Damper assembly and piston for the same

Abstract

The present disclosure provides a damper assembly and a piston therefor. The damper assembly includes a damper tube extending along a central axis and defining a fluid chamber. The piston is attached to the damper rod and divides the fluid chamber into a compression chamber and a rebound chamber. The piston includes a piston body and a frequency-dependent (FD) valve. The piston body defines an intermediate chamber in fluid communication with the rebound chamber. The FD valve includes: an FD housing having a tubular shape surrounding an FD chamber; an FD slider disposed within the FD housing and dividing the FD chamber into an FD pressure chamber and an FD displacement chamber, the FD control stack being configured to regulate fluid flow between the intermediate chamber and the FD pressure chamber, and the FD working disk being configured to deflect together with the FD housing to regulate fluid flow between the rebound chamber and the compression chamber.

Description

Technical Field

[0001] The present invention generally relates to a damper assembly for a vehicle. Background Art

[0002] Damper assemblies are well known in the art for use in vehicles. One such damper assembly is disclosed in patent publication US5706920A, which discloses a monotube damper assembly including a main tube disposed on a central axis and extending between a first end and a second end. The damper defines a fluid chamber between the first end and the second end for receiving a working fluid. A main piston is slidably disposed in the fluid chamber, dividing the fluid chamber into a rebound chamber and a compression chamber. A piston rod is disposed on the central axis, extends along the central axis to a distal end, and is attached to the main piston for moving the main piston between a compression stroke and a rebound stroke.

[0003] Conventional passive shock absorber valves provide a poor compromise between performance, safety, and ride comfort. To improve this situation, active suspensions and semi-active suspensions are commonly proposed. However, they require the use of additional sensors, ECUs, and control algorithms, which makes them complex and very expensive. For this reason, adaptive passive valves are becoming increasingly popular and are favored by automobile manufacturers.

[0004] Various adaptive valve technologies provide damping characteristics that depend not only on the damper velocity but also on the excitation frequency. Such a solution allows for achieving a high damping force at low frequencies associated with body movement and a low damping force at high frequencies associated with wheel vibrations.

[0005] It is known in the art that damper assemblies include frequency-dependent valve assemblies to enable the damper assembly to have the ability to reduce the damping force level of high-frequency events, thereby providing better comfort and road support for the occupants. However, the known valve assemblies are generally expensive, complex, and have limited tuning ability. In addition, most existing frequency-dependent valves are configured as add-ons to existing damper designs. These additional valves may significantly increase the dead zone length of the damper. Moreover, they typically require drilling additional intersecting bypass holes, which is an expensive process that generates contaminants and may weaken parts of the damper, such as valve spigots. Therefore, an improved damper assembly is needed. Summary of the Invention

[0006] The present invention provides a damper assembly. The damper assembly includes a damper tube having a tubular shape extending along a central axis and defining a fluid chamber. The damper assembly further includes a piston attached to a damper rod and movable along the central axis through the damper tube and dividing the fluid chamber into a compression chamber and a rebound chamber, the piston including a piston body and a frequency-dependent (FD) valve. The piston body defines an intermediate chamber in fluid communication with the rebound chamber. The FD valve includes: an FD housing having a tubular shape surrounding an FD chamber; an FD slider disposed within the FD housing and dividing the FD chamber into an FD pressure chamber and an FD displacement chamber; an FD control stack configured to regulate fluid flow between the intermediate chamber and the FD pressure chamber; and an FD working disk configured to deflect with the FD housing to regulate fluid flow between the rebound chamber and the compression chamber.

[0007] The present invention also provides a piston for a damper assembly. The piston includes a piston body defining an intermediate chamber. The piston further includes a frequency-dependent (FD) valve. The FD valve includes: an FD housing having a tubular shape surrounding an FD chamber; an FD slider disposed within the FD housing and dividing the FD chamber into an FD pressure chamber and an FD displacement chamber; an FD control stack configured to regulate fluid flow between the intermediate chamber and the FD pressure chamber; and an FD working disk configured to deflect with the FD housing to regulate fluid flow between the rebound chamber and the compression chamber. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Other advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in conjunction with the accompanying drawings, wherein:

[0009] Figure 1 A cross-sectional perspective view of the damper assembly is shown;

[0010] Figure 2 An enlarged cross-sectional perspective view of the piston of the damper assembly including the frequency-dependent valve is shown;

[0011] Figure 3 An exploded view of the piston of the damper assembly including the frequency-dependent valve is shown;

[0012] Figure 4A A partial cross-sectional view of the piston of the damper assembly is shown, illustrating the response of the frequency-dependent working disk to high-frequency excitation;

[0013] Figure 4B A partial cross-sectional view of the piston of the damper assembly is shown, illustrating the response of the frequency-dependent working disk to low-frequency excitation;

[0014] Figure 5 Shows a partial cross-sectional view of the FD valve housing of the piston of the damper assembly of the present disclosure; and

[0015] Figure 6 Shows a cross-sectional view of the FD slider of the piston of the damper assembly of the present disclosure. DETAILED DESCRIPTION

[0016] Referring to the accompanying drawings, in which like reference numerals represent corresponding components in several views, one aspect of the present invention is to provide a damper assembly 20 that can be used as part of a suspension in a vehicle (such as a passenger car or a truck). The damper assembly 20 of the present disclosure is shown as a monotube damper. However, the principles of the present disclosure can be used with other types of dampers, such as in a twin-tube damper.

[0017] The damper assembly 20 of the present disclosure provides a unique solution for implementing a frequency adaptive section within the piston valve assembly.

[0018] As Figure 1 generally shown in, the damper assembly 20 includes a damper tube 22 having a tubular shape extending between a first end 24 and a second end 26 along a central axis A, and the damper tube 22 defines main compartments 30, 32, 34 therein. The damper assembly 20 further includes an air cup 28 disposed in the main compartments 30, 32, 34, sealingly engaged with the damper tube 22 and slidable along the central axis A to divide the main compartments 30, 32, 34 into a fluid compartment 32, 34 and a gas compartment 30 for containing gas. The gas compartment 30 extends between the first end 24 and the air cup 28, and the fluid compartments 32, 34 extend between the air cup 28 and the second end 26.

[0019] The damper assembly 20 further includes a damper rod 36 extending along the central axis A. The damper rod 36 includes a rod end 38 located inside the fluid compartments 32, 34. A piston 40 is attached to the damper rod 36 adjacent to the rod end 38 and is configured to move along the central axis A through the damper tube 22 together with the damper rod 36. The piston 40 divides the fluid compartments 32, 34 into a compression chamber 32 and a rebound chamber 34. The compression chamber 32 extends between the piston 40 and the air cup 28, and the rebound chamber 34 extends between the second end 26 and the piston 40.

[0020] The first closure 42 seals the gas chamber 30 at the first end 24 of the damper tube 22. The damper mount 44 is attached to the first closure 42 and is configured to attach the damper assembly 20 to the vehicle body (not shown). The damper assembly 20 of the present disclosure can be used in other configurations and / or orientations. For example, the damper mount 44 can connect the damper tube 22 of the damper assembly 20 to a chassis component of the vehicle 10.

[0021] The damper assembly 20 further includes a second closure 46 disposed adjacent the second end 26 of the damper tube 22 to enclose the rebound chamber 34. The second closure 46 defines a hole 48 for the damper rod 36 to pass through. The second closure 46 can provide a fluid-tight seal with the damper rod 36 to prevent fluid from leaking out of the rebound chamber 34.

[0022] Figure 2 An enlarged cross-sectional perspective view of the piston 40 of the damper assembly 20 including the frequency-dependent valve 90 is shown. As Figure 2 shown, the damper rod 36 includes a rod body 50 having a cylindrical shape, a first rod shoulder 52 facing the rod end 38. The damper rod 36 further includes a first rod extension 53 that extends from the first rod shoulder 52 toward the rod end 38 and has a generally cylindrical shape with a diameter smaller than that of the rod body 50. The first rod extension 53 defines a second rod shoulder 54 facing the rod end 38. The damper rod 36 further includes a second rod extension 55 that extends from the second rod shoulder 54 toward the rod end 38 and has a generally cylindrical shape with a diameter smaller than that of the first rod extension 53. The second rod extension 55 defines a third rod shoulder 56 facing the rod end 38. The damper rod 36 further includes a third rod extension 57 that extends from the third rod shoulder 56 to the rod end 38 and has a generally cylindrical shape with a diameter smaller than that of the second rod extension 55.

[0023] Also as Figure 2 shown, the piston 40 includes a piston body 60 disposed around the first rod extension 53. The piston body 60 includes an annular seal 62 made of an elastic material, and the annular seal 62 is configured to abut against the inner surface of the damper tube 22 ( Figure 2Sealed (not shown in the figure). The piston body 60 defines a compression passage 64 that is in fluid communication with the compression chamber 32 and provides a path for fluid flow to the rebound chamber 34. The piston body 60 defines a first rebound passage 66 that is in fluid communication with the rebound chamber 34 and extends axially and radially inwardly away from the rebound chamber 34. The piston body 60 further defines an intermediate chamber 67 having an annular shape that is in fluid communication with the rebound chamber 34 via the first rebound passage 66. The piston body 60 also defines a second rebound passage 68 that is in fluid communication with the intermediate chamber 67 and extends axially from the intermediate chamber 67 and toward the first rod shoulder 52. The first rebound passage 66, the intermediate chamber 67, and the second rebound passage 68 together provide a path for fluid flow to the compression chamber 32 during the rebound stroke.

[0024] The piston 40 further includes compression valve assemblies 70, 72, 73, 74 that are configured to regulate fluid flow from the compression chamber 32 to the rebound chamber 34 during the compression stroke, wherein the damper rod 36 pushes the piston 40 toward the first end 24 of the damper tube 22. The compression valve assemblies 70, 72, 73, 74 include a compression disk holder 70 having an annular shape, disposed around the first rod extension 53, and contacting the first rod shoulder 52. The compression valve assemblies 70, 72, 73, 74 further include a first spacer ring 72 having an annular shape, disposed around the first rod extension 53 adjacent to the compression disk holder 70 and opposite the first rod shoulder 52. The compression valve assemblies 70, 72, 73, 74 further include a compression disk stack 73, 74 that covers the end of the compression passage 64 opposite the compression chamber 32. The compression disk stack 73, 74 includes a plurality of first compression disks 73 and a plurality of second compression disks 74 that are wider than the first compression disks 73. However, the compression disk stack 73, 74 may include a different number of first compression disks 73 and / or second compression disks 74. Alternatively, the compression disk stack 73, 74 may include only disks having uniform dimensions. For example, the compression disk stack 73, 74 may include only first compression disks 73 and / or only second compression disks 74. The first spacer ring 72 has a smaller diameter than the compression disk stack 73, 74 and supports an inner portion of the compression disk stack 73, 74, leaving an outer portion of the compression disk stack 73, 74 unsupported and capable of deflecting away from the compression passage 64 in response to a pressure differential across the compression passage 64, and thereby regulating fluid flow through the compression passage 64 and into the rebound chamber 34.

[0025] The piston 40 further includes a rebound valve assembly 76, 78, 80 configured to regulate fluid flow from the rebound chamber 34 to the compression chamber 32 during a rebound stroke, wherein the damper rod 36 pulls the piston 40 toward the second end 26. The rebound valve assembly 76, 78, 80 includes a second spacer ring 76 having an annular shape, adjacent to the compression disc stack 73, 74 and disposed around the first rod extension 53 opposite to the first spacer ring 72. The rebound valve assembly 76, 78, 80 further includes a rebound disc stack 78 including a plurality of discs covering an end of the second rebound passage 68 opposite to the frequency-dependent valve 90. The second spacer ring 76 has a smaller diameter than the rebound disc stack 78 and supports an inner portion of the rebound disc stack 78, leaving an outer portion of the rebound disc stack 78 unsupported and capable of deflecting away from the second rebound passage 68 in response to a pressure difference across the second rebound passage 68, and thereby regulating fluid flow through the second rebound passage 68 and into the compression chamber 32.

[0026] The rebound valve assembly 76, 78, 80 further includes a rebound bypass disc 80 disposed between the second rebound passage 68 and the rebound disc stack 78. The rebound bypass disc 80 has a disc shape with a plurality of notches in its peripheral edge to provide limited fluid communication between the second rebound passage 68 and the compression passage 64, which can equalize the pressure between the second rebound passage 68 and the compression passage 64 and when the rebound disc stack 78 does not deflect away from the second rebound passage 68.

[0027] Figure 2 Details of the frequency-dependent (FD) valve 90 are also shown, which includes an FD slider 102 having an annular shape disposed around an FD guide 104. The FD guide 104 has a tubular shape disposed around the second rod extension 55 and extending from the second rod shoulder 54 to the third rod shoulder 56. The FD guide 104 can provide a fluid-tight seal with the FD slider 102.

[0028] Still referring to Figure 2, the FD valve 90 further includes an FD housing 110 having a generally tubular shape that is disposed annularly around the FD slider 102. The FD housing 110 is partially disposed within the piston body 60 and projects axially from the piston body 60 toward the rod end 38. A spring retainer 112 is disposed annularly within the FD housing 110 around the third rod extension 57 and adjacent to the third rod shoulder 56. The spring retainer 112 contacts the helical spring 106, where the helical spring 106 extends from the spring retainer 112 to the FD slider 102. The FD housing 110 defines FD chambers 116, 118, where the FD slider 102 divides the FD chambers 116, 118 into an FD pressure chamber 116 and an FD displacement chamber 118.

[0029] The FD valve 90 further includes FD control stacks 92, 94, 98, 100 disposed between the intermediate chamber 67 and the FD slider 102 and around the second rod extension 55. The FD control stacks 92, 94, 98, 100 are best shown in Figure 3 an exploded view and include a slotted disk 92, an FD control disk 94, and an FD deflecting disk 98. The slotted disk 92 supports the FD control disk 94 and defines a plurality of apertures 93 that permit fluid to flow through a control orifice 96 into the FD pressure chamber 116.

[0030] The helical spring 106 contacts the FD slider 102 and biases the FD slider 102 toward the FD control stacks 92, 94, 98, 100.

[0031] An FD working disk stack 120 including one or more FD working disks covers the spring retainer 112 and contacts the edge 119 of the FD housing 110. The FD working disk stack 120 is configured to deflect with the FD housing 110 to regulate fluid flow between the rebound chamber 34 and the compression chamber 32 by applying an additional force to the FD housing 110. The FD working disk stack 120 includes an FD bypass disk 114 that has a plurality of notches in the peripheral edge of the FD bypass disk 114 to permit fluid from within the FD displacement chamber 118 to flow into the compression chamber 32. The FD valve 90 further includes a fourth spacer ring 122 having an annular shape that is disposed around the third rod extension 57 and adjacent to the FD working disk stack 120 and opposite the spring retainer 112. The fourth spacer ring 122 has a smaller diameter than the FD working disk stack 120 and supports an inner portion of the FD working disk stack 120, leaving an outer portion of the FD working disk stack 120 unsupported and able to deflect with the FD housing 110 in response to a pressure differential across it and thereby regulate fluid flow out of the FD displacement chamber 118 and into the compression chamber 32.

[0032] The FD valve 90 further includes an FD disk retainer 124, which has a disk shape, is disposed around the third rod extension 57, and covers the fourth spacer ring 122 opposite to the FD working disk stack 120. A fastener 126 is disposed around the third rod extension 57 and contacts the FD disk retainer 124 to secure the FD valve 90 to the damper rod 36. The fastener 126 may include a nut that threadedly engages the third rod extension 57, although other types of fasteners may also be used.

[0033] As Figure 2 shown, the FD valve 90 is located in the rebound flow path of the piston 40 and thus functions during the rebound stroke. Two main valves, including the compression valve assemblies 70, 72, 74 and the rebound valve assemblies 76, 78, 80, are located on the rod side of the piston 40 opposite to the rod end 38. The FD valve 90 functions as an auxiliary valve that works in parallel with the rebound valve assemblies 76, 78, 80 to release pressure according to the excitation frequency or more precisely according to the pressure rate in the FD pressure chamber 116.

[0034] Figure 3 An exploded view of the piston 40 of the damper assembly 20 including the FD valve 90 is shown. As Figure 3 shown, the compression disk stack 73, 74 includes five disks having two different sizes. However, the compression disk stack 73, 74 may have a different number of disks and / or a different configuration, where all disks have a consistent size and / or two or more different sizes. Also as Figure 3 shown, the rebound disk stack 78 includes three disks all having a uniform size. However, the rebound disk stack 78 may have a different number of disks and / or a different configuration of disks having two or more different sizes. Also as Figure 3 shown, the FD control stack 92, 94, 98, 100 includes a single FD deflector disk 98. However, the FD control stack 92, 94, 98 may include a stack having two or more FD deflector disks in the FD deflector disk 98, and these FD deflector disks may have characteristics adjusted according to a specific application, such as width, thickness, and material.

[0035] Also as Figure 3 shown, the FD control disk 94 defines a control orifice 96 in its peripheral edge. The function of the FD control disk 94 is described in more detail below with reference to Figures 4A to 4B More specifically. Also as Figure 3 shown, the FD working disk stack 120 includes three disks all having a uniform size. However, the FD working disk stack 120 may include a different number of disks, and the disks of the FD working disk stack 120 may have different configurations having two or more different shapes and / or sizes.

[0036] As Figure 3As shown, the FD valve 90 further includes an FD bypass disk 114 disposed between the spring retainer 112 and the FD working disk stack 120. The FD bypass disk 114 has a disk shape with a plurality of notches in its peripheral edge to provide fluid communication between the FD displacement chamber 118 and the compression chamber 32, and thus enable the FD slider 102 to move freely towards the rod end 38.

[0037] Figures 4A to 4B Each shows a partial cross-sectional view of the piston 40, illustrating the response of the FD valve 90 to different excitations. Specifically, Figure 4A shows the state of the piston 40 when the damper assembly 20 is under high-frequency excitation conditions, and Figure 4B shows the state of the piston 40 when the damper assembly 20 is under low-frequency excitation conditions. Figures 4A to 4B Some additional structural details of the piston 40 are also shown. As Figures 4A to 4B shown, a first O-ring seal 103 is disposed in a corresponding annular hole 178 in the outer surface of the FD slider 102 to provide a fluid-tight seal between the FD slider 102 and the inner surface of the FD housing 110. A second O-ring seal 105 is disposed in a corresponding annular hole in the outer surface of the FD guide 104 for sealing against the radially inner surface of the FD slider 102. The first O-ring seal 103 and the second O-ring seal 105 together are used to prevent fluid migration between the FD pressure chamber 116 and the FD displacement chamber 118 when the FD slider 102 translates within the FD housing 110.

[0038] As Figures 4A to 4B best shown, the first axial end 150 of the FD housing 110 contacts the upper surface of the slotted disk 92 adjacent its peripheral edge. The piston body 60 defines an annular ridge 132 that supports the lower surface of the slotted disk 92 to regulate the fluid flow from the first rebound channel 66 flowing out via the FD channel 134 to the compression chamber 32, and the FD channel 134 extends annularly between the FD housing 110 and the piston body 60.

[0039] During the rebound stroke, fluid flows from the rebound chamber 34 through the first rebound channel 66 and the intermediate chamber 67, passes through the control orifice 96 in the FD control disk 94 and enters the FD pressure chamber 116, causing the FD slider 102 to move axially towards the rod end 38. In other words, the control orifice 96 in the FD control disk 94 provides fluid communication between the intermediate chamber 67 and the FD pressure chamber 116, as Figures 4A to 4B indicated by the small flow arrows above.

[0040] When there is sufficient pressure in the FD pressure chamber 116, the FD slider 102 moves axially towards the rod end 38 (i.e., away from the FD control stack 92, 94, 98, 100), thereby increasing the volume of the FD pressure chamber 116. The FD bypass disk 114 located near the FD working disk stack 120 allows oil to freely flow into and out of the FD shift chamber 118, where the helical spring 106 is located, and thus enables the FD slider 102 to move freely.

[0041] The operation of the FD valve 90 is regulated by the flow area of the control orifice 96 in the FD control disk 94, the spring rate and preload of the helical spring 106, and the number and thickness of the disks in the FD working disk stack 120. The FD working disk stack 120 is responsible for generating the main damping force of the FD valve 90, while the FD control stack 92, 94, 98, 100 is responsible for FD valve enhancement at low frequencies. The FD working disk stack 120 also holds the FD housing 110 in place and biases the FD housing 110 axially towards the slotted disk 92 when the FD valve 90 is closed.

[0042] Figure 5 A partial cross-sectional view of the FD housing 110 is shown. As shown, the FD housing 110 includes a generally tubular shape extending between a first axial end 150 and a second axial end 152. As Figure 4B best shown, the first axial end 150 may contact the slotted disk 92. Returning to Figure 5 , the first axial end 150 defines an annular notch 154 in the outer surface to facilitate the flow of fluid via the FD passage 134 to the compression chamber 32. The FD housing 110 includes a first tubular portion 156 that axially extends from the first axial end 150 to a catch surface 158 having an annular shape and facing the first axial end 150. The FD housing 110 also includes a second tubular portion 160 that extends from the catch surface 158 to the second axial end 152. The first tubular portion 156 and the second tubular portion 160 have the same outer diameter, providing a smooth outer surface for the FD housing 110. However, the inner diameter of the second tubular portion 160 is less than that of the first tubular portion. The FD housing 110 also includes an end support 162 that radially extends inwardly from the second tubular portion 160 adjacent the first axial end 150 and supports an annular ridge 164 that axially extends beyond the first axial end 150 to define an edge 119 of the FD housing 110.

[0043] The FD slider 102 can engage the capture surface 158 to define the maximum axial travel limit of the FD slider 102, which can limit the maximum pressure level in the FD pressure chamber 116. When the FD slider 102 contacts the capture surface 158, the FD slider 102 can push the FD housing 110 away from the off-slot disk 92, thereby providing enhanced flow through the FD valve 90, as Figure 4B illustrated.

[0044] Figure 6 A cross-sectional view of the FD slider 102 is shown. The FD slider 102 includes a disk-shaped base 170 and an inner tubular portion 172 that is coupled to and axially extends from the disk-shaped base 170. The inner tubular portion 172 defines a slider bore 173 that is configured to surround and axially slide along the second rod extension 55. The FD slider 102 further includes an outer tubular portion 174 that is coupled to the disk-shaped base 170 adjacent its peripheral edge and axially extends from the disk-shaped base 170. The outer tubular portion 174 is disposed annularly around the inner tubular portion 172 and defines a spring pocket 176 therebetween for receiving an end of the helical spring 106. The outer tubular portion 174 also defines an annular bore 178 for receiving the first O-ring seal 103.

[0045] In some embodiments, the FD valve 90 can operate as an open system, where the inputs and outputs (i.e., the channels providing fluid flow into and out of the FD pressure chamber 116) are isolated. For example, and as Figure 6 shown, the FD slider 102 can define a hole 180 extending therethrough. In this case, the pressure ratio in the FD pressure chamber 116 depends on the ratio of the flow areas through the inlet and outlet channels (i.e., fluid flows into the FD pressure chamber 116 through the control orifice 96 in the FD control disk 94 and out through the hole 180 in the FD slider 102). Alternatively, the FD valve 90 can operate as a closed system, where the inputs and outputs are connected together. For example, a single channel (such as the control orifice 96 in the FD control disk 94) can be used as both the inlet and outlet for fluid to enter and leave the FD pressure chamber 116, and there can be no other channels for fluid to flow into or out of the FD pressure chamber 116.

[0046] Obviously, many modifications and variations of the present disclosure are possible in light of the above teachings, and these modifications and variations can be implemented in a manner different from the specific description while remaining within the scope of the appended claims. These foregoing statements should be construed to cover any combination of the novelty and practicality of the present invention.

Claims

1. A damper assembly, the damper assembly comprising: A damper tube having a tubular shape extending along a central axis and defining a fluid compartment; A piston attached to a damper rod and movable along the central axis through the damper tube and dividing the fluid compartment into a compression chamber and a rebound chamber, the piston including a piston body and a frequency-dependent valve; The piston body defining an intermediate chamber in fluid communication with the rebound chamber; And The frequency-dependent valve includes: a frequency-dependent housing, a frequency-dependent slider, a frequency-dependent control stack, and a frequency-dependent working disk. The frequency-dependent housing has a tubular shape surrounding a frequency-dependent chamber. The frequency-dependent slider is disposed within the frequency-dependent housing and divides the frequency-dependent chamber into a frequency-dependent pressure chamber and a frequency-dependent displacement chamber. The frequency-dependent control stack is configured to regulate fluid flow between the intermediate chamber and the frequency-dependent pressure chamber. The frequency-dependent working disk is configured to deflect with the frequency-dependent housing to regulate fluid flow between the rebound chamber and the compression chamber, Wherein the frequency-dependent slider defines a hole therethrough such that the frequency-dependent valve operates as an open system; or the frequency-dependent slider has a solid configuration such that the frequency-dependent valve operates as a closed system having a single passage serving as both an inlet and an outlet for fluid to enter and leave the frequency-dependent pressure chamber.

2. The damper assembly according to claim 1, wherein, The frequency-dependent control stack includes a frequency-dependent control disk defining a control orifice providing fluid communication between the intermediate chamber and the frequency-dependent pressure chamber.

3. The damper assembly according to claim 1, wherein, The frequency-dependent control stack includes a frequency-dependent deflecting disk and a slotted disk. The slotted disk supports the frequency-dependent deflecting disk and defines holes allowing fluid pressure in the intermediate chamber to act on the frequency-dependent deflecting disk to deflect the frequency-dependent deflecting disk away from the slotted disk and thus allowing fluid to flow around the frequency-dependent deflecting disk and into the frequency-dependent pressure chamber.

4. The damper assembly according to claim 1, wherein, The frequency-dependent housing defines a capture surface configured to engage the frequency-dependent slider and defining a maximum axial travel limit of the frequency-dependent slider relative to the frequency-dependent housing.

5. The damper assembly according to claim 4, wherein, The frequency-dependent control stack includes a frequency-dependent deflecting disk and a slotted disk supporting the frequency-dependent deflecting disk, Wherein the frequency-dependent housing includes a first axial end contacting an upper surface of the slotted disk adjacent to a peripheral edge of the slotted disk, and Wherein the frequency-dependent slider is configured to bias the frequency-dependent housing away from the slotted disk at the maximum axial travel limit and thereby increase the flow rate through the frequency-dependent valve.

6. The damper assembly according to claim 1, wherein, The piston further includes a compression valve assembly and a rebound valve assembly, each disposed on an end of the piston body adjacent to the rebound chamber.

7. The damper assembly according to claim 1, wherein The piston further includes a compression valve assembly and a rebound valve assembly, and Wherein, the frequency-dependent valve is disposed at an end of the piston body opposite to each of the rebound valve assembly and the compression valve assembly.

8. The damper assembly according to claim 1, wherein, The frequency-dependent valve further includes a frequency-dependent guide having a tubular shape disposed around the damper rod and providing a fluid-tight seal with the frequency-dependent slider.

9. The damper assembly according to claim 1, wherein, The frequency-dependent valve further includes a spring configured to bias the frequency-dependent slider toward the frequency-dependent control stack.

10. The damper assembly according to claim 9, wherein, The frequency-dependent valve further includes a spring retainer extending annularly around the damper rod, and the spring includes a helical spring extending around the damper rod and between the spring retainer and the frequency-dependent slider.

11. A damper assembly, the damper assembly comprising: A damper tube having a tubular shape extending along a central axis and defining a fluid chamber; A piston attached to a damper rod and movable along the central axis through the damper tube and dividing the fluid chamber into a compression chamber and a rebound chamber, the piston including a piston body and a frequency-dependent valve; The piston body defines an intermediate chamber in fluid communication with the rebound chamber; And The frequency-dependent valve includes: a frequency-dependent housing, a frequency-dependent slider, a frequency-dependent control stack, and a frequency-dependent working disk. The frequency-dependent housing has a tubular shape around a frequency-dependent chamber. The frequency-dependent slider is disposed within the frequency-dependent housing and divides the frequency-dependent chamber into a frequency-dependent pressure chamber and a frequency-dependent displacement chamber. The frequency-dependent control stack is configured to regulate fluid flow between the intermediate chamber and the frequency-dependent pressure chamber. The frequency-dependent working disk is configured to deflect together with the frequency-dependent housing to regulate fluid flow between the rebound chamber and the compression chamber. Wherein, the frequency-dependent housing defines a capture surface configured to engage the frequency-dependent slider and defining a maximum axial travel limit of the frequency-dependent slider relative to the frequency-dependent housing. Wherein, the frequency-dependent control stack includes a frequency-dependent deflecting disk and a slotted disk supporting the frequency-dependent deflecting disk. Wherein, the frequency-dependent housing includes a first axial end that contacts an upper surface of the slotted disk adjacent to an outer peripheral edge of the slotted disk, and Wherein, the frequency-dependent slider is configured to bias the frequency-dependent housing away from the slotted disk at the maximum axial travel limit and thereby increase the flow rate through the frequency-dependent valve.

12. A piston for a damper assembly, the piston comprising: A piston body defining an intermediate chamber; And Frequency-dependent valve, said frequency-dependent valve comprising: a frequency-dependent housing, a frequency-dependent slider, a frequency-dependent control stack, and a frequency-dependent working disk, said frequency-dependent housing having a tubular shape surrounding a frequency-dependent chamber, said frequency-dependent slider being disposed within said frequency-dependent housing and dividing said frequency-dependent chamber into a frequency-dependent pressure chamber and a frequency-dependent displacement chamber, said frequency-dependent control stack being configured to regulate fluid flow between said intermediate chamber and said frequency-dependent pressure chamber, said frequency-dependent working disk being configured to deflect together with said frequency-dependent housing to regulate fluid flow between a rebound chamber and a compression chamber, wherein, said frequency-dependent slider defines a hole therethrough such that said frequency-dependent valve operates as an open system; or wherein, said frequency-dependent slider has a solid configuration such that said frequency-dependent valve operates as a closed system, said closed system having a single passage that serves as both an inlet and an outlet for fluid to enter and leave said frequency-dependent pressure chamber.

13. The piston according to claim 12, wherein, Said frequency-dependent control stack includes a frequency-dependent control disk that defines a control orifice providing fluid communication between said intermediate chamber and said frequency-dependent pressure chamber.

14. The piston according to claim 12, wherein, Said frequency-dependent control stack includes a frequency-dependent deflecting disk and a slotted disk, said slotted disk supporting said frequency-dependent deflecting disk and defining a hole that allows fluid pressure in said intermediate chamber to act on said frequency-dependent deflecting disk to bias said frequency-dependent deflecting disk away from said slotted disk, and thus allowing fluid to flow around said frequency-dependent deflecting disk and into the frequency-dependent pressure chamber.

15. The piston according to claim 12, wherein, Said frequency-dependent housing defines a capture surface configured to engage said frequency-dependent slider and defining a maximum axial travel limit of said frequency-dependent slider relative to said frequency-dependent housing.

16. The piston according to claim 15, wherein, Said frequency-dependent control stack includes a frequency-dependent deflecting disk and a slotted disk that supports said frequency-dependent deflecting disk, wherein, said frequency-dependent housing includes a first axial end that contacts an upper surface of said slotted disk adjacent to a peripheral edge of said slotted disk, and wherein, said frequency-dependent slider is configured to bias said frequency-dependent housing away from said slotted disk at the maximum axial travel limit and thereby increase the flow rate through said frequency-dependent valve.

17. The piston according to claim 12, said piston further comprising a compression valve assembly and a rebound valve assembly, and Among them, said frequency-dependent valve is disposed at an end of said piston body opposite to each of said rebound valve assembly and said compression valve assembly.

18. A piston for a damper assembly, said piston comprising: a piston body that defines an intermediate chamber; and Frequency-dependent valve, the frequency-dependent valve comprising: a frequency-dependent housing, a frequency-dependent slider, a frequency-dependent control stack, and a frequency-dependent working disk, the frequency-dependent housing having a tubular shape surrounding a frequency-dependent chamber, the frequency-dependent slider being disposed within the frequency-dependent housing and dividing the frequency-dependent chamber into a frequency-dependent pressure chamber and a frequency-dependent displacement chamber, the frequency-dependent control stack being configured to regulate fluid flow between the intermediate chamber and the frequency-dependent pressure chamber, the frequency-dependent working disk being configured to deflect with the frequency-dependent housing to regulate fluid flow between a rebound chamber and a compression chamber, wherein the frequency-dependent housing defines a capture surface configured to engage the frequency-dependent slider and defining a maximum axial travel limit of the frequency-dependent slider relative to the frequency-dependent housing, wherein the frequency-dependent control stack includes a frequency-dependent deflecting disk and a slotted disk supporting the frequency-dependent deflecting disk, wherein the frequency-dependent housing includes a first axial end that contacts an upper surface of the slotted disk adjacent to an outer peripheral edge of the slotted disk, and wherein the frequency-dependent slider is configured to bias the frequency-dependent housing away from the slotted disk at the maximum axial travel limit and thereby increase the flow rate through the frequency-dependent valve.

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