Shock Absorber Assembly and Method

A shock absorber is provided having a cylinder, a piston rod, a piston body, and a valve. The valve also includes a first valve seat formed at least in part by the piston body and a second valve seat formed at least in part by the piston body. The valve includes a first circumferential valving element configured to mate and demate with a first valve seat and a second circumferential valving element having a distal end portion, a proximal end portion, and a medial spring interposed between the distal end portion and the proximal end portion, the distal end portion configured to mate and demate with the second valve seat. A pair of pump pistons are also provided to provide feedback rebound forces to the first and second valving elements through springs. Engagement surfaces are also provided between the first and second valving elements. A method is also provided.

TECHNICAL FIELD

This disclosure pertains to hydraulic or pneumatic shock absorbers and damping and/or shock mitigating valves and mechanisms for mitigation of shock transmission. More particularly, this disclosure relates to shock absorbers and damping and/or shock mitigating valves and control of shock absorber cavity pressures where impact force of a moving object is absorbed by causing a piston to displace hydraulic fluid from a cylinder through metering orifices, sprung bodies, fluid feedback loops and/or valves.

BACKGROUND OF THE INVENTION

Shock absorbers and damping valves have been used on a number of vehicles including automobiles, trucks, motorcycles, and off-road vehicles to dampen shock transmission from a vehicle wheel to a frame or structure. Such shock absorbers and damping valves have also been used on industrial machines and processing equipment to dampen shock transmission between parts or subassemblies. They have also been used on any of a number of various operating mechanisms and machines, including weapons systems and mitigation systems for a pipe fluid shock transmission system. However, certain environments impart a broad range of high speed, large deformation, high speed, small deformation, low speed, large deformation, and low speed, small deformation. Presently used shock absorbers and valve assemblies fail to provide optimal performance across a full spectrum of such shock transmission conditions and further improvements are needed to provide higher order response characteristics and tunability in order to maximize performance, particularly for racing and competition conditions.

SUMMARY OF THE INVENTION

A hydraulic shock absorber and auxiliary hydraulic fluid valve assemblies are provided for tuning and mitigating shock transmission over a broad range of impact speeds, forces, and volumetric fluid displacements for vehicles, machinery, and equipment.

According to one aspect, a shock absorber is provided having a cylinder, a piston rod, a piston body, and a valve. The cylinder is filled with a fluid. The piston rod reciprocates within the cylinder. The valve is carried by the piston body. The valve has at least one flow port through the piston body and communicating with a compression chamber end of the valve body. The valve also includes a first valve seat formed at least in part by the piston body and a second valve seat formed at least in part by the piston body. The valve further includes an annular valve chamber defined in part by the piston body and fluid coupled with the at least one flow port. The valve further includes a first circumferential valving element configured to mate and demate with the first valve seat at a proximal end and having a radially inward extending engagement flange on a proximal end. Additionally the valve includes a second circumferential valving element having a distal end portion, a proximal end portion, and a medial spring interposed between the distal end portion and the proximal end portion, the distal end portion configured to mate and demate with the second valve seat and engage with the proximal end of the first circumferential valving element when the first valving element demates with the first valve seat and the second valve element is mated with the second valve seat. Further, the valve includes a first valve spring configured to urge the first valving element in movable mating and demating relation against the first valve seat. The valve includes a second valve spring configured to urge the second valving element in movable mating and demating relation against the second valve seat, the first valve seat and the second valve seat each respectively demated from the first valve seat and the second valve seat responsive to fluid pressure in the annular valve chamber compressing the first spring and the second spring to provide a first fluid flow path and a second fluid flow path. Finally, the valve includes a housing including an auxiliary reservoir communicating with one of the compression chamber and the rebound chamber and a by-pass passage penetrating an inside of the piston rod in a longitudinal direction of the piston rod, the housing configured to form an auxiliary passage connected to one of the compression chamber and the rebound chamber.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG.1is an exploded and perspective vertical centerline sectional view of a mid-valve piston assembly1022from the inlet end of a shock absorber assembly similar to that shown in FIGS. 62-80 in U.S. Pat. No. 11,448,282, herein incorporated by reference in its entirety. However, certain components of mid-valve piston assembly1022are changed over those shown in FIGS. 62-80 of U.S. Pat. No. 11,448,282. Namely, circumferential outer valving element, or outer circumferential cone piston2114and inner circumferential compound (or frustoconical) valving element, or inner circumferential compound cone piston2112cooperate to provide a modification over that shown in FIGS. 62-80 of U.S. Pat. No. 11,448,282. Specifically, inner circumferential compound cone piston2112forms a distal end portion that cooperates with a proximal end portion, or base flange tube2113and a medial spring stack of cup washers2115and2117interposed between the distal end portion2112and the proximal end portion2113. An inner spring stack1138engages with a proximal radial inward flange end of base flange tube2113to urge base flange tube2113at a distal end with stacked cup washers2115and2117which further engage with a proximal end of inner cone piston2112. Inner cone piston2112and outer cone piston2114move away from a circumferential valve seat on piston1100responsive to hydraulic fluid pressure passing through a mid-valve shock absorber piston1100of a shock absorber10(seeFIG.63). Springs2115,2117and1138serve to urge inner cone piston2112via base flange tube2113into engagement with a circumferential valve seat on piston1100. Hydraulic fluid pressure from a distal side of piston1100can urge inner cone piston2112away from piston1100to open up a circumferential inner fluid flow path, while outer cone piston2114can be urged away from piston1100to compress outer spring stack1140and open up a circumferential outer fluid flow path with a circumferential valve seat of piston1100. A ducted support housing1142stacks and seats with piston1100. Inner spring stack1138and outer spring stack1140are supported circumferentially about piston rod, or shaft1020. A piston band seal1102(and an o-ring seal) are provided about an outer periphery of piston1100to form a sliding seal within an inner cylindrical wall of a shock absorber tube.

A female rebound tube1080is threaded within a female bore of shaft1020, as shown inFIG.1. A rebound nut assembly then threads atop a male thread on shaft1020. A nut1066affixes a stop plate1067, a spring1092and a check valve washer1090onto and against rebound nut assembly1084. A threaded rebound needle1042is threaded coaxially within shaft102for axial adjustable positioning. A shaft spacer2131and a base cup2133are each made from heat treated steel. A circumferential o-ring retainer2135of anodized aluminum is configured to prevent an associated o-ring from being sucked, or pulled onto shaft1020. An outer pump piston1112is slidably received in a cylindrical housing1128to act against spring1140responsive to rebound hydraulic fluid within a shock absorber. Likewise, an inner pump piston1114is slidably received within cylindrical housing1128to slide along shaft1020to act against spring1138responsive to rebound hydraulic fluid within a shock absorber. Pump piston1112includes a circumferential piston band seal1113(and o-ring seal). A collar1068having a radially inwardly extending array of fingers1069entraps collar1068on shaft1020such that nut1084entraps all associated components of mid-valve piston assembly1022in assembly between nut1084and collar1068.

FIG.3is a vertical centerline sectional view of the mid-valve piston assembly1022taken along line3-3ofFIG.2showing one pair of rebound ports1094. A rebound shim stack assembly1098of individual spring steel shims are urged against piston1100to cover rebound ports1094by a spacer ring1078and rebound nut assembly1084. Assembly1098in operation flexes to allow fluid to rebound through rebound ports1094back to the compression chamber of a shock absorber. Cylindrical housing1128is affixed on shaft1020to engage support housing1142against piston1100in assembly. A rubber or plastic cylindrical bump stop1056is provided on shaft1020typically spaced from housing1128. A threaded rebound needle1042is threaded to axially position within shaft1020to control fluid flow. Shaft1020is shown in simplified form with a right end shown in shortened form, but would be longer in actual applications and could be shown in breakaway to indicate a longer shaft1020as shown inFIG.63.

FIG.5is a compound sectional view of the mid-valve piston assembly1022taking along line5-5ofFIG.4showing both a compression port1096and a rebound port1094in piston1100. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.7is a compound sectional view of the mid-valve piston1022ofFIGS.1-3taken along line7-7ofFIG.6showing both a compression port1096and the mid-valve piston1100at a static state and a rebound port1094at a static state showing a rebound needle1042(within shaft1020) with a position adjustment change from that ofFIG.55depicting the needle1042in a more open position than that ofFIG.55. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.8is an enlarged sectional view of a mated inner valve seat2188and a piston surface2192taken from encircled region8ofFIG.7. More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192sprung into a closed position against seat2188restricting any shock absorber fluid flow therebetween.

FIG.9is an enlarged sectional view of a mated outer circumferential valve seat2190and piston surface2194taken from encircled region9ofFIG.7. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194sprung into a closed position against seat2190restricting any shock absorber fluid flow therebetween.

FIG.10is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region10ofFIG.7. A gap is provided between flange2119and stop1143corresponding with the closed position of the outer circumferential valving element.

FIG.11is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region11ofFIG.7showing springs2115and2117sprung apart.

FIG.12is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region12ofFIG.7corresponding with the closed position of the outer circumferential valving element.

FIG.13is an enlarged sectional view of an open position for rebound needle1042taken from encircled region13ofFIG.7.

FIG.15is a compound sectional view of the mid-valve piston assembly1022ofFIGS.1-13taken along line15-15ofFIG.14showing both a compression port1964and a rebound port1094at a later state than shown inFIG.7with more fluid flow at a later point in time. Rebound needle1042(within shaft1020) is shown with a position adjustment change from that ofFIG.55depicting the needle1042in a more open position than that ofFIG.55. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.16is an enlarged sectional view of a mated inner valve seat2188and a piston surface2192taken from encircled region16ofFIG.15. More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192sprung into a closed position against seat2188restricting any shock absorber fluid flow therebetween.

FIG.17is an enlarged sectional view of a mated outer circumferential valve seat2190and piston surface2194taken from encircled region17ofFIG.15. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194urged (against spring forces) into a partially open position against seat2190providing a circumferential pathway2182for shock absorber fluid flow therebetween.

FIG.18is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region18ofFIG.15. A reduced size gap is provided between flange2119and stop1143corresponding with the partially open position of the outer circumferential valving element.

FIG.19is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region19ofFIG.15showing springs2115and2117sprung apart.

FIG.20is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region20ofFIG.15corresponding with the partially open position of the outer circumferential valving element with flange2171bottomed out, or engaged with shelf2173.

FIG.21is an enlarged sectional view of an open position for rebound needle1042taken from encircled region21ofFIG.15.

FIG.23is a compound sectional view of the mid-valve piston assembly1022ofFIGS.1-21taken along line23-23ofFIG.22showing both a compression port1096and a rebound port1094at a later state than shown inFIG.15with yet even more fluid flow and the initiation of pump piston movement to initiate shutting of the outer conical piston. Rebound needle1042(within shaft1020) is shown with a position adjustment change from that ofFIG.55depicting the needle1042in a more open position than that ofFIG.55. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.24is an enlarged sectional view of an open and demated inner valve seat2188and a piston surface2192taken from encircled region24ofFIG.23forming a circumferential fluid flow path2186. More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192urged against spring forces into an open position relative to seat2188providing a fluid flow pathway2186for shock absorber fluid flow therebetween.

FIG.25is an enlarged sectional view of a demated outer circumferential valve seat2190and piston surface2194taken from encircled region25ofFIG.23providing a further enlarged circumferential fluid flow pathway2182over that shown inFIG.17. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194urged (against spring forces) into a further open position against seat2190providing a circumferential pathway2182for shock absorber fluid flow therebetween.

FIG.26is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region26ofFIG.23. A completely closed gap is provided between flange2119and stop1143corresponding with the further open position of the outer circumferential valving element.

FIG.27is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region27ofFIG.23showing springs2115and2117sprung apart.

FIG.28is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region28ofFIG.23corresponding with the further open position of the outer circumferential valving element with flange2171bottomed out, or engaged with shelf2173.

FIG.29is an enlarged sectional view of an open position for rebound needle1042taken from encircled region29ofFIG.23.

FIG.31is a compound sectional view of the mid-valve piston assembly1022ofFIGS.1-29taken along line31-31ofFIG.30showing both a compression port1096and a rebound port1094at a later state than shown inFIG.23with fluid flow restriction where the outer conical piston is closed. Rebound needle1042(within shaft1020) is shown with a position adjustment change from that ofFIG.55depicting the needle1042in a more open position than that ofFIG.55. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.32is an enlarged sectional view of an open and demated inner valve seat2188and a piston surface2192taken from encircled region32ofFIG.31forming a circumferential fluid flow path2186. More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192urged against spring forces into an open position relative to seat2188providing a fluid flow pathway2186for shock absorber fluid flow therebetween.

FIG.33is an enlarged sectional view of a closed, or mated outer circumferential valve seat2190and piston surface2194taken from encircled region33ofFIG.31providing a no circumferential fluid flow pathway2182over that shown inFIG.17. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194urged (against spring forces) into a closed, or mated position against seat2190providing a closed circumferential pathway2182for shock absorber with no fluid flow therebetween.

FIG.34is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region34ofFIG.31. A completely open gap is provided between flange2119and stop1143corresponding with the open position of the outer circumferential valving element.

FIG.35is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region35ofFIG.31showing springs2115and2117urged together into a completely closed, or stacked position.

FIG.36is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region36ofFIG.31corresponding with the open position of the outer circumferential valving element with flange2171bottomed out, or engaged with shelf2173.

FIG.37is an enlarged sectional view of an open position for rebound needle1042taken from encircled region37ofFIG.31.

FIG.39is a compound sectional view of the mid-valve piston assembly1022ofFIGS.1-37taken along line39-39ofFIG.38showing both a compression port1096and a rebound port1094at a later state than shown inFIG.31with fluid flow restriction allowing bypass where the outer conical piston body is opening again in response to a threshold excessive force. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.40is an enlarged sectional view of an open and demated inner valve seat2188and a piston surface2192taken from encircled region40ofFIG.39forming a circumferential fluid flow path2186. More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192urged against spring forces into an open position relative to seat2188providing a fluid flow pathway2186for shock absorber fluid flow therebetween.

FIG.41is an enlarged sectional view of an open, or demated outer circumferential valve seat2190and piston surface2194taken from encircled region41ofFIG.39providing a demated circumferential fluid flow pathway2182. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194urged (against spring forces) into an open position relative to seat2190providing a circumferential pathway2182for shock absorber fluid flow therebetween.

FIG.42is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region42ofFIG.39. A completely closed gap is provided between flange2119and stop1143as they are in contact, corresponding with the open position of the outer circumferential valving element.

FIG.43is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region43ofFIG.39showing springs2115and2117spaced apart in a completely open or uncompressed position.

FIG.44is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region44ofFIG.39corresponding with the open position of the outer circumferential valving element with flange2171bottomed out, or engaged with shelf2173.

FIG.45is an enlarged sectional view of an open position for rebound needle1042taken from encircled region45ofFIG.39.

FIG.47is a compound sectional view of the mid-valve piston assembly ofFIGS.1-45taken along line47-47ofFIG.46showing both a compression port1096and a rebound port1094at a later state than shown inFIG.39with a perspective in a rebound fluid flow direction causing the rebound flapper valve stack (not shown) to move to an open flow position in response to a rebound stroke. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.48is an enlarged sectional view of a closed, or mated inner valve seat2188and a piston surface2192taken from encircled region48ofFIG.47forming a closed circumferential fluid flow path2186(seeFIG.40). More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192urged by spring forces into engagement with seat2188and providing no fluid flow pathway for shock absorber fluid flow therebetween.

FIG.49is an enlarged sectional view of a closed, or mated outer circumferential valve seat2190and piston surface2194taken from encircled region49ofFIG.47providing a closed, or mated circumferential fluid flow pathway. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194urged into contact with seat2190providing no circumferential pathway for shock absorber fluid flow therebetween.

FIG.50is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region50ofFIG.47. A completely open gap is provided between flange2119and stop1143as they are spaced apart, corresponding with the closed position of the outer circumferential valving element.

FIG.51is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region51ofFIG.47showing springs2115and2117spaced apart in a completely open or uncompressed position.

FIG.52is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region52ofFIG.47corresponding with the closed position of the outer circumferential valving element with flange2171spaced apart from shelf2173.

FIG.53is an enlarged sectional view of an open position for rebound needle1042taken from encircled region53ofFIG.47.

FIG.55is a compound sectional view of the mid-valve piston assembly1022ofFIGS.1-53taken along line55-55ofFIG.54showing both a compression port1096and the mid-valve piston1100at a static state and a rebound port1094at a static state showing a rebound needle1042of within shaft1020in a position adjustment changed from that ofFIG.47depicting the needle1042positioned in a more, or nearly closed position than that ofFIG.47and a rebound port1094at a later state than shown inFIG.47with fluid flow restriction allowing bypass where the outer conical piston is opening again in response to a threshold excessive force. The shim stack assembly1098ofFIG.3has been omitted to simplify the view. Bump stop1056, housing1128, support housing1142, nut1084, shaft1020and rebound needle1042are as shown and described inFIG.3.

FIG.56is an enlarged sectional view of a closed, or mated inner valve seat2188and a piston surface2192taken from encircled region56ofFIG.55forming a closed circumferential fluid flow path2186(seeFIG.40). More particularly, inner circumferential valve seat2188is shown with circumferential piston, or valving element2192urged by spring forces into engagement with seat2188and providing no fluid flow pathway for shock absorber fluid flow therebetween.

FIG.57is an enlarged sectional view of a closed, or mated outer circumferential valve seat2190and piston surface2194taken from encircled region57ofFIG.55providing a closed, or mated circumferential fluid flow pathway. More particularly, outer circumferential valve seat2190is shown with circumferential piston, or valving element2194urged into contact with seat2190providing no circumferential pathway for shock absorber fluid flow therebetween.

FIG.58is an enlarged sectional view of an outer valving element outer end stop rim flange2119and circumferential shelf1143taken from encircled region58ofFIG.55. A completely open gap is provided between flange2119and stop1143as they are spaced apart, corresponding with the closed position of the outer circumferential valving element.

FIG.59is an enlarged sectional view of opposed conical springs, or Belleville washers2115and2117taken from encircled region59ofFIG.55showing springs2115and2117spaced apart in a completely open or uncompressed position.

FIG.60is an enlarged sectional view of an outer valving element inner end stop rim flange2171and a circumferential shelf2173taken from encircled region60ofFIG.55corresponding with the closed position of the outer circumferential valving element with flange2171spaced apart from shelf2173.

FIG.61is an enlarged sectional view of an open position for rebound needle1042taken from encircled region61ofFIG.55.

FIG.62is a simplified partial component view showing the circumferential outer valving element, or outer circumferential cone piston2114and the inner circumferential compound valving element, or inner circumferential compound cone piston2112. Cone piston2112forms a distal end component of a compressible two component member having an intermediate spring. More particularly, a pair of cone washers, or springs2115and2117are stacked between distal cone piston tube2121and proximal base flange tube2113to form cone piston2112. Base flange tube2113has a radially outwardly extending proximal flange2173that engages on a proximal side with spring stack1138and on a distal side with a proximal end of outer cone piston1114, save for a gap, “G” that delays engagement as outer cone piston2114is moved to an open position in a proximal direction away from the mid-valve piston (not shown). Outer valving element outer end stop rim flange2119also acts as a motion stop, as discussed previously above. Flange2173can engage with flange2171of outer circumferential compound cone piston2114along circumferential surfaces2175and2177which causes both springs1138and1140to act on piston2114to urge it closed when gap “G” is closed. Outer pump piston1112and inner pump piston1114receive pressure from hydraulic fluid in a rebound chamber to further urge springs1138and1140into outer cone piston2114and inner cone piston2112, respectively. Under lower hydraulic pressure through the mid-valve piston, outer spring stack1140engages outer cone piston2114along circumferential piston surface2194with an outer circumferential valve seat2190on the mid-valve piston1100(seeFIG.7). Inner spring stack1138engages inner cone piston2112along circumferential piston surface2192with inner circumferential valve seat2188on mid-valve piston1100(seeFIG.7). Inner cone piston2112and outer cone piston2114each form a valving element.

FIG.62is a simplified partial component view showing the circumferential outer valving element which is explained in greater detail above with reference toFIG.31in a compressing and closing state wherein one version provides that elements are compounded to allow for spring and action from one direction of valve seat demating and from another aspect to mate and provide compound spring activity when closing. A first part ofFIG.62is from a demate perspective articulation. Now from a compound mating spring compression aspect, an outer circumferential cone piston2114is supported by spring pressure created via slidable piston1112moving towards the spring1140and compressing the outer elements to seat more firmly with a more robust force of the spring1140imparting tension with compressing action of the outer spring creating a tighter seat pressure against the primary mid-valve piston1100valve element (not shown). SeeFIG.31. Outer piston valve element1112independently slides coaxially over inner piston valve element shown inFIG.31as well as with inner valving piston element separately working to allow for individual acting leverages due to leverage ratios of larger diameter leverage force of piston element1112and lesser leverage by a lesser leverage area volume size of inner piston element1114. According to one construction, a unique spring deign1140is a wave spring which is developed to work similarly with rates or has the ability to overcome the standard rate challenge of larger diameter springs using more wire as a smaller diameter spring. A wave spring1138and1140has many waves on each coil constructed between coils to make rates to a needed value that will not be affected by a diameter size of the spring. As outer circumferential valving element has a larger sealing edge, it also will take advantage of a compounding spring rate from springs1138and1140when they work together during the ratio of combined pumping piston action from the chamber being filled with fluid to expand the chamber cylinder and press on the spring1138and1140. As stated previously. pistons1114and1112cooperate with elements of the chamber volume and work with leverage proportion, the springs1138and1140and the inner and outer sprung circumferential valving elements2114and2112work independently to close or compress the circumferential valve seats2112and2114against the piston1100to close off or stiffen fluid travel through the piston compression ports1094and annular piston chamber1116during a compression stroke of the shock absorber. With the momentum and the power of the spring1138and1140, tension increases and the springs compress the cup washers, or cone springs2115and2117at a rate wherein the gap “G” will lessen and eventually the base flange tube will engage against the outer circumferential piston2114. Along an end opposite the seat end and with connection, the inner circumferential valving element2112and the outer circumferential valving element2114both will have existing tension of spring force from individual spring elements1138and1140. After the base flange tube connects, closing the gap, “G” both springs1138and1140become united and work together to extend/increase/power up spring work force power to favor/direct/add to the outer circumferential valving element2114. This will modify the sprung force of one/each spring rate to combine the springs1138and1140during the compressing/shortening of springs2115and2117. This will impart increased spring rate to close both circumferential valving elements2114and2112more forcibly with only extra/more/connected (double sprung) power only being directed to the outer circumferential valving element2114. Inner circumferential valving element2112will retain only the rates of inner spring1138and cone washers2115and2117even under full compression of the two other springs1138and1140. Importantly until the gap “G” is completely used up, outer seat2114has the ability to act with only the outer spring1140up until it opens far enough to close gap “G” and is stiffened. The pumping action can also eat up the gap “G” and dual the ratio to the “outer” circumferential seat2114. Gap “G” works in both directions. All of the springs can be tuned to a desired ratio.

FIG.63is a perspective view from above of an exemplary hydraulic shock absorber10having a primary mid-valve piston assembly1022ofFIGS.1-62and a secondary pair of adjustable auxiliary hydraulic fluid valves30and32. Shock absorber10includes a main cylindrical shock tube, or cylinder12containing a primary mid-valve piston1022carried for movement within an internal cylindrical bore between a compression chamber and a rebound chamber within tube12. Tube12has an end cap28that forms an adjuster and reservoir end cap assembly16that includes and supports secondary pair of primary and secondary adjustable auxiliary hydraulic fluid valves30and32within bridge end cap, or body28. Although not shown, a dust cap and a seal head assembly are provided along a bottom end of cylinder12and provide support for shaft1020during reciprocation relative to cylinder12. Each fluid valve30and32communicates in fluid relation with a piston and reservoir assembly34. Shock absorber assembly10is installed between articulating components of a suspension or shock absorbing mechanism, such as a vehicle suspension, using a busing and bolt (not shown) through a top-most bushing17and a bolt and busing (not shown) that extends through bottom-most clevis18. Clevis18is affixed to a bottom end of a reciprocating piston rod assembly14including shaft, or rod1020. Other alternative mounting configurations, constructions and orientations are also possible for shock10.

Operating components of the primary structural elements depicted inFIGS.1-63can be constructed from aluminum, anodized aluminum, steel and hardened steel. Other suitable materials can include composite materials and plastics or rubbers.

In compliance with the statute, embodiments of the invention have been described in language more or less specific as to structural and methodical features. It is to be understood, however, that the entire invention is not limited to the specific features and/or embodiments shown and/or described, since the disclosed embodiments comprise forms of putting the invention into effect. The invention is, therefore, claimed in any of its forms or modifications within the proper scope of the appended claims appropriately interpreted in accordance with the doctrine of equivalents.