Valve arrangement for shock absorber comprising triple spring arrangement

Abstract

The present disclosure relates to a valve device for a shock absorber. The valve arrangement includes a valve member axially movable relative to the housing and a triple spring arrangement including a first spring, a second spring, and a coil spring disposed between the valve member and a coupling member coupled to the first spring and the second spring. The valve arrangement is adapted such that the first spring deflects to adjust a force balance of the valve member when the valve member moves no more than a first stroke length relative to a predetermined reference position, the second spring deflects to adjust said force balance when the valve member moves more than the first stroke length, and the second spring deflects to adjust said force balance when the valve member moves more than the first stroke length. And when the valve member moves beyond a second stroke length greater than the first stroke length, the coil spring compresses to adjust the force balance. A shock absorber comprising such a valve arrangement and a method for controlling a flow of a damping medium in a shock absorber are also disclosed.

Description

[0001] This application is a divisional application of Chinese Patent Application No. 202111228347.8. The filing date of that Chinese Patent Application was October 21, 2021, and the invention was entitled "Valve Device with Triple Spring Mechanism for Shock Absorber". Technical Field

[0002] This invention relates to a valve device for a shock absorber, which is used to regulate the flow of damping medium between the damping chambers of the shock absorber, and particularly to a valve device including a triple spring device, which is capable of achieving desired damping force characteristics. Background Technology

[0003] Spring mechanisms consisting of a weak spring and a hard spring (where the weak spring biases the hard spring and contributes to different spring masses in different parts of the stroke) are used in many technical structures, such as valves designed to control the flow of damping media in shock absorbers. Especially in shock absorber applications (where the valve must have a precise damping pressure level without adjustable mechanisms), a low spring constant at the very beginning of the stroke is important. This low spring constant then transitions to a higher spring constant to match the high pressures that may be generated in the shock absorber during rapid motion.

[0004] EP 2201262 A1 describes a known design within the technical field of the present invention.

[0005] The aim is to improve known designs to achieve desired damping force characteristics. However, some known inventions fail to provide reliable solutions, partly due to poor tolerances of the springs intended for use. Some solutions also occupy a considerable amount of space within the limited space of the shock absorber. Some solutions offer acceptable damping force characteristics in certain travel length ranges while sacrificing quality in other travel length ranges.

[0006] Therefore, there is a need for an improved valve device for shock absorbers that at least alleviates some of these problems. Summary of the Invention

[0007] The object of this invention is to provide an improved solution that mitigates the aforementioned disadvantages of existing solutions. Furthermore, the object is to provide a valve device for a shock absorber capable of providing desired damping force characteristics. Here, the desired damping force characteristics may include: a first damping force region over a first stroke length interval, wherein the damping force increases slowly; a second damping force region over a subsequent second stroke length interval, wherein the damping force increases rapidly; and a third damping force region over a further subsequent third stroke length interval, wherein the damping force increases more slowly. Furthermore, the object is to provide a shock absorber incorporating such a valve device, and also to provide a corresponding method for controlling the flow of damping medium between the damping chambers of the shock absorber.

[0008] The present invention is based on the inventor's understanding that the aforementioned objectives can be achieved by incorporating a specially designed triple spring device into a valve assembly. The triple spring device includes a helical spring, a first spring, and a second spring, each adapted to deform, thereby adjusting the force balance of the valve components during different stroke length intervals corresponding to the aforementioned different damping force regions. The present invention further aims to provide a valve assembly including a spring device that is compact and simple, and inexpensive to assemble, manufacture, and adjust.

[0009] According to a first aspect of the invention, a valve device for a shock absorber is provided. The valve device includes a valve member axially movable relative to a housing, by which an opening defined by an interface between the valve member and a valve seat is adjusted. The valve device includes a spring device. The spring device includes a first spring, a second spring, and a helical spring, the helical spring being disposed between the valve member and a connecting member connected to the first spring and the second spring. The valve device is adapted such that, when disposed in a shock absorber, the flow of damping medium between the damping chambers of the shock absorber is regulated by a force balance of the valve member, which is generated partially or primarily by a damping medium pressure that depends on the flow of the damping medium and acts on the valve member in opposition to the action of the spring device. The valve device is further adapted such that when the valve member moves no more than a first stroke length relative to a predetermined reference position, the first spring deflects to adjust the force balance; when the valve member moves beyond the first stroke length, the second spring deflects to adjust the force balance; and when the valve member moves beyond a second stroke length greater than the first stroke length, the helical spring compresses to adjust the force balance.

[0010] Therefore, when the valve device is arranged accordingly in the shock absorber, the damping force characteristics of the shock absorber are characterized by the following for continuously increasing stroke lengths: a first region of slowly increasing damping force corresponding to a first stroke length; a second region of rapidly increasing damping force corresponding to a second stroke length; and a third region of slowly increasing damping force corresponding to a third stroke length greater than the second stroke length, which is defined by the remaining stroke length in which the valve member can move until it is prevented from moving further into the housing.

[0011] More specifically, this desired damping force characteristic is achieved at least in part by the spring assembly comprising a first spring, a second spring, and a helical spring (i.e., a triple spring assembly), and by how the spring assembly is adapted to interact with the valve member as it moves relative to the housing.

[0012] As mentioned above, the valve member is adapted to engage with a valve seat. The valve seat may be a separate component from the housing. Furthermore, the valve seat and valve member may be adapted in shape and form to define a recess at their interface for distributing damping medium over a larger area at the interface. This facilitates controlled movement of the valve member relative to the housing and away from the valve seat. The valve member may include a through-hole axially aligned with the valve member, adapted to allow flow of the damping medium without forcing displacement of the valve member relative to the valve seat.

[0013] As mentioned above, the valve assembly is designed to regulate the flow of damping medium between the damping chambers of the shock absorber. The damping chambers can refer to the compression chamber and the rebound chamber. Furthermore, the damping medium can flow through an opening defined by the interface between the valve member and the valve seat, thereby mitigating increased pressure buildup to some extent. In other words, the position of the valve member relative to the valve seat can regulate the flow of the damping medium.

[0014] The connecting member can be adapted to facilitate the connection of the helical spring with the first and second springs. The connecting member can be adapted and mounted such that the first spring deflects in front of the second spring in response to the flow of damping medium and / or the movement of the valve member. The connecting member can represent a component of a triple-spring device, i.e., the spring device may include the connecting member. The connecting member can be adapted to connect with the valve member to hold the helical spring in place.

[0015] As mentioned, the first stroke length, second stroke length, and third stroke length are measured relative to a predetermined reference position in the housing. The predetermined reference position refers to a position within the housing that is fixed at least during use. The stroke length of the valve member is then measured as the distance along the stroke path of the valve member within the housing, relative to the fixed position.

[0016] In the context of this application, the terms "slow" and "fast" used in connection with damping forces in different damping force regions should be understood merely as indicating the relationship between the damping force behavior of the different damping force regions. That is, compared to the damping forces in the first and third damping force regions, the second damping force region is characterized by a damping force that increases more rapidly with respect to the stroke length. Similarly, compared to the damping force in the second damping force region, the first and third damping force regions are characterized by a damping force that increases more slowly with respect to the stroke length.

[0017] In the context of this application, "pressure-responsive valve" should be understood as a valve adapted to achieve a larger flow opening in response to pressure changes. A pressure-responsive valve can refer to a valve adapted to achieve a larger flow opening in response to an increase in pressure. Further, a pressure-responsive valve can refer to a valve adapted to actuate from a closed state to an open state in response to a pressure change. Examples of pressure-responsive valves can include gasket stacks, lift valves, etc.

[0018] In the context of this application, low stroke speed, medium stroke speed, and high stroke speed can be primarily considered as stroke speeds within the ranges of 0-1 m / s, 1-2 m / s, and 2-4 m / s, respectively. Further stroke speeds exceeding 4 m / s can be considered as included in the high stroke speed range.

[0019] In the context of this application, "arranged in series" should be understood as objects A and B being arranged such that they are fluidly connected to each other. The phrase "fluidly connected" should be understood as object A being connected to object B via any connecting device (such as a channel, pipe, hose, or other connecting device through which a damping medium can flow). The connection can be direct or indirect. Furthermore, in the context of this application, "fluidly arranged between" object B and object C should be understood as object A being placed between object B and object C, within a fluid path extending between object B and object C. Therefore, object A does not need to be "fluidly arranged" as if it were floating.

[0020] In the context of this application, "open state" should be understood as object A being configured to allow the flow of damping medium through the object. Conversely, "closed state" should be understood as object A being configured to prevent the flow of damping medium through the object.

[0021] In the context of this application, "compression stroke" should be understood as the movement of the piston head as it moves toward the compression chamber. Furthermore, "springback stroke" should be understood as the movement of the piston head as it moves toward the springback chamber.

[0022] In the context of this application, the expression "connected to / connected with" should be understood as object A being mechanically connected to object B in some way, not necessarily a direct mechanical connection—for example, there could be an object C connecting object A and object B. Similarly, the expression "arranged between" should be understood as not limited to the case where object C is directly arranged between object A and object B, but could also include other objects D, E, etc., directly existing between object C and A and / or B.

[0023] According to one embodiment, the second spring has a higher spring constant than both the first spring and the helical spring. This ensures that the first spring deflects before the second spring when the valve member moves axially toward a higher stroke position. The advantage of this is that it allows the triple spring device to function reliably and passively. The higher spring constant can be achieved due to the difference in material and / or shape between the second spring and the first spring. For example, the second spring can be characterized by dimensions that are thicker, wider, or shorter than the first spring.

[0024] According to a further embodiment, the helical spring is biased when the valve member is in a resting position relative to the predetermined reference position. The resting position can refer to when the valve member is engaged with the valve seat, i.e., resting on the valve seat. The helical spring can be biased between the connecting member and the valve member. The helical spring can be biased such that it only begins to compress after the first and second springs have deflected as the valve member moves axially toward a higher stroke position. Further, the helical spring can be characterized by its spring constant, which is lower than that of the second spring. This can represent a specific way to achieve desired damping force characteristics. Furthermore, the spring constant of the helical spring can be equal to, higher than, or lower than the spring constant of the first spring. The magnitude of the relationship and difference can be adjusted to achieve specific damping force characteristics in the first and third damping force regions. The resting position can be a position axially offset relative to the predetermined reference position.

[0025] According to one embodiment, the connecting member is a spring cap adapted to a latch for maintaining the bias of the helical spring while allowing the helical spring to be compressed in a controlled manner. Each corresponding latch may be arranged on a corresponding branch of the spring cap. Each corresponding branch may be flexible, allowing the latches to shift toward each other when inserted into the valve member, and when inserted, the latches engage with the valve member, thereby maintaining the helical spring in a biased state. The length of the branch determines how much the helical spring is biased when the valve member is in its rest stroke position. The spring cap may include two, three, four, five, or more latches, each arranged on a corresponding branch. In a preferred embodiment, the spring cap includes three latches.

[0026] According to one embodiment, a predetermined rest stroke position is adjustable by inserting an adjusting shim of preferred thickness between the valve seat and the valve housing. This allows adjustment of whether and by how much the first spring will be biased when the valve member is in the rest stroke position, thus enabling the damping force characteristics to be adjusted to the desired characteristics. The valve seat can be adapted to a protrusion for engaging the adjusting shim. The width of the adjusting shim then determines how much the valve seat will offset from the housing, thereby also adjusting how much the valve member will be adjusted according to its position when in the rest stroke position. When the valve assembly is assembled into the shock absorber, the valve seat will offset relative to the housing by an offset distance corresponding to the thickness of the adjusting shim. Advantageously, the valve assembly can be adapted to be configured with one or more of a set of adjusting shims, and the adjusting shims can then be selected to achieve a specific offset distance, and thereby achieve the desired bias of the first spring. The valve assembly can be configured with multiple such adjusting shims to achieve the desired bias of the first spring. The set of adjusting shims can include adjusting shims with a thickness of up to 1 mm.

[0027] According to one embodiment, both the first spring and the second spring are provided by a deflectable washer spring portion of a single washer spring. Thus, the triple spring assembly can be provided with a more compact form factor. The washer spring can be a circular washer spring.

[0028] According to one embodiment, the first spring is provided by an outer washer spring portion forming the outer edge of the washer spring, and an inner washer spring portion separated from the outer washer spring portion and connected to the outer washer spring portion via a flexible branch, such that the outer washer spring portion and the inner washer spring portion can deflect relative to each other by a first deflection distance corresponding to the first stroke length. The second spring is provided by the inner washer spring portion, and an innermost washer spring portion separated from the inner washer spring portion but connected to the inner washer spring portion via a flexible branch, such that the inner washer spring portion and the innermost washer spring portion can deflect relative to each other by a second deflection distance corresponding to the second stroke length. With this design, the first and second springs occupy less space in the axial direction. Furthermore, this design results in a beneficial synergy with a helical spring, whose dimensions can be appropriately determined according to the spring constant and bias, thereby achieving the desired function.

[0029] According to one embodiment, the connecting member is a spring cap including a protrusion adapted to press against the innermost washer spring portion. The spring cap may include a body and a protrusion extending axially from the body. The protrusion may be adapted to engage with one of a first spring and a second spring, thus facilitating connection therewith. Further, the body may be adapted to engage with the first or second spring in a restrictive manner, i.e., how much the protrusion protrudes axially from the body determines how much the first or second spring can deflect. In other words, this determines the length of the first or second stroke.

[0030] According to one embodiment, the deflection distance between the outer washer spring portion and the inner washer spring portion is generated by biasing the first spring between the first fixing member in the valve housing and the helical spring. Therefore, the first spring can deflect reliably and in a controlled manner. Furthermore, the deflection of the first spring may be limited, meaning that the first spring does not contribute to the damping force characteristics in the second or third damping force region.

[0031] According to one embodiment, the deflection distance between the innermost and innermost washer spring portions is generated by biasing the second spring between the second fixing member in the valve housing and the connecting member. Specifically, the connecting member can be connected to the innermost washer spring portion via the previously mentioned protrusion when the connecting member is a spring cap. The deflection distance between the inner and innermost washer spring portions can be determined by how much the protrusion extends from the body of the spring cap. This provides a reliable way to ensure that the deflection distance of the second spring is indeed limited and does not affect the damping force characteristics in the third damping force region.

[0032] According to one embodiment, the legs connecting the innermost washer spring portion to the inner washer spring portion extend radially from the center of the washer spring. The legs can be symmetrically positioned between the inner and innermost washer spring portions. The thickness, width, and length can be formed accordingly to achieve a desired spring constant.

[0033] According to one embodiment, a branch connecting the inner washer spring portion and the outer washer spring portion extends in the circumferential direction of the washer spring. The branch can be symmetrically positioned between the outer washer spring portion and the inner washer spring portion. The thickness, width, and length can be formed accordingly to achieve a desired spring constant.

[0034] According to one embodiment, one or both of the first stroke length and the second stroke length are less than 2 mm, preferably less than 1 mm. By having a smaller stroke length, the valve device can be manufactured in a more compact form factor.

[0035] According to one embodiment, the valve device can be adapted to be arranged in a damper including a pilot valve. The pilot valve may include one or more pilot valve members adapted to be axially displaceable relative to a pilot valve seat. The one or more pilot valve members may be adapted to be axially displaceable via a solenoid device configured to generate a solenoid force acting on the one or more pilot valve members. The solenoid device may include an actuating member adapted to be axially movable to or from the one or more pilot valve members under the influence of the solenoid device. The solenoid force is then generated by the solenoid device, thereby forcing the actuating member to move toward and interact with the one or more pilot valve members. The pilot valve may include a pilot valve spring arranged to counteract the solenoid force acting on the pilot valve members. The pilot valve spring may be arranged to interact with the one or more pilot valve members in the direction of counteracting the solenoid force. The pilot valve spring may form part of the one or more pilot valve members. The pilot valve spring can be a shim spring adapted to be movable between a first position interacting with the pilot valve seat and a second position positioned away from the pilot valve seat. The actuating member can be adapted to interact with the shim spring, causing the shim spring to deflect into the first position. When the shim spring is in the second position, the actuating member can be in a position not interacting with the shim spring, or in a position contacting the shim spring but not causing further deflection of the shim spring. The shim spring can regulate the damping medium flow differently in the first and second positions. The solenoid force can be adjusted by adjusting the solenoid device.

[0036] The pilot valve is designed for fail-safe operation, a safe operating mode where the solenoid force may unintentionally disappear. The pilot valve spring pushes the pilot valve assembly to a position where damping fluid can flow through it. When the pilot valve spring forms part of one or more pilot valve assemblies, the shim spring can be moved to a position with less deflection. The pilot valve can define a first damping medium flow path and a second medium flow path. During normal operation of the solenoid device, the pilot valve can regulate the damping medium flow along the first damping medium flow path. Specifically, the damping medium flow can be regulated along the first damping medium flow path by means of the shim spring. Furthermore, the magnitude of the solenoid force can be related to how much the damping medium flow is regulated. During fail-safe operation, i.e., when the solenoid force is absent or insufficient to counteract the pilot valve spring, the first damping medium flow path can be closed, allowing most or all of the damping medium to flow along the second damping medium flow path. The pilot valve can be adapted to regulate the damping medium flow along the second damping medium flow path during fail-safe operation. The pilot valve can be adapted to achieve this via a fail-safe gasket. Under fail-safe operation, the fail-safe gasket may be biased. If the pilot valve spring forms part of one or more pilot valve components and is a gasket spring, the first damped medium flow path can be closed by the gasket spring during fail-safe operation. The first damped fluid flow path may be partially defined by one or more passages extending through the pilot valve body.

[0037] The pilot valve spring can be a shim spring, such as a helical spring. According to a preferred embodiment, the pilot valve spring can be a shim spring. The pilot valve spring can be adapted to provide different spring forces by deflecting different spring portions according to the position of the pilot valve member. Different spring portions can be adapted to abut against an inner portion of the pilot valve. According to one embodiment, the pilot valve spring defines a first shim spring and a second shim spring interconnected. The first shim spring can be defined by a first shim spring portion corresponding to the outer edge of the shim spring and a second shim spring portion corresponding to the inner portion, the inner portion being connected to the first shim spring portion via a flexible branch. The second shim spring can be defined by a second shim spring portion corresponding to the inner portion and a third shim spring portion corresponding to the innermost shim spring portion, the innermost shim spring portion being connected to the inner portion via a flexible branch. The flexible branches connecting the first and second shim spring portions can be two, three, four, five, or more. The flexible branches connecting the second shim spring portion to the third shim spring portion can be two, three, four, five, or more. The first washer spring can be characterized by a different spring constant than the second washer spring. The first washer spring can be characterized by a spring constant larger than that of the second washer spring. Alternatively, the first washer spring can be characterized by a spring constant smaller than that of the second washer spring. The flexible branch connecting the first and second washer spring portions can extend in the circumferential direction. "Extending in the circumferential direction" can refer to the distance the flexible branch extends from a point in the first washer spring portion to a point in the second washer spring portion, which is offset in the circumferential direction relative to a point in the first washer spring portion and the center point of the washer spring. The circumferential offset can be between 10 and 90 degrees. The flexible branch connecting the second and third washer spring portions can also extend in the circumferential direction. The circumferential offset between corresponding points can be between 10 and 90 degrees.

[0038] According to one embodiment, the valve device is adapted to operate under the influence of a pilot valve controlled by a solenoid device. The solenoid device can be controlled to adjust the pressure affecting the operation of the valve device. The solenoid device can adjust the pilot valve. The valve device can be in fluid connection with the pilot valve. A damping medium flow can flow through the valve device to the pilot valve. The pilot valve can be adapted to provide a first damping medium flow path and a second damping medium flow path. During normal operation, the damping medium flow can be regulated along the first damping medium flow path via the pilot valve. During fail-safe operation, i.e., when the solenoid device no longer provides solenoid force or at least a sufficiently large solenoid force, the pilot valve can regulate the damping medium flow along the second damping medium flow path. The first and second damping medium flow paths can form parallel damping medium flow paths.

[0039] According to a second aspect of the invention, a shock absorber is provided. The shock absorber includes a valve device according to the first aspect of the invention or any embodiment thereof. By having the valve device in the shock absorber, the shock absorber can therefore operate in a desired manner. For example, the shock absorber may be characterized by the previously mentioned desired damping force characteristics.

[0040] According to a third aspect of the invention, a method for controlling the flow of damping medium between the damping chambers of a shock absorber is provided. This is accomplished by a valve device comprising: a valve member axially movable relative to a housing, by which an opening defined by an interface between the valve member and a valve seat is adjusted; and a spring device comprising a first spring, a second spring, and a helical spring disposed between the valve member and a connecting member connected to the first spring and the second spring, wherein the flow of damping medium between the damping chambers of the shock absorber is regulated by a force balance of the valve member, the force balance being generated partially or primarily by a damping medium pressure that depends on the flow of damping medium and acts on the valve member in opposition to the action of the spring device. The method includes the following steps: when the valve component moves no more than a first stroke length relative to a predetermined reference position, adjusting the force balance by deflecting the first spring; when the valve component moves beyond the first stroke length, adjusting the force balance by deflecting the second spring; and when the valve component moves beyond a second stroke length greater than the first stroke length, adjusting the force balance by compressing the helical spring.

[0041] This invention is defined by the appended independent claims, and embodiments are set forth in the appended dependent claims, in the following description and in the accompanying drawings. Attached Figure Description

[0042] The invention will be described in more detail below with reference to the accompanying drawings, in which: Figure 1 A valve device is shown assembled into a solenoid for a shock absorber according to an embodiment of the present invention; Figure 2 An exploded perspective view of a valve device according to an embodiment of the present invention is shown; Figure 3 An exploded side view of a valve device according to an embodiment of the present invention is shown; Figures 4a to 4d A cross-sectional view of a valve device according to an embodiment of the present invention is shown; Figure 5 A spring of a spring device according to an embodiment of the present invention is shown; Figure 6 The damping force characteristics achieved by a valve device according to an embodiment of the present invention are shown; Figure 7 A spring according to an embodiment of the present invention is shown; Figure 8a and Figure 8b A cross-sectional view of a valve device and a pilot valve having fail-safe operation according to an embodiment of the present invention is shown. Figure 9a and Figure 9b Each illustrates a shock absorber according to an embodiment of the present invention, and Figure 10 A flowchart of a method according to an embodiment of the present invention is shown. Detailed Implementation

[0043] The invention will be described more fully below with reference to the accompanying drawings, in which preferred embodiments of the invention are illustrated. However, the invention can be implemented in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. In the drawings, the same reference numerals denote the same elements.

[0044] Figure 1 A valve device 1 according to an embodiment of the present invention is shown. The valve device 1 is adapted to be arranged in or to shock absorbers 200a, 200b, and to regulate the flow of damping medium between the damping chambers (commonly referred to as compression chambers and rebound chambers) of the shock absorber. However, in Figure 1 In order to show the valve device 1 in a more focused manner, all parts of the shock absorbers 200a and 200b except for the solenoid 100 are omitted from the figure. See also Figure 9a , Figure 9b The document demonstrates different types of shock absorbers 200a and 200b that combine the valve device 1 and the solenoid 100.

[0045] like Figure 1 As shown, the valve device 1 includes a valve member 3 that is axially movable relative to the housing 4. The housing 4 is provided with a generally cylindrical shape, and the valve member 3 is inserted into this generally cylindrical shape through an opening facing the bottom, such that... Figure 1 As seen in the image. Valve member 3 is adapted to move axially away from valve seat 2 within housing 4, and valve member 3 rests on valve seat when in rest stroke position X0' (see [reference]). Figure 4aWhen valve member 3 moves axially relative to housing 4, the opening defined by the interface between valve member 3 and valve seat 2 is adjusted. This opening is closed when valve member 3 rests on valve seat 2, but opens when valve member 3 moves axially from valve seat 2, thus allowing damping medium flow through the opening. As valve member 3 moves away from valve seat 2 or even further, the opening between them increases, thus allowing even greater damping medium flow. Valve member 3 is thus adapted to be movable relative to housing 4 in response to damping medium flow Q flowing through valve seat 2 toward valve member 3. The axial displacement (i.e., stroke length) of valve member 3 is measured relative to a fixed and predetermined reference position X0 of housing 4 (see, for example, [reference needed]). Figure 4a ).

[0046] Furthermore, such as Figure 1 As can be seen, valve member 3 is provided with a through hole, the size and shape of which are adapted to allow a specific damping medium flow through the through hole. If the damping medium flow is larger than the size of the through hole of the valve member, pressure buildup occurs, acting on valve member 3, causing the valve member to further shift axially from valve seat 2 into housing 4. This allows the damping fluid flow to be regulated by valve device 1.

[0047] The valve assembly 1 further includes a spring assembly. The spring assembly includes a first spring 6a, a second spring 6b, and a helical spring 5. This "triple spring assembly" is adapted to resist axial movement of the valve member 3, biasing the valve member towards the valve seat 2 to return to its rest stroke position. Figure 1 In the illustrated embodiment, the first spring 6a and the second spring 6b are provided by the deflectable washer spring portion of a single washer spring 6. A helical spring 5 is arranged between the valve member 3 and the connecting member 7. Figure 1 In this configuration, the connecting member 7 is a spring cap adapted to be connected to the end of the helical spring 5. The spring cap 7 is slidably latched in the valve member 3, thus securely holding the helical spring 5 in place. The latching mechanism is provided by a set of latches arranged on corresponding flexible branches, which are flexible such that the branches flex toward each other, thereby allowing the spring cap 7 to be partially inserted into the valve member 3. When inserted, the branches flex away from each other, thus placing the latches in place and preventing the spring cap from disengaging from the valve member 3.

[0048] In one embodiment, when the valve member 3 is in the rest stroke position X0', the helical spring 5 is biased. The degree of bias of the helical spring 5 depends on the length of the helical spring 5, the depth of the cavity in the valve member 3 in which the helical spring 5 is placed, and the length of the branch of the spring cap 7. These parameters can be varied accordingly to achieve certain damping force characteristics.

[0049] According to some embodiments, in Figure 2 and Figure 3Each component of the valve device 1 can be seen here. As can be seen, the spring cap 7 is arranged such that it contacts the washer spring 6. Furthermore, the spring cap 7 is provided with a protrusion 71 extending in the axial direction. The purpose of this protrusion is to engage with the innermost washer spring portion 62 of the washer spring 6. The first spring 6a and the second spring 6b are connected to each other, and the protrusion 71 of the spring cap 7 enables a small interaction area, which helps the washer spring 6 to deform as expected.

[0050] According to one embodiment, it is desirable that when the valve member 3 is in the rest stroke position X0', the first spring 6a is biased. The bias of the first spring 6a is adjusted to press against the shim spring 6, such that as the stroke length increases, the first spring 6a deflects first and then the second spring 6b deflects. The valve device 1 allows one or more adjusting shims 8 to be inserted between the valve seat 2 and the housing 4. This allows adjustment of the offset distance between the valve seat 2 and the housing 4, and thus adjustment of the rest stroke position of the valve member 3.

[0051] Figure 4a A cross-sectional view is shown with the valve seat 2 arranged in the housing 4, illustrating the gap between the adjusting shim 8 and the fixed portion 43 of the housing 4. When correctly assembled, there is no gap between the valve seat 2 and the housing 4, or between the valve seat 2, the housing 4, and any adjusting shims placed between them. Further, the relative position of the valve seat 2 with respect to the housing 4 can be adjusted by inserting adjusting shims 8 of preferred thickness. This thus adjusts the rest stroke position X0' of the valve member 3 in the housing 4. If no adjusting shims 8 are inserted, the valve seat 2 and the housing 4 can abut against each other, thus further positioning the rest stroke position of the valve member 3 on the housing 4. Assuming the dimensions of the valve member 3 and the spring assembly remain unchanged, the further the rest stroke position of the valve member 3 is positioned in the housing 4, the more the first spring 6a is biased. Conversely, the thicker the adjusting shims, or the more adjusting shims are included, the more the rest stroke position of the valve member 3 is positioned outward toward the housing 4. This reduces the degree to which the first spring 6b is biased when the valve member 3 is in the rest stroke position. Therefore, it is possible that the first spring is not biased at all when the valve member 3 is in the rest stroke position.

[0052] from Figure 4a It can be understood that in the illustrated embodiment, the first spring 6b is biased when the valve member 3 is in the rest stroke position—this can be understood as the washer spring 6 being in a completely unbiased state, but the valve seat 2 not yet fully inserted into the housing 4.

[0053] When arranged in a shock absorber, the flow of damping medium between the damping chambers of the shock absorber is regulated by the force balance of the valve member 3. This force balance is generated partly or primarily by the damping medium, which depends on the flow of the damping medium and acts on the valve member 3 in opposition to the action of the spring mechanism. Therefore, when the damping medium acts on the valve member 3 and cannot flow through the valve member through-hole to the necessary extent, the pressure increases and the valve member 3 is forced away from the valve seat 2. In response to this movement, the first spring 6a deflects, causing the deflectable spring portion of the washer spring to move toward the fixed portion 42 of the housing 4. Since the helical spring is biased by the spring cap 7, it does not compress further until the first and second springs have deflected first. When the stroke length X1 (as measured from the predetermined reference position X0 of the housing 4) is reached, the deflectable spring portion abuts against the fixed portion 42, which prevents the first spring 6a from deflecting further. This is in Figure 4b As shown in the image.

[0054] When valve component 3 moves beyond the stroke length X1, the second spring 6b begins to deflect. The extent to which the second spring 6b deflects depends on how far the protrusion of the spring cap 7 protrudes from the body of the spring cap 7. Once the body of the spring cap 7 abuts against the washer spring 6, further deflection of the second spring 6b is prevented. Figure 4c As shown in the diagram. Once this occurs (at the second stroke length X2), the coil spring 5 will begin to compress to the maximum stroke length X3, in which case the valve member 3 abuts against the outer edge of the washer spring, as shown. Figure 4d As shown in the image.

[0055] Figure 5 The washer spring 6 is shown in more detail, and the helical spring 5 is also shown. The washer spring 6 is sized and shaped to provide a first spring 6a and a second spring 6b. The first spring 6a is provided by an outer washer spring portion 60 forming the outer edge of the washer spring 6, and an inner washer spring portion 61 separated from the outer washer spring portion 60 and connected to the outer washer spring portion via a flexible branch 63, such that the outer washer spring portion 60 and the inner washer spring portion 61 can deflect relative to each other. The deflection of the outer washer spring portion 60 and the inner washer spring portion 61 relative to each other corresponds to a first deflection distance of a first stroke length X1. The second spring 6b is provided by the inner washer spring portion 61, and an innermost washer spring portion 62 separated from the inner washer spring portion 61 but connected to the inner washer spring portion via a flexible branch 64, such that the inner washer spring portion 61 and the innermost washer spring portion 62 can deflect relative to each other. The inner washer spring portion 61 and the innermost washer spring portion 62 are able to deflect relative to each other by a second deflection distance corresponding to the second stroke length X2.

[0056] Furthermore, in Figure 5In the diagram, the flexible branch 64 connecting the innermost washer spring portion 62 to the inner washer spring portion 61 is shown extending radially from the center of the washer spring 6. However, the flexible branch 64 may alternatively extend circumferentially. There are a total of five flexible branches 64, symmetrically arranged between the innermost washer spring portion 62 and the inner washer spring portion 61. The flexible branch 63 connecting the inner washer spring portion 61 and the outer washer spring portion 60 extends circumferentially in the washer spring 6. There are a total of two flexible branches 63, symmetrically placed between the inner washer spring portion 61 and the outer washer spring portion 60.

[0057] The damping force characteristics obtained by this invention are in Figure 6 The diagram shows the magnitude of the force along the vertical axis and the stroke length along the horizontal axis. The damping force characteristics are characterized by: a first damping force region, where the damping force increases slowly between a predetermined reference position X0 and a first stroke length X1; a second damping force region, where the damping force increases more rapidly between the first stroke length X1 and the second stroke length X2; and a third damping force region, where the damping force increases slowly with increasing stroke length in the interval between the second stroke length X2 and the third stroke length X3. During the first damping force region, the first spring 6a deflects. During the second damping force region, the second spring 6b deflects. During the third damping force region, the helical spring 5 is compressed.

[0058] Figure 1 A pilot valve 12, fluidly connected to the valve assembly 1, is also depicted. The pilot valve 12 includes a gasket spring 9, a pilot valve seat 14, and a pilot valve body 11. Figure 1In the illustrated embodiment, the pilot valve seat 14 is formed as an integral part of the valve housing 4. Alternatively, the pilot valve seat may be formed as a separate part from the valve housing, but fixedly attached to it. The shim spring 9 includes an outer shim spring portion and an innermost shim spring portion, the innermost shim spring portion being connected to the outer shim spring portion via a flexible branch, either directly or via an intermediate inner shim spring portion, which is connected to the outer shim spring portion via a flexible branch. Thus, the shim spring 9 is adapted to partially move between a first position and a second position, in which the innermost shim spring portion interacts with the valve seat 14 to regulate the flow of damped medium through the pilot valve seat 14, and in the second position, away from the pilot valve seat 14. The outer shim spring portion of the shim spring 9 is substantially fixed relative to the pilot valve seat 14, but offset from it. Therefore, when interacting with valve seat 14 in the first position, or when displaced at least from the second position, the innermost gasket spring portion is biased to move in the direction toward the second position. The position of the innermost gasket spring portion is controlled by a solenoid device 100 configured to generate a solenoid force acting on the innermost gasket spring portion via an actuating member 13, which is axially displaceable relative to the pilot valve body 11 to interact with the innermost gasket spring portion. Further, the pilot valve body 11 is sized and shaped to define a cavity extending in the axial direction in which the actuating member 13 is movable.

[0059] The pilot valve body 11 also defines one or more pilot valve body channels extending from an opening facing the pilot valve seat 14 and corresponding auxiliary openings around the pilot valve body 11. Figure 1 Two such auxiliary openings are shown in the diagram. One or more pilot valve body passages are further defined, at least partially, by the gap between the actuating member 13 and the pilot valve body 11. Figure 1 As shown, the actuating member 13 is narrower than the through-hole of the pilot valve body 11, resulting in the formation of the gap.

[0060] The washer spring 9 can have the following characteristics: Figure 7 The shapes shown in the image. Figure 7The washer spring 9 shown includes a first washer spring portion 90 (also referred to herein as the outer washer spring portion) corresponding to the outer edge of the washer spring. The washer spring also includes a second washer spring portion 91 corresponding to the inner portion of the washer spring. The washer spring 9 further includes a third washer spring portion 92 (also referred herein as the innermost washer spring portion) corresponding to the innermost portion of the washer spring. The first washer spring portion 90 and the second washer spring portion 91 are interconnected via a flexible branch 93, allowing the first washer spring portion 90 and the second washer spring portion 91 to deflect relative to each other, thereby defining the first washer spring. The flexible branch 93 extends in the circumferential direction. The second washer spring portion 91 and the third washer spring portion 92 are interconnected via a flexible branch 94, allowing the second washer spring portion 91 and the third washer spring portion 92 to deflect relative to each other, thereby defining the second washer spring. The flexible branch 94 also extends in the circumferential direction.

[0061] The pilot washer spring 9 can also be adapted in shape and size to provide one or more openings 95 near the outer diameter of the washer spring, such as... Figure 7 As shown in the diagram. One or more openings can be as follows: Figure 7 The diagram shows three openings, but there could also be two, four, or more. The one or more openings 95 allow for fluid communication between the pilot valve body 11 and the valve housing 4 via the pilot washer spring 9, as shown in the diagram. Figure 8a As shown in the diagram, the damping medium flow can flow through one or more openings via the main port in the pilot valve seat and / or the auxiliary valve port in the pilot valve seat.

[0062] In cases where the solenoid device cannot generate a solenoid force acting on the washer spring 9, the pilot valve 12 can also be adapted for fail-safe operation. Fail-safe operation can be achieved via the pilot valve 12, which defines a first damping medium flow path Q1 and a second damping medium flow path Q2. Along the first damping medium flow path, the washer spring 9 regulates the damping medium flow, and in the second damping medium flow path, the fail-safe washer 10 regulates the damping medium flow. Figure 8a and Figure 8b These are shown in more detail, as well as fail-safe operation.

[0063] exist Figure 8a In the middle, the pilot valve operates normally, which means that the solenoid force F sThe action on the washer spring 9 causes the innermost washer spring portion 92 to be pushed against the valve seat 14. Therefore, the damping medium flow is regulated at the interface 15 between the valve seat 14 and the innermost washer spring portion 92. A first damping medium flow path extends from this regulation interface 15 into the pilot valve body passage formed in the pilot valve body 11, along the gap between the actuating member 13 and the inner surface of the pilot valve body 11, and then through auxiliary openings leading to the periphery of the pilot valve body 11. This first damping medium flow path... Figure 8a The arrow indicates this. When the washer spring 9 is in this state, the washer spring is biased to return to a position with less deflection, meaning that unless the solenoid force F... s The action on the washer spring 9 will cause the washer spring to move away from the pilot valve seat 14.

[0064] However, when the solenoid device 100 intentionally or unintentionally stops generating the solenoid force F acting on the innermost washer spring portion 92... s At this time, the innermost shim spring portion 92 moves away from the valve seat 14 to a second position, in which the innermost shim spring portion blocks the first damping medium flow path Q1 by covering the pilot valve body passage opening in the pilot valve body 11. In this state, the damping medium flow is forced to flow along the second damping medium flow path Q2, such as... Figure 8b As shown, the fail-safe shim adjusts the flow of the damping medium. Specifically, the adjustment occurs at the interface 16 formed between the fail-safe shim and the shim spring 9.

[0065] Therefore, even if the solenoid device stops generating solenoid force F s Pilot valve 12 can also provide damped medium flow regulation.

[0066] Figure 9a , Figure 9b Shock absorbers according to different embodiments of the present invention are shown. Figure 9a A three-cylinder shock absorber 200a is shown, which includes a valve device 1 and a solenoid device 100. In this design, the valve device 1 regulates the flow of the damping medium during both the rebound and compression strokes. Figure 9b A dual-cylinder shock absorber 200b is shown, comprising a first valve assembly and a second valve assembly 1, and a corresponding solenoid device 100. In this design, one of the two valve assemblies regulates the flow of damping medium during the rebound stroke, while the other valve assembly regulates the flow of damping medium during the compression stroke.

[0067] Figure 10A flowchart of a method according to an embodiment of the present invention is shown. Method S0 relates to a method for controlling the flow of damping medium between the damping chambers of a shock absorber via a valve device 1. The valve device 1 includes a valve member 3 axially movable relative to a housing 4, by which an opening defined by an interface between the valve member 3 and a valve seat 2 is adjusted. The valve device 1 used in this method includes a spring device comprising a first spring 6a, a second spring 6b, and a helical spring 5, the helical spring being arranged between the valve member 3 and a connecting member 7 connected to the first spring 6a and the second spring 6b. The flow of damping medium between the damping chambers of the shock absorber is regulated by a force balance of the valve member 3, which is generated partly or mainly by the damping medium pressure, which depends on the flow of damping medium and acts on the valve member 3 in opposition to the action of the spring device. The method includes the following steps: when the valve component 3 moves no more than a first stroke length X1 relative to a predetermined reference position X0, the force balance described in S1 is adjusted by deflecting the first spring 6a; when the valve component 3 moves beyond the first stroke length X1, the force balance described in S2 is adjusted by deflecting the second spring 6b; and when the valve component 3 moves beyond a second stroke length X2 which is greater than the first stroke length X1, the force balance described in S3 is adjusted by compressing the helical spring 5.

[0068] Preferred embodiments and examples of the invention have been disclosed in the accompanying drawings and description, and although specific terminology has been used, it is used in a general and descriptive sense only and not for limiting purposes, and the scope of the invention is set forth in the appended claims.

Claims

1. A valve device (1) for a shock absorber, the valve device comprising: The valve member (3), which is axially movable relative to the housing (4), adjusts the opening defined by the interface between the valve member (3) and the valve seat (2) by moving it. A spring device comprising a first spring (6a), a second spring (6b), and a helical spring (5) arranged between the valve member (3) and the connecting member (7), the connecting member being connected to the first spring (6a) and the second spring (6b). The valve device (1) is adapted such that, when arranged in a shock absorber, the flow of damping medium between the damping chambers of the shock absorber is regulated by the force balance of the valve member (3), which is generated partly or mainly by the damping medium pressure, which depends on the flow of the damping medium and acts on the valve member (3) in opposition to the action of the spring devices (5, 6a, 6b, 7). When the valve member (3) moves no more than a first stroke length (X1) relative to a predetermined reference position (X0), the first spring (6a) deflects to adjust the force balance; when the valve member (3) moves beyond the first stroke length (X1), the second spring (6b) deflects to adjust the force balance; and when the valve member (3) moves beyond a second stroke length (X2) greater than the first stroke length (X1), the helical spring (5) compresses to adjust the force balance.

2. The valve device (1) according to claim 1, wherein, The second spring (6b) has a higher spring constant than the first spring (6a) and the helical spring (5).

3. The valve device (1) according to any one of claims 1 to 2, wherein, When the valve component (3) is in the stationary stroke position (X0') relative to the predetermined reference position (X0), the helical spring (5) is biased.

4. The valve device (1) according to any one of claims 1 to 2, wherein, The connecting member (7) is a spring cap that is adapted to the latch (72) to maintain the bias of the helical spring while allowing the helical spring (5) to be compressed in a controlled manner.

5. The valve device (1) according to claim 3, wherein, The predetermined rest stroke position (X0') is adjustable by inserting an adjusting shim (8) of preferred thickness between the valve seat (2) and the valve body (4).

6. The valve device (1) according to any one of claims 1 to 2, wherein, Both the first spring (6a) and the second spring (6b) are provided by deflectable washer spring portions (60, 61, 62) of a single washer spring (6).

7. The valve device (1) according to claim 6, wherein, The first spring (6a) is provided by an outer washer spring portion (60) forming the outer edge of the washer spring (6) and an inner washer spring portion (61) separate from the outer washer spring portion (60) and connected to the outer washer spring portion via a flexible branch (63), such that the outer washer spring portion (60) and the inner washer spring portion (61) can deflect relative to each other by a first deflection distance corresponding to the first stroke length (X1), and wherein the second spring (6b) is provided by the inner washer spring portion (61) and an innermost washer spring portion (62) separate from the inner washer spring portion (61) but connected to the inner washer spring portion via a flexible branch (64), such that the inner washer spring portion (61) and the innermost washer spring portion (62) can deflect relative to each other by a second deflection distance corresponding to the second stroke length (X2).

8. The valve device (1) according to claim 7, wherein, The connecting member (7) is a spring cap that includes a protrusion (71) adapted to press against the innermost washer spring portion (62).

9. A shock absorber comprising a valve device (1) according to any one of the preceding claims.

10. A method (S0) for controlling the flow of damping medium between the damping chambers of a shock absorber via a valve device, the valve device comprising: A valve member (3) that is axially movable relative to the housing (4) adjusts the opening defined by the interface between the valve member (3) and the valve seat (2) by moving; and a spring device comprising a first spring (6a), a second spring (6b) and a helical spring (5) arranged between the valve member (3) and a connecting member (7) connected to the first spring (6a) and the second spring (6b). The flow of damping medium between the damping chambers of the shock absorber is regulated by the force balance of the valve component (3), which is generated partly or mainly by the damping medium pressure, which depends on the flow of damping medium and acts on the valve component (3) in opposition to the action of the spring devices (5, 6a, 6b, 7). The method (S0) includes the following steps: When the valve component (3) moves no more than the first stroke length (X1) relative to the predetermined reference position (X0), the force balance is adjusted (S1) by deflecting the first spring (6a). When the valve component (3) moves beyond the first stroke length (X1), the force balance is adjusted (S2) by deflecting the second spring (6b), and When the valve component (3) moves beyond a second stroke length (X2) greater than the first stroke length (X1), the force balance is adjusted (S3) by compressing the helical spring (5).

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