Vibration damper unit and use
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- VIBRACOUSTIC SE
- Filing Date
- 2026-01-20
- Publication Date
- 2026-07-30
Smart Images
Figure EP2026051237_30072026_PF_FP_ABST
Abstract
Description
[0001] January 16, 2026
[0002] 82162-0695- P WO - Ke / Pez
[0003] Applicant: Vibracoustic SE
[0004] Höhnerweg 2-4
[0005] 69469 Weinheim
[0006] Vibration damper unit and use
[0007] The invention relates to a vibration damping unit according to claim 1 and a use of a rolling bellows according to claim 10.
[0008] Foot point adjustment devices are known from practice. They comprise a bellows-constrained hydraulic chamber for adjusting the distance between a vehicle body and the ground.
[0009] A rolling bellows with a rolled fold is known for this application. The rolling bellows achieves height adjustment by means of the rolled fold. A prerequisite for a rolled fold is that the bellows can be folded over to form the fold and that the bellows allows the rolled fold to roll during operation when adjusting the position. The area of the rolling bellows encompassed by the rolled fold must therefore be able to change diameter between the larger diameter on the outer circumference of the rolled fold and the smaller diameter on the inner circumference of the rolled fold. To prevent the bellows from flexing under dynamic loads, measures are known that keep the outer diameter of the bellows constant or prevent it from expanding beyond a certain limit. One such measure for rolling bellows is an external guide.
[0010] For hydro-chamber-limiting bellows, fiber reinforcements are known whose fibers run parallel to the longitudinal axis in the roll fold to allow for easy rolling of the roll fold and thus low harshness. Such bellows require external guidance to prevent bursting.
[0011] As an alternative to the rolling bellows, a bellows without roll gussets is known for limiting the hydro chamber. Height adjustment in the bellows without roll gussets is achieved by changing its diameter. Therefore, it necessarily exhibits elastic deformability with respect to its diameter. However, under dynamic loads, this results in constant flexing and undesirable springiness in the bellows without roll gussets. Furthermore, the constantly flexing bellows contributes to the overall spring travel. Thus, the bellows properties under dynamic load are part of the overall properties of the strut, such as the dynamic stiffening typical of elastomer bellows. Particularly detrimental dynamic, amplitude-dependent stiffening is also observed in air springs equipped with bellows featuring cross-layered fiber reinforcement. Here, measured at 1 Hz, the dynamic stiffnesses at 1 mm amplitude are regularly between 10 and 40% higher than at 25 mm amplitude.This is also referred to as a K1 / K25 ratio of 1.1 to 1.4.
[0012] The object of the invention is to improve upon the aforementioned prior art, in particular to create a vibration damper unit with a hydraulic base adjustment device, the rolling diaphragm of which is durable and cost-effective, requires minimal installation space, and exhibits a particularly low K1 / K25 ratio under dynamic loads, thus providing advantageous harshness. Furthermore, the vibration damper unit with hydraulic base adjustment device should not exhibit spring action.
[0013] Features of the invention are specified in claims 1 and 10. Embodiments are the subject of claims 2 to 9.
[0014] According to the invention, a vibration damper unit is proposed through which a bellows longitudinal axis projects, comprising a hydro foot point adjustment device and a hook spring element connected in series with the hydro foot point adjustment device, wherein the hydro foot point adjustment device comprises:
[0015] a hydro chamber which is filled or fillable with a liquid, and
[0016] a rolling diaphragm that limits the hydro chamber on its outer circumference,
[0017] - wherein the rolling bellows comprises a pair of fiber reinforcement layers,
[0018] - wherein the fiber reinforcement layer pair comprises a first fiber reinforcement layer and a second fiber reinforcement layer,
[0019] - wherein fibers of the two fiber reinforcement layers of the fiber reinforcement layer pair cross over each other, thereby forming a cross-layer reinforcement. The invention is based on the finding that the combination of a hydraulic base adjustment device with a series-connected hook spring element, while simultaneously using a bellows with a rolled fold (hence referred to as a rolling bellows) and cross-layers, solves the aforementioned problem. Surprisingly, it was found that the dynamic disadvantages of cross-layer bellows in a vibration damping unit do not come into play when the rolling bellows is filled with a liquid and connected in series with a hook spring element. The hook spring element optimizes the harshness of the vibration damping unit.
[0020] It was recognized that the harshness can be kept low despite the use of intersecting fibers in the bellows. In fact, the bellows, which can be described as a cross-layer bellows, surprisingly results in very low harshness in the hydraulic foot-point adjustment device, even though the rolled-fold cross-layer bellows, especially with large crossing angles, should theoretically worsen the harshness within the rolled fold.
[0021] It has also been recognized that large crossing angles, particularly in the roll fold, do not lead to the service life reductions known, for example, from air springs. This is due to the functional separation implemented in the invention between dynamic decoupling via the hook spring element and quasi-static height adjustment via the hydro-base adjustment device. The series connection and dynamic decoupling mean that the fluid-filled or fillable roll diaphragm does not have to perform a spring function. As a result, the crossing angle, as well as the outer diameter of the roll diaphragm, can remain constant on both sides of the roll fold during suspension by the hook spring element. The harshness is low.The dynamic hardening caused by the cross-layer reinforcement in the roll fold therefore plays no role in the harshness, nor does the flexing in the roll fold known from air springs with cross-layer bellows negatively affect the service life, since the roll fold hardly moves at all under the dynamic load induced by road excitation.
[0022] In contrast, conventional air-filled rolling bellows exhibit longitudinal flexion because air is compressible, unlike liquid. This flexion causes the rolling fold to shift, resulting in a constantly changing crossing angle. This leads to high harshness, or undesirable dynamic stiffening, at small amplitudes.
[0023] The vibration damper unit can be a strut. The strut can serve to suspend a vehicle and is positioned between the wheel carrier and the body. The hydro-adjustable base point includes a base point that is adjustable by the hydro-adjustable base point mechanism. The base point is the wheel carrier-side or body-side contact point of the hook spring element. The hydro-adjustable base point mechanism serves to adjust the distance between the wheel carrier and the wheel carrier-side contact point of the hook spring element and / or between the body and the body-side contact point of the hook spring element, independent of the suspension travel. By adjusting the hydro-adjustable base point mechanism, the distance between the body and the wheel carrier can be adjusted. The base point can directly or indirectly adjust a force application point into the hook spring element in the direction of the bellows' longitudinal axis.The longitudinal axis of a spring element can be identical to the longitudinal axis of the bellows or tilted relative to it.
[0024] The hydraulic base adjustment device comprises a first part and a second part. The first part can be a volume cover. The first part can axially limit the hydraulic chamber in a first axial direction. The second part can also be a volume cover. The second part can axially limit the hydraulic chamber in a second axial direction. The first and second axial directions can be opposite to each other, originating from the hydraulic chamber. The hydraulic chamber can be limited by the first part in the first axial direction, by the second part in the second axial direction, and by the rolling diaphragm on its outer circumference. The rolling diaphragm can be an outer diaphragm or the first diaphragm. On the inner circumference, another rolling diaphragm, an inner diaphragm, or a second diaphragm can be arranged. The hydraulic chamber can be rotationally symmetrical and also torus-shaped. The fluid in the hydraulic chamber can be an incompressible fluid.The fluid, particularly the incompressible fluid, serves to prevent the hydro-foot adjustment mechanism from springing back. The hydro-foot adjustment mechanism is suitable for the static adjustment of a foot point.
[0025] The hydraulic base adjustment device can include a rolling diaphragm, outer diaphragm, or first diaphragm on the outer circumference of the hydraulic chamber. The hydraulic base adjustment device can additionally include a rolling diaphragm, inner diaphragm, or second diaphragm on the inner circumference of the hydraulic chamber.
[0026] It is conceivable that one of the two parts has a receptacle for the Hook spring element, suitable for accommodating it. It is conceivable that the other of the two parts can be connected to a vehicle. It is conceivable that one of the two parts has a valve to the hydraulic chamber for introducing or releasing fluid into the hydraulic chamber.
[0027] The two parts are arranged and / or designed to be movable relative to each other, at least along the longitudinal axis of the bellows. One of the two parts may be movable relative to the other and / or guided by a guide. The two parts may be adjustable between a close-proximity position and a distance position. The two parts may be spaced apart from each other along the longitudinal axis of the bellows. The two parts may be arranged opposite each other along the central longitudinal axis, i.e., on two opposite sides of the hydraulic chamber. The distance between the two parts can be adjusted by the fill level of the hydraulic chamber – an increase in volume increases the distance, while a decrease in volume decreases the distance.The fluid present, or potentially present, in the hydraulic chamber prevents volume changes caused by external forces encountered in vehicles. The distance is adjusted by the movement of the rolling fold, not by a change in the diameter of the rolling diaphragm. Furthermore, the maximum and minimum distances between the two parts can be mechanically defined by end stops and / or sensors.
[0028] At least the rolling bellows, preferably the rolling bellows or outer bellows and the inner bellows, can be attached to the first part and the second part by forming a fastening there. The rolling bellows can be attached to the two parts separately from the inner bellows and vice versa. The rolling bellows can comprise an elastomeric base body in which the fiber reinforcement layers are embedded.
[0029] The two fiber reinforcement layers are separate from each other. The intersection of the fiber reinforcement layers is viewed radially. The fiber reinforcement layers are arranged one behind the other in the radial direction. The fibers within a fiber reinforcement layer can run in a directed direction, at least partially, preferably completely.
[0030] The Hookean spring element is designed to follow the linear spring law at its static operating point, i.e., for all loading conditions. The longitudinal axis of the bellows runs through the rolling diaphragm in the longitudinal direction. The length of the rolling diaphragm is adjusted along this longitudinal axis. The term "harshness" refers to a stiff spring behavior during oscillations of higher frequency and low amplitude.
[0031] The vibration damping unit can include at least one damping element, for example a jounce bumper and / or a damper.
[0032] The directional terms "radial," "radial direction," "axial," and "axial direction" refer to the longitudinal axis of the bellows. According to a possible further development, the rolling bellows has a roll-fold-captured area in which the cross-layer reinforcement is arranged. Thus, the layers can also cross within the roll-fold, thereby reducing manufacturing costs. The invention ensures that the cross-layer reinforcement in this area does not impair the service life. The roll-fold-captured area can be the region of the rolling bellows in which the roll-fold can form.
[0033] According to a further development of the vibration damping unit, the rolling diaphragm, preferably in the area captured by the roll folds, comprises exclusively a single pair of fiber reinforcement layers or several pairs of fiber reinforcement layers. Thus, no further fiber reinforcements are present in the rolling diaphragm or in the area captured by the roll folds. A single pair of fiber reinforcement layers can reduce costs, while several pairs of fiber reinforcement layers can increase robustness.
[0034] According to a further development of the vibration damper unit, the fiber reinforcement layers each comprise or are formed from a single layer of fabric. For example, if the rolling bellows is reinforced by means of a pair of fiber reinforcement layers, two layers of fabric are used. Accordingly, the number of fabric layers is always twice the number of fabric layer pairs. Fabric layers are cost-effective, so the laying of individual fibers can be omitted in the manufacturing process. Nevertheless, fabric layers enable the realization of the advantages of the invention.
[0035] Alternatively, the fiber reinforcement layer pairs can also be formed from individually laid fibers. Such individually laid fibers can be positioned with particular precision. This results in especially uniform bellows properties, and in particular a long service life. Within a fiber reinforcement layer pair, the individually laid fibers can run parallel to each other.
[0036] According to a possible further development of the vibration damper unit, the bellows can form an outer section, a rolled fold, and an inner section. The rolled fold can be arranged along the bellows between the sections. The outer section, the rolled fold, and the inner section can connect directly to one another. The outer section can be arranged radially outside the rolled fold. The inner section can be arranged radially inside the rolled fold. The inner section can abut a part, preferably the first part, preferably on the outer circumferential side of the part. The rolled fold allows the bellows to change its length longitudinally. The bellows achieves height adjustment by means of the rolled fold.
[0037] The bellows can have a second stationary fold. This fold can project inwards radially. The bellows can be clamped on the inwards radially projecting stationary inner section of the fold. Such a second stationary fold can be advantageous for bellows assembly and for the robustness of the clamping. The stationary fold can rest against either of the two parts.
[0038] According to a possible further development of the vibration damper unit, the diameter of the outer section can be constant, at least in certain areas, preferably completely. The rolling diaphragm can therefore have a cylindrical shape, at least in certain areas. This constantness can be permanent. The diameter can be constant during operation. Thus, the diameter can remain constant regardless of the operating state of the vibration damper unit and / or the hydraulic base adjustment device. The constant diameter can be achieved through design. The vibration damper unit can include an outer guide against which the outer section can rest, and / or an arrangement of the fiber reinforcement layer pairs in the outer section forming a crossing angle in the range of 59° to 66°, preferably 61° to 66°, and more preferably 63°. This crossing angle can be referred to as the limiting angle.The crossing angle can reach its maximum when the bellows expands, especially without external guides, as the internal pressure increases. It is conceivable that the vibration damping unit could be designed without external guides. The aforementioned crossing angle can asymptotically approach the limiting angle as the internal pressure increases.
[0039] According to a possible further development of the vibration damper unit, the outer section can be cylindrical. This allows the vibration damper unit to be used in confined installation spaces, as the height adjustment is achieved via the rolled fold and not by a bulging of the rolling bellows.
[0040] According to a possible further development of the vibration damper unit, the rolling diaphragm can be fixed in place at both ends, in particular clamped, preferably exclusively clamped. It can be fixed in place at the first part and the second part. The robust rolling diaphragm according to the invention can withstand tensile stresses without sustaining damage. The vibration damper unit can be free of an axial end stop for the rolling diaphragm. The fixed position can form a diaphragm attachment. According to a further development of the vibration damper unit, the wall thickness of the rolling diaphragm can be between 2 mm and 3 mm, preferably between 2.2 mm and 2.8 mm. The rolling diaphragm can have this wall thickness in the area covered by the roll fold. Such a wall thickness provides sufficient flexibility for the roll fold to form and change its position.Thus, if the position of the rolled diaphragm changes, the diameter of the area covered by the rolled diaphragm can easily change between the diameter in the outer section and the diameter in the inner section. The rolled diaphragm can have a constant wall thickness.
[0041] The rolling diaphragm may have a textured surface on its side facing away from the liquid. Furthermore, the rolling diaphragm may have a greater wall thickness or a bead in the area of fixed fixation than outside this area. Such a bead can provide additional positive locking of the clamping fit, thus making the clamping more robust. The constant wall thickness can only be present in the outer section, the rolled fold, the fold, and / or the inner section(s), and does not include any textures or structures. Therefore, a rolling diaphragm with a texture / structure and / or two clamping beads is also to be understood as a rolling diaphragm with a constant wall thickness within the meaning of the disclosure.
[0042] According to a further development of the vibration damping unit, the crossing angle between the crossed fibers or fabric layers of the two fiber reinforcement layers of the fiber reinforcement layer pair in an inner section of the bellows, preferably in a cylindrical inner section, can be between 30° and 90°, more preferably between 30° and 50°. The inner section can be the inner section described above. Such crossing angles are easy to manufacture and therefore cost-effective. Furthermore, they allow the rolled fold to unroll easily. It is conceivable that the angle bisector extends parallel to the longitudinal axis of the bellows.
[0043] According to a further development of the vibration damper unit, it can be designed and / or arranged such that a change in the distance along the longitudinal axis of the bellows between a first bellows attachment and a second bellows attachment by a certain distance results in a displacement of a roll fold contact point by half that distance. The distance can be a defined distance. The displacement can occur along the longitudinal axis of the bellows. The displacement can be caused by a quasi-static volume change in the hydro chamber. The distance can be a longitudinal distance. The longitudinal distance can run parallel to the longitudinal axis of the bellows. The roll fold contact point can be the boundary between the roll fold and the inner section. Alternatively or additionally, the roll fold contact point can be the boundary between a bellows section that is in contact and a bellows section that is not in contact or is free.The point on the bellows where it lifts off its inner-circumferential mounting can be the roll fold contact point. A change in the distance of the bellows mounting by a certain distance can lead to a corresponding shift in the contact point of the hook spring element, for example, a coil spring. If the roll fold contact point changes by half that distance, this means that the movement occurs exclusively in a single roll fold. This results in an overall robust vibration damping unit.
[0044] According to a further development of the vibration damper unit, the hydraulic base adjustment device can have a stiffness that is at least 10 times, preferably at least 50 times, greater than the stiffness of the series-connected hook spring element. Since the stiffness of the base adjustment device can change slightly depending on the operating position, particularly when the base adjustment device is extended or retracted to such an extent that mechanical end stops engage, the stiffness of the base adjustment device should be understood as being relative to the mean operating position, i.e., the position corresponding to half of the maximum adjustment travel. Furthermore, the stiffnesses of the hook spring element and the base adjustment device to be compared in the direction of the bellows' longitudinal axis should be used to clearly define the reference direction.Because the stiffness of the hook spring element is significantly lower than that of the foot-adjustment device, the spring movements of the strut induced by road surface excitation occur primarily within the hook spring element, while the spring movements within the foot-adjustment device are negligible. Surprisingly, this results in a vibration damper unit according to the invention exhibiting a particularly advantageous, low harshness despite the use of a cross-layer bellows in the hydro foot-adjustment device, provided that the hydro foot-adjustment device is at least ten times, preferably at least 50 times, stiffer than the hook spring element.
[0045] According to a further development, the dynamic stiffness of the vibration damper unit, measured at 1 Hz and an amplitude of 1 mm, can be at most 5% higher, preferably at most 2% higher, and particularly preferably at most 1% higher, than the dynamic stiffness of the vibration damper unit measured at 1 Hz and an amplitude of 25 mm. This K1 / K25 ratio has the surprising advantage that, despite the use of a cross-layer bellows in the vibration damper unit, the rolling diaphragm contributes almost no to the dynamic stiffness of the vibration damper unit. Rather, to a first approximation, the entire spring travel takes place within the Hooke spring element.However, since breakaway torques, such as those observed in ball joints and dampers, also exhibit amplitude dependence, it can be advantageous to limit the dynamic stiffness measurements according to the invention to the series-connected foot-point adjustment device and the Hook spring element, and not to include other components, such as the damper, in the measurements. The measured stiffness of the vibration damper unit can then be based solely on the foot-point adjustment device and the Hook spring element.
[0046] According to a further development, the vibration damper unit can include an external guide for the rolling diaphragm or be designed without an external guide. The external guide ensures a constant outer diameter for the outer section. The outer section can rest against the inner circumference of the external guide. However, if an external guide is omitted, an advantageous crossing angle in the outer section, as explained above, can be present. If an external guide is used, significantly higher fluid pressures can be employed, resulting in a more compact design.
[0047] According to a possible further development of the vibration damper unit, the Hookean spring element can be a coil spring, a steel leaf spring, or a fiber-reinforced composite leaf spring. A steel leaf spring is highly resilient and exhibits inherent damping due to internal friction. A fiber-reinforced composite leaf spring is corrosion-resistant and possesses inherent damping properties that effectively absorb vibrations and shocks.
[0048] According to a possible further development of the vibration damping unit, the cross-layer reinforcement can be arranged in the inner section of the roll fold and / or in the inner section of the fold, and in the outer section, preferably continuously. This can reduce manufacturing costs. Alternatively, it is possible to apply additional fiber reinforcement layer pairs only locally in order to reinforce defined areas locally.
[0049] According to a possible further development of the vibration damper unit, the rolling diaphragm can comprise a first elastomer layer or inner elastomer layer and / or a second elastomer layer or outer elastomer layer. A third elastomer layer or elastomer intermediate layer can be arranged between these two elastomer layers, preferably a single third elastomer layer. The first elastomer layer or inner elastomer layer and / or the second elastomer layer or outer elastomer layer can be arranged directly adjacent to the third elastomer layer or elastomer intermediate layer. The first elastomer layer or inner elastomer layer can face the hydro chamber and / or be hydro exposed. The second elastomer layer or outer elastomer layer can face away from the hydro chamber.The third elastomer layer or elastomer interlayer serves to connect the first elastomer layer or inner elastomer layer to the second elastomer layer or outer elastomer layer in a cost-effective manner. According to a possible further development of the vibration damper unit, the first fiber reinforcement layer can be arranged between the first elastomer layer or inner elastomer layer and the third elastomer layer or elastomer interlayer, or in the interface between the first elastomer layer or inner elastomer layer and the third elastomer layer or elastomer interlayer. The first fiber reinforcement layer can contact the first elastomer layer or inner elastomer layer and the third elastomer layer or elastomer interlayer. This serves to connect the first elastomer layer or inner elastomer layer to the third elastomer layer or elastomer interlayer in a cost-effective manner.This applies in particular if the first fiber reinforcement layer is located on the surface of the first elastomer layer or inner elastomer layer.
[0050] According to a possible further development of the vibration damper unit, the second fiber reinforcement layer can be arranged between the second elastomer layer or outer elastomer layer and the third elastomer layer or intermediate elastomer layer, or in the interface between the second elastomer layer or outer elastomer layer and the third elastomer layer or intermediate elastomer layer. The second fiber reinforcement layer can contact the second elastomer layer or inner elastomer layer and the third elastomer layer or intermediate elastomer layer. This serves as a cost-effective connection between the second elastomer layer or inner elastomer layer and the third elastomer layer or intermediate elastomer layer. This applies particularly if the second fiber reinforcement layer is arranged on the surface of the second elastomer layer or outer elastomer layer.
[0051] According to a possible further development of the vibration damper unit, a third elastomer layer or elastomer interlayer can be arranged between adjacent fiber reinforcement layers that together form a fiber reinforcement layer pair. Preferably, a third elastomer layer or elastomer interlayer is arranged between all fiber reinforcement layers that together form a fiber reinforcement layer pair. This arrangement of the third elastomer layer or elastomer interlayer serves to produce a bellows with elastomer layers encompassing more than two fiber reinforcement layers.
[0052] According to the invention, the use of a rolling bellows in a vibration damper unit for the outer circumferential limitation of a fluid-filled or fillable hydro chamber of a hydro foot point adjustment device is also proposed.
[0053] - wherein the rolling bellows comprises a pair of fiber reinforcement layers,
[0054] - wherein the fiber reinforcement layer pair comprises a first fiber reinforcement layer and a second fiber reinforcement layer,- wherein fibers of the two fiber reinforcement layers cross over each other, thereby forming a cross-layer reinforcement
[0055] - wherein the hydro foot point adjustment device is connected in series with a hook spring element.
[0056] The rolling diaphragm, the vibration damping unit, and the hydraulic base adjustment device can be designed as disclosed. Regarding its use, the advantages already described for the vibration damping unit apply, to which reference is hereby made.
[0057] Further features, details and advantages of the invention will become apparent from the wording of the claims and from the following description of exemplary embodiments with reference to the drawings. The drawings show:
[0058] Fig. 1 shows a longitudinal sectional view of a vibration damper unit,
[0059] Fig. 2 shows a longitudinal sectional view of another vibration damper unit,
[0060] Fig. 3 shows a cross-layer reinforcement,
[0061] Fig. 4 shows a sectional view of line IV-IV from Fig. 3.
[0062] Fig. 5a shows a schematic representation of an operating state of the vibration damper unit and Fig. 5b shows a schematic representation of another operating state of the vibration damper unit.
[0063] In the figures, identical or corresponding elements are designated with the same reference numerals and are therefore not described again unless expedient. Features already described are not described again to avoid repetition and are applicable to all elements with the same or corresponding reference numerals, unless explicitly excluded. The disclosures contained in the entire description are transferable analogously to identical parts with the same reference numerals or component designations. Furthermore, the positional designations chosen in the description, such as top, bottom, side, etc., refer to the directly described and illustrated figure and must be applied analogously to any new position.Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions.
[0064] Figure 1 shows a vibration damper unit 100. The vibration damper unit 100 comprises a hydraulic base adjustment device 200 and a Hooke's spring element in the form of a helical spring 102. The Hooke's spring element and the hydraulic base adjustment device 200 are connected in series. The hydraulic base adjustment device 200 comprises a toroidal hydraulic chamber 202, which is filled with a liquid, the volume of which can be selectively changed by introducing and draining the liquid. On its outer circumference, the hydraulic chamber 202 is bounded by a rolling diaphragm 300, which can be referred to as the outer diaphragm. A longitudinal axis L of the diaphragm projects through the rolling diaphragm 300. A radial axis R extends perpendicular to this axis. On its inner circumference, the hydraulic chamber 202 is bounded by another rolling diaphragm 301, which can be referred to as the inner diaphragm. Along the longitudinal axis L of the bellows, the hydro chamber 202 is axially bounded by a first part 204.In the axially opposite direction, the hydraulic chamber 202 is bounded by a second part 206. The second part 206 is a volume cover and is adjustable along the longitudinal axis L of the bellows by changing the volume of the hydraulic chamber 202. The second part 206 has a receptacle 208 with a support point (base point) for the Hook spring element.
[0065] The two parts 204, 206 are arranged and designed to be movable relative to each other, at least along the longitudinal axis L of the bellows. The second part 206 is guided on the first part 204 and / or on a damper 104 by means of a guide. The two parts 204, 206 are adjustable between a close-proximity position and a distance position. The rolling bellows 300, 301 extend separately between the two parts 204, 206, forming attachments there. The rolling bellows 300 is attached to the first part 204 by means of a first bellows attachment 314 and to the second part 206 by means of a second bellows attachment 316. The attachments 314, 316 can be clamps. The attachments 314, 316 have a longitudinal distance X from each other in the longitudinal direction parallel to the longitudinal axis L of the bellows.
[0066] The bellows 300 forms an outer section 308, a roll fold 310, and an inner section 312, which are directly adjacent to one another. The outer section 308 is arranged radially R outside the roll fold 310, while the inner section 312 is arranged radially R inside the roll fold 310. In this case, the outer section 308 is cylindrical and has a constant diameter. The bellows 300 has a roll-fold-captured area 320, which is the area of the bellows 300 in which the roll fold 310 can form. The inner section 312 rests against the outer circumference of the first part 204. The point on the bellows 300 where it lifts off from its inner circumferential mounting is a roll fold attachment point 318. The roll fold attachment point 318 is the boundary between the roll fold 310 and the inner section 312.It is evident that the inner section 312 is in contact and the roll fold 310 is not in contact or is free.
[0067] The rolling bellows 300 further forms a stationary fold 313 with an inwardly radially projecting inner section 322. The fold 313 is directed inwards and rests against the second part 206. The vibration damper unit 100 comprises a support element 106 for the hook spring element, which can be a strut tower. The hook spring element is therefore supported at one end by the support element 106 and at the other end by the second part 206. A longitudinal axis of the spring element projects through the hook spring element, which in the illustrated embodiment is congruent with the longitudinal axis L of the bellows; however, the axes do not necessarily have to coincide. The vibration damper unit 100 comprises a first damping element in the form of a damper 104. A second damping element in the form of a jounce bumper 108 is arranged on the support element 106. The Jouncebumper 108 limits the travel of the damper 104.
[0068] The vibration damping unit 100 is designed without external guides; therefore, it has no external guide for the rolling diaphragm 300. Furthermore, the vibration damping unit 100 is free of an axial end stop for the rolling diaphragm 300.
[0069] To avoid repetition, only the differences between Figure 2 and Figure 1 will be described below. Features already described but not repeated here shall be deemed to be disclosed and described. The vibration damper unit 100 comprises an outer guide 210 for the rolling diaphragm 300. The outer guide 210 is formed by the second part 206. The rolling diaphragm 300 can bear against the inner circumference of the outer guide 210 with its outer section 308.
[0070] Figure 3 shows a schematic side view of a cross-ply reinforcement of the previously described bellows 300. The bellows 300 comprises two fiber reinforcement layers 304, 306, which form a fiber reinforcement layer pair 303. The fiber reinforcement layers 304, 306 are each formed from a single layer of fabric; alternatively, they can consist of individually laid fibers. For clarity, only the weft threads are shown schematically here. In the roll-folded area 320, the bellows 300 comprises only a single fiber reinforcement layer pair 303. The cross-ply reinforcement is arranged in the inner section 312, in the roll fold 310, and in the outer section 308, preferably continuously.
[0071] The fibers of the two fiber reinforcement layers 304, 306 intersect, thereby forming the cross-layer reinforcement. The two fiber reinforcement layers 304, 306 are separate layers from each other, and their intersection is viewed in the radial direction R. The fiber reinforcement layers 304, 306 are arranged one behind the other in the radial direction R. A crossing angle W1 is formed between the crossed fibers or fabric layers of the two fiber reinforcement layers 304, 306, with this angle being between 30° and 90°. The bisector Wh of the crossing angle W1 extends parallel to the longitudinal axis L of the bellows. In the outer section 308, the crossing angle W1 is larger than in the inner section 312.
[0072] Figure 4 shows that the fiber reinforcement layers 304, 306 are embedded in an elastomeric base body 302 of the rolling bellows 300. The wall thickness S of the rolling bellows 300 can be between 2 mm and 3 mm and is constant. The rolling bellows 300 has an elastomeric intermediate layer 326 between the fiber reinforcement layers 304, 306. The elastomeric intermediate layer 326 can be arranged between all fiber reinforcement layers 304, 306 that together form a fiber reinforcement layer pair 303. If several fiber reinforcement layer pairs 303 are used, an elastomeric intermediate layer 326 can also be arranged between adjacent fiber reinforcement layer pairs 303. In addition, the rolling bellows 300 is formed on the fluid side by an inner elastomer layer 324, and on the fluid-free side by an outer elastomer layer 328.
[0073] Figures 5a and 5b schematically illustrate two operating states of the hydraulic base adjustment device 200. In Figure 5a, the volume of the hydraulic chamber 202 is smaller than in Figure 5b. As the volume in the hydraulic chamber 202 increases, the second part 206 is adjusted, thereby increasing the longitudinal distance X by the adjusted distance D. This also results in a change in position or migration of the roll fold 310 and the roll fold attachment point 318. A change in the longitudinal distance X between the bellows attachments 314, 316 by the distance D leads to a displacement of the roll fold attachment point 318 by half the distance D / 2. Although Figures 5a and 5b show the increase in volume, in the case of a decrease in volume, the displacement occurs such that the longitudinal distance X is shortened by the distance D and the roll fold attachment point 318 is displaced by half the distance D / 2.
[0074] The figures further show the use of the cross-layer reinforced rolling bellows 300 in a vibration damper unit 100 for the outer circumferential limitation of the fluid-filled hydro chamber 202 of a hydro foot point adjustment device 200, wherein the hydro foot point adjustment device 200 is connected in series with the hook spring element.
[0075] The invention is not limited to one of the embodiments described above, but can be modified in a variety of ways. All features and advantages arising from the claims, the description, and the drawings, including design details, spatial arrangements, and process steps, can be essential to the invention both individually and in various combinations. The scope of the invention includes all combinations of at least two of the features disclosed in the description, the claims, and / or the figures.
[0076] To avoid repetition, features disclosed by the device shall also be deemed disclosed by the process and be claimable. Likewise, features disclosed by the process shall be deemed disclosed by the device and be claimable. Reference numerals list
[0077] 100 vibration damper units
[0078] 102 coil spring
[0079] 104 dampers
[0080] 106 Support element
[0081] 108 Jouncebumper
[0082] 200 Hydro foot point adjustment device
[0083] 202 Hydro chamber
[0084] 204 first part
[0085] 206 Part Two
[0086] 208 recording
[0087] 210 Exterior
[0088] 300 Rollbelg
[0089] 301 Roll diaphragm
[0090] 302 Basic body
[0091] 303 fiber reinforcement layers pair
[0092] 304 first fiber reinforcement layer
[0093] 306 second fiber reinforcement layer
[0094] 308 Outer section
[0095] 310 roll fold
[0096] 312 Interior section
[0097] 313 folds
[0098] 314 first bellows attachment
[0099] 316 second bellows attachment
[0100] 318 Roll fold attachment point
[0101] 320 roll fold-captured area
[0102] 322 Interior section
[0103] 324 Inner elastomer layer
[0104] 326 Interelastomer layer
[0105] 328 Outer elastomer layer
[0106] D distance
[0107] D / 2 half distance
[0108] L Bellows longitudinal axis
[0109] R Radial direction
[0110] S wall thickness
[0111] Wh Angle bisector
[0112] W1 Crossing angle
[0113] W1 / 2 half crossing angle
[0114] X Longitudinal distance
Claims
Patent claims 1. Vibration damper unit (100) through which a bellows longitudinal axis (L) projects, comprising a hydro-base adjustment device (200) and a hook spring element connected in series with the hydro-base adjustment device (200), wherein the hydro-base adjustment device (200) comprises: a hydro chamber (202) which is filled or fillable with a liquid, and a rolling diaphragm (300) which delimits the hydro chamber (202) on its outer circumference, - wherein the rolling diaphragm (300) comprises a pair of fiber reinforcement layers (303), - wherein the fiber reinforcement layer pair (303) comprises a first fiber reinforcement layer (304) and a second fiber reinforcement layer (306), - wherein fibers of the two fiber reinforcement layers (304, 306) of the fiber reinforcement layer pair (303) cross over each other and thereby form a cross-layer reinforcement.
2. Vibration damping unit (100) according to claim 1, characterized in that the rolling diaphragm (300), preferably in the roll-fold-captured area, comprises exclusively a single fiber reinforcement layer pair (303) or several fiber reinforcement layer pairs (303).
3. Vibration damping unit (100) according to claim 1 or 2, characterized in that the fiber reinforcement layers (304, 306) each comprise or are formed from a layer of fabric.
4. Vibration damping unit (100) according to one of the preceding claims, characterized in that the wall thickness (S) of the rolling bellows (300) is between 2 mm and 3 mm, preferably between 2.2 mm and 2.8 mm.
5. Vibration damping unit (100) according to one of the preceding claims, characterized in that a crossing angle (W1) between the crossed fibers or fabric layers of the two fiber reinforcement layers (304, 306) of the fiber reinforcement layer pair (303) in an inner section (312), preferably in a cylindrical inner section, is between 30° and 90°.
6. Vibration damping unit (100) according to one of the preceding claims, characterized in that a change in the distance along the longitudinal axis (L) of the bellows between a first bellows attachment (314) and a second bellows attachment (316) by a distance (D) leads to a displacement of a roll fold attachment point (318) by half the distance (D / 2).
7. Vibration damping unit (100) according to one of the preceding claims, characterized in that the hydro foot point adjustment device (200) has a stiffness that is at least by a factor of 10, preferably at least by a factor of 50, greater than the stiffness of the hook spring element connected in series.
8. Vibration damping unit (100) according to one of the preceding claims, characterized in that its dynamic stiffness measured at 1 Hz and an amplitude of 1 mm is at most 5% higher, preferably at most 2% higher, particularly preferably at most 1% higher, than its dynamic stiffness measured at 1 Hz and an amplitude of 25 mm.
9. Vibration damping unit (100) according to one of the preceding claims, characterized in that it comprises an external guide (210) for the rolling diaphragm (300), or is designed without an external guide.
10. Use of a rolling bellows (300) in a vibration damping unit (100) for the outer circumferential limitation of a fluid-filled or fillable hydraulic chamber (202) of a hydraulic base adjustment device (200), - wherein the rolling bellows (300) comprises a pair of fiber reinforcement layers (303), - wherein the fiber reinforcement layer pair (303) comprises a first fiber reinforcement layer (304) and a second fiber reinforcement layer (306), - wherein fibers of the two fiber reinforcement layers (304, 306) cross over each other and thereby form a cross-layer reinforcement, - wherein the hydro foot point adjustment device (200) is connected in series with a hook spring element.