EP2348226A1 - Elastomer torsion spring element, device for transferring force with same and seat device with a device for transferring force - Google Patents

Abstract

The element (10) has an internal casing (12) rotated at a rotation angle (phi) about a rotation axis (6) during pivoting movement of a back support or a seat. The internal casing is moved relative to an external casing (14). Deformation of an elastomer body (16) is generated such that the body generates restoring torque between the external and internal casings, where the torque acts against the rotation. A contact surface (12a) of the external and internal casings comprises a non-circular cross section in a sectional plane perpendicular to the rotation axis. An independent claim is also included for a seat assembly comprising a support for a back support and/or a seat.

Description

The invention relates to an elastomer torsion spring element, a device for transmitting power between two relatively movable bodies with an elastomer torsion spring element and a seat device with a device for transmitting power.

For example, elastomer torsion spring elements are known which comprise an inner housing, an outer housing surrounding the inner housing and an elastomer body arranged in a space between the inner housing and the outer housing. In this case, the inner housing generally has at least one contact surface on which the elastomeric body is in contact with the inner housing, while the outer housing has at least one contact surface on which the elastomeric body is in contact with the outer housing. Furthermore, the inner housing and / or the outer housing of the respective elastomer Torsionsfederelements is rotatably disposed about a rotation axis and a rotation of the inner housing and / or the outer housing by a rotation angle about the axis of rotation executable such that during the respective rotation, the inner housing moves relative to the outer housing and wherein a deformation of the elastomeric body is generated, so that the elastomeric body between the outer housing and the inner housing generates a restoring torque which is opposite to the rotation.

Such an elastomer torsion spring element is used, for example, in devices for transmitting power between relatively movable bodies in order to obtain a Movement of a first body relative to a second body to generate a restoring force, which counteracts the respective movement. The respective force transmission device, for example, causes - if a first force acts on the first body and consequently moves the first body relative to the second body - the power transmission device generates a restoring force which counteracts the first force, so that the first body is in an equilibrium position can assume relative to the second body, wherein in the equilibrium position, the first force is compensated by the respective restoring force.

Such a device for transmitting power between a first body and a second, relative to the first body movable body can with at least one elastomer torsion spring element of the aforementioned type and with a first coupling means for coupling the first body to the outer housing of the respective elastomer torsion spring element and a second coupling means for coupling the second body to the inner housing of the respective elastomer Torsionsfederelements be realized. For this purpose, the first coupling means and the second coupling means may be formed, for example, such that the first body is coupled to the outer housing of the respective elastomer Torsionsfederelements and the second body is coupled to the inner housing of the respective elastomer torsion spring member that at Movement of the first body relative to the second body, a rotation of the inner housing and / or the outer housing is performed by a rotational angle about the axis of rotation at which rotation, the inner housing moves relative to the outer housing and thereby a deformation of the elastomeric body is generated. In this case, the elastomer body of the respective elastomer Torsionsfederelements generates between the respective outer housing and the respective inner housing a restoring torque, which is opposite to the rotation of the inner housing or the outer housing. The restoring torque generated by the respective elastomer torsion spring element corresponds to a restoring force, which counteracts the respective movement of the first body relative to the second body.

Devices for power transmission according to the above-mentioned type are used in many technical fields in the field of mechanical engineering.

An application of such devices for power transmission u.a. Seats, for example chairs.

Seat devices are often not rigid, but usually comprise a fixedly arranged support structure and a pivotable relative to the support structure back and / or a pivotable relative to the support structure seat, for example, to allow, on the one hand, the spatial arrangement of the back and / or the seat be adapted to the respective posture of sitting on the respective seat, their body posture constantly changing, or to achieve, for example, that the same seat device to different needs of different people, for example, have a different body size or a different weight or different habits in terms preferred posture can be tuned. In this case, a power transmission device of the above-mentioned type can be advantageously used to couple the back part to the support structure via the respective elastomer torsion spring element and to allow the back part to move relative to a predetermined one upon application of a force acting on the back part Starting position is pivotally and the respective elastomer torsion spring element at the respective Pivoting movement of the back part generates a restoring force acting on the back part or a restoring torque acting on the back part in order to keep the back part in a stable equilibrium position. The latter improves the seating comfort. Accordingly, a power transmission device of the aforementioned type may be used to couple a seating of the seat assembly to the support structure via the respective elastomeric torsion spring element.

The EP 1486142 A1 shows a chair with an elastomer-elastomer torsion spring element 258 of the aforementioned type, which serves to generate a restoring torque, which counteracts a pivoting movement of a seat support about a rotation axis. The elastomer torsion spring element 258 includes an inner housing 260 and an outer housing 264, wherein in an intermediate space between the inner housing 260 and the outer housing 264, an elastomeric body 262 is introduced. The inner housing 260 has on its outer side a contact surface on which the elastomeric body 262 is in contact with the inner housing 260, and the outer housing 264 has on its inner side a contact surface on which the elastomeric body 262 with the outer housing 264 in Contact is. In this case, the elastomeric body 262 is fixedly connected to the respective contact surface of the inner housing 260 and the respective contact surface of the outer housing 264, so that the elastomeric body 262 neither on the contact surface of the inner housing 260 nor on the contact surface of the outer housing 264 relative to the inner housing or to can slip the outer housing.

The outer housing 264 and the inner housing 260 are cylindrical and arranged coaxially with each other. The outer housing 264 is held on a support structure of the chair, while the inner housing 260 rotatably on a shaft 250 is seated, which is rotatable about its longitudinal axis. A seat 32 of the chair is coupled to the shaft 250 such that, if the seat 32 is loaded by the weight of a person, the shaft 250 is rotated about its longitudinal axis and the seat 32 is pivoted from a predetermined home position. As a result of the rotation of the shaft 250, the inner housing 260 is rotated about its longitudinal direction and thereby rotated relative to the outer housing 264, with the result that the elastomer torsion spring member 258 generates a restoring torque acting on the shaft 250 and the seat 32, respectively Shaft 250 and the pivoting movement of the seat 32 counteracts and increases with increasing angle of rotation. In the case of the elastomeric torsion spring member 258, the magnitude of the minimum torque acting on the shaft 250 when the seat 32 is pivoted from said home position (hereinafter called "minimum restoring torque") may be changed, for example, depending on the weight person sitting on the chair. For this purpose, the outer housing 264 can be rotated about its longitudinal axis by means of a arranged on the support structure of the chair rotating mechanism and thus rotated about the longitudinal axis of the shaft 250, wherein the outer housing 264 relative to the support structure of the chair and relative to the inner housing 260 and Shaft 250 is twisted. By means of the rotation of the outer housing 264 relative to the inner housing 260, the elastomer torsion spring element 258 is biased, wherein the rotational angle by which the outer housing 264 is rotated relative to the inner housing 260 when the seat 32 is in the home position, the size of the "minimum Reset torque "determined.

Because of the cylindrical shape of the outer housing 264 and the inner housing 260, the respective contact surfaces of the outer housing 264 and of the inner housing 260 adjoining the elastomer body 262 are each in a direction perpendicular to the shaft 250 Cutting plane - each circular. Upon rotation of the shaft 250 about its longitudinal direction, the elastomeric body 262 is deformed so that it is loaded in each case to train.

The elastomer torsion spring element 258 has the disadvantage that the restoring torque, which is generated upon rotation of the shaft 250 by a certain angle of rotation shows a relatively small increase as a function of the respective angle of rotation, especially if the elastomer torsion spring element 258 not or only is slightly biased. This results in a further disadvantage that the elastomer torsion spring element 258 must be very strong biased when a large minimum restoring torque is to be adjusted, for example, to provide persons with high weight adequate seating comfort can. Furthermore, the return torque as a function of the rotational angle of the shaft 250 greatly increases nonlinear (progressive) when the shaft 250 is to be rotated, for example, by a rotation angle in the range of 0 to about 70 °. A large non-linearity of the restoring torque in said rotation angle range is undesirable in view of seat-related applications because such nonlinearities are generally perceived as unpleasant by a user. Thus, the available rotation angle range is reduced, which is uncomfortable. In addition, the elastomeric body 262 is permanently and heavily loaded by the high bias voltage, which fatigues faster. As a result, the elastomer torsion spring member 258 has a short life and must be replaced frequently. Another disadvantage is that an adjustment of the respective bias of the elastomer Torsionsfederelements 258 tedious and time consuming, especially since the outer housing 264 must be adjusted by a large angle relative to the inner housing 260 to a specific Set minimum return torque.

Out GB 2070727 A Another elastomer torsion spring element of the above type is known. This elastomeric torsion spring element is used in a device for transmitting power between a base plate and a motor movably mounted relative to the base plate. This elastomer torsion spring element also has an inner housing and an outer housing surrounding the inner housing, wherein the inner housing and / or the outer housing is rotatably arranged about a rotational axis. The outer surface of the inner housing and the inner surface of the outer housing have a cross section with the shape of a square in a sectional plane perpendicular to the axis of rotation. Between the inner housing and the outer housing, a gap is formed. The inner housing of the elastomer torsion spring element is rotated in a "basic position" relative to the outer housing by 45 ° about the axis of rotation, so that in this case, the intermediate space consists essentially of four sub-areas, which are formed in the four corners of the outer housing and - a cross section perpendicular to the axis of rotation - have the shape of a triangle. In each of these four sections each an elastomeric body (preferably made of rubber) is used. The respective elastomer body has the shape of a cylinder in the undeformed state. The elastomeric bodies are each compressed prior to introduction into the respective subregions of the interspace and - in the compressed state - inserted into the respective subregion of the interspace such that each of the subregions is substantially filled by one of the elastomeric bodies and each of the elastomeric bodies a certain pressure on the outer surface of the inner housing and the inner surface of the outer housing rests, wherein the elastomeric body are firmly connected to neither the inner housing nor with the outer housing. The four elastomer body This elastomer torsion spring element are each identical, so that the inner housing of the elastomer torsion spring element is held by the elastomeric bodies in said basic position, if acting on the outer housing or the inner housing no external forces, which could rotate the inner housing relative to the outer housing about the axis of rotation. However, if the inner housing is rotated relative to the outer housing about the axis of rotation, the four elastomeric body generate a restoring torque between the inner housing and the outer housing, which counteracts the respective rotational movement and grows with increasing rotational angle. This elastomer torsion spring element has several disadvantages. The inner housing can be rotated about the axis of rotation by a maximum of about 30 ° relative to the outer housing, in both directions of rotation in the same mass. Twists of more than 30 ° compared to the basic position are not practicable. On the one hand, the restoring torque of this elastomer torsion spring element increases with a large non-linearity when the inner housing is rotated by an angle of rotation (relative to the aforementioned basic position with respect to the outer housing) as a function of the angle of rotation in the range from 0 to 30 °. Furthermore, there is a risk that the elastomeric body slip by more than 30 ° with respect to the inner housing or the outer housing during a rotation of the inner housing. In this case, the inner housing can get into an unstable position, so that the elastomeric body are no longer able to produce a restoring torque, which can bring the inner housing with certainty back into the respective basic position relative to the outer housing. Such instability is undesirable in many applications and may need to be prevented, for example, by safety measures which block further rotation of the inner housing when the rotation of the inner housing relative to the basic position is a critical limit reached from about 30 ° from the basic position.

The present invention is therefore based on the object to avoid the disadvantages mentioned and to provide a Torsionsfederelement which allows a rotation of the inner housing relative to the outer housing by more 30 ° and generates a restoring torque, which is a relatively steep increase as a function of the respective angle of rotation and in a substantially large rotation angle as a function of the angle of rotation shows a possible large angle of rotation range. Furthermore, applications of the inventive Torsionsfederelements be proposed in connection with a device for transmitting power between two relatively movable bodies and in connection with a seat device.

The stated object is achieved by an elastomer torsion spring element having the features of patent claim 1.

The elastomer torsion spring element comprises an inner housing, an outer housing surrounding the inner housing and an elastomer body arranged in a gap between the inner housing and the outer housing. The inner housing has at least one contact surface on which the elastomeric body is in contact with the inner housing, and the outer housing has at least one contact surface on which the elastomeric body is in contact with the outer housing, wherein the elastomeric body with the Contact surface of the inner housing and the contact surface of the outer housing is firmly connected. Furthermore, the inner housing and / or the outer housing is rotatably arranged about a rotation axis and a rotation of the inner housing and / or the outer housing about a rotational angle about the axis of rotation can be carried out such that during rotation, the inner housing moves relative to the outer housing and thereby a deformation of the elastomeric body is generated so that the elastomeric body between the outer housing and the inner housing generates a restoring torque which is opposite to the rotation.

According to the invention, the respective contact surfaces of the inner housing and / or the outer housing are formed such that the contact surface of the inner housing in a plane perpendicular to the axis of rotation cutting plane has a non-circular cross-section and / or the contact surface of the outer housing in a plane perpendicular to the axis of rotation cutting plane has a non-circular cross-section having.

The elastomeric body may be made of rubber, for example.

This (inventive) elastomer torsion spring element differs from the above, from EP 1486142 A1 known elastomere torsion spring element essentially in that the contact surface of the inner housing in a plane perpendicular to the axis of rotation cutting plane and / or the contact surface of the outer housing in a plane perpendicular to the axis of rotation cutting plane is not circular, while in the case of EP 1486142 A1 known elastomer torsion spring element, the contact surface of the inner housing in a plane perpendicular to the axis of rotation cutting plane and / or the contact surface of the outer housing each have cross sections in the form of two concentric circles. In case of out EP 1486142 A1 known elastomer Torsionsfederelements the contact surfaces of the inner housing and the outer housing are thus formed rotationally symmetrical to the axis of rotation of the elastomer Torsionsfederelements. This has, inter alia, the result that the elastomer body of this elastomer torsion spring element is loaded exclusively on tension during a rotation of the inner housing relative to the outer housing and is thus deformed, the spatial distribution of the mechanical stress in the elastomeric body is in each case rotationally symmetrical with respect to the axis of rotation of the elastomer torsion spring element. In contrast, in the case of the elastomer torsion spring element according to the invention, at least one of the contact surfaces of the inner housing or the outer housing is not formed rotationally symmetrical to the axis of rotation. As a result of this difference, the respective elastomeric body of the inventive elastomer torsion spring element and the EP 1486142 A1 known elastomer torsion spring element deformed in different ways, when the inner housing of the respective elastomer Torsionsfederelements is rotated relative to the outer housing of the respective elastomer Torsionsfederelements about the respective axis of rotation. Due to the cross-sectional shape of the inner housing or the inner housing, the inventive elastomer torsion spring element generates a restoring torque, which in principle (in comparison to that of EP 1486142 A1 known elastomer torsion spring element) has a steeper rise as a function of the respective angle of rotation (in particular in the range of small rotation angle). In this comparison, it is assumed that the elastomeric bodies of the respective elastomer torsion spring element are made of the same elastomer, for example rubber. Accordingly, the inventive elastomer torsion spring element has the advantage that the inner housing must be rotated relative to the outer housing by a smaller angle of rotation about the axis of rotation to bias the elastomeric body such that the elastomer torsion spring element generates a predetermined minimum return torque. In this way, the elastomer torsion spring element according to the invention offers the advantage that the elastomer body must be stretched to a lesser extent and consequently less susceptible to wear and fatigue phenomena.

The inventive elastomer torsion spring element differs from the above, from GB 2070727 A known elastomer torsion spring element, inter alia, characterized in that the elastomeric body is firmly connected to the contact surface of the inner housing and the contact surface of the outer housing. This results in the advantage that the elastomeric body in the region of said contact surfaces can not move relative to the contact surface of the inner housing or against the contact surface of the outer housing, even if the inner housing is rotated relative to the outer housing about the axis of rotation and the elastomeric body is deformed , Characterized in that the elastomeric body is firmly connected to the inner housing and the outer housing, it is possible in the case of the inventive elastomer torsion spring element to introduce the elastomeric body into the space between the inner housing and the outer housing so that the elastomeric body ( at least in a certain position of the inner housing relative to the outer housing) is not biased and in particular is not compressed. This results - especially in comparison with the GB 2070727 A known elastomer torsion spring element - that the inner housing (starting from a certain basic position relative to the outer housing) over a rotation angle range of more than 30 °, for example by rotation angle in the range of 0 ° - 80 °, relative to the outer housing can be rotated without the Damage elastomeric body. Furthermore, the elastomeric body can be formed such that the elastomer torsion spring element according to the invention generates a restoring torque when the inner housing is rotated relative to the outer housing, which shows a substantially linear course as a function of the angle of rotation for angles of rotation in the range of, for example, 0 ° -80 ° ,

An embodiment of the inventive elastomer Torsionsfederelements is characterized in that the Contact surface of the inner housing and the contact surface of the outer housing are arranged relative to each other such that upon rotation of the inner housing and / or the outer housing around the axis of rotation at least in a predetermined rotation angle range a reduction of a distance between a defined point of the inner housing and a defined point of the outer housing hervorufbar is. In this case - because of the mentioned reduction in the distance between the respective points of the inner housing and the outer housing - the elastomer body is not exclusively loaded with a rotation of the inner housing relative to the outer housing to train, but in certain areas of the elastomeric body on pressure loaded. Accordingly, the respective deformation of the elastomer body is determined by superimposition of tensile and compressive stresses. The compressive load in certain areas of the elastomeric body compensates for tensile stress in other areas of the elastomeric body. As a result, the entire material of the elastomeric body is loaded non-homogeneously. This embodiment makes it possible to generate a restoring torque between the outer housing and the inner housing, which shows a particularly steep rise as a function of the respective rotation angle and in a particularly large rotation angle range a substantially linear course as a function of the rotation angle.

An embodiment of the inventive elastomer torsion spring element is characterized in that the contact surface of the inner housing and the contact surface of the outer housing in a plane perpendicular to the axis of rotation cutting plane have a non-circular cross-section and are arranged relative to each other, that by means of the rotation of the inner housing and / or the outer housing a pressure load in at least one region of the elastomeric body can be produced around the axis of rotation. In the case of this embodiment the elastomeric body is deformed at a rotation angle of the inner housing and / or the outer housing about the axis of rotation at least in a certain rotation angle range, that the elastomeric body in certain areas to train and other areas is subjected to pressure. Tensile and pressure are distributed within the elastomer body in such a way that the elastomer body is loaded non-homogeneously and the respective compressive stresses at least partially compensate for the respective tensile stresses. This embodiment makes it possible to generate a restoring torque between the outer housing and the inner housing, which shows a particularly steep rise as a function of the respective rotation angle and in a particularly large rotation angle range a substantially linear course as a function of the rotation angle.

In one embodiment of the elastomer torsion spring element, the contact surface of the inner housing and the contact surface of the outer housing are formed such that the respective rotation of the inner housing and / or the outer housing about the rotational axis by a rotational angle in a predetermined rotational angle range causes a linearly increasing with the respective rotational angle restoring torque , Since the contact surface of the inner housing or the contact surface of the outer housing are not rotationally symmetrical to the axis of rotation, the dependence of the restoring torque on the angle of rotation is substantially determined by the position that occupies the inner housing relative to the outer housing when the inner housing is in a predetermined basic position. The basic position of the inner housing relative to the outer housing can be chosen such that the restoring moment shows a linear course as a function of the angle of rotation in the respectively predetermined rotation angle range.

In one embodiment of the elastomer torsion spring element, the contact surface of the inner housing and / or the contact surface of the outer housing - each in a plane perpendicular to the axis of rotation cutting plane - polygonal. Such a configuration of the contact surfaces of the inner housing and the outer housing allows an application-specific, non-homogeneous deformation of the elastomer body as a function of the respective angle of rotation.

In one embodiment of the elastomer Torsionsfederelements the contact surface of the outer housing is at least partially cylindrical. As a result, the elastomer body is loaded non-homogeneously relative to the outer housing during a rotation of the inner housing.

In one embodiment of the elastomer Torsionsfederelements the contact surface of the outer housing - each rectangular in a plane perpendicular to the axis of rotation - rectangular, wherein at least two pairs opposite corners are rounded. Such an embodiment of the inner surface of the outer housing also allows an application-specific, non-homogeneous loading of the elastomeric body as a function of the respective angle of rotation.

In one embodiment of the elastomer torsion spring element, the contact surface of the outer housing contains two pairwise opposite, isosceles angular segments and two pairwise opposite semicircular segments, the ends of which are respectively connected to the ends of the rectangular angle segments. Based on measurement series has been found that the elastomer torsion spring element having a contact surface of the outer housing formed in this way has a characteristic curve in which the course of the restoring torque in relation to the rotation angle is linear.

In one embodiment of the elastomer Torsionsfederelements the contact surface of the inner housing - each in a plane perpendicular to the axis of rotation cutting plane - rectangular. Such a configuration of the contact surface of the inner housing proves to be particularly advantageous, as a result, certain areas of the elastomeric body are loaded with a rotation of the inner housing relative to the outer housing with compressive forces, which compensate for tensile forces in the elastomeric body. As a result of this non-homogeneous loading of the elastomer body, the restoring torque generated by the elastomer torsion spring element as a function of the rotational angle in a particularly large rotational angle range shows a linear course with a particularly steep rise. For example, the contact surface of the inner housing - in a plane perpendicular to the axis of rotation cutting plane - be square.

A further development of the aforementioned embodiments of the elastomer torsion spring element comprises a holding element which is designed to (i) hold the inner housing in a predetermined basic position relative to the outer housing, in which basic position the elastomeric body has a predetermined elastic deformation and between the outer housing and generating a restoring torque equal to a predetermined minimum value to the inner housing, and (ii) releasing rotation of the inner housing relative to the outer housing by a rotational angle about the rotational axis in a rotational direction in which the restoring torque increases with increasing rotational angle.

In this variant, the inner housing, if it is in the normal position, rotated only in one direction of rotation about the axis of rotation and thus be rotated relative to the outer housing: The holding member blocks rotation in the other direction when the inner housing in the Home position is located. In the present case, the elastomeric body always has an elastic deformation, so that the elastomer torsion spring element generates a restoring torque with a rotation of the inner housing relative to the outer housing, the size of which is always greater than zero. When the inner housing is in the home position, then the restoring torque generated by the elastomeric body is received by the retaining element. If the inner housing, starting from the basic position, rotated relative to the outer housing, then the elastomer body between the outer housing and the inner housing generates a restoring torque, which steadily increases with increasing angle of rotation, starting at the minimum value. This minimum value thus defines the minimum restoring torque that can be generated with the elastomer torsion spring element. The minimum value is determined by the magnitude of the elastic stress (hereinafter also referred to as "preload of the elastomeric body") which the elastomeric body has when the inner housing is in the home position relative to the outer housing. This minimum value can be set as needed. This variant of the elastomer torsion spring element can advantageously be used in devices for force transmission between two bodies, if during a relative movement between the two bodies a restoring torque is to be generated which is always greater than or equal to a minimum value (greater than 0).

The bias of the elastomeric body can for example be realized such that the respective elastomer torsion spring element is first made so that the respective elastomeric body is firmly connected to the contact surfaces of the respective inner housing and the contact surfaces of the respective outer housing such that the elastomeric Body is initially undeformed and therefore no mechanical Having tensions when the inner housing is in a starting position relative to the outer housing. Subsequently, the inner housing and / or the outer housing is rotated about the axis of rotation in a predetermined rotational direction by an angle of rotation until the rotational angle relative to the initial position reaches a predetermined value (hereinafter referred to as "angular offset relative to the starting position" called), so that the elastomer body The retaining element can then be installed such that further rotation of the inner housing or the outer housing in the predetermined direction of rotation is possible, but a corresponding rotation in the opposite direction is blocked as soon as the respective angle of rotation relative to Starting position is equal to the said "angular offset" is.

The elastomer torsion spring element according to the invention has the advantage that the "angular offset" can be chosen to be relatively small in order to ensure that the restoring torque assumes a certain minimum value (for example compared to FIG EP 1486142 A1 known elastomer torsion spring element). This is gentle on the elastomeric body and thus conducive to a long life of the elastomeric body.

The holding element may be a rod in a simple embodiment, which is arranged on an end face of the inner housing and perpendicular to the axis of rotation and is further firmly connected to the inner housing. Further, a mechanical stop for the rod may be attached to the outer housing, which is arranged such that the rod abuts against the stop during rotation of the inner housing in a certain direction of rotation, so that further rotation in the same direction of rotation is blocked. A rotation of the inner housing in the opposite direction of rotation is released. The position of the stop determines in this case the basic position of the inner housing relative to the outer housing. The mechanical stop or the outer housing takes on the bias of the elastomeric body, respectively, when the inner housing is in the normal position.

The inner housing may be held in the predetermined basic position relative to the outer housing of the holding element, for example, such that the restoring torque increases linearly with increasing rotational angle at the respective released from the holding element rotation of the inner housing relative to the outer housing.

In a variant of the above-mentioned embodiment, the holding element comprises at least one clamping element, which has a first portion which is in a fixed engagement with the inner housing, and a second portion which - when the inner housing is in the predetermined basic position relative to the outer housing - Strikes against a portion of the outer housing and releases a rotation of the inner housing and the outer housing in relation to each other about the axis of rotation in that direction of rotation, in which the restoring torque increases. In an alternative to this variant, the holding element may also comprise at least one clamping element which has a first portion which is in a fixed engagement with the outer housing, and has a second portion which - when the inner housing in the predetermined basic position relative to the outer housing abuts against a portion of the inner housing and releases a rotation of the inner housing and the outer housing in relation to each other about the axis of rotation in the rotational direction in which the restoring torque increases. The clamping element can be used in each case in the above-mentioned variants as a "tool" to - by means of a rotary movement of the clamping element about the axis of rotation of the elastomer torsion spring element - to rotate the inner housing relative to the outer housing and thereby to provide the elastomeric body with that mechanical tension (preload), which is maintained by means of the retaining element, when the inner housing by means of the retaining element in the basic position relative to the outer housing is held. This elastomer torsion spring element has the advantage that the holding element can be realized by simple means: According to the invention, the inner housing and / or outer housing have a non-circular cross section, either the outer housing or the inner housing can serve as a mechanical stop for the respective clamping element, wherein the When the outer housing or the inner housing rotates about the axis of rotation, the clamping element in each case follows a circular path around the axis of rotation. In order to achieve a predetermined bias, the clamping element must be brought only in a suitable position relative to the outer housing or the inner housing.

In a variant of the elastomer torsion spring element, the inner housing comprises a recess, wherein the first portion of the clamping element is rotationally rigidly inserted into this recess in the inner housing and the second portion of the clamping element - when the inner housing is in the predetermined basic position relative to the outer housing - against a portion of the outer casing strikes. The latter section of the outer housing can be arranged, for example, on an outer side of the outer housing. As a result, the angle between the inner housing and the outer housing is held offset in relation to each other by a predetermined "angular offset".

The use of the clamping elements has several advantages. The respective clamping element can be produced inexpensively with a low use of material. Also, the assembly can be of the clamping element on the inner housing and on the outer housing of the elastomer Torsionsfederelements make very easily and in a short time. In addition, no components must be firmly connected to the inner housing or the outer housing. Advantageously, a plurality of elastomer torsion spring elements can be biased in parallel by one associated clamping elements in one step, whereby the assembly time is further shortened.

Preferably, the inner housing and the outer housing are arranged to each other such that the elastomeric body at a predetermined orientation of the outer housing relative to the inner housing has a bias. It is also possible for a plurality of elastomer torsion spring elements to be arranged parallel to one another, for example plugged onto a bearing shaft. The elastomer torsion spring elements can be biased to different degrees, wherein the respective outer housing can still be aligned with each other.

The inventive elastomer torsion spring element can be used advantageously in particular in a device for transmitting power between a first body and a second, relative to the first body movable body. Such a power transmission device may comprise, for example, at least one elastomer torsion spring element (according to the invention), first coupling means for coupling the first body to the outer housing of the respective elastomer torsion spring element and second coupling means for coupling the second body to the inner housing of the respective elastomer torsion spring element. In this case, the first body can be coupled to the outer housing of the respective elastomer torsion spring element in such a way and the second body can be coupled to the inner housing of the respective elastomer torsion spring element in such a way Movement of the first body relative to the second body, a rotation of the inner housing and / or the outer housing is performed by a rotational angle about the axis of rotation at which rotation, the inner housing moves relative to the outer housing and thereby a deformation of the elastomeric body is generated, so that the elastomeric Body generates a restoring torque between the outer housing and the inner housing, which is opposite to the rotation. The respective coupling means may for example be realized as a material or non-positive connection between the respective components to be coupled or comprise any device which is suitable for a relative movement between the first and the second body in a rotation of the inner housing and / or the outer housing implement the respective elastomer Torsionsfederelements.

A variant of this device for transmitting force may comprise a plurality of the elastomer torsion spring element according to the invention, wherein the respective elastomer torsion spring elements are arranged side by side such that the inner housing and / or the outer housing of the respective elastomer torsion spring elements are rotatably arranged about the same axis of rotation. In this case, the entirety of all elastomer torsion spring elements produce a restoring torque resulting from the superposition of those restoring torques generated by the individual elastomer torsion spring elements (coupled respectively to the first and second bodies).

The device for power transmission can be modular. The entirety of all elastomer torsion spring element can for example form an assembly, which can be transported or mounted as a whole. This simplifies the manufacture and maintenance of the power transmission device. The entirety of all elastomer torsion spring elements can be pre-assembled in an assembly, for example, and then combined with other components.

In order to combine a plurality of elastomer torsion spring elements to form an assembly, for example, the inner housing of the respective elastomer Torsionsfederelemente can be rigidly connected together and / or the outer housing of the respective elastomer Torsionsfederelemente are rigidly interconnected. For this purpose, the respective inner housing can be set, for example, on a common bearing shaft and fixed thereto.

The elastomer torsion spring elements of the respective assembly may optionally have different characteristics: The different elastomer torsion spring elements may differ, for example, with respect to the course of the restoring torque as a function of the angle of rotation. Various elastomer torsion spring elements may, for example, comprise elastomer bodies which may be biased differently, so that different elastomer torsion spring elements provide different sized restoring torques when the inner housing of the respective torsion spring element is in the normal position relative to the outer housing. Therefore, by a combination of different elastomer torsion spring elements having different characteristics, power transmission devices having different characteristics can be manufactured as needed or, e.g., in a simple, inexpensive manner. by replacing individual elastomer torsion spring elements, suitably modified.

The inventive elastomer torsion spring element or the aforementioned device for power transmission can be used advantageously for the realization of a seat device become. A seat device designed according to the invention may comprise, for example, a seat, a back support and a support for the back support and / or the seat, wherein the back support and / or the seat is pivotally hinged to the carrier and further comprising a device for transmitting power between the back support and the support and / or for power transmission between the seat and the carrier is present and the device for transmitting force comprises at least one elastomer torsion spring element according to the invention. In this case, the carrier is coupled to the outer housing of the respective elastomer Torsionsfederelements and the back support and / or the seat by means of the second coupling means with the inner housing of the respective elastomer Torsionsfederelements means of the first coupling means. Alternatively, the carrier can also be coupled by means of the second coupling means to the inner housing of the respective elastomer Torsionsfederelements and the back support and / or the seat by means of the first coupling means with the outer housing of the respective elastomer torsion spring element.

Fig. 1

eine Ausführungsform eines Stuhls;

Fig. 2

eine schematische Seitenansicht eines Elastomer-Torsionsfederelements in einer ersten beispielhaften Ausführungsform;

Fig. 3A

ein Diagramm mit zwei Kennlinienverläufen von Rückstelldrehmomenten als Funktion des Drehwinkels für ein Elastomer-Torsionsfederelement in einer beispielhaften Ausführungsform der Erfindung (Kurve K1) und ein herkömmliches Elastomer-Torsionsfederelement (Kurve K2);

Fig. 3B

ein Diagramm mit Kennlinienverläufen von Rückstelldrehmomenten als Funktion des Drehwinkels für verschiedene Ausführungsformen Elastomer-Torsionsfederelemente gemäss der Erfindung;

Fig. 4

das Elastomer-Torsionsfederelement in der ersten beispielhaften Ausführungsform, welches durch ein Halteelement vorgespannt ist;

Fig. 5

eine beispielhafte Verwendung von vier Elastomer-Torsionsfederelementen in der ersten beispielhaften Ausführungsform, welche in einem Kraftsystem eines Stuhls eingebaut sind;

Fig. 6

ein Elastomer-Torsionsfederelement in einer zweiten beispielhaften Ausführungsform, welches durch ein Halteelement vorgespannt ist;

Fig. 7A-7C

eine weitere beispielhafte Verwendung von drei Elastomer-Torsionsfederelementen in der zweiten beispielhaften Ausführungsform, welche jeweils durch ein Halteelement vorgespannt sind und welche in ein Kraftsystem eines Stuhls eingebaut sind;

Fig. 8A-8C

ein Elastomer-Torsionsfederelement in der zweiten beispielhaften Ausführungsform, mit verschiedenen Stellungen des Innengehäuses relativ zum Aussengehäuse, wobei das Innengehäuse und das Aussengehäuse in Relation zueinander um unterschiedliche Drehwinkel verdreht sind;

Fig. 9

die Elastomer-Torsionsfederelemente in der zweiten beispielhaften Ausführungsform, welche zu einem Kraftsystem zusammengesetzt sind, welches in einen Träger eines Stuhls montiert ist; und

Fig. 10A-10E

eine Spannvorrichtung zum Herstellen des in Fig. 7A-7C dargestellten Kraftsystems.

Further details of the invention and in particular exemplary embodiments of the inventive elastomer torsion spring element and applications of the inventive elastomer Torsionsfederelements in a device for power transmission for a seat device are explained below with reference to the accompanying drawings. Show it:

Fig. 1

an embodiment of a chair;

Fig. 2

a schematic side view of an elastomer torsion spring element in a first exemplary embodiment;

Fig. 3A

a graph with two characteristic curves of restoring torque as a function of the angle of rotation for an elastomer torsion spring element in an exemplary embodiment of the invention (curve K1) and a conventional elastomer torsion spring element (curve K2);

Fig. 3B

a diagram with characteristic curves of restoring torques as a function of the angle of rotation for various embodiments elastomer torsion spring according to the invention;

Fig. 4

the elastomer torsion spring member in the first exemplary embodiment, which is biased by a holding member;

Fig. 5

an exemplary use of four elastomer torsion spring elements in the first exemplary embodiment, which are installed in a power system of a chair;

Fig. 6

an elastomer torsion spring member in a second exemplary embodiment which is biased by a holding member;

Figs. 7A-7C

another exemplary use of three elastomer torsion spring elements in the second exemplary embodiment, which are each biased by a holding element and which are installed in a power system of a chair;

Figs. 8A-8C

an elastomer torsion spring element in the second exemplary embodiment, with different positions of the inner housing relative the outer housing, wherein the inner housing and the outer housing are rotated in relation to each other by different rotational angles;

Fig. 9

the elastomer torsion spring members in the second exemplary embodiment, which are assembled into a power system mounted in a support of a chair; and

10A-10E

a tensioning device for producing the in Figs. 7A-7C illustrated force system.

FIG. 1 shows an exemplary embodiment of a seat device in the form of a chair 1. The chair 1 is designed as an office swivel chair and mounted on a support column 2, via which the chair 1 is height adjustable and rotatable by 360 °. At the upper end of the support column 2, a support 42 is mounted, which is arranged substantially horizontally. The carrier 42 serves as a housing for accommodating mechanical elements which will be described later. On the carrier 42, a back support 44 is pivotally connected via a bearing shaft 26. At the other end of the back support 44, a back part 3 is connected, which serves to receive a substantially vertically arranged backrest 4. The back part 3 can be displaceable at the connection to the back support 44. Also, the backrest 4 can be adjustable in height.

The carrier 42 includes a seat support, not shown in the figure, on which a substantially horizontally arranged seat 5 is mounted. The seat carrier may also be pivotally hinged to the carrier 42. Due to the pivotable articulation of the back support 44 and the seat support on the carrier 42, it is possible that a on the Chair 1 seated person with the backrest 4 can lean back and at the same time in synchronism with the seat support and thus the seat 5 can be pivoted. To this end, an elastomeric torsion spring member (not shown) disposed in the bracket 42 applies restoring torque between the bracket 42 and the back support 44, the return torque being directed in a direction opposite to the pivoting direction when the back bracket 44 is pivoted relative to the bracket 42 ,

FIG. 2 shows a schematic side view of the elastomer torsion spring element 10, which is executed in a first embodiment, in a plane perpendicular to a rotation axis 6 cutting plane. The elastomer torsion spring element 10 includes an inner housing 12 and an outer housing 14. In an intermediate space between the inner housing 12 and the outer housing 14, an elastomeric body 16 is arranged.

The inner housing 12 has on its outer side a contact surface 12a on which the elastomeric body 16 is in contact with the inner housing. Furthermore, the outer housing 14 has on its inner side a contact surface 14a on which the elastomeric body 16 is in contact with the outer housing 14. The contact surface 12a of the inner housing 12 and the contact surface 14a of the outer housing 14 enclose the axis of rotation 6 in each case in an annular manner. Accordingly, in the present example, the elastomeric body 16 forms a closed ring surrounding the axis of rotation 6.

The elastomeric body 16 is made of an elastomer, ie a solid and elastically deformable material. The elastomeric body 16 is formed such that it is fixedly connected to the contact surface 12 a of the inner housing 12 and the contact surface 14 a of the outer housing 14, ie upon movement of the inner housing 12 relative to the outer housing 14 (For example, upon rotation of the inner housing 12 or the outer housing 14 about the axis of rotation 6) there is no displacement of the surfaces of the elastomeric body 16 adjacent to the contact surfaces 12a and 14a relative to the contact surfaces 12a and 14a. The elastomeric body 16 may, for example, be connected in a material-locking or form-fitting manner to the contact surfaces 12a or 14a with the inner housing 12 and the outer housing 14.

A particularly suitable for the production of the elastomeric body 16 elastomer is for example rubber, which is not only an elastically deformable and high-strength material, but also in a simple manner with the contact surfaces 12a and 14a can be firmly connected, for example by means of vulcanization.

The inner housing 12 and the outer housing 14 are made of a solid material, such as steel. The respectively adjacent to the elastomer body 16 contact surfaces 12a and 14a of the inner housing 12 and the outer housing 14 differ - in a plane perpendicular to the axis of rotation 6 sectional plane - at least partially from a circular shape. As a result of this particular shape, in some regions of the elastomeric body 16, when rotating the inner housing 12 about the axis of rotation 6 in relation to the outer housing 14, pressure loads occur which compensate for tensile loads therein. Thus, the elastomeric body 16 is advantageously loaded non-homogeneously.

In the FIG. 2 For example, the inner casing 12 is shown in a "non-rotated" state (solid line) and a "twisted state" (dashed line), and the inner casing 12 is rotated around the rotation axis 6 in the twisted state by a rotational angle φ clockwise compared to the untwisted state is while the position of the outer housing 14 it remains unchanged. It is assumed that the elastomeric body 16 is not biased in the case of the untwisted state, ie has no mechanical stresses. In the untwisted state, the distances from the upper right corner and the lower left corner of the inner housing 12 to respectively defined points on the inside of the outer housing 14 are shown with arrows x1 and y1, respectively. In the twisted state, the distances from the upper right corner and the lower left corner of the inner housing 12 to respectively defined points on the inner side of the outer housing 14 are indicated by arrows x2 and y2, respectively. Like in the FIG. 2 the distance x2 is less than x1 and the distance y2 is less than y1. In these areas, thus, the elastomeric body 16 is compressed when the inner housing 12 is rotated about the rotation axis 6 and thereby rotated relative to the outer housing 14. From these respective compressions result the above-mentioned pressure loads.

After a rotation of the inner housing 12 by the rotational angle φ about the axis of rotation 6, the elastomer body 6 is deformed and generates between the outer housing 14 and the inner housing 12, a restoring torque D, which is opposite to the rotation and increases with the rotation angle φ.

The fact that the distances x2-x1 and y2-y2 are reduced by the rotation angle φ when the inner housing 12 rotates is a consequence of the cross-section of the contact surface 12a and the contact surface 14a (in a sectional area perpendicular to the axis of rotation 6) ) is not circular. The geometric deviation of the mentioned cross-sections of the contact surfaces 12a and 14a of a circular shape has the consequence that upon rotation of the inner housing 12 by the rotation angle φ results in a spatial distribution of the mechanical stress in the elastomeric body 6, which is not rotationally symmetric to the axis of rotation 6, in contrast to the spatial distribution of the mechanical stresses in an elastomer torsion spring according to EP 1486142 A1 which is in each case rotationally symmetrical to the axis of rotation 6. These differences in the voltage distributions lead to significant differences in the dependencies of the restoring torque D as a function of the rotation angle φ. In particular, these differences lead to the elastomer torsion spring element according to the invention exhibiting a significantly greater increase in the restoring torque D as a function of the angle of rotation φ than the elastomer torsion spring element according to FIG EP 1486142 A1 (which will be explained in more detail below).

In the in FIG. 2 In the embodiment shown, the contact surface 12a of the inner housing 12 adjoining the elastomeric body 16 is square-shaped. Here, the inner housing 12 is formed as a square sleeve (square), which has a parallel to the axis of rotation 6 extending, continuous channel 12.1 with a square cross-section. This has the advantage that a square bearing shaft (not shown) formed with the same dimensions can be accommodated radially in a form-fitting manner in the channel 12.1 of the inner housing 12.

Like in the FIG. 2 can be seen, between the inner housing 12 and the outer housing 14 in the untwisted state of the inner housing 12 (solid line) before a rotational offset. More specifically, the outer surfaces of the inner housing 12 and the (linearly extending) outer surfaces of the outer housing 14 are not aligned parallel to each other (rotational offset). The size of this rotational offset is a further parameter which has an influence on the course of the return torque D as a function of the rotational angle φ.

On the outer surface of the outer housing 14, an outer housing cam 18 is formed, which for engagement with a (in Fig. 2 not shown) blocking element, which in the following in connection with the Figures 5 and 9 is still explained, can serve.

The adjacent to the elastomer body 16 contact surface 14a of the outer housing 14 has a contour which is to be regarded as a combination of a rectangle and a circle. More specifically, the contour of the outer housing 14 is composed of two pairs equal isosceles angular segments, which in the present example form an angle of 90 °, and of two pairs opposite semicircular segments, the ends of which are respectively connected to the ends of said angle segments. It has been found on the basis of several series of measurements that this "lemon-shaped" contour of the outer housing 14, in combination with the square contour of the inner housing 12, is particularly advantageous for providing an elastomeric torsion spring element 10 whose characteristic of the restoring torque D in relation to the rotation angle φ linearly in almost all areas of the rotation angle φ.

FIG. 3A 11 is a graph showing each of the above-mentioned characteristic curve K1 (restoring torque D in relation to the rotational angle φ) of the elastomer torsion spring member in the embodiment of the present invention and a characteristic curve K2 of a conventional elastomer torsion spring member (as shown in FIG EP 1486142 A1 known), wherein the curves K1 and K2 have each been determined for elastomer torsion spring elements in which the respective elastomers of the same material (rubber), so that the curves K1 and K2 associated elastomer Torsionsfederelemente essentially only in terms the shapes of the respective inner housing and the shapes of the respective outer housing differ. The curves K1 and K2 show first that the return torque D increases with increasing rotation angle φ. The maximum angle of rotation is 70 ° in this example. The characteristic curve K1 of the elastomer torsion spring element was determined on the basis of measurement series, which correspond to the in FIG. 2 shown elastomer torsion spring element (lemon shape) were performed. In Fig. 3A the cross-sections of those elastomer torsion spring elements are shown below said diagram, for which said curves K1 and K2 were determined: The two solid lines 14a and 12a give (in this order) the contour of the contact surface of the outer housing or the contour of the contact surface the inner casing of the elastomeric torsion spring member to which the characteristic K1 is associated; the two dashed lines 14a and 12a indicate (in this order) the contour of the contact surface of the outer housing or the contour of the contact surface of the inner housing of the elastomer Torsionsfederelements, which is associated with the characteristic K2. In order to allow a comparison between the cross-sectional shapes and the dimensions of the two elastomer torsion spring elements are in Fig. 3A the respective cross sections of the two elastomer torsion spring elements shown superimposed.

As can be seen from the diagram, the characteristic curve K1 of the elastomer torsion spring element according to the embodiment of the present invention advantageously extends linearly in almost all rotation angle ranges. In contrast, the characteristic curve K2 of the conventional elastomer torsion spring element is non-linearly (progressively) increasing particularly in the initial rotation angle range. The diagram also shows that the characteristic curve K1 of the elastomer torsion spring element according to the embodiment has the present invention in comparison to the characteristic curve K2 of the conventional elastomer Torsionsfederelements a greater slope. Thus, even at low angles of rotation φ, a larger restoring torque D acts. As a result, the elastomer material is less deformed compared to the elastomer material of the conventional elastomer torsion spring element at a same restoring torque D. Advantageously, the elastomer material is thus less loaded and therefore less fatigued. This results in a longer life.

It is known that elastomer torsion spring elements can only be rotated up to a certain maximum angle of rotation. Turning beyond this maximum angle of rotation would result in excessive nonlinearities and eventually tearing of the elastomeric material. In the measurement series for plotting the characteristic curves K1 and K2, the elastomer torsion spring elements to be compared were twisted up to a rotation angle φ of at most 70 °.

Fig. 3B shows in each case the course of the restoring torque D as a function of the rotational angle φ for six different embodiments of the elastomer torsion spring element according to the invention. The curves for the course of the return torque D corresponding to the various embodiments are numbered (1-6), respectively. All embodiments have in common that the outer housing of the respective elastomer Torsionsfederelements has a square profile, wherein the cross section of the contact surface of the respective outer housing is a square with the side length 60 mm (relative to a sectional surface perpendicular to the axis of rotation). The various embodiments differ in that the cross section of the contact surface of the inner housing for the various embodiments have different shapes and different sizes. In the case of the curves 1 and 2, the cross-section of the contact surface of the inner case is a circle of diameter 10mm and 20mm, respectively (in this order). In the case of the curves 3-6, the cross section of the contact surface of the inner housing is a square with side lengths of 20mm, 25mm, 30mm and 40mm respectively (in that order). In the case of curves 3-6, it is assumed that the contact surfaces of the inner housing are arranged parallel to corresponding contact surfaces of the outer housing, if the rotation angle φ = 0 and the restoring torque D = 0. In all cases it is assumed that the respective elastomeric body consists of the same material (rubber). A comparison of the curves 1-6 shows that the restoring torque D increases more in the range "small" rotation angle with the rotation angle φ, the larger in the case of the curves 1 and 2 of the respective diameter and in the case of the curves 3-6 the respective side length the cross section of the contact surface of the inner housing is. Furthermore, it is found that a square profile of the inner housing leads to a steeper increase of the restoring torque D as a function of the rotational angle φ than a round profile of the inner housing with a correspondingly large diameter. Furthermore, it can be seen that the curves 1-5 are linear in the range 0-70 °, while the curve 6 shows a progressive increase above 40 °. If, with regard to a particular application, there is an interest that the return torque D as a function of the rotation angle φ over a largest possible rotation angle range (eg 0-70 °) shows a linear course, it is advantageous if the cross-sectional area of the inner housing in relation to the cross-sectional area of the outer housing does not exceed a certain value (eg 0.6 in the present example).

FIG. 4 shows that in FIG. 2 shown elastomer torsion spring element 10 in a first embodiment of the present invention with a holding member 19 in one Perspective view. The holding element 19 serves to hold the inner housing 12 and the outer housing 14 in a "basic position" relative to each other, in which the elastomeric body 16 has a mechanical stress (preload) and thus between the inner housing 12 and the outer housing 14, a restoring torque D. generated, which is different from zero. In this "basic position" the inner housing is opposite to the "unrotated" position (without pretension) according to Fig. 2 by a rotational angle Δφ (hereinafter referred to as "biasing angle") rotated, with respect to Fig. 2 clockwise and in terms of Fig. 4 in the counterclockwise direction. The holding element 19 contains in this example two clamping elements 20, which are each plugged onto one of the end faces of the elastomer torsion spring element 10. The tensioning element 20 is a substantially flat plate which is punched out in the center region such that two opposing flanges 22 remain. These flanges 22 are each bent by 90 ° inwards (in the plane of the figure). At an outer region of the clamping element 20 are tabs 24 ', 24 "formed, which are also bent by 90 ° inwards.

For mounting the tensioning element 20 on the elastomer torsion spring element 10, the flanges 22, which are designed such that their outer regions are positively connected to the inner surface of the inner housing 12 are connected by a first distance in the inner housing 12. Then, the clamping element 20 and thus radially positively connected to the inner housing 12, with a fixed outer housing 14, counterclockwise rotated by a certain angle (for example, 20 °) in relation to the outer housing 14.

Subsequently, the clamping element 20 is pressed with its flanges 22 completely into the channel 12.1 of the inner housing 12, wherein at the same time the tabs 24 ', 24 "occupy a positive connection with the outer surface of the outer housing 14. Mounted in this way, the tensioning element 20 maintains the pretensioning. Specifically, the pretensioning angle Δφ can no longer be undershot, since the tabs 24', 24 "strike against the outer surface of the outer housing 14. However, it is possible to increase the rotational offset (also in the counterclockwise direction) between the inner housing 12 and the outer housing 14. With an increase in this rotational offset, the inner regions of the tabs 24 ', 24 "are dragged along the outer surface of the outer housing or lifted off from it.To prevent destruction of the elastomer Torsionsfederelements 10, in this example, a maximum angle of rotation between the inner housing 12 and outer housing 14th (For example, 70 °.) At the maximum rotation angle φ namely the tab 24 'abuts against the outer housing cam 18, whereby a further rotation is advantageously prevented.

FIG. 5 shows three elastomer Torsionsfederelemente 10'-10 "', each with frontally mounted clamping elements, as detailed in FIG. 4 shown. These elastomer torsion spring elements 10'-10 "'are plugged via their inner housing onto a bearing shaft 26. The bearing shaft 26 and the respective regions of the inner housing of the respective elastomer torsion spring elements 10'-10"' are dimensioned in such a way that a radially form-locking connection is produced is. The bearing shaft 26 is also plugged radially into an inner housing of a base-elastomer Torsionsfederelements 28 in a form-fitting manner. This arrangement forms a power transmission device 30 for a (in Fig. 5 not shown, but in Fig. 1 chair), hereinafter referred to as "force system" 30. This force system 30 serves in principle for applying a restoring torque to a back support or a seat of the chair in the event that the back support or the seat is pivoted relative to a support for the back support or the seat. The power system 30 is connected to the substantially rigid support (not shown) of the chair via the outer housing of the base elastomer torsion spring element 28. The bearing shaft 26 is rotatably connected at its axial end portions with the back support. If a person sitting on the chair leans back with the back part, the back support and any seat support that may be hinged in sync with it are swiveled. Since the back carrier is rotatably connected to the bearing shaft 26, the bearing shaft 26 is rotated (in this example, the rotation is counterclockwise). This rotation is always counteracted by at least one restoring torque, which is caused by the base elastomer Torsionsfederelements 28.

In the FIG. 5 Furthermore, blocking elements 32'-32 "'are shown, which are articulated on a shaft running parallel to the bearing shaft 26. The blocking elements 32'-32"' are actuatable via locking cams 34'-34, "'which are mounted radially on a camshaft 36 When activated, the blocking elements 32'-32 "'are each pivoted separately from one another discretely into two different positions. In the in the FIG. 5 As shown, all locking elements 32'-32 "'are currently arranged such that they are not in contact with the outer housing cams 18'-18"', which are formed on the respective outer casings of the elastomer torsion spring elements 10'-10 "' The locking elements 32'-32 "'and the elastomer torsion spring elements 10'-10"' are in a decoupled state. The camshaft 36 extending parallel to the bearing shaft 26 can be rotated such that the individual locking cams 34 ' 34 "'assume a changed position in which one or more locking elements 32' or 32" or 32 "'(depending on the respective position of the camshaft 36 after the respective rotation) are pivoted to a position in which those locking elements 32 'and 32 "and 32"', which were pivoted during the respective rotation of the camshaft 36, with the respective outer housing cams 18 'and 18, respectively "or 18 '" of the respective elastomer torsion spring elements 10'-10 "' brought into contact and thus with the respective elastomer Torsionsfederelementen 10'-10"'are coupled (in Fig. 5 Not shown). In this coupled state fix those blocking elements 32 'and 32 "or 32"', which were pivoted at the respective rotation of the camshaft 36, the outer housing of the respective elastomer torsion spring elements 10'-10 "'in a predetermined position.

At the in Fig. 5 shown example, there is no coupling between the locking elements 32'-32 '''and the outer housing cams 18'-18 "', so that in the above-mentioned reclining a person sitting on the chair, the bearing shaft 26 would rotate counterclockwise and the elastomeric torsion spring elements 10'-10 "'as a whole would follow the rotation of the bearing shaft 26. As described above, the total restoring torque D provided by the power system 30 in this example is identical to the restoring torque caused solely by the base elastomer torsion spring member 28. Accordingly, the elastomer torsion spring elements 10'-10 '''do not contribute to the restoring torque D provided by the power system 30.

With a changed rotation of the camshaft 36, for example, a coupling between one or more locking elements 32'-32 "'and one or more outer housing cams 18'-18"' can be realized. Thus, those elastomer torsion spring elements 10'-10 "'which are coupled to one of the respective blocking elements 32'-32"', locked to their outer housings. As a result, all of the restoring torque provided by the power system 30 is the sum of all of the restoring torques transmitted by the base elastomer torsion spring element 28 and those elastomer torsion spring elements 10'-10 "', respectively respective locking elements 32'-32 "'are arrested, caused. More specifically, the total restoring torque can be adjusted depending on the rotation of the camshaft 36.

Like in the FIG. 5 As a result, the elastomer torsion spring elements 10 '' cause greater restoring torque than the elastomer torsion spring element 10 '. ', which causes a greater restoring torque than the elastomer torsion spring element 10'. By a corresponding separate coupling or decoupling of individual elastomer Torsionsfederelementen 10'-10 "'thus a total of eight different restoring torques are selectable .This restoring torques are switchable, each corresponding to the individual weight of a person sitting on the chair suitable coupling or decoupling of the respective elastomer torsion spring elements 10'-10 "'and the respective locking elements 32'-32"' experience a person with, for example, a weight of 45 kg ergonomically adjusted restoring force, as well as a person with a weight of example 120 kg can experience an ergonomically adjusted restoring force Due to the above mentioned eight different steps, people with a weight of between 45 kg and 120 kg, for example, can be ergonomically optimally supported greatly increased.

FIG. 6 shows an elastomer torsion spring element 10 in a second embodiment. In this embodiment, the inner housing (not shown) and the outer housing 14 are biased in relation to each other by a clamping element 38. For a more detailed description of this elastomer torsion spring is on the Figures 7A-7C directed.

Figures 7A-7C each show a force system 30 in different views, which, similar to that in FIG. 5 also comprises three elastomer torsion spring elements 10'-10 "'. These three elastomer torsion spring elements 10'-10"' are each in the form shown in FIG FIG. 6 illustrated embodiment executed. The power system 30 further includes a base elastomer torsion spring member 28 and a shaft 26. In the illustrated example, tension members 38'-38 "" different from those shown in FIGS FIGS. 4 and 5 differ shown clamping elements 20. The clamping elements shown 38 '-38 "" are plate-like elements whose inner areas are punched rectangular. Here, the contour of the punched form fit to the outer contour of the (square) bearing shaft 26 is adjusted. At the outer regions of the clamping elements 38 '- 38''''bulges39'-39"" are formed, each containing a vertical through hole.

When mounting the power system 30, the bearing shaft 26 and the inner housing of the base elastomer Torsionsfederelements 28 are connected to each other in a radially form-fitting manner. Subsequently, a first clamping element 38 'attached via its punched onto the bearing shaft 26, so that between the bearing shaft 26 and the clamping element 38' is a radially positive connection is made. Subsequently, a first elastomer torsion spring element 10 'on the Bearing shaft 26 attached. Following this step, a further clamping element 38 "is placed, etc., after all three elastomer torsion spring elements 10'-10"'are placed on the bearing shaft 26, each with interposed clamping elements 38'-38'', finally the last clamping element 38th "" frontally attached.

Subsequently, the elastomer torsion spring elements 10'-10 "'either biased individually or simultaneously, for example, by their outer housing, with radially fixed bearing shaft 26, clockwise rotated about the longitudinal direction of the bearing shaft 26. This rotation takes place up to a rotational angle at which Pins 40 ', 40 "through the respective holes of the bulges 39'-39" "can be inserted therethrough. After the pins 40 ', 40 "have been pushed through these bores, the introduction of force to turn over the outer casings is ended. In this state, the individual elastomer torsion spring elements 10'-10"' remain in this position, since the outer surfaces of the outer casings are now opposite Thus, it is no longer possible that the respective outer housing is rotated back to the initial state.

An advantage of the arrangement and the design of the clamping elements 38'-38 "" is that now, in contrast to the in the FIGS. 4 and 5 Thus, the bearing shaft 26 is in radial positive engagement with the entire inner surface of the respective inner housings, thereby creating a clearance between the bearing shaft 26 and the inner housing the elastomer torsion spring elements 10'-10 "'avoided. In case of in the FIGS. 4 and 5 In contrast, a bearing clearance occurs, which is based on the fact that the initiation of the restoring torques of the respective Elastomer Torsionsfederelemente 10'-10 '''in the bearing shaft 26 in sections via the flanges 22 and the inner housing of the respective elastomer Torsionsfederelemente 10'-10 "' therefore can not be in mechanical contact with the bearing shaft 26 (see FIGS. 4 and 5 ).

Another advantage of in Figures 7A-7C example shown is that the mounting opposite to in the FIGS. 4 and 5 shown example, in which each elastomer torsion spring element was previously populated with its clamping elements 20, is much easier. In addition, the assembly time is greatly reduced. Another advantage is the much simpler and less time-consuming production of the individual clamping elements 38'-38 "". These can be produced inexpensively only by punching.

Figures 8A-8C each show an elastomer torsion spring element 10 in the second exemplary embodiment, in which the inner housing 12 and the outer housing 14 are rotated in relation to each other in sequence of the figures by an increasing angle of rotation φ against each other. In Fig. 8A For example, the elastomeric torsion spring member 10 is shown in a non-rotated initial condition, assuming that the elastomeric body 16 does not exhibit elastic deformation in this condition and thus does not generate restoring torque between the inner housing 12 and the outer housing 14 (D = 0). Here, the inner housing 12 and the outer housing 14 are arranged in relation to each other at a rotational angle φ of -40 ° counterclockwise rotated. In Fig. 8B For example, the elastomer torsion spring member 10 is shown rotated in a clockwise rotated state. In this case, the inner housing 12 is arranged relative to the outer housing 14 at a rotational angle φ = 0 °. More precisely, these are the inner case 12 and the outer housing 14 in relation to each other, in comparison to the in Fig. 8A shown initial state, by Δφ = 40 ° twisted. In Fig. 8C is the elastomer torsion spring element 10 shown twisted state, wherein the inner housing 12 in comparison to the states according to Fig. 8A is rotated by Δφ = 70 °.

The advantage of the rotational offset by -40 ° between the inner housing 12 and outer housing 14 in comparison to the untwisted initial state ( Fig. 8A ) is that a further turning over between the inner housing 12 and the outer housing 14 in a clockwise direction relative to each other (see Figs. 8B-8C ) takes place in a rotational angle range in which the characteristic curve of the restoring torque as a function of the rotational angle φ is linear over a large angular range and has a particularly large pitch as a function of the rotational angle.

FIG. 9 shows that in Figures 7A-7C illustrated power system 30, which in a support 42 of a chair (in Fig. 9 not shown) is installed. Here, the base-elastomer torsion spring element 28 is connected via its outer housing fixed to the carrier 42. The bearing shaft (not shown) may be rotatably coupled through an opening of the carrier 42 with a portion of a back carrier 44. The back support 44 in turn serves to receive a back part 3 according to Fig. 1 (in Fig. 9 not shown), with which a substantially vertically extending backrest 4 according Fig. 1 connected is. The backrest 4 is thus pivotable against the introduced by the power system 30 restoring torque. Furthermore, a seat support for a seat 5 according Fig. 1 be connected to the back support 44 and / or the backrest, so that the seat 5 is pivotable in synchronism with the backrest 4.

As already described in the description of FIG. 5 described power system 30, the bearing shaft 26 is rotated as soon as a person sitting on the chair reclines. At the in FIG. 9 As shown, the bearing shaft would turn clockwise when reclining the person. In a state in which the outer housing cams (not shown) of the respective elastomer torsion spring elements 10'-10 "'of the power system 30 are not coupled via the locking elements to the carrier 42, the individual elastomer torsion spring elements 10'-10' Follow this turn.

Depending on a respective rotation of the camshaft 36, the individual locking elements 32'-32 ", each actuated by individual locking cams 34'-34"'arranged on the camshaft 36, can be switched such that they engage with the respective outer housing cams 18 '-18''of the elastomer torsion spring elements 10'-10''are coupled. When a coupled condition is established with any outer housing cam 18'-18 "of an elastomeric torsion spring member 10 ', 10" or 10 "', this coupled elastomer torsion spring member 10 ', 10" or 10 "would have its respective return torque , in addition to the restoring torque of the base elastomer torsion spring member 28, is applied to the support shaft 26. Thus, the elastomer torsion spring members 10 ', 10 ", or 10" are advantageously designed and arranged to be individually connected to the rotation angle apply linear restoring torque, which is adapted to the weight of a person sitting on the chair, to the back support, providing optimal restoring force against the person's back, which increases comfort.

10A-10E show different views of a tensioning device 46 for biasing in the Figures 7A-7C shown elastomer torsion spring elements 10'-10 "'with the intermediate and frontally mounted clamping elements 38'-38'''' Fig. 10A and 10C the tensioning device 46 is shown in a full view, viewed from different directions. In Fig. 10B and 10D the tensioning device 46 is shown in a detail view, viewed from different directions. The tensioning device 46 is used for simple and rapid pretensioning of the individual elastomer torsion spring elements 10'-10 "'in only a few steps The tensioning device 46 contains fixing devices 48', 48", which support the bearing shaft 26 (in FIG 10A-10E not shown) fixedly clamped at their axial ends. On the bearing shaft 26 are previously, as to describe the Figures 7A-7C The individual elastomer torsion spring elements 10'-10 "'are plugged on, the clamping elements 38'-38""being respectively interposed therebetween and on the front side .These clamping elements 38'-38""are each connected in a form-fitting radial manner to the bearing shaft.

The tensioning device 46 further includes a rod 50 which is connected perpendicularly between two lever arms of a lever 52. The lever arms are pivotably hinged via jig bearings 54 ', 54 ".The lever 52 is deflectable back and forth at its lower end by a drive 56. Upon deflection of the lower portion of the lever 52 in a direction out of the plane of the figure Fig. 10A out, the rod 50 is deflected toward the elastomeric torsion spring elements 10'-10 ", as indicated by an arrow A.

How very good in 10C-10E to recognize, at a first stage of the deflection of the rod 50 in the direction of arrow A, a surface region of the rod 50 first with a region of the outer surface of the outer housing of a first elastomer Torsionsfederelements 10 "', for example via an outer housing cam formed thereon 18'-18"', in engagement.

From a second stage of deflection of the rod 50 in the direction of the arrow A, another surface portion of the rod 50 engages the outer surface of the outer housing of a second elastomeric torsion spring member 10 "during deflection of the rod 50 between the first stage and the second stage , the previously engaged outer surface of the outer casing of the first elastomer torsion spring element 10 "'is pivoted or rotated. In a third stage of the deflection of the rod 50 in the direction of the arrow A, a portion of the outer surface of the outer housing of a third elastomer Torsionsfederelements 10 'is engaged. During deflection of the rod 50 between the second stage and the third stage, the elastomer torsion spring members 10 "'and 10" are deflected. In a fourth stage of the deflection of the rod 50, all the elastomer torsion spring elements 10'-10 "'are now deflected or rotated parallel to one another in such a way that they are likewise in Figures 7A-7C shown pins 40 ', 40 "through the holes of the respective curvatures 39'-39""of the individual clamping elements 38'-38""through." Once the pins 40', 40 "are inserted through said holes, the said deflection of the rod 50 reversed, ie the rod 50 is moved counter to the arrow A direction. The inserted pins 40 ', 40 "bear against the individual outer surfaces of the outer casings of the elastomer torsion spring elements 10'-10"' and are clamped due to the effect of the restoring torques of the elastomer torsion spring elements 10'-10 "', 40 "respectively by the radially torsionally coupled clamping elements 38'-38"" held. Thus, the individual elastomer torsion spring elements 10'-10 "'no longer in the respective undeflected initial state ( 10A-10E ) to return.

Figure 10E shows the tensioning device 46 in a view viewed axially with respect to the tensioner bearing 54 ', 54 "In this figure, it can be seen particularly clearly that the individual elastomer torsion spring elements 10'-10"' are differently deflected in their initial state. This is due to the fact that the respective inner casings of the elastomer torsion spring elements 10'-10 '''are each arranged with a rotational offset in relation to the contour of their respective outer casings, which is in each case of different size for the elastomer torsion spring elements 10'-10''. The rotational offsets may be 20 °, 25 ° and 40 ° for the elastomer torsion spring elements 10'-10 "', for example. As a result of the respectively different rotational offset between the inner housing and the outer housing, the individual elastomer torsion spring elements 10'-10 '' are thus biased to different degrees In this example, therefore, the elastomer torsion spring element 10 '' is more strongly pretensioned than the elastomer torsion spring element 10 which in turn is biased more strongly than the elastomer torsion spring element 10 ' Figures 10A and 10C-10E 1, the pins 40 ', 40 "can be inserted through the bores of the curvatures 39'-39""of the respective clamping elements 38'-38""after pretensioning. 10 "'by the pins 40', 40" maintained.

This bias voltage can not be fallen below, however, the outer housing of the individual elastomer torsion spring elements 10'-10 "'relative to the corresponding inner housings in a rotational direction can be rotated such that of the respective Torsionsfederelement 10'-10 '''generated restoring torque is increased with increasing angle of rotation until the exterior housing cam formed on the respective outer housing 18'-18 "' abut against the pin 40. In this state, the elastomer Torsionsfederelemente 10'-10th '' arrived at their maximum permissible angle of rotation and each provide the greatest possible return torque ready.

The in the Figures 10A-10E shown clamping device 46 and the method described by way of example show that the power system 30 described above can be made very quickly and with only a few simple steps, even with differently biased elastomer torsion spring 10'-10 "'.

Claims (15)

Elastomer torsion spring element (10, 28) which comprises an inner housing (12), an outer housing (14) surrounding the inner housing (12) and an elastomer body (16) arranged in a space between the inner housing (12) and the outer housing,
which inner housing (12) has at least one contact surface (12a), at which the elastomeric body (16) is in contact with the inner housing (12),
which outer housing (14) has at least one contact surface (14a), at which the elastomeric body (16) is in contact with the outer housing (14),
wherein the elastomeric body (16) is fixedly connected to the contact surface (12a) of the inner housing (12) and the contact surface (14a) of the outer housing (14),
wherein the inner housing (12) and / or the outer housing (14) about a rotational axis (6) is rotatably arranged and a rotation of the inner housing (12) and / or the outer housing (14) by a rotational angle (φ) about the axis of rotation (6 ) is such executable that during rotation, the inner housing (12) relative to the outer housing (14) moves while a deformation of the elastomeric body (16) is generated, so that the elastomeric body (16) between the outer housing (14) and the inner housing (12) generates a restoring torque, which is opposite to the rotation,
characterized in that
the contact surface (12a) of the inner housing (12) in a plane perpendicular to the axis of rotation (6) does not have a cutting plane has circular cross-section and / or the contact surface (14a) of the outer housing (14) has a non-circular cross-section in a sectional plane perpendicular to the axis of rotation (6). Elastomer torsion spring element (10, 28) according to claim 1, wherein the contact surface (12a) of the inner housing (12) and the contact surface (14a) of the outer housing (14) are arranged relative to each other such that upon rotation of the inner housing (12). and / or of the outer housing (14) about the rotation axis (6) at least in a predetermined rotation angle range a reduction (x1-x2, y1-y2) of a distance between a defined point of the inner housing (12) and a defined point of the outer housing (14) is provable. Elastomer torsion spring element (10, 28) according to one of the preceding claims, in which the contact surface (12a) of the inner housing (12) and the contact surface (14a) of the outer housing (14) have a non-circular cross-section in a sectional plane perpendicular to the axis of rotation (6) and are arranged relative to each other such that by means of the rotation of the inner housing (12) and / or the outer housing (14) about the rotational axis (6) a pressure load in at least one region of the elastomeric body (16) is hervorufbar. Elastomer torsion spring element (10, 28) according to any one of the preceding claims, wherein the contact surface (12a) of the inner housing (12) and / or the contact surface (14a) of the outer housing (14) - each in a plane of rotation to the (6) vertical sectional plane - Are formed polygonal. Elastomer torsion spring element (10, 28) according to one of the preceding claims, in which the contact surface (14a) of the outer housing (14) (A) is at least partially cylindrical or (b) in each case in a direction of rotation of the axis (6) vertical sectional plane - is rectangular, wherein at least two pairs opposite corners are rounded, or (c) includes two pairs of opposite, isosceles angular segments and two pairwise opposed semicircular segments, the ends of which are respectively connected to the ends of the angle segments contains. Elastomer torsion spring element (10) according to one of the preceding claims, wherein the contact surface (12a) of the inner housing (12) - in each case in a direction of rotation (6) vertical sectional plane - is rectangular. Elastomer torsion spring element (10) according to one of the preceding claims, comprising a holding element (19, 20, 38, 38'-38 ""), which is designed (I) to keep the inner housing (12) in a predetermined basic position relative to the outer housing (14), in which basic position the elastomeric body (16) has a predetermined elastic deformation and between the outer housing (14) and the inner housing (12) Restoring torque generated, which is equal to a predetermined minimum value, and (ii) a rotation of the inner housing (12) relative to the outer housing about an angle of rotation (φ) about the axis of rotation (6) to release in a rotational direction in which the restoring torque increases with increasing rotational angle (φ). Elastomer torsion spring element (10) according to claim 7, wherein the inner housing (12) in the predetermined basic position relative to the outer housing (14) of the holding element (19, 20, 38, 38 '-38 "") is held such that the Resetting torque at the respective from the holding element (20, 38, 38'-38 "") released rotation of the inner housing (12) relative to the outer housing (14) increases linearly with increasing rotational angle (φ). An elastomeric torsion spring element (10) according to claim 7 or 11, wherein the retaining element comprises at least one tensioning element (19, 20, 38, 38'-38 "") which either (I) has a first portion which is in a fixed engagement with the inner housing (12), and a second portion which - when the inner housing (12) is in the predetermined basic position relative to the outer housing - against a portion of the outer housing (14) abuts and releases a rotation of the inner housing (12) and the outer housing (14) in relation to each other about the axis of rotation (6) in the direction in which the restoring torque increases, or (ii) has a first portion which is in a fixed engagement with the outer housing (14), and a second portion which - when the inner housing (12) is in the predetermined basic position relative to the outer housing (14) - against a Section of the inner housing (12) abuts and a rotation of the inner housing (12) and the outer housing (14) in relation to each other about the axis of rotation (6) in the direction of rotation releases, in which the restoring torque increases. Elastomer torsion spring element (10) according to claim 9, wherein the inner housing (12) comprises a recess (12.1) and the first portion of the clamping element (20) is rotationally rigidly inserted into this recess (12.1) in the inner housing (12) and the second section of the clamping element (20) - when the inner housing (12) is in the predetermined basic position relative to the outer housing (14) - abuts against a portion of the outer housing (14). Device for transmitting power between a first body and a second, relative to the first body movable body, with
at least one elastomer torsion spring element (10, 28) according to one of claims 1-13,
first coupling means for coupling the first body to the outer housing of the respective elastomer torsion spring element (10, 28),
second coupling means for coupling the second body to the inner housing of the respective elastomer torsion spring element (10, 28),
wherein the first body is coupled to the outer housing of the respective elastomer torsion spring element and the second body is coupled to the inner housing of the respective elastomer Torsionsfederelements such that upon movement of the first body relative to the second body, a rotation of the inner housing (12) and / or the outer housing (14) by a rotation angle (φ) about the axis of rotation (6) is carried out at which rotation, the inner housing (12) relative to the outer housing (14) moves and thereby deformation of the elastomeric body (16) is generated so that the elastomer body (16) generates a restoring torque between the outer housing (14) and the inner housing (12) which is opposite to the rotation. Apparatus according to claim 11, comprising
a plurality of the elastomer Torsionsfederelements, wherein the respective elastomer Torsionsfederelemente are arranged side by side, that the inner housing (12) and / or the outer housing (14) of the respective elastomer torsion spring elements about the same axis of rotation (6) are rotatably arranged. Apparatus according to claim 12, wherein
the inner housing of the respective elastomer Torsionsfederelemente are rigidly interconnected and / or the outer housing of the respective elastomer Torsionsfederelemente are rigidly interconnected. Seating device,
with a seat (5),
with a back support (44),
with a carrier (42) for the back support and / or the seat (5), wherein the back support (44) and / or the seat (5) is pivotally articulated to the carrier (42);
and with a device according to one of claims 14 to 16 for force transmission between the back support (44) and the support (42) and / or for power transmission between the seat (5) and the support (42),
in which (I) the support (42) by means of the first coupling means with the outer housing (14) of the respective elastomer torsion spring element (10, 28) and the back support (44) and / or the seat (5) by means of the second coupling means is coupled to the inner housing (12) of the respective elastomer Torsionsfederelements (10, 28) or (ii) the carrier (43) by means of the second coupling means with the inner housing (12) of the respective elastomer torsion spring element (10, 28) and the back support (44) and / or the seat (5) by means of the first coupling means with the outer housing ( 12) of the respective elastomer Torsionsfederelements (10, 28) is coupled. Seat assembly (1) according to claim 14, in which (i) the outer housing (14) of the respective elastomer torsion spring element (10, 28) is connected to the carrier (42) and the inner housing (12) of the respective elastomer torsion spring element (10, 28) with a about the axis of rotation (6) rotatable bearing shaft (26) is connected, which is torsionally rigidly connected to the back support (44) and / or the seat (5), or (ii) the outer housing (14) of the respective elastomer torsion spring element is connected to the back support (44) and / or the seat and the inner housing (12) of the respective elastomer torsion spring element is connected to a bearing shaft which is rotationally rigidly connected to the support (42 ) connected is.

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