DE102008007566B4 - Vibration fluid damping and / or suspension - Google Patents

Abstract

Vibration fluid damping and / or suspension, in particular for a vehicle, into which a vibration load (L) can be introduced and which has a working piston, the effective surface of which can be increased and / or reduced in order to change a fluid damper and / or spring force counteracting the vibration load (L) , wherein an electrically operated actuator is arranged on the working piston in order to displace a movable outer side of the working piston so that the effective area is expanded and / or reduced, the working piston being designed as a rolling piston (7, 31, 101), with a flexible rolling bellows (15) is attached to the movable outer side, with radial surface components of the rolling piston (7, 31, 101) exposed to a working fluid defining the active surface, characterized in that the movable outer side of the rolling piston (7, 31, 101) can be rolled in Sleeve (61) is formed, the peripheral ends (65) of which overlap.

Description

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 made EP 1 541 386 A2 known.

DE 199 52 799 A1 discloses a so-called tandem piston, in which two in the damping and / or suspension longitudinal direction one behind the other, rigidly coupled to each other working piston heads are used, each with an effective area. The working piston heads each have a conical longitudinal outer side, whereby the passive spring damping characteristic change 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.

Out DE 102 23 216 A1 is a device for shock absorption by means of piezo actuators known.

DE 102 36 246 B4 relates to a level adjustable air suspension device for vehicles.

DE 1 127 729 A discloses a rolling body of metal, rubber or plastic for a Stülpbalg of air springs.

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 off DE 41 35 900 C2 known. 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. Electrically operated 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 becomes an active one Shock characteristic change achieved by energy is introduced into the spring damping system to calm it targeted, the shock absorber in its production remains cost-effective and it does not require a presetting of the strut length.

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.

According to the invention 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 an embodiment of the invention, the movable outer side of the rolling piston is formed by a roll-up sleeve whose peripheral ends overlap. By rollable sleeve structure, a relatively stable structure is provided, which allows a targeted concentric expansion of the movable outer side 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 operated 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 translation gear structure such that an expansion or contraction amplitude of the component is gear-converted into an enlarged or reduced radial adjustment amplitude to appropriately adjust the effective effective area. 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 electrified piezoelectric material. Preferably, the component and at least one inner side of the container are 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 a preferred aspect of the invention is a tandem piston 31 provided with two in damping and / or suspension longitudinal direction one behind the other, rigidly coupled to each other 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 a further preferred aspect of the invention, a vibration fluid damping 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, is inclined relative to the damping and / or spring longitudinal direction to form a taper can, with 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 assigned to a pivot joint 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:

1 a schematic cross-sectional view of a hydropneumatic strut with a single piston assembly;

2 a schematic cross-sectional view of a hydropneumatic strut in another embodiment with a tandem piston;

3a respectively. 3b a plan view of a rolling piston in a limited operating state or a widened operating state;

4a respectively. 4b a plan view of a radially expandable outer jacket of a rolling piston in a retracted operating state or in a widened operating state;

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

6 a plan view of the actuator according to 5 ;

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

8th a partially cutaway, perspective view of a piezoelectric component, which is suitable for an actuator for changing the effective area of a rolling piston;

9 a side view of the piezoelectric component according to 8th ;

10 a cross-sectional view of the piezoelectric component along the section line XX after 9 ;

11a respectively. 11b schematic cross-sectional views of a piezoelectric component group to form an actuator, which is arranged concentrically to the piston rod and is shown in a limited operating state or a widened operating state;

12 a partially cutaway perspective view of a rolling piston with a tiltable axial longitudinal side, which is shown in a tilt-free state;

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

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

15 a cross-sectional view of the rolling piston according to 14 ,

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

Part of the outside of the single piston 7 , an inside 13 of the cylindrical housing 9 as well as an outside long side 11 of the single piston 7 with the inner longitudinal side of the cylindrical housing 9 connecting rolling bellows 15 limit a closed hydraulic working chamber 17 to which dissipation channels 21 a surge tank 19 connected. In the expansion tank 19 is a compressible gas volume 23 intended.

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

At a load oscillation L, the single piston 7 axially into and out of the working chamber 17 pressed, causing the hydraulic fluid through the Dissipationskanäle 21 in the expansion tank 19 and flows out, whereby a damping effect is achieved. A spring action causes the compressibility of the gas volume 23 out.

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

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

In 2 a further embodiment of a hydropneumatic suspension strut according to the invention is shown. For better readability of the description of the figures, with regard to the comments on 1 for similar or identical components, the same reference numbers for the strut according to 2 used.

The strut 1 according to 2 is different from that 1 in that the working piston as a so-called tandem piston 31 is trained. 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 according to the single piston 7 according to 1 educated. The vibration load side piston head 33 is via a piston rod 37 with the body-side piston head 35 rigidly connected.

The effective effective area of the strut 1 according to 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 contains in its cavity 39 two piezoelectric ring structures 41 . 43 which, when activated, restrict or widen the movable axial outer longitudinal side 45 of the piston head 35 cause.

It was found that a tandem piston construction according to 2 especially good then suitable when rapid spring characteristic changes are necessary.

3a and 3b show a piston construction 40 with a radially movably mounted outside 45 passing through four sleeve sections 47 to 50 is formed in substantially the same structure. In retracted operating state according to 3a lie the sleeve sections 45 to 49 on a circular circumferential line to each other and concentric with the longitudinal axis S of a piston rod 37 , The piston rod 37 takes on the inside an unspecified actuator on which with the sleeve sections 47 to 50 via radially projecting setting pins 51 to 57 is coupled. The adjusting pins 51 to 57 extend from the inside of the piston rod 51 radially outward through the rod wall and having an inner side of the respective sleeve portion 47 to 50 connected.

To the effective surface of the rolling piston 41 To enlarge, the adjusting pins 51 to 57 displaced radially outward, as in 3b is indicated. This also the sleeve sections 45 to 49 taken radially outwards, whereby the effective surface of the working piston 41 is significantly increased. In the 3a and 3b is not shown that a rolling bellows ( 15 , Reference numerals, see 1 and 2 ) on the outside of the sleeve sections 47 to 50 is attached to form a fluid-tight working space.

In the 4a and 4b is another basic principle of a moving outside 45 for a wide piston construction 40 shown. The mobile outside 45 of the piston assembly 40 is by a substantially concentric rolled sleeve 61 with two overlapping, mutually displaceable circumferential ends 65 educated. On the outside of the not closed sleeve 61 is the rolling bellows ( 15 . 1 and 2 ) attached to form the fluid-tight working space. When radial forces occur, the sleeve can 61 expand 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.

An in 5 illustrated piezoelectric drive 67 can in particular for the rolling piston according to the 3a and 3b be used. The piezoelectric actuator 67 is mostly within a piston rod 37 housed defining a longitudinal axis S. In a rotation-shaped, approximately circular cavity of the piston rod 37 are two piezoelectric stacks 69 . 71 housed, the maximum extension direction with the longitudinal axis S of the piston rod 37 coincides. The stacks 69 . 71 are supported 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 is an elastically deformable displacement body 73 arranged on which the piezoelectric stacks 69 . 71 can act as a deformation.

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

The displacement body 73 serves as a kind of transmission gear for a conversion of the axial expansion amplitude of the piezoelectric stack 69 . 71 in an enlarged radial amplitude of movement of the adjusting pin 51 to 57 , When the piezoelectric stack 69 . 71 electrically activated, they expand in the longitudinal direction and press on the displacement body 73 in the radial direction to constriction 75 dodging. Due to the constriction 75 becomes the movement of the adjusting pin 51 to 57 strengthened.

In the 8th to 10 a piezoelectric component element is shown in detail, generally with the reference numeral 79 provided and a piezoelectric stack 71 of several, stacked piezoelectric disks 81 having. Upon electrical activation, each disc expands 81 among other things in the width direction, ie in the longitudinal direction of the stack 71 out. With the summation of the individual dimensions of the discs 81 There is a non-negligible longitudinal extent of the piezoelectric component element 79 ,

As in 10 can be seen, is the piezoelectric stack 71 of two half-shells 83 . 85 eingehäust. A longitudinal extension of an interior, the two axially adjacent half shells 83 . 85 is less than the longitudinal extent of the inactivated piezoelectric stack 71 , so that the bottom inside of the half-shells 83 . 85 in contact with the piezoelectric stack 71 are without touching the Endschalenränder.

As in 8th and 10 is apparent, exists 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 A gap 84 , The gap 84 serves to allow caused by current application, outer diameter changes, without causing the radial, cylindrical outer dimension of the component element 79 to change. This allows the component element 79 readily in a radially complementary shape, cylindrical cavity in the piston rod 37 be used without causing undesirable internal stresses due to the inevitable Outer diameter changes of the piezoelectric stack 69 . 71 can come.

In the 11a and 11b a further embodiment of a piezoelectric actuator according to the invention is shown. The actuator is generally denoted by the reference numeral 87 provided and includes a closed, stretchable Elastomertragring 89 , On a peripheral outside 91 the elastomeric support ring 89 , which runs in a circle, are several hinged joints 93 introduced in the same circumferential distance from each other, where - in the 11a and 11b not shown - axially extending slats are pivotally attachable.

At the inner circumference 92 of the elastomeric ring 89 are at the same circumferential distance projections to each other 95 radially inwardly, delimiting in the circumferential direction, radially inwardly open compartments. In each compartment between two adjacent inner projections 95 is a piezoelectric stack 97 arranged. The piezoelectric stack 97 has a maximum expansion direction, which is substantially in the circumferential direction of the actuator 97 is aligned.

As in the 11a and 11b 11, there are eleven piezoelectric stacks in number 97 provided, but it can be used more or less. All piezoelectric stacks 97 can be supplied individually or collectively with electricity.

In 11a are the piezoelectric stacks 97 de-energized while in 11b the piezoelectric stacks 97 are energized. Due to the electrical activation, the piezoelectric stacks expand 97 especially in the longitudinal direction, whereby an elastic deformation of the elastomeric ring 89 accompanied. As in 11b can be seen causes the expansion of the piezoelectric stack 97 a bruise of the inner projections 95 and a radial expansion of the Elastomertragrings 89 whereby an increase in the effective area of a piston, not shown, whose movable outer side is accessible to the actuator 87 works together.

In the 12 . 13 . 14 and 15 is an inventive rolling piston 101 shown in detail. The peculiarity of the rolling piston 101 is that an effective area change by changing an inclination of the movable outer side 102 of the rolling piston 101 opposite to a suspension and / or damping longitudinal direction D is reached.

The in the 12 to 15 illustrated rolling piston 101 has a partially shown piston rod 103 around which are two annular, mutually parallel piezoelectric actuators 105 . 107 supported on the rigid outer side of the piston rod, as in the 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 will be on the description to the 11a and 11b directed.

On the outside of the annular actuators 105 . 107 are several lamellar plates 109 arranged that the rigid movable axial outside 102 of the rolling piston 101 define. On the lower piezoelectric actuator 107 is a swivel joint 111 for the articulation of a slat plate 109 intended. On the outside of the lamellar plates 109 is a fully revolving rolling bellows 113 attached fluid-tight, which is a Abrollfalte 115 forms. The rolling bellows 113 is attached to a non-illustrated cylinder housing fluid-tight.

Should now only the annular actuator 105 be activated, so goes a purely radial expansion of the outside of the actuator 105 associated. Due to the pivotal connection, the lamellar plates 109 inclined relative to the suspension and / or damping longitudinal direction D. In this way, the working piston forms 101 with the inclined lamellar plates 109 Other radial outer side components, which is the effective effective area of the rolling piston 101 enlarge.

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

hydropneumatic strut

3, 5

Body-side and Radlastseitiger connection

7

Single piston

9

casing

11

long side

13

inside

15

Abrollbalg

17

hydraulic working chamber

19

surge tank

21

Dissipationskanäle

23

gas volume

24

gap

25

cavity

27, 29

piezoelectric ring components

31

tandem piston

33

piston head

35

piston head

37

piston rod

39

cavity

40

piston assembly

41, 43

ring structures

45

Outer longitudinal side

47 to 50

sleeve sections

51 to 57

adjusting pin

61

shell

65

circumferential ends

67

piezoelectric actuator

69, 71

piezoelectric stacks

73

displacer

75

constriction

79

piezoelectric component element

81

piezoelectric discs

83, 85

shells

84

gap

87

actuator

89

Elastomeric support ring

91

Scope outside

92

Circumferential inner side

93

hinges

95

internal projections

97

piezoelectric stack

101

roll-off

102

outside

103

piston rod

105, 107

actuators

109

lamella plates

111

pivot

113

Abrollbalg

115

Abrollfalte

A, B

Single active surfaces

D

Spring and / or damping longitudinal direction

L

vibrational load

S

longitudinal axis

Claims (25)

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 surface for changing one of the vibration load (L) counteracting Fluiddämpfer- and / or spring force can be increased and / or reduced in which an electrically operated actuator is arranged on the working piston in order to displace a movable outer side of the working piston so that the working surface is widened and / or reduced, the working piston acting as a rolling piston ( 7 . 31 . 101 ), wherein a flexible rolling bellows ( 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, characterized in that the movable outer side of the rolling piston ( 7 . 31 . 101 ) by a roll-up sleeve ( 61 ) whose circumferential ends ( 65 ) overlap. Vibration damping and / or suspension according to claim 1, characterized in that the actuator ( 67 . 87 ) is operated piezoelectrically or electromechanically. Vibration damping and / or suspension according to claim 1 or 2, characterized in that the actuator is located in a cavity of a piston rod ( 37 ) is housed or attached to the outside thereof. Vibration damping and / or suspension according to one of claims 1 to 3, characterized in that an overlap of the peripheral ends ( 65 ) remains even at maximum expansion of the movable outer side. Vibration fluid damping and / or suspension according to one of claims 1 to 4, characterized in that the movable outer side of the rolling piston ( 7 . 31 . 101 ) by a plurality of separate, substantially concentric sleeve sections ( 47 to 50 ) which are coupled for radial displacement on the actuator. Vibration fluid damping and / or suspension according to one of claims 1 to 5, characterized in that the movable outer side of the rolling piston ( 7 . 31 . 101 ) by a plurality of Lammellen aligned in Dämpfungs- and / or suspension longitudinal direction (D) ( 109 ) is formed, which are radially displaceable by the actuator and are arranged in a radially extended state at a circumferential distance from each other. Vibration fluid damping and / or suspension according to one of claims 1 to 6, characterized in that at least one piezoelectric component of the actuator has a predetermined largest extension longitudinal direction and cooperates with expansion or shrinkage of the component with a transmission gear structure such that an expansion or shrinkage amplitude of the component gear ratio is increased or decreased to widen or limit the effective area. Vibration fluid damping and / or suspension according to claim 7, characterized in that the component is accommodated in a container which substantially completely surrounds the component and which consists of two rigid shell parts which can be moved apart in the expansion longitudinal direction (US Pat. 83 . 85 ) is formed, 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. Vibration fluid damping and / or suspension according to claim 8, characterized in that the component and at least one inner side of the container is cylindrical, wherein an outer diameter of the component is smaller than the diameter of the inner side. Vibration fluid damping and / or suspension according to one of claims 7 to 9, 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 ). Vibration damping and / or suspension according to one of Claims 8 to 10, characterized in that the component is replaced by a stack of stacked discs ( 81 ) is formed of piezoelectric material, wherein the extension longitudinal direction corresponds to the stacking direction. Vibration fluid damping and / or suspension according to one of Claims 7 to 11, characterized in that the transmission gear structure has an elastically deformable displacement body ( 73 ), the shape of which, when deformed by the component, causes a geared amplified radial movement. Vibration fluid damping and / or suspension according to one of claims 8 to 13, characterized in that the displacement body ( 73 ) one the displacement body ( 73 ) surrounding, rigid, radial constriction ( 75 ) is assigned such that upon expansion of the component of the displacement body ( 73 ) in the constriction ( 75 ) is urged. Vibration fluid damping and / or suspension according to one of claims 7 to 13, characterized in that the expansion longitudinal direction of the component is parallel to the damping and / or suspension longitudinal direction (D). Vibration damping and / or suspension according to one of Claims 7 to 14, characterized in that the component is located in a cavity of a piston rod ( 37 ) is housed and on the one hand on a rigid inner surface on the other hand on the deformable displacement body ( 73 ) is supported. Vibration damping and / or suspension according to one of claims 7 to 15, characterized in that at a radial outer end of the displacement body ( 73 ) a radially extending adjusting pin ( 51 to 57 ) is arranged, which is connected to a movable outer side of the working piston. Vibration fluid damping and / or suspension according to one of claims 1 to 16, characterized in that the actuator is formed by at least one ring structure having a plurality of piezoelectric components, the extension longitudinal direction is aligned substantially in the circumferential direction of the ring structure and in an elastically deformable shell are included. Vibration damping and / or spring suspension according to claim 17, characterized in that the ring structure around a piston rod ( 37 ) is attached around. Vibration fluid damping and / or suspension according to one of claims 1 to 18, in which a vibration load (L) can be introduced and which is a tandem piston ( 31 ) with two in the damping and / or suspension longitudinal direction (D) in a row, mutually rigidly coupled piston heads ( 33 . 35 ), each having an active surface (A, B), wherein an effective total effective area of the vibration 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 piston heads ( 33 . 35 ) for changing a fluid damper and / or spring force counteracting the vibration load (L) in response to the vibration load (L) is variable according to their time scale. Vibration fluid damping and / or suspension according to one of claims 1 to 19, in which a vibration load (L) can be introduced and which is a working piston ( 101 ), the effective surface of which is variable for changing one of the vibration load (L) counteracting fluid damper and / or spring force, characterized in that one of the outer sides ( 102 ) of the working piston ( 101 ) relative to the damping and / or suspension longitudinal direction (D) can be inclined to form a taper, wherein a degree of inclination of the outside ( 102 ) is adjustable. Vibration fluid damping and / or suspension according to claim 20, characterized in that the outer side has an umbrella-shaped structure. Vibration damping and / or suspension according to claim 20 or 21, characterized in that the outside ( 102 ) by a plurality of hingedly hinged to a support of the working piston slats ( 100 ) is formed, on the outer surface of a rolling bellows 113 is attached. Vibration damping and / or suspension according to one of claims 20 to 22, characterized in that an actuator ( 105 . 107 ) between a piston rod ( 103 ) and the Slats ( 109 ), the inclination of the slats ( 109 ). Vibration damping and / or suspension according to one of claims 20 to 23, characterized in that the actuator ( 105 . 107 ) a swivel joint ( 111 ) of the slats ( 109 ) assigned. Vibration damping and / or suspension according to one of claims 1 to 24, characterized in that the actuator ( 105 . 107 ) is connected to a control and / or regulating device.

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