DE19922916A1 - Door closer with drive for closing door casement has spring piston and damping piston mounted rotationally secured relative to stroke cam plate through interaction with drive housing - Google Patents

Abstract

The drive includes a spring piston (3a) and damping device for damping the closing and opening movement. The piston and/or damping piston (5a, 5b) is/are mounted relative to the stroke cam plate (22a, 22b) so that they cannot rotate through the positive interaction of the spring piston and damping piston or parts of the damping piston with the drive housing (11) or a part mounted with force locking or keyed engagement in the drive housing. The spring piston and/or damping piston can be stepped pistons.

Description

The invention relates to a door closer with the features of the preamble of Claim 1.

DE 33 45 004 describes a door closer with a closer spring as Energy storage and a separately designed damping device with Damping pistons and a closer shaft with a cam disc. The in Housing-supported closer spring acts on a spring piston in the closer direction, the spring piston via a pressure roller in operative connection with the Stroke cam stands. A return spring acts on the separately trained Deten damping piston in the opening direction, the damping piston just if there is an operative connection with the cam disc via a pressure roller.

By the torque which the compressed closer spring on the spring piston, or the return spring exerts on the damping piston, there is Risk of twisting the spring piston or damping piston around your own Longitudinal axis. This twisting can lead to the respective pressure roller is no longer securely engaged with the cam disc and the operation of the Door closer is disturbed.

DE 40 41 824 C1 describes a door lock constructed in principle in an analog manner ßer, which has an additional anti-rotation. The anti-rotation device  consists of two rods, which are mounted on the front of the spring piston are. The two rods run in the axial direction of the spring piston with little Distance left and right of the closer shaft immediately above the lifting curves disc and dip into blind holes of the damping piston on the opposite overlying side of the closer shaft. A twisting of spring pistons and Damping piston is opposite due to the small scope of the two rods the closer shaft and the cam disc excluded. Disadvantageous this version, however, is that by arranging two bars on both sides space is required for the closer shaft. Especially with particularly This can be done with narrow door closers for concealed installation Lack of space. In addition, two bars are required for the anti-rotation device assemble, one for each direction of rotation, so that the assembly comparatively on is agile.

The object of the invention is a door closer of the type mentioned develop in which the spring piston and the damping piston with a twist securing against mutual twisting about its longitudinal axis and / or Twist against the cam cam of the gearbox are secured, whereby the anti-rotation device is as simple as possible and only minimal additional Chen space requirements.

The object is achieved by the subject matter of the To saying 1.

In one embodiment of the invention, the spring piston and / or the Damping piston formed in two stages as a so-called stage piston, with one Piston area of larger diameter and a piston area smaller Diameter. The piston chamber is complementary to this. The respective towards the central axes of the piston areas of larger diameter and smaller Diameters are not concentric to each other, but offset to each other. The result of this is that the stepped piston only has a defined vertical alignment tion in the piston chamber and twisting is no longer possible is.  

In an alternative embodiment of the anti-rotation device for spring pistons and / or Damping piston, the piston is designed without gradation. By a twist To ensure safety, the piston has a rotationally asymmetrical preferably non-circular cross-section. For example, elliptical, square, rectangular, triangular or polygonal cross section. Alternatively, only a portion of the piston is designed to be rotationally asymmetrical or out of round, or a piston side or a piston region have a flattened portion. The Piston chamber is complementary to the piston.

In a further embodiment, the piston has a longitudinal groove. The Longitudinal groove can extend over the entire length of the piston or part of it Length. One attached to the inside wall of the piston chamber Guide nose engages in the longitudinal groove and prevents the piston from twisting bens. Alternatively, the radial guide lug can also be formed on the piston be and in a corresponding axially extending in the housing wall groove intervention.

Another device for securing against rotation has a piston rod which is arranged stationary in the piston chamber, for example on the end face of the Kol benraums attached, preferably concentric within the Kol benraums extends. The piston rod dips into an axial blind bore inside of the spring piston and / or the damping piston. To twist the To prevent piston on the piston rod, the piston rod has a un round cross section.

Alternatively, a z. B. round piston rod in an eccentric in the piston immerse the ordered axial blind hole. Or it can be a rotati in cross section Onsymmetrical, preferably non-circular piston rod as a guide rod on Pistons are firmly attached in a corresponding complementary arrangement is guided positively in the housing.

In a further embodiment, the power transmission roller, and / or damper tion roller with which the spring piston, or the damping piston with the respective interacting cam disc, with a rolling surface special Shaped shape, for example a spherical, convex or concave  Shape. Accordingly, the rolling surface of the cam plate is complementary here too trained.

Alternatively, the rolling surface of the power transmission roller and / or the damper roll, be equipped with a flange or a groove, which with a complementary groove, or a flange in the rolling surface of the lifting curves disc, interacts.  

The invention is explained in more detail in the figures. It shows:

Fig. 1 shows a longitudinal section through an inventive door closer with two spring piston and two damping piston;

FIG. 2 shows an enlarged illustration from FIG. 1 in the region of the closer shaft;

Fig. 3 is a detail view of the formed spring piston as a stepped piston in Fig. 1;

Fig. 4 is a cross section of the spring piston, taken along line IV-IV in Fig. 3;

Fig. 5 is an alternative embodiment of the spring piston with an elliptical cross-section;

Fig. 6 shows a cross section through the spring piston, taken along line VI-VI in Fig. 5;

. Fig. 7 alternative embodiments of the spring piston in Figure 5) quadrati's cross-section and b) c) d with longitudinal groove with a round cross section with a flattening) with guide nose;

Fig. 8 is a longitudinal section through a guided on a piston rod spring piston;

9 shows a cross section through the spring piston taken along line IX-IX in Fig. 8.

Fig. 10 shows an alternative embodiment with a power transmission roller with a spherical rolling surface.

Fig. 1 shows a longitudinal section through a door closer 1 for concealed installation in door leaves or door frames. For this purpose, the door closer 1 is added in a recess, which is milled in the area of the upper edge of the door leaf or the lower edge of the door frame. The door closer 1 is a hydraulically damped door closer 1 . The door closer has two separate closer springs 4 a, 4 b arranged in the door closer housing 11 . The closer springs 4 a, 4 b are compressed when the wing is opened and the NEN as an energy store for automatically closing the wing. The closing operation takes place under the action of a damping device which has two damping pistons 5 a, 5 b, hydraulically damped.

A closer shaft 2 is mounted approximately in the middle in the door closer housing 11 . The closer shaft 2 is mounted in a bearing between the front ends of the housing in the area of the upper side 21 a and the lower side 21 b of the door closer housing 11 . The closer shaft 2 emerges on the top of the housing 11 . There, the closer shaft 2 is rotatably coupled to a force-transmitting linkage, the free end of which is supported in a rotary or sliding bearing which is fixed on the door frame or on the door leaf. A sliding arm linkage is preferably used as the force-transmitting linkage. It consists of a sliding arm that can be coupled in a rotationally fixed manner to the closer shaft and that is articulated at its free end to a slider that is guided so as to be displaceable in a slide rail. When the door closer is concealed, the slide rail is concealed in the upper lintel of the door frame or in the door leaf. The slide arm extends through the rebate area between the door leaf and frame.

With the closer shaft 2 , two cam disks 22 a, 22 b are positively or positively connected. These cam disks 22 a, 22 b have symmetrically designed cam tracks in order to be able to use the door closer 1 in both right-hand and left-hand mounting. The two cam disks 22 a, 22 b are offset from one another on the closer shaft 2 . One cam disc 22 a, 22 b is arranged in the upper region of the closer shaft 2 and interacts with the spring piston 3 a on the left in FIG. 1, and the other cam disc 22 a, 22 b is arranged in the lower region of the closer shaft 2 and cooperates the right in Fig. 1 spring piston 3 b together.

In the embodiment shown, the housing of the door closer 1 has two piston chambers 12 a, 12 b of larger diameter and two piston chambers 13 a, 13 b of smaller diameter. One of the two larger piston chambers 12 a is formed on the left side of the closer shaft 2 , and the other piston chamber 12 b on the right side of the closer shaft 2 . Here, the left-hand piston chamber 12 a is formed in the upper housing area and the right-hand piston chamber 12 b is formed in the lower housing area. The same applies in mirror image to the two smaller piston chambers 13 a, 13 b, so that a larger and a smaller piston chamber to the left and right of the closer shaft 2 are opposite each other. All piston chambers 12 a, 12 b, 13 a, 13 b are in the same, in Fig. 1 Darge section plane arranged in the housing.

In each of the two larger piston chambers 12 a, 12 b, one of the spring pistons 3 a, 3 b and one of the two closer springs 4 a, 4 b and a device for adjusting the closing force 6 a, 6 b are added. The spring piston 3 a, 3 b is sealingly guided in the piston chamber 12 a, 12 b. As can be seen in FIG. 2, a force transmission roller 31 a, 31 b is rotatably mounted on the closer shaft 2 facing side of each spring piston 3 a, 3 b on an axle bolt 32 a, 32 b, which with one of the cam disks 22 a, 22 b interacts.

The two larger piston spaces 12 a, 12 b have a greater axial length than the two smaller piston spaces 13 a, 13 b. The resulting installation space 9 a, 9 b in connection to the two smaller piston spaces 13 a, 13 b can optionally also be used for the installation of additional facilities. Such facilities can, for. B. a locking device, a solenoid valve, a sensor device or the like Sen. The installation space 9 a, 9 b can also be used for the installation of an additional spring piston with a closer spring, which can be hydraulically connected to one of the two larger piston spaces 12 a, 12 b.

In each of the two smaller piston chambers 13 a, 13 b, a sealingly guided damping piston 5 a, 5 b is received, which is acted upon by a return spring 55 a, 55 b in the direction of the closer shaft. On the side of the closer shaft 2 facing each damping piston 5 a, 5 b, a damping roller 51 a, 51 b is rotatably mounted on an axle bolt 52 a, 52 b, which also cooperates with one of the cam disks 22 a, 22 b. The rollers 31 a, 31 b, 51 a, 51 b each have a spring piston 3 a, 3 b and a damping piston 5 a, 5 b interact with the same cam disc 22 a, 22 b. As with a conventional door closer 1 , the closer springs 4 a, 4 b are tensioned when the door is opened manually and then bring about a hydraulically damped closing of the door. About the closing force setting 6 a, 6 b, the bias of the closer springs 4 a, 4 b can be changed in the idle state. Such a device for setting the closing force 6 a, 6 b is described, for example, in DE 93 08 568.

As shown in Fig. 2, the two smaller piston spaces 13 a, 13 b hy draulically coupled to each other. The hydraulic flow takes place via an inlet 7 e in the lower left pressure-side piston chamber 13 b and a horizontal channel 7 a in an annular groove 71 in the cover of the lower bearing 22 b of the closer shaft 2 . In the annular groove 71 , the hydraulic fluid is guided around the closer shaft 2 and opens out on the opposite side of the bearing 22 b into the continuation of the horizontal channel 7 b. Via a vertical channel 7 c that is not in the sectional plane, the hydraulic fluid then reaches an upper horizontal channel 7 d and opens into the upper pressure-side piston chamber 13 a for an inlet 7 g.

In the upper horizontal channel 7 d, a damping valve, not shown, and a stop valve are arranged. Via the inlet 7 g, the damping valve and the horizontal channel 7 d, the pressure-side part of the piston chamber 13 a is connected to the unpressurized part of the piston chamber 13 a. The unpressurized part of the piston chamber 13 a is open towards the receiving space of the closer shaft 2 , in which the horizontal channel 7 d opens in the area of the upper bearing 21 a.

When the door is opened, the upper spring piston and the upper damping piston 5 a move to the left and the lower spring piston and the lower damping piston 5 b to the right. The damping pistons 5 a, 5 are acted upon by the return springs 55 a, 55 b. Hydraulic fluid is exchanged directly between unpressurized and pressure-side piston chamber 13 a via the check valve arranged in the upper damping piston 5 a. Upper and lower damping pistons 5 a, 5 b stand on the one hand via the hydraulic line 7 a, 7 b, 7 c, 7 d and also via the receiving space of the closer shaft in the liquid exchange.

When the door closes, the upper spring piston 3 a and the upper damping piston 5 a move to the right and the lower spring piston 3 b and the lower damping piston 5 b to the left. Hydraulic fluid is exchanged via the inlet 7 g, the damping valve and the horizontal channel 7 d between the pressure-side part of the piston chamber 13 a and the unpressurized part of the piston chamber 13 a. The closing movement of the door is hydraulically damped by the damping valve and the return springs 55 a, 55 b are compressed. At a certain closing angle of the door, the inlet 7 f connected to the end stop valve comes into connection with an annular groove 53 in the damping piston 5 a. Hydraulic fluid then flows via a control bore 54 in the damping piston 5 a bypassing the damping valve via the end stop valve from the pressure-side piston chamber 13 a into the unpressurized piston chamber 13 b. The door then carries out the so-called end stop.

Due to the hydraulic coupling of the upper and lower piston chambers 13 a, 13 b, only one valve for adjusting the damping and only one valve for adjusting the end stroke is required for two damping pistons. Instead of the check valve arranged in the upper damping piston, a pressure relief valve, not shown, is arranged in the lower damping piston. The pressure relief valve prevents damage to the hydraulic system when the door is forced to close manually.

Due to their spiral structure, the closer springs 4 a, 4 b and the return springs 55 a, 55 b exert not only a linear restoring force, but also a slight torque on the respective pistons 3 a, 3 b, 5 a, 5 b, on which they are based. As a result, there is a risk of the piston 3 a, 3 b, 5 a, 5 b rotating relative to the associated cam disc 22 a, 22 b.

In order to avoid twisting the spring piston 3 a, 3 b and the resultant ver edging of the power transmission roller 31 a, 31 b and cam disc 22 a, 22 b during the opening and closing process, the spring piston 3 a, 3 b has an anti-rotation device according to the invention on. The anti-rotation device is described below using the example of the upper spring piston 3 a, but is designed analogously for the lower spring piston 3 b. Furthermore, the damping pistons 5 a, 5 b can be equipped with a corresponding anti-rotation device, or with an alternative anti-rotation device, as described below.

The spring piston 3 a as shown in Fig. 3 in detail as a two-stage construction so--called stepped piston. The piston area 33 b facing away from the closer shaft 2 of the spring piston 3 a (in Fig. 3a on the left in the picture) has a larger diameter than the inner area 33 a facing the closer shaft 2 (in Fig. 3 on the right in the picture). The gradation 33 c of the stepped piston lies between the two piston regions 33 a, 33 b. On the left side, the closer spring 4 a is supported on the piston 3 a and on the right side the force transmission roller 31 a is mounted in the piston 3 a on an axle bolt, the force transmission roller 31 a being in operative contact with the cam disc 22 a, not shown in FIG. 3.

The piston chamber 12 a is formed in a complementary manner to the stepped piston 3 a. The left-hand part of the piston chamber 14 b has a larger diameter than the right-hand part of the piston chamber 14 a. A step 14 c is also formed in the piston chamber at the point of transition from a larger to a smaller diameter. Since the spring piston 3 a moves axially in the piston chamber 12 a, the gradation 33 c of the spring piston 3 a and the gradation 14 c of the piston chamber 12 a are axially offset from one another, so that there is sufficient scope for the movement of the spring piston 3 a.

Fig. 4 shows a section along line IV-IV through the spring piston 3 a in Fig. 3. The respective centers of the piston areas of larger diameter 33 b and smaller diameter 33 a are not concentric to each other, but slightly offset. The result of this is that the stepped piston 3 a can only be guided in a defined vertical orientation in the piston chamber 12 a and twisting is no longer possible.

An alternative and very simple embodiment of the anti-rotation device is shown in FIG. 5 using the example of the spring piston 3 a. However, use is possible both for the spring pistons 3 a, 3 b and for the damping pistons 5 a, 5 b. The spring piston 3 a is formed in the piston chamber 12 a as a normal piston without gradation. As already described, the closer spring 4 a is supported on the piston 3 a on the left and on the right side the force transmission roller 31 a is mounted in the piston 3 a on an axle bolt. In order to ensure an anti-rotation, the Fe derkolben 3 a, in contrast to conventional pistons, has a non-circular cross-section. As the sectional view in FIG. 6 shows, both the piston 3 a and the piston chamber 12 a have an elliptical cross section. Through this cross-sectional shape, the orientation of the piston 3 a in the piston chamber 12 a is clearly defined and rotation is prevented.

Fig. 7 shows some modifications of the piston shape. For example, the piston ben 3 a as shown in Fig. 7a have a square shape. Rectangular, triangular, polygonal piston shapes are also possible. As shown in Fig. 7b, the piston 3 may be embodied also a substantially circular cross-section, wherein a piston side is flattened over their entire length or part of their length. In order to achieve an anti-rotation is the associated piston space 12 is formed complementary to a respective piston.

The piston shown in Fig. 7c has a longitudinal groove. The longitudinal groove may first emerge over the entire length of the piston or part of its length. A guide lug attached to the inner wall of the piston chamber 12 a engages in the longitudinal groove 36 and prevents the piston 3 a from rotating. The piston is round in cross section in the case shown.

Alternatively, the radial guide lug can also be formed on the piston, as shown in FIG. 7d, and engage in a corresponding groove that extends axially in the housing wall. In this case too, the piston is round in cross section.

Another anti-rotation with a piston rod 38 shown in FIG. 8. The Kol benstange 38 is fixed in the piston chamber 12 a arranged, for example on the front side of the piston chamber 12 a fixed, extending concentrically within the closing spring 4a. The piston rod 38 dips into an axial blind bore 39 within the spring piston 3 a. In order to prevent the piston 3 a from rotating on the piston rod 38 , the piston rod 38 , as shown in FIG. 9, has a non-circular, for example square, cross section which is complementary to the cross section of the blind bore 39 . Designs with rectangular, elliptical and other geometries are also possible.

Alternatively, a round piston rod 38 can be immersed in an eccentric piston 3 a in an ordered axial blind bore 39 . In this case, too, there is an anti-twist device.

Or a piston rod can be firmly attached to the piston as a guide rod be, e.g. B. as a polygonal rod in a corresponding complementary to order in the housing is positively guided.

Another way to prevent rotation is the power transmission roller 31 a, 31 b and / or damping roller 51 a, 51 b, with which the spring piston ben 3 a, 3 b and the damping piston 5 a, 5 b with the respective cam disc 22 a, 22 b cooperate with a rolling surface 34 of special shape.

In the simplest case, the rolling surface 34 has a spherical or convex shape, as shown in FIG. 10. The rolling surface 24 of the cam disc is then designed to be correspondingly complementary. Conversely, the force transmission roller and / or damping roller can also have a concave rolling surface 34 and the cam disc can be equipped with a convex rolling surface.

In further embodiments, not shown, the rolling surface 34 of the power transmission roller 31 a, 31 b and / or the damping roller 51 a, 51 b can be equipped with a flange or a groove which has a complementary groove or a flange in the rolling surface of the cam disc 22 a, 22 b cooperates.

List of reference numbers

1

Door closer

11

Door closer housing

12th

a,

12th

b large piston chamber

13

a,

13

b small piston space

14

a,

14

b narrow and wide piston chamber

14

c Gradation in the piston chamber

2nd

Closer shaft

21

a top camp

21

b lower bearing

22

a,

22

b cam disc

24th

Rolling surface

3rd

a,

3rd

b spring piston

31

a,

31

b Power transmission roller

32

a,

32

b Axle pin

33

a,

33

b narrow and wide piston area

33

c Gradation in the piston

34

Rolling surface

35

Flattening

36

Longitudinal groove

37

Leader

38

Piston rod

39

Blind hole

4th

a,

4th

b closer spring

5

a,

5

b damping piston

51

a,

51

b damping roller

52

a,

52

b Axle pin

53

Ring groove

54

Control bore

55

a,

55

b return spring

6

a,

6

b Closing force setting

7

a,

7

b,

7

d horizontal hydraulic channel

7

c vertical hydraulic channel

7

e,

7

f,

7

g inlet bore

71

Ring channel

9

a,

9

b Installation space

Claims (20)

1. Drive for a wing of a door, a window or the like
with a drive housing, with at least one closer spring arranged in the drive housing, which is acted upon when the wing is opened or closed and is designed as an energy store for automatically closing or opening the wing,
with a damping device arranged in the drive housing for damping the closing and / or opening movement of the leaf, preferably hydraulic damping device with a damping piston,
with an output element arranged in the drive housing, preferably a closer shaft which interacts with the energy store and / or with the damping device, preferably with a force-transmitting linkage which is supported on the one hand in a rotary or sliding bearing and on the other hand is connected to the output element,
wherein the output member via a gear, for. B. cam disc, interacts with egg NEM arranged in the drive housing spring piston, on which a closer spring is supported,
and / or wherein the output member via a gear, for. B. cam disc, cooperates with a damping piston arranged in the drive housing, on which a return spring is supported, characterized in that
that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) are arranged or is ver non-rotatably with respect to the cam disc ( 22 a, 22 b), the anti-rotation device acting through a positive interaction of spring pistons ( 3 a, 3 b) or parts of the spring piston and / or the damping piston ( 5 a, 5 b) and / or parts of the damping piston with the drive housing ( 11 ) or one in the drive housing ( 11 ) in a non-positive and / or positive manner stored part is given. 2. Device according to claim 1, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) as a stepped piston with a piston region of larger diameter ( 33 b) and a piston region of smaller diameter ( 33 a) is trained. 3. Apparatus according to claim 2, characterized in that the piston region of larger diameter ( 33 b) and the piston region of smaller diameter ( 33 a) are arranged eccentrically with respect to the axials of the piston ( 3 a, 3 b, 5 a, 5 b) , wherein preferably the axis of the piston area of larger diameter, preferably its central axis or axis of gravity, is arranged offset to the axis of the piston area of smaller diameter, preferably offset to its central axis or axis of gravity. 4. The device according to claim 1, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) in cross-section is rotationally asymmetrical and / or out of round. 5. The device according to claim 4, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) are elliptical. 6. The device according to claim 4, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) are formed in a quadratic, rectangular, triangular or polygonal manner. 7. The device according to claim 4, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b), preferably with a rotationally asymmetrical in cross section, z. B. Out of round design have a flattening ( 35 ) in the cross-sectional area. 8. The device according to claim 4, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b), preferably have a longitudinal groove ( 36 ) in a cross-sectionally rotationally asymmetrical design. 9. The device according to claim 8, characterized in that the longitudinal groove ( 36 ) extends over the entire length of the piston ( 3 a, 3 b, 5 a, 5 b), or only over a portion of the piston ( 3 a, 3rd b, 5 a, 5 b). 10. The device according to claim 4, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) have a guide lug ( 37 ) or a guide element. 11. The device according to one of claims 2 to 10, characterized in that the piston chamber ( 12 a, 12 b, 13 a, 13 b) complementary to the spring piston ( 3 a, 3 b) and / or damping piston ( 5 a, 5th b) is trained. 12. The apparatus according to claim 1, characterized in that one in the spring piston ( 3 a, 3 b) and / or in the damping piston ( 5 a, 5 b) received and with the cam disc ( 22 a, 22 b) cooperating force transmission roller ( 31 a, 31 b) and / or damping roller ( 51 a, 51 b) has a rolling surface ( 34 ) of special shape, preferably uneven shape, which is designed to prevent rotation. 13. The apparatus according to claim 11, characterized in that the rolling surface ( 34 ) of the power transmission roller ( 31 a, 31 b) and / or damping roller ( 51 a, 51 b) is convex or concave. 14. The apparatus according to claim 11, characterized in that the rolling surface ( 34 ) of the power transmission roller ( 31 a, 31 b) and / or damping roller ( 51 a, 51 b) has a flange ( 39 ). 15. The apparatus according to claim 11, characterized in that the rolling surface ( 34 ) of the power transmission roller ( 31 a, 31 b) and / or damping roller ( 51 a, 51 b) has a groove ( 38 ). 16. The device according to one of claims 12 to 15, characterized in that the rolling surface ( 24 ) of the cam disc ( 22 a, 22 b) complementary to the rolling surface ( 34 ) of the power transmission roller ( 31 a, 31 b) and / or damping roller ( 51 a, 51 b) is formed. 17. The apparatus according to claim 1, characterized in that the spring piston ( 3 a, 3 b) and / or the damping piston ( 5 a, 5 b) on a preferably in the drive housing ( 11 ) and / or on the damping piston and / or on the spring piston attached piston rod ( 38 ) are guided. 18. The apparatus according to claim 17, characterized in that the piston rod ( 38 ) has a non-circular cross-section. 19. The apparatus of claim 17 or 18, characterized in that the piston rod ( 38 ) in an axial blind bore ( 39 ) within the spring piston ( 3 a, 3 b) or the damping piston ( 5 a, 5 b) is immersed. 20. Device according to one of claims 17 to 19, characterized in that the axial blind bore ( 39 ) is arranged eccentrically in the spring piston ( 3 a, 3 b) or in the damping piston ( 5 a, 5 b).