WO2019246440A1

WO2019246440A1 - Shock absorber assembly

Info

Publication number: WO2019246440A1
Application number: PCT/US2019/038312
Authority: WO
Inventors: Peter Russell
Original assignee: N10Z Performance Shocks LLC
Priority date: 2018-06-20
Filing date: 2019-06-20
Publication date: 2019-12-26
Also published as: US20230013721A1; EP3810956A4; US20230003274A1; US11448282B2; EP3810956A1; US20190390730A1; US11913519B2

Abstract

A shock absorber is provided having a cylinder, a piston rod, a piston body, and a valve. The cylinder is configured to receive fluid. The piston body is connected to the piston rod and is configured to reciprocate within the cylinder between a compression chamber and a rebound chamber. The valve is provided by the piston body having a fluid flow port, a valve seat, a circumferential valving element, and a spring configured to urge the valve body into the valve seat. A primary damping valve and an auxiliary damping valve are also provided.

Description

DESCRIPTION

SHOCK ABSORBER ASSEMBLY

CROSS REFERENCE TO RELATED APPLICATION

This application claims priority to U.S. Provisional Patent Application Serial No. 62/687,708, entitled“Shock Absorber

Assembly”, which was filed on June 20, 201 8, the entirety of which is incorporated by reference herein. TECHNICAL FIELD

This disclosure pertains to a 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 mechanism 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, a valve, and a housing. The cylinder is filled with a fluid. The piston rod reciprocates within the cylinder. The valve is carried by the piston body having: at least one flow port through the piston body and communicating with a

compression chamber end of the valve body; a first valve seat formed at least in part by the piston body; a second valve seat formed at least in part by the piston body; an annular valve chamber defined in part by the piston body and fluid coupled with the at least one flow port; at least one circumferential valving element configured to mate and demate with the first valve seat and the second valve seat; and at least one spring configured to urge the at least one valving element in movable mating and demating relation against the first valve seat and the second valve seat, the at least one valve seat demated from the first valve seat and the second valve seat responsive to fluid pressure in the annular valve chamber compressing the at least one spring to provide a first fluid flow path and a second fluid flow path at least one of radially inwardly and outwardly of the first fluid flow path, and forming a first fluid flow path with a first flow diversion angle and a second fluid flow path with a second flow diversion angle less than the first flow diversion angle. The housing includes 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.

According to another aspect, a shock absorber piston is provided having a piston body and a valve. The valve is carried by the piston body having: at least one flow port through the piston body and communicating with a compression chamber end of the valve body; an annular volumetric expansion chamber defined i n part by the piston body and fluid coupled with the at least one flow port; a first annular valve seat carried by the piston body proximate the annular volumetric expansion chamber; a second annular valve seat carried by the piston body proximate the annular volumetric expansion chamber; at least one valving element configured to mate and demate with the first valve seat and the second valve seat; and at least one spring configured to urge the at least one valving element in mating and demating relation against the first valve seat and the second valve seat, the at least one valving element demated from the first valve seat and the second valve seat responsive to fluid pressure in the annular volumetric expansion chamber to compress the at least one spring and provide a first fluid flow path having a first flow diversion angle and a second fluid flow path with a second flow diversion angle less than the first flow diversion angle.

According to yet another aspect, a shock absorber valve is provided having a valve body, an outer piston, an inner piston, a spring, a compression fluid passage, and a rebound fluid passage.

The valve body has an axial bore forming an annular valve seat at one end. The outer piston is carried in the axial bore having an inner axial bore opposite the valve seat. The inner piston slidably received in the axial bore of the outer piston and cooperati ng with the outer piston axial bore to define a variable volume reservoir. The spring is seated against the inner piston to urge the inner piston and the outer piston biased towards the annular valve seat. The compression fluid passage extends from proximate the valve seat through the outer piston to the variable volume reservoir. The rebound fluid passage has a one-way check valve extending from the variable volume reservoir through the outer piston proximate the valve seat.

According to even another aspect, an auxiliary damping valve for a shock absorber is provided having a valve body, a freely reciprocating first piston , a biased second piston, a spring, and a fluid flow passage. The valve body has a hydraulic cylinder. The freely reciprocating first piston is movable axially withi n the cylinder. The biased second piston is provided in the cylinder adjacent the first piston defining an expansible fluid chamber between the first piston and the second piston . The spring is disposed between the second piston and one end of the cylinder configured to u rge the second piston towards the expansible fluid chamber. The fluid flow passage extends from a compression chamber of a shock absorber into the expansible fluid chamber to provide a sprung fluid capacitive storage for the shock absorber.

BRIEF DESCRI PTION OF THE DRAWINGS

Preferred embodiments of the disclosure are described below with reference to the following accompanying drawings.

FIG. 1 is a perspective view from above of an exemplary hydraulic shock absorber having a primary mid-valve piston assembly and a secondary pair of adjustable auxiliary hydraulic fluid valves.

FIG. 1 A is a compound sectional and perspective view from above of the hydraulic shock absorber shown in FIG. 1 taken along line 1 A-1 A of FIG. 1 in a centerline sectional view through the main body and the auxiliary body cylindrical components.

FIG. 2 is an enlarged partial and compound sectional and perspective view of the shock absorber rotated counter-clockwise from that shown in FIG. 1 . FIG. 3 is an enlarged partial and compound sectional and perspective view of the sectioned shock absorber as shown in FIG. 1 .

FIG. 4 is an enlarged partial sectional and perspective view of the sectioned shock absorber as shown in FIG. 3, but from a higher perspective angle above.

FIG. 4A is an enlarged view of a fluid reservoir communication port between the adjusters from the encircled region of FIG. 4.

FIG. 5 is an enlarged component sectional perspective view from above of the mid-valve piston assembly showing the

compression bleed rebound seal in a sealed closed position and showi ng the inner piston and the outer piston in an open position for the shock absorber of FIGS. 1 and 1 A.

FIG. 5A is an enlarged view of a compression bleed rebound seal taken from encircled region 5A of FIG. 5. FIG. 6 is a midline vertical centerline sectional and exploded perspective view of the mid-valve piston assembly of FIG. 5.

FIG. 7 is an exploded perspective view from the rebound end of the mid valve piston of FIG. 6.

FIG. 8 is an exploded perspective view from the compression end of the mid-valve piston assembly of FIG . 6.

FIG. 9 is an exploded perspective view taken from the rebound end of the mid-valve piston assembly of FIG . 6 showing an opposed side depicted in FIG. 7.

FIG. 1 0 is an exploded perspective view taken from the compression chamber end of the mid-valve piston assembly of FIG. 6 showi ng an opposed side depicted in FIG. 8.

FIG. 11 is an end view of the mid-valve piston assembly taken from the compression end. FIG. 1 2 is a compound sectional view of the mid-valve piston assembly taken along compound line 1 2-1 2 of FIG. 1 1 .

FIG. 1 3 is an end view of the mid-valve piston assembly taken from the compression end.

FIG. 14 is a compound sectional view of the mid-valve piston assembly taken along compound line 1 4-1 4 of FIG. 1 3.

FIG. 14A is an enlarged encircled region 14A from FIG. 1 4 showi ng a gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 14B is a gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 14B from FIG . 14.

FIG. 14C is a gap between an inner shelf of the outer piston and an outer shelf of the inner piston from the enlarged encircled region 1 4C from FIG. 1 4.

FIG. 1 5 is a compound sectional view of the mid-valve piston assembly taken along compound line 1 5-1 5 of FIG. 1 3.

FIG. 1 5A is an enlarged encircled region 1 5A from FIG. 1 5 showi ng a closed gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 1 5B is a gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 1 5B from FIG . 1 5.

FIG. 1 5C is a partially smaller gap between an inner shelf of the outer piston and an outer shelf of the inner piston than depicted in FIG. 14C from the enlarged encircled region 1 5C from FIG. 1 5.

FIG. 1 6 is a compound sectional view of the mid-valve piston assembly taken along compound line 1 6-1 6 of FIG. 1 3. FIG. 16A is an enlarged encircled region 16A from FIG.16 showing a closed gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 16B is a gap between a rear edge of the inner piston and a forward surface of the stop plate similar in size to that shown in FIG. 15B from the enlarged encircled region 16B from FIG.16.

FIG. 16C is a closed gap between an inner shelf of the outer piston and an outer shelf of the inner piston than depicted in FIG. 15C from the enlarged encircled region 16C from FIG.16.

FIG. 17 is a compound sectional view of the mid-valve piston assembly taken along compound line 17-17 of FIG.13.

FIG. 17A is an enlarged encircled region 17A from FIG.17 showing a closed gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 17B is a closed gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 17B from FIG.17.

FIG. 17C is a closed gap between an inner shelf of the outer piston and an outer shelf of the inner piston than depicted in FIG. 16C from the enlarged encircled region 17C from FIG.17.

FIG. 17D is an unseated o-ring in a circumferential channel within an inner wall of the outer piston from the encircled region 17D of FIG.17.

FIG. 18 is a compound sectional view of the mid-valve piston assembly taken along compound line 18-18 of FIG.13.

FIG. 18A is a seated o-ring in a circumferential channel within an inner wall of the outer piston from the encircled region 18A of FIG. FIG. 1 8B is a circumferential gap between the inner piston and the outer piston shown in the enlarged encircled region 1 8B of FIG. 1 8.

FIG. 1 9 is a compound sectional view of the mid-valve piston assembly with the inner piston and the outer piston in a closed position and compression bleed rebound o-ring seal closed and taken along compound line 19- 1 9 of FIG. 1 3.

FIG. 1 9A is an enlarged encircled region from FIG. 1 9 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 20 is a compound sectional view of the mid-valve piston assembly with the inner piston and the outer piston in a closed position and compression bleed rebound o-ring seal open and taken along compound line 20-20 of FIG. 1 3. FIG. 20A is an enlarged encircled region from FIG. 20 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 21 is a compound sectional view of the mid-valve piston assembly taken along compound line 21 -21 of FIG. 1 3. FIG. 21 A is an enlarged encircled region from FIG. 21 of the outer piston moved slightly open than that of FIG. 20.

FIG. 22 is a compound sectional view of the mid-valve piston assembly showing a fully open inner piston and outer piston and o- ring in an open position taken along compound line 22-22 of FIG. 1 3. FIG. 22A is an enlarged encircled region from FIG. 22.

FIG. 23 is an end view of the mid-valve piston assembly taken from the compression end.

FIG. 24 is a compound sectional view of the mid-valve piston assembly with the outer piston partially open and the inner piston closed with the o-ring in an open position taken along compound line 24-24 of FIG. 23.

FIG. 24A is an enlarged encircled region from FIG. 24 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 24B is an enlarged encircled region 24B from FIG. 24A showi ng a gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 24C is a gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 24C from FIG. 24A.

FIG. 24D is a gap between an inner shelf of the outer piston and an outer shelf of the inner piston from the enlarged encircled region 24D from FIG. 24A.

FIG. 25 is an end view of the mid-valve piston assembly from the compression end.

FIG. 26 is a compound sectional view of the mid-valve piston assembly taken along compound line 26-26 of FIG. 25.

FIG. 26A is an enlarged encircled region from FIG. 26 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 26B is an enlarged encircled region 26B from FIG. 26A showi ng a gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 26C is a gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 26C from FIG. 26A. FIG. 26D is a gap between an inner shelf of the outer piston and an outer shelf of the inner piston from the enlarged encircled region 26D from FIG. 26A.

FIG. 27 is an end view of the mid-valve piston assembly from the compression end.

FIG. 28 is a compound sectional view of the mid-valve piston assembly taken along compound line 28-28 of FIG. 27.

FIG. 28A is an enlarged encircled region from FIG. 28 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 28B is an enlarged encircled region 28B from FIG. 28A showi ng a gap between a rear edge of the outer piston and a forward surface of the stack plate.

FIG. 28C is a gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 28C from FIG. 28A.

FIG. 28D is a gap between an inner shelf of the outer piston and an outer shelf of the inner piston from the enlarged encircled region 28D from FIG. 28A.

FIG. 29 is an end view of the mid-valve piston assembly from the compression end.

FIG. 30 is a compound sectional view of the mid-valve piston assembly taken along compound line 30-30 of FIG. 29.

FIG. 30A is an enlarged encircled region from FIG. 30 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 30B is an enlarged encircled region 30B from FIG. 30A showi ng a gap between a rear edge of the outer piston and a forward surface of the stack plate. FIG. 30C is a gap between a rear edge of the inner piston and a forward surface of the stop plate from the enlarged encircled region 30C from FIG. 30A.

FIG. 30D is a gap between an inner shelf of the outer piston and an outer shelf of the inner piston from the enlarged encircled region 30D from FIG. 30A.

FIG. 31 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly for the shock absorber of FIG. 1 showing the compression bleed rebound seal in a rebound closed position and further showing the inner piston and the outer piston in a closed position .

FIG. 31 A is an enlarged view of encircled region 31 A from FIG. 31 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 32 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly of FIG.

31 showing the compression bleed rebound seal in an open flow position and showing the inner piston and outer piston in an open position.

FIG. 32A is an enlarged view of encircled region 32A from FIG.

32 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 33 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly of FIG. 31 showing the compression bleed rebound seal in a compression open flow position and showing the inner piston in a closed position and the outer piston in an intermediate open position.

FIG. 33A is an enlarged view of encircled region 33A from FIG.

33 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal. FIG. 34 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly for the shock absorber of FIG. 1 showing the compression bleed rebound seal in a rebound open position and showing the inner piston and the outer piston both in a closed position .

FIG. 34A is an enlarged view of encircled region 34A from FIG. 34 of the inner and outer piston for the mid-valve piston assembly and the compression bleed rebound o-ring seal.

FIG. 35 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in centerline section in FIGS. 1 -3 depicting the valve at a shock u nloaded state before receiving any auxiliary fluid from the shock with the pump piston sprung to the right.

FIG. 36 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the valve at a shock loaded state showing a movement of the adjuster clicker screw to more open position depicted in FIG. 35 beginning to receive auxiliary fluid from the shock with the pump piston sprung to the right and the conical piston body moving to the left and opening a frustoconical flow path .

FIG. 37 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the valve at a shock loaded state further receiving auxiliary fluid from the shock than that depicted in FIG. 36 with the pump piston moving to the left against the stacked springs as the pumping chamber expands and the cone body moved right to close the frustoconical flow path.

FIG. 38 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the conical piston body more tightly closed and the pump piston urged further leftward against the stacked springs than depicted in FIG. 37. FIGS. 38A and 38B show respectively a displaced return flow shim stack and a return check valve washer from encircled regions 38A and 38B of FIG. 38.

FIG. 39 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the conical piston body closed and the pump piston urged further leftward against the stacked springs than in FIG. 37 and the check valve is in an open state showing a paused state of compression and rebound.

FIGS. 39A and 39B show respectively a closed return flow shim stack and an open return check valve washer from encircled regions 39A and 39B of FIG. 39.

FIG. 40 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting all hydraulic fluid flow valves in closed positions.

FIGS. 40A through 40D show respectively a closed ball check valve, a closed tapered metering pin, a closed return flow shim stack, and a closed return check valve washer shown in encircled regions 40A through 40D.

FIG. 41 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting all hydraulic fluid flow valves in open positions.

FIGS. 41 A through 41 D show respectively, an open ball check valve, an open tapered metering pin, an open return flow shim stack, and an open return check valve washer shown in encircled regions 41 A through 41 D.

FIG. 42 is a perspective view from above of the primary auxiliary hydraulic fluid valve hydraulic fluid valve of FIGS. 35-41 in a static state and taken in horizontal section from the flow inlet end.

FIG. 43 is an angled side view from above of the sectioned primary auxiliary hydraulic fluid valve of FIG. 42. FIG. 43A is an enlarged view of the check valve and the assembly bleed port from encircled region 43A of FIG. 43.

FIG. 44 is a side view of the primary auxiliary hydraulic fluid valve of FIG. 42 in centerline section.

FIG. 44A is an enlarged view of the check valve and the assembly bleed port from encircled region 44A of FIG. 44.

FIG. 45 is a centerline sectional view of the primary auxiliary hydraulic fluid valve as shown in section in FIG. 41 depicting all hydraulic fluid flow valves in open positions.

FIG. 46 is an exploded vertical centerline sectional view of the primary auxiliary fluid valve of FIGS. 35-45.

FIG. 47 is an exploded perspective view from above of the inlet end of the primary fluid valve of FIGS. 35-46.

FIG. 48 is an exploded perspective view from above of the adjuster end of the primary fluid valve of FIGS. 35-47.

FIG. 49 is a vertical centerline sectional view of the exploded perspective view from above of the inlet end of the primary fluid valve of FIGS. 35-48.

FIG. 50 is a vertical centerline sectional perspective view of the exploded perspective view above of the adjuster end of the primary fluid valve of FIGS. 35-49.

FIG. 51 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the valve at a shock unloaded state before receiving any auxiliary fluid from the shock with the pump piston sprung to the left.

FIG. 52 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the valve at a shock loaded state beginning to receive auxiliary fluid from the shock with the pump piston sprung to the left and the slider valve moving to the left and opening a frustoconical flow path.

FIG. 53 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the valve at a shock loaded state further receiving auxiliary fluid from the shock than that depicted in FIG. 53 with the threaded adjuster compressing the cup washers creating a firmer starting point for the cup washers and further limiting travel of the pump piston.

FIG. 54 is a a centerline sectional view of the secondary auxiliary hydraulic fluid valve as shown in section in FIGS. 1 -3 depicting the initial state but having more preload on the cup washer (spring) set by the threaded cap than that depicted in FIG . 51 .

FIG. 55 is a vertical centerline sectional view through the secondary fluid valve of FIG. 54 but later in time and showing the fluid fully compressing the cup washers and not completely compressing the slider valve.

FIG. 56 is an exploded vertical centerline sectional view of the secondary auxiliary fluid valve of FIGS. 51 -55.

FIG. 57 is an exploded vertical side view of the secondary auxiliary fluid valve of FIGS. 51 -56.

FIG. 58 is an exploded and perspective vertical centerline sectional view of the secondary fluid valve from the inlet end of FIGS. 51 -57.

FIG. 59 is an exploded and perspective view of the secondary fluid valve from the inlet end of FIGS. 51 -58.

FIG. 60 is an exploded and perspective centerline sectional view of the secondary fluid valve from the adjuster end of FIGS. SI - 59. FIG. 61 is an exploded and perspective view of the secondary fluid valve from the adjuster end of FIGS. 51 -60.

FIG. 62 is an end view of yet another alternative mid-valve piston assembly for a shock absorber according to another

construction.

FIG. 63 is a vertical centerline sectional view of the mid-valve piston taken along line 63-63 of FIG. 62 showing one a pair of rebound ports.

FIG. 64 is an end view of the mid-valve piston of FIGS. 62-63 showi ng the compression ports.

FIG. 65 is a compound sectional view of the mid-valve piston of FIG. 64 showing both a compression port and a rebound port.

FIG. 66 is an end view of the mid-valve piston of FIGS. 64-65 showing the compression ports.

FIG. 67 is a compound sectional view of the mid-valve piston of FIGS. 64-66 showing both a compression port and a rebound port at a beginning state with no fluid flow.

FIG. 67C is an enlarged encircled region view showing the rebound flapper shims in a closed position.

FIG. 67D is an enlarged encircled region view showing the check valve in a closed position.

FIG. 67E is an enlarged encircled region view showing the outer conical piston body closed against the outer piston frustoconical seat.

FIG. 67F is an enlarged encircled region view showing the inner cone piston body closed against the inner piston frustoconical seat.

FIG. 67G is an enlarged encircled region view showing a motion limiting gap between a back surface of the outer cone piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

FIG. 67H is an enlarged encircled region view showing the inner cone flapper shim stack closed or more unloaded state (and minimally preloaded) against the rear surface of the inner cone piston body.

FIG. 67M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

FIG. 68 is an end view of the mid-valve piston of FIGS. 64-67 showi ng the compression ports.

FIG. 69 is a compound sectional view of the mid-valve piston of FIGS. 62-67 showing both a compression port and a rebound port at a later state than shown in FIG. 67 with more fluid flow at a later point in time.

FIG. 69C is an enlarged encircled region view showing the flapper shims in a closed position.

FIG. 69D is an enlarged encircled region view showing the check valve in a closed position.

FIG. 69E is an enlarged encircled region view showing the outer cone piston body partially open relative to the outer piston

frustoconical seat.

FIG. 69F is an enlarged encircled region view showing the inner cone piston body closed against the inner piston frustoconical seat.

FIG. 69G is an enlarged encircled region view showing a motion limiting gap decreasing in size over that shown in FIG. 67G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder. FIG. 69H is an enlarged encircled region view showing the inner cone flapper shim stack closed and less loaded (minimally preloaded state) against the rear surface of the inner cone piston body.

FIG. 69M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

FIG. 70 is an end view of the mid-valve piston of FIGS. 62-69 showi ng the compression ports.

FIG. 71 is a compound sectional view of the mid-valve piston of FIGS. 62-69 showing both a compression port and a rebound port at a later state than shown in FIG. 69 with yet even more fluid flow and the initiation of pump piston movement to initiate shutting of the outer conical piston.

FIG. 71 C is an enlarged view from the encircled region and showi ng the rebound flapper shims in a closed position.

FIG. 71 D is an enlarged view from the encircled region and showi ng the check valve in a closed position.

FIG. 71 E is an enlarged encircled region view showing the outer cone piston body partially open relative to the outer piston

frustoconical seat.

FIG. 71 F is an enlarged encircled region view showing the inner cone piston body partially open relative to the inner piston

frustoconical seat.

FIG. 71 G is an enlarged encircled region view showing a motion limiting gap same in size over that shown in FIG. 69G between a back surface of the outer cone piston body and the outer sleeve travelling limiting radially inwardly extending shoulder. FIG. 71 H is an enlarged encircled region view showing the inner cone flapper shim stack being urged and flexed by rearward

movement of the rear surface of the inner cone piston body.

FIG. 71 M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

FIG. 72 is an end view of the mid-valve piston of FIGS. 64-71 showi ng the compression ports.

FIG. 73 is a compound sectional view of the mid-valve piston of FIGS. 64-71 showing both a compression port and a rebound port at a later state than shown in FIG. 71 with fluid flow restriction where the outer conical piston is closed.

FIG. 73C is an enlarged view from the encircled region and showi ng the rebound flapper shims in a closed position. FIG. 73D is an enlarged view from the encircled region and showi ng the check valve in a closed position.

FIG. 73E is an enlarged encircled region view showing the outer cone piston body closed against the outer piston frustoconical seat.

FIG. 73F is an enlarged encircled region view showing the inner cone piston body partially open relative to the inner piston

frustoconical seat.

FIG. 73G is an enlarged encircled region view showing a motion limiting gap increasing in size over that shown in FIG. 71 G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

FIG. 73H is an enlarged encircled region view showing the inner cone flapper shim stack being urged and flexed by rearward

movement of the rear surface of the inner cone piston body. FIG. 73M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

FIG. 74 is an end view of the mid-valve piston of FIGS. 62-73 showi ng the compression ports.

FIG. 75 is a compound sectional view of the mid-valve piston of FIGS. 64-73 showing both a compression port and a rebound port at a later state than shown in FIG. 73 with fluid flow restriction allowing bypass where the outer conical piston body is opening again in response to a threshold excessive force.

FIG. 75C is an enlarged view from the encircled region and showi ng the rebound flapper shims in a closed position.

FIG. 75D is an enlarged view of the encircled region and showi ng the check valve in a closed position.

FIG. 75E is an enlarged encircled region view showing the outer cone piston body fully open relative to the outer piston frustoconical seat.

FIG. 75F is an enlarged encircled region view showing the inner cone piston body partially open relative to the inner piston

frustoconical seat.

FIG. 75G is an enlarged encircled region view showing a motion limiting gap completely closed over that shown in FIG. 73G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder. FIG. 75H is an enlarged encircled region view showing the inner cone flapper shim stack being urged and flexed by rearward

movement of the rear surface of the inner cone piston body. FIG. 75M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

FIG. 76 is an end view of the mid-valve piston of FIGS. 64-75 showi ng the compression ports.

FIG. 77 is a compound sectional view of the mid-valve piston of FIGS. 64-75 showing both a compression port and a rebound port at a later state than shown in FIG. 75 with a perspective in a rebound fluid flow direction causing the rebound flapper valve stack to an open flow position in response to a rebound stroke.

FIG. 77C is an enlarged view of the encircled region and showi ng the flapper shims in an open position.

FIG. 77D is an enlarged view of the encircled region and showi ng the check valve in an open position .

FIG. 77E is an enlarged encircled region view showing the outer cone piston body closed against the inner piston frustoconical seat.

FIG. 77F is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat.

FIG. 77G is an enlarged encircled region view showing a motion limiting gap same as that shown in FIG . 67G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

FIG. 77H is an enlarged encircled region view showing the inner cone flapper shim stack closed (and preloaded) against the rear surface of the inner cone piston body.

FIG. 77M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions. FIG. 78 is an end view of the mid-valve piston of FIGS. 64-77 showi ng the compression ports.

FIG. 79 is a compound sectional view of the mid-valve piston of FIGS. 64-78 showing both a compression port and the mid-valve piston is at a static state and a rebound port at a static state showing a rebound needle position adjustment change from that of FIG. 77 depicting the needle position in a more closed position than that of FIG. 77 and a rebound port at a later state than shown in FIG. 77 with fluid flow restriction allowing bypass where the outer conical piston is opening again in response to a threshold excessive force.

FIG. 79C is an enlarged view of the encircled region and showi ng the flapper shims in a closed position .

FIG. 79D is an enlarged view of the encircled region and showi ng the check valve in a closed position.

FIG. 79E is an enlarged encircled region view showing the outer cone piston body closed against the outer piston frustoconical seat.

FIG. 79F is an enlarged encircled region view showing the inner cone piston body closed against the inner piston frustoconical seat.

FIG. 79G is an enlarged encircled region view showing a motion limiting gap same as that shown in FIG . 79G between a back surface of the outer cone piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

FIG. 79H is an enlarged encircled region view showing the inner cone flapper shim stack closed or in a less loaded state (and minimally preloaded) against the rear surface of the inner cone piston body.

FIG. 79M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to a mostly closed position . FIG. 80 is an exploded and perspective vertical centerline sectional view of the secondary fluid valve from the inlet end of FIGS. 63-79.

FIG. 81 is a perspective view from above of yet another alternative primary compression adjuster for a shock absorber according to another construction.

FIG. 81 A is an enlarged perspective view of the end portion for the primary compression adjuster taken from encircled region 81 A from FIG. 81 . Figure 81 B is a plan view of the end portion for the primary compression adjuster.

FIG. 82 is a centerline sectional view of the primary

compression adjuster taken along line 82-82 of FIG. 81 B.

FIG. 82A is an enlarged encircled portion centerline sectional view of the primary compression adjuster of FIG. 82.

FIG. 83 is an end view of yet even another alternative mid-valve for a shock absorber according to another construction.

FIG. 84 is a vertical centerline sectional view of the mid-valve of FIG. 83. DETAILED DESCRI PTION OF THE PREFERRED EMBODIMENTS

This disclosure is submitted in furtherance of the constitutional purposes of the U.S. Patent Laws "to promote the progress of science and useful arts" (Article 1 , Section 8) .

As shown herein , the drawings (that are not perspective views) are to scale in the x and y axis 1 : 1 and represent actual engineering drawings to scale, unless otherwise state as being "simplified" or "conceptual". As used herein, the term "mid-valve piston" refers to a piston assembly having a two-way fluid, hydraulic, or air valve and placed for reciprocating movement intermediate of a shock absorber between a compression chamber and a rebound chamber or for shocks having bypass passages communicating with a shock tube of a sealed shock body.

Figures 1 -61 are various views of a first exemplary hydraulic shock absorber 1 0 having a primary mid-valve piston valve 1 6 and a secondary pair of adjustable auxiliary hydraulic fluid valves 32 and 34. Cross-sectional views are show in 1 : 1 scale in the x-axis and y-axis and were obtained from engineering drawings in the drawing set provided herein.

Figure 1 is a perspective view from above of an exemplary hydraulic shock absorber assembly 10 having a main cylindrical shock tube, or cylinder 1 2 having a primary mid-valve piston 22 (see Fig.

1 A) contained for movement within tube 1 2 via an end cap 28, forming an adjuster and reservoir end cap assembly 1 6 that contains a secondary pair of primary and secondary adjustable auxiliary

hydraulic fluid valves 30 and 32 within a bridge end cap, or body 28. Each fluid valve 30 and 32 communicates with a piston and reservoir assembly 34. Assembly 10 is installed between articulating

components of a suspension or shock absorbing mechanism, such as a vehicle suspension, using a bushing and bolt (not shown) through top-most bushing bore 1 7 and a bolt and bushing (not shown) that extends through bottom-most clevis 1 8. Clevis 1 8 is affixed to a bottom end of a reciprocating piston rod assembly 1 4.

Figure 1 A is a compound sectional and perspective view from above of the hydraulic shock absorber assembly 1 0 shown in Figure 1 taken along line 1 A-1 A of Figure 1 in a centerline sectional view through the main body and the auxiliary body cylindrical components for an exemplary hydraulic shock absorber assembly 1 0 according to one aspect. Shock absorber assembly 1 0 includes a sealed shock body 1 2 including a main cylindrical shock tube, or cylinder 36, a bridge end cap 28, and a dust cap 26. End cap 28 is threaded in sealed engagement via an o-ring seal 38 to tube 36. Optionally, shock body 1 2 can be made from one or more parts that are integrally formed together, or are welded or bonded together in assembly. A pair of fluid ports 60 and 62 fluid couple adjusters 30 and 32, respectively, with compression chamber 76. Shock absorber assembly 1 0 also includes piston rod assembly 14 having a hollow piston rod, or shaft 20, a mid-valve piston 22 moveable within tube 36 between a compression chamber 76 and a rebound chamber 78 each filled with hydraulic fluid (not shown) . A clevis 18 is provided affixed to a bottom end of piston rod 20, forming piston rod assembly 1 4 for affixing to a frame member or a vehicle component. A top cap assembly, or bridge 1 6 is affixed atop cylinder 1 2 opposite clevis 38 and includes a bushing bore post 1 7 (see Fig. 1 ) for affixing a top end of shock 1 0. Movement of mid-valve piston 22 within cylinder 1 2 causes hydraulic fluid contained within sealed shock body 1 2 to move through bi-directional resistance valving structures in mid-valve piston 22 and also through adjustors, or adjustable primary valve 30 and adjustable secondary valve 32. A piston and reservoir assembly 34 includes a separator piston 48 (having a sliding o-ring seal 50) that divides an inner portion of a reservoir body 46 into an oil filled chamber 82 and an air-filled chamber 84. Optionally, piston 48 can be a flexible divider membrane within a medial portion of reservoir body 46. Oil reservoir, or chamber 82 receives hydraulic fluid passing through one or both adjusters 32 and 34, while air-filled chamber 84 contains pressurized air received via a closable air valve 52. Such pneumatic pressure provides a spring force against separator piston 48 and optionally, a coil spring can be substituted for air-filled chamber 84.

As shown in Figure 1 A, a seal head assembly 24 is affixed adjacent a bottom end of shock tube 36 behind a seal cap 26. More particularly, seal head assembly 24 includes a seal head body 58 with a radially inwardly extending circumferential groove configured to receive an o-ring seal 54 and a bumper stop 56 formed of a resilient energy absorbing material , such as a synthetic rubber. Bumper stop 56 is a cylindrical rubber washer having vertically extending

cylindrical inner and outer wall edge flanges that serve to provide progressive resistance when mid-valve piston 22 extends to a maximum position on rebound. Seal head body 58 has a cylindrical radially outwardly extending groove in an outer wall portion that matches a radially inwardly extending groove in tube 36, each cooperating to receive a c-shaped spring clip 40 to affix seal head body 58 within tube 36. An air chamber 80 is provided between piston 58 and dust cap 26. Piston 58 includes a bushing along the piston rod, a washer and top and bottom wiper seals (not numbered) .

Also shown in Figure 1 A, piston shaft 20 includes a rebound needle 42 that is axially positioned using a threaded rebound adjuster screw 44 (threads not shown) provided in clevis 1 8.

Figure 2 is an enlarged partial and compound sectional and perspective view of the shock absorber 1 0 rotated counter-clockwise from that shown in Figure 1 . More particularly, shock absorber 1 0 is shown with bridge end cap 28 having a female threaded portion 72 that secures to a complementary male threaded portion 74. Mid-valve piston 22 has a piston band seal 1 02 received in a radial inward groove on an outer surface of piston 22. A compression o-ring 1 04 is retained in a circumferential groove of piston 22 beneath piston band seal 1 02. A nut 66 is affixed with complementary threaded portions to shaft 20. A port, or bore 70 in shaft 20 is flow regulated for hydraulic fluid via axial positioning of rebound needle 42 within shaft 20. Bore 70 communications with a compression chamber defined within inner cylindrical bore 64 above piston 22. Such chamber for hydraulic fluid also communications with flow ports 60 and 62 to drive primary adjuster 30 and secondary adjuster 32. Piston and reservoir assembly 34 stores excess hydraulic fluid during a shock absorbing operation.

Figure 3 is an enlarged partial and compound sectional and perspective view of the sectioned shock absorber 1 0 as shown in Figure 1 . More particularly, bridge end cap 28 is secured atop shock tube 36 to contain mid-valve piston 22 and piston rod, or shaft 20 for reciprocation therein. Fluid, such as hydraulic fluid, is forced through primary adjuster 32 and secondary, or pre-adjuster 30 via fluid ports 62 and 60, respectively. After passing through adjusters 32 and/or 30 and communicating together via cross port 92 (see Fig. 4A) , fluid passes through fluid port 86 and into fluid, or oil chamber 82.

Pneumatic, or air pressure in air chamber 84 urges a separator piston 48 against oil inside of chamber 82 with a preset pressure applied via a Schrader pneumatic valve mounted in threaded and sealing relation in a bottom surface of a reservoir body 46 of piston and reservoir assembly 34. Separator piston 48 includes an o-ring seal 50 and a piston band seal 51 each provided in a respective outer peripheral groove of piston 48.

Figure 4 is an enlarged partial sectional and perspective view of the sectioned shock absorber 1 0 as shown in Figure 3, but from a higher perspective angle above. Bridge end cap 28 is shown with a horizontal section taken through an upper portion of cap 28, exposing mid-valve piston assembly 22 within the compression chamber 76. Fluid ports 60 and 62 delivers hydraulic fluid, or oil from compression chamber 76 and through valves 30 and 32 as mid-valve piston assembly 22 rises in tube 36 from compression forces exerted via yoke 1 8 mounted to a suspension frame component (not shown) .

Such fluid passes through valves 30 and 32 where further energy is managed/stored/released so as to mitigate shock transmission where it is stored in piston and reservoir assembly 34. Fluid passes into and out of valve 30, but passes through (bidirectionally) valve 32.

However, valve 32 can produce a net flow in either direction through valve 32 and into reservoir 34. However, valve 30 only produces a differential pressure flow that accommodates capacitive fluid storage against spring forces inside of valve 30 and does not produce a net flow through valve 30 during a compression and expansion cycle. Figure 4A is an enlarged view of a fluid reservoir communication port, or cross-port 92 provided between the adjusters 30 and 32 from the encircled region of Figure 4. More particularly, when the shock absorber is compressed fluid passes through adjusters 30 and 32 and into circumferential cavities, or chambers 88 and 90 where fluid leaves chamber 88 and enters into chamber 90 via cross port 92 into vertical port 86 and chamber 82 (see Fig. 3).

Figure 5 is an enlarged component sectional perspective view from above of the mid-valve piston assembly 22 showing the compression bleed rebound seal 1 08 in a compression closed position and showing the inner piston 1 1 2 and the outer piston 1 14 in an open position for the shock absorber 1 0 of Figures 1 and 1 A. More particularly, piston assembly 22 includes a cylindrical piston body 1 00 carried coaxially by piston rod, or shaft 20. Piston body 1 00 is trapped onto shaft 20 between a cylindrical shoulder 1 20 and a threaded end nut 66. A central fluid port 70 extends through piston body 1 00 down to a tapered metering pin end 1 34 that is axially adjustable in position via integral rebound needle 42 being adjusted in threaded

engagement at an opposite end (not shown) with shaft 20. In this way, the flow rate of shock absorber fluid, or oil through port 70 of piston assembly 22 can be adj usted for optional performance for certain shock conditions. Radially outwardly extending ports, such as port 1 24, let such fluid pass through piston body 1 00 during

compression and rebound movements within a shock tube 36 (see FIG. 1 A).

Also retained between shaft 20 and piston body 1 00, a washer 1 18 and a flexible rebound shim stack assembly 98 are secured between nut 66 and piston body 1 00 i n assembly as shown in Figure 5. A pair of stepped circumferential grooves are provided in a radial outer surface of piston body 1 00 to secure a piston band seal 1 02 and a compression o-ring seal 1 04 there beneath . According to one construction, band seal 1 02 is a PTFE (polytetrafluoroethylene) bronze filled band seal . Optionally, any other suitable sealing surface and material can be used. Circumferential arrays of equally spaced- apart compression ports 94 and rebound ports 96 are provided between opposed faces of piston body 1 00 for enabling fluid, or oil to pass from one side of piston body 1 00 to an opposite side when mid valve piston assembly 22 (see FIG. 1 A) moves toward a compression chamber and a rebound chamber during respective compression and rebound stages of suspension travel. Concurrently, fluid also moves through port 70 from one side of piston body 1 00 to another side through piston body 1 00 and the amount of fluid flow is tailored, or tuned by presetting position of tapered metering pin end 1 34 relative to an opening on port, or bore 70 in order to tailor shock performance.

In order to further add shock absorption and/or damping control to a shock assembly, fluid flow through ports 94 and 96 are resisted by the action of fluid flow past respective pistons and flow restrictors as shown in Figure 5. More particularly, compression ports 94 each join together into an annular volumetric expansion chamber 11 6 where fluid, or oil builds pressure that urges a pair of circumferential pistons, an inner piston 1 1 2 and an outer piston 1 1 4 against a pair of

corresponding inner spring stacks, such as inner spring stack 1 38 and outer spring stack 1 40. Spring stacks 1 38 and 1 40 are seated against a cylindrical stop plate 1 28 that is trapped about shaft 20 between a cylindrical spacer 1 20 and a cylindrical stack plate 142 and a cylindrical disk plate 1 26 such that piston assembly 22 is assembled together in stacked relation. An array of circumferentially equally spaced-apart ports 1 21 are provided through platen 1 28 (see also Figures 7 and 1 0) to enable fluid flow through plate 1 28. Similarly, rebound ports 96 covered on a compression chamber end by rebound shim stack assembly 98. Individual cylindrical spring plates of assembly 98 flex under fluid pressure from ports 96 to allow fluid passage through piston body 1 00 from a rebound chamber to a compression chamber on opposed sides of piston body 1 00. In this way, fluid flow through piston body 1 00 is regulated by flow path resistance of ports 96 and spring resistance of shim stack 98 during a rebound movement of mid-valve piston assembly 22. As shown in Figure 5, inner circumferential piston 112 and outer circumferential piston 114 each have a beveled, or frustoconical piston surface 188 and 190 that seats in parallel engagement with a respective stationary frustoconical piston valve seat 192 and 194. As inner piston 112 and outer piston 114 move away from piston body 100, surfaces 188 and 190 move away from seat surfaces 192 and 194, forming circumferential flow paths for fluid or oil to pass through piston body 100 from a compression chamber to a rebound chamber. Pursuant of a first implementation, inner spring stack 138 and outer spring stack 140 are constructed from wave coil springs of similar material. Since outer spring stack 140 has a larger diameter than inner spring stack 140, this results in outer spring stack 140

compressing before spring stack 138, enabling outer piston 114 to compress and open before inner piston 112. Optionally, spring stiffnesses between springs stacks 138 and 140 can be adjusted so that the inner spring stack compresses before or concurrently with the outer spring stack.

In addition to spring stacks 138 and 140 and pistons 112 and 114 resisting fluid flow during a compression stage of a shock, another compression shim, or spring stack 106 modifies the resulting fluid flow, as shown in Figure 5. A first flow path downstream of pistons 112 and 114 is provided by a circumferential array of radially outwardly extending elongate oval-shaped ports 136 provided equally- distance spaced apart about an outer periphery of outer piston 114. A second flow path is provided when piston 114 is only partially compressed by a gap between a bottom edge of piston 114 and plate 142. A bottom edge of piston 114 includes a circumferential array of circumferentially equally spaced and scalloped relief vents, or gaps 119 provided in a bottom surface of stack plate 142 between adjacent legs 117. A third flow path is provided by a circumferential array of circumferentially equally spaced and scalloped relief vents, or gaps 132 provided in a bottom surface of stack plate 142. Each vent 132 is bordered on each end by a downward terminal leg 130. Shim stack 106 normally seats against legs 130. As fluid flow and pressure increase, individual shim springs of stack 106 flex downwardly and a further gap forms between stack 106 and a bottom outer-peripheral surface edge of plate 142, enabling a greater flow volume along such path during a compression phase of shock operation.

Figure 5A is an enlarged view of a compression bleed rebound seal, or o-ring 108 taken from encircled region 5A of Figure 5. More particularly, a tapered circumferential channel 110 is formed in a circumferential inner surface of outer piston 114, between piston 114 and an outer circumferential surface of inner piston 112. Channel 110 is tapered so as to widen extending towards a bottom edge, as shown in Figure 5A. O-ring 108, shown in a lowered position within channel 110 provides a circumferential fluid passage between inner piston 112 and outer piston 114 for fluid flowing in a downward direction and raises to seat and seal any fluid flow when raised in an upward direction.

Figures 6-10 variously show in exploded views the construction and components of mid-valve piston assembly 22 of Figure 5. Figure 6 is a midline vertical centerline sectional and exploded perspective view, while Figures 7-10 are various exploded perspective views of mid-valve piston assembly 22. As shown in Figure 6, female threads 144 on nut 144 affix in threaded engagement with complementary male threads 146 on piston rod, or shaft 20 such that disc plate 126, compression shim stack assembly 106 (springs 152, 154 and 156), stack plate 142, stop plate 128, outer spring stack 140, spacer 120, inner spring stack 138, inner piston 112, outer piston 114, piston body 100, rebound shim stack assembly 98 (springs 158-164), and washer 118 are stacked together and entrapped between cylindrical shoulder 122 (see Fig.7) on shaft 20 and nut 144. Figures 7-10 also show further construction and assembly details of such components.

As further shown in Figure 6, central bore, or port 70 extends down piston shaft 20 to provide a fluid, or oil flow path. Scalloped edges, or vents 132 in stack plate 142 provide another fluid flow path. Inner piston 112 and outer piston 114 assemble inside of annular volumetric expansion chamber 116 which communicates with ports 94 and 96 (see Fig.7). O-ring 108 is carried within a groove in piston 114 and band seal 102 and o-ring seal 104 are carried in

corresponding cylindrical recesses in piston body 100. An axially movable needle valve 150 is carried within a port 151 (see Fig.8) in outer piston 114. Further details of such components are shown variously in Figures 7-10.

As shown in Figure 7, a sprocket-shaped hollow post 166 is provided centrally of and integrally with piston body 100. Post 166 includes an array of equally spaced-apart and radially outwardly extending fingers, or legs 168. Each adjacent pair of legs 168 are separated from one another by a flute, or groove 170, allowing inner cone piston 112 and inner cone frusta-conical seat 188 to slide concentrically and align and be guided by the circular circumferential bushing type surface caused by post 166 and a frustoconical piston seat 192 inner angular circumferential surface to create hydraulic fluid pathways by the flutes 170 when inner cone piston 112 opens and angularly exposing the flutes to a hydraulic fluid path extending hydraulic fluid flow towards spacer 120 with its end rounded edges and smaller diameter than that of inner cone piston 112 internal bore, allowing a smooth transfer of hydraulic fluid (not shown)pressure at an less angular fluid path flow and spreading or dissipating the dynamic fluid back pressure feedback threshold towards fluid exit or pathway through circumferential lower body end of the inner cone piston 112 and through inner wave spring 138 open gaps between coils and outer wave spring 140 gaps between coils and stop plate 128 inner circumferential array of ports(need a number) (best seen in Figure 219A) and further fluid path from inner cone piston 112 extends to ports 136 and scallops 119 in outer cone piston 114 and scallops 132 in stack plate 142 flowing past the angular gaps of shim stack 106 making the spread of feedback hydraulic pressure to a minimum. Post 166 further includes a central bore 172. Furthermore, inner piston 112 includes an array of equally spaced-apart and radially inwardly extending flutes 174. Flutes 170 and 174 provide fluid flow paths in assembly under certain operating conditions. Port 1 24 is also shown in Figure 7 adjacent to a reduced diameter end portion 1 23 of shaft 1 22.

Figures 1 1 -34 variously illustrate mid-valve piston assembly 22 in various stages of operation including in a resting, unloaded state. Figures 1 1 -1 8 show successive end and sectional views of piston assembly 22. Figures 1 9-30D show successive end, sectional and enlarged partial sectional views of piston assembly 22. Figures 31 -34 show enlarged component sectional perspective views from above of the mid-valve piston assembly 22 for the shock absorber 1 0 of Figure 1 .

Figure 1 1 is an end view of the mid-valve piston assembly 22 taken from the compression end of a shock absorber. More

particularly, piston assembly 22 in end view shows a circumferential array of compression ports 94 about central piston rod shaft 20 and nut 66. Ports 94 are just outboard of an outer peripheral portion of rebound shim stack assembly 98.

Figure 1 2 is a compound sectional view of the mid-valve piston assembly 22 taken along compound line 1 2- 1 2 of Figure 1 1 and showi ng the mid-valve piston assembly 22 in a static state without any fluid flow. More particularly, rebound needle 42 is shown positioned in bore 70 of shaft 20, while shim stack assemblies 98 and 1 06 and pistons 1 1 2 and 1 14 are shown in fluid flow closed positions. Springs stacks 1 38 and 140 are fully expanded to seat pistons 1 12 and 1 14 into piston body 1 00. In such static state, no fluid is moving through ports 94 and shim stack assembly 1 06 is seated against portions, or legs 1 30 of stack plate 1 42 and is held against stop plate 1 28 by shim stack 1 06 preload. Stack plate 142 consist of legs 1 30 with many different configurations and spacings such as three legs 1 30 or four legs 1 30 to perform many kinds of shim deformation tactics, such as longer legs 1 30 on two opposing sides and 2 shorter legs 1 30 on two opposing sides inner legs 1 30 and outer legs 1 30 with different length legs 1 30 making shim stack 1 06 deformation flex and preload spring force to act as a more progressive stack 1 06 with less preload or a less progressive stack 1 06 with more preload, creating an endless variation of stack plate 142 configuration to match a suitable ratio of stack plate 142 outer cone piston 1 1 4 preload and progression to outer cone piston 1 14 as it opens frustoconically away from the piston 1 00. Piston band seal 1 02 and 0-ring seal 1 04 are carried with body 1 00 and are not moving relative to the piston tube (not shown) .

Finally, needle valve 1 50 is shown closed within body 1 00. It is understood that needle valve 1 50 has a central shaft with three sides, two adjacent sides are flat, and a third side is curved and convex.

The terminal tip end of the needle valve 1 50 has a conical tapering end and the head end is flared and enlarged. As the needle valve 1 50 acts, compression fluid flow direction is allowed and the needle flows back into its stepped orifice 1 51 and seals during a rebound stroke, making the needle valve 1 50 a one-way check valve.

Figure 1 3 is an end view of the mid-valve piston assembly 22 taken from the compression end and showing a compound section taken to realize cross-section views for Figures 14-22.

Figure 14 is a compound sectional view of the mid-valve piston assembly 22 taken along compound line 14- 14 of Figure 1 3 and showi ng the mid-valve piston assembly 22 in a static state without any fluid flow. The compound cross-section is taken through both ports 94 and 96 and shows springs 1 38 and 140 in a fully expanded state that closes pistons 1 1 2 and 11 4 agai nst piston body 1 00 to minimize volume of annular chamber 1 1 6. Shim stack assembly 1 06 is closed at rest but in a preloaded state against stack plate 1 42 while springs 1 38 and 1 40 are seated against plate 1 28. Shim stack assembly 98 is also closed at rest against a top face of piston body 1 00 which means each cylindrical spring plate 99 is flat.

Figure 14A is an enlarged encircled region 14A from Figure 14 showi ng a gap 1 76 between a rear edge of the outer piston 1 1 4 and a forward surface of stack plate 1 42. Figure 14B is a gap 178 between a rear edge of the inner piston 112 and a forward surface of the stop plate 128 from the enlarged encircled region 14B from Figure 14.

Figure 14C is a gap 180 between an inner shelf of the outer piston 114 and an outer shelf of the inner piston 112 from the enlarged encircled region 14C from Figure 14.

Figure 15 is a compound sectional view of the mid-valve piston assembly 22 taken along compound line 15-15 of Figure 13 and showing the mid-valve piston assembly 22 in a small fluid flow rate state where fluid passes between inner piston 112 and outer piston 114 as o-ring seal is in an open position. The compound cross- section is taken through both ports 94 and 96 and shows springs 138 and 140 in a slightly loaded state that closes piston 112 and starts to slightly open piston 114 relative to piston body 100 to slightly increase fluid flow from annular chamber 116. Shim stack assembly 106 is closed at rest against plate 142 while springs 138 and 140 are seated against plate 128. Shim stack assembly 98 is also closed at rest against a top face of piston body 100 which means each cylindrical spring plate 99 is flat. Optionally, a small taper can be provided on the face of piston 100 on the rebound side creating an initial load tension or preload to the shock stack 98.

Figure 15A is an enlarged encircled region 15A from Figure 15 showing a closed gap 176 between a rear edge of the outer piston 114 and a forward surface of the stack plate 142.

Figure 15B is a gap 178 between a rear edge of the inner piston 112 and a forward surface of the stop plate 128 from the enlarged encircled region 15B from Figure 15.

Figure 15C is a partially smaller gap 180 between an inner shelf of the outer piston 114 and an outer shelf of the inner piston 112 smaller than depicted in Figure 14C from the enlarged encircled region 15C from Figure 15. Figure 16 is a compound sectional view of the mid-valve piston assembly taken along compound line 16-16 of Figure 13 and showing the mid-valve piston assembly 22 in a small-to-medium fluid flow rate state. The compound cross-section is taken through both ports 94 and 96 and shows springs 138 and 140 in an increased loaded state over that shown in Figure 14 that closes inner piston 112 and partially opens outer piston 114 relative to piston body 100 to form a

frustoconical fluid flow gap 182 that further increases fluid flow from annular chamber 116. Shim stack assembly 106 is urged rearward by stack plate 142 and outer piston 114 while springs 138 and 140 are seated and compressed against stop plate 128. Shim stack assembly 98 is also closed at rest against a top face of piston body 100 which means each cylindrical spring plate 99 is flat.

Figure 16A is an enlarged encircled region 16A from Figure 16 showing a closed gap 176 between a rear edge of the outer piston 114 and a forward surface of the stack plate 142.

Figure 16B is a gap 178 between a rear edge of the inner piston 112 and a forward surface of the stop plate 128 similar in size to that shown in Figure 15B from the enlarged encircled region 16B from Figure 16.

Figure 16C is a closed gap 180 between an inner shelf of the outer piston 114 and an outer shelf of the inner piston 112 smaller than depicted in Figure 15C from the enlarged encircled region 16C from Figure 16.

Figure 17 is a compound sectional view of the mid-valve piston assembly 22 taken along compound line 17-17 of Figure 13 and showing the mid-valve piston assembly 22 in a large fluid flow rate state. The compound cross-section is taken through both ports 94 and 96 and shows both inner piston 112 and outer piston 114 compressed against their respective springs in large, or maximum loaded state over that shown in Figure 14 that fully opens both inner piston 112 and outer piston 114 relative to piston body 100 to form an outer frustoconical fluid flow gap 182 and an inner frustoconical fluid flow gap 186 that further increases fluid flow from the annular chamber. Shim stack assembly 106 is urged even further rearward by stack plate 142 (than in Figure 16) and outer piston 114 while springs 138 and 140 are further seated and compressed against plate 128. Shim stack assembly 98 is also closed at rest against a top face of piston body 100 which means each cylindrical spring plate 99 is flat. Shim stack assembly 98 opens on a rebound phase of operation.

Figure 17A is an enlarged encircled region 17A from Figure 17 showing a closed gap 176 between a rear edge of the outer piston 114 and a forward surface of the stack plate 142.

Figure 17B is a closed gap 178 between a rear edge of the inner piston 112 and a forward surface of the stop plate 128 from the enlarged encircled region 17B from Figure 17.

Figure 17C is a closed gap 180 between an inner shelf of the outer piston 114 and an outer shelf of the inner piston 112 than depicted in Figure 16C from the enlarged encircled region 17C from Figure 17.

Figure 17D is an unseated o-ring 108 in a circumferential channel 110 within an inner wall of the outer piston from the encircled region 17D of Figure 17.

Figure 18 is a sectional view of the mid-valve piston assembly 22 taken along compound line 18-18 of Figure 13 and showing the mid-valve piston assembly 22 in a static, or zero fluid flow rate state. The compound cross-section is taken through both ports 94 and 96 and shows both inner piston 112 and outer piston 114 closed relative to piston body 100 that minimizes size of the annular chamber. Shim stack assembly 106 is in a resting state seated against plate 142 and outer piston 114 while springs 138 and 140 are in their fully extended state against plate 128. Shim stack assembly 98 is also closed at rest against a top face of piston body 100 which means each cylindrical spring plate is flat. Shim stack assembly 98 opens on a rebound phase of operation.

Figure 18A is a seated o-ring 108 in a circumferential channel 110 within an inner wall of the outer piston 114 from the encircled region 18A of Figure 18 showing o-ring 108 in a sealed position that stops fluid flow towards the compression chamber of a shock absorber.

Figure 18B is a circumferential gap 184 between the inner piston 112 and the outer piston 114 shown in the enlarged encircled region 18B of Figure 18.

Figure 19 is a sectional view of the mid-valve piston assembly 22 with the inner piston 112 and the outer piston 114 in a closed position against piston body 100 in a static state and the compression bleed rebound o-ring seal 108 closed and taken along compound line 19-19 of Figure 13.

Figure 19A is an enlarged encircled region from Figure 19 of the inner piston 112 and the outer piston 114 for the mid-valve piston assembly 22 and the compression bleed rebound o-ring seal 108 shown in a static, unloaded state. More particularly, inner spring stack 112 and outer spring stack 114 are both expanded while o-ring seal 108 is driven forward within circumferential channel 110 to seal any fluid passage between inner piston 112 and outer piston 114. Likewise, pistons 112 and 114 are fully seated against piston body 100 to prevent any fluid exchange with compression port 94 chamber 116. Piston, or cone 112 has an inner circumferential ledge 125, while piston, or cone 114 has an outer circumferential ledge 127. Ledges 125 and 127 provide fluid driving surfaces that urge pistons 112 and 114, respectively, into engagement with piston body 100 during a rebound initiation of a shock absorber.

Figure 20 is a sectional view of the mid-valve piston assembly 22 with the inner piston 112 and the outer piston 114 urged against piston body 100 in a small flow position and with the compression bleed rebound o-ring seal open and taken along compound line 20-20 of Figure 13.

Figure 20A is an enlarged encircled region from Figure 20 of the inner piston 112 and the outer piston 114 for the mid-valve piston assembly 22 and the compression bleed rebound o-ring seal 108 shown in an open flow position within circumferential channel 110. In the small flow position, o-ring seal 108 enables fluid flow between piston 112 and piston 114 while engaged against piston base 100 via flow path 184 during a compression shock absorption phase. In this manner, fluid or oil flows from port 94 and chamber 116 into

circumferential (or frustoconical) flow path 184. Flutes 184 enable fluid flow from fluid path 184 to the rebound side of piston body 100 and around springs 138 and 140.

Figure 21 is a sectional view of the mid-valve piston assembly 22 taken along line 21-21 of Figure 13 with the inner piston 112 urged against piston body 100 and the and the outer piston 114 urged slightly away from piston body 100 in a small/medium flow position and with the compression bleed rebound o-ring seal open and taken along line 20-20 of Figure 13.

Figure 21A is an enlarged encircled region from Figure 21 of the inner piston 112 and the outer piston 114 for the mid-valve piston assembly 22 and the compression bleed rebound o-ring seal 108 shown in an open flow position within circumferential channel 110. In the small flow position, o-ring seal 108 enables fluid flow between piston 112 and piston 114 along a flow path between pistons 112 and 114. Inner piston 112 is still engaged against piston base 100 and spring stack 138 during such a compression shock absorption phase, while outer piston 114 is urged against spring stack 140, compressing stack 140 to provide a circumferential and frustoconical fluid flow path 182 between piston 114 and piston body 100. In this manner, fluid or oil flows from port 94 and chamber 116 into flow path 182 and between pistons 112 and 114. Figure 22 is a sectional view of the mid-valve piston assembly 22 taken along line 22-22 of Figure 13 with the inner piston 112 urged fully away from the piston body 100 and the and the outer piston 114 urged fully away from piston body 100 in a large flow position and with the compression bleed rebound o-ring seal 108 open and taken along line 20-20 of Figure 13.

Figure 22A is an enlarged encircled region from Figure 22 of the inner piston 112 and the outer piston 114 for the mid-valve piston assembly 22 and the compression bleed rebound o-ring seal 108 shown in an open flow position within circumferential channel 110. In the small flow position, o-ring seal 108 enables fluid flow between piston 112 and piston 114 along a flow path between pistons 112 and 114. Inner piston 112 is disengaged from piston base 100 and urged against spring stack 138 during such a compression shock absorption phase to form a cylindrical, or frustoconical flow path 186, while outer piston 114 is urged against spring stack 140, compressing stack 140 to provide a circumferential and frustoconical fluid flow path 182 between piston 114 and piston body 100. In this manner, fluid or oil flows from port 94 and chamber 116 into flow paths 182 and 186, and between pistons 112 and 114.

As shown in Figure 22A, a first frustoconical piston contact surface 188 on inner piston 112 engages and disengages with a complementary first frustoconical valve seat 192 on body 100. A second frustoconical piston contact surface 190 on outer piston 114 engages and disengages with a complementary second frustoconical valve seat 194 on body 100. Although surfaces 188 and 190 and seats 192 and 194 are shown as frustoconical surfaces, they are also conical sections, and it is understood that they can alternatively be conical, frustoconical, curved conical segments or surfaces, linear conical surfaces or portions, or any portion or circumferential or partial circumferential surface geometry capable of providing passage of fluid between the piston body 100 and the pistons 112 and 114. Figure 23 is an end view of the mid-valve piston assembly 22 taken from the compression end and showing a compound section taken to realize the cross-sectional view for Figure 24.

Figure 24 is a centerline sectional view of the mid-valve piston assembly 22 taken along line 24-24 of Figure 23 showing a static no fluid flow condition.

Figure 24A is an enlarged encircled region from Figure 24 of the inner piston 1 1 2 and the outer piston 1 1 4 for the mid-valve piston assembly 22 both closed against the piston body 1 00 from force of respective spring stacks 1 38 and 1 40 during a static no fluid flow condition and showing the compression bleed rebound o-ring seal 1 08 in a closed or sealed position within circumferential channel 1 1 0.

Figure 24B is an enlarged encircled region 24B from Figure 24A showi ng a small gap 1 76 between a rear edge of the outer piston 11 4 and a forward surface of the stack plate 142.

Figure 24C is a gap 1 78 between a rear edge of the inner piston 1 12 and a forward surface of the stop plate 1 28 from the enlarged encircled region 24C from Figure 24A.

Figure 24D is a gap 1 80 between an i nner shelf of the outer piston 1 1 4 and an outer shelf of the in ner piston 1 12 from the enlarged encircled region 24D from Figure 24A.

Figure 25 is an end view of the mid-valve piston assembly 22 from the compression end and showing a compound section taken to realize the cross-sectional view for Figure 26. Figure 26 is a centerline sectional view of the mid-valve piston assembly 22 taken along line 26-26 of Figure 25 showing a small fluid flow condition.

Figure 26A is an enlarged encircled region from Figure 26 of the inner piston 1 1 2 and the outer piston 1 1 4 for the mid-valve piston assembly 22 both closed against the piston body 1 00 (with rebound return port 96) from force of respective spring stacks 1 38 and 140 during a small fluid flow condition and showing the compression bleed rebound o-ring seal 1 08 in an open fluid flow position within

circumferential channel 1 1 0.

Figure 26B is an enlarged encircled region 26B from Figure 26A showi ng a closed gap 1 76 between a rear edge of the outer piston 1 14 and a forward surface of the stack plate 142.

Figure 26C is a gap 1 78 between a rear edge of the inner piston 1 12 and a forward surface of the stop plate 1 28 from the enlarged encircled region 26C from Figure 26A.

Figure 26D is a gap 1 80 between an inner shelf of the outer piston 1 1 4 and an outer shelf of the in ner piston 1 1 2 from the enlarged encircled region 26D from Figure 26A.

Figure 27 is an end view of the mid-valve piston assembly 22 from the compression end and showing a compound section taken to realize the cross-sectional view for Figure 28.

Figure 28 is a centerline sectional view of the mid-valve piston assembly 22 taken along line 28-28 of Figure 27 showing a

small/medium flu id flow condition.

Figure 28A is an enlarged encircled region from Figure 28 of the inner piston 1 1 2 and the outer piston 1 1 4 for the mid-valve piston assembly 22 with the inner piston 1 1 2 closed against the piston body 1 00 (with return port 96) and the outer piston 11 4 open relative to the piston body acting against the force of respective spring stacks 1 38 and 140 during a small-to-medium fluid flow condition and showing the compression bleed rebound o-ring seal 1 08 in an open fluid flow position within circumferential channel 1 1 0.

Figure 28B is an enlarged encircled region 28B from Figure 28A showi ng a gap 1 76 between a rear edge of the outer piston 1 1 4 and a forward surface of the stack plate 142. Figure 28C is a gap 1 78 between a rear edge of the inner piston 1 12 and a forward surface of the stop plate 1 78 from the enlarged encircled region 28C from Figure 28A.

Figure 28D is a closed gap 1 80 between an inner shelf of the outer piston. 1 14 and an outer shelf of the inner piston 1 1 2 from the enlarged encircled region 28D from Figure 28A.

Figure 29 is an end view of the mid-valve piston assembly 22 from the compression end and showing a compound section taken to realize the cross-sectional view for Figure 30. Figure 30 is a centerline sectional view of the mid-valve piston assembly 22 taken along line 30-30 of Figure 29 showing a large fluid flow condition.

Figure 30A is an enlarged encircled region from Figure 30 of the inner piston 1 1 2 and the outer piston 1 1 4 for the mid-valve piston assembly 22 both open fully relative to the piston body 1 00 (with return port 96) acting against the force of respective spring stacks 1 38 and 140 during a full fluid flow condition to provide fluid flow paths 1 86 and 1 90 between surface 1 88 and seat 1 92 and surface 1 90 and seat 1 94, and further showing the compression bleed rebound o-ring seal 1 08 in an open fluid flow position within circumferential channel 1 1 0.

Figure 30B is an enlarged encircled region 30B from Figure 30A showi ng a closed gap 1 76 between a rear edge of the outer piston 1 14 and a forward surface of the stack plate 142. Figure 30C is a closed gap 1 78 between a rear edge of the inner piston 1 1 2 and a forward surface of the stop plate 1 28 from the enlarged encircled region 30C from Figure 30A.

Figure 30D is a closed gap 1 80 between an inner shelf of the outer piston 11 4 and an outer shelf of the inner piston 1 1 2 from the enlarged encircled region 30D from Figure 30A. Figure 31 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly 22 for the shock absorber of Figure 1 showing the compression bleed rebound seal 108 in a fluid flow closed position and further showing the inner piston 112 and the outer piston 114 in a closed position urged against piston body 100 corresponding with a static no fluid flow condition.

Figure 31 A is an enlarged view of encircled region 31A from Figure 31 of the inner piston 112 and the outer piston 114 for the mid valve piston assembly 22 and the compression bleed rebound o-ring seal 108 shown in a raised closed flow position within circumferential channel to prevent fluid flow between pistons 112 and 114.

Figure 32 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly 22 of Figure 31 in a small flow position and showing the inner piston 112 and the outer piston 114 in a closed fluid flow position, but showing the compression bleed rebound seal 108 downward in circumferential channel 110 in an open flow position to enable fluid flow between pistons 112 and 114.

Figure 32A is an enlarged view of encircled region 32A from Figure 32 of the inner piston 112 and the outer piston 114 closed against the piston body 100 for the mid-valve piston assembly 22 and the compression bleed rebound o-ring seal 108 lowered in

circumferential channel 110 to provide fluid flow between pistons 112 and 114.

Figure 33 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly 22 of Figure 31-32 in a small/medium fluid flow position showing the compression bleed rebound seal 108 in a downward open fluid flow position enabling fluid flow between pistons 112 and 114 and showing the inner piston 112 in a closed position and the outer piston 114 in an intermediate open position. Figure 33A is an enlarged view of encircled region 33A from Figure 33 of the inner piston 1 1 2 and the outer piston 1 1 4 for the mid valve piston assembly 22 (of Figure 33) for a small/medium fluid flow condition where the outer piston is axially displaced from piston body 1 00 and the inner piston 1 1 2 is urged against piston body 1 00, and the compression bleed rebound o-ring seal 1 08 is seated downwardly within circumferential chamber 1 1 0 to provide a fluid flow passage between pistons 11 2 and 1 14.

Figure 34 is an enlarged component compound sectional perspective view from above of the mid-valve piston assembly for the shock absorber of Figures 31 -33 showing a large fluid flow position with the compression bleed rebound seal in a downward open fluid flow position enabling fluid flow between pistons 1 1 2 and 11 4, and further showing the inner piston 1 1 2 and the outer piston 1 1 4 both in a fully open fluid flow position relative to the piston body 1 00.

Figure 34A is an enlarged view of encircled region 34A from Figure 34 of the inner piston 1 1 2 and the outer piston 1 1 4 for the mid valve piston assembly and showing the compression bleed rebound o- ring seal 1 08 in a downward open position at a large or maximum fluid flow position within circumferential channel 1 10 enabling fluid flow between pistons 11 2 and 1 14 while fluid also flows between both of pistons 1 1 2 and 1 14 and the piston body.

Figure 35 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 depicting the valve 32 at a shock unloaded state before receiving any auxiliary fluid (not shown) from the shock with the pump piston 21 0 sprung to the right. More particularly, fluid valve 32 includes a cap body 200 affixed in threaded engagement with an outer base 202 via male threaded portion 242 and female threaded portion 240 to form a housing. Optionally, cap 200 and body 202 can be press fitted together with tight tolerances. An o-ring groove pictured in Figure 2 fits the outer periphery grove of valve 32 cap closest to the external portion of body 1 6, when threaded into housing 1 6 in Figure 1 A creating a seal barrier between the inner shock and outer shock to retain hydraulic fluid and hydraulic flu id pressure within the shock assembly 1 0 when threaded in via mating threads 238 coupling the primary auxiliary valve 32 to upper shock housing 1 6 and or 28. A pump piston 21 0 is carried for reciprocating movement about an alignment shaft tube body 21 4 and within an inner cylindrical bore 260 for pump piston 21 0 of a conical piston body 21 2. A pair of o-ring seals 261 and 262 seal piston 21 0 for reciprocation between

alignment shaft tube body 21 4 and body 21 2. Conical piston body 21 2 is axially reciprocated relative to a frustoconical seat, or surface 302 (see Fig. 36) of outer base 202. A check valve assembly 220 is provided at an open end of valve 32 with a stack of springs 268 and a slit lock ring 270. A check shim 21 6 and a coil spri ng 21 8 seats against a cylindrical array of ports 276 about a cylindrical flange of alignment shaft tube body 21 4 (see Fig. 48) and within a bore 299 of outer base 202. A male threaded portion 284 on body 21 4 is engaged with a complementary threaded portion 282 on cone body 21 2. A spring stack 204 extends from a shim stack 291 inside of an inner bore within pump piston 21 0. An adjustable flow volume clicker screw 206 is threaded into cap 200 with male threads 232 engaging in complementary relation with female threads 230. A ball 226 is sprung with coil spring 228 to engage with a discrete number of detents 244 (see Fig. 50) about a periphery of the bore in which screw 206 is seated. An o-ring 224 fits into a groove about threaded screw clicker 206 and seals between the screw 206 and primary cap 200 containing fluid pressure within the valve assembly 32. A tool slot 222 in screw 206 enables rotation to discrete locations defined by each detent 244. A c-shaped snap ring 208 is seated in a circumferential groove to retain screw 206. A metering pi n 236 on screw 206 is axially adjusted within a metering pin hole 234 to adjust fluid flow from a central bore 246 via plate 253, spring 257 and pin 255 as fluid pressure moves plate 253 against coil spring 257 forming an annular gap with bore 290. Pin 255 is slidably received in a complementary cylindrical bore 259. A circumferential array of equally spaced apart bores 277 provides a fluid flow out and in of the outer base 202. A male threaded portion 242 and a female threaded portion 240 are used to secure together adjuster 206 to make a shock absorber adjuster assembly. The assembly of adjuster 32 uses male threaded portion 238 to secure adjuster 32 into the shock absorber cap assembly 1 6 (see Fig. 1 A) . An assembly bleed bore 275 in the outer periphery of outer base 202 accommodates installation of Primary valve assembly 32 into shock housing 1 6 to create a fluid bleed to o-ring (not shown) and to add a bypass flow leak as one option to gain fluid flow through fluid bypass port 275 or better known as assembly bleed bore 275, making a small bypass bleed around the valving structure 32 tuned to precisely acquiesce a non-covered restriction flow path without changing a hydraulic fluid pressure frequency more aggressively by making a non-covered restriction bleed flow path internally and harming the integrity of the primary auxiliary valves 32 pressure building seats.

An array of circumferential fluid ports 279 receive fluid in a rebound shaft 20 movement of piston mid-valve assembly 22 (see Fig. 3) causing fluid to leave the reservoir chamber 34 and fluid chamber 82 presses via gas pressure in chamber 84 separator piston 48 and hydraulic fluid flows through fluid port 86 and around the outer base 202 outer periphery and into an exterior array of fluid ports 277, entering fluid port 279 and penetrating check valve assembly 220 by method of opening check shims 268 and flowing back to shock body compression chamber 76 through fluid port 62.

A male threaded plug, or set screw 294 having a central through-bore engages with complementary female threads 296 in cap body 200 to provide a flow restriction that is metered with a ball 252 and a coil spring 254, receiving fluid flow from connecting ports 250 and 251 . Internal bores 272, 286, and 288 in the resulting housing formed by cap 200 and outer base 202 create clearances with tolerances to flow hydraulic pressurized fluid when close interference of cone valve piston 21 2 and pump piston 21 0 are proximate in range during action. An o-ring seal 258 is seated in a circumferential groove 256 integrally within cap 200. A circumferential groove 274 is formed in outer base 202 for receiving an o-ring seal (not shown) to seal within the shock absorber cap assembly (see Fig. 1 A) .

A circumferential array of equally spaced apart bores 279 in base 202 provide fluid passage to bore 272. O-ring seal 264 within a cylindrical groove seals with a shaft of body 214. A cylindrical array of equally spaced apart bores 297 enable rebound flow from behind plate 21 6 when spring 21 8 is compressed. During a compression cycle, a step bore 278 in a flange of alignment shaft tube body 214 provides a fluid flow path to drive piston 21 0 rearward against springs 204 which tends to urge conical piston body 21 2 to close with a frustoconical seat 302 (see Fig. 36) . Step bore 278 comprises a smaller bore and a larger bore to maximize drilling efficiency of a particularly small drill. A bore 298 in cap 200 carries fluid from circumferential groove 292 for sprung passage past shim stack 292 when over a threshold pressure.

Further relating to a hydraulic fluid (not shown) pressure response in an primary auxiliary hydraulic fluid valve 32 of Figure 35 in part are o-ring 258 and o-ring 262 working in combination to act as a seal formed with and mating circumferential embodiment to alignment shaft tube body 21 4 an encapsulated wall inner groove similar to that of circumferential groove 256 and forming an enclosed fitting to capture and retain fluid bypass and also forming a guide bush slidable during receiving and retracting cap body 200 correlation to that of moving part alignment shaft tube body 21 4 and moving part pump piston 21 0 to keep concentricity and alignment.

Flow paths for Figure 35 are depicted flowing through a network of proximate flow ports in an primary auxiliary valve 32 starting from inlet check valve 220 end receiving fluid flow of volumetric proportion of piston rod 20 entering sealed piston body 36 to displace a fluid volume ratio of travel used by the piston rod 20 is similar volume to that received through fluid port 60 forcing fluid to meter through primary auxiliary valve actuating a responsive

measure, producing counter reacting valve seating and valve seat pressures. As piston rod shaft 20 engages or initiates an entry to shock body 36 fluid acts to flow by hydraulic force into fluid port 60 or fluid port 62 and in an engagement to move hydraulic fluid through the primary auxiliary valve 32, the fluid (not shown) enters into center bore of shim stack check valve 220 and around outer base head end 202 to the assembly bleed port 275 (lead in hole not shown) , as fluid continues the direction towards the innermost part of valve 32 it prevails to flow the path of least resistance first. The path towards the frustoconical seal 300 and 302 surface area is the largest surface area seat contained in the valve 32 comprising minimal spring 204 preload when at an static initial state hydraulic fluid pressure opens the frustoconical seat 300 and 302, a circumferential valve plate 253 and surface of outer most end of alignment shaft tube body 214 presses against a loaded tension spring 257 with a smaller surface area volume and more initial spring 257 tension than spring assembly 204, fluid port 297 receives fluid and directs towards stepped fluid port 278 engaging a very small fraction of fluid flow (not shown) into cone piston body 21 2 cylinder interior wall 260 (see FIG. 37) expanding by volumetric leverage, presses sealed cone piston 21 0 towards spring assembly 204 towards opposite valve 32 end of incoming fluid flow and cone piston body 21 2 and conical valve seat 300 drives towards frusta-conical valve seat 302 causing a tighter seat seal pressure and lessoning the surface area volume leverage advantage to open at the frustoconical seat 300 and 302 from incoming continuous frequency changing hydraulic fluid pressure flow, making a self-progressing or adjusting leverage valve, having a mitigation to control the hydraulic fluid flow to the inner cone piston 21 2 cylinder wall 260 through port 278 and against the inner chamber face of the pump piston 21 0 to manage a slow chamber fill, leaving or savoring the chance for/of more incoming hydraulic fluid into valve 32 with an intense flow frequency fluid pressure to excite or overcome the spring assembly 204 tension and open again the valve frusta- conical valve seat 300 and continue support via stability of the outer periphery of cone piston valve 21 2 larger diameter along the inner wall 272 and slide freely, keeping concentricity and stability to the conical piston valve 21 2.

Further detailing yet another arrangement of fluid flow paths in Fig. 35 amid the primary auxiliary valve 32, hydraulic fluid pressure penetrates the sealing surface (see example of an open check washer 253 Fig. 37, not numbered) of check washer 253 resting or seating under spring 257 tension and against alignment shaft tube 214, fluid enters chamber wall 292 area with encountering a mitigated clicker 206 needle valve port 234, fluid also travels through port 251 and redirects through fluid port 250 preceding through ball detent 252 to later bypass spring could of spring 254 and later pass through bored thread plug, also turning hydraulic fluid flow to enter a circumferential array of ports 298 and penetrate flapper shim stack 291 causing an arc bend of flexible flapper shims 291 (not shown in this static state) , causing fluid to bypass via the bending arc, transporting through the primary auxiliary valve backwards on the inner periphery of the cylinder was 272 and through the seen octagonal shape cutouts or flats (see Fig. 47) or round edge cutouts of the outermost exterior of the conical piston valve 21 2 and exiting the amid section of the primary auxiliary valve through a lateral array of fluid ports 277.

Figure 36 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 further depicting the valve at a shock loaded state showing a more increased opening of the adjuster clicker screw 206 (see FIG. 35) which includes a seal o-ring 224 (see Fig. 35) externally of the clicker making the fluid path more open to hydraulic fluid bleed through bore 234 in the cap body 200 (see FIG. 35) and metering pin 236, showing a fluid path area between the exterior wall of the outer conical valve piston 21 2 and inner wall 272 of the outer base 202 (see FIG. 35) . Conical valve piston 21 2 is movable to a receiving/internal wall bore 272 within having fluid paths formed by outer flutes or flats creating an octagonally engaged and alignment piston bearing guide (see Fig. 47) further depicted for stability and concentricity to that of the inner wall bore 272 of the outer base 202. Also showing in Figure 36 is a fluid flow path through fluid port 277. Port 277 further defines a fluid circuit pattern having pathway ports for hydraulic fluid travelling (not shown) within the primary auxiliary hydraulic fluid valve 32. Also providing one possible beginning state to receive auxiliary fluid in an aggressive form from the shock compression of chamber 76 through port 62 received from mid-valve 22 (see FIG. 1 -1 A) during a

compression stroke with the pump piston sprung to the right and the conical piston body moving to the left and opening a frustoconical flow path formed by an inner frustoconical bore, or valve seat 302 in outer base 202 and conical piston frustoconical seat 300 by which hydraulic fluid passes and moves towards and through an array of flow ports 277. Conical piston valve 21 2 is shown making an end stop against the cap body 200 limiting hydraulic fluid flow through frustoconical seats 300 and 302. Spring assembly 204 shows a more compressed state than that depicted in Fig. 35. One optional use of cone piston valve 21 2 is to seal the back stop edge against an end of the circumferential bore of cone piston valve 21 2 to connect with outer cap 200 and form a temporary stop in hydraulic fluid flow through the center alignment shaft tube body 21 4 in variance of hydraulic frequency blast aiding to push back against cone piston body 21 2. Circumferential chamber 292 communicates with a plurality of individual ports 234 for fluid flow. O-ring seal 258 seals an elongate shaft of body 21 4. Piston 21 0 reciprocates within cone body 21 2. Check valve 220 admits hydraulic fluid into adjuster 32 and fluid ports 276, 278 and 297 direct fluid through respective components. Finally, circumferential groove 274 receives an o-ring seal (not shown) to seal in assembly with the shock absorber cap assembly housing adjuster 32.

Figure 37 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 depicting valve 32 at a shock loaded state further receiving auxiliary fluid from the shock compression chamber 76 (see FIG. 1 A) via stroke of shaft 20 directing fluid through port 62 (see FIG. 1 A) than that depicted in Figure 36 with the pump piston 21 0 receiving fluid pressure via fluid step port 278 moving to the left against the stacked springs 204 as the pumping chamber 260 expands and the conical piston body 21 2 moves right to close the frustoconical flow path through seats 300 and 302 (see FIG. 36). An alignment shaft tube body internal port 246 (see FIG. 35) receives hydraulic fluid pressure via opening of check washer 253 (see FIG. 35) in response to fluid pressure, directing fluid to chamber 292 (see FIG. 35) . pring stack 204 is shown in

compression towards shim stack 291 (see FIG. 5) via step port 278 and chamber 260 expanding against pump piston 21 0, and shim stack 291 is flexing open and allowing fluid to pass through fluid port 298 (see FIG. 35) and past shim stack 291 (see FIG. 35) in response to spring assembly 204 end compressing shims progressively according to cup washer flex compression becoming more flat limiting fluid flow (see FIG. 38) through port 298 and changing from a more check valve opening to a more flex type opening. Alternatively, a cup washer spring in spring assembly 204 can be faced in an opposite direct in order to create a greater resistance of hydraulic fluid pressure through ports 298 (see FIG. 35) . The check ball 252 and fluid port 251 and 250 (see FIG. 35) receive hydraulic fluid pressure that causes ball 252 to open towards spring 254 sending bypass fluid through spring 254 and out threaded set screw 294 until spring 254 exceeds a threshold of hydraulic volume and compresses to a coil bond state limiting flow through its coils. In this manner, an initial fluid flow through spring 254 is greater and a later fluid flow through spring 254 is more restrictive, causing a small but responsive damping curve pressure resistance increase. Fluid ports 276, 278, 297 and 299 are also show relative to check valve 220. Bore 286 and groove 274 are also shown.

Figure 38 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 depicting the conical piston body 21 2 closed, sealing together frustoconical valve piston surface 300 and frustoconical seat 302. Furthermore, the pump piston 21 0 is urged further leftward against the stacked springs 204 than is depicted in Figure 37, causing pump piston 21 0 to become more sealed in the inner bore of the cap body and limiting the flow path. The check ball 252 (see FIG. 35) opens towards spring 254 and check plate 253, thereby mitigating a closing position after the shock absorber mid-valve piston 22 (see FIG. 1 A) has started to return to a rebound state and shims 291 (see FIG. 35) have released the last fluid amount of hydraulic fluid pressure and the check ball 252 (see FIG. 35) has released its last amount of hydraulic fluid pressure.

Pump piston 21 0 is ready to be received via the fast response cone piston valve inner wall 260 and is ready to spring (through spring stack 204) as spring stack 204 becomes expanded again with force towards the flange of alignment shaft tube body 21 4 (see FIG. 35) and fluid moves and an array of circumferential ports 298 (see FIG. 35) will release pressure to make a fast and speedy return of pump piston 21 0 to its far right position (see FIG. 39). Check shim 21 6 (see FIG. 35) has not started to open in Figure 38.

Figure 38A shows an expanded encircled sectional view from Figure 38 having a displaced return flow shim stack 291 in an open position in a maximum open position resting/pressing/flexing against spring stack 204 end tapered cup washer wherein fluid arrayed ports 298 are dispatching hydraulic fluid.

Figure 38B shows an expanded encircled sectional view from Figure 38 where the return check valve washer 21 6 shown in its sealed closed state against port 276 adjacent bore 299 and spring 21 8.

Figure 39 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 depicting the conical piston body 21 2 closed and the pump piston 21 0 urged further leftward away from the compression state stacked springs 204 (see FIG. 38) as they expand further right than that depicted in Figure 37. Concurrently, primary auxiliary valve 32 enters into a full rebound stroke, further receiving hydraulic fluid pressure from interacting reservoir 34 and fl uid chamber 82 (see FIG. 1 A) resulting from air pressure tank chamber 84 pressing air piston 48. Excess fluid transfers from shaft 20 (see FIG. 1 A) and there is a volumetric exchange which occurs through bi-directional fluid port 86 and around the outer base body 202 (see FIG. 35), through the array of fluid ports 277 (see FIG. 35), and out fluid arrayed fluid ports 279 (see FIG. 35) . This opens check stack springs and washers 268, being retained and secured by C-shaped shim 270 in groove 271 (see FIG. 42) , allowing hydraulic fluid pressure from reservoir 34 (see FIG. 1 A) to be received back to compression chamber 76 through port 62. Hydraulic fluid pressure from cone valve piston chamber 260 is quickly returned or exited via larger multiple ports 276 diameters of than that of fluid step port 278 and around check shi m 21 6 compressing check spring 21 8 within chamber bore 299 (see FIG. 35) and out fluid ports 297 wherein the fluid path leads to port 62 (see FIG. 1 A) and then compression chamber 76. Check ball 252 (see FIG. 35) is shown sprung against port 250 (see FIG. 35) making a seal, and shim flapper stack 291 (see FIG. 35) again is at a closed sealed state.

Figure 39A shows a return flow shim stack 291 closed against a fluid flow port 298 and adjacent a spring stack 204 from encircled region 39A of Figure 39.

Figure 39B shows respectively an open return check valve washer 21 6 and compressed check spring 21 8 from encircled region 39B of Figure 39 opening up port 276 for fluid flow.

Figure 40 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 depicting all hydraulic fluid flow valves in closed positions as pump piston 21 0 is rested more towards the right and cone piston 21 2 valve is seated against a frustoconical seat adjacent check valve 220. Figures 40A through 40D show respectively, a closed ball 252 of a check valve mating with a port 250 via a coil spring 254, a closed tapered metering pin 236 on a screw clicker mating to create a seal in bore 234 and axial positioned with co-acting threaded portions 230 and 232, a closed return flow shim stack 291 sealed against ports 298 adjacent spring stack 204, and a closed return check valve washer 21 6 relative to coil sprig 21 8 and fluid flow port 276, as shown in encircled regions 40A through 40D of Figure 40.

Figure 41 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figures 1 -3 depicting all hydraulic fluid flow valves in open positions except check washer 253 (see FIG. 35) which axially slides with an inward through hole bore over a pin shaft sliding on a pin guide shaft and compresses the spring when in an open state. Adjuster 32 shows cone body 21 2 open and pump piston 21 0 closed in relation to check valve 220 from which fluid is exchanged.

Figures 41 A through 41 D show respectively, an open ball check valve 252 with a port 250 and spri ng 254, an open tapered metering pin 236 (and bore 236) set axially with threads 230 and 232, an open return flow shim stack 291 with port 298 and spring stack 204, and an open return check valve washer 21 6 relative to port 276 and coil spring 21 8 shown in encircled regions 41 A through 41 D.

Figure 42 is a perspective centerline sectional view from above of the primary auxiliary hydraulic fluid valve hydraulic fluid valve 32 of Figures 35-41 taken in horizontal section from the flow inlet end showi ng a static valve state and showing clearly the C-shaped end that retains ring shim 270 and check shim stack 220. Adjuster 206 is shown in cap 200. Ports 250, 251 , ball 252, and spring 292 are shown. Also shown , the tip end of the cone piston valve 21 2 and center port 246 in the inlet view perspective on alignment shaft tube body 21 4 and outer periphery perspective of the primary auxiliary valve 32 and o-ring groove 274 separating the flow ports 277 and port 275. Flow port 275 can be drilled or placed in the end of outer base in any location to provide a non-sealed pressure regulating seat as it is necessary to connect to fluid return ports 279 (see FIG. 35) or at least one port of ports 279 and bypass an inner edge of the check shim stack 220. This means that the fluid bleed port 275 may be at an angle when drilled. In this manner, fluid bleed port 275 retains at a specific frontal position connection proximation to fluid ports 279 (see FIG. 35) and drilled to a specific desired bleed orifice to arrange the desire resistance to a pre- pressured valving resistance. Optionally, hydraulic fluid towards bleed port 275 and outer groove can be made in the outer periphery of the outer base 202 and can wrap arou nd the front edge of outer base 202 around the check shim stack 220 and groove 271 . A more precise bleed port 275 is made using a drilled or machined hole. Frustoconical piston surface 300 and seat 302 are also shown in a closed position.

Figure 43 is an angled side view from above of the sectioned primary auxiliary hydraulic fluid valve hydraulic fluid valve 32 of Figure 42 showing the tapered outer periphery of outer base 202 which creates a surface gap between the inner bore of body 1 6 (see FIG. 1 A). Primary auxiliary valve 32 is placed in the body and allows fluid bypass in a volumetric balance with that of fluid ports 277 and port 86 (see FIG. 1 A) . In this manner, fluid can achieve a reasonable fluid volume bypass around the outer periphery of outer base 202 and within the bore in body 16, not exceeding a pressure threshold in that of the shock body 1 6 component and that of the outer base 202 wall thickness. Pump piston 21 0 is shown closed and cone body 21 2 is shown closed. Port 275 and groove 274 are also shown adjacent check valve 220.

Figure 43A is an enlarged view of the check valve 32 with the shim assembly 220 and discharge port 277 showing in part the circumferential array of ports 275 and 277 from encircled region 43A of Figure 43.

Figure 44 is a centerline sectional side view of the primary auxiliary hydraulic fluid valve 32 and its outer assembly perspective view of Figure 42 in centerline section showing cap 200 joined to base 202 and illustrating position of ports 275 and 277 and groove 274.

Figure 44A is an enlarged view of a centerline sectional view of a discharge port 277, an assembly bleed port 275, and groove 274 from encircled region 44A of Figure 44.

Figure 45 is a centerline sectional view of the primary auxiliary hydraulic fluid valve 32 as shown in section in Figure 41 depicting all hydraulic fluid flow valves in open positions except spring 257 preloaded into check valve 253 (see FIG. 35) . More particularly, spring stack 204 is not compressed as pump piston 21 0 is not displaced and cone body 21 2 is open, providing a frustoconical gap between surfaces 300 and 302. Spring 21 8 is compressed by check shim 21 6 as fluid flows through port 276 and out port 297. Groove 274 and port 275 are shown proximate check valve 220. Figure 46 is an exploded vertical centerline sectional view of the primary auxiliary fluid valve 32 of Figures 35-45 showing adjuster 206, C-ring 208, cap 200 (having ball 252, spring 254, and plug 294) , shim stack 291 , spring stack 204, pump piston 21 0, body 214, check shim 21 6, spring 21 8, cone body 21 2, base 202, spring 268, and lock ring 270.

Figure 47 is an exploded perspective view from above of the inlet end of the primary fluid valve 32 of Figures 35-46 showing adjuster 206, C-ring 208, cap 200, shim stack 291 , spring stack 204, pump piston 21 0, body 21 4, cone body 21 2, base 202 (with ports 275, 277, and 279) , spring 268, and lock ring 270.

Figure 48 is an exploded perspective view from above of the adjuster end of the primary fluid valve 32 of Figures 35-47 showing adjuster 206, C-ring 208, cap 200, shim stack 291 , spring stack 204, pump piston 21 0, body 21 4, check shim 21 6, spring 21 8, cone body 21 2, base 202, spring 268, and lock ring 270. Figure 49 is a vertical centerline sectional view of the exploded perspective view from above of the inlet end of the primary fluid valve 32 of Figure 35-48 showing adjuster 206, C-ring 208, cap 200, shim stack 291 , spring stack 204, pump piston 21 0, body 214, cone body 21 2, base 202, spring 268, and lock ring 270.

Figure 50 is a vertical centerline sectional perspective view of the exploded perspective view above of the adjuster end of the primary fluid valve 32 of Figure 35-49 showing adjuster 206, C-ring 208, cap 200 (with ball 252, spring 254, and plug 294) , shim stack 291 , pin 255 and spring 257, spring stack 204, pump piston 21 0, body 214, check shim 21 6, spring 21 8, cone body 21 2, base 202, spring 268, and lock ring 270.

Figure 51 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve 30 as shown in section in Figures 1 -4 depicting the valve 30 at a shock unloaded, or resting state before receiving any auxiliary fluid from the shock absorber 1 0 (see Fig. 1 A) with the pump piston sprung to the left. More particularly, a housing for valve 30 is provided by cap 400 and outer base 402 which are secured together when they are inserted into end cap assembly 1 6 (see Fig. 1 A) and male threads 438 are secured into complementary female threads in the end cap assembly, trapping the assembly of cap 400 and base 402 within such assembly housing. A base plate tubular member 468 is secured in press-fit relation to outer base 402. An o- ring seal 470 seal the leading end of valve 30 when inserted and assembled within a complementary bore within end cap assembly 1 6 (see Fig. 1 A) . Another o-ring seal 463 is carried by cap 400 adjacent threaded male portion 438 configured to further seal valve 300 within a receiving bore in end cap assembly 1 6 (see Fig. 1 A) . A flow restricting port 447 is provided through member 468 in fluid

communication with bore 446. A preload tension adjuster seat collar 41 0 is secured inside of cap 400 with a threaded male segment, or threads 442 that are mating with a complementary threaded female segment, or threads 440. Another o-ring seal 461 seals seat collar 41 0 inside of bore 445 within cap 400.

As shown in Figure 51 , slider valve 41 4 is carried is slidable sealed relation within seat collar 41 0 and tube member 468 via o-ring seals 459, 464, and 469. Slider valve 41 4 includes a radial outwardly extending and integrally formed outer slider seal piston 41 6 having a radial outer edge groove sized to receive o-ring seal 464. Piston 41 6 reciprocates in sliding and sealed relation within a cylindrical bore 492 internally of collar 41 0. A circumferential array of lugs 409 on collar 41 0 enable a gripping tool to mate and rotate collar 41 0 within cap 400 to a desired axial position.

Fluid flow volume adjuster 406 of Figure 51 is carried in a proximal end of seat collar 41 0 via mating complementary male threaded portion 432 and female threaded portion 430 within a bore of collar 41 0. A ball 426 and cylindrical coil spring 426 are provided in a bore (not numbered) within adjuster 406 such that a circumferential array of elongate grooves 444 in a bore of collar 41 0 provide a

"clicker" discrete for setting a threaded position of adjuster 406 at any one of a plurality of discrete axial locations relative to collar 41 0. In this manner, a distal metering pin 436 of adjuster 406 can be repeatable set to one a plurality of axial locations relative to a fluid flow bore 434 in order adjust the annular orifice size provided by axial positioning of adjuster 406. Metering pin 436 and bore 434 are provided coaxially within a cylindrical inner slide seal piston 41 8 of adjuster 406 that reciprocates in sealed relation within a cylindrical bore 488. Bore 434 is ensmalled towards a distal end to provide greater material in piston 41 8 for mounting o-ring seal 469.

A pump piston 41 2 is carried for sealed reciprocation with a cylindrical bore 460 within outer base 402 in order to provide a fluid cushion as well as a stored fluid capacitor when spring stack 204 has been compressed via movement of piston 41 2 into spring stack 204 and later released. Piston 41 2 includes a circumferential outer periphery groove sized to contain an o-ring seal 465. Piston 41 2 also contains an inner periphery groove sized to contain another o-ring seal 467. A radially outwardly extending a circumferentially equally spaced apart array of bores 474 provide fluid flow from about metering pin 436 into a circumferential chamber 480 to drive pump piston 41 2 into compression with spring stack 204 during certain shock loading conditions. Another bore 476 is provided through slider piston 41 6 to prevent hydraulic lock-up of slider piston 41 6. Bore 476 has a reduced diameter portion 478 sized to realize a desired fluid flow rate. Finally, base 402 includes a circumferential array of equally spaced apart ports 475 in thickened wall portion 466 into chamber 88 and cross port 92 (of Fig. 4A).

Figure 52 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve 30 as shown in section in Figures 1 -3 depicting the valve at a shock loaded state beginning to receive auxiliary fluid from the shock with the pump piston 41 2 positioned all the way left and the slider valve, or inner slider seal piston 41 8 moving to the left and opening a frustoconical flow path. Preload tension adjuster seat collar 41 0 is shown extended outwardly to the left. Figure 53 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve 30 as shown in section in Figures 1 -3 depicting the valve at a shock loaded state further receiving auxiliary fluid from the shock than that depicted in Figure 53 with the threaded preload tension adjuster seat collar 41 0 compressing the cup washers creating a firmer starting point for the cup washers 204 by displacing pump piston 41 2 to the right and further limiting travel of the pump piston 41 2. Inner slider seal piston 41 8 is shown displace fully to the right.

Figure 54 is a centerline sectional view of the secondary auxiliary hydraulic fluid valve 30 as shown in section in Figures 1 -3 depicting the initial state but having more preload on the cup washers 404 (spring) set by the preload tension adjuster seat collar 41 0 than that depicted in Figure 51 . Pump piston 41 2 is only slightly displaced to the right, slightly compressing spring stack 404. Piston 41 8 is also move fully to the right.

Figure 55 is a vertical centerline sectional view through the secondary fluid valve 30 of Figure 54 but later in time and showing the fluid fully compressing the cup washers 404 and not completely compressing the slider valve 41 4.

Figure 56 is an exploded vertical centerline sectional view of the secondary auxiliary fluid valve 30 of Figures 51 -55 showing adjuster 406, C-clip 408, cap 400, collar 41 0, slider valve 414, pump piston 41 2, spring stack (of cup washers) 404, outer base 402, and base plate 468 (with o-ring seal 470) .

Figure 57 is an exploded side view of the secondary auxiliary fluid valve 30 of Figures 51 -56 showing adjuster 406, C-clip 408, cap 400, collar 41 0, slider valve 414, pump piston 41 2, spring stack (of cup washers) 404, outer base 402, and base plate 468 (with o-ring seal 470) .

Figure 58 is an exploded and perspective vertical centerline sectional view of the secondary fluid valve 30 from the inlet end of Figures 51 -57 showing adjuster 406, C-clip 408, cap 400, collar 41 0, slider valve 414, pump piston 41 2, spring stack (of cup washers) 404, outer base 402, and base plate 468 (with o-ring seal 470) .

Figure 59 is an exploded and perspective view of the secondary fluid valve 30 from the inlet end of Figures 51 -58 showing adjuster 406, C-clip 408, cap 400, collar 41 0, slider valve 414, pump piston 41 2, spring stack (of cup washers) 404, outer base 402, and base plate 468 (with o-ring seal 470) .

Figure 60 is an exploded and perspective centerline sectional view of the secondary fluid valve 30 from the adjuster end of Figures 51 -59 showing adjuster 406, C-clip 408, cap 400, collar 41 0, slider valve 41 4, pump piston 41 2, spring stack (of cup washers) 404, outer base 402, and base plate 468 (with o-ring seal 470) . Figure 61 is an exploded and perspective view of the secondary fluid valve 30 from the adjuster end of Figures 51-60 showing adjuster 406, C-clip 408, cap 400, collar 410, slider valve 414, pump piston 412, spring stack (of cup washers) 404, outer base 402, and base plate 468 (with o-ring seal 470).

Figure 62 is an end view of yet another alternative mid-valve piston assembly 1022 for a shock absorber according to another construction, such as for a front fork mid-valve shock on a motorcycle.

Figure 63 is a vertical sectional view of the mid-valve piston 1022 taken along line 63-63 of Figure 62 showing in vertical cross section one pair of rebound ports 1096 which are formed in a circumferential equally spaced apart array extending through piston body 1100. A piston body 100 along with a ducted support housing 1142 (including flow ports 1106) and a cylindrical housing 1128 are trapped in stacked relation onto piston rod, or shaft 1020 between a rebound nut 1084 and fluid directing collar 1068. Collar 1068 has a cylindrical array of radially inwardly extending discrete locking fingers 1076 (also see Fig.80) on a proximate end of shaft 1020 adjacent to piston 1100 that engage shaft 1020 where shaft 1020 increases in diameter, preventing movement of collar 1068 away from piston 1100. A shim stack 1098 seals ports 1096 until rebound motion of piston 1022 in a shock absorber tube urges and flexes individual springs 1099 of stack 1098 to flex and open ports 1096 for fluid flow.

In a compression mode, fluid enters a bi-directional metering hole 1088 and goes through a metering orifice 1107. Fluid

communicates with bore 1108 of female rebound tube 1080 and reduced bore 1110 where is passes out of ports 111 or exits between a cylindrical end of bore 1110 and a metering pin end of rebound needle 1042. Fluid also enters compression ports 1096 into an annular volumetric expansion chamber 1116 where the compression fluid reacts with an inner frustoconical piston 1112 and an outer frustoconical piston 1114, similar to the manner in which pistons 112 and 114 behave in the mid-valve piston of shock absorber 10 depicted variously in Figures 1-61. Pistons 1112 and 1114 are spring into engagement with seats on piston body 1100 via compression of springs 1138 and 1140. As springs are compressed from compression fluid flow, springs 1138 and 1140 are compressed and annular flow paths open between springs 1112 and 1114 (as previously discussed with reference to pistons 112 and 114 in Figures 1-61). However, fluid passes down radial ports 1115 pass into a circumferential channel 1118 where it passes out ports 1120 behind pistons 1138 and 1140, causing such pistons 1138 and 1140 to be urged into springs 1138 and 1140, compressing such springs as pistons translate toward piston body 1100 and causing pistons 1112 and 1114 to close against piston body 1100 and close related fluid flow paths. A rubber or plastic spring stop bushing 1066 is carried on shaft 1020 and receives a coil spring (not shown) in assembly to prove shock absorption in the event that piston assembly reached a maximum stroke position.

Finally, a shim stack 1113 resists and regulate fluid flow from between inner piston 1112 and piston body 1100.

Figure 64 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 65-65 of mid-valve piston assembly 1022 for a shock absorber.

Figure 65 is a compound sectional view of the mid-valve piston 1022 of Figures 62-63 showing both a compression port 1094 and a rebound port 1096.

Figure 66 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 67-67 of mid-valve piston assembly 1022 for a shock absorber.

Figure 67 is a compound sectional view of the mid-valve piston 1022 of Figures 62-63 showing both a compression port 1094 and a rebound port 1096 at a beginning state with no fluid flow. Figure 67C is an enlarged encircled region view showing the rebound flapper shims in a closed position.

Figure 67D is an enlarged encircled region view showing the check valve in a closed position.

Figure 67E is an enlarged encircled region view showing the outer conical piston body closed against the outer piston frustoconical seat.

Figure 67F is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat. Figure 67G is an enlarged encircled region view showing a motion limiting gap between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 67H is an enlarged encircled region view showing the inner cone flapper shim stack closed (and preloaded) against the rear surface of the inner cone.

Figure 67M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions. Figure 68 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 69-69 of mid-valve piston assembly 1 022 for a shock absorber.

Figure 69 is a compound sectional view of the mid-valve piston 1 022 of Figures 62-67 showing both a compression port 1 094 and a rebound port 1 096 at a later state than shown in Figure 67 with more fluid flow at a later point in time.

Figure 69C is an enlarged encircled region view showing the flapper shims in a closed position. Figure 69D is an enlarged encircled region view showing the check valve in a closed position.

Figure 69E is an enlarged encircled region view showing the outer cone partially open relative to the outer piston frustoconical seat.

Figure 69F is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat.

Figure 69G is an enlarged encircled region view showing a motion limiting gap decreasing in size over that shown in Figure 67G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 69H is an enlarged encircled region view showing the inner cone flapper shim stack closed (and preloaded) against the rear surface of the inner cone. Figure 69M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

Figure 70 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 71 -71 of mid-valve piston assembly 1 022 for a shock absorber.

Figure 71 is a compound sectional view of the mid-valve piston 1 022 of Figures 62-69 showing both a compression port 1 094 and a rebound port 1 096 at a later state than shown in Figure 69 with yet even more fluid flow and the initiation of pump piston movement to initiate shutting of the outer conical piston.

Figure 71 C is an enlarged view from the encircled region and showi ng the flapper shims in a closed position . Figure 71 D is an enlarged view from the encircled region and showi ng the check valve in a closed position.

Figure 71 E is an enlarged encircled region view showing the outer cone partially open relative to the outer piston frustoconical seat.

Figure 71 F is an enlarged encircled region view showing the outer cone partially open relative to the outer piston frustoconical seat.

Figure 71 G is an enlarged encircled region view showing a motion limiting gap same in size over that shown in Figure 69G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 71 H is an enlarged encircled region view showing the inner cone flapper shim stack being urge and flexed by rearward movement of the rear surface of the inner cone.

Figure 71 M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

Figure 72 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 73-73 of mid-valve piston assembly 1 022 for a shock absorber.

Figure 73 is a compound sectional view of the mid-valve piston of Figures 62-71 showing both a compression port and a rebound port at a later state than shown in Figure 71 with fluid flow restriction where the outer conical piston is closed.

Figure 73C is an enlarged view from the encircled region and showi ng the flapper shims in a closed position . Figure 73D is an enlarged view from the encircled region and showi ng the check valve in a closed position.

Figure 73E is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat to form gap 1 1 82.

Figure 73F is an enlarged encircled region view showing the outer cone partially open relative to the outer piston frustoconical seat to from gap 1 1 86.

Figure 73G is an enlarged encircled region view showing a motion limiting gap increasing in size over that shown in Figure 71 G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 73H is an enlarged encircled region view showing the inner cone flapper shim stack being urge and flexed by rearward movement of the rear surface of the inner cone.

Figure 73M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

Figure 74 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 75-75 of mid-valve piston assembly 1 022 for a shock absorber.

Figure 75 is a compound sectional view of the mid-valve piston 1 022 of Figures 62-73 showing both a compression port 1 094 and a rebound port 1 096 at a later state than shown in Figure 73 with fluid flow restriction allowing bypass where the outer conical piston is opening again in response to a threshold excessive force.

Figure 75C is an enlarged view from the encircled region and showi ng the flapper shims in a closed position . Figure 75D is an enlarged view of the encircled region and showi ng the check valve in a closed position.

Figure 75E is an enlarged encircled region view showing the outer cone fully open relative to the outer piston frustoconical seat. Figure 75F is an enlarged encircled region view showing the outer cone partially open relative to the outer piston frustoconical seat.

Figure 75G is an enlarged encircled region view showing a motion limiting gap completely closed over that shown in Figure 73G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 75H is an enlarged encircled region view showing the inner cone flapper shim stack being urge and flexed by rearward movement of the rear surface of the inner cone. Figure 75M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

Figure 76 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 77-77 of mid-valve piston assembly 1 022 for a shock absorber.

Figure 77 is a compound sectional view of the mid-valve piston 1 022 of Figures 62-75 showing both a compression port 1 094 and a rebound port 1 096 at a later state than shown in Figure 75 with fluid flow restriction allowing bypass where the outer conical piston is opening again in response to a threshold excessive force.

Figure 77C is an enlarged view of the encircled region and showi ng the flapper shims in an open position. Figure 77D is an enlarged view of the encircled region and showi ng the check valve in an open position .

Figure 77E is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat.

Figure 77F is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat.

Figure 77G is an enlarged encircled region view showing a motion limiting gap same as that shown in Figure 67G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 77H is an enlarged encircled region view showing the inner cone flapper shim stack closed (and preloaded) against the rear surface of the inner cone.

Figure 77M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to one of a plurality of potential open positions.

Figure 78 is an end view from the rebound end showing the support housing and housing flow ports and compound sectional view taken along compound line 79-79 of mid-valve piston assembly 1 022 for a shock absorber.

Figure 79 is a compound sectional view of the mid-valve piston of Figures 62-77 showing both a compression port and a rebound port at a later state than shown in Figure 77 with fluid flow restriction allowing bypass where the outer conical piston is opening again in response to a threshold excessive force.

Figure 79C is an enlarged view of the encircled region and showi ng the flapper shims in a closed position .

Figure 79D is an enlarged view of the encircled region and showi ng the check valve in a closed position. Figure 79E is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat.

Figure 79F is an enlarged encircled region view showing the outer cone closed against the outer piston frustoconical seat.

Figure 79G is an enlarged encircled region view showing a motion limiting gap same as that shown in Figure 79G between a back surface of the outer piston body and the outer sleeve travelling limiting radially inwardly extending shoulder.

Figure 79H is an enlarged encircled region view showing the inner cone flapper shim stack closed (and preloaded) against the rear surface of the inner cone.

Figure 79M is an enlarged encircled region view showing the rebound metering fluid needle and tube seat adjusted to a completely closed position.

Figure 80 is an exploded and perspective vertical centerline sectional view of the secondary fluid valve 1 022 from the inlet end of Figures 63-79 showing nut 1 066 with threads 11 50 assembled together onto female rebound tube 1 080 with stop plate 1 067, spring 1 092, and check valve washer 1 090 entrapped there between. A rebound nut assembly 1 084 includes a bi-directional fluid metering hole, or bore 1 088, a circumferential array of rebound circuit fluid ports 1 086, and female threads 11 44. A spacer ring 1 078 stacks up against a rebound shim stack assembly 1 098 that is seated against a piston body 1 1 00, selectively blocking ports 1 096 unless the

cylindrical springs, or flex washers (or shim flappers) 1 099 of shim stack assembly 1 098 are flexed and urged away form an adjacent surface of piston body 1 1 00 from flu id pressure exerted via ports 1 096. Piston body 1 1 00 also carries a piston band 1 1 02 and a compression o-ring seal 1 1 04. An opposed rear face of piston body 1 100 provides an inner frustoconical seat 1 1 92 and an outer frustoconical seat 1 1 94 spaced across a circumferential an annular volumetric expansion chamber 1116. Compression ports 1094 are also provide through piston body 1100. A proximal end of a female rebound tube 1080 threads within female threads 1146 within shaft 1020. An inner cone piston 2112 carries an inner frustoconical seal, or seat 1188 that mates and demates in sealing relation with seat 1192 in operation. Male threads 1144 mate with female threads 1144 in assembly. An inner cone compression shim stack 1113 is stacked between a round spacer and a front end of a base plate cover 1101. Outer cone piston 2114 has a frustoconical piston surface 1190 configured to mate and demate in sealing relation with complementary seat 1194. Piston rod end, or shaft 1082 extends coaxially through a ducted support housing 1142 having a circumferential array of through flow ports 1106. An outer spring stack (of wave springs) 1140 and an inner stack (of wave springs) 1138. An axially adjustable (via co acting threaded portions) metering pin 1042 with a tapering conical tip extends within piston rod, or shaft 1020. An outer pump piston 1112 and an inner piston pump 1114 reciprocate coaxially within cylindrical housing 1128. A radially inwardly turned discrete array of fingers 1076 on a fluid directing collar 1068 facilitate entrapped assembly of adjacent parts. A circumferential array of ports 1074 and 1139 in collar 1068 facilitate fluid flow and o-ring seals 1070 and 1072 provide sealed assembly between adjacent parts. A rubber or plastic cylindrical bump stop 1056 is provide on shaft 1020 to mitigate any over-stroke shock transmission.

Figure 81 is a perspective view from above of yet another alternative primary compression adjuster for a shock absorber according to another construction.

Figure 81 A is an enlarged perspective view of the end portion for the primary compression adjuster taken from encircled region 81A from Figure 81.

Figure 81 B is a plan view of the end portion for the primary compression adjuster. Figure 82 is a centerline sectional view of the primary

compression adjuster taken along line 82-82 of Figure 81 B.

Figure 82A is an enlarged encircled portion centerline sectional view of the primary compression adjuster of Figure 82.

Figure 83 is an end view of yet even another alternative mid valve 1 322 for a shock absorber 1 0 mid-valve piston assembly 22 (see Fig 1 A-Fig. 34) and respectively (see Fig.63 - Fig. 80) according to another construction

Figure 84 is a vertical centerline sectional view of Figure 83 alternative mid-valve 1 322 according to another construction for a bicycle fork or motorcycle fork mid-valve piston assembly

respectively semi mimicking many operations with some minor function differences of Figures 63-80 (see Fig.63 - Fig. 80) taken along line 84 -84 of Figure 83 showing in vertical cross section a rebound port 1 396 which is formed in a circumferential equally spaced apart array extending through a piston body 1400 of piston assembly 1 322. Piston body 1 400 includes a circumferential array of

compression ports 1 394 and rebound ports 1 396. A piston band 1 302 is provided circumferentially about piston body 1 400. Compression ports 1 394 communicate with a common circumferential chamber 1 383. The piston body 1400 along with a threaded shaft 1 320 on each end, having a stepped longitudinal shaft 1 320 stepping down in dimension to the left, starting from the large periphery diameter on the right a left facing flange and looking to the left, having a

circumferential connecting groove to the rebound vertical bores interconnecting with shaft inner bore 1 308 and a larger o-ring outer periphery holding groove that is a dual sided groove having a channel for the o-ring to bound and fitting in to the outer periphery groove diameter and looking further to the left to a smaller shaft diameter with a circumferential array of ports leading from inner shaft through bore 1 308, to exterior of the shaft 1 320 and having another smaller diameter to the left for holding a cylindrical washer spacer and making a first stop face lip on the shaft 1 320 and yet a next smaller shaft diameter making a second step stop face to hold against the piston valve 1400 inner bore face and where the small end shaft rod extends through the piston valve and rebound shim assembly that is not threaded and ending with a threaded outer dimension and end of piston rod shaft stem 1 320, having a rebound nut 1 366 with female mating thread connecting via mating shaft stem 1 320 end the small end thread on smallest shaft diameter trapping the mid-valve assembly 1 322 to the shaft stem 1 320 in the area between the left facing flange to the nut.

Mid-valve assembly 1 322 traps within the shaft stem 1 320 starting at the right and moving towards the left from the left facing flange to the left end threads and end rebound nut 1 366 an inner pump piston 1 31 4 and sealing o-ring groove towards the inner dimension of the inner pump piston 1 31 4 bore and having an inner bore step self-facing the right towards the pump fluid ports and having an equally spaced circumferential array of notches to the more right making the inner pump piston sealed and cylindrically slidable to the shaft stem 1 320 via an o-ring cylindrically fitting in the groove of inner pump piston, an outer pump piston 1 31 2 with inner and outer cylindrical sliding capability fitting over the inner pump piston 1 31 4 to make a tight tolerance inner seal slide fit to mate with inner pump piston 1 314 and an outer periphery diameter slidably fit to mate with an outer housing 1 302 having inner bore with a seal slide fit to the outer periphery of the outer pump piston 1 31 2 mating to the outer housing 1 302 cylinder forming a high tolerance slide fit, the outer housing 1 302 has an inner bore that cylindrically reciprocates over the o-ring dual sided periphery and seals via the captured o-ring allowing an ability to slide to the left and to the right concerning a compression stroke or a rebound stroke, during a rebound stroke outer housing 1 302 slides to the left allowing fluid to pass via the rebound groove at that of the rebound vertical port location and enter shaft stem 1 320 the vertical rebound ports and bypass a rebound needle metering pin assembly 1 342 and an inner end bore seat in the shaft stem 1 320 inner bore 1 308 and through bore 1 308 as one pathway. During a compression stroke, outer housing 1 302 slides to the right making a seal against the left facing flange of the shaft stem 1 320 and the right end of the pump housing 1 302 sealing about the rebound end on the shaft stems 1 320 left facing flange and having an outer periphery right end bleed port located in the outer housing 1 302 about the rebound groove of the pump housing 1 302, allowing a metered flow of compression stroke bleed to exit as it goes through port 1 308 and towards the rebound metering pin assembly 1 342 from the compression end of the mid-valve piston assembly 1 322 and also causing hydraulic fluid pressure to enter the circumferential array of pump fill ports in the shaft stem 1 320 into the sealed housing chamber causing a hydraulic fluid pressure to build and expand with acting force, causing the outer pump piston 1 31 2 which is a larger diameter and having a larger surface area volumetric rate of expansion and a larger diameter spring which uses a lesser angle of coil and typically the coil wire is longer because of the larger diameter making a softer spring than that of an inner spring, urges the outer pump piston 1 31 2 to the left compressing the outer spring 1 340 against a spacer washer 1 380 seated against a larger internal bore of the piston valve 1 400 and seating against a ledge portion of the cone piston tube which are set to equal a same flat havi ng that of a similar inner tolerance to that of the outer surface of the cone piston tube 1 368 extends the tube body further out of the cone piston making a second partial seal when pressing towards a right facing ledge a of the cone piston tube equally leveled with a larger depth bore of the piston valve 1400, creating a mating surface more secure seal to slow hydraulic fluid bypass through outer portion of the cone piston tube 1 368 external circumferential flats about the most outer periphery making a check valve opening of the spacer washer during a first compression stroke volume bypass of fluid from compression side(see Fig 1 A) of the piston valve, when outer spring 1 340 is in a free floating non compressed state and a second firming in fluid flow resistance as outer pump piston urges the outer spring toward the spacer washer 1 380. Once the outer spring 1 340 has started to move relative to the pump hydraulic fluid pressure, the inner pump piston 1 31 4 acts to compress the step washer and urge the small spring 1 331 until shim spacer seats against the more right end of the cone piston tube 1 368, and to hold middle spring 1 330 at a loaded state but not excessively urging an inner pump spring 1 330 to slowly build hydraulic fluid pressure towards the left, as the outer pump travels to the left a circumferential array of side bleed ports the outer periphery wall of the pump housing 1 302 set to distribute hydraulic fluid pressure by allowing fluid to exit as the outer pump piston 1 31 2 moves towards the left, outer periphery holes take hydraulic fluid pressure to a lesser pressure slowing the action of the outer pump piston, causing a balance of hydraulic fluid pressure of the inner pump piston until the outer pump piston has traveled to the furthest left position and pump housing side periphery bleed ports allow the escape of more hydraulic fluid volumetric pressure that than which enters the hydraulic fluid pump via the circumferential array of the fill ports extending to the into the pump housing chamber. 1 31 4 wherein the end allows hydraulic fluid pressure to travel from inner pump shaft bore 1 308 and to the right most end of the inner pump piston 131 4 expanding outward to an outer pump piston 1 31 2 with inner and outer cylindrical sliding capability fitting over the inner pump piston 1 31 4 to make a tight tolerance inner seal slide fit to mate with inner pump piston 1 314 and an outer periphery diameter slidable fit to mate with the outer housing 1 302 inner bore with a seal slide fit on the outer periphery of the outer pump piston 1 31 2 mating to the outer housing cylinder forming a high tolerance slide fit, an inner pump piston 1 31 4 bore and having an inner bore step self-facing the right towards the pump fluid ports and having an equally spaced circumferential array of ports. Also trapped in the mid-valve assembly 1 322, an inner spring

1 330 is cylindrically fit over the shaft wherein right end

connects/mates to the inner pump piston 1 31 4 and the left end faces and mates to a shim spacer, the shim spacer mates to the step washer and step washer mates to the spring 1 331 fitting and cylindrically slidable over shaft stem 1 320 and is preloaded against a piston valve tube or piston cone tube or cone piston tube 1 368 also cylindrically slidable on the shaft stem 1 320, the piston valve tube is an extended tube with a cupped slidable inward faci ng flange end wall and inner bore to house the spring 1 331 and step washer keeping the piston valve tube concentric and slidable on the shaft stem 1 320 also having a circumferential array of side ports from inner cone piston tube 1 368 bore to the outer wall allowing trapped hydraulic pressure to escape. A piston valve tube 1 368 seats about a step washer, or ring collar 1 324 to entrap a coil spring 1 331 .

Claims

CLAIMS The invention claimed is:

1 . A shock absorber, comprising:

a cylinder filled with a fluid;

a piston rod reciprocating within the cylinder;

a piston body;

a valve carried by the piston body having:

at least one flow port through the piston body and communicating with a compression chamber end of the valve body;

a first valve seat formed at least in part by the piston body;

a second valve seat formed at least in part by the piston body;

an annular valve chamber defined in part by the piston body and fluid coupled with the at least one flow port;

at least one circumferential valving element configured to mate and demate with the first valve seat and the second valve seat; and

at least one spring configured to urge the at least one valving element in movable mating and demating relation against the first valve seat and the second valve seat, the at least one valve seat demated from the first valve seat and the second valve seat

responsive to fluid pressure in the annular valve chamber

compressing the at least one spring to provide a first fluid flow path and a second fluid flow path at least one of radially inwardly and outwardly of the first fluid flow path, and forming a first fluid flow path with a first flow diversion angle and a second fluid flow path with a second flow diversion angle less than the first flow diversion angle; and 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.

2. A shock absorber piston , comprising:

a piston body; and

a valve carried by the piston body having:

an annular volumetric expansion chamber defined in part by the piston body and fluid coupled with the at least one flow port;

a first annular valve seat carried by the piston body proximate the annular volumetric expansion chamber;

a second annular valve seat carried by the piston body proximate the annular volumetric expansion chamber;

at least one valving element configured to mate and demate with the first valve seat and the second valve seat; and

at least one spring configured to urge the at least one valving element in mating and demating relation against the first valve seat and the second valve seat, the at least one valving element demated from the first valve seat and the second valve seat responsive to fluid pressure in the annular volumetric expansion chamber to compress the at least one spring and provide a first fluid flow path having a first flow diversion angle and a second fluid flow path with a second flow diversion angle less than the first flow diversion angle.

3. A shock absorber valve, comprising:

a valve body having an axial bore forming an annular valve seat at one end;

an outer piston carried in the axial bore having an inner axial bore opposite the valve seat;

an inner piston slidably received in the axial bore of the outer piston and cooperating with the outer piston axial bore to define a variable volume reservoir;

a spring seated against the inner piston to urge the inner piston and the outer piston biased towards the annular valve seat;

a compression fluid passage extending from proximate the valve seat through the outer piston to the variable volume reservoir; and

a rebound fluid passage having a one-way check valve extending from the variable volume reservoir through the outer piston proximate the valve seat.

4. An auxiliary damping valve for a shock absorber, comprising:

a valve body having a hydraulic cylinder;

a freely reciprocating first piston movable axial ly within the cylinder;

a biased second piston provided in the cylinder adjacent the first piston defining an expansible fluid chamber between the first piston and the second piston;

a spring disposed between the second piston and one end of the cylinder configured to urge the second piston towards the expansible fluid chamber; and

a fluid flow passage extending from a compression chamber of a shock absorber into the expansible fluid chamber to provide a sprung fluid capacitive storage for the shock absorber.

5. A shock absorber, comprising:

a cylinder configured to receive fluid;

a piston rod;

a piston body connected to the piston rod and configured to reciprocate within the cylinder between a compression chamber and a rebound chamber;

a valve provided by the piston body having a fluid flow port, a valve seat, a circumferential valving element, and a spring configured to urge the valve body into the valve seat.

6. The shock absorber of claim 5, wherein the valve seat is a frustoconical valve seat.

7. The shock absorber of claim 5, wherein the

circumferential valving element is a frustoconical piston valve surface.

8. The shock absorber of claim 5, wherein a pair of

cylindrical piston bodies are provided with a pair of complementary valve seats.

9. The shock absorber of claim 8, wherein one of the piston bodies is a cylindrical outer piston body and another of the piston bodies is a cylindrical inner piston body.

1 0. The shock absorber of claim 9, wherein the inner piston body is carried for reciprocation coaxially within the outer piston body.

1 1 . The shock absorber of claim 1 0, wherein a circumferential valve is provided between the inner piston and the outer piston.

1 2. The shock absorber of claim 1 1 , wherein the

circumferential valve is a one-way valve.

1 3. The shock absorber of claim 1 2, wherein the

circumferential valve is an o-ring seal carried in a circumferential channel within at least one of the first piston and the second piston having an ensmalled upper sealing portion and an enlarged lower flow portion .

14. The shock absorber of claim 5, wherein a proximal end of the spring communicates with the piston and a distal end of the spring communicates with an expansible chamber having a movable piston provided for reciprocation within the chamber and the piston seats against the distal end of the spring to compress the spring and seat the valve element against the valve seat.

1 5. The shock absorber of claim 14, wherein a fluid flow path is provided from the piston body to impart fluid pressure to the chamber to move the piston against the spring.

1 6. The shock absorber of claim 14, wherein a pair of cylindrical piston bodies are provided with a pair of complementary valve seats and a pair of springs and expansible chambers each having a movable piston are provided for reciprocation within the chamber and the piston seats against the distal end of the spring to compress the spring and seat the valve element against the valve seat.

1 7. The shock absorber of claim 1 6, wherein a first movable piston urges a first spring to urge the first valvi ng element against the first valve seat.

1 8. The shock absorber of claim 1 7, wherein a second movable piston urges a first spring to urge the second valving element against the second valve seat.

1 9. The shock absorber of claim 5, wherein the piston body includes a circumferential array of compression ports for fluid flow in a first direction and a second circumferential array of rebound ports for fluid flow in a second direction.

20. The shock absorber of claim 1 9, wherein at least one of the array of compression ports and the array of expansion ports are configured in fluid communication with an annular volumetric

expansion chamber.