Abstract:
A bicycle suspension includes a stroke adjustment unit, a suspension damper, a damper adjustment unit, and a control mechanism. The stroke adjustment unit is configured to adjust a stroke of the bicycle suspension, which is configured to expand and contract within the stroke. The suspension damper is configured to apply damping force to the bicycle suspension. The damper adjustment unit is configured to adjust the damping force applied by the suspension damper. The control mechanism operatively couples the stroke adjustment unit to the damper adjustment unit and is configured to sequentially adjust the stroke and the damping force.

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates to a suspension for a bicycle. 
     2. Discussion of Background 
     Bicycling is becoming an increasingly more popular form of recreation, as well as a dependable means of transportation. Moreover, bicycling has become a very popular competitive sport for both amateurs and professionals, alike. Whatever the purpose, the bicycle industry is constantly seeking to improve various components of bicycles. For instance, conventional bicycles had rigid frames and forks without front or rear suspensions and, as a result, transmitted terrain-induced vibrations directly to a rider. More recently, bicycles, such as mountain bikes (MTB) and all-terrain bikes (ATB), have been fit with front and/or rear suspension assemblies configured to substantially absorb terrain-induced vibrations that would otherwise be transmitted to a rider. Depending upon the terrain, however, some riders may find it desirable to quickly adjust or even lockout these suspension assemblies. Even though bicycles including adjustable suspension assemblies have been introduced, such as in German Patent No. DE 19532088 A1, improvements upon the structure and function of these components are still desired. 
     SUMMARY OF THE INVENTION 
     An aspect of the present invention advantageously provides a bicycle suspension including a stroke adjustment unit, a suspension damper, a damper adjustment unit, and a control mechanism. The stroke adjustment unit is configured to adjust a stroke of the bicycle suspension, which is configured to expand and contract within the stroke. The suspension damper is configured to apply damping force to the bicycle suspension. The damper adjustment unit is configured to adjust the damping force applied by the suspension damper. The control mechanism operatively couples the stroke adjustment unit to the damper adjustment unit and is configured to sequentially adjust the stroke and the damping force. 
     Additional features, aspects, and advantages of the present invention will become apparent to those skilled in the art from the following detailed description, wherein various exemplary embodiments are shown and described, simply by way of illustration of the best mode contemplated of carrying out the invention. As will be realized, the invention is capable of other and different embodiments, and its several details are capable of modifications in various obvious respects, all without departing from the invention. Accordingly, the drawings and description are to be regarded as illustrative in nature, and not as restrictive. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       A more complete appreciation of the invention and many of the attendant advantages thereof will become readily apparent with reference to the following detailed description, particularly when considered in conjunction with the accompanying drawings, wherein: 
         FIG. 1  is a schematic elevation view of a portion of a bicycle equipped with a suspension control unit configured to selectively control a suspension assembly of the bicycle, according to an exemplary embodiment; 
         FIG. 2  is a schematic plan view of the suspension control unit of  FIG. 1 , according to an exemplary embodiment; 
         FIG. 3  is a schematic elevation view of the suspension assembly of  FIG. 1 , according to an exemplary embodiment; 
         FIGS. 4 and 5  are schematic perspective views of portions of the suspension assembly of  FIG. 1 , according to exemplary embodiments; 
         FIG. 6  is a simplified sectional view of a damper adjustment unit of the suspension assembly of  FIG. 3 , according to an exemplary embodiment; 
         FIG. 7  is a simplified sectional view of a stroke adjustment unit of the suspension assembly of  FIG. 3 , according to an exemplary embodiment; 
         FIG. 8  is a sectional view of a portion of the stroke adjustment unit of  FIGS. 3 and 7 , according to an exemplary embodiment; 
         FIGS. 9 and 10  are sectional views of portions of the damper adjustment unit of  FIGS. 3 and 8 , according to an exemplary embodiment; 
         FIG. 11  is a sectional view of a portion of the damper adjustment unit of  FIGS. 3 and 8  in a “normal” operating state, according to an exemplary embodiment; 
         FIG. 12  is a sectional view of the damper adjustment unit of  FIG. 11  taken along line XII-XII, according to an exemplary embodiment; 
         FIG. 13  is a sectional view of a portion of the damper adjustment unit of  FIGS. 3 and 8  in a “locked out” operating state, according to an exemplary embodiment; 
         FIG. 14  is a sectional view of the damper adjustment unit of  FIG. 13  taken along line XIV-XIV, according to an exemplary embodiment; 
         FIGS. 15A-15C  and  16 A- 16 C schematically illustrate processes for controlling the suspension assembly of  FIG. 1 , according to exemplary embodiments; 
         FIG. 17  is a sectional view of a portion of a modified damper adjustment unit of  FIGS. 3 and 8 , according to an exemplary embodiment; 
         FIG. 18  is a sectional view of the damper adjustment unit of  FIG. 17  taken along line XVIII-XVIII, according to an exemplary embodiment; 
         FIG. 19  is a sectional view of the damper adjustment unit of  FIG. 18  taken along line XIX-XIX, according to an exemplary embodiment; and 
         FIGS. 20A-1 ,  20 A- 2 ,  20 B- 1 ,  20 B- 2 ,  20 C- 1 , and  20 C- 2  schematically illustrate a process for controlling the suspension assembly of  FIG. 1  including the modified damper adjustment unit of  FIGS. 17-19 , according to an exemplary embodiment. 
     
    
    
     DESCRIPTION OF EXEMPLARY EMBODIMENTS 
     Various exemplary embodiments will now be described hereinafter with reference to the accompanying drawings, wherein like reference numerals designate corresponding or identical elements throughout the various drawings. Accordingly, the drawings and description are to be regarded as illustrative in nature, and not as restrictive. 
       FIG. 1  is a schematic elevation view of a portion of a bicycle equipped with a suspension control unit configured to selectively control a suspension assembly of the bicycle, according to an exemplary embodiment.  FIG. 2  provides a schematic plan view of the suspension control unit of  FIG. 1 , whereas  FIGS. 3-5  illustrate various schematic views of the suspension assembly of  FIG. 1 . In one particular implementation, the suspension control unit is configured to enable a rider (not shown) to dynamically adjust a stroke and/or a damping force of the suspension assembly, such as a fork-type suspension assembly of a bicycle. While specific reference will be made hereto, it is contemplated that various exemplary embodiments also find application in other suspension assemblies, such as linear suspension assemblies, etc., as well as in other vehicles, e.g., tricycles, motorcycles, and the like. 
     Referring initially to  FIGS. 1-3 , a bicycle  10  includes a control unit  14  configured to dynamically control a fork-type suspension assembly (hereinafter suspension)  12  among various operating states, such as a first state (e.g., a first suspension setting), a second state (e.g., a second suspension setting) and a third state (e.g., a third suspension setting). These operating states are configured to sequentially adjust a stroke and a damping force of the suspension  12 , as will become more readily apparent below. It is noted, however, that the control unit  14  may be configured to sequentially toggle between the first state and the second state and between the second state and the third state. As such, the control unit  14  may sequentially adjust the stroke and the damping force. 
     According to various exemplary embodiments, an upper end portion  12   a  of the suspension  12  is rotatably mounted within, for example, a head tube  16  of a frame  18  of the bicycle  10  and lower end portions  12   b  of the suspension  12  are rotatably coupled to a wheel  20  of the bicycle  10 . In this manner, the suspension  12  is configured to absorb, for instance, terrain-induced vibrations that would otherwise be transmitted to a rider (not shown) through the frame  18  and the wheel  20 . According to one embodiment, the first state of the suspension  12  may relate to a relatively “long” stroke suspension setting, whereas the second state may relate to a relatively “short” stroke suspension setting, as will become more readily apparent below. In certain instances, the suspension  12  may be dynamically locked out, such as when an operating state (e.g., a third state) of the suspension  12  is controlled to lock a damping force of the suspension  12 . As such, actuation (e.g., contraction and expansion (or rebound)) of a first shock absorber unit  22  and a second shock absorber unit  24  of the suspension  12  may be dynamically adjusted and locked or unlocked via the control unit  14 . 
     As seen in FIGS.  1  and  3 - 5 , the suspension  12  includes the first shock absorber unit  22  that includes an upper telescopic member  26  slidably received within a lower portion  28 , and the second shock absorber unit  24  that includes an upper telescopic member  30  slidably received within a lower portion  32 . In this manner, the first and second shock absorber units  22  and  24  are configured to absorb and dampen, for example, terrain-induced vibrations when riding the bicycle  10 . The upper telescopic members  26  and  30  are respectively provided with suspension setting mechanisms  34  and  36  for dynamically adjusting a stroke and/or damping force of the suspension  12  and, as a result, enabling a rider to control the expansion (or rebound) and contraction of the telescopic members  26  and  30 . The suspension setting mechanisms  34  and  36  are provided with respective cable operated adjustment pulleys (or adjustment actuators)  38  and  40  that can be actuated (e.g., rotated) between at least two positions, such as the first state corresponding to the relatively “long” stroke suspension setting, and the second state corresponding to the “short” stroke suspension setting), via the control unit  14 . According to certain embodiments, one or more of the cable operated adjustment pulleys  38  and  40  may be actuated, via the control unit  14 , to a third state corresponding to a locked-out suspension setting. 
     Averting back to  FIGS. 1 and 2 , the control unit  14  may be mounted to a handlebar  42  of the bicycle  10  via a tube clamp of a brake lever  44 ; however, it is contemplated that the control unit  14  may be alternatively mounted to the handlebar  42  via a separate tube clamp or any other suitable mounting device or assembly. In the illustrated embodiment, the control unit  14  is configured and, thereby, arranged to operate one or more of the adjustment pulleys  38  and  40  by, for example, a control cable  46 , such as a bowden cable, etc., that includes an inner wire  46   a  and an outer casing  46   b . The inner wire  46   a  may be manipulated via the control unit  14 , such as in a “pulling” fashion, for switching the suspension  12  from, for instance, the first state to the second state and from the second state to the third state. It is noted that the inner wire  46   a  may also be manipulated via the control unit  14 , such as in a “releasing” fashion, for switching the suspension  12  from the second state to the first state and from the third state to the second state. As a result, when the control unit  14  is actuated to, for instance, “pull” the inner wire  46   a , one or more of the adjustment pulleys  38  and  40  may rotate about respective rotational axes  48  and  50  in a first direction of rotation, such that when the control unit  14  is actuated to “release” the inner wire  46   a , one or more of the adjustment pulleys  38  and  40  may rotate about the rotational axes  48  and  50  in a second direction of rotation, such as an opposite direction of rotation. 
     As seen in  FIG. 2 , the control unit  14  includes a base member  52  and a wire winding mechanism  54  having a lever portion  56  and a release mechanism  58 . The base member  52  is a stationary member fixedly mounted to the handlebar  42  and is positioned to enable a rider to easily manipulate the wire winding mechanism  54  and the release mechanism  58 , such as, for example, without requiring the rider&#39;s hand to leave the handlebar  42 . Generally, the wire winding mechanism  54  has an operating path that curves about a center mounting axis  60  of the handlebar  42 , while the release mechanism  58  has an operating path that extends, such as linearly, e.g., parallel, with respect to the mounting axis  60 . The wire winding mechanism  54  includes a first operating member  62  movably mounted relative to the base member  52  for rotation between the first state and the second state and between the second state and the third state, such as about a rotational axis. 
     According to exemplary embodiments, the first operating member  62  may have a resting position, which may correspond to the first state. In this manner, the first operating member  62  may be biased relative to the base member  52  and, thereby, establish (or otherwise correspond to) the second state. Accordingly, a user can manipulate, e.g., pull or otherwise actuate, the operating member  62  from the first state to one or more of the second or third states. It is noted that the operating member  62  “locks” in place when manipulated from the first state to the second or from the second state to the third state. In order to return from a locked position, the user may actuate the release mechanism  58 , which is configured to “unlock” the operating member  62  from, for instance, the second state or the third state. As such, the aforementioned biasing effect returns the operating member  62  to, for instance, the first state or the second state. Although exemplary embodiments are described with respect to the control unit  14 , other suitable or equivalent control units may be additionally (or alternatively) utilized, as will be readily apparent to those of ordinary skill in the art. Furthermore, it is contemplated that one or more intermediary operating states may be provided between the first state and the second state and/or between the second state and the third state. 
     Averting to  FIGS. 3-5 , the suspension  12  may be incorporated into (or otherwise define) a fork of the bicycle  10 , such as a front-fork of the bicycle  10 . It is contemplated, however, that the suspension  12  may be alternatively (or additionally) utilized as or part of a rear suspension assembly and, thereby, may include other control units corresponding to these other suspension assembly configurations. In the illustrated embodiment, however, the suspension  12  includes a center tubular member (e.g., a steerer tube)  64  pivotally connected to the frame  18  and a bracket (or first connector)  66  that rigidly connects center the tubular member  64  to the first shock absorber unit  22  and the second shock absorber unit  24 , which are respectively attached at the lower end portions  12   b  to either ends of an axle  68  of the wheel  20 . A structural member or bracket (or second connector)  70  is provided and configured to rigidly connect the lower portion  28  of the shock absorber unit  22  to the lower portion  32  of the second shock absorber unit  24 . In this manner, the structural member  70  provides structural stability to the suspension  12 . It is noted that the frame  18 , via the head tube  16 , is rotatably attached to the center tubular member  64  of the upper telescopic members  26  and  30  (which are interconnected via the bracket  66 ), and the wheel  20  is attached to the lower portions  28  and  32  (which are interconnected via a bracket  74 ) of the shock absorber units  22  and  24 , respectively. As such, the suspension  12  may be provided between the frame  18  and the wheel  20  so as to enable terrain-induced vibrations from, for example, the wheel  20  to be absorbed and dampened instead of being transmitted to the frame  18  and a rider thereon. 
     According to various exemplary embodiments, the first shock absorber unit  22  includes the upper telescopic member  26  having an upper end thereof connected to (e.g., threadedly engaged with) a connecting bracket  72  of the bracket  66 . The upper telescopic member  26  also includes a lower end thereof slidably received within an upper end of the lower portion  28  of the first shock absorber unit  22 . In a similar fashion, the second shock absorber unit  24  includes the upper telescopic member  30  having an upper end thereof connected to (e.g., threadedly engaged with) a connecting bracket  74  of the bracket  66  and a lower end thereof slidably received within an upper end of the lower portion  32  of the second shock absorber unit  24 . As previously noted, the lower end portions  12   b  of the lower portions  28  and  32  are attached to the axle  68  of the wheel  20  via any suitable coupling device, assembly, or mechanism. 
     With continued reference to  FIGS. 1 and 3 , the suspension setting mechanisms  34  and  36  are provided at upper end portions of the upper telescopic members  26  and  30 , respectively, and protrude from an upper surface of the bracket  66 . The suspension setting mechanisms  34  and  36  respectively include adjustment actuators (i.e. the adjustment pulleys)  38  and  40  configured to respectively adjust a stroke and a damping force of the suspension  12 . Even though the suspension setting mechanisms  34  and  36  are shown exposed to an ambient environment, it is contemplated that the suspension setting mechanisms  34  and/or  36  may be covered (or otherwise concealed) by way of one or more housing members (not shown). The suspension setting mechanisms  34  and  36  are described in more detail in accordance with  FIGS. 4 ,  5 , and  8 - 10 . 
       FIGS. 4 and 5  provide enlarged, schematic perspective views of the suspension setting mechanisms  34  and  36  of the suspension  12 , respectively. According to exemplary embodiments, the suspension setting mechanisms  34  and  36  respectively include the adjustment pulleys  38  and  40  configured to be actuated, e.g., rotated about respective rotational axes  48  and  50 , via interaction with the control unit  14 , such as manipulation of the operating member  62  of the control unit  14  among and between various operating states. In this manner, a portion  46   c  of the control cable  46  may extend from the control unit  14  to a cable receiving portion  76  of the suspension setting mechanism  36 . The portion  46   c  of the control cable  46  may be secured in a recessed region  78  of the adjustment pulley  40  via any suitable coupling mechanism  80 , such as a set screw. Accordingly, a portion  46   d  of the control cable  46  may extend from the adjustment pulley  40  to the adjustment pulley  38  and may be correspondingly secured in a recessed region  82  of the adjustment pulley  38  via any suitable coupling mechanism  84 , such as a set screw. As will become more readily apparent below, adjusting an operating tension of the control cable  46  causes one or more of the adjustment pulleys  38  and  40  to rotate about respective rotational axes  48  and  50  and, thereby, affecting a change in a stroke and/or damping force characteristic of the suspension  12 . Accordingly, the control unit  14  and the control cable  46  essentially constitute a control mechanism operatively coupling a stroke adjustment unit to a damper adjustment unit of the suspension  12  so as to sequentially adjust the stroke and the damping force of the suspension  12 . 
     According to certain exemplary embodiments, the adjustment pulley  40  may be biased relative to a rotational position (e.g., resisting state) of a shaft  86  of the second shock absorber unit  24  that, when actuated (e.g., rotated), is configured to modify a stroke of the suspension  12 . It is noted that one or more internal components of the second shock absorber unit  24  for effectuating these modifications (or adjustments) are described in more detail in accordance with  FIGS. 7 and 8 . In this manner, the adjustment pulley  40  may include a second anchoring portion  88  for coupling the adjustment pulley  40  to a distal end of a biasing member (such as a coil spring)  90  configured to bias the adjustment pulley  40  to, for instance, one or more of the aforementioned operating states, such as about the rotational axis  50 . An opposing distal end of the biasing member  90  may be coupled to, for instance, an anchoring bracket  92  extending from and fixedly engaged with the bracket  66  of the suspension  12 . 
     Additionally (or alternatively), the adjustment pulley  38  may be biased relative to a rotational position (e.g., resting state) of an actuating member  94  of the first shock absorber unit  22  that, when actuated (e.g., rotated), is configured to modify a damping force of the suspension  12 . In certain embodiments, rotation of the pulley  38  eventually engages the actuating member  94 , such that both pulley  38  and actuating member  94  may rotate as a unit. Accordingly, rotation of the actuating member  94  may be utilized to “lockout” the first shock absorber unit  22 . It is noted that one or more internal components of the first shock absorber unit  22  for effectuating “lockout” and/or dampening adjustments are more fully described in association with FIGS.  6  and  9 - 14 . In this manner, a biasing member (such as a torsion spring)  96  may be anchored between a first anchoring portion  98  and the adjustment pulley  38 . For instance, a torsion spring  96  may be coiled about an inner diametrical surface (not shown) of recess region  82  of the adjustment pulley  38 . As such, a first distal end of the torsion spring  96  may be anchored to the first anchoring portion  98 , whereas a second distal end of torsion spring  96  may be anchored to the adjustment pulley  38  via bore opening  100 . Accordingly, torsion spring  96  may bias the adjustment pulley  38  to, for instance, one or more of the aforementioned operating states, such as about rotational axis  48 . 
       FIGS. 6 and 7  are, respectively, simplified sectional views of the first and second shock absorber units  22  and  24  of the suspension  12 . It is noted that the component(s) of the first and second shock absorber units  22  and  24  are shown in a generic manner in order to simplify the depictions thereof, whereas  FIGS. 8-14  provide more detailed views of the first and second shock absorber units  22  and  24 . According to exemplary embodiments, the first shock absorber unit  22  is configured as a damper adjustment unit and, thereby, incorporates an adjustable dampening unit  102 , whereas the second shock absorber unit  24  is configured as a stroke adjustment unit and, thereby, incorporates an adjustable air spring  104 , which in unison (via, for example, the bracket  66 ) provide the suspension  12  with adjustable spring and dampening characteristics. It is noted that the first shock absorber  22  incorporates a damper adjustment unit  106   a  on an upper end of the adjustable dampening unit  102  and the second shock absorber unit  24  incorporates a stroke adjustment unit  108  on an upper end of the adjustable air spring  104 . 
     Referring to  FIG. 7 , the adjustable air spring  104  includes an upper seal member  110  connected to the upper telescopic member  30  via the stroke adjustment unit  108 . A longitudinal position of the upper seal member  110  along the upper telescopic member  30  may be adjusted by the stroke adjustment unit  108 , which will become more apparent below. It is noted that adjustment of the stroke adjustment unit  108  determines a stroke length (e.g., maximum, minimum, etc., stroke length) of the second shock absorber unit  24 . 
     According to various exemplary embodiments, the adjustable air spring  104  includes a lower seal member  112  rigidly connected to a lower end of the lower portion  32  via a tube  114 . The lower seal member  112  is slidably received within a tube  116  connected to the upper seal member  110  and, thereby, a chamber (e.g., an air chamber)  118  is defined between the upper seal member  110  and the lower seal member  112 . In this manner, the lower seal member  112  may be referred to as a “piston”  112 . It is noted that the chamber  118  may act as an air spring between the upper telescopic member  30  (via the upper seal member  110 ) and the lower portion  32  (via the lower seal member  112 ). A relative constant volume and, thereby, variable pressure of gas (e.g., air) within the chamber  118  may be adjusted via a valve/nozzle  120 , which is fluidly connected to the chamber  118  via a passage extending through the tube  114 . The adjustable air spring  104  may also include a coil spring  122  that functions to bias the lower seal member  112  toward upper seal member  110  and, thereby, provides further spring and/or dampening characteristics to the adjustable air spring  104 . 
     As previously described, the stroke adjustment unit  108  can be used to adjust a stroke length of the second shock absorber unit  24  by adjusting a longitudinal position of the upper seal member  110  along a length of the upper telescopic member  30 . Since a volume of for instance, air within the chamber  118  can remain relatively constant during use (absent adjustment via the valve/nozzle  120 ), relative positions between the upper seal member  110  and the lower seal member  112  remain relatively constant when external forces (e.g., vibrations) on the suspension  12  are disregarded. As such, adjustment of a longitudinal position of the upper seal member  110  along the upper telescopic member  30  has an effect of adjusting a longitudinal position of the lower seal member  112  in a same direction, which thereby adjusts a stroke length of the second shock absorber unit  24 . For example, if the upper seal member  110  is displaced upward (e.g., toward a suspension setting unit  36 ), then the lower seal member  112  may also displace upward relative to the upper telescopic member  30  and, for instance, a maximum stroke length of the second shock absorber unit  24  can be reduced. Such a stroke adjustment is transmitted to the first shock absorber unit  22  via the structural member  70 . 
     Averting to  FIG. 6 , the dampening unit  102  includes an upper seal member  124  rigidly connected to the upper telescopic member  26 . The dampening unit  102  further includes a lower seal member  126  rigidly connected to a lower end of the lower telescopic member  28  by a tube  128 . The lower seal member  126  is slidably received within a tube  130  of the upper telescopic member  26 . In this manner, the lower seal member  126  may be referred to as a “piston”  126 . A fluid chamber  132  is defined between the upper seal member  124  and the lower seal member  126  on a lower end of the upper telescopic member  26 . Accordingly, the fluid chamber  132  may contain, therein, any suitable dampening fluid, such as oil, that is used in conjunction with the lower seal member  126  to act as a damper. The lower seal member  126  includes a plurality of holes (or fluid flow ports)  134  that enable fluid from the fluid chamber  132  to travel therethrough. In this manner, the lower seal member  126  effectively divides the fluid chamber  132  into an upper cavity  136  and a lower cavity  138 , with the holes  134  of the lower seal member  126  enabling fluid to travel from one cavity to the other depending on a force(s) acting on the upper telescopic member  26  and the lower portion  28 . It is noted that an effective dampening force realized by way of the dampening unit  102  is substantially related to a volume of fluid capable of traveling through the holes  134  when the lower seal member  126  received within the tube  130  is displaced into (or out of) the fluid chamber  132 . As such, dampening forces may act on the upper telescopic member  26 , as well as the lower portion  28 . 
     As seen in  FIG. 6 , the damper adjustment unit  106   a  includes several components that enable fluid from the fluid chamber  132  to be displaced into and out of a reservoir chamber  140  disposed, for example, above the upper seal member  124 . For instance, a tube  142  may be provided to extend downward through an opening in the upper seal member  124 , one or more holes  144  are provided in the upper seal member  124 , and one or more one-way valves (e.g., back-flow flaps that may be spring-biased) for the holes  144  are provided on a lower surface of the upper seal member  124  to enable fluid flow into, but not out of the fluid chamber  132 . One or more upper openings  146  are provided, for example, at an upper end of the tube  142 , and one or more one-way valves for the upper openings  146  are provided to enable upward flow from the fluid chamber  132  and into the reservoir chamber  140  through the openings  146 , but not downward fluid flow from the openings  146  to the fluid chamber  132  through the tube  142 . According to particular embodiments, the damper adjustment unit  106   a  includes a valve  148  acting as an actuator capable of closing or opening the upper openings  146  for controlling fluid flow to the reservoir cavity  140 . It is noted that when the valve  148  is closed, the openings  146  are also closed and, thus, fluid is prevented from flowing between the fluid chamber  132  and the reservoir cavity  140 . In this manner, the damper adjustment unit  106   a  can provide a lockout feature for the first shock absorber unit  22 . 
       FIG. 8  is an enlarged, partial sectional view of a stroke adjustment unit  150  of the second shock absorber unit  24 . The stroke adjustment unit  150  includes a shaft  152  having a helically threaded or grooved surface  152   a  on an outer circumference thereof, which is provided as an actuator for adjusting a stroke of the second shock absorber unit  24 . Generally, the adjustment unit  150  includes the shaft  152 , an upper cylinder  154  having an upper portion rigidly connected to an upper end of the upper telescopic member  30 , and a lower cylinder  156  having an upper portion slidably received within a lower portion of the upper cylinder  154 . The shaft  152  is rotatably received by an upper portion of the upper cylinder  154 . It is noted that the shaft  152  includes an upper end  152   b  acting as the adjustment actuator  40 , or a component thereof. The shaft  152  also includes flanges  152   c  and  152   d  positioned adjacent to an upper surface and a lower surface, respectively, of the upper cylinder  154  such that the shaft  152  cannot axially move, but may rotate about a rotational axis thereof. A lower end  152   e  of the shaft  152  is provided within a lower portion of the upper cylinder  154 . The upper portion of the lower cylinder  156  includes ball members  158  that mesh with the threaded surface  152   a  of the shaft  150  and support the lower cylinder  156  within an interior of the upper cylinder  154 . Seals or gaskets  160  (e.g., O-rings, etc.) are provided on an outer circumference of an upper portion of the lower cylinder  156  in order to seal an interface between the lower cylinder  156  and the upper cylinder  154 . As previously described, the control unit  14  is configured to manipulate (e.g., rotate) the upper end  152   b  of the shaft  152 , such that corresponding rotational motion of the helically threaded or grooved surface  152   a  guides the ball members  158  and the lower cylinder  156  can relatively move upward or downward within the upper cylinder  154  as guided by the seals  160 . Such mechanical adjustment of the stroke adjustment unit  150 , such as via the threaded surface  152   a  of the shaft  152 , provides fine control over adjustment settings of a stroke length, given that an adjusted length of a stroke and its adjustable range can be precisely determined with respect to an amount of rotation of the shaft  152 . For example, a diameter of the actuator shaft  152  and a pitch of threaded portion  152   a  thereon can be selected for providing a desired adjustment setting, e.g., a desired maximum, minimum, etc., length with a desired adjustability of length between the maximum and minimum lengths. 
     Referring now to  FIGS. 9 and 10 , there are illustrated two sectional views of a damper adjustment unit  106   b  of the first shock absorber unit  22 . According to various exemplary embodiments, the damper adjustment unit  106   b  may include a damping piston  162 , a lockout valve  164 , a lockout piston  166 , a return valve  168 , a blow-off mechanism  170 , a free piston  172 , a compression spring  174 , an upper support member  176 , an upper body member  178 , and a damping force adjustment valve  180 . The lockout valve  164  and the lockout piston  166  cooperate to form a damping lockout mechanism that effectively locks the suspension  12  so that the suspension  12  can function as a rigid non-suspension fork, when in a “locked out” mode. 
     The suspension setting mechanism  34  is positioned at a top portion of the upper telescopic member  26  and is operatively coupled to the lockout valve  164  and the damping force adjustment valve  180 . According to particular embodiments, the suspension setting mechanism  34  includes a first actuating member  38  and a second actuating member  94 . The first actuating member  38  is operatively coupled to the damping force adjustment valve  180  to enable adjust of a damping force of the damper adjustment unit  106   b . The second actuating member  94  is operatively coupled to the lockout valve  164 . 
     The damping piston  162  essentially divides the upper telescopic member  26  into two areas so as to define an upper internal chamber  182  (e.g., reservoir chamber  140 ) and a lower internal chamber  184  (e.g., fluid chamber  132 ). In this manner, the damping piston  162  includes an annular seal or O-ring disposed between an outer peripheral surface and an internal surface of the upper telescopic member  26  to create a seal therebetween and, thereby, upper and lower internal chambers  182  and  184 . The damping piston  162  may also include a plurality of rebound ports  186  and a plurality of compression ports  188 . The rebound ports  186  and the compression ports  188  are alternately arranged about the damping position  162 , such as in a circumferential manner around the damping piston  162 . In one embodiment, the damping piston  162  includes a check valve  190  and a shim stack valve  192 ; however, it is contemplated that other suitable directional valves (or flow control mechanisms) may be employed. 
     In the depicted embodiment, the check valve  190  may include a check valve plate  190   a , a compression spring  190   b , and a spring retainer  190   c . In this manner, the check valve plate  190   a  may press against a lower end of the damping piston  162  in light of a biasing force imposed by the compression spring  190   b  that normally closes off the rebound ports  186 ; however, during suspension rebound (e.g., expansion of the suspension  12 ), fluid from the upper internal chamber  182  displaces check valve plate  190   a  from the lower end of the damping piston  162  and, thereby, opens the rebound ports  186 , which enables fluid from the upper internal chamber  182  to flow therethrough. As such, the check valve  190  selectively enables fluid communication between the upper internal chamber  182  and the lower internal chamber  184  through the rebound ports  186  during rebounding displacement of the suspension  12 . 
     The shim stack valve  192  normally abuts an upper end of the damping piston  162  to close off the compression ports  188 . In this manner, the shim stack valve  192  may be a single shim, or a stack comprised of multiple shims, which may be substantially annular in shape, however, any suitable geometry may be utilized. The shim stack valve  192  selectively allows fluid communication between the upper internal chamber  182  and the lower internal chamber  184  via the compression ports  188 . During compression of the suspension  12 , the shim stack valve  192  may essentially serve as a diaphragm spring and, thereby, is configured to flex in response to sufficient aggregation of fluid pressure in the lower internal chamber  184 . During rebounding displacement of the suspension  12 , the shim stack valve  192  is engaged with an upper surface of the damping piston  162  to prevent fluid from flowing through the shim stack valve  192 . It is noted, however, that the check valve  190  enables fluid communication between the upper internal chamber  182  and the lower internal chamber  184  through the rebound ports  186  during rebound of the suspension  12 . 
     The lockout valve  164  is rotatably mounted in the upper telescopic member  26  with its outer peripheral surface spaced inwardly from an internal surface of the upper telescopic member  26 . In this manner, the lockout valve  164  is rotatable between a lockout position corresponding to a non-damping or lockout mode and an unlocked position corresponding to a normal damping or operating mode. According to various exemplary embodiments, however, the lockout valve  164  may be rotatable between any number of positions that ultimately progress towards the aforementioned lockout position. In any event, rotating the lockout valve  164  to a lockout position (or state), fluid flow through the lockout piston  166  and, thereby, between the upper and lower internal chambers  182  and  184  is effectively blocked. When the lockout valve  164  is in an unlocked position, fluid may flow through the lockout piston  166  and, thereby, between the upper and lower internal chambers  182  and  184  so that the suspension  12  can operate in one or more “normal” operating modes, i.e., one or more modes configured to absorb terrain-imposed vibrations. 
     Averting to  FIGS. 11 and 13 , the lockout valve  164  may include a main body portion  164   a , an upper shaft portion  164   b , and a lower shaft portion  164   c . A center bore  164   d  extends axially through the portions  164   a  to  164   c  to enable fluid to flow therethrough. As seen in  FIGS. 12 and 14 , the main body portion  164   a  includes a plurality of lobe sections (e.g., three lobe sections), which may be equally spaced apart in a circumferential direction and, thereby, define a plurality of axial fluid flow passages  194 . In this manner, a plurality of radial bores (e.g., three radial bores)  164   e  extend radially from the center bore  164   d  to axial fluid flow the passages  194  to enable fluid to flow from the center bore  164   d  through the radial bores  164   e  to axial fluid flow the passages  194  during compression of the suspension  12 . Accordingly, the center bore  164   d  and the radial bores  164   e  form a center compression fluid passage connecting the lower internal chamber  184  to the upper internal chamber  182 . The damping force adjustment valve  180  can be disposed in the center bore  164   d  of the lockout valve  164  for regulating a flow rate of fluid passing from the center bore  164   d  through the radial bores  164   e  to axial fluid flow passages  194 . In this manner, a lower tip end of the damping force adjustment valve  180  cooperates with the center bore  164   d  of the lockout valve  164  to essentially form a needle valve. As such, the damping force adjustment valve  180  is axially movable within the center bore  164   d  of the lockout valve  164  such that the tip end of the damping force adjustment valve  180  can selectively change a flow area between the center bore  164   d  and the tip end of the damping force adjustment valve  180 . 
     The upper shaft portion  164   b  of the lockout valve  164  may include internal threads within the center bore  164   d  of the lockout valve  164  for securing the second actuating member  94  thereto, as will become more readily apparent below. As such, rotation of the second actuating member  94  causes the lockout valve  164  to rotate therewith. 
     The lower shaft portion  164   c  of the lockout valve  164  supports the damping piston  162  together with the check valve  190  and the shim stack valve  192 . In particular, a lower end of the lower shaft portion  164   c  of the lockout valve  164  includes an external thread for threadedly receiving a nut  196 . 
     According to certain exemplary embodiments, the lockout piston  166  includes a piston portion  166   a  and a shaft portion  166   b . The piston portion  166   a  includes an annular seal or O-ring disposed between its outer peripheral surface and an internal surface of the upper telescopic member  26  to create a seal therebetween. The piston portion  166   a  may include a plurality of main fluid flow ports (e.g., three main fluid flow ports)  166   c , a plurality of blow ports (e.g., six blow ports)  166   d  and a plurality of return ports (e.g., eighteen return ports)  166   e . The main fluid flow ports  166   c  may be arranged about the piston portion  166   a , such as arranged in a circumferential manner around the piston portion  166   a  with each of the areas between the main fluid flow ports  166   c  including, for instance, two blow ports  166   d . The main fluid flow ports  166   c  may be axially arranged and configured to extend between upper and lower axial end faces of the piston portion  166   a . The blow ports  166   d  extend at an angle with respect to a center axis of the lockout piston  166  to enable the blow ports  166   d  to extend between the upper and lower axial end faces of the piston portion  166   a . The return ports  166   e  are arranged, such as in three groups of six ports  166   e  with one of the groups of return ports  166   e  being located radially outward from a corresponding one of main fluid flow ports  166   c . The return ports  166   e  may extend at an angle with respect to a center axis of the lockout piston  166  so that the return ports  166   e  can extend between the lower axial end face of the piston portion  166   a  and one of the main fluid flow ports  166   c.    
     As previously described, the lockout valve  164  prevents fluid from flowing through the damping piston  162  when in a lockout mode; however, when the lockout valve  164  is in one or more non-lockout modes, the axial fluid flow passages  194  enable the fluid flow ports  166   c  of the damping piston  162  to be axially aligned with the fluid flow ports  166   c  of the lockout valve  164 . A flow direction of fluid through the damping piston  162 , the lockout valve  164 , and the lockout piston  166  during compression of the suspension  12  is primarily axially upward when the damping lockout mechanism is in a non-lockout mode. Accordingly, a directional flow of fluid through the damping piston  162 , the lockout valve  164 , and the lockout piston  166  does not reverse its axial direction. Likewise, a directional flow of fluid through the damping piston  162 , the lockout valve  164 , and the lockout piston  166  does not extend in a primarily radial direction at any point through the damping piston  162 , the lockout valve  164 , and the lockout piston  166 . Such a substantially linear (e.g., axial) flow path of fluid through the damping piston  162 , the lockout valve  164 , and the lockout piston  166  effectively prevents unnecessary damping effects from occurring at a flow path through the damping piston  162 , the lockout valve  164 , and the lockout piston  166 . 
     According to exemplary embodiments, the return valve  168  may be disposed between the main body portion  164   a  of the lockout valve  164  and the piston portion  166   a  of the lockout piston  166 . In this manner, the return valve  168  normally closes off the return ports  166   e  of the lockout piston  166  so that fluid does not normally flow through the return ports  166   e  of the lockout piston  166 . According to one implementation, the return valve  168  may include a return valve plate  168   a  and a compression spring  168   b . The return valve plate  168   a  normally abuts a lower end of the lockout piston  166  by the compression spring  168   b  to normally close off the return ports  166   e . It is noted; however, that during rebound of the suspension  12  when in a lockout mode, fluid in the lower internal chamber  184  forces the return valve plate  168   a  away from a lower end of the lockout piston  166  to open the return ports  166   e  and, thereby, enables fluid to flow therethrough. As such, the return valve  168  selectively enables fluid communication between the upper internal chamber  182  and the lower internal chamber  184  through the return ports  166   e  during rebound of the suspension  12 . Furthermore, the return ports  166   e  may serve to bias the lockout piston  166  when the suspension  12  rebounds while in the lockout mode. 
     The blow-off mechanism  170  normally abuts an upper end of the lockout piston  166  to close off the blow ports  166   d . In this manner, the blow-off mechanism  170  may be provided to include a blow-off valve plate  170   a , an abutment plate  170   b  and a compression spring  170   c  disposed between the blow-off valve plate  170   a  and the abutment plate  170   b . The blow-off mechanism  170  selectively permits fluid communication between the upper internal chamber  182  and the lower internal chamber  184  through the blow ports  166   d . During a normal operating mode of the suspension  12 , the blow-off mechanism  170  engages with an upper surface of the lockout piston  166  in order to prevent fluid from flowing through the blow-off mechanism  170 . When in a lockout mode, if the suspension  12  is subjected to a sufficiently large enough force to counteract the compression spring  170   c , the blow-off mechanism  170  may act as a safety valve to permit the suspension  12  to compress. In response to such forces on the suspension  12  when in the aforementioned lockout mode, sufficient aggregation of fluid pressure acting on blow-off mechanism  170  from the lower internal chamber  184  will open the blow ports  166   d  to enable fluid flow through the blow ports  166   d  into the upper internal chamber  182 . 
     According to various embodiments, the shaft portion  166   b  of the lockout piston  166  may be integrally formed with the piston portion  166   a  of the lockout piston  166  as a one-piece, e.g., unitary, member. An upper end of the shaft portion  166   b  of the lockout piston  166  may be threaded to the upper support member  176  so that the lockout piston  166  remains stationary with respect to the upper telescopic member  26 . 
     The first shock absorber unit  22  also includes the free piston  172  axially slidable on the shaft portion  166   b  of the lockout piston  166 . It is noted, however, that the free piston  172  is normally held by fluid pressure within the lower internal chamber  184  against the compression spring  174 . When the suspension  12  is compressed, fluid pressure in the upper internal chamber  182  of the upper telescopic member  26  increases to compress the compression spring  174  such that an area of the upper internal chamber  182  increases. During rebound, fluid pressure in the upper internal chamber  182  of the upper telescopic member  26  decreases and the compression spring  174  moves the free piston  172  back to its normal resting position (or state). According to certain embodiments, the free piston  172  has an annular seal or O-ring disposed between its outer peripheral surface and an internal surface of the upper telescopic member  26  to create a seal therebetween. Also, the free piston  172  may have an inner sealing arrangement between its inner peripheral surface and an outer surface of the shaft portion  166   b  of the lockout piston  166  so as to create a seal therebetween. As such, an uppermost space of the upper telescopic member  26  above the free piston  172  may be isolated from the upper internal chamber  182  of the upper telescopic member  26 . 
     Upper support member  176  includes a stepped center bore with a lower bore portion  176   a  with an internal thread, a middle bore portion  176   b  with an annular seal or O-ring, and an upper bore portion  176   c  having a respectively larger diameter than respective diameters of portions  176   a  and  176   b . Upper support member  176  is threaded into the upper body member  178  so as to be fixed to an upper end of the upper telescopic member  26 . An annular seal or O-ring is disposed between its outer peripheral surface and an internal surface of the upper body member  178  to create a seal therebetween. Also, an annular seal or O-ring can be disposed between its outer peripheral surface and an internal surface of the upper body member  178  to create a seal therebetween. An upper end of the shaft portion  166   b  of the lockout piston  166  is threaded into the lower bore portion  176   a  of the upper support member  176  so as to be fixed to the upper end of the upper telescopic member  26 . In this manner, the upper bore portion  176   c  of the upper support member  176  rotatably supports part of the second actuating member  94 , as will be described in more detail below. 
     According to exemplary embodiments, the upper body member  178  is threaded into an upper end of the upper telescopic member  26  with an annular seal or O-ring disposed between its outer peripheral surface and an internal surface of the upper telescopic member  26  so as to create a seal therebetween. The upper body member  178  has a stepped center bore with a lower bore portion  178   a  including an internal thread, a middle bore portion  178   b  having an internal thread, and an upper bore portion  178   c  having a plurality of indexing recesses. The upper body member  178  also has an annular recess  178   d  in an upper surface with annular recess  178   d  coaxially surrounding the upper bore portion  178   c . A plurality of curved slots (e.g., two curved slots)  178   e  are formed in the upper body member  178  so that the lower bore portion  178   a  can communicate with the annular recess  178   d . It is noted that the curved slots  178   e  may be arcuately shaped slots having center points located on a center axis of the stepped center bore of the upper body member  178 . The upper bore portion  178   c  and the annular recess  178   d  form an upper shaft portion  178   f  having an external thread that threadedly receives the first actuating member  38  therein. 
     The damping force adjustment valve  180  has an upper end coupled to the first actuating member  38  so that operation of the first actuating member  38  causes the damping force adjustment valve  180  to move in an axial direction. For instance, an upper end of the damping force adjustment valve  180  is externally threaded and, thereby, threadedly engaged with an internal thread of the middle bore portion  178   b  of the upper body member  178 . Accordingly, when the first actuating member  38  is rotated, the damping force adjustment valve  180  is also rotated, but the damping force adjustment valve  180  also moves in an axial direction due to engagement of the external thread of the internal thread of the middle bore portion  178   b  of the upper body member  178 . Axial movement of the damping force adjustment valve  180  enables selective adjustment of a fluid flow rate of fluid from the lower internal chamber  184  to the upper internal chamber  182 . As such, a lower tip end of the damping force adjustment valve  180  cooperates with the center bore  164   d  of the lockout valve  164  to form, in essence, a needle valve. 
     In the illustrated embodiment, the first and second actuating members  38  and  94  are capable of mutually exclusive actuation such that the damping force adjustment valve  180  can remain in a set position when the second actuating member  94  is operated (e.g., rotated) between a lockout position (or state) corresponding to a non-damping or lockout mode and an unlocked position (or state) corresponding to a normal damping or operating mode. Furthermore, the first and second actuating members  38  and  94  are both rotatably mounted to the upper body member  178  about a common center axis of the upper telescopic member  26 . In this manner, the first actuating member  38  is disposed within the second actuating member  94  so that the second actuating member  94  can rotate about the first actuating member  38 . 
     According to exemplary embodiments, the first actuating member  38  includes a pulley portion  38   a , a shaft portion  38   b , a spring  38   e , a ball detent  38   d  and an internally threaded cap  38   e . The spring  38   c  and the ball detent  38   d  are located in a radially extending bore of the shaft portion  38   b , such that the ball detent  38   d  is biased against an annular inner surface of the upper body member  178 . An inner surface of the upper body member  178  has a plurality of recesses  178   g  (only two of which are illustrated) that selectively engage with the ball detent  38   b  to provide individual adjustment points for controlling a clamping rate for the adjustment unit  34 . As such, an indexing arrangement is formed by the shaft portion  38   b , the spring  38   c , the ball detent  38   d , and recesses  178   a . The shaft portion  38   b  of the first actuating member  38  has a lower end thereof including a non-circular cross section disposed in a non-circular bore of an upper end of the damping force adjustment valve  180 . The pulley portion  38   a  is fixedly mounted to an upper end of the shaft portion  38   b  of the first actuating member  38  by, for example, a set screw, pin, or other suitable fixing mechanism. In this manner, rotation of the first actuating member  38  causes the damping force adjustment valve  180  to rotate therewith. It is noted that an internally threaded cap  38   e  may be threaded onto the upper body member  178 . When internally threaded cap  38   e  is threaded onto the upper body member  178 , the shaft portion  38   b  of the first actuating member  38  is prevented from moving upwardly such that a lower end of the shaft portion  38   b  can remain disposed within the aforementioned non-circular bore of the upper end of the damping force adjustment valve  180 . Since the pulley portion  38   a  is fixedly mounted to an upper end of the shaft portion  38   b , the internally threaded cap  38   e  may also act to retain the pulley portion  38   a  of the first actuating member  38  to the damping force adjustment valve  180 . 
     In certain exemplary embodiments, the second actuating member  94  includes a portion  94   a  and a control rod  94   b . The portion  94   a  and the control rod  94   b  are interconnected via a plurality of pins  94   c  so that the portion  94   a  and the control rod  94   b  can rotate together as a unit, such as in response to actuation of the control cable  46 . 
     Averting back to  FIG. 6 , a lower damping unit  198 , according to various exemplary embodiments, includes the lower seal member (or damping piston)  126 , the tube (or connecting rod)  128 , a sealing member  200 , and a damping force adjustment valve  202 . It is noted that the lower damping unit  198  becomes immovable in the lockout mode due to the free piston  172  becoming immovable in response to a lock-out operation essentially characterized by a scenario where dampening fluid can no longer flow through the damper adjustment unit  106   a . The lower damping unit  198  may be any suitable damping mechanism and, therefore, is not described or illustrated in any further detail. It is noted, however, that the damping piston  126  is held stationary with respect to the lower portion  28  of the first shock absorber unit  22  and, thereby, slidably contacts internal surface of the upper telescopic member  26 . As previously described, the damping piston  126  includes axially extending the fluid flow ports  134  configured to provide a damping effect. The connecting rod  128  is, in exemplary embodiments, a hollow rod that fixedly attaches the damping piston  126  to a bottom end of the lower portion  28 . In this manner, an interior cavity region  128   a  of the connecting rod  128  is sealed at its upper and lower ends so as to form an air tight chamber. As previously described, the lower seal member  126  forms a seal between an upper end of the connecting rod  128  and the internal surface  130  of the upper telescopic member  26 . The sealing member  200 , however, is held stationary with respect to the lower portion  28  and slidably contacts the internal surface of the upper telescopic member  26 . In this manner, the damping force adjustment valve  202  is disposed in an upper end of the connecting rod  128  in order to regulate a fluid flow rate passing from above the damping piston  126  to the lower cavity  138  below the damping piston  126 . A lower damping control unit  204  is configured and arranged to move the damping force adjustment valve  202  in an axial direction and, thus, to regulate the fluid flow rate. 
       FIGS. 15A-15C  and  16 A- 16 C schematically illustrate processes for controlling the suspension  12  via the control unit  14 , according to exemplary embodiments. It is noted that the previously described components of the suspension  12  are shown in block diagram form in order to avoid unnecessarily obscuring the proceeding description. Referring to  FIGS. 15A-15C  with continued reference to  FIGS. 3-14 , the control unit  14  may be configured to provide three sequential operating modes for the suspension  12 , such as a “long” stroke mode (or mode)  1501  shown in  FIG. 15A , “short” stroke mode (or mode)  1503  shown in  FIG. 15B , and “locked-out” mode (or mode)  1505  shown in  FIG. 15C . It is contemplated, however, that one or more intermediary modes may be provided between modes  1501  and  1503  and/or between modes  1503  and  1505 . 
     In the mode  1501 , the control unit  14  may be in a first state and, as such, a slack  46   e  may be present in a portion  46   d  of the control cable  46 . Accordingly, when the control unit  14  is manipulated (e.g., the lever portion  56  is, for example, pushed) to actuate the suspension adjusting mechanism  36  to the mode  1503 , the pulley  40  will rotate, such as in a clockwise fashion about the rotational axis  50 , such that the slack  46   e  in the portion  46   d  of the control cable  46  will be decreased (or removed) and the biasing member  90  will be stretched as the second anchoring portion  88  of the pulley  40  is rotated away from the anchoring bracket  92 . In this manner, the biasing member  90  will bias the pulley  40  towards the mode  1501 . Accordingly, such rotation of the pulley  40  about the rotational axis  50  drives the shaft  152  of the stroke adjustment unit  150  to shorten a stroke length of the suspension  12 . As such, intermediary modes between the modes  1501  and  1503  may be provided for fine tuning a stroke length between the “long” stroke mode  1501  and the “short” stroke mode  1503 . It is noted that if the control unit  14  is actuated to return the suspension  12  to the mode  1501  from the mode  1503  (e.g., the releasing mechanism  58  is, for instance, depressed), a biasing force of the biasing member  90  will return the pulley  40  to the mode  1501 . 
     According to exemplary embodiments, if the control unit  14  is manipulated to actuate the suspension  12  between the modes  1503  and  1505  (e.g., the lever portion  56  is, for example, pushed further), both of the adjusting mechanisms  34  and  36  will be actuated, e.g., will be rotated, such that both of the pulleys  38  and  40  will be rotated in clockwise fashions about the respective rotational axes  48  and  50 . Subsequently, rotation of the pulley  38  engages the second actuating member  94 , such that both the pulley  38  and the second actuating member  94  will rotate to the mode  1505 . In this manner, rotation of at least the pulley  38  torques the biasing member  96  to effectively bias at least the pulley  38  to the mode  1503 . As such, intermediary modes between the modes  1503  and  1505  may be provided for fine tuning a dampening characteristic of the damper adjustment unit  22 . Accordingly, rotation of the pulley  38  and the second actuating member  94  to the mode  1505  drives the lockout valve  164  to “lockout” the damper adjustment unit  22 . Once the damper adjustment unit  22  is “locked out,” subsequent rotation of the pulley  40  will no longer affect changes to a stroke length of the suspension  12  (that is, until the damper adjustment unit  22  is “unlocked”) while the further rotation of the pulley  40  torques the biasing member  90  to effectively bias the pulley  40  to the mode  1503 . It is noted that if the control unit  14  is actuated (e.g., the releasing mechanism  58  is, for instance, depressed) to return the suspension  12  to the mode  1503  from the mode  1505 , a biasing force of the biasing member  96  will return the pulley  38 , and thereby the actuating member  94  to the mode  1503 . 
     Second Embodiment 
     Referring to  FIGS. 16A-16C , the control unit  14  and the suspension  12  operate as described with respect to  FIGS. 15A-15C ; however, one or more of the biasing members  90  and  96  may be replaced by the biasing member  101 . Accordingly, when the control unit  14  is manipulated to actuate the suspension adjusting mechanism  36  to the mode  1503 , the pulley  40  will rotate, such as in a clockwise fashion about the rotational axis  50 , such that the control cable  46  will slide with respect to the coupling mechanism  84  and the biasing member  101  will be drawn towards and abut against the coupling mechanism  84 . Since a compression spring  103  will resist compounding as the biasing member  101  is drawn towards the coupling mechanism  84 , the biasing member  101  can bias the pulley  40  to the mode  1501  shown in  FIG. 16A . If the control unit  14  is manipulated to actuate the suspension  12  between the modes  1503  shown in  FIG. 16B and 1505  shown in  FIG. 16C  (e.g., the lever portion  56  is, for example, pushed further), both of the adjusting mechanisms  34  and  36  will be actuated, such that both of the pulleys  38  and  40  will be rotated in clockwise fashions about the respective rotational axes  48  and  50 . In this manner, the biasing member  101  will remain abutted against the coupling mechanism  84  while the control cable  46  is kept slid with respect to the coupling mechanism  84  and, in this state (the mode  1503 ), when the control cable  46  is further slid, the biasing member  101  can bias the pulleys  38  and  40 , as well as the actuating member  90  to the mode  1505 . 
     According to certain other embodiments, one or both of the adjustment pulleys  38  and  40  may be biased, respectively, relative to their aforementioned rotational positions via the biasing member  101  coupled to a distal end of the control cable  46  via the compounding spring  103 , as can be seen in  FIGS. 16A-16C . In this manner, as one or more of the adjustment pulleys  38  and  40  are actuated (e.g., rotated) via the control unit  14 , biasing member  101  may be drawn towards and abut against coupling mechanism  84 . Since biasing member  101  will resist compounding as a tension in the control cable  46  increases, biasing member  101  can bias one or more of the adjustment pulleys  38  and  40  to, for instance, one or more of the aforementioned operating states, such as about respective rotational axes  48  and  50 . 
     Third Embodiment 
     According to another embodiment, the damper adjustment unit  24  may be modified to corresponding to a damper adjustment unit  1122 , as seen in  FIGS. 17-19 . In this embodiment, the damper adjustment unit  1122  is used with the suspension  12  by substituting the damper adjustment unit  24 , discussed above, with the damper adjustment unit  1122 . The damper adjustment unit  1122  is identical to the damper adjustment unit  24  of the suspension  12 , except that a modified damping adjustment unit  1106  is used in place of the damper adjustment unit  1122 . As such, the actuating member  38  is utilized to regulate a damping force of the modified damper adjustment unit  1106  and to lockout the modified damper adjustment unit  1106  in a same manner as previously described. In view of these similarities, the components of this embodiment that are identical to the components of the previously described embodiments are given the same reference numerals as the components of the previously described embodiments. Moreover, the descriptions of the components of this embodiment that are identical to the components of the previously described embodiments may be omitted for the sake of brevity. 
     Accordingly, the components of the modified damping adjustment unit  1106  that are different from the damping adjustment units  106   a  and  106   b  include a modified lockout valve  1164 , a modified lockout piston  1166 , a modified return valve  1168 , and a modified blow-off valve  1170 . In this exemplary embodiment, the damping adjustment unit  1106  is axially shorter than the damping adjustment units  106   a  and  106   b  because the modified blow-off valve  1170  utilizes a shim stack that includes a pair of blow-off valve shims  1170   a  with a pair of arcuately shaped preset valve members  1170   b  disposed between the blow-off valve shims  1170   a  (instead of a coil spring in a conventional blow-off valve). A nut  1170   c  holds the blow-off valve shims  1170   a  and the preset valve members  1170   b  in place against the modified lockout piston  1166 . The preset valve members  1170   b  are configured and arranged to change an amount of fluid pressure needed to flex the blow-off valve shims  1170   a  so as to enable fluid to flow through the modified lockout piston  1166 . In this manner, the preset valve members  1170   b  elastically deform the upper one of the blow-off valve shims  1170   a . Because of the use of the modified blow-off valve  1170 , minor changes are also implemented to the modified lockout valve  1164 , the modified lockout piston  1166 , and the modified return valve  1168  with respect to the previously described embodiments. 
     The modified lockout valve  1164  and the modified lockout piston  1166  are essentially the same as the lockout valve  164  and the modified lockout piston  166 , except that the number and arrangements of the ports and passages has changed to accommodate the modified blow-off valve  1170 . For example, as seen in  FIG. 18 , the modified lockout piston  1166  has only two fluid flow passages; however, the overall function and operation of the modified damping adjustment unit  1106  is the same as the damping adjustment units  106   a  and  106   b , as discussed above. 
     As seen in  FIGS. 17-19 , the modified lockout piston  1166  is essentially the same as the lockout piston  166 , except that the modified lockout piston  1166  is a two piece structure and only utilizes a pair of two fluid flow passages. It is noted that the modified lockout piston  1166  basically includes a piston portion  1166   a  and a shaft portion  1166   b  that is separate from the piston portion  1166   a . The piston portion  1166   a  has an annular seal or O-ring disposed between its outer peripheral surface and an internal surface of an upper telescopic member  1126  to create a seal therebetween. In certain embodiments, the piston portion  1166   a  includes two main fluid flow ports  1166   e , a plurality of blow ports  1166   d  (e.g., four blow ports), and a plurality of return ports  1166   e  (e.g., four return ports). Main fluid flow ports  1166   c  are axially arranged and extend between upper and lower axial end faces of the piston portion  1166   a.    
     It is also noted that the adjustment unit  34  may positioned at a top portion of the upper telescopic member  1126  and may be operatively coupled to the lockout valve  164  and the damping force adjustment valve  180 . In this embodiment, however, the actuating members  38  and  94  may rotate about the rotational axis  48  as a single unit and, therefore, the modified lockout value  1164  and the damping force adjustment valve  180  may rotate together. 
     An exemplary operation of the suspension  12  including the modified damper adjustment unit  1122  is described with respect to  FIGS. 20A-1  through  20 C- 2 . In this implementation, one of the biasing members  90  and  96  may not be utilized (however, may be used if desired). As such, the control unit  14  may be configured to provide three operating modes for the suspension  12  including the modified damper adjustment unit  1122 , such as a “long” stroke mode (or mode)  2001  shown in  FIG. 20A-1  and  FIG. 20A-2 , a “short” stroke mode (or mode)  2003  shown in  FIG. 20B-1  and  FIG. 20B-2 , and a “locked-out” mode (or mode)  2005  shown in  FIG. 20C-1  and  FIG. 20C-2 . It is contemplated, however, that one or more intermediary modes may be provided between the modes  2001  and  2003  and/or between the modes  2003  and  2005 . 
     In the mode  2001 , the control unit  14  may be in a first state; however, the portion  46   d  of the control cable  46  is taut between the coupling mechanisms  80  and  84  and the main fluid flow ports  1166   c  are in an open state, as shown in  FIG. 20A-1  and  FIG. 20A-2 . Accordingly, when the control unit  14  is manipulated (e.g., the lever portion  56  is, for example, pushed) to actuate the suspension  12  to the mode  2003 , both of the pulleys  38  and  40  will rotate, such as in a clockwise fashion about the respective rotational axes  48  and  50 . As such, rotation of the pulley  40  about the rotational axis  50  drives the shaft  152  of the stroke adjustment unit  150  to shorten a stroke length of the suspension  12 , whereas the rotation of the pulley  38  drives the modified lockout valve  1164 . It is noted, however, that the main fluid flow ports  1166   c  will remain open despite the driving of the modified lockout valve  1164  to the mode  2003 , as can be seen in  FIG. 20B-1  and  FIG. 20B-2 . It is noted that if the control unit  14  is actuated to return the suspension  12  to the mode  2001  from the mode  2003  (e.g., the releasing mechanism  58  is, for instance, depressed), a biasing force of either biasing member  90  or  96  will return the pulleys  38  and  40  to the mode  2001 . 
     If the control unit  14  is manipulated further to actuate the suspension  12  between the modes  2003  and  2005  (e.g., the lever portion  56  is, for example, pushed further), both of the adjusting mechanisms  34  and  36  will be actuated, e.g., will be rotated, such that the pulleys  38  and  40  will be rotated in clockwise fashions about the respective rotational axes  48  and  50 . At the mode  2005 , however, rotation of the pulley  38  and, thereby, also of the actuating member  94  will drive the modified lockout valve  1164  to “lockout” the damper adjustment unit  1122 . That is, the main fluid flow ports  1166   c  will be closed off, as shown in  FIG. 20C-1  and  FIG. 20C-2 . Once the modified damper adjustment unit  1122  is “locked out,” subsequent rotation of pulley  40  will no longer affect changes to a stroke length of the suspension  12  (that is, until the modified damper adjustment unit  1122  is “unlocked”). As such, if the control unit  14  is actuated (e.g., the releasing mechanism  58  is, for instance, depressed) to return the suspension  12  to the mode  2003  from the mode  2005 , a biasing force of either biasing member  90  or  96  will return the pulley  38  and the actuating member  94  to the mode  2003 . 
     While certain exemplary embodiments and implementations have been described herein, other embodiments and modifications will be apparent from this description. Accordingly, the invention is not limited to such embodiments, but rather to the broader scope of the presented claims and various obvious modifications and equivalent arrangements.