Improved fulcrum disc and check disc for shock absorber with optimized discharge range and adjustability

Abstract

A shock absorber (20) for a vehicle (20) includes a pressure tube (30) defining a fluid chamber (42), a piston (60) including a fluid passage (100) disposed within the fluid chamber, and a valve assembly (62). The valve assembly includes a flow limiting disc (102), an orifice disc (104), a fulcrum disc (106), and a non-return disc (108). The flow restricting disc includes a first ring (112), first fingers (116) covering the fluid passage, and first apertures (118). The orifice plate includes a second ring (120), a second finger (124), and a second orifice (126). The second finger overlaps the first finger, and the second aperture is aligned with the first aperture. The non-return disc includes a third ring (132) and a third finger (136) above the second finger. The fulcrum disk has a fourth ring (128). The damping response characteristic of the shock absorber can be changed by adjusting the outer diameter of the third ring and the outer diameter of the fourth ring.

Description

Technical Field

[0001] This disclosure relates to automotive shock absorbers / dampers. More specifically, this disclosure relates to shock absorber / damper assemblies that provide optimized bleed range and adjustability. Background Technology

[0002] The statements in this section provide only background information in connection with this disclosure and may not constitute prior art.

[0003] Shock absorbers are typically used in conjunction with a car's suspension system or other suspension systems to absorb unwanted vibrations generated during the suspension system's movement. To absorb these unwanted vibrations, automotive shock absorbers are usually connected between the sprung mass (body) and the unsprung mass (suspension / drivetrain) of the vehicle.

[0004] The most common types of shock absorbers for automobiles are single-tube and twin-tube types. In a single-tube shock absorber, a piston is placed within a fluid chamber defined by a pressure tube and connected to the sprung mass of the vehicle via a piston rod. The pressure tube is connected to the unsprung mass of the vehicle. The piston divides the fluid chamber of the pressure tube into a first working chamber and a second working chamber. The piston includes a compression valve system that restricts the flow of hydraulic fluid from the second working chamber to the first working chamber during the compression stroke. The piston also includes a rebound valve system that restricts the flow of hydraulic fluid from the first working chamber to the second working chamber during the rebound or extension stroke. Because both the compression and rebound valve systems restrict the flow of hydraulic fluid, the shock absorber generates a damping force to counteract oscillations / vibrations that would otherwise be transmitted from the unsprung mass to the sprung mass.

[0005] The compression valve system and rebound valve system of the shock absorber work together to control the fluid flow between the upper and lower working chambers of the shock absorber. By regulating the fluid flow between the two working chambers, a pressure drop can be created between them, which helps to generate the damping force of the shock absorber. The compression valve system, rebound valve system, and check valve assembly can be used to adjust the damping force, thereby optimizing vehicle ride comfort and handling, and effectively suppressing noise, vibration, and acoustic harshness (NVH).

[0006] Despite the existence of various features and components for adjusting vibration dampers, further improvements are still needed to enhance the adjustability and performance consistency of vibration dampers. Summary of the Invention

[0007] This section provides a general description of the invention and does not constitute a complete disclosure of its entire scope or all its features.

[0008] According to one aspect of this disclosure, a vehicle shock absorber is provided. The shock absorber includes: a pressure tube defining a fluid chamber, a piston disposed within the fluid chamber and including a fluid passage, and a valve assembly. The valve assembly includes a restriction disc, an orifice disc, a pivot disc, and a check disc. The restriction disc includes a first ring, a first finger extending from the first ring, and a first orifice extending through the first finger. The first finger covers the fluid passage of the piston. The orifice disc includes a second ring, a second finger extending from the second ring, and a second orifice through the second finger. The second finger overlaps with the first finger, and the second orifice is aligned with the first orifice. The check disc includes a third ring and a third finger extending from the third ring, wherein the third finger is positioned above the second finger. The pivot disc has a fourth ring. The damping response of the shock absorber can be altered by adjusting the outer diameters of the third ring and the fourth ring. For example, the closing torque of the check plate and the transition process from the open discharge state to the normal discharge state can be adjusted by adjusting the outer diameter of the fulcrum plate and the check plate.

[0009] One aspect of this disclosure relates to a method for controlling the flow of hydraulic fluid between an upper working chamber and a lower working chamber of a pressure tube, the method being implemented by a piston disposed within the pressure tube, the piston having one or more flow channels. The method includes: a fulcrum disk disposed near the piston, the fulcrum disk having a first ring having a first central bore, a first inner diameter, and a first outer diameter; a check disc disposed near the side of the fulcrum disk opposite to the piston, the check disc including a second ring having a second central bore, a second inner diameter, a second outer diameter, and one or more radial extensions extending from the second ring; and selecting the first outer diameter and the second outer diameter according to a desired damping response.

[0010] According to one aspect of this disclosure, a vehicle shock absorber kit is provided. The kit includes: a pressure tube defining a fluid chamber; a piston disposed within the fluid chamber; a first pivot plate; a first check plate; a second pivot plate; and a second check plate. The piston divides the fluid chamber into an upper working chamber and a lower working chamber, wherein the piston defines a pair of bleed passages and blow-off passages extending through the piston and between the upper and lower working chambers. The first pivot plate has a ring, a first pivot plate inner diameter, and a first pivot plate outer diameter. The first check plate has a ring, a first check plate inner diameter, a first check plate outer diameter, and one or more first radial extensions. The second pivot plate has a ring, a second pivot plate inner diameter, and a second pivot plate outer diameter, wherein the second pivot plate outer diameter differs from the first pivot plate outer diameter. The second check plate has a ring, a second check plate inner diameter, a second check plate outer diameter, wherein the second check plate outer diameter differs from the first check plate outer diameter, and one or more second radial extensions. Based on the desired damping response, the damper contains only one of the first pivot plate or the second pivot plate, and only one of the first check plate or the second check plate.

[0011] According to another aspect of this disclosure, a shock absorber for a vehicle is provided. The shock absorber includes a pressure tube defining a fluid chamber, a piston disposed within the fluid chamber, and a valve assembly. The piston divides the fluid chamber into an upper working chamber and a lower working chamber, wherein the piston includes a first side, a second side, and a fluid passage extending through the piston between the upper and lower working chambers. The valve assembly includes: a flow-limiting disc near the first side of the piston, an orifice disc (the flow-limiting disc is located between the orifice disc and the first side of the piston), a check disc, and a pivot disc (the pivot disc is located between the orifice disc and the check disc). The flow-limiting disc includes a first ring and a first finger extending radially outward from the first ring, the first finger being configured to cover the fluid passage and having a first vent orifice, wherein the first vent orifice remains open at any position of the flow-limiting disc. The orifice disc includes a second ring and a second finger extending radially outward from the second ring, the second finger having a second vent orifice, wherein the second vent orifice remains open at any position of the orifice disc. The second finger-shaped portion of the orifice plate overlaps with the first finger-shaped portion of the flow-limiting plate, and the second bleed orifice is aligned with the first bleed orifice. The check plate includes a third ring and a third finger-shaped portion extending radially outward from the third ring, the third finger-shaped portion of the check plate being located above the second finger-shaped portion of the orifice plate. The fulcrum plate includes a fourth ring.

[0012] Further applications and advantages will become clear from the description provided herein. It should be understood that the descriptions and specific examples herein are for illustrative purposes only and are not intended to limit the scope of this disclosure. Attached Figure Description

[0013] The accompanying drawings described herein are for illustrative purposes only, representing selected embodiments and not all possible implementations, and are not intended to limit the scope of this disclosure.

[0014] Figure 1 This is a schematic diagram of an exemplary vehicle equipped with shock absorbers in accordance with the teachings of this disclosure; Figure 2 This is a partial side view of a vibration damper constructed according to the teachings of this disclosure; Figure 3A It is an exploded perspective view, showing Figure 2 The shock absorber shown includes the piston body, bleed valve assembly, blowoff valve assembly, and piston rod. Figure 3B It is an exploded perspective view, showing Figure 2 The shock absorber shown includes a rebound vent valve assembly, a rebound discharge valve assembly, and a fixing nut. Figure 4 It is along Figure 3A A cross-sectional view of the vibration damper taken from line 4-4 in the middle; Figure 5 It is along Figure 3A A cross-sectional view of the vibration damper taken from line 5-5 in the middle; Figure 6A This is a perspective view of the first side of an exemplary piston body in accordance with the teachings of this disclosure; Figure 6B This is a perspective view of the first side of an exemplary piston body in accordance with the teachings of this disclosure; Figure 7A This is a perspective view of an exemplary flow-limiting disc of a shock absorber shown in accordance with the teachings of this disclosure; Figure 7B This is a perspective view of another exemplary flow-limiting disc of a shock absorber according to the teachings of this disclosure; Figure 7C This is a perspective view of another exemplary current-limiting plate of a damper according to the teachings of this disclosure; Figure 7D yes Figure 7A A perspective view of an exemplary flow-limiting disc mounted on an exemplary piston body; Figure 7E yes Figure 7B A perspective view of an exemplary flow-limiting disc mounted on an exemplary piston body; Figure 7F yes Figure 7C A perspective view of an exemplary flow-limiting disc mounted on an exemplary piston body; Figure 8 It is a perspective view of an exemplary orifice plate stacked on an exemplary flow-limiting plate of a vibration damper; Figure 9A This is an exploded perspective view of an exemplary relief valve assembly based on the teachings of this disclosure; Figure 9B This is an exploded perspective view of an exemplary relief valve assembly based on the teachings of this disclosure; Figure 10 It is a schematic diagram of the force response curve when the shock absorber moves towards the compression position; and Figure 11 This is a schematic diagram of the force response curve when the vibration damper moves to the compression position.

[0015] The corresponding reference numerals indicate the corresponding parts in several views throughout the accompanying drawing. Detailed Implementation

[0016] The following description is exemplary in nature and is not intended to limit this disclosure, its application or use.

[0017] Exemplary embodiments are provided to make this disclosure exhaustive and to fully communicate its scope to those skilled in the art. Numerous details, such as examples of specific components, apparatuses, and methods, are set forth to aid in a comprehensive understanding of embodiments of this disclosure. Those skilled in the art will understand that the exemplary embodiments may take many different forms without requiring specific details and should not be construed as limiting the scope of this disclosure. In some exemplary embodiments, known processes, known apparatus structures, and known technologies are not described in detail.

[0018] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “the” may also include the plural forms. The terms “comprising,” “containing,” “including,” and “having” are open-ended descriptions, meaning that the stated features, elements, steps, operations, components, and / or parts are explicitly present, but do not preclude the possibility of the presence or addition of one or more other features, elements, steps, operations, components, and / or combinations thereof. The method steps, processes, and operations described herein, unless explicitly specified as the order of execution, should not be construed as necessarily having to be performed in the specific order shown in the discussion or illustrations. It should also be understood that additional or alternative steps may be employed.

[0019] When an element or layer is described as being "above," "joined to," "connected to," or "coupled to" another element or layer, it may be directly above, joined to, connected to, or coupled to that element or layer, or there may be intermediate elements or layers. Conversely, when an element is described as being "directly above," "directly joined to," "directly connected to," or "directly coupled to" another element or layer, there are no intermediate elements or layers. Other terms describing relationships between elements should be interpreted similarly (e.g., "between" vs. "directly between," "adjacent" vs. "directly adjacent," etc.). The term "and / or" in this document covers any combination of one or more of the listed related terms.

[0020] Although terms such as “first,” “second,” and “third” may be used herein to describe various elements, components, regions, layers, and / or portions, these elements, components, regions, layers, and / or portions should not be limited by these terms. These terms are used only to distinguish different regions, layers, or portions. Numerical terms such as “first” and “second” as used in this specification do not imply order or sequence unless explicitly indicated by the context. Therefore, the first element, component, region, layer, or portion described below may also be referred to as a second element, component, region, layer, or portion without departing from the teachings of the exemplary embodiments.

[0021] Spatial relative terms (such as "inner side," "outer side," "below," "below," "lower part," "above," "upper part," etc.) are used in this specification for ease of description to illustrate the relative relationship between a component or feature in the illustrations and other components or features. Spatial relative terms may cover not only the orientation of the illustrated device but also different orientations during use or operation. For example, if the illustrated device is flipped, a component originally described as "below" or "below" will become "above." Therefore, the term "below" can encompass both the upper and lower orientations. The device may be in other orientations (rotated 90 degrees or other angles), and the spatial relative descriptive terms used herein should be interpreted accordingly.

[0022] See Figure 1 The illustration shows a vehicle 10 comprising a rear suspension 12, a front suspension 14, and a body 16. The rear suspension 12 is equipped with a rear axle assembly (not shown) adapted to operatively support the rear wheels 18 of the vehicle. This rear axle assembly is operatively connected to the body 16 via a pair of shock absorbers 20 and a pair of coil springs 22. Similarly, the front suspension 14 comprises a front axle assembly (not shown) operatively supporting the front wheels 24 of the vehicle. This front axle assembly is operatively connected to the body 16 via a second pair of shock absorbers 26 and a pair of coil springs 28. The shock absorbers 20 and 26 function to suppress relative movement between the unsprung parts (front suspension 14 and rear suspension 12, respectively) and the sprung parts (i.e., the body 16) of the vehicle 10. Although the illustrated vehicle 10 is a passenger car equipped with front and rear axle assemblies, the shock absorbers 20 and 26 can also be applied to other types of vehicles or machinery, or for other applications, such as vehicles employing independent front and / or independent rear suspension systems. Furthermore, the term "shock absorber" as used herein refers to shock absorbers and shock absorber systems in general, and therefore includes MacPherson struts. It should be specifically noted that the scope of protection of this disclosure covers independent shock absorbers 20 and coil-over shock absorbers 26.

[0023] See also: Figure 2 The shock absorber 20 is shown in more detail. Although Figure 2 Only damper 20 is shown, but it should be understood that damper 26 also includes the piston assembly described below for damper 20. The only difference between damper 26 and damper 20 is the manner in which they are adapted to be connected to the sprung and unsprung parts of vehicle 10, and the mounting position of coil spring 28 relative to damper 26.

[0024] The shock absorber 20 includes a pressure tube 30, a piston assembly 32, and a piston rod 34. The pressure tube 30 and the piston rod 34 extend coaxially along a longitudinal axis 35. The pressure tube 30 forms an internal chamber 42. The piston assembly 32 is slidably disposed within the internal chamber 42 of the pressure tube 30, dividing the internal chamber into a first working chamber 44 and a second working chamber 46. A seal 48 is disposed between the piston assembly 32 and the pressure tube 30, allowing the piston assembly 32 to slide relative to the pressure tube 30 without generating excessive friction, while also achieving a sealed isolation between the first working chamber 44 and the second working chamber 46.

[0025] Piston rod 34 is connected to piston assembly 32 and extends through first working chamber 44 and through upper end cap 50 of first end 51 of closed pressure tube 30. The connecting end 53 of piston rod 34 opposite piston assembly 32 is connected to body 16 of vehicle 10 (i.e., the sprung portion of vehicle 10). Pressure tube 30 is filled with hydraulic fluid, and its second end 55 is provided with a connecting joint 54, which connects to the unsprung portions of suspension 12 and 14. Thus, first working chamber 44 is located between first end 51 of pressure tube 30 and piston assembly 32, and second working chamber 46 is located between second end 55 of pressure tube 30 and piston assembly 32. Suspension movement of vehicle 10 will cause piston assembly 32 to extend / rebound or compress relative to pressure tube 30. A valve system inside piston assembly 32 controls the flow of hydraulic fluid between first working chamber 44 and second working chamber 46 as piston assembly 32 moves within pressure tube 30. It should be understood that the shock absorber 20 can be installed in reverse: in this case, the connecting end 53 of the piston rod 34 is connected to the unsprung parts of the suspension 12 and 14, while the connecting joint 54 is connected to the body 16 (i.e. the sprung part of the vehicle 10).

[0026] Reference Figure 3A , Figure 3B , Figure 4 and Figure 5The piston assembly 32 includes a piston body 60 connected to a piston rod 34, a compression relief valve assembly 62, a springback relief valve assembly 64, a compression discharge valve assembly 66, and a springback discharge valve assembly 68. The piston rod 34 has a reduced-diameter section 70 at its end, which is positioned within a pressure tube 30, forming a shoulder 72 that abuts against the piston assembly 32. The piston body 60 is located on the reduced-diameter section 70. The compression relief valve assembly 62 and the compression discharge valve assembly 66 are longitudinally distributed between the piston body 60 and the shoulder 72; the springback relief valve assembly 64 and the springback discharge valve assembly 68 are longitudinally distributed between the piston body 60 and the threaded end 74 of the piston rod 34. A retaining nut 76 engages with the threaded end 74 of the piston rod 34 to fix the compression discharge valve assembly 66, the compression relief valve assembly 62, the piston body 60, the springback relief valve assembly 64, and the springback discharge valve assembly 68 to the piston rod 34. The piston body 60 abuts against the compression relief valve assembly 62, the compression relief valve assembly abuts against the compression discharge valve assembly 66, and the compression discharge valve assembly abuts against the shoulder 72 formed on the piston rod 34. The piston body 60 also abuts against the springback relief valve assembly 64, the springback relief valve assembly abuts against the springback discharge valve assembly 68, and the springback discharge valve assembly abuts against the retaining nut 76. The retaining nut 76 secures the piston body 60, the compression relief valve assembly 62, the compression discharge valve assembly 66, the springback relief valve assembly 64, and the springback discharge valve assembly 68 to the piston rod 34.

[0027] Continue to refer to Figure 3A , Figure 3B , Figure 4 and Figure 5 The piston body 60 includes a first surface 80 located on a first side 82 and a second surface 84 located on a second side 86. The first surface 80 is opposite to and spaced apart from the second surface 84 along a longitudinal axis 35. In some embodiments, the first surface 80 and the second surface 84 may be planar. The first surface 80 and the first side 82 may face a first working chamber 44, and the second surface 84 and the second side 86 may face a second working chamber 46. The piston body 60 includes a central bore 88 through which a piston rod 34 is configured to extend. The piston body 60 also includes a hub 90 surrounding the central bore 88, which extends from the first surface 80 and the second surface 84, respectively. Each hub 90 has a hub surface 92 formed at its end. The outer periphery 94 of the piston body 60 is configured to receive a seal 48. The piston body 60 defines a plurality of compressed flow discharge channels 96, a plurality of rebound flow discharge channels 98, and a plurality of venting channels 100. The compressed flow discharge channel 96, the rebound flow discharge channel 98, and the discharge channel 100 are all channels through which hydraulic fluid can flow. Therefore, the compressed flow discharge channel 96, the rebound flow discharge channel 98, and the discharge channel 100 can all be referred to as fluid channels.

[0028] Compression relief valve assembly and springback relief valve assembly The compression relief valve assembly 62 includes, for example, a first set of valve components, such as a flow-limiting disc 102, an orifice disc 104, a fulcrum disc 106, a check disc 108, and a spring 110. The flow-limiting disc 102, orifice disc 104, fulcrum disc 106, check disc 108, and spring 110 of the compression relief valve assembly 62 are stacked along axis 35 on a first side 82 of the piston body 60.

[0029] The springback relief valve assembly 64 includes, for example, a second set of valve assemblies, wherein the second set of valve assemblies has the same type and number of components as the first set of valve assemblies. The springback relief valve assembly 64 includes, for example, a flow-limiting disc 102, an orifice disc 104, a fulcrum disc 106, a check disc 108, and a spring 110. The flow-limiting disc 102, orifice disc 104, fulcrum disc 106, check disc 108, and spring 110 of the springback relief valve assembly 64 are stacked along axis 35 on the second side 86 of the piston body 60.

[0030] Although the compression relief valve assembly 62 and the springback relief valve assembly 64 have the same type and number of components in the illustrations and description, in some embodiments, the type and number of components in the compression relief valve assembly 62 may differ from those in the springback relief valve assembly 64. Furthermore, in some embodiments, one or more of the compression relief valve assembly 62 and the springback relief valve assembly 64 may include more, fewer, and / or other components without departing from the scope of the invention. Therefore, there is no requirement for the exact type, number, and / or arrangement of the components. The flow-limiting disc 102, the orifice disc 104, and the check disc 108 can be collectively referred to as relief discs.

[0031] Continue to refer to Figure 3A and 3B The flow limiting plate 102, the orifice plate 104, the fulcrum plate 106, the check plate 108, and the spring 110 will be shown and explained in more detail.

[0032] Rate limiting disk The flow-limiting disc 102 includes a ring 112 having a central aperture 114 and fingers 116 extending radially outward from the ring 112. In some embodiments, the fingers 116 are opposite each other such that they are spaced approximately 180 degrees apart about an axis 35. In some embodiments, the fingers 116 are spaced apart from each other at angles less than or greater than 180 degrees about the axis 35. The flow-limiting disc 102 may be bow-tie shaped. For example, the width of the fingers 116 gradually increases along their extension direction, such that the fingers 116 gradually widen away from the ring 112. Although illustrated as a bow-tie shape, in some embodiments, the fingers 116 of the flow-limiting disc 102 may take other shapes, such as being limited to rectangular or square shapes. Although illustrated with two fingers 116, the flow-limiting disc 102 may also include only one or more fingers 116. The flow-limiting disc 102 can move from an unbent / undeflected position to a bent / deflected position. In the unbent / undeflected position, the fingers 116 of the flow-limiting disc 102 are configured to contact the piston body 60.

[0033] The flow-limiting disc 102 also includes one or more orifices 118. For example, each finger 116 is provided with an orifice 118 extending radially inward from the outer edge of each finger 116 of the flow-limiting disc 102. The orifices 118 are designed to allow fluid to flow axially and / or radially relative to the axis 35 of the damper 20. Hydraulic fluid can flow through the orifices 118 and the venting passage 100. Each orifice 118 is open in the axial direction and configured to allow fluid to flow axially through the flow-limiting disc 102 relative to the axis 35. Furthermore, each orifice 118 is open in the radial direction and configured to allow fluid to flow radially relative to the axis 35 through the orifice 118 at the outer edge of the finger 116. In some embodiments, the orifices 118 are configured to remain open for fluid flow regardless of the position of the flow-limiting disc 102.

[0034] Orifice plate The orifice plate 104 includes a ring 120 having a central hole 122 and fingers 124 extending radially outward from the ring 120. In some embodiments, the fingers 124 are opposite each other such that they are spaced approximately 180 degrees apart about an axis 35. The orifice plate 104 may be bow-tie shaped. For example, the width of the fingers 124 gradually increases along its extension direction, such that the fingers 124 gradually widen as they extend away from the ring 120. Although illustrated as a bow-tie shape, in some embodiments, the fingers 124 of the orifice plate 104 may take other shapes, such as being limited to rectangular or square shapes. Although illustrated as two fingers 124, the orifice plate 104 may also include only one or more fingers 124. In some embodiments, the fingers 124 of the orifice plate 104 have the same size and shape as the fingers 116 of the flow-limiting plate 102.

[0035] The orifice plate 104 also includes one or more orifices 126. For example, each finger 124 is provided with an orifice 126, which extends radially inward from the outer edge of each finger 124 in the orifice plate 104. In some embodiments, the orifices 126 of the orifice plate 104 have the same size and shape as the orifices 118 of the flow-limiting plate 102. In some embodiments, the orifices 126 of the orifice plate 104 have different sizes and / or shapes than the orifices 118 of the flow-limiting plate 102.

[0036] The orifice 126 is designed to allow fluid to flow axially and / or radially relative to the axis 35 of the damper 20. Hydraulic fluid can flow through the orifice 126 and the venting passage 100. Each orifice 126 opens in the axial direction and is configured to allow fluid to flow axially relative to the axis 35 through the orifice plate 104. Furthermore, each orifice 126 opens in the radial direction and is configured to allow fluid to flow radially relative to the axis 35 through the orifice 126 at the outer edge of the finger 124. In some embodiments, the orifice 126 remains open for fluid flow regardless of the position of the orifice plate 104.

[0037] Pivot plate The fulcrum plate 106 includes a ring 128 with a center hole 130. The fulcrum plate 106 is configured to provide a fulcrum for the check plate 108.

[0038] Stop-loss order The check valve 108 includes a ring 132 having a central aperture 134 and fingers 136 extending radially outward from the ring 132. In some embodiments, the fingers 136 are opposite each other such that they are spaced approximately 180 degrees apart about axis 35. The check valve 108 may be bow-tie shaped. For example, the width of the fingers 136 gradually increases along their extension direction, such that the fingers 136 gradually widen as they extend away from the ring 132. Although illustrated as a bow-tie shape, in some embodiments, the fingers 136 of the check valve 108 may take other shapes, such as being limited to rectangular or square. Although illustrated as two fingers 136, the check valve 108 may also include only one or more fingers 136. In some embodiments, the fingers 136 of the check valve 108 have the same size and shape as the fingers 116 of the flow restrictor 102 and / or the fingers 124 of the orifice 104.

[0039] spring Spring 110 includes a ring 138 having a central hole 140, and a plurality of arms 142 extending circumferentially and radially outward from the ring 138. The plurality of arms 142 are bent at an angle relative to the plane formed by the ring 138. Spring 110 is made of an elastically deformable material, such as spring steel, plastic with suitable elastic properties, etc. Although three arms 142 are illustrated, spring 110 may also contain only one, two, or more than three arms 142. In some embodiments, spring 110 may employ a wave spring structure.

[0040] Compression valve assembly and springback valve assembly The compression relief valve assembly 66 includes, for example, a third valve assembly including a blowoff disc 144, a ring 146, multiple valve plates 148, a pivot disc 150, a pivot support disc 152, and a valve limiter 154. The blowoff disc 144, ring 146, multiple valve plates 148, pivot disc 150, pivot support disc 152, and valve limiter 154 are stacked along axis 35 on a first side 82 of the piston body 60, wherein the compression relief valve assembly 62 is disposed between the piston body 60 and the compression relief valve assembly 66.

[0041] The springback discharge valve assembly 68 includes, for example, a fourth set of valve assemblies, which has the same type and number of components as the third set of valve assemblies. The springback discharge valve assembly 68 includes, for example, a discharge disc 144, a ring 146, multiple valve plates 148, a pivot disc 150, a pivot support disc 152, and a valve limiter 154. The discharge disc 144, ring 146, multiple valve plates 148, pivot disc 150, pivot support disc 152, and valve limiter 154 of the springback discharge valve assembly 68 are configured to be stacked along axis 35 on the second side 86 of the piston body 60, wherein the springback discharge valve assembly 64 is located between the piston body 60 and the springback discharge valve assembly 68.

[0042] Although the compression relief valve assembly 66 and the springback relief valve assembly 68 have the same type and number of components in the illustrations and description, in some embodiments, the type and number of components in the compression relief valve assembly 66 may differ from those in the springback relief valve assembly 68. Furthermore, in some embodiments, one or more of the compression relief valve assembly 66 and the springback relief valve assembly 68 may include additional, fewer, and / or other components without departing from the scope of the invention. Therefore, it is not required that the components have a precise type, number, and / or arrangement.

[0043] Continue to refer to Figure 3A and 3B The following section will provide a more detailed demonstration and explanation of each of the following components: discharge disc 144, ring 146, multiple valve plates 148, pivot disc 150, and valve limiter 154.

[0044] Discharge disc The discharge disc 144 is a disc-shaped structure with a central hole 156 and a plurality of openings 158. These openings 158 are arranged around an axis 35. In some embodiments, the openings 158 of the discharge disc 144 overlap circumferentially when two or more openings 158 are located on a common radius extending from the axis 35. These openings 158 may be spaced apart from each other along the radial direction of the discharge disc 144. The openings 158 are configured to reduce the stiffness of the discharge disc 144 and allow fluid to flow from one side of the discharge disc 144 to the other. Although three openings 158 are illustrated, in some embodiments, the discharge disc 144 includes more than three openings 158. In some embodiments, the discharge disc 144 includes fewer than three openings 158. In other embodiments, the discharge disc 144 does not include openings 158.

[0045] ring The ring 146 has a circular structure and a central hole 160. This ring can be made of metal, plastic, or any suitable material. It is positioned radially outward of the opening 158 of the discharge disc 144 to provide internal preload to the valve plate 148.

[0046] Valve plate The valve plate 148 is a circular thin sheet structure with a central hole 162. The valve plate 148 has elastic deformation capability. For example, a force applied to the outer edge of the valve plate 148 can cause it to bend and deform, resulting in axial displacement of the outer edge relative to the respective central hole 162 of the valve plate 148. The valve plate 148 is made of an elastically deformable material, such as spring steel or plastic with suitable elastic properties.

[0047] In some embodiments, the valve plate 148 has a different diameter. For example, as Figure 3A , Figure 3B , Figure 4 and Figure 5 As shown, the valve plates 148 are arranged such that the valve plate 78 with the largest diameter is closest to the piston body 60, while the valve plate 78 with the smallest diameter is furthest from the piston body 60. Therefore, the diameter of each valve plate 78 decreases along the axis 35 with increasing distance from the piston body 60. For example, the outer diameter of the first valve plate 78 closest to the piston body 60 is larger than the outer diameter of the valve plate immediately adjacent to it, and so on. Therefore, the diameter of the valve plate 78 furthest from the piston body 60 is smaller than the diameters of the other valve plates 78. In another example, the valve plates 148 can be designed as a leaf spring-like structure.

[0048] Pivot plate The pivot plate 150 includes a ring 164 with a central hole 166. The pivot plate 150 provides a pivot or bending point for the valve plate 148. For example, the pivot plate 150 abuts against the smallest valve plate 78, opposite the adjacent larger valve plate 78. The outer diameter of the pivot plate 150 is smaller than the outer diameter of the smallest valve plate 78 it abuts against.

[0049] Pivot support plate The fulcrum support plate 152 includes a ring 168 having a central hole 170. This plate maintains a predetermined distance between the valve plate 148 and the valve limiter 154, allowing the valve plate 148 to bend during operation. The fulcrum support plate 152 can also be configured to limit the deflection of the valve plate 148.

[0050] Valve limiter The valve limiter (or preload gasket) 154 includes a ring 172 with a center hole 174. This limiter is used to protect the valve plate 78 and is configured to limit the deflection of the valve plate 148.

[0051] Piston body Reference Figure 4 , Figure 5 and Figure 6A The structural details of the piston body 60 are further shown and explained. Multiple compression discharge channels 96 include, for example, a first compression discharge channel 176, a second compression discharge channel 178, and a third compression discharge channel 180. Multiple springback discharge channels 98 include, for example, a first springback discharge channel 182, a second springback discharge channel 184, and a third springback discharge channel 186.

[0052] The piston body 60 also includes additional features disposed on its first side 82 and second side 86. The additional features of the piston body 60 include a plurality of first circumferential walls 188 and a plurality of second circumferential walls 190. The piston body 60 may also include one or more additional optional features, such as: one or more notches 192, one or more walls 194, one or more ribs 196 (see...). Figure 6B One or more support members 198 and one or more support members 200. For example... Figure 4 , Figure 5 and Figure 6A As shown, these features are identical on both the first surface 80 and the second surface 84. Therefore, for simplicity, these features will be described below using only the first side 82 of the piston body 60 as an example. It should be understood that in some embodiments, the features on the first side 82 of the piston body 60 may differ from those on the second side 86. It should also be understood that in some embodiments of the piston body 60, not all features are necessary.

[0053] First and second circumferential walls and bosses A plurality of first circumferential walls 188 located on the first side 82 of the piston body 60 extend from the first surface 80 of the piston body 60 in a direction away from the second surface 84. Each first circumferential wall 188 terminates at its distal end with a first circumferential boss 202. In some embodiments, the first circumferential boss 202 is parallel to the first surface 80. On the first side 82 of the piston body 60, each compression discharge passage 96 is surrounded by a corresponding first circumferential wall 188 and a first circumferential boss 202. For example, on the first side 82 of the piston body 60, each first compression discharge passage 176, second compression discharge passage 178, and third compression discharge passage 180 is surrounded by a corresponding first circumferential wall 188 and a first circumferential boss 202.

[0054] A first circumferential boss 202 on the first side 82 of the piston body 60 is located at a first distance from the first surface 80 and at a greater distance from the second surface 84. During operation of the damper 20, a discharge disc (e.g., discharge disc 144) is configured to be selectively driven to engage with the first circumferential boss 202. The first circumferential boss 202 provides a first sealing surface configured to selectively form a seal with the discharge disc (e.g., discharge disc 144).

[0055] A plurality of second circumferential walls 190 located on the first side 82 of the piston body 60 extend from the first surface 80 of the piston body 60 in a direction away from the second surface 84. Each second circumferential wall 190 terminates at its distal end with a second circumferential boss 204. In some embodiments, the second circumferential boss 204 is parallel to the first surface 80. On the first side 82 of the piston body 60, each springback discharge channel 98 and each vent channel 100 is surrounded by a corresponding second circumferential wall 190 and a second circumferential boss 204. For example, on the first side 82 of the piston body 60, each second springback discharge channel 184, third springback discharge channel 186, and vent channel 100 are all surrounded by a corresponding second circumferential wall 190 and a second circumferential boss 204.

[0056] The second circumferential boss 204 on the first side 82 of the piston body 60 is located at a second distance from the first surface 80 of the piston body 60. This second distance is smaller than the first distance. The second circumferential boss 204 is located in the longitudinal direction between the first surface 80 of the piston body 60 and the first circumferential boss 202.

[0057] During operation of the damper 20, a portion of the bleed disk (e.g., the flow-limiting disk 102) is configured to be selectively driven to engage with the second circumferential boss 204. For example, at least partially, the fingers 116 of the flow-limiting disk 102 are configured to be selectively driven to engage with the second circumferential boss 204. When the fingers 116 engage with the second circumferential boss 204, they cooperate to form a seal at their interface. The smaller surface area of ​​the second circumferential boss 204 facilitates sealing compared to the entire flat surface of a conventional piston body. Furthermore, the second circumferential wall 190 and the second circumferential boss 204 minimize the risk of small particles (such as contaminants) in the hydraulic fluid becoming trapped below the flow-limiting disk 102 and between the flow-limiting disk 102 and the piston body 60, thereby preventing the formation of leakage paths. Therefore, compared to a conventional piston body, the second circumferential boss 204 provides improved sealing performance for the flow-limiting disk 102 and achieves more repeatable closure behavior.

[0058] Sloping notch Continue to refer to Figure 6A Inside the second circumferential wall 190 surrounding the drain channel 100, and located between the second circumferential wall 190 and the drain channel 100, a notch 192 inclined or sloped towards the drain channel 100 is provided, thereby forming a flow-guiding structural feature designed to enhance the flowability of hydraulic fluid into the drain channel 100. In some embodiments, the inclination angle of the notch 192 relative to the first surface 80 of the piston body 60 may be between about 10 degrees and about 80 degrees. In some embodiments, the angle of the notch 192 relative to the first surface 80 of the piston body 60 may range from about 20 degrees to about 60 degrees. In some embodiments, the angle of the notch 192 relative to the first surface 80 of the piston body 60 may range from about 30 degrees to about 50 degrees. In some embodiments, the angle of the notch 192 relative to the first surface 80 of the piston body 60 may be about 45 degrees. In some embodiments, the angle of the notch 192 relative to the first surface 80 of the piston body 60 may be about 22 degrees.

[0059] like Figure 6A As shown, the width of the notch 192 is less than the radial length of the drain channel 100. The notch 192 is approximately aligned with the middle of the radial length of the drain channel 100. In some embodiments, the width of the notch 192 is equal to the radial length of the drain channel 100. The width of the notch 192 near the second circumferential wall 190 is greater than the width of the notch 192 near the drain channel 100. However, in some embodiments, the width of the notch 192 near the second circumferential wall 190 may be smaller than the width of the notch 192 near the drain channel 100. In other embodiments, the width of the notch 192 near the second circumferential wall 190 may be equal to the width of the notch 192 near the drain channel 100.

[0060] The notch 192 is configured to provide an increased available venting adjustment area without excessively occupying the area of ​​the discharge channel by optimizing the use of the area between the venting channel 100 and the adjacent discharge channel (e.g., the first rebound discharge channel 182). The notch 192 provides additional area for hydraulic fluid flow.

[0061] Walls and bosses One or more walls 194 of the piston body 60 are located on a first side 82 of the piston body 60 and are adjacent to one or more spring-loaded discharge channels 98. For example, one or more walls 194 extend from a first surface 80 of the piston body 60 in a direction away from a second surface 84. The one or more walls 194 may be radially located between a central bore 88 and one or more spring-loaded discharge channels 98. Each wall 194 terminates at its distal end with a boss 206, wherein each boss 206 is coplanar with a first circumferential boss 202. For example, as shown in the image. Figure 6A As shown, each wall 194 on the first side 82 of the piston body 60 can be connected to the first circumferential wall 188 of an adjacent compressed flow discharge passage 96 (such as a second compressed flow discharge passage 178). In some embodiments, a low-lying region or gap 208 is provided between adjacent first circumferential bosses 202 and 206, which forms a flow channel for hydraulic fluid.

[0062] During operation of the damper 20, the discharge disc 144 is configured to be selectively driven to engage with the boss 206. Due to the existence of two fluid channels (e.g., venting channel 100 and first rebound discharge channel 182) between the compressed flow discharge channels 96 (e.g., first compressed flow discharge channel 176 and second compressed flow discharge channel 178), the circumferential distance between some of the compressed flow discharge channels 96 is relatively large. This large circumferential distance can cause deformation of the discharge disc (e.g., discharge disc 144), thus affecting the repeatability of the damper 20. Therefore, the wall 194 and the boss 206 thereon provide support for the discharge disc (e.g., discharge disc 144) to reduce or eliminate deformation of the discharge disc.

[0063] The compression flow discharge channel 96, the spring flow discharge channel 98, the first circumferential wall 188, the first circumferential boss 202, the second circumferential wall 190, and the second circumferential boss 204 are all located near the outer periphery 94 of the piston body 60.

[0064] Support components One or more supports 198 of the piston body 60 are located on a first side 82 of the piston body 60. The supports 198 extend from a first surface 80 of the piston body 60 in a direction away from a second surface 84. Each support 198 terminates at its distal end with a boss 210, wherein each boss 210 is coplanar with a second circumferential boss 204. Therefore, each boss 210 is positioned at the same distance as the second circumferential boss 204. Figure 6AAs shown, in some embodiments, a support 198 extends along a first surface 80 and partially circumferentially around a central bore 88 of the piston body 60, and may be located between the hub 90 and the compression flow discharge channel 96 and the spring flow discharge channel 98, maintaining a radial distance from the axis 35. For example, the support 198 is arcuate, and there are one or more interruptions or gaps 212 between each support 198. In some embodiments, these interruptions or gaps 212 allow hydraulic fluid to flow between the support 198 and the hub 90. In some embodiments, the piston body 60 may have only a single support 198. For example, the support 198 may be a circular support structure surrounding the hub 90 without any gaps or interruptions. In some embodiments, the support 198 may extend radially between the hub 90 and the compression flow discharge channel 96 and the spring flow discharge channel 98, wherein one or more supports 198 are spaced apart from each other circumferentially along the central bore 88 of the piston body 60. The support member 198 is radially located between the hub 90 and the first circumferential boss 202 and the second circumferential boss 204.

[0065] Furthermore, one or more supports 200 are located on a first side 82 of the piston body 60. The supports 200 extend from the first surface 80 of the piston body 60 in a direction away from the second surface 84. The distal end of each support 200 terminates with a boss 214, wherein each boss 214 is coplanar with the second circumferential boss 204 and the boss 210 of the support 200. Therefore, each boss 214 is positioned at the same distance as the second circumferential boss 204. Figure 6A As shown, in some embodiments, the support 200 extends circumferentially around the central hole 88 of the piston body 60 along the first surface 80 and may be located between the hub 90 and the support 200, at a radial distance from the axis 35.

[0066] Boss 210 is configured to support the surface of a bleed disc (e.g., flow-limiting disc 102). Boss 210 also serves to prevent deformation of the flow-limiting disc 102. Support 198 on the first side 82 allows hydraulic fluid to flow below the flow-limiting disc 102, between the first surface 80 of the piston body 60 and the flow-limiting disc 102. Therefore, the pressure difference experienced by the flow-limiting disc 102 is zero, as the pressure above and below it will be equal. Second circumferential boss 204 and boss 210 are used to support a portion of the surface of the bleed disc (e.g., flow-limiting disc 102) at a second distance from the first surface 80. The bleed disc, the second circumferential wall 190, and the first support 198 are configured to cooperate in forming a fluid channel through which hydraulic fluid can flow between the surface of the bleed disc and the first surface 80 of the piston body 60.

[0067] The support 198 serves to reduce the contact surface area between the flow-limiting disc 102 and the piston body 60. Because a conventional piston body has a generally flat surface, there is a relatively large contact surface area between the piston body and any flow-limiting disc it contacts. This relatively large contact surface area, along with the hydraulic fluid accumulating between the conventional piston body and the flow-limiting disc, can cause the flow-limiting disc to adhere to the piston body. This adhesion can trigger abnormal or uncontrolled opening and / or closing behavior of the flow-limiting disc. Therefore, by reducing the contact surface area, the support 198 reduces or eliminates the adhesion between the flow-limiting disc 102 and the piston body 60, thereby reducing or eliminating undesirable or uncontrolled opening and / or closing behavior of the flow-limiting disc 102. Furthermore, the support 198 reduces or eliminates contact noise between the flow-limiting disc 102 and the piston body 60, thereby reducing noise, vibration, and harshness (NVH) problems. Furthermore, the support member 198, boss 210, support member 200, and boss 214, together with the second circumferential wall 190 and the second circumferential boss 204, help reduce the risk of small particles (such as contaminants) in the hydraulic fluid becoming trapped below the flow restrictor 102 and between the flow restrictor 102 and the piston body 60, thus creating a leakage path. Therefore, compared to a conventional piston body, the second circumferential boss 204, boss 210, and boss 214 provide improved sealing capability of the flow restrictor 102 and more repeatable closing behavior results.

[0068] rib like Figure 6B As shown, in some embodiments, the piston body 60 also includes ribs 196 extending from one or more first circumferential walls 188 in a direction away from the fluid passage surrounded by the first circumferential walls 188. These ribs 196 are configured to reduce the contact area between the piston body 60 and the drain plates (e.g., the flow-limiting plate 102, the orifice plate 104, and the check plate 108). This reduction in contact area reduces friction by reducing or preventing the edges of one or more drain plates from scraping against the piston body 60. Furthermore, by reducing the contact area and friction between the drain plates and the piston body 60, the repeatability of the drain plate's opening-draining-closing behavior is improved.

[0069] Assembled compression relief valve assembly and springback relief valve assembly After describing the various components of the compression relief valve assembly 62 and the springback relief valve assembly 64, the following section combines... Figure 3A , Figure 3B , Figure 4 and Figure 5 This describes the position and arrangement of each component when the compression relief valve assembly 62 and the rebound relief valve assembly 64 are assembled to the vibration damper 20. In some embodiments, such as... Figure 3A , Figure 3B , Figure 4 and Figure 5As shown, the assembly layout of the compression relief valve assembly 62 is the same as that of the springback relief valve assembly 64. That is, the components on the first side 82 of the piston body 60 are arranged in a mirror image symmetrically on the second side 86. Therefore, the following description of the assembly arrangement of the compression relief valve assembly 62 on the first side 82 of the piston body 60 also applies to the springback relief valve assembly 64 on the second side of the piston body 60. It should be noted that this assembly layout is only an example, and in some embodiments, the number, type, and layout of the components may differ, but all remain within the scope of the present invention.

[0070] When assembled into the damper 20, the flow-limiting disc 102 is close to the piston body 60, the hub 90 is accommodated in the central hole 114 of the flow-limiting disc 102, and the fingers 116 selectively cover the bleed passage 100. For example, the fingers 116 are circumferentially aligned with the bleed passage 100 and extend radially beyond the bleed passage 100.

[0071] The orifice plate 104 contacts the flow-limiting plate 102, which is located between the piston body 60 and the orifice plate 104. Furthermore, when assembled into the damper 20, the hub 90 is received in the central bore 122 of the orifice plate 104, and the fingers 124 of the orifice plate 104 overlap or cover the fingers 116 of the flow-limiting plate 102. Additionally, when assembled into the damper 20, the orifice 126 of the orifice plate 104 is aligned with the orifice 118 of the flow-limiting plate 102. The orifice 126 of the orifice plate 104 and the orifice 118 of the flow-limiting plate 102 cooperate to form a radially open region and an axially open region (parallel to axis 35). The radially open region provides a continuously open fluid flow path to allow radially open venting flow.

[0072] The pivot plate 106 contacts the orifice plate 104, wherein the flow-limiting plate 102 and the orifice plate 104 are located between the piston body 60 and the pivot plate 106. Furthermore, when assembled to the damper 20, the hub 90 is received in the center bore 130 of the pivot plate 106. The pivot plate 106 provides a fulcrum or bending point for the return plate 108.

[0073] The check disc 108 contacts the pivot disc 106, wherein the flow-limiting disc 102, the orifice disc 104, and the pivot disc 106 are located between the piston body 60 and the check disc 108. Furthermore, when assembled to the shock absorber 20, the hub 90 is received in the center bore 134 of the check disc 108. Additionally, when assembled to the shock absorber 20, the fingers 136 of the check disc 108 are located above one or more fingers 124 of the orifice disc 104 and the fingers 116 of the flow-limiting disc 102.

[0074] The check disc 108 is configured to be selectively in a first position or a second position. When the check disc 108 is in the first position, the fingers 136 of the check disc 108 are positioned above the fingers 124 of the flow restrictor 104 and maintain a distance from the orifice disc 108 equal to the thickness of the fulcrum disc 106. Furthermore, when the check disc 108 is in the first position, both the axial opening region and the radial opening region are open to fluid flow. When the check disc 108 is in the second position, its fingers 136 contact the fingers 124 of the orifice disc 104 and cover the orifice 126 of the orifice disc 104 and the orifice 118 of the flow restrictor 102. Furthermore, when the check disc 108 is in the second position, the axial opening region is closed to fluid flow, and only the radial opening region remains open to fluid flow. (Refer to...) Figure 4 The check plate 108 includes a first surface that can selectively engage with the opposing surface of the orifice plate 104 to close the axial opening region.

[0075] When assembled into the damper 20, the ring 138 of the spring 110 contacts the hub surface 92 of the hub 90. Furthermore, the orientation of the spring 110 causes its arm 142 to abut against the check disc 108, thereby applying a force to the check disc. This force will push the stacked check disc 108, fulcrum disc 106, orifice disc 104, and flow-limiting disc 102 against the piston body.

[0076] Assembled compression valve assembly and springback valve assembly After describing the components of the compression discharge valve assembly 66 and the spring discharge valve assembly 68, refer now to Figure 3A , Figure 3B , Figure 4 and Figure 5 This describes the position and arrangement of each component when the compression relief valve assembly 66 and the rebound relief valve assembly 68 are assembled into the vibration damper 20. In some embodiments, such as... Figure 3A , Figure 3B , Figure 4 and Figure 5 As shown, the assembly layout of the components of the compression discharge valve assembly 66 is the same as that of the components of the spring-loaded discharge valve assembly 68. That is, the arrangement of the components on the first side 82 of the piston body 60 is mirror-symmetrical to the arrangement on the second side 86. Therefore, the following description of the component arrangement of the compression discharge valve assembly 66 on the first side 82 of the piston body 60 also applies to the spring-loaded discharge valve assembly 68 on the second side 86 of the piston body 60. It is understood that this component arrangement is only illustrative, and in some embodiments, the number, type, and arrangement of the components may differ, but all of these do not depart from the scope of protection of this invention.

[0077] When assembled into the damper 20, the compression relief valve assembly 66 is in contact with at least a portion of the compression relief valve assembly 62; and the springback relief valve assembly 68 is in contact with at least a portion of the springback relief valve assembly 64.

[0078] The discharge disc 144 contacts the spring 110 of the adjacent compression relief valve assembly 62 or the springback relief valve assembly 64. The discharge disc 144 also contacts the first circumferential boss 202 of the piston body 60. The ring 146 contacts the discharge disc 144, which is located between the piston body 60 and the ring 146. A plurality of valve plates 148 are provided, with the first valve plate 148 contacting the ring 146, and the discharge disc 144 and the ring 146 located between the piston body 60 and the plurality of valve plates 148. The pivot disc 150 contacts the last valve plate 78 of the plurality of valve plates 148. The discharge disc 144, the ring 146, and the plurality of valve plates 148 are located between the piston body 60 and the pivot disc 150. Valve limiter 154 contacts pivot plate 150, wherein discharge plate 144, ring 146, multiple valve plates 148 and pivot plate 150 are located between piston body 60 and valve limiter 154.

[0079] Function During the compression stroke, three types of fluid flows exist between the second working chamber 46 and the first working chamber 44. The first fluid flow is through a continuously open fluid flow path, which is formed by the radially open area formed by the orifice 118 extending to the edge of the flow-limiting disc 102 of the springback relief valve assembly 64 and the orifice 126 extending to the edge of the orifice disc 104, and the radially open area formed by the orifice 118 extending to the edge of the flow-limiting disc 102 of the compression relief valve assembly 62 and the orifice 126 extending to the edge of the orifice disc 104. This allows fluid to flow even when the piston assembly 32 is at zero or near zero speed during the compression stroke. Furthermore, the second fluid flows through the axial opening region (parallel to axis 35) formed by the orifice 118 on the flow-limiting disc 102 and the orifice 126 on the orifice disc 104 in the springback relief valve assembly 64, and through the axial opening region (parallel to axis 35) formed by the orifice 118 on the flow-limiting disc 102 and the orifice 126 on the orifice disc 104 in the compression relief valve assembly 62. The third fluid flows through the compression discharge channel 96.

[0080] During operation, the compression stroke of the piston assembly 32 causes an increase in fluid pressure within the second working chamber 46, multiple compressed flow discharge channels 96, and multiple venting channels 100. Initially, fluid flows into the venting channel 100 through the orifice 126 of the orifice plate 104 of the rebound venting valve assembly 64 and the orifice 118 of the flow-limiting plate 102. After passing through the venting channel 100, it then flows into the first working chamber 44 through the orifice 118 of the flow-limiting plate 102 and the orifice 126 of the orifice plate 104 of the compressed venting valve assembly 62. At this time, the fluid simultaneously flows through both the first fluid flow path and the second fluid flow path.

[0081] As the speed of piston assembly 32 increases, the fluid pressure in the second working chamber 46 will rise. The fluid pressure acting on the check plate 108 of the springback relief valve assembly 64 will cause the check plate 108 to deflect upward toward the orifice plate 104, thereby closing the axial opening region (i.e., the second fluid flow) formed by the orifice 118 in the flow-limiting plate 102 and the orifice 126 in the orifice plate 104 of the springback relief valve assembly 64. This cuts off the second fluid flow and only allows fluid flow through the radial opening region (i.e., the first fluid flow) formed by the orifice 118 in the flow-limiting plate and the orifice 126 in the orifice plate 104 of the springback relief valve assembly 64.

[0082] As the piston assembly 32 speed increases further, the fluid pressure in the multiple compressed flow discharge channels 96 will increase. The fluid pressure acting on the discharge disc 144 of the compressed discharge valve assembly 66 will overcome the bias load between the ring 146 and the valve plate 148 of the compressed discharge valve assembly 66. At this time, the discharge disc 144 of the compressed discharge valve assembly 66 will move axially to open the multiple compressed flow discharge channels 96, thereby forming a third fluid flow.

[0083] During the rebound stroke, three types of fluid flow also exist between the first working chamber 44 and the second working chamber 46. The first fluid flow is through a continuously open fluid flow path, which passes through a radially open area formed by the orifice 118 extending to the edge of the flow-limiting disc 102 of the compression relief valve assembly 62 and the orifice 126 extending to the edge of the orifice disc 104, and through the radially open area formed by the orifice 118 extending to the edge of the flow-limiting disc 102 of the rebound relief valve assembly 64 and the orifice 126 extending to the edge of the orifice disc 104. This allows fluid to continue flowing even when the piston assembly 32 is at zero or near zero speed during the rebound stroke. Furthermore, during the rebound stroke, the second fluid flows through the axial opening region (parallel to axis 35) formed by the orifice 118 on the flow-limiting disc 102 and the orifice 126 on the orifice disc 104 in the compression relief valve assembly 62, and through the axial opening region (parallel to axis 35) formed by the orifice 118 on the flow-limiting disc 102 and the orifice 126 on the orifice disc 104 in the rebound relief valve assembly 64. The third fluid flows through the rebound flow discharge channel 98.

[0084] During operation, the rebound stroke of the piston assembly 32 causes an increase in fluid pressure within the first working chamber 44, the multiple rebound flow discharge channels 98, and the multiple discharge channels 100. Initially, fluid flows into the discharge channel 100 through the orifice 126 of the orifice plate 104 and the orifice 118 of the flow-limiting plate 102 in the compression discharge valve assembly 62. After passing through the discharge channel 100, it flows through the orifice 118 in the flow-limiting plate 102 and the orifice 126 in the orifice plate 104 of the rebound discharge valve assembly 64, finally entering the second working chamber 46. At this time, the fluid simultaneously flows through both the first fluid flow path and the second fluid flow path.

[0085] As the piston assembly 32 speed increases, the fluid pressure in the first working chamber 44 rises. The fluid pressure acting on the check plate 108 of the compression relief valve assembly 62 causes the check plate 108 to deflect downward toward the orifice plate 104, thereby closing the axial opening region (or second fluid flow) formed by the orifice 118 in the flow-limiting plate 102 and the orifice 126 in the orifice plate 104 of the compression relief valve assembly 62. This cuts off the second fluid flow and only allows fluid flow through the radial opening region (i.e., the first fluid flow) formed by the orifice 118 in the flow-limiting plate and the orifice 126 in the orifice plate 104 of the compression relief valve assembly 62. (Refer to...) Figure 4 The check plate 108 has a first surface that can selectively engage with the opposite surface of the orifice plate 104 to close the axial opening region.

[0086] As the speed of piston assembly 32 increases further, the fluid pressure in the multiple spring flow discharge channels 98 will increase accordingly. The fluid pressure acting on the discharge disc 144 of spring discharge valve assembly 68 will overcome the bias load of ring 146 and valve plate 148 of spring discharge valve assembly 68, causing the discharge disc 144 of spring discharge valve assembly 68 to move axially, thereby opening the multiple spring flow discharge channels 98 and forming a third fluid flow path.

[0087] The adjustment of the shock absorber 20 can be controlled by: controlling the size and number of the compression flow discharge channel 96, the rebound flow discharge channel 98, and the venting channel 100; controlling the angle and / or size of the notch 192 in the piston body 60; controlling the design, type, quantity, and / or arrangement of each component of the compression venting valve assembly 62, the rebound venting valve assembly 64, the compression discharge valve assembly 66, and the rebound discharge valve assembly 68; and controlling other design features of the shock absorber 26. Furthermore, the adjustment of the venting fluid flowing through the venting channel 100 can be achieved by: controlling the size and number of the venting channel 100; controlling the size and number of orifices 118 and 126 in the flow-limiting plate 102 and the orifice plate 104 respectively; and / or controlling the thickness of the flow-limiting plate 102, the orifice plate 104, the fulcrum plate 106, and / or the check plate 108.

[0088] Alternative implementation of current limiting disk Current limiting finger section Reference Figure 7A , Figure 7B , Figure 7C , Figure 7D , Figure 7E , Figure 7F This describes an alternative embodiment of the flow-limiting disc 1102. The flow-limiting disc 1102 can directly replace the flow-limiting disc 102. Although it is shown in the illustrations in conjunction with the piston body 60 described herein, the flow-limiting disc 1102 can also be used with other types of piston bodies without departing from the scope of the invention. Therefore, the piston body 60 is not necessarily used in conjunction with the flow-limiting disc 1102, nor is the flow-limiting disc necessarily used in conjunction with the piston body.

[0089] The flow-limiting disc 1102 includes a ring 112 having a central aperture 114, one or more fingers 116 extending radially outward from the ring 112, and one or more apertures 118 extending radially inward from the outer edge of each finger 116. The flow-limiting disc 1102 may be substantially the same as the flow-limiting disc 102, but in addition to including one or more flow-limiting fingers 1116 extending radially outward from the ring 112. The length of the flow-limiting fingers 1116 is defined as a radius 1120 extending from the axis 35. In some embodiments, each flow-limiting finger 1116 has the same radius 1120. In some embodiments, the radius 1120 of one or more flow-limiting fingers 1116 may differ from the radius 1120 of the other one or more flow-limiting fingers 1116. Not all flow-limiting fingers 1116 need to have the same radius 1120. The flow-limiting finger 1116 is configured to extend toward the inlet of one or more compressed flow discharge channels 96 or spring flow discharge channels 98.

[0090] When the radius 1120 of the flow-limiting finger 1116 is sufficiently large, the flow-limiting finger 1116 can at least partially cover one or more inlets of the compressed flow discharge channel 96 or the spring flow discharge channel 98. The larger the radius 1120, the larger the area of ​​the lower inlet of the compressed flow discharge channel 96 or the spring flow discharge channel 98 covered. Therefore, the larger the radius 1120, the stronger the flow-limiting effect on the hydraulic fluid flowing into the compressed flow discharge channel 96 or the spring flow discharge channel 98.

[0091] Depending on the radius 1120 of the flow-limiting finger 1116, the flow-limiting degree of the compressed flow discharge channel 96 or the rebound flow discharge channel 98 can be adjusted between 0% and 100%. For example, Figure 7D As shown, the flow-limiting disc 102 is located on the first side 82 of the piston body 60, and the radius 1120 of the flow-limiting finger 1116 makes the flow restriction degree of the second spring discharge channel 184 and the third spring discharge channel 186 in the spring discharge channel 98 0%. For example, as... Figure 7E As shown, the flow-limiting disc 102 is located on the first side 82 of the piston body 60, and the radius 1120 of the flow-limiting finger 1116 causes the flow restriction degree of the second spring discharge channel 184 and the third spring discharge channel 186 in the spring discharge channel 98 to be 50%. For example, as... Figure 7FAs shown, the flow-limiting disc 102 is located on the first side 82 of the piston body 60, and the radius 1120 of the flow-limiting finger 1116 causes the flow restriction degree of the second spring discharge channel 184 and the third spring discharge channel 186 in the spring discharge channel 98 to be 100%. When the flow restriction degree is 100%, hydraulic fluid can only flow through the piston body 60 through the discharge channel 100 and the first spring discharge channel 182 or the first compression discharge channel 176 of the piston body 60. Although only the flow restriction conditions of 0%, 50%, and 100% are shown, it should be understood that the radius 1120 of the flow-limiting finger 1116 can be selected to provide any flow restriction percentage between 0% and 100%. Figure 11 As shown, as the percentage of current restriction provided by the upper current finger 1116 of the current limiting disc 1102 increases, the damping force of the damper 20 at higher speeds increases accordingly, which can be seen from the E segment parameter of the force response curve of the damper 20.

[0092] In some embodiments, the damper 20 is provided as a kit comprising a plurality of flow-limiting discs 1102, each configured to cover different percentages of the discharge channels (e.g., compression flow discharge channel 96 and rebound flow discharge channel 98) to achieve different percentages of flow restriction. Therefore, the radial length or radius 1120 of the flow-limiting fingers 1116 between the flow-limiting discs 1102 provided in the kit is different. For example: the first flow-limiting disc 1102 in the kit may have one or more flow-limiting fingers 1116 covering 20% ​​of the emission channel; the second flow-limiting disc 1102 in the kit may have one or more flow-limiting fingers 1116 covering 40% of the emission channel; the third flow-limiting disc 1102 in the kit may have one or more flow-limiting fingers 1116 covering 60% of the emission channel; the fourth flow-limiting disc 1102 in the kit may have one or more flow-limiting fingers 1116 covering 80% of the emission channel; and the fifth flow-limiting disc 1102 in the kit may have one or more flow-limiting fingers 1116 covering 100% of the emission channel. Therefore, one of the flow-limiting discs 1102 in the kit can be selected and incorporated into the damper 20 according to the desired damping response.

[0093] Radial opening region and axial opening region For reference Figure 8 The additional adjustment functions of the current limiting plate 1102 and the orifice plate 104 are described below. For example... Figure 8 As shown, when the orifice plate 104 and the flow-limiting plate 1102 are stacked, the orifice 118 of the flow-limiting plate 1102 and the orifice 126 of the orifice plate 104 work together to form a radial opening region 1122 and an axial opening region 1124. The components labeled 1122 and 1124 are not physical parts of the flow-limiting plate 1102 and the orifice plate 104, but rather represent the size and shape of the radial opening region 1122 and the axial opening region 1124.

[0094] The radial opening region 1122 is defined by: (1) the width of the orifice 118 of the flow-limiting disc 1102; (2) the width of the orifice 126 of the orifice disc 104; (3) the thickness of the flow-limiting disc 1102; and (4) the thickness of the orifice disc 104. Therefore, the radial opening region 1122 can be adjusted by changing one or more of the following: (1) the width of the orifice 118 of the flow-limiting disc 1102; (2) the width of the orifice 126 of the orifice disc 104; (3) the thickness of the flow-limiting disc 1102; and (4) the thickness of the orifice disc 104. Adjusting the radial opening region 1122 will change... Figure 10 and Figure 11 The parameters in segment A of the force response curve of the damper 20 shown. Increasing the area of ​​the radial opening region 1122 can expand the conventional discharge range.

[0095] By setting an orifice plate 104 above the flow-limiting plate 1102, with orifices 118 and 126 respectively, the thickness coefficient increases accordingly; when the orifice plate 104 and the flow-limiting plate 1102 have the same thickness, the thickness coefficient will double. Furthermore, by setting an orifice plate 104 above the flow-limiting plate 1102, with orifices 118 and 126 respectively, the ability to adjust the radial opening area can be maximized.

[0096] Refer again Figure 8 The axial opening region 1124 is defined by the smaller of the following two: (1) the width of the orifice 118 of the flow-limiting disk 1102; and (2) the width of the orifice 126 of the orifice disk 104. Therefore, the axial opening region 1124 can be adjusted by adjusting the smallest of the following: (1) the width of the orifice 118 of the flow-limiting disk 1102; or (2) the width of the orifice 126 of the orifice disk 104. That is, the maximum axial opening region 1124 is determined by the minimum orifice size. In some embodiments, the width of the orifice 118 of the flow-limiting disk 1102 is greater than the width of the orifice 126 of the orifice disk 104, such that the axial opening region of the orifice 118 of the flow-limiting disk 1102 is greater than the axial opening region of the orifice 126 of the orifice disk 104.

[0097] The thickness of the axial opening region 1124 and the fulcrum disk 106 together affect the decrease in damping force under open discharge conditions (e.g. Figure 10 and 11(Parameters in segment F of the force response curve of the damper 20 shown). By providing an orifice plate 104 above the flow-limiting plate 1102, independent adjustment of the radial opening region 1122 and the axial opening region 1124 can be achieved. For example, the axial opening region 1124 can be reduced by using an orifice plate 104 with a reduced orifice width 126, while a constant radial opening region 1122 can be maintained by using a flow-limiting plate 1102 with an increased orifice width 118. This ability to independently adjust the radial opening region 1122 and the axial opening region 1124 improves the adjustability of the opening and drainage function.

[0098] In some embodiments, the width of the orifice 118 in each finger 116 of the flow-limiting disk 1102 may be different. For example, the width of the orifice 118 on one finger 116 of the flow-limiting disk 1102 may be smaller than the width of the orifice 118 on another finger 116 of the flow-limiting disk 1102. This provides another way to improve the adjustability of the discharge state.

[0099] Similarly, in some embodiments, the width of the orifice 126 in each finger 124 of the orifice plate 104 may be different. For example, the width of the orifice 126 in one finger 124 of the orifice plate 104 may be smaller than the width of the orifice 126 in another finger 124 of the orifice plate 104. This provides another way to improve the adjustability of the discharge state.

[0100] In some embodiments, the damper 20 is provided as a kit comprising a plurality of flow-limiting discs 1102 and a plurality of orifice discs 104. The flow-limiting discs 1102 in the kit may have different thicknesses, different orifice widths 118, and different radial lengths or radii 1120 of the flow-limiting fingers 1116. Furthermore, the orifice discs 104 in the kit may have different thicknesses and different orifice widths 118. Therefore, one flow-limiting disc 1102 and one orifice disc 104 can be selected from the kit and included in the damper 20 according to the desired damping response.

[0101] although Figure 8 The flow-limiting disc 1102 shown includes flow-limiting fingers 1116, but not all embodiments require the inclusion of these flow-limiting fingers. For example, in some embodiments, one, some, or all of the flow-limiting fingers 1116 may be omitted, and this does not affect the ability to adjust the flow state by changing the radial opening region 1122 and the axial opening region 1124.

[0102] Alternative embodiment – ​​Pivot plate diameter and check plate diameter See now Figure 9A and 9BAn alternative embodiment of the relief valve assembly (e.g., compression relief valve assembly 1162 or springback relief valve assembly 1164) includes a flow-limiting disc 102, an orifice disc 104, a fulcrum disc 1106, and a check disc 1108. The fulcrum disc 1106 and check disc 1108 directly replace the fulcrum disc 106 and check disc 108, respectively. Although illustrated in conjunction with the piston body 60 described herein, compression relief valve assembly 1162 and / or springback relief valve assembly 1164 can also be used with other types of piston bodies without departing from the scope of the invention. Therefore, the piston body 60 is not necessarily required to be used with compression relief valve assembly 1162 and / or springback relief valve assembly 1164, and vice versa.

[0103] The pivot plate 1106 includes a ring 128 having a central bore 134. The ring 128 of the pivot plate 1106 has an inner diameter 2000 (defined by the central bore 130), an outer diameter 2002, and a ring width 2004 defined by the difference between the outer diameter 2002 and the inner diameter 2000. Furthermore, the check plate 1108 includes a ring 132 having a central bore 134. The ring 132 of the check plate 1108 has an inner diameter 2006 (defined by the central bore 134), an outer diameter 2008, and a ring width 2010 defined by the difference between the outer diameter 2008 and the inner diameter 2006. Figure 9A As shown, the outer diameters 2002 and 2008 of the fulcrum plate 1106 and check plate 1108 are smaller than 1 / 2002 and 1 / 2008, respectively. Figure 9B The corresponding outer diameters of the components are 2002 and 2008. Furthermore, Figure 9A The widths 2004 and 2010 of the rings of the fulcrum disk 1106 and check disk 1108 shown are less than [the widths of the rings]. Figure 9B The widths of the rings of the fulcrum disk 1106 and the check disk 1108 shown are 2004 and 2010, respectively.

[0104] Normally, adjusting the relief valve assembly only requires changing the thickness of the pivot plate and check plate. However, the design of the pivot plate 1106 and check plate significantly improves the adjustability of the relief valve assembly (e.g., compression relief valve assembly 1162 or springback relief valve assembly 1164). The outer diameter 2002 of the pivot plate 1106 and the outer diameter 2008 of the check plate 1108 can be selected according to the desired damping response of the damper 20. Changing the outer diameter 2002 of the pivot plate 1106 and the outer diameter 2008 of the check plate 1108 will affect the closing torque of the check plate 1108 (e.g., ...). Figure 10 and Figure 11(The parameters in segment G of the force response curve of the damper 20 shown). For example, increasing the outer diameter 2002 of the pivot plate 1106 and the outer diameter 2008 of the check plate 1108 will effectively shorten the length of the finger portion 136 of the check plate 1108. This will reduce the lever arm of the finger portion 136, thereby increasing the force required to deflect the check plate 1108 as desired. As the outer diameter 2002 of the pivot plate 1106 and the outer diameter 2008 of the check plate 1108 increase, the stiffness of the check plate 1108 will increase accordingly.

[0105] Changing the outer diameter 2002 of the fulcrum plate 1106 and the outer diameter 2008 of the check plate 1108 will also affect the curve from the open discharge state to the normal discharge state (i.e. Figure 10 and Figure 11 The parameters of segment F in the force response curve of the damper 20 shown.

[0106] In some embodiments, the outer diameter 2002 of the fulcrum disk 1106 is the same as the outer diameter 2008 of the check disk 1108. In some embodiments, the outer diameter 2002 of the fulcrum disk 1106 is different from the outer diameter 2008 of the check disk 1108. In some embodiments, the outer diameter 2002 of the fulcrum disk 1106 can be adjusted independently of the outer diameter 2008 of the check disk 1108.

[0107] In some embodiments, the damper 20 is provided as a kit having a plurality of pivot discs 1106 and a plurality of check discs 1108. The pivot discs 1106 in the kit may have different outer diameters 2002. In some embodiments, the pivot discs 1106 in the kit may have different outer diameters 2002 and different thicknesses. Furthermore, the check discs 1108 in the kit may have different outer diameters 2008. In some embodiments, the check discs 1108 in the kit may have different outer diameters 2008 and different thicknesses. Therefore, one pivot disc 1106 and one check disc 1108 from the kit can be selected and incorporated into the damper 20 according to the desired damping response.

[0108] Now refer to Figure 10 and Figure 11 , Figure 10 and Figure 11This is a force-velocity relationship (force response curve) diagram when the damper moves towards the compression position. The vertical axis (y-axis) represents the force provided by the damper 20, and the horizontal axis (x-axis) represents the velocity of the piston rod 34. As previously mentioned: changing the radial opening region 1122 will change the parameters of segment A; changing the axial opening region 1124 and the thickness of the pivot plate 106 will change the parameters of segment F; changing the thickness of the pivot plate 106 and the check plate 108 will change the parameters of segment G. Furthermore, increasing the flow restriction percentage provided by the upper flow finger 1116 of the flow-limiting plate 1102 will change the parameters of segment E. Additionally, changing the thickness of the valve limiter 154 will change the parameters of segment C. Changing one or more of the outer diameter 2002 of the pivot plate 1106, the thickness of the pivot plate 1106, the outer diameter 2008 of the check plate 1108, and the thickness of the check plate 1108 can change the parameters of segments C, D, F, and G.

[0109] The above description of the embodiments is for illustrative purposes only and is not intended to exhaustively explain or limit the invention. Various elements or features in a particular embodiment are generally not limited to that embodiment and are interchangeable where applicable. Even if not explicitly shown or described, these elements or features are interchangeable and can be used in selected other embodiments. Furthermore, the above embodiments can be modified in various ways, and such modifications should not be considered a departure from the spirit of the invention; all modifications should be included within the scope of protection of the invention.

Claims

1. A method for controlling the flow of hydraulic fluid between an upper working chamber and a lower working chamber of a pressure tube by means of a piston disposed within the pressure tube, the piston having one or more fluid passages, the method comprising: A pivot disk is disposed near the piston, the pivot disk including a first ring having a first central hole, a first inner diameter and a first outer diameter; A check disc is disposed near the fulcrum disk and opposite the piston. The check disc includes a second ring having a second central hole, a second inner diameter, and a second outer diameter, and one or more extensions extending radially from the second ring. The first outer diameter and the second outer diameter are selected based on the desired damping response.

2. The method according to claim 1, wherein, The desired damping response is the expected transition from the open discharge state to the normal discharge state.

3. The method according to claim 1, wherein, The first outer diameter is equal to the second outer diameter.

4. The method according to claim 1, wherein, The first outer diameter is smaller than the second outer diameter.

5. The method according to claim 1, wherein, The fulcrum plate has a first thickness, the check plate has a second thickness, and the method further includes selecting the first thickness and the second thickness according to the desired damping response.

6. A shock absorber for a vehicle, comprising: Pressure tubes that define fluid chambers; A piston disposed within the fluid chamber, the piston dividing the fluid chamber into an upper working chamber and a lower working chamber, wherein the piston includes a first side, a second side, and a fluid passage extending through the piston between the upper working chamber and the lower working chamber; as well as Valve assembly, comprising: A flow-limiting disc near the first side of the piston, the flow-limiting disc comprising: The first ring; and A first finger-shaped portion extending radially outward from a first ring is configured to cover the fluid channel and has a first drain orifice, wherein the first drain orifice remains open at any position of the flow restrictor. Orifice plate, wherein the flow-limiting plate is located between the orifice plate and a first side of the piston, the orifice plate comprising: The second ring; and A second finger-shaped portion extending radially outward from the second ring, the second finger-shaped portion having a second drain orifice, wherein the second drain orifice remains open at any position on the orifice plate; wherein the second finger-shaped portion of the orifice plate overlaps with the first finger-shaped portion of the flow-limiting plate, and wherein the second drain orifice is aligned with the first drain orifice; Stop-loss orders, which include: The third ring; and A third finger-shaped portion extending radially outward from the third ring, the third finger-shaped portion of the check disc being located above the second finger-shaped portion of the orifice disc; and A fulcrum plate, wherein the fulcrum plate is located between the orifice plate and the check plate, and the fulcrum plate includes a fourth ring.

7. The vibration damper according to claim 6, wherein, The third ring of the check plate has an outer diameter, and the fourth ring of the fulcrum plate has an outer diameter.

8. The vibration damper according to claim 7, wherein, Changing the outer diameter of the third ring of the check plate and the outer diameter of the fourth ring of the fulcrum plate can change the damping response of the shock absorber.

9. The vibration damper according to claim 7, wherein, The damping response of the shock absorber depends on the outer diameter of the third ring of the check plate and the outer diameter of the fourth ring of the pivot plate.

10. The vibration damper according to claim 7, wherein, The outer diameter of the third ring of the check plate is equal to the outer diameter of the fourth ring of the fulcrum plate.

11. The vibration damper according to claim 7, wherein, The outer diameter of the third ring of the check disc is different from the outer diameter of the fourth ring of the fulcrum disc.

12. The vibration damper according to claim 7, wherein, The check disc is configured to be selectively in a first position and a second position, and wherein changing the outer diameter of the third ring of the check disc and the outer diameter of the fourth ring of the fulcrum disc can change the force required to move the check disc from the first position to the second position.

13. The vibration damper according to claim 12, wherein, When the check disc is in the first position, the third finger of the check disc is located above and spaced apart from the second finger of the orifice disc; and when the check disc is in the second position, the third finger of the check disc is in contact with the second finger of the orifice disc.

14. The vibration damper according to claim 6, wherein, The fulcrum plate has a first thickness, the check plate has a second thickness, and the damping response of the damper can be adjusted by changing the first thickness and the second thickness.

15. The vibration damper according to claim 6, wherein, The fulcrum disc has a first thickness, the check disc has a second thickness, wherein the check disc is configured to be selectively in a first position and a second position, and wherein changing the first thickness and the second thickness changes the force required to move the check disc from the first position to the second position.

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