EP2247457A1

EP2247457A1 - Oscillating fluid damping and/or suspension

Info

Publication number: EP2247457A1
Application number: EP09707474A
Authority: EP
Inventors: Peter Pelz; Jens RÖSNER
Original assignee: Technische Universitaet Darmstadt
Current assignee: Technische Universitaet Darmstadt
Priority date: 2008-02-05
Filing date: 2009-02-05
Publication date: 2010-11-10
Also published as: DE102008007566A1; DE102008007566B4; WO2009098064A1

Abstract

The invention relates to an oscillating fluid damping and/or suspension for a vehicle, wherein an oscillation load can be introduced into said damping or suspension and has an operating piston, the effective surface of which can be increased and/or decreased for varying a fluid damping and/or suspension force counter-acting the oscillation load. The invention provides that an electrically operated actuator is disposed on the operating piston in order to shift a movable exterior side of the operating piston such that the effective surface is expanded and/or reduced.

Description

Vibration fluid damping and / or suspension

The invention relates to a vibration fluid damping and / or suspension in particular for vehicles, such as motor vehicles, such as bicycles, motorcycles, automobiles, etc. In addition, the invention may also relate to vibration bearings that can be used for example in construction, especially in bridges or in laboratory technology.

In the fields of application, the vibration load applied to the vibration fluid damping and / or suspension often does not remain constant, but may change depending on the operating condition. In the past, spring damping systems have been developed which can provide a changing spring / damping characteristic. A distinction is made between a passive spring characteristic change and an active spring characteristic change.

A passive spring damping characteristic change may be formed, for example, by using a piston-cylinder arrangement, the piston having a conical outside. When the piston is displaced axially, the effective radial effective area of the displacement piston changes due to the conicity, whereby the spring / damping characteristic curve changes directly in proportion to the travel of the piston in the course of the axial stroke of the piston. An example of such a conical piston structure is known from EP 1 541 386 A1.

DE 199 52 799 A1 discloses a so-called tandem piston, in which two operating piston heads, each rigidly coupled to one another in the direction of damping and / or suspension, are used, each with one active surface. The working piston heads each have a conical longitudinal outside, whereby the passive Federdämpfungskennlinienände- tion is provided. The effective total effective area of the vibration fluid damping and / or suspension according to DE 199 52 799 A1 is defined by the difference between the respective effective areas of the piston head pair.

- 64.302 - A spring-damping system with the possibility of an active change of the spring damping characteristic, that is, for example, depending on the driving conditions of a motor vehicle and independent of the travel of the working piston, is known from DE 41 35 900 C2. The desired spring damping characteristic is adjusted by radially displacing a movable piston wall of the working piston to thereby increase the effective effective area of the rolling piston on which a rolling bellows is mounted. The extension of the outer side of the rolling piston is achieved in that in a duct system in the working piston, a pneumatic control pressure is generated, which causes the displacement of the piston longitudinal outer wall forming fins.

It has been found that because of the compressibility of the actuating pneumatics, the active change in the spring damping characteristic curves in the response to dynamic oscillatory loads on a time scale of the oscillation period of the system can often only be realized insufficiently. The known systems are too slow.

It is an object of the invention to overcome the disadvantages of the prior art, in particular to provide vibration fluid damping and / or suspension, especially for vehicles, with an active damping spring characteristic change depending on the driving conditions of the motor vehicle on a time scale of the oscillation period of the system can be achieved ,

This object is solved by the features of claim 1. Thereafter, a vibration fluid damping and / or spring is provided in particular for a vehicle, wherein a vibration load should be introduced into the vibration fluid damping and / or suspension. The vibration fluid damping and / or suspension has a working piston whose effective surface can be increased and / or reduced in size for changing a fluid damper and / or spring force counteracting the vibration load. According to the invention, an electrically operated actuator is arranged on the working piston in order to displace a movable outer side of the working piston, in particular radially, so that the effective surface is widened and / or limited or reduced. Electromotive actuators, such as electrically operated worm gears, can be used as the electrically operated actuator. Particularly preferred are piezoelectric actuators, as described below. With the measure according to the invention, in the exemplary application in motor vehicles, the spring damping characteristic of a suspension strut can be adapted on a time scale to the vibration duration of the vibration load. In this way, a higher load can be supported by the strut with unchanged strut length. By electrically operating the actuator shortest control cycles can be maintained. In this way, an active strut characteristic change is achieved by energy is introduced into the spring damping system to calm it targeted, the shock absorber remains cost-effective in its manufacture and it does not require a presetting of the strut length.

The invention particularly relates to a hydropneumatic spring damper leg which can be adjusted adaptively. In general, a spring damper strut is not an exclusive damping system but also a system for transferring bearing forces of two mutually movable components, such as wheel axle and body. Thus, the invention also relates to a Schwingungsfluiddämpfungs- and suspension system, are to be transferred to the carrying forces via a working or support piston between a force input side and Kraftaustrags- side of the system, especially in a strut between the wheel axle and the body. Due to the variability of the effective surface of the working or supporting piston, the load capacity of the Schwingungsdämpfungs- and suspension system, in particular the shock absorber, can be adjusted.

In a preferred embodiment of the invention, the actuator is housed in a cavity of a piston rod or attached to the outside thereof. In this way, a particularly space-saving design can be achieved. The maintenance of the system is reduced due to the sheltered housing in the cavity of the piston rod.

Preferably, the working piston is designed as a rolling piston, wherein a flexible Abrollbalg forming a Abrollfalte is attached to the movable outer side. The effective effective area of the rolling piston is defined by the radial surface components exposed to a working fluid. In hydraulic spring damping systems particularly electrorheological fluids have proven their viscosity is variable by the application of an electric field.

In a preferred embodiment of the invention, the movable outer side of the rolling piston is formed by a roll-up sleeve whose peripheral ends overlap. By the rollable sleeve structure is provided with a relatively stable structure that allows for a targeted concentric expansion of the movable outer surface of the rolling piston. Preferably, an overlap of the circumferential ends of the sleeve remains even at maximum expansion of the movable outer side.

In an alternative embodiment of the invention, the movable outer side of the rolling piston is formed by a plurality of separate, substantially concentric sleeve sections arranged one another. The sleeve sections are coupled for their radial displacement to the electrically driven actuator. When attaching the Abrollbalgs on the outside of the sleeve sections additional circumferential folds are provided for the Abrollbalg so that when expanding the sleeve sections of the rolling bellows is not claimed to train and a fluid-tight working chamber is guaranteed.

In a further development of the invention, the movable outer side of the rolling piston is formed by a plurality of aligned in damping and / or suspension longitudinal direction slats, which are radially displaceable by the actuator and are arranged in a radially extended state at a circumferential distance from each other.

In a preferred embodiment of the invention, at least one piezoelectric component of the actuator has a predetermined largest extension longitudinal direction. Upon expansion or contraction of the component, it cooperates with a transmission gear structure such that an expansion or shrinkage amplitude of the component is gear-converted into an enlarged or reduced radial adjustment amplitude to adjust the effective effective area accordingly. In this way, in particular the usually small piezoelectric movement amplitudes can be amplified in order to achieve the desired effective surface adaptation.

In a preferred embodiment of the invention, the component is housed in a substantially completely surrounding the component container, which is formed by two in the extension longitudinally apart movable rigid shell parts, in particular half shells. Between a substantially parallel to the extension longitudinal direction extending longitudinal side of the component and one of the longitudinal side facing inner longitudinal side of the container, a free space is provided which serves to compensate for radial expansions of the e- lektrisierten piezoelectric material. Preferably, the component and at least an inside of the container complementary in shape cylindrical, wherein an outer diameter of the component is smaller than the diameter of the inner side to provide the compensation clearance.

Preferably, a longitudinal extent of the component is greater than a longitudinal extent of adjacent shell parts in the expansion longitudinal direction.

Preferably, the piezoelectric component is formed by a stack of stacked disks of piezoelectric material, wherein the extension longitudinal direction corresponds to the stacking direction. In this way, a strong expansion of the stack in a certain direction is provided.

In a preferred embodiment of the invention, the transmission gear structure has an elastically deformable displacement body, the shape of which, when deformed by the component, causes a gearbox-reinforced radial movement. In this case, the displacement of a body surrounding the displacement body, rigid, axially directed constriction be assigned such that upon expansion of the component of the displacement body is urged radially into the constriction. It is the constriction that causes the transmission translation corresponding diverting magnification of Stellstellungsungs amplitude of the piezoelectric material.

Preferably, the extension longitudinal direction of the piezoelectric component is parallel to the damping and / or suspension longitudinal direction.

In a preferred embodiment of the invention, the component is accommodated in a cavity of a piston rod, wherein the piezoelectric component is supported on the one hand on a rigid inner surface on the other hand on the deformable displacement body.

In a further development of the invention, at least one radially extending adjusting pin, which is connected to a movable outer side of the working piston, is guided at a radial outer end of the displacement body, in particular at the radial height of the constriction. In a preferred embodiment of the invention, the electrically operated actuator is formed by at least one ring structure, preferably two mutually parallel ring structures, which has a plurality of piezoelectric components. The extension longitudinal direction of the piezoelectric components is aligned substantially in the circumferential direction of the ring structure. The piezoelectric components are accommodated in an elastically deformable, annular jacket. In this way, a plurality of electrical components can be used, which can lead to a relatively large radial Stellbewegungsamplitude. Preferably, the ring structure may be supported on a piston rod mounted around the latter.

In an independent and combinable with the above-described vibration fluid damping and / or suspension aspect of the invention, a tandem piston 31 is provided with two in the damping and / or suspension longitudinal direction one behind the other, rigidly coupled together working heads, each having an effective area. An effective total effective area of the vibration fluid damping and / or suspension is defined by the difference of the effective area of the piston heads. According to the invention, the effective area of one or both of the piston heads for varying a fluid damper and / or spring force counteracting the vibration load is variable in response to the vibration load according to their time scale.

In another independent or combinable with the abovementioned Erfindunsgegenständen aspect of the invention, a Schwingungsfluiddämpfung- and / or - suspension is provided in which one of the outer sides of the working piston, preferably a substantially axial longitudinal side of the working piston, with respect to the damping and / or - Spring longitudinal direction can be inclined to form a taper, wherein the degree of inclination of the outside is adjustable. Preferably, the outside has an umbrella-shaped construction.

In development of the invention, the outside is formed by a plurality of pivotable, hinged to a support of the working piston slats. On the outside of the slats, a rolling bellows for the formation of a fluid-tight working space is attached.

Preferably, the actuator, which is arranged between a piston rod and the slats, the inclination of the slats. In this case, the actuator can be a Schwenkge- be assigned steering of the slats. Preferably, the electrically operated actuator is connected to a control and / or regulating device.

Further features, advantages and features of the invention will become apparent from the following description of a preferred embodiment of the inventors with reference to the accompanying drawings, in which:

FIG. 1 shows a schematic cross-sectional view of a hydropneumatic suspension strut with a single-piston construction;

FIG. 2 shows a schematic cross-sectional view of a hydropneumatic suspension strut in a further embodiment with a tandem piston;

3a and 3b show a plan view of a rolling piston in a limited operating state or a widened operating state;

FIGS. 4a and 4b show a top view of a radially expandable outer jacket of a rolling piston in a retracted operating state or in a widened operating state;

Figure 5 is a partially cutaway, perspective view of a piezoelectric actuator for changing the effective area of a rolling piston;

Figure 6 is a plan view of the actuator according to Figure 5;

FIG. 7 shows a cross-sectional view along the section line VII-VII according to FIG. 6;

Figure 8 is a partially cut-away perspective view of a piezoelectric component suitable for an actuator for varying the effective area of a rolling piston; 9 shows a side view of the piezoelectric component according to FIG

FIG. 8;

FIG. 10 shows a cross-sectional view of the piezoelectric component along the section line X-X in FIG. 9;

Figures I Ia and I Ib schematic cross-sectional views of a piezoelectric

Component group for forming an actuator, which is arranged concentrically to the piston rod and is shown in a limited operating state or a widened operating state;

Figure 12 is a partially cutaway perspective view of a

Rolling piston with a tiltable axial longitudinal side, which is shown in a tilt-free state;

FIG. 13 a cross-sectional view of the rolling piston according to FIG. 12;

Figure 14 is a partially cutaway, perspective view of the piston according to Figures 12 and 13, wherein the longitudinal side is inclined relative to the axial longitudinal axis; and

FIG. 15 shows a cross-sectional view of the rolling piston according to FIG. 14.

In Figure 1, a hydropneumatic strut for a motor vehicle according to the invention is generally provided with the reference numeral 1. The strut 1 has a body-side and a wheel-side terminal 3, 5. The strut 1 also includes a displaceable in an axial spring / damping direction F single piston 7, which is housed within a cylindrical body-side closed housing 9 concentrically. The vibration load-side terminal 5 is fixed to the single piston 7.

A part of the outside of the individual piston 7, an inner side 13 of the cylindrical housing 9 and a rolling bellows 15 connecting an outer longitudinal side 11 of the individual piston 7 with the inner longitudinal side of the cylindrical housing 9 delimit a closed hydraulic armature. Chamber of 17, to the Dissipationskanäle 21 a surge tank 19 is connected. In the expansion tank 19, a compressible gas volume 23 is provided.

As indicated in Figure 1 by the double arrow A, an effective effective area of the individual piston 7, which can be referred to as a rolling piston, results from the diameter of the individual piston 7 and the radial width of the between the longitudinal outer side 11, the single piston 7 and the cylindrical Housing 9 forming gap 24 constant circumferential width.

In a load vibration L, the single piston 7 is pressed axially into and out of the working chamber 17, whereby the hydraulic fluid flows through the dissipating channels 21 into the expansion tank 19 and out, whereby a damping effect is achieved. A spring effect causes the compressibility of the gas volume 23.

The strut 1 according to the invention has, within a cavity 25 in the individual piston 7, an electrically operated actuator, which in the embodiment shown in FIG. 1 is formed by two piezoelectric ring components 27, 29 (see also FIGS. 11a, 11b).

Upon electrical activation, the piezoelectric ring components 27, 29 expand, whereby a movable outer longitudinal side 11 of the single piston 7 is displaced radially outwards, so that the space 24 formed between the outer side 11 and the cylindrical housing 9 decreases and thus the effective effective area A the individual piston 7 is increased. In this way, the spring-damping characteristic of the strut 1 can be adjusted even during operation of the motor vehicle, so the intelligent spring damping system of the strut 1 according to the invention can respond to dynamic loads L on a time scale of the oscillation period of the system and adapted accordingly.

FIG. 2 shows a further embodiment of a hydropneumatic shock absorber according to the invention. For better readability of the description of the figures, the same reference numerals for the spring strut according to FIG. 2 are used with regard to the statements relating to FIG. 1 for similar or identical components.

The strut 1 according to Figure 2 differs from that of Figure 1 in that the working piston is designed as a so-called tandem piston 31. The tandem piston 31 has two piston heads, namely a vibration load-side piston head 33 and a body-side piston head 35. The vibration load-side piston head 33 is formed corresponding to the single piston 7 according to FIG. The vibration load-side piston head 33 is rigidly connected via a piston rod 37 to the body-side piston head 35.

The effective effective area of the shock absorber 1 according to FIG. 2 is defined by the difference between the effective individual effective areas A and B of the piston heads 33 and 35.

Also, the body-side piston head 35 includes in the cavity 39, two piezoelectric ring structures 41, 43, which cause a limitation or widening of the movable axial outer longitudinal side 45 of the piston head 35 when they are activated.

It has been found that a tandem piston construction according to FIG. 2 is particularly well suited if rapid spring characteristic changes are necessary.

Figures 3a and 3b show a piston assembly 40 with a radially movably mounted outer side 45 which is formed by four sleeve sections 47 to 50 of substantially the same construction. In the retracted operating state according to Figure 3a, the sleeve sections 45 to 49 are on a circular circumference to each other and concentric to the longitudinal axis S of a piston rod 37. The piston rod 37 receives inside an unspecified actuator, with the sleeve sections 47 to 50 via radially projecting setting pins 51 to 57 is coupled. The adjusting pins 51 to 57 extend radially from the interior of the piston rod 51 through the rod wall to the outside and are connected to an inner side of the respective sleeve portion 47 to 50.

In order to increase the effective area of the rolling piston 41, the adjusting pins 51 to 57 are displaced radially outwards, as indicated in FIG. 3b. In this case, the sleeve portions 45 to 49 are taken radially outward, whereby the Wirkfiäche of the working piston 41 is significantly increased. In Figures 3a and 3b is not shown that a rolling bellows (15, reference numerals, see Figures 1 and 2) on the outside of the sleeve portions 47 to 50 is fixed to form a fluid-tight working space.

FIGS. 4a and 4b show another basic principle of a movable outer side 45 for a widenable piston assembly 40. The movable outer side 45 of the piston assembly 40 is formed by a substantially concentric rolled-up sleeve 61 with two overlapping, mutually displaceable circumferential ends 65. On the outside of the non-closed sleeve 61 of the rolling bellows (15, Figure 1 and 2) is attached to form the fluid-tight working space. Upon the occurrence of radial forces, the sleeve 61 can widen in the radial direction, whereby the effective area of the rolling piston is increased, without the sleeve-shaped outer structure of the working piston must be abandoned.

A piezoelectric drive 67 shown in FIG. 5 can be used in particular for the rolling piston assembly according to FIGS. 3a and 3b. The piezoelectric actuator 67 is mostly housed within a piston rod 37 defining a longitudinal axis S. In a rotationally shaped, approximately circular cavity of the piston rod 37, two piezoelectric stacks 69, 71 are accommodated, whose maximum extension direction coincides with the longitudinal axis S of the piston rod 37. The stacks 69, 71 are based on diametrically opposed radial inner surfaces of the cavity of the piston rod 37 rigid. Approximately in the axial center of the cavity of the piston rod 37, an elastically deformable displacement body 73 is arranged, on which the piezoelectric stacks 69, 71 can act in a deforming manner.

The cavity opens at the peripheral outer region of the piston rod 37 in an axial constriction 75, in each of which an adjusting pin 51 to 57 is guided radially.

The displacement body 73 serves as a kind of transmission gear for converting the axial expansion amplitude of the piezoelectric stacks 69, 71 into an increased radial amplitude of movement of the adjusting pins 51 to 57. When the piezoelectric stacks 69, 71 are electrically activated, they expand in the longitudinal direction and press on the displacement body 73, which dodges in the radial direction to the constriction 75. Due to the constriction 75, the movement of the adjusting pins 51 to 57 is amplified.

A piezoelectric component element is shown in detail in FIGS. 8 to 10, which is generally designated by the reference numeral 79 and has a piezoelectric stack 71 of a plurality of piezoelectric disks 81 stacked on top of one another. Upon electrical activation, each disc 81 expands inter alia in the width direction, ie in the longitudinal direction of the stack 71. With the summation of the individual dimensions of the discs 81 there is a non-negligible longitudinal extent of the piezoelectric component element 79th

As can be seen in FIG. 10, the piezoelectric stack 71 is enclosed by two half shells 83, 85. A longitudinal extent of an internal space, which would form both axially adjacent half-shells 83, 85, is smaller than the longitudinal extent of the inactivated piezoelectric stack 71, so that the bottom inner sides of the half-shells 83, 85 are in contact with the piezoelectric stack 71, without the Endschalenränder touch.

As can be seen in FIGS. 8 and 10, there is a gap 84 in the radial direction between the grooved outer longitudinal side of the piezoelectric stack 71 and the inner longitudinal side of the half shells 83, 85. The gap 84 serves to allow the outer diameter changes caused by the application of current without the radial, cylindrical outer dimension of the component element 79 change. As a result, the component element 79 can readily be inserted into a radially complementary cylindrical cavity in the piston rod 37 without undesirable internal stresses due to the inevitable outer diameter changes of the piezoelectric stack 69, 71 can occur.

In the figures 1 Ia and Ib, a further embodiment of a piezoelectric actuator according to the invention is shown. The actuator is generally designated by the reference numeral 87 and comprises a closed, stretchable elastomer support ring 89. On a circumferential outer side 91 of the elastomer support ring 89, which runs in a circle, a plurality of hinge joints 93 are introduced at the same circumferential distance from each other, in which - in the figures I Ia and I Ib not shown - axially extending lamellae are pivotally attachable. On the circumferential inner side 92 of the elastomeric ring 89 are protrusions 95 radially inwardly at the same circumferential distance from each other, which limit in the circumferential direction, radially inwardly open compartments. In each compartment between two adjacent inner projections 95, a piezoelectric stack 97 is arranged. The piezoelectric stack 97 has a maximum extension direction which is oriented substantially in the circumferential direction of the actuator 97.

As shown in FIGS. 11a and 11b, the number of piezoelectric stacks 97 is eleven, but more or less may be used. All piezoelectric Stacks 97 may be powered individually or collectively with electrical power.

In FIG. 11a, the piezoelectric stacks 97 are de-energized, while in FIG. 11b, the piezoelectric stacks 97 are energized. Due to the electrical activation, the piezoelectric stacks 97 expand, especially in their longitudinal direction, whereby an elastic deformation of the elastomer ring 89 is accompanied. As can be seen in Figure 1 Ib, causes the expansion of the piezoelectric stack 97 crushing of the inner projections 95 and a radial expansion of the Elastomertragrings 89, whereby a Wirkflächenvergrößerung a piston, not shown, can be reached, the movable outer side of the actuator 87 cooperates.

In Figures 12, 13, 14 and 15, an inventive rolling piston 101 is shown in detail. The peculiarity of the rolling piston 101 is that an effective surface change by changing an inclination of the movable outer side 102 of the rolling piston 101 relative to a suspension and / or damping longitudinal direction D can be achieved.

The rolling piston 101 shown in FIGS. 12 to 15 has a partially represented piston rod 103 around which two annular piezoelectric actuators 105, 107 extending parallel to one another are supported on the rigid outer side of the piston rod, as shown in FIGS. 11a and 11b are shown.

The piezoelectric actuators 105, 107 can be operated independently of each other. With regard to the detailed structure of the annular piezoelectric actuators 105, 107, reference is made to the description of FIGS. 11a and 11b.

On the outside of the annular actuators 105, 107 a plurality of lamellar plates 109 are arranged, which define the rigid movable axial outer side 102 of the rolling piston 101. At the lower piezoelectric actuator 107, a pivot joint 111 for steering each of a lamella plate 109 is provided. On the outside of the lamellar plates 109, a fully revolving Abrollbalg 113 is attached fluid-tight, which forms a Abrollfalte 115. The rolling bellows 113 is attached to a non-illustrated cylinder housing fluid-tight. If now only the annular actuator 105 are activated, then a purely radial expansion of the outside of the actuator 105 is accompanied. Due to the pivotal connection, the lamellar plates 109 are inclined relative to the suspension and / or damping longitudinal direction D. In this way, the working piston 101 with the inclined lamellar plates 109 forms further radial outer side components, which increase the effective effective area of the rolling piston 101.

The features disclosed in the foregoing description, the figures and the claims may be of importance both individually and in any combination for the realization of the invention in the various embodiments.

LIST OF REFERENCE NUMBERS

1 hydro-pneumatic strut

3, 5 body-side and wheel load side connection

7 individual pistons

9 housing

11 long side

13 inside

15 rolling bellows

17 hydraulic working chamber

19 expansion tank

21 dissipation channels

23 gas volume

24 space

25 cavity

27, 29 piezoelectric ring components

31 tandem pistons

33 piston head

35 piston head

37 piston rod

39 cavity

40 piston construction

41, 43 ring structures

45 outside long side

47 to 50 sleeve sections

51 to 57 setting pins

61 sleeve

65 circumferential ends

67 piezoelectric actuator

69, 71 piezoelectric stacks

73 displacement body

75 constriction 79 piezoelectric component element

81 piezoelectric disks

83, 85 half shells

84 gap

87 actuator

89 Elastomer support ring

91 outer circumference

92 peripheral inside

93 hinged joints

95 internal projections

97 piezoelectric stack

101 rolling piston

102 outside

103 piston rod

105, 107 actuators

109 lamellar plates

111 swivel joint

113 rolling bellows

115 roll fold

A, B single-action surfaces

D spring and / or damping longitudinal direction

L vibration load

S longitudinal axis

Claims

claims

1. Vibration fluid damping and / or suspension in particular for a vehicle, in which a vibration load (L) can be introduced and which has a working piston whose effective area for changing one of the vibration load (L) counteracting fluid damper and / or spring force can be increased and / or is reducible, characterized in that an electrically operated actuator is arranged on the working piston to displace a movable outer side of the working piston, so that the active surface is extended and / or reduced.

2. vibration fluid damping and / or suspension according to claim 1, characterized g e characterized in that the actuator (67, 87) is operated piezoelectrically or electromechanically.

3. vibration fluid damping and / or suspension according to claim 1 or 2, characterized in that the actuator is housed in a cavity of a piston rod (37) or attached to the outside thereof.

4. vibration fluid damping and / or suspension according to one of claims 1 to 3, characterized in that the working piston is designed as a rolling piston (7, 31, 101), wherein a flexible Abrollbalg (15) is mounted on the movable outer side, wherein A working fluid exposed radial surface components of the rolling piston (7, 31, 101) define the active surface.

5. vibration fluid damping and / or suspension according to claim 4, characterized g e- characterized in that the movable outer side of the rolling piston (7, 31, 101) by a rollable sleeve (61) is formed, whose peripheral ends (65) overlap-

- 64Y ₆₂ - pen, wherein in particular an overlap of the peripheral ends (65) remains even at maximum expansion of the movable outer side.

6. vibration fluid damping and / or suspension according to claim 4, characterized g e- indicates that the movable outer side of the rolling piston (7, 31, 101) by a plurality of separate, substantially concentric with each other sleeve portions (47 to 50) is formed, the are coupled for radial displacement on the actuator.

7. vibration fluid damping and / or suspension according to one of claims 4 to 6, characterized in that the movable outer side of the rolling piston (7, 31, 101) formed by a plurality of damping and / or suspension longitudinal direction (D) aligned Lammellen (109) is, which are radially displaceable by the actuator and are arranged in a radially extended state at a circumferential distance from each other.

8. vibration fluid damping and / or suspension according to one of claims 1 to 7, characterized in that at least one piezoelectric component of the actuator has a predetermined largest expansion longitudinal direction and cooperates with expansion or shrinkage of the component with a transmission structure such that an expansion or Shrinkage amplitude of the component gear ratio is increased or decreased to widen or limit the effective area.

9. oscillation fluid damping and / or suspension according to claim 8, characterized g e- indicates that the component is housed in a substantially completely surrounding the component container, which consists of two in the extension longitudinal direction apart movable rigid shell parts (83, 85), wherein between a substantially parallel to the extension longitudinal direction extending longitudinal side of the component and one of the longitudinal side facing inner longitudinal side of the container, a free space is provided.

10. oscillation fluid damping and / or suspension according to claim 9, characterized g e- indicates that the component and at least one inside of the container zy- is cylindrical, wherein an outer diameter of the component is smaller than the diameter of the inner side.

11. oscillation fluid damping and / or suspension according to one of claims 8 to 10, characterized in that a longitudinal extent of the component is greater than a longitudinal extent of the abutting in the expansion longitudinal direction shell parts (83, 85).

12. Vibration fluid damping and / or suspension according to one of claims 9 to 11, characterized izech that the component is formed by a stack of stacked discs (81) of piezoelectric material, wherein the extension longitudinal direction corresponds to the stacking direction.

13. vibration fluid damping and / or suspension according to one of claims 8 to 12, characterized in that the transmission gear structure comprises an elastically deformable displacement body (73), the shape causes a gear transmission according to increased radial movement when deformed by the component.

14. vibration fluid damping and / or suspension according to one of claims 8 to 13, characterized gekennzei chnet, that the displacement body (73) of the displacement body (73) surrounding, rigid, radial constriction (75) is associated such that upon expansion of the component the displacement body (73) is forced into the constriction (75).

15. oscillation fluid damping and / or suspension according to one of claims 8 to 14, characterized in that the expansion longitudinal direction of the component is parallel to the damping and / or suspension longitudinal direction (D).

16. oscillation fluid damping and / or suspension according to one of claims 8 to 15, characterized in that the component is housed in a cavity of a piston rod (37) and on the one hand on a rigid inner surface on the other hand on the deformable displacement body (73) is supported.

17. Vibration fluid damping and / or suspension according to one of claims 8 to 16, characterized GE IETNET that at a radial outer end of the displacement body (73) in particular at the radial height of the constriction (75) has a radially extending adjusting pin (51 to 57) is arranged, which is connected to a movable outer side of the working piston.

18. vibration fluid damping and / or suspension according to one of claims 1 to 17, characterized in that the actuator is formed by at least one ring structure, preferably two mutually parallel ring structures, comprising a plurality of piezoelectric components whose extension longitudinal direction substantially in the circumferential direction of the ring structure is aligned and which are accommodated in an elastically deformable jacket.

19. Vibration fluid damping and / or suspension according to claim 18, characterized g e- indicates that the ring structure is fixed around a piston rod (37) around.

20. Vibration fluid damping and / or suspension, in particular for a vehicle, in particular according to one of claims 1 to 19, in which a vibration load (L) can be introduced and which has a tandem piston (31) with two damping and / or suspension longitudinal directions (D). one behind the other, having mutually rigidly coupled piston heads (33, 35) each having an active surface (A, B), wherein an effective total effective area of the oscillation fluid damping and / or suspension by a difference of the active surfaces (A, B) of the piston heads (33, 35) characterized in that the effective area of one or both of the piston heads (33, 35) for varying one of the vibration load (L) counteracting fluid damper and / or spring force in response to the vibration load (L) is variable according to their time scale ,

21. Vibration fluid damping and / or suspension, in particular for a vehicle, in particular according to one of claims 1 to 20, in which a vibration load (L) can be introduced and which has a working piston (101), whose effective area for changing one of the vibration load (L) counteracting fluid damper and / or spring force is variable, characterized in that one of the outer sides (102) of the Working piston (101), preferably a substantially axial longitudinal side, relative to the damping and / or suspension longitudinal direction (D) can be inclined to form a taper, wherein a degree of inclination of the outer side (102) is adjustable.

22. Vibration fluid damping and / or suspension according to claim 21, characterized g e- kennnet ichnet that the outside has an umbrella-shaped structure.

23. vibration fluid damping and / or suspension according to claim 21 or 22, characterized in that the outer side (102) is formed by a plurality of hingedly hinged to a support of the working piston fins (100), on the outer surface of a Abrollbalg 113 is attached.

24. oscillation fluid damping and / or suspension according to one of claims 21 to 23, characterized in that an actuator (105, 107) which is arranged between a piston rod (103) and the lamellae (109), the inclination of the slats (109 ).

25. vibration fluid damping and / or suspension according to one of claims 21 to 24, characterized in that the actuator (105, 107) is associated with a pivot joint (111) of the slats (109).

26. Vibration damping and / or suspension according to one of claims 1 to 25, characterized in that the actuator (105, 107) is connected to a control and / or regulating device.