to the embodiments and illustrations contained herein but include modified forms of those embodiments including portions of the embodiments and combinations of elements of different embodiments as come within the scope of the following claims.