Apparatus to adjust a hydraulic damper

Abstract

An adjustable hydraulic damper valve is adapted to provide single path, variable hydraulic flow restriction between chambers of a damper in proportional relationship to the operating pressure in the damper. The valve is configured to control the flow of hydraulic fluid between chambers of the damper in a predetermined relationship to the pressure differential across the valve of the damper via a variable orifice arrangement based on proportionally opened shaped apertures, and provide adjustability for the damper by modifying said relationship by means of changing the position of said shaped apertures.

Description

DescriptionTitle of Invention : Apparatus to Adjust a Hydraulic DamperTechnical Field

[0001] Embodiments of the present invention relate generally to the field of damping devices for vehicles.Background Art

[0002] Vehicle damping devices, hydraulic dampers in particular, are used to control vehicle movements. Hydraulic dampers, in general, utilize a piston to be slidably carried within a fluid-filled cylinder and peripherally sealed to its walls and a valve controlling the movement of the piston. The valve restricts the flow of fluid induced by this movement. As the piston of a damper is moved in the cylinder, fluid is compressed and passes from one side of the valve to the other side. Fluid dampers have resistance to movement which varies in relation to displacement rate (i.e. , velocity); this relation is defined as the force-velocity relation.

[0003] If the passages of a valve are configured as fixed orifices, then the pressure differential across the valve increases as the square of the hydraulic flow through the orifices which, in turn, results in a progressive damping rate. In applications of shock absorber dampers for wheeled vehicles, it is desired to have a suspension damper with a relatively linear or digressive force-velocity relationship. The method of achieving desirable damping characteristics in such applications is to vary the orifice area in a predetermined relationship to pressure differential across the valve.

[0004] The most commonly used variable orifice damper valve arrangement consists of a stack of compliant plates installed over an array of hydraulic passages. The pressure differential across the piston applies load on the plates causing them to deflect which, in turn, creates a path for hydraulic fluid. Conventional damping devices provide a constant damping rate during compression or extension; other conventional damping devices provide mechanisms for varying the damping rate. As various types of recreational and sporting vehicles continue to become more technologically advanced, it creates a demand for improved techniques forvarying the clamping rate. To provide adjustability for such arrangement, devices varying closing force or preload on the stack of compliant plates are used. The design of such valve is not capable of precisely adjusting damping rate with a broad range of characteristics since large forces generated by operating pressure within the damper are controlled by relatively short-travel valve arrangement. Also, preload adjusting devices have a tendency to modify force-velocity characteristics by uniformly increasing and decreasing damping characteristic graphs. This tendency creates limitations for usage in suspension which operates in constantly changing conditions.

[0005] Another type of variable orifice damper valve arrangement is listed in U.S. Pat. No. 8,800,732 B2 issued to Laurence et. al. The ‘732 patent claims the hydraulic damper spool valve for controlling force-velocity relation that consists of a sleeve with apertures and a cylindrical spool with spring slidably disposed within. The spool is longitudinally moved by pressure, generated by piston movement, against the biasing force of a coil spring. The moved spool uncovers a portion of flow apertures allowing the fluid to flow across the arrangement. The claimed invention offers the valve which characteristic is dictated by geometric configuration of the shaped flow apertures; however, does not describe a relatively precise method of externally adjusting the valve damping rate.

[0006] The existing adjustable variable orifice valve arrangements either have adjustable spring preload or adapted to perform adjustments by gradually closing or opening its primary apertures.

[0007] To date, a commercially available adjusting device, operating by closing or opening primary apertures of a hydraulic damper spool valve, requires an external sleeve with slots and a sleeve with apertures and a spool displaced therein. The wall thickness of the spool sleeve in this configuration creates a gap between the spool metering the flow and the sleeve controlling the aperture opening, so that the resultant shape of aperture created by the external sleeve is one wall thickness distance away from the spool. Blow-by flow through the created clearance may result in divergence between desired and operational characteristics.

[0008] In summary, the above-mentioned methods to provide adjustability for hydraulic damper valves are not readily capable of providing precise operation together with a wide range of adjustments.Summary of Invention

[0009] An object of the present disclosure is to therefore provide a method of adjustment and an adjustable valve for hydraulic damper that reduces the number of required components, simplifies the assembly procedure, allows for wide range of damping rate adjustments while improving overall performance of the damper. Accordingly, the valve is configured to control the flow of hydraulic fluid between chambers of the damper in a predetermined relationship to the pressure differential across the valve of the damper via a variable orifice arrangement based on proportionally opened shaped apertures, and provide adjustability for the damper by modifying said relationship by means of changing the position of said shaped apertures.

[0010] In a first principal embodiment of the invention, an adjustable hydraulic damper valve for a hydraulic damper comprises a valve body configured with openings adjacent its opposing ends, one of which openings is in fluid communication with a first portion of the hydraulic damper and the other one of which openings is in fluid communication with a second portion of the hydraulic damper to facilitate flow of a hydraulic fluid between the first portion and the second portion under operating pressures, a hollow cylindrical valve guide sleeve interrupted by a valve body or a cylindrical restrictor and being fixed in relation to the valve body, the hollow cylindrical valve guide sleeve configured with at least one cut-out for a corresponding movable valve sleeve protrusion to be moved within, a cylindrical valve adjusting sleeve either covering or being covered by the valve guide sleeve configured with at least one shaped flow aperture adjacent the respective valve guide sleeve cut-out to create at least partial channel overlap to selectively connect hydraulically the first portion and the second portion of the hydraulic damper via said overlap, a movable valve sleeve configured to be slidably carried against the valve guide sleeve wall either covering or being covered by the valve guide sleeve inversely to the location of said valve adjusting sleeve with apertures, configured with a number of protrusions matching with a number of said valve guide sleeve cut-outs, and said protrusions extend towardssaid valve guide sleeve and adapted to selectively block the flow, at any one time, through all the shaped apertures, or only the at least one shaped aperture, a resilient energy storage member which is disposed against movable valve sleeve so as to bias the movable valve sleeve in the opposing direction to the forces generated by the operating pressure in the hydraulic fluid of the hydraulic damper, such that when the energy storage member is compressed as operating pressure is induced at the corresponding valve body opening acting upon movable sleeve effective area, and the movable valve sleeve with protrusions moves relative to the respective valve adjusting sleeve with apertures, so that an open area of the at least one shaped aperture adjacent the moving valve sleeve protrusion varies in proportional relationship to the pressure, thereby varying the hydraulic flow restriction between the first portion and the second portion of the hydraulic damper, and said variable hydraulic flow restriction is altered by means of changing the position of said valve adjusting sleeve with apertures relative to the position of the valve guide sleeve, thereby changing the shape of said resultant channel overlap formed by the valve guide sleeve cut-out and the adjusting sleeve flow apertures, a one-way check valve is adapted to allow hydraulic flow so as to create a unobstructed flow path through the valve body in the reverse direction relative to the operating direction of corresponding adjustable valve apertures to create a continuous flow path between the first portion and second portion of the damper internal chamber with the limiting hydraulic single-path flow area restriction defined by said resultant channel overlap formed by the valve guide sleeve cut-out and the adjusting sleeve flow apertures.

[0011] In a further aspect of the invention, the arrays of flow apertures are configured with predetermined precise shapes and each of the movable valve sleeve’s protrusion is adapted to accurately control the variable open area of the respective flow apertures in a proportional relationship to the operating pressure in the damper so as to provide the desired pressure-flow characteristics.

[0012] In a further aspect of the invention, the resilient energy storage member is a coil spring.

[0013] In a further aspect of the invention, the inner and outer circular surfaces of the hollow cylindrical valve guide sleeves are adapted to slidably contact the valveadjusting sleeve and movable sleeve with protrusions with a predetermined close tolerance radial clearance that is configured to allow sliding movement of each of the valve adjusting sleeve and movable sleeve with protrusions relative to the respective cylindrical valve guide sleeve while preventing hydraulic flow through the radial clearances.

[0014] In a further aspect of the invention, the hydraulic damper valve is affixed to the main piston or mounted within the damper main body using mechanical fastening or the like.

[0015] In a further aspect of the invention, a fixed orifice bypass passage is provided between the first portion of the hydraulic damper and the second portion of the hydraulic damper so as to provide a hydraulic flow path in parallel with the shaped apertures of the valve adjusting sleeve, and said fixed orifice bypass passage providing a hydraulic flow path in parallel with the shaped apertures is configured with a mechanism to vary an effective orifice area.

[0016] In a further aspect of the invention, a change in a position of the adjusting sleeve and an area of said fixed orifice bypass passage is facilitated by manipulation of an exterior portion of said vehicle suspension damper or facilitated by solenoid, thereby provides adjustability of damping rate without a necessity to disassemble the valve of the present disclosure.Technical Problem

[0017] What is needed is a variable-orifice hydraulic damper valve that offers precise operation within a wide range of adjustments together with a quick-acting adjusting mechanism.Solution to Problem

[0018] The solution for the stated problem is the valve configuration of the present disclosure which controls the flow of hydraulic fluid between chambers of the damper in a predetermined relationship to the pressure differential across the valve of the damper via a variable orifice arrangement based on proportionally opened shaped apertures, and provides adjustability for the damper by modifying said relationship by means of changing the position of said shaped apertures.Brief Description of Drawings

[0019] Aspects of the present invention are illustrated by way of example, and not by way of limitation, in the accompanying drawings, wherein:

[0020] FIG. 1 is a perspective view of a hydraulic damper assembly.

[0021] FIG. 2 is a partial cut-away view of the hydraulic damper assembly of FIG. 1.

[0022] FIG. 3A is a cross-sectional view of components within an adjustable valve assembly embodiment with no hydraulic fluid flow.

[0023] FIG. 3B is a perspective sectional view of components within an adjustable valve assembly embodiment with no hydraulic fluid flow.

[0024] FIG. 4A is a cross-sectional view of a portion of an adjustable hydraulic valve assembly during a rebound stroke.

[0025] FIG. 4B is a cross-sectional elevation view of a portion of an adjustable hydraulic valve assembly during a compression stroke.

[0026] FIG. 5 is an exploded perspective view of the adjustable hydraulic damper valve of the present disclosure.

[0027] FIG. 6A and FIG. 6B depict broken-out sectional views of components within an adjustable valve assembly, in accordance with an embodiment.

[0028] FIG. 7A is a cross-sectional view of an alternative embodiment of the adjustable hydraulic damper valve and main piston of the hydraulic damper of the present disclosure.

[0029] FIG. 7B is a perspective sectional view of an alternative embodiment of the adjustable hydraulic damper valve, in accordance with an embodiment.

[0030] FIG. 8 is an exploded perspective view of an alternative embodiment of the adjustable hydraulic damper valve and main piston of the hydraulic damper of the present disclosure.

[0031] FIG. 9A, FIG. 9B, and FIG. 9C each depict a cross-sectional elevation view of the hydraulic damper containing the adjustable hydraulic damper valve of the present disclosure.

[0032] FIG. 10 is an elevated cross-sectional view of components within an adjustable valve assembly comprising an independently adjustable orifice area bypass passage.

[0033] FIG. 11 A and FIG. 11B depict elevation and axial section views of an adjustable valve with an independently adjustable orifice area bypass passage comprising multiple adjusting sleeve flow apertures, in accordance with an embodiment.

[0034] FIG. 12A, FIG. 12B, and FIG. 12C depict side views of an adjustable valve, in accordance with an embodiment.

[0035] FIG. 13 is an elevated cross-sectional view of components within the hydraulic damper assembly comprising an adjustable valve, in accordance with an embodiment.

[0036] FIG. 14A and FIG. 14B are cross-sectional views of various operational positions of an embodiment of the adjustable valve assembly, wherein adjustability is facilitated by a solenoid.

[0037] FIG. 15 is a perspective sectional view of components of the adjustable valve assembly embodiment as disclosed herein.

[0038] FIG. 16 elevated cross-sectional view of the hydraulic damper assembly comprising a solenoid operated adjustable valve embodiment as disclosed herein.Description of Embodiments

[0039] Reference will now be made in detail to embodiments of the present technology, examples of which are illustrated in the accompanying drawings. While the technology will be understood that they are not intended to limit the present technology to these embodiments. On the contrary, the present technology is applicable to alternative embodiments, modifications, and equivalents, which may be included within the spirit and scope of the invention as defined by the appended claims.

[0040] Referring to FIG. 1 and FIG. 2, a hydraulic damper assembly (1 ) consists of a main body (3), a shaft assembly (5) and a main piston (7) that is configured to divide the internal chamber (9) of the main body (3) into a first portion (11) and a second portion (13). The first portion (11 ) and the second portion (13) of the internal chamber (9) contain hydraulic fluid. The main piston (7) comprises an adjustable hydraulic damper valve (15) which is mounted to the shaft assembly(5) and controlled by an external adjuster (16). The adjustable hydraulic damper valve (15) may be affixed to the shaft assembly (5) using a mechanical fastener, welding, a threaded connection, or the like. As shown in FIG. 2, one or more seals (17) may be disposed between the adjustable hydraulic damper valve (15) and the main body (3).

[0041] The following discussion describes FIGS. 1 - 6B and embodiments shown therein.

[0042] The adjustable hydraulic damper valve (15) comprises a valve body (19).

[0043] In one embodiment of the present technology, the adjustable hydraulic damper valve (15) is affixed to the main piston (7) and provides a single directional hydraulic flow restriction in the direction of rebound (retraction). The valve body may be provided with several such valves to control the hydraulic flow restriction in both directions. Referring to FIG. 3A, the adjustable hydraulic damper valve (15) also comprises a hollow cylindrical valve guide sleeve (21 ) securely mounted centrally within the valve body (19). The valve guide sleeve (21 ) is securely mounted centrally within the valve body (19) and interrupted by a cylindrical restrictor (23). The valve guide sleeve (21 ) is secured by check valve ring (25) by a guide sleeve flange (27) (shown in FIG. 5) against the cylindrical restrictor (23) which is seated to the valve body (19).

[0044] The valve guide sleeve (21 ) is configured with an array of cut-outs (29) for corresponding movable valve sleeve protrusions (31) to be moved within. The cylindrical valve adjusting sleeve (33) covering the valve guide sleeve (21 ) is configured with an array of shaped flow apertures (35) adjacent the respective valve guide sleeve cut-out (29). FIG. 3B shows a partial channel overlap (37) formed by guide sleeve cut-outs (29) and shaped flow apertures (35). A movable valve sleeve (39) with valve sleeve protrusions (31 ) is configured to be slidably carried against the valve guide sleeve (21 ) inner wall, so that the valve guide sleeve (21 ) is located between the movable valve sleeve (39) and the valve adjusting sleeve (33) with a predetermined close tolerance radial clearance that is configured to allow sliding movement of each of the valve adjusting sleeve (33) and movable valve sleeve (39) with protrusions (31 ) relative to the respective cylindrical valve guide sleeve (21 ) while preventing hydraulic flow through theradial clearances. The number of valve sleeve protrusions (31) is configured to match a number of valve guide sleeve cut-outs (29), and valve sleeve protrusions (31) extend towards the valve guide sleeve (21 ). The valve sleeve protrusions (31) are adapted to selectively block the flow, at any one time, through all the shaped flow apertures (35), or only the at least one shaped flow aperture (35). FIG. 4A represents a fluid flow during the rebound stroke whereinto the first portion (11 ) and the second portion (13) of the internal chamber (9) selectively connected hydraulically via the channel overlap (37) formed by guide sleeve cutouts (29) and shaped flow apertures (35). A resilient energy storage member is disposed against movable valve sleeve (39). In an embodiment of the present technology, this resilient energy storage member is a coil spring (41 ) which biases the movable valve sleeve (39). The movable valve sleeve (39) may seat against the cylindrical valve restrictor (23) or the valve body (19) when at rest and is preferably biased by the coil spring at all times.

[0045] FIG. 4A and 4B depict cross-sectional views of a portion of an adjustable hydraulic valve assembly during rebound and compression stroke respectfully, in accordance with an embodiment. The valve body (19) is provided with a first opening (43) and a second opening (45). When the hydraulic damper assembly(I ) is at rest, there is no induced pressure differential between the first portion(I I ) and the second portion (13). When the hydraulic damper's main piston (7) moves in the direction of rebound the pressure is induced at the second opening (45) of the valve body (19) and acts upon the effective area of the movable valve sleeve (39), and the movable valve sleeve (39) with protrusions (31) moves relative to the respective valve adjusting sleeve (33) with apertures (35) against the biasing force of the coil spring (41). When the movable valve sleeve (39) with protrusions (31) moves longitudinally, an open area of the at least one shaped aperture (35) adjacent the moving valve sleeve protrusion (31 ) varies in proportional relationship to the pressure, thereby varies the hydraulic flow restriction between the first portion (11 ) and the second portion (13) of the internal chamber (9). When the hydraulic damper's main piston (7) moves in the direction of compression, the pressure induced at the first opening (43) of the valve body (19) is released by a one-way check shim (47). A one-way check valve is adapted to allow hydraulic flow so as to create a unobstructed flow paththrough the valve body (19) in the reverse direction relative to the operating direction of corresponding adjustable valve apertures (35) to create a continuous flow path between the first portion (11) and the second portion (13) of the damper internal chamber (9) with the limiting hydraulic single-path flow area restriction defined by the resultant channel overlap (37) formed by guide sleeve cut-outs (29) and shaped flow apertures (35).

[0046] The arrays of flow shaped apertures are configured with predetermined precise shapes and each of the movable valve sleeve’s protrusion is adapted to accurately control the variable open area of the respective flow apertures in a proportional relationship to the operating pressure in the damper so as to provide the desired pressure-flow characteristics.

[0047] An actuator includes any mechanism or means configured to change the position of the valve adjusting sleeve relative to the valve guide sleeve, for example the external adjuster and adjusting rod described herein, or alternatively a solenoid assembly also described herein. In one embodiment, a position of valve adjusting sleeve (33) with apertures (35) in the adjustable hydraulic damper valve (15) is controlled by the external adjuster (16). The external adjuster (16) is connected to a valve adjusting rod (49) which is correspondingly engaged to the valve adjusting sleeve (33) with apertures (35). The change in the position of the adjusting sleeve (33) is facilitated by manipulation of an external adjuster (16). FIG. 6A and FIG. 6B illustrate the change in the position of the valve adjusting sleeve (33) with apertures (35) relative to the guide sleeve cut-out (29). The hydraulic flow area restriction is defined by the resultant channel overlap, thereby the change of the shape of the resultant channel overlap formed by the valve guide sleeve cut-out and the adjusting sleeve flow apertures alters the pressureflow characteristics of the damper.

[0048] Additionally, the adjustable hydraulic damper valve (15) can be configured with a separate bypass passage that provides a direct, unobstructed hydraulic flow path between the first portion (11) and the second portion (13) of the internal chamber (9). The bypass passage is configured so that the hydraulic fluid can pass between the first portion (11 ) and the second portion (13) when the flow of hydraulic fluid through apertures (35) of the valve adjusting sleeve (33) is completely blocked by protrusions (31) of the movable valve sleeve (39). Thebypass passage is configured with a fixed area orifice that provides a predetermined square law pressure-flow relationship at low levels of main piston (7) displacement rate (i.e. , velocity). In this manner, a sharp transition in the force-velocity characteristic is avoided when the hydraulic damper experiences low-velocity movement. In an embodiment of the present technology, the bypass passage is a low-speed orifice (51) which flow area intersects with low-speed adjusting orifices (53) located on the valve adjusting sleeve (33) (Shown in FIG. 3B and 5). The flow area of such bypass passage is altered by the change in the position of the valve adjusting sleeve (33) and controlled by the external adjuster (16).

[0049] The following discussion describes FIGS. 7A - 8 and embodiments shown therein.

[0050] FIG. 7A illustrates an alternative embodiment of the present disclosure in which the valve guide sleeve (121 ) is securely mounted centrally within the valve body (119) and interrupted by its closed end. The valve guide sleeve (121 ) is configured with an array of cut-outs (129) for corresponding movable valve sleeve protrusions (131) to be moved within. In this alternative embodiment, a cylindrical valve adjusting sleeve is located within the bore of the valve guide sleeve (121). The cylindrical valve adjusting sleeve (33) covered by the valve guide sleeve (121) is configured with an array of shaped flow apertures (135) adjacent the respective valve guide sleeve cut-out (129). A movable valve sleeve (139) with valve sleeve protrusions (131) is configured to be slidably carried against the valve guide sleeve (121 ) outer wall, so that the valve guide sleeve (121) is located between the movable valve sleeve (139) and the valve adjusting sleeve (133). The number of valve sleeve protrusions (131) is configured to match a number of valve guide sleeve cut-outs (129), and valve sleeve protrusions (131) extend towards the valve guide sleeve (121 ). Additionally, the check valve ring (125) is located with a predetermined close tolerance radial clearance that is configured to allow sliding movement of the valve sleeve (139) with sleeve protrusions (131 ) while preventing hydraulic flow through the radial clearances.

[0051] The valve body (119) is provided with a first opening (143) and a second opening (145). These valve body openings (143)(145) replace the previouslydescribed valve body openings (43)(45). FIG. 7B represents a direction of fluid flow during rebound stroke (160) in which the limiting hydraulic single-path flow area restriction defined by the resultant channel overlap (137) formed by guide sleeve cut-outs (129) and shaped flow apertures (135), and a direction of fluid flow during compression stroke (163) in which a unobstructed flow path through the valve body (119) is created via a one-way check valve, consisting of one-way check shim (147) and the check valve ring (125). A low-speed orifice (151 ) and a low-speed adjusting orifice (153) operate identically to previously described (51 ) (53) orifices. FIG. 8 represents an exploded perspective view of an alternative embodiment of the adjustable hydraulic damper valve and main piston of the hydraulic damper of the present disclosure. This arrangement may allow the usage of fewer number of parts compared to the embodiment in which the adjusting sleeve covers the guide sleeve.

[0052] FIG. 9A, FIG. 9B, and FIG. 9C each depicts a cross-sectional elevation view of the hydraulic damper containing the adjustable hydraulic damper valve of the present disclosure.

[0053] FIG. 9A represents hydraulic damper assembly (201 ) in which the rebound valve (215) is slidably displaced within the internal chamber (209) of the main body (203) and the compression valve (216) is mounted stationary within the main body (203). Each of the valves is controlled by corresponding rebound external adjuster (217) and compression external adjuster (218). The rebound valve (215) provides the single directional variable hydraulic flow restriction between the first portion (211) and the second portion (213) of the internal chamber (209). The compression valve (216) provides the single directional variable hydraulic flow restriction between the internal chamber (209) and the main body inner volume (204). During compression, the volume of the shaft assembly (205) displaces, from the internal chamber (209), a volume of hydraulic fluid contained within the internal chamber (209) corresponding to the volume of the shaft assembly (205) incurring into the internal chamber (209). During extension or “rebound”, the volume of hydraulic fluid must be replaced as the shaft assembly (205) leaves the interior of the internal chamber (209).

[0054] An alternative embodiment of the present disclosure is shown in FIG. 9B in which the rebound valve (215) and the compression valve (216) are integratedinto one valve body (219), and the valve body (219) is affixed to shaft assembly (205). The valve body (219) is slidably displaced within the internal chamber (209) of the main body (203). Each of the valves is controlled by corresponding rebound external adjuster (217) and compression external adjuster (218). Both adjustable valves, the rebound valve (215) and the compression valve (216) selectively provide the single directional variable hydraulic flow restriction between the first portion (211) and the second portion (213) of the internal chamber (209).

[0055] A further alternative embodiment of the present disclosure is shown in FIG. 9C in which the rebound valve (215) and the compression valve (216) are integrated into one valve body (219), and the valve body (219) is mounted within the main body (203). Each of the valves is controlled by corresponding rebound external adjuster (217) and compression external adjuster (218). The main body (203) is provided with flow passages (208) that provide an unobstructed hydraulic path between the first portion (211) and the first opening (243) and the valve body (219) is further configured so as to provide an unobstructed hydraulic path between the second portion (213) and the second opening (245). Both adjustable valves, the rebound valve (215) and the compression valve (216) selectively provide the single directional variable hydraulic flow restriction between the first portion (211 ) and the second portion (213).

[0056] The following discussion describes FIGS. 10 - 13 and embodiments shown therein.

[0057] FIG. 10 shows an elevated cross-sectional view of components within an adjustable valve assembly of the present disclosure configured with an independently adjustable orifice area bypass passage. The adjustable hydraulic damper valve (315) is provided with the exit flow passages (352) to create an unobstructed hydraulic path between the low-speed orifice (351 ) and the first opening (311). Thus, the first opening (311) and the second opening (313) are hydraulically connected with the limiting hydraulic flow area restriction defined by the position of the low-speed adjuster. In one embodiment of the present technology, the adjustable hydraulic damper valve (315) includes a metering needle (361) to control an open area of the low-speed bypass passage. That metering needle (361 ) can be adjusted by rotation of the low-speed externaladjuster (363) which correspondingly rotates low-speed adjusting rod (365). The shaft of the metering needle (361 ) is non round and engages a similarly non round hole low-speed adjusting rod (365). When the low-speed external adjuster (363) is rotated, the metering needle (361 ) is rotated and also traverses its threaded housing axially. As the metering needle (361 ) moves axially, an open area of the low-speed orifice (351 ) is correspondingly altered.

[0058] FIG. 11 A and FIG. 11 B depict elevation and axial section views of an adjustable valve with an independently adjustable orifice area bypass passage comprising multiple adjusting sleeve flow apertures. The valve adjusting sleeve (333) of the adjustable hydraulic damper valve (315) is configured with multiple shaped flow apertures for one corresponding guide sleeve cut-out (329). In one embodiment of the present technology, the valve adjusting sleeve (333) is configured with the first flow aperture (371), second flow aperture (372), and third flow aperture (373). The array of flow apertures is configured, so as to provide different pressure-flow characteristics from one another, such that an arrangement with multiple flow apertures for a corresponding guide sleeve cutout may provide a wider range of adjustments. Accordingly, the first flow aperture (371) provides “soft” setting, the second flow aperture (372) provides “medium” setting, and the third flow aperture (373) provides “firm” setting. The apertures may be arranged so that the channel overlap (337) is formed between one guide sleeve cut-out (329) and several flow apertures at the same time. In this way, the damping rate characteristic of the adjustable valve may be set at any position of the valve adjusting sleeve (333) within the range of its flow apertures. Such that, FIG. 11 A and FIG. 11 B represent the valve adjusting sleeve (333) set at a position, in which the guide sleeve cut-out (329) overlaps with a flow area of second flow aperture (372) and partially with a flow area of third flow aperture (373). In this manner, the valve sleeve protrusion (331 ) controls an open area of the second flow aperture (372) and the third flow aperture (373) at the same time in a proportional relationship to the operating pressure in the damper. The external adjuster (316) of the valve allows to modify the resultant channel overlap (337) by a rotation of the adjusting sleeve (333) towards the direction of “firmer” damping characteristic (375) or the direction of “softer” damping characteristic (376).

[0059] FIG. 12A, FIG. 12B, and FIG. 12C show side views of an adjustable valve (315) with different adjustments being set. More particularly, FIG. 12A represents “soft” setting when the active flow area of the first flow aperture (371) is predominant, FIG. 12B represents “medium” setting when the active flow area of the second flow aperture (372) is predominant, and FIG. 12C represents “firm” setting when the active flow area of the third flow aperture (373) is predominant

[0060] FIG. 13 is an elevated cross-sectional view of components within the hydraulic damper assembly (301) comprising an adjustable valve in which the adjustable hydraulic valve (315) provides the single directional variable hydraulic flow restriction between the internal chamber (309) and the main body inner volume (304) during compression stroke. The adjustable hydraulic valve (315) is mounted stationary within the main body (303). The operation principle of the damper assembly of this embodiment is identical to the embodiment depicted in FIG. 9A. The adjustable hydraulic valve’s (315) damping characteristic is adjusted by corresponding valve external adjuster (316) which controls the position of the valve adjusting sleeve (333) and the low-speed external adjuster (363) which controls an open orifice area of a bypass passage.

[0061] The following discussion describes FIGS. 14A - 16 and embodiments shown therein.

[0062] FIG. 14A and FIG. 14B are cross-sectional views of various operational positions of an embodiment of the adjustable valve assembly, wherein adjustability is facilitated by a solenoid. Referring to FIG. 14A, a solenoid balanced by an armature biasing spring (475) axially locates the metering needle (461), controlling an open area of the low-speed bypass passage, affixed to the valve adjusting sleeve (433) by a threaded connection. The axial displacement of the valve adjusting sleeve (433) is facilitated by an electromagnetic interaction between the armature (477) and the coil (479). As the position of valve adjusting sleeve (433) with apertures (435) changes relative to the position of the valve guide sleeve (421), the shape of the resultant channel overlap (437), formed by the valve guide sleeve cut-out (429) and the adjusting sleeve flow apertures (435), changes. Thus, the variable hydraulic flow restriction is altered. The valve adjusting sleeve (433) is pressure-balanced, therefore a relatively small solenoid(using relatively low amounts of power) can control relatively large operating pressure.

[0063] In one embodiment, the valve adjusting sleeve (433) is arranged to be axially displaced relative to the valve guide sleeve (421) while prevented from rotation by a locating pin (not shown). Adjustment of the current in the coil (479) (via modulation of the current from a power source [not shown]) to predetermined values causes the armature (477), and hence the valve adjusting sleeve (433) with the metering needle (461 ), to move in corresponding predetermined axial positions relative to the coil (479). As such, the valve adjusting sleeve (433) with the metering needle (461 ) can be adjusted as shown in FIGS. 14A -14B.

[0064] FIG. 14A is a cross-sectional view of the adjustable valve assembly (415), with the valve shown in “firm” position. This position corresponds to minimum or no current in the solenoid. In FIG. 14A, the valve adjusting sleeve (433) is axially displaced in such way that the large flow area of the shaped apertures (435) is located further away from the valve sleeve protrusion (431 ). A relatively larger displacement, and thus relatively high operating pressure is needed for valve sleeve protrusion to provide a specific open flow area of the shaped aperture which results in firmer damping rate.

[0065] FIG. 14B is a cross-sectional view of the adjustable valve assembly (415), with the valve shown in “soft” position. This position corresponds to a higher current in the solenoid. FIG. 14B shows the valve adjusting sleeve (433), which is axially displaced relative to its position in FIG. 14A, with the large flow area of the shaped apertures (435) located closely to the valve sleeve protrusion (431). Thus, relatively lower operating pressure is needed for valve sleeve protrusion to provide a specific open flow area of shaped aperture which results in a softer damping rate.

[0066] FIGS. 14A -14B show the adjustable hydraulic damper valve (415) is provided with the exit flow passages (452) to provide an unobstructed exit flow path for the low-speed orifice (451). In one embodiment of the present technology, the adjustable hydraulic damper valve (415) includes a metering needle (461) to control an open area of the low-speed bypass passage. The axial displacement of the metering needle (461 ) with the valve adjusting sleeve (433)is facilitated by an electromagnetic interaction between the armature (477) and the coil (479). As the metering needle (461) moves axially, an open area of the low-speed orifice (451) is correspondingly altered. FIGS. 14A -14B show the low- speed orifice (451 ) which open flow area is controlled by the axial displacement of the metering needle (461 ). The low-speed orifice (451) meters low speed flow of fluid to control movements of the damper at low levels of main piston displacement rate (when magnitude and rate is insufficient for the valve sleeve with protrusions to allow the flow of fluid via the shaped apertures). FIG. 15 is a further perspective sectional view of the adjustable valve assembly and the components therein. In the FIGS. 14A -14B, the net result is a decreased damping rate due to increased open area of the low-speed orifice (451 ) and a further damping rate decrease due to the large flow area of the shaped apertures (435) is axially displaced closer to the valve sleeve protrusion (431).

[0067] FIG. 16 elevated cross-sectional view of the hydraulic damper assembly (401 ) comprising a solenoid operated adjustable valve. The adjustable hydraulic valve (415) is mounted stationary within the main body (403). The adjustable hydraulic valve (415) provides the single directional variable hydraulic flow restriction between the internal chamber (409) and the main body inner volume (404) during compression stroke. The main body (403) is provided with flow passages (408) that provide an unobstructed hydraulic path between the internal chamber (409) and the valve body first opening (443), and between the main body inner volume (404) and the valve body second opening (445). The adjustable hydraulic valve (415) provides the single directional variable hydraulic flow restriction between the internal chamber (409) and the main body inner volume (404). During compression, the volume of the shaft assembly (405) displaces, from the internal chamber (409), a volume of hydraulic fluid contained within the internal chamber (409) corresponding to the volume of the shaft assembly (405) incurring into the internal chamber (409). During extension or “rebound', the volume of hydraulic fluid must be replaced as the shaft assembly (405) leaves the interior of the internal chamber (409). In this way, the hydraulic damper assembly (401) compression damping characteristic is defined by the axial position of the valve adjusting sleeve with the metering needle of the adjustable hydraulic valve (415), which is controlled by a solenoid.

Claims

AMENDED CLAIMS received by the International Bureau on May 12, 2026 (12.05.2026)Claims[Claim 1] A hydraulic damper valve comprising: a. a valve body having openings adjacent its opposing ends, a first opening being in fluid communication with a first portion of a hydraulic damper and a second opening in fluid communication with a second portion of the hydraulic damper to facilitate flow of a hydraulic fluid between the first portion and the second portion of the hydraulic damper under operating pressures; b. a valve guide sleeve interrupted by the valve body or a cylindrical restrictor and being fixed in relation to the valve body;C. the valve guide sleeve having at least one cut-out for a corresponding movable valve sleeve protrusion to be moved within; d. a movable valve adjusting sleeve either covering or being covered by the valve guide sleeve configured with at least one shaped flow aperture adjacent the respective valve guide sleeve cut-out to create at least partial channel overlap to selectively connect hydraulically the first portion and the second portion of the hydraulic damper via said overlap; e. a movable valve sleeve configured to be slidably carried against the valve guide sleeve either covering or being covered by the valve guide sleeve inversely to the location of said valve adjusting sleeve with apertures, configured with a number of protrusions matching a number of said valve guide sleeve cut-outs, and said protrusions extend towards said valve guide sleeve and adapted to selectively block the flow, at any one time, through all the shaped apertures, or only the at least one shaped aperture; f. a resilient energy storage member which is disposed against the movable valve sleeve so as to bias the movable valve sleeve in a direction opposing forces generated by the operating pressure in the hydraulic fluid of the hydraulic damper;g. such that, when operating pressure is applied at the corresponding valve body opening and acts upon an effective area of the movable valve sleeve, the energy storage member is compressed, and the movable valve sleeve with protrusions moves relative to the respective valve adjusting sleeve with apertures, so that an open area of the at least one shaped aperture adjacent the moving valve sleeve protrusion varies in proportional relationship to the operating pressure, thereby varying a hydraulic flow restriction between the first portion and the second portion of the hydraulic damper; i. and said variable hydraulic flow restriction is altered by means of changing a position of said valve adjusting sleeve with apertures relative to the position of the valve guide sleeve, thereby changing a shape of said resultant channel overlap formed by the valve guide sleeve cut-out and the adjusting sleeve flow apertures.[Claim 2] The hydraulic damper valve of claim 1, wherein a one-way check valve is adapted to allow hydraulic flow so as to create an unobstructed flow path through the valve body in a reverse direction relative to an operating direction of corresponding adjustable valve apertures to create a continuous flow path between the first portion and the second portion of the hydraulic damper with a limiting hydraulic single-path flow area restriction defined by said resultant channel overlap formed by the valve guide sleeve cut-out and the adjusting sleeve flow apertures.[Claim 3] The hydraulic damper valve of claim 1, wherein the at least one shaped flow aperture is configured with a predetermined precise shape and each of the movable valve sleeve's protrusions is adapted to accurately control the variable open area of the at least one shaped flow aperture in a proportional relationship to the operating pressure in the hydraulic damper so as to provide desired pressure-flow characteristics.[Claim 4] The hydraulic damper valve of claim 1, wherein the resilient energy storage member is a coil spring.[Claim 5] The hydraulic damper valve of claim 1, wherein inner and outer circular surfaces of the valve guide sleeve are adapted to slidably contact the valve adjusting sleeve and the movable valve sleeve with protrusions with a predetermined close tolerance radial clearance that is configured to allow sliding movement of each of the valve adjusting sleeve and the movable valve sleeve with protrusions relative to the valve guide sleeve while preventing hydraulic flow through the radial clearances.[Claim 6] The hydraulic damper valve of claim 1, wherein the hydraulic damper valve is affixed to a main piston or mounted within a main body of the hydraulic damper using mechanical fastening.[Claim 7] The hydraulic damper valve of claim 1, wherein a fixed orifice bypass passage is provided between the first portion of the hydraulic damper and the second portion of the hydraulic damper so as to provide a hydraulic flow path in parallel with the shaped apertures of said valve adjusting sleeve, and said fixed orifice bypass passage providing a hydraulic flow path in parallel with the shaped apertures is configured with a mechanism to vary an effective orifice area.[Claim 8] The hydraulic damper valve of claim 1, wherein a change in the position of the adjusting sleeve is facilitated by manipulation of an exterior portion of said hydraulic damper.[Claim 9] The hydraulic damper valve of claim 7, wherein a change in the position of the adjusting sleeve and an area of said fixed orifice bypass passage is facilitated by manipulation of an exterior portion of said hydraulic damper.[Claim 10] The hydraulic damper valve of claim 1, wherein a solenoid assembly is configured to facilitate a change in a position of said adjusting sleeve, said solenoid assembly comprising: a. a solenoid as a power source configured to facilitate a change in a position of said adjusting sleeve relative to said valve guide sleeve; b. an armature coupled to the solenoid and operatively connected to said adjusting sleeve;c. a spring biasing said adjusting sleeve toward a position obstructing the at least one shaped flow aperture.[Claim 11] The hydraulic damper valve of claim 7, wherein a solenoid assembly is configured to facilitate a change in a position of said adjusting sleeve and an area of said fixed orifice bypass passage, said solenoid assembly comprising: a. a solenoid as a power source configured to facilitate a change in a position of said adjusting sleeve relative to said valve guide sleeve; b. an armature coupled to the solenoid and operatively connected to said adjusting sleeve; c. a spring biasing said adjusting sleeve toward a position obstructing the at least one shaped flow aperture.[Claim 12] A hydraulic damper valve comprising: a. a valve body having a first opening and a second opening, the first opening of the valve body being in fluid communication with a first portion of a hydraulic damper and the second opening of the valve body being in fluid communication with a second portion of the hydraulic damper to permit flow of hydraulic fluid between the first portion of the hydraulic damper and the second portion of the hydraulic damper under operating pressure; b. a valve guide sleeve fixed with respect to the valve body and configured with at least one cut-out;C. a movable valve sleeve disposed for sliding movement relative to the valve guide sleeve, the movable valve sleeve having at least one protrusion configured to cooperate with the cut-out to control fluid flow, the movable valve sleeve being biased by a resilient energy storage member in opposition to the operating pressure such that movement of the movable valve sleeve varies an open area of the cut-out in response to the operating pressure;d. a valve adjusting sleeve disposed relative to the valve guide sleeve and configured with at least one shaped flow aperture positioned to overlap with the cut-out to define a variable orifice; and e. an actuator configured to change the position of the valve adjusting sleeve relative to the valve guide sleeve so as to alter the overlap and thereby adjust a hydraulic flow restriction between the first portion of the hydraulic damper and the second portion of the hydraulic damper.

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