EP0476265A1 - Fluid actuator with slotted cylinder - Google Patents

Abstract

In a fluid actuator with a slotted cylinder (1), a piston (3) is coupled to a power-output member (18) merely in such a way as to transmit axial forces. The power-output member (18) has a guide on the cylinder (1). The guide is designed in mirror image relative to a centre plane (14) through the cylinder axis (9) and the slot of the cylinder (1). On either side of the centre plane (14), the guide in each case has two guideways (11, 35 and 29, 31 and resp. 11, 36 and 30, 32). One guideway (29, 31 or 30, 32) runs at an angle to the centre plane (14) inside a sloping guide groove (27 or 28) in the cylinder (1) and is non-adjustable, while the other guideway (11, 35 or 11, 36) runs in or parallel to the outer surface (11) having the slot and at right angles to the centre plane (14) and is adjustable perpendicularly to this outer surface (11). To adjust this other guideway (11, 35 or 11, 36), a guide strip (35 or 36) adjustable by means of regulating screws (37 or 38) perpendicularly to the outer surface (11) is provided in the power-output member (18). In the guide designed in this way, faulty adjustments can easily be recognized and they cannot lead to any overloading of the connecting means (16). Expansion of the cylinder (1) caused by pressurising does not lead to jamming of the power-output member (18). Normal force loads of the power-output member (18) are transmitted free of wedge action to the cylinder (1). <IMAGE>

Description

The invention relates to a pressure medium cylinder with a longitudinally slotted cylinder tube which is closed at the end and which is delimited on the slot side by an outer surface which is perpendicular to the slot and in which a piston is guided in a sealed manner by means of two piston seals arranged near its ends and is guided in the area between the piston seals by means of one of the slots penetrating connecting means is firmly connected to a driver located in front of the slot on the outside of the cylinder tube, with a sealing tape arranged inside the inside of the cylinder tube and pressure-tightly covering the slot outside the section enclosed by the two piston seals and optionally with a covering tape covering the outside of the slot with the exception of the passage area of the connecting means, with an the outside of the slot axially displaceably guided force output member, which at least faces away from the driver and overlaps laterally, where in the case of the guide of the force-transmitting member formed on both sides of the slot symmetrically to a central plane running through the slot and containing the cylinder axis, each has two planar guideways running parallel to one another and axially parallel to one another, each with a guide groove arranged on the cylinder tube and an adjustable guide bar arranged on the force-giving member, and with one arranged between the driver and the force output member and with limited transverse and rotational mobility transmitting axial forces between these parts coupling device.

Such a pressure medium cylinder is known from EP-B 0 157 892, in which the guide is obviously designed in accordance with DE-A 31 24 915 mentioned in this document or EP-B 0 068 088 corresponding to it. In this guide according to DE-A 31 24 915 or EP-B 0 068 088, the force-transmitting member at least partially overlaps the side surfaces of the cylinder tube in an area in which wedge-like guide grooves are incorporated into these side surfaces. The force output member carries guide strips which engage the keyways with correspondingly roof-like guide surfaces. The guide strips can be adjusted perpendicularly to the central plane by means of adjusting screws arranged at right angles to the central plane in the force output member. This design of the guidance of the force output member is intended to counteract an expansion of the cylinder tube caused by the application of pressure medium. However, this task can hardly be solved functionally with the described guide, since, should the cylinder tube widen and thus press against the guide strips, the force output member would be jammed to the cylinder tube and would hardly be movable. Accordingly, EP-B 0 157 892 also states that the guide described must have a certain amount of play for reasons of ease of movement. This certain play must obviously also be present when the pressure medium cylinder is at maximum pressure and thus the cylinder tube is maximally expanded; it can be adjusted by means of the adjusting screws. Since the cylinder tube contracts again with narrowing of the slot when the pressure medium is applied to a lesser extent, this reduced or even missing pressure medium application results in a correspondingly increased play, so that the force output member no longer experiences exact guidance. In addition, the guide strips must be guided so that they can be moved at right angles to the central plane in order to be able to be adjusted; this guide requires a sliding guide with play in the guide strips in the grooves of the force-transmitting member receiving them in the direction parallel to Middle plane. This sliding guide play impairing the quality of the guidance of the force output member cannot be influenced by the adjusting screws, it cannot therefore be adjusted, but is only dependent on manufacturing tolerances and wear.

In this known pressure medium cylinder there is also the risk that the aforementioned certain play is incorrectly adjusted by means of the adjusting screws when the pressure medium cylinder is depressurized; when pressure medium is applied, this certain play is then consumed immediately, and with increasing pressure medium pressure, pressing the guide grooves on the guide strips results in jamming of the force output member to the cylinder tube, so the pressure medium cylinder fails. In addition to the misalignment option mentioned above, there is a high risk of further misalignment with this guide if the guide has too much play: If, based on this too much play, only the one guide bar is readjusted by means of the adjusting screws arranged on one side, This results in a displacement of the force output member at right angles to the central plane to the side of the readjusted guide bar, the driver designed as a web penetrating the slot can come to rest against the wall of the slot, as a result of which the excessive play is eliminated and the power output member appears to be incorrectly adjusted correctly. Such misalignment of the pressure medium cylinder can lead to its immediate damage or destruction. This adjustment error is also possible with a pressure medium cylinder having this guide according to the mentioned EP-B 0 157 892, since the coupling device there does not allow any transverse displacements between the driver and the force output element, therefore the driver is taken along when the force output element is moved and its web-like connecting means to the Slit side wall is pressed.

Another deficiency of this known guide is to be seen in the fact that, in the case of normal force loading of the force output member, which occurs frequently in practical cylinder operation, i.e. its load due to a force which runs in the central plane and is perpendicular to the cylinder axis, the force transmission to the cylinder tube takes place via wedge-shaped guide tracks, whereby in Comparison of the power transmission to a hypothetical guideway running at right angles to the direction of the force. Increased forces with increased friction and increased wear corresponding to the wedge angle are to be transmitted.

In order to enable transverse displaceability between the driver and the force output member with the advantages resulting therefrom, it is proposed with a patent application of the same age to arrange a transverse feather key as a coupling device between these two parts.

From EP-A 0 234 033 and 0 280 309 it is known to guide the force output member by means of round guide rods arranged laterally of the cylinder tube, which are supported over their entire length against the cylinder tube or are held only on the end of the cylinder tube; However, these guide rods represent additional components which make the pressure medium cylinder more expensive and, moreover, require an increased installation space, since the force-transmitting member laterally overlaps the guide rods and must accordingly be made wider. In addition, it is also possible with these guides for the force output member to jam when the cylinder tube is widened under pressure medium.

It is an object of the invention to design a pressure medium cylinder of the type mentioned at the outset with simple means in such a way that the abovementioned shortcomings are avoided, in particular that the entire play in the guidance of the force output element can be adjusted, So there are no unadjustable partial games that jamming of the force output member by expanding the cylinder tube, and undetectable misalignments with dangerous late consequences are avoided and advantageous power transmission is achieved with normal force loading of the power output member.

This object is achieved according to the invention in that, in a pressure medium cylinder with the features mentioned at the outset, the guidance of the force-transmitting member on both sides of the slot within the guide groove has one guideway and the other guideway on the outer surface, one guideway being non-adjustable and inclined to The central plane runs, and the other guideway runs parallel to the outer surface and has the guide strip that is adjustable in the direction perpendicular to the outer surface.

In the known pressure medium cylinder, as already mentioned above, the guide strips have to be guided so as to be able to move transversely to the center plane in the force output member in order to be able to adjust them by means of the adjusting screws. The transversely displaceable guidance of the guide strips requires play between them and the force output element, which cannot be adjusted by means of the adjusting screws. In contrast, it results in a design of the pressure medium cylinder according to the present invention that the effective in the transverse direction to the central plane guide play of the guide rails in the power output member without influence on its play relative to the cylinder tube, so any play between these two parts is adjustable.

Fig.1

einen Längsschnitt durch einen Druckmittelzylinder,

Fig.2

ein vergrößertes Schnittbild gemäß Linie A-A durch den Druckmittelzylinder gemäß Fig.1,

Fig.3

ein ebenfalls vergrößertes Schnittbild gemäß Linie B-B in Fig.1,

Fig.4

ein nicht vergrößertes Schnittbild entsprechend Fig.3 durch eine geänderte Ausführungsform des Druckmittelzylinders und

Fig.5

ein der Fig.4 entsprechendes Schnittbild durch eine weitere Ausführungsform des Druckmittelzylinders.

In the drawing, exemplary embodiments of pressure medium cylinders designed according to the invention are shown, and that shows

Fig. 1

a longitudinal section through a pressure medium cylinder,

Fig. 2

3 shows an enlarged sectional view along line AA through the pressure medium cylinder according to FIG. 1,

Fig. 3

1 also an enlarged sectional view according to line BB in FIG. 1,

Fig. 4

a not enlarged sectional view corresponding to Figure 3 by a modified embodiment of the pressure cylinder and

Fig. 5

a sectional view corresponding to Figure 4 through a further embodiment of the pressure medium cylinder.

1 to 3, the pressure medium cylinder has a cylinder tube 1, which is closed at the end by cylinder cover 2. The cylinder covers 2 convey the pressure medium feeds to the pressurization chambers 4 and 5 located on both sides of a piston 3. The cylinder tube 1 has an approximately square cross-section on the outside, it is provided with an eccentrically arranged cylinder bore 6, in which the piston 3 is guided. In the outer wall of the cylinder tube 1, a plurality of mounting and guide grooves 7, which are of no further interest here, are incorporated. The cylinder wall 8 of the cylinder tube 1 lying in the direction of offset of the cylinder bore 6 is cut open by means of a slot 10 running parallel to the cylinder axis 9.

The cylinder tube 1 has an outer surface 11 on the side of the slot 10 and a side surface 12 or 13 on the side of the slot 10. A central plane 14 runs through the cylinder axis 9 and centrally through the slot 10.

The piston 3 is axially relatively elongated, it has a piston seal 15 near each of its two ends to limit the pressurizing spaces 4 and 5. In the area between the Piston seals 15, the piston 3 is provided with a web-like connecting means 16 which extends through the slot 10 and firmly connects the piston 3 to a driver 17 located in front of the slot 10 on the outside of the cylinder tube. The driver 17 is facing away from the slot and overlapped laterally by a bow-like force output member 18 which is guided on both sides of the slot 10 by means of guide arrangements to be described later in detail on the cylinder tube 1.

The slot 10 is covered on the inside of the cylinder tube in the area of the pressurized spaces 4 and 5 by a sealing tape 19 in a pressure-tight manner; in the area of the piston 3 between its piston seals 15, the sealing tape 19 is lifted from the slot 10 and guided through a guide channel 20 of the piston 3 such that the slot 10 is free for the connection means 16 to pass through. On the outside of the cylinder, the slot 10 is covered outside the area of the piston 3 by a shroud 21, which is also lifted from the slot 10 in the area of the piston 3 and is guided through a space 22 located between the driver 17 and the force output member 18, such that the connecting means 16 can pass through the slot 10 and can be firmly connected to the driver 17, can optionally be made in one piece with the latter. To hold the shroud 21 on the outer surface 10 10 magnetic tapes 23 are inserted into the cylinder tube 1 on both sides of the slot, which magnetically hold the shroud 21 made of a suitable material outside the area of the piston 3. However, the tape holder can also be made in another known manner.

For coupling the driver 17 to the force output member 18, the driver 17 has a transverse groove 24 approximately in the middle of its longitudinal extent on its side facing away from the slot, to each of which a groove-like recess 25 in the force output member 18 adjoins the transverse groove 24. In the transverse groove 24, a feather key 26 is inserted such that these with their end portions in the recesses 25 engage; the feather key 26 thus extends transversely to the central plane 14. The feather key 26 together with the transverse groove 24 and the recesses 25 represents a coupling device between the driver 17 and the force output member 18, which, depending on the play of the feather key 26 in the transverse groove 24 or the recesses 25 relative movements and rotations between the driver 17 and the power output member 18 allows.

According to FIGS. 2 and 3, a guide groove 27 and 28 each emanate from the outer surface 11 to the side of the slot 10, which are incorporated into the cylinder tube 1 and which are inclined obliquely downward from the outer surface 11 toward the side surfaces 12 and 13, So run to the middle level 14 diverging. The correspondingly inclined walls of the guide grooves 27 and 28 on the outer surface side represent guide surfaces 29 and 30, respectively, against which corresponding guide surfaces of the force output member 18 are slidably applied; the guide surfaces of the force output element 18 are located on guide strips 31 and 32, which are firmly held on strip-like extensions 33 of the force output element 18 which project obliquely downwards and outwards. The extensions 33 engage in the guide grooves 27, 28 with play on all sides. The guide surfaces 29 and 30, together with the associated guide strips 31 and 32, each form a non-adjustable guide track 29, 31 and 30, 32, respectively, which are inclined mirror-inverted to the central plane 14. On the outside, each of the extensions 33 is adjoined by a section 34 of the force-transmitting member 18, the sections 34 cover the outer surface 11 until their transition into the side surfaces 12 and 13. On the outside surface, a guide bar 35 or 36 is vertically displaceable in the sections 34, So slidably inserted parallel to the central plane 14. The guide strips 35 and 36, like the guide strips 31 and 32, extend parallel to the cylinder axis 9. The undersides of the guide strips 35 and 36 lie displaceably on flat edge strip sections of the outer surface 11. Set screws 37, 38 are adjustably screwed to the two sections 34, the set screws 37 and 38 have axial directions which run parallel to the central plane 14 and cross the cylinder axis 9 at right angles. A plurality of adjusting screws 37 and 38 are arranged at uniform intervals in each section 34 over the longitudinal extent of the force output member 18 in the direction of the cylinder axis 9. The screwing of the set screws 37 and 38 to the sections 34 can be designed to be self-locking, but lock nuts can also be provided in a manner not shown for securing the respective adjustment position. The ends of the set screws 37 and 38 on the outer surface lie on support strips 39 on the sides of the guide strips 35 and 36 facing away from the outer surface; the support strips 39 extend parallel to the cylinder axis 9 and, together with the guide strips 35 and 36, are displaceably guided parallel to the central plane 14. The guide strips 35 and 36 thus form, together with the outer surface 11, adjustable guide tracks 11, 35 and 11, 36, respectively, which lie in a plane perpendicular to the central plane 14.

By means of the set screws 37 and 38, the height of the guide strips 35 and 36 can be adjusted such that the guide tracks 29, 31; 30.32; 11, 35 and 11, 36 a desired play possibility or sliding mobility remains, the force output member 18 is thus adjusted in the desired manner relative to the cylinder tube 1 and guided displaceably. The guideways 29, 31 and 30, 32 take over the lateral guidance of the force output member 18 and preclude its lifting up from the cylinder tube 1. Possible side play of the guide strips 35 and 36 relative to the sections 34 have no influence on the quality of the lateral guidance of the power output member 18 relative to the cylinder tube 1. Since the mentioned, possible side play of the guide strips 35 and 36 also has no influence on the adjustment screws 37 and 38 has certain vertical position of the guide strips 35 and 36 relative to the sections 34, this side play has no influence whatsoever on the quality of the guidance of the force output member 18 on the cylinder tube 1 of the adjusting screws 37 and / or 38 are easily ascertainable at any time: even one-sided, too far screwing in of the adjusting screws 37 or 38 results in a slight lateral displacement of the force output member 18 which jams in the guideways relative to the cylinder tube 1, it being essential that the mentioned Lateral displacement of the power output member 18 is possible within the scope of the play of the connecting means 18 in the slot 10, so that the power output member 18 does not come to rest on a side wall of the slot 10. If the adjusting screws 37 and / or 38 are unscrewed too far, the guide play for the force output member 18 is too great. Both the jamming and the guide play which is too great can be easily ascertained and corrected. If, after adjustment by pressurization of the medium, the cylinder tube 1 spreads apart, then only the play on the middle side between the guide grooves 27 and 28 and the extensions 33 is reduced somewhat, without the occurrence of systems which prevent movement; at the same time there is a slight increase in play on the guide tracks 29, 31 and 30, 32, which, however, does not impair or disrupt the functionality of the pressure medium cylinder in any way. When the force output member 18 is loaded by normal forces, which run in or parallel to the central plane 14, perpendicularly intersecting or crossing the cylinder axis 9, the force transmission takes place through the guide tracks 11, 35 and 11, 36 which are perpendicular to this direction of force, so there is no wedge effect on, which could increase the load on the mentioned guideways 11, 35 and 11, 36. The power transmission can thus take place with little friction and correspondingly little wear.

In the embodiment according to FIG. 4, the force output member 18 overlaps the upper sections of the side surfaces 12 and 13 of the cylinder tube 1 with guide legs 40 on the side of the guide tracks 11, 35 and 11, 36. In the overlapping area, guide grooves 41 and 42 extend from the side surfaces 12 and 13 , which is inclined substantially obliquely in the direction of the outer surface 11 Extend cylinder tube 1. The outer surface walls of these guide grooves 41 and 42 form guide surfaces 43 and 44, respectively, which correspond to the guide surfaces 29 and 30 of the exemplary embodiment according to FIGS. 2 and 3 and against which the guide strips 31 and 32 rest, which are firmly attached to the guide grooves 41 and 42 engaging portions of the guide leg 40 are connected. This results in guideways 31, 43 and 32, 44 which functionally correspond completely to the guideways 29, 31 and 30, 32 missing in the exemplary embodiment according to FIG. 4 in accordance with the exemplary embodiment described above. The remaining structure of the pressure medium cylinder according to FIG. 4 corresponds completely to the exemplary embodiment according to FIGS. 1 to 3; some appealing reference numbers are given. The functions and advantages described for this exemplary embodiment thus apply in the same way to the exemplary embodiment according to FIG.

The embodiment according to FIG. 5 corresponds to the position and arrangement of the guideways 11, 35; 11.36; 31, 43 and 32, 34 completely the exemplary embodiment according to FIG. 4, it thus also has the functions and advantages explained for the first described exemplary embodiment. The exemplary embodiment according to FIG. 5 differs from that according to FIG. 4 only with regard to the adjustment arrangement. According to FIG. 5, the set screws 37 and 38 are screwed to the guide legs 40 with an axial direction perpendicular to the center plane 14. The set screws 37 and 38 act on wedge members 45 which are displaceable in the force output member 18 and which are displaceably supported on the outer surface facing away from the force output member 18 via wedge surfaces 46 and on the outer surface facing the guide strips 35, 36, optionally with intermediate arrangements of corresponding not shown strips corresponding to the support strips 39. The wedge surfaces 46 extend in the direction of distance from the central plane 14 to the outer surface 11 so that when the set screws 37, 38 are screwed in together with the guide strips 35, 36 there is a displacement within the force output member 14 in the direction of the outer surface 11 Experienced. In this embodiment too, the set screws 37, 38 can be designed to be self-locking or lockable with lock nuts.

Of course, a wedge adjustment according to Figure 5 can also be provided in the embodiment of Figures 2 and 3. In the exemplary embodiments according to FIG. 4 and FIG. 5, the guide grooves 41, 42 can also be designed in a T-groove-like manner on their side facing away from the outer surface 11, as they are then also used to hold parts to be fastened to the cylinder tube 1, for example end stops for the power output member 14, suitable. In a modification of the exemplary embodiment according to FIGS. 2 and 3, it may be expedient to design the cover band 21 with a width that is greater than the distance between the mutually facing mouth edges of the two guide grooves 27 and 28; the space 22 and thus the entire force output member 18 are then designed to be correspondingly wide in order to carry out the shroud 21 through the force take-off member 18. This modification ensures that the shroud 21 not only covers the slot 10 outside the force output member 18, but also the two guide grooves 27 and 28 and thus protects against contamination. A pressure medium cylinder designed in this way is particularly well suited for operation in an environment where there is a risk of contamination.

The guide strips 35, 36 do not have to interact directly with the outer surface 11, which extends over the entire width of the cylinder tube, to form the guide tracks 11, 35 and 11, 36; rather, they can also rest on outer surface sections which are vertically offset from the remaining outer surface 11; the vertical offset facilitates the machining of the surface sections of the cylinder tube 1 which cooperate with the guide strips 35, 36.

In all embodiments, the guide strips 31, 32, 35 and / or 36 can be mounted from an end face of the power output member 18, even if the power output member 18 is already on the cylinder tube 1. This enables a simple replacement of worn guide rails.

Short version:

In a pressure medium cylinder with a longitudinally slotted cylinder tube (1), a piston (3) is only coupled to a force output member (18) for axial force transmission. The force output member (18) has a guide on the cylinder tube (1), which is designed as a mirror image of a central plane (14) through the cylinder axis (9) and the slot of the cylinder tube (1). On both sides of the central plane (14), the guide has two guideways (11.35 and 29.31 or 11.36 and 30.32). One guideway (29, 31 or 30, 32) runs inclined to the central plane (14) within an oblique guide groove (27 or 28) in the cylinder tube (1) and is not adjustable, while the other guideway (11, 35 or 11, 36) runs in or parallel to the outer surface (11) which has the slot and is perpendicular to the central plane (14) and can be adjusted perpendicularly to this outer surface (11). To adjust this other guideway (11, 35 or 11, 36), a guide bar (35 or 36) adjustable by means of adjusting screws (37 or 38) perpendicular to the outer surface (11) is provided in the force output member (18).

With the guide designed in this way, misalignments are easily recognizable, they cannot lead to overloading of the connecting means (16). Expansions of the cylinder tube (1) due to exposure do not lead to jamming of the force output member (18). Normal force loads on the force output member (18) are transmitted to the cylinder tube (1) without wedge action

Reference symbol list

1

Cylinder barrel

2nd

Cylinder cover

3rd

piston

4th

Pressurization room

5

Pressurization room

6

Cylinder bore

7

Bracket groove

8th

Cylinder wall

9

Cylinder axis

10th

slot

11

Outside surface

12

Side surface

13

Side surface

14

Middle plane

15

Piston seal

16

Lanyard

17th

Carrier

18th

Power link

19th

Sealing tape

20th

Guide channel

21

Shroud

22

room

23

Magnetic tape

24th

Cross groove

25th

Recess

26

adjusting spring

27th

Guide groove

28

Guide groove

29

Leadership area

30th

Leadership area

31

Guide bar

32

Guide bar

29.31

Guideway

30.32

Guideway

33

Continuation

34

section

35

Guide bar

36

Guide bar

11.35

Guideway

11.36

Guideway

37

Set screw

38

Set screw

39

Support bar

40

Guide leg

41

Guide groove

42

Guide groove

43

Leadership area

31.43

Guideway

32.44

Guideway

44

Leadership area

45

Wedge link

46

Wedge surface

Claims (8)

Pressure medium cylinder with a longitudinally slotted cylinder tube (1) which is closed at the end and which is delimited on the slot side by an outer surface (11) which is perpendicular to the slot (10) and in which a piston (3) is displaceably guided in a sealed manner by means of two piston seals (15) arranged near its ends , which is fixedly connected in the area between the piston seals (15) by means of a connecting means (16) penetrating the slot (10) to a driver (17) located in front of the slot (10) on the outside of the cylinder tube, with a slot (10) arranged on the inside of the cylinder tube outside of the section enclosed by the two piston seals (15) and sealing tape (19) that covers the pressure medium-tight and optionally a cover tape (21) covering the slot (10) on the outside with the exception of the passage area of the connecting means (16), with a force-transmitting member (axially displaceably guided on the outside of the cylinder) 18) which the driver ( 17) at least facing away from the slot and overlapping laterally, the guide of the force-transmitting member (18) on both sides of the slot (10) running symmetrically to a central plane (14) running through the slot (10) and containing the cylinder axis (9), each having two axially parallel to one another running, flat guideways (29.31 or 31.43 and 11.35 and 30.32 or 32.44 and 11.36) each with a guide groove (27.28 or 41.42) arranged on the cylinder barrel (1) ) and a guide bar (35, 36) which is adjustably arranged on the force output member (18), and with one arranged between the driver (17) and the force output member (18) and with limited transverse and Rotational mobility of the coupling device transmitting axial forces between these parts (17 and 18), characterized in that the guiding of the force-transmitting member (18) on both sides of the slot (10) within the guide groove (27, 28 and 41, 42) each has a guideway (29, 31; 30.32 or 31.43; 32.44) and on the outer surface (11) the other guideway (11.35; 11.36), one guideway (39.31; 30.32 or 31,43; 32,44) is not adjustable and runs inclined to the central plane (14) and the other guide track (11,35; 11,36) runs parallel to the outer surface (11) and which is adjustable in the direction perpendicular to the outer surface (11) Guide bar (35; 36). Pressure medium cylinder according to Claim 1, characterized in that the guide grooves (27, 28), starting from the outer surface (11), are inclined towards the side surfaces (12, 13) of the cylinder tube (1) and one guide surface (29, 30) ) are located on the inclined surfaces of the guide grooves (27, 28) facing the outer surface (11) (Fig. 2, 3). Pressure cylinder according to claim 2, with a shroud, characterized in that the shroud has a width which is greater than the distance between the mutually facing mouth edges of the two guide grooves (27, 28), so that in addition to the slot (10) it also has the mouths of the two guide grooves (27, 28) is able to cover. Pressure medium cylinder according to claim 1, characterized in that the guide grooves (41, 42) from the side surfaces (12, 13) of the cylinder tube (1) adjoining the outer surface (11) are inclined towards the outer surface (11) and the a guide surfaces (43, 44) are located on the inclined surfaces of the guide grooves (41, 42) facing the outer surface (11) (FIGS. 4.5). Pressure medium cylinder according to claim 4, characterized in that the guide grooves (41, 42) facing away from the outer surface (11) are of T-groove type. Pressure cylinder according to one or more of the preceding claims, characterized in that the guide strips (35, 36) held in the force output member (18) can be adjusted by means of adjusting screws (37, 38) arranged in the power output member (18) at right angles to the outer surface (11) (Fig. 2 to 4). Pressure medium cylinder according to one or more of claims 1 to 5, characterized in that the guide strips (35, 36) are arranged in the force output member (18) and at right angles to the outer surface (11) by wedge members (45) with wedge surfaces (13) which run inclined to the outer surface (11). 46) are supported, the wedge members (45) being adjustable by means of adjusting screws (37, 38) arranged at right angles to the central plane (14) in the power output member (18) (FIG. 5). Pressure medium cylinder according to claim 7, characterized in that the wedge surfaces (46) are arranged so as to divergently incline in the direction of distance from the central plane (14) from the outer surface (11).

Images