WO2012155892A2

WO2012155892A2 - Braking and/or clamping device having a driven cage

Info

Publication number: WO2012155892A2
Application number: PCT/DE2012/000532
Authority: WO
Inventors: Günther Zimmer; Martin Zimmer
Original assignee: Zimmer Guenther; Martin Zimmer
Priority date: 2011-05-17
Filing date: 2012-05-16
Publication date: 2012-11-22
Also published as: DE102011101804A1; WO2012155892A3; DE102011101804B4

Abstract

The invention relates to a braking and/or clamping device of a carriage guided on at least one rail, wherein the device comprises at least one frictional locking mechanism that can be actuated by means of a wedge drive. The frictional locking mechanism has at least one frictional jaw that can be pressed onto the rail. The wedge drive has at least one cage, which can be driven between a frictional jaw and an adjusting element by the actuator. The cage has at least one guiding hole perpendicular to the sliding direction of the cage. Rolling elements lying next to one another are arranged in the guiding hole. The frictional jaw and/or the adjusting element has/have an end face facing the cage that has a surface, the inclination of said surface being between 0.2 and 5 angular degrees relative to the sliding direction. According to the invention, a braking and/or clamping device is developed that has a simple and space-saving design along with large clamping forces and short response times and that is also lastingly maintenance-free.

Description

Brake and / or clamping device with

powered cage

Description:

The invention relates to a braking and / or clamping device guided on at least one rail carriage, wherein the device comprises at least one operable via a wedge gear, Reibgehemme, the at least one of the

Rail having compressible friction jaws. The wedge gear parts moved with the aid of external energy are movable for loading and unloading of the Reibgehemmes per loading and unloading by means of at least one actuator or by means of a spring system, wherein the spring system comprises at least one spring element.

From DE 10 2004 027 984 such a brake and / or clamping device is known. A sliding wedge driven by a cylinder-piston unit acts via at least one rolling element on a wedge surface of a friction jaw belonging to a friction brake.

The present invention is based on the problem to develop a brake and / or clamping device, which is a simple at large clamping forces and short reaction times

CONFIRMATION COPY and space-saving construction and is also permanently maintenance-free.

This problem is solved with the features of the main claim. The wedge gear has at least one cage which can be driven by the actuator between at least one friction jaw and at least one adjusting element transversely to the friction jaw. The at least one cage has transversely to its direction of displacement at least one guide recess in which two or - multiples of two - are arranged side by side contacting rolling elements. The at least one friction jaw and / or the adjusting element has an end facing the cage, which at least partially has a surface or a groove whose inclination relative to the direction of displacement is between 0.2 and 5 degrees.

In this brake and / or clamping device, e.g. the track fixed to the machine table, at which the carriage carrying the device is to be braked or clamped, from a base in the form of e.g. C-shaped bracket partially surrounded. The main body is in this case fixed in the direction of travel of the carriage dimensionally stable on the carriage, so that the braking force flow has the shortest possible path between the machine bed and carriage.

In a first variant of the braking and / or clamping device, a sliding wedge gear is actuated by a pneumatic actuator for braking and / or clamping, while in a second variant, such a drive for releasing the brake and / or clamping device is used. The or the respective drives span at least when they are actuated a spring accumulator whose spring energy is released later in a corresponding - the pneumatic drive movement - oppositely acting movement. Between the actuator and the respective friction jaws a narrow-built sliding wedge gear is used to apply the required braking or clamping or releasing force. This sliding wedge gear replaces the known driving splined wedge by a drivable cage, in which at least two rolling bodies are arranged transversely to the direction in which the actuator is displaced in a guide opening. The juxtaposed rolling elements are forced by means of the cage in a narrowing in the direction of travel gap, on the two lateral walls they act expansive. The first wall of the narrowing gap is an inner contact surface of an adjusting screw or a housing wall. The second wall is an inner contact surface of a friction jaw or the contact surface of an acting on the friction shoes gear part.

The narrowing of the gap is predetermined by the inclination of the walls relative to the actuator travel direction. In this case, both walls can be inclined with respect to the actuator movement direction with the same or different wedge angles. In another variant, one of the two walls may have a wedge angle of zero degrees.

Instead of a pneumatic actuator, hydraulic cylinder-piston units, diaphragm cylinders, solenoids, immersion coil drives, piezo actuators, shape memory elements or spring accumulators can also be used. All actuators can be used for both loading and unloading direction. In doing so, equal or different Such actuators per load direction - are arranged one behind the other or side by side in or on the housing.

The entire brake and / or clamping device has a cross-section - that is normal to the longitudinal direction of the guide - a contour that remains within the cross-sectional contour of most commercial carriages.

Of course, the brake and / or clamping device can also be completely integrated into a guide carriage or in the carriage. Also, the device can be used as an emergency brake.

The device is not limited to linear guides. With appropriate adaptation of the brake shoes, it can also be applied to circular paths or other e.g. in-plane curved tracks are used.

Further details of the invention will become apparent from the dependent claims and the following description of schematically illustrated embodiments.

Figure 1 · Dimetric representation of a brake and / or

Clamping device;

FIG. 2: vertical cross section to FIG. 1;

FIG. 3: horizontal longitudinal section to FIG. 2;

Figure 4: vertical longitudinal section to Figure 2;

FIG. 5: view of the pneumatic piston;

FIG. 6 shows a horizontal longitudinal section according to FIG. 2, but with two rolling elements bearing recesses in FIG

Piston rod; FIG. 7: view of the friction jaw;

FIG. 8 shows a diagrammatic representation of a brake and / or brake

Clamping device with two Reibhememmen;

Figure 9: vertical cross-section to Figure 8 through the

friction pad;

Figure 10 is a horizontal longitudinal section of Figure 9;

Figure 11 vertical longitudinal section to Figure 9;

FIG. 12 shows a vertical cross section to FIG. 10

Housing and non-round pistons;

FIG. 13: Dimetric view of the cage.

FIGS. 1 to 7 show a braking and / or clamping device which according to FIG. 2 encompasses a guide rail (7). It consists u.a. from a base body (10), a pneumatic actuator (60), cf. 3, a plurality of Rückhubfederelemen- th (88) and a sliding wedge gear (50). The device is attached via the base body (10) to the carriage (1), which is to be braked or clamped on the guide rail (7), cf. FIG. 2. The guide rail (7) runs parallel to the carriage movement direction or to the guide longitudinal direction (2). FIG. 8 shows a section of a double-prismatic guide rail (7). The guide rail (7) consists of a rod with an approximately parallelepiped Hüll- cross-section, in each of which a substantially V-shaped groove with widened groove base is incorporated on both sides. It contacts via its bottom surface e.g. the machine bed (5) carrying it, cf. FIG. 2.

The guide rail (7) has according to Figure 2 above the V-shaped groove, inter alia, two minor surfaces (8, 9), based on the vertical center longitudinal plane (6) are mirror images of each other. Both auxiliary surfaces (8, 9) are aligned parallel to each other. They serve the Reibhememme (51) as contact surfaces for the friction pads (53).

The e.g. one-piece, made of 16 nCr 5 basic body (10) is essentially a cuboidal component, which on its underside a. off-center groove (19) with a e.g.

has rectangular cross-section. In the groove (19), the guide rail (7), according to Figure 2, to ca. three quarters.

The basic body (10) has, for example, the following dimensions: 58 mm × 35 mm × 28 mm.

The main body (10) has e.g. a small, right (11) and a large, left housing zone (12). Both zones (11, 12) are located below a flange zone (13). The left housing zone (12) has a width of about 23 mm, while the width of the right housing zone (11) measures only about 11 mm. In the flange zone (13) is u.a. a device carrier (95) stored. The device carrier (95) according to Figure 1 has a key-like geometry. Its upper adapter surface has two threaded holes (96) for attachment to the device supporting slide (1), see. Figure 2. Transverse to the threaded holes (96) it has e.g. two slide holes (97) parallel to the clamping direction (3) and also transversely to the guide longitudinal direction (2), see. Figure 3, are oriented.

In the top of the base body (10) for mounting the device carrier (95) in a longitudinal direction of the guide (2) oriented slot (15) is incorporated, which is cut by two transverse bores (16). The width of the elongated hole (15) measured in the clamping direction (3) is like the length of the oblong hole (15) measured in the guide longitudinal direction (2) in each case for example, 2 mm wider than the corresponding extension of the device carrier (95).

The device carrier (95) sits over with little play _. 5 its slide holes (97) on the in the transverse bores (16) clamped sliding pins (98). To center the housing (10) elastically floating in the clamping direction (3) on the device carrier (95), sitting on both sides of the device carrier (95) elastomeric body (99), which are also on the Gleitstif- ten (98) stored. The elastomeric body (99) can the. Shape of a tome, the shape of a perforated disc or the shape of a rectangular or other polygonal mono- or multi-perforated plate have. After assembly, the adapter surface of the device carrier (95) protrudes, for example, from 0.1 to 0.5 mm 15 over the upper side of the base body (10).

The housing zone (12) has a multi-stage blind bore (21) for receiving the drive (60), whose center line (29)

20 parallel to the guide longitudinal direction (2) is oriented, see.

FIG. 3. The blind hole (21) is composed of a cylinder

¹ derflächenausnehmung (22) and a wedge gear recess (23) together. Between both recesses (22, 23) is a flat housing collar (24). The cylindrical surface

25 mung (22) is when using a piston with a circular cross-section a cylinder jacket surface. In the present embodiment, the pneumatic piston (61) has a rectangular surface with rounded corners. Accordingly, the Zylinderflächenausnehmung (22) is a piston cross-section, he has e.g.

30 an area of approx. 452 mm ² , adapted square recess.

- The wedge gear recess (23) is according to Figures 3 and 4, a cylindrical bore with a flat bottom. Its inside diameter measures eg 20 mm. The plan reason is according to FIG. 4 three short cylindrical blind holes (37), each also having a flat bottom. Their center lines are eg in a plane. Each blind bore (37) carries a return spring (88).

In the vicinity of the front end surface (14) of the base body (10) are in its side surfaces, the top and the bottom four threaded transverse bores (17) whose center lines lie in a plane and also cross the center line (29) perpendicular or cross ,

Transverse to the stepped bore (21) extends a Gehemmebohrung (30), the center line (39), the center line (29) of the Stufenboh- ments (21) crosses or cuts. Here, the center line (39) with respect to the center line (29) - with an appropriate adjustment of the wedge angle (alpha) - occupy an angle of 90 ± 3 degrees. The Gehemmebohrung (30) has four stepped areas, see. FIG. 6. From the main body outside, these are a sealing seat bore (31), a main bore (32), a pressure piece guide bore (33) and an outlet recess (34). The

Main bore (32) intersects with the wedge gear recess (23). In this area), cf. Figure 3, there is a e.g. two cylindrical rollers (91, 92) bearing cage (71).

The sealing seat bore (31) located between the outside of the housing and the main bore (32) receives a setting screw (45). In the area of the adjusting screw (45), the main bore (32) for the adjustable positioning of the adjusting screw (45) carries a fine thread. The adjusting screw (45) is a cylindrical disc having bores for engaging a spanner on the outer end face. It has an inner, planar end face (46), which is oriented in the embodiments normal to its center line, it is congruent to the center line (39).

It has an external thread that ends in an annular groove. In the groove, a crimp ring is inserted as a screw lock and for sealing against the sealing seat bore (31). With the adjusting device (45), the freedom of movement of the sliding wedge gear (50) is ensured when the device is mounted, and the clearance between the friction surface (58) of the friction pad (53) and the secondary surface (8) of the guide rail (7) is influenced ,

Depending on the design of the base body (10), it is also possible to dispense with the adjusting screw (45). In this case, the end face (46) is an integral part of the basic body (10).

The pressure piece guide bore (33) adjoins the guide bore (7) to the main bore (32). It goes over a e.g. plan housing collar (35) into the outlet recess (34) via. The latter has a smaller cross section than the pressure piece guide bore (33). The also has possibly a non-circular cross-section.

The pressure piece (54) is the cylindrical piston of the friction jaw (53). On the piston (54) a piston rod (57) is formed, see. FIG. 7. The end face of the piston rod (57) projecting into the groove (19) carries at its free end the friction surface (58) of the friction jaw (53). The latter has a which is congruent with the center line (39) of the Gehemmebohrung (30).

The end face of the pressure piece (54) oriented towards the bore hole (30) is an e.g. plane wedge surface (55), which is inclined relative to the center line (29) by 0.2 to 5 degrees. In the exemplary embodiment, the angle of inclination or the wedge angle (alpha) is 2 degrees. Due to this inclination, the distance to the inner end face (46) of the adjusting screw (45) that can be measured transversely to the center line (29) narrows with increasing depth of the stepped bore (21).

The piston rod (57) projects out of the outlet recess (34) when the friction clip (51) is actuated. At the transition of the piston rod (57) to the piston (54) there is an e.g. ring-channel-like end groove (56), in which, according to Figures 3 and 7, an elastic Rückhubring (59) with e.g. rectangular single cross section sits. The return stroke ring (59) holds the pressure piece (54) in its rear position when the friction clip is not actuated (the device has no clamping or braking effect).

The piston rod (57) whose outer, radial contour lies within the end groove (56) has, according to FIG. 7, at least approximately - for preventing rotation about the center line (39) - a square cross-section.

To prevent rotation any other cross-sections for the piston rod (57) are conceivable. It is also possible to move the anti-twist device into the piston (54).

Between the pressure piece (54) and the adjusting screw (45) of the cage (71), for example, as a molded part of a pneumatic piston (61) is arranged. The combination of pneumatics Ben (61) and cage (71), inserted from the front side (14) of the main body (10), in the stepped bore (21), wherein the pneumatic piston (61) in the Zylinderflächenausneh- mung (22) is guided. The piston or pressure chamber (25) is sealed to the front (14) with a lid (40) gas-tight.

The cover (40) whose outer end surface is flush with the front side (14) of the main body (10) in the exemplary embodiment has a peripheral annular groove (41) in which a sealing ring (42) is arranged. Between the annular groove (41) and the front side (14) it has e.g. four holes (43), which with the corresponding threaded cross bores (17) of the

Body (10) are aligned. In the threaded cross bores (17) of the base body (10) for fixing the cover (40) threaded pins (44) are screwed. The e.g. completely in the base body (10) countersunk threaded pins (44) have their cover thread formed in the made of an aluminum alloy or a plastic cover (40) itself.

If the pneumatic piston (61) has a circular cross-sectional shape, the cover (40) in the base body (10) is e.g. just as fixed as the adjusting screw (45).

The combination of the pneumatic piston (61) and the cage (71) is shown in FIG. The piston (61) has a rectangular cross section with dimensions of 20 mm x 23 mm. For example, the corners are rounded off with a 3 mm radius. The pneumatic piston (61) has an annular groove (62) in which, according to FIG. 3, a sealing ring (63) is arranged. The piston front side has, according to FIGS. 3 to 5, an approximately 0.5 mm deep air distribution groove (64). The cage (71) adjoins the back of the pneumatic piston (61) in the shape of a koibenstangen. The cross section of the cage (71) essentially represents a circular area which is reduced by two opposing, equally sized circular sections. The circular area here has a diameter which is, for example, slightly smaller, for example 0.1 to 0.2 mm, than the diameter of the wedge gear recess (23). The circular sections have a height of eg

3, 4 mm. The predetermined by the circular sections of the cross-section planar side edges (73, 74) of the cage (71) are executed with respect to the cylinder jacket-shaped Käfigaußenwandung rounded. Between the mutually parallel side flanks (73, 74) extends, e.g. in the rear region of the cage (71), a guide opening in the form of a rectangular channel (81). The rectangular channel (81) according to Figure 4 has a width of 7 mm and a height of 14 mm. He has normal to the center line (29) two at least partially planar channel walls (85, 86). Possibly. Both channel walls (85, 86), or at least the one which must withstand the higher surface pressure during operation of the device, are provided with a wear-resistant coating, e.g. hard chrome plating, nitriding layer or the like. In this rectangular channel (81) sit with little play two cylindrical rollers (91, 92), the contact each other in the region of the rectangular channel center - with clamped device -. The cylindrical rollers (91, 92), which in this case almost fill the width of the rectangular channel (81), are arranged between their planar end faces and their cylindrical outer surface with a radius of e.g. 0.5 to 1.2 mm rounded.

According to FIG. 6, which shows parts of a variant of the previous device, the cage (71) has two transversely to the middle line. never (29) parallel to each other arranged guide openings in the form of rectangular channels (81, 82). Between the rectangular channels (81, 82) is a dimensionally stable partition of the width of eg 1 mm.

In both rectangular channels (81, 82) are respectively

(n) Cylindrical rollers (91, 93), where (n), in FIG. 6, there are four pieces belonging to the set of natural even numbers which are greater than or equal to 2. The cylindrical rollers (91) of the piston remote rectangular channel (81) have a diameter (r), while the cylindrical rollers (93) of the piston near rectangular channel (82) have a radius (R). The rectangular channel center lines (83, 84) are at a distance (a). At a wedge angle (alpha), a cylindrical roller radius (R) results for the cylindrical rollers (93) of the piston-near rectangular channel (82), which results from the following formula: a * tan (alpha)

R = r +

1

(2n - 1) +

cos (alpha)

In the exemplary embodiments of FIGS. 1 to 7, when the device is not actuated, i. the pneumatic piston (61) contacts the cover (40), the respective outer, left cylindrical roller (91) on the adjusting screw (45) and the respective outer, right cylindrical roller (92) on the wedge surface (55) of the pressure piece (54). The return springs (88) and already biased in this position Rückhubring (59) ensure a play-free system.

In the solutions described so far, the cylinder rollers (91, 93) are always located, for example, in pairs, four or six adjacent to one another in the rectangular channels (81, 82). Through this Arrangement rolls, eg ei two cylindrical rollers (91, 92), when retracting the cage (71), so when clamping, according to Figure 3, the left cylindrical roller (91) on the adjusting screw (45) in the counterclockwise direction, while the right cylindrical roller ( 92) on the pressure piece (54) rotates clockwise. In the contact point of the two cylindrical rollers (91, 92) they roll - without relative movement - to each other. Both cylindrical rollers (91, 92) are supported by a sliding movement on the front duct wall (85) of the rectangular duct (81). Due to the play of the cylindrical rollers (91, 92) in the rectangular channel (81) these do not contact the rear channel wall (86).

For example, in devices that require lower clamping or braking forces, the cylindrical rollers can be replaced by balls. The balls then sit in the cage (71) in corresponding guide holes. In this case, instead of a wedge surface (55), the pressure piece (54) can also have a ball-guiding groove. If several guide bores are used per cage, they can be arranged one behind the other and / or next to each other with respect to the guide longitudinal direction. Even an oblique offset is possible.

The clamping shown in FIG. 3 is in the unactuated state. The pneumatic piston (61) rests against the cover (40). For example, compressed air is pressed in between the piston front side and the rear side of the cover (40) via a supply air bore (38) arranged on the upper side of the housing (10). As a result, the combination of piston (61) and cage (71) - including against the action of the return springs (88) - moved backwards. Via the front channel wall (85) of the rectangular channel (81), the two cylindrical rollers (91, 92) between the adjusting screw (45) and the pressure piece (54) forced. As a result, the pressure piece (54) yields under compression of the elastic return stroke ring (59). The friction pad (53) moves to the right according to FIG. 3, in order to be applied to the auxiliary surface (8) of the guide rail (7), cf. In this process, the base body (10) moves relative to the device carrier (95) so far to the left until the right groove wall (20) of the groove (19) on the right side surface (9) of the guide rail (7) applies.

To release the brake or clamping, the supply air connection (38) is vented. The return springs (88) move the combination of cage (71) and piston (61) forward. At the same time, the relieving return stroke ring (59) pushes the friction jaw (53) into its starting position known from FIG. The clamp or brake is open.

In the figures 8 to 13, a device is shown, which has two opposing Reibgehemme (51, 52). In this device, the base body (10) is rigidly attached to the slide (1), not shown here. For this it has e.g. in the top of the base body (10) arranged mounting holes (18). Clamping and / or braking is here e.g. by means of spring force, while the release takes place pneumatically.

The structure of the Reibhememme (51, 52) is known from the description of Figures 3 and 4. However, the single cage (71, 72) has the form of a separate disc, cf. Figure 13, which is flattened front and rear relative to the guide longitudinal direction (2). At the rear flattening (76), cf. 11, a return spring (88) is located, which is located in a base body bore on a ball (48) which is compressed there. supports. Possibly. located in the rear flattening (76) has a recess into which the return spring (88) is immersed.

At the front flattening (75) is located in a guide bore (26) of the base body (10) mounted on the piston rod (65). The piston rod (65) is in a c-shaped piston (61), see. FIG. 12, fixed by means of transverse press fit, cf. Figures 10 and 11, and projects into a recess (77) of the cage (71, 72).

The piston rod (65) is sealed with respect to the cage (71, 72) and / or leading Gehemmeausnehmung (30) with a lip seal (66), wherein the sealing lips in the direction of the piston (61) show. Between the piston (61) and the lip sealing ring (66) in the section (27) of the stepped bore (26) a flange-mounted guide bushing (67) is arranged, which holds with its flange, the lip seal (66) in its intended position and on the other hand, the screw spring (68) supporting itself on the flange leads. The latter is supported on the piston (61).

The base body (10) is closed towards the front with a lid (40) which has at least approximately the cross section of the piston (61). The lid (40) has a circumferential groove for receiving a sealing ring (42). Between the front of the housing (14) and the annular groove (41), the cover (40) has a few transverse bores (43). These transverse bores (43) each sit in the extension of special threaded transverse bores (17) of the main body (10). As in the variant according to FIGS. 1 to 7, e.g. four setscrews (44) the lid (40) in its intended position.

Before the cover (40), a spring-loaded housing (100) is arranged on the base body (10). The latter has at least approximate the same overall cross section as the main body (10). The eg with two screws (108) on the base body (10) attached spring-loaded housing (100) has in addition to the holes for the screws (108), for example, four further spring guide holes (101). The open to the cover (40) spring guide holes (101) take, for example, two nested coil springs (105, 106).

Each spring box (105, 106) acts via a support pin (102) on the front of the piston (61). In this case, the individual support bolt (102) is mounted on the one hand via its shaft in the cover (40) and on the other hand by means of its on the coil springs (105, 106) adjacent Stützbolzenflansches (103) in the corresponding spring guide bore (101).

In the spring guide bores (101) instead of the

Coil springs also identical or interchangeable stacked disc springs or other suitable spring types can be used.

In this device variant according to Figures 8 to 13, the clamping and / or braking by means of the coil springs (105, 106) of the spring accumulator as soon as the pneumatic pressure chamber (25) is vented, see. FIG. 10. The coil springs (105, 106) push the piston (61) into the pressure chamber (25) via the support bolts (102), the piston rods (65) deflecting the cages (71, 72) against the action of the springs (68 , 88) to push the friction jaws (53) against the guide rail (7).

To release the device is via the compressed air line (38), see. 11, the pressure chamber (25) supplied with compressed air, wherein the piston (61) moves back to thereby the spring Memory to load. The return stroke is supported by the springs (68, 88).

For passages which have the word sequence "at least approximately" in the context of a parallel or perpendicular arrangement of two abstract lines or of two concrete objects, deviations from the parallel or vertical of ± 3 degrees of angle are permitted.

List of reference numbers:

1 sled

2 guide longitudinal direction, carriage movement,

displacement direction

3 clamping direction

5 machine bed

6 vertical middle longitudinal plane

7 rail, guide rail

8, 9 secondary areas

10 basic body, c-shaped; casing

11 housing zone, right

12 housing zone, left

13 flange zone

14 front side; Face, front

15 slot

16 cross holes

17 threaded cross bores

18 housing threaded holes, mounting holes

19 groove

20 groove wall, right 21 blind hole, stepped

22 Zylinderflächenausnehmung, cylinder

23 wedge gear recess

24 housing collar

25 pressure chamber

26 pilot hole, multi-stepped

27 section for (guide bush)

29 center line of (21)

30 Gehemmebohrung, Gehemmeausnehmung 31 sealing seat bore

32 main hole

33 pressure piece guide bore

34 exit recess

35 housing collar

Blind holes, short

Supply air connection, supply air hole

Centerline of (30)

cover

Ring groove, circumferential

seal

cross holes

screws

45 adjusting screw; Wedge gear part

46 face, inside

48 ball

50 wedge gearboxes, sliding wedge gearbox

51, 52 Friction crutch

53 friction jaws

54 pressure piece, cyl. Piston; Wedge gear part

55 wedge surface, area

56 face groove

57 piston rod

58 friction surface

59 Return ring, elastic

60 actuator, drive

61 pneumatic pistons, pistons 62 ring groove

63 sealing ring

64 air distribution groove

65 piston rod

66 lip seal

67 guide bush

68 coil spring

71, 72 cage; Wedge gear part

73, 74 side flanks, flat

75 flattening, front

76 flattening, rear

77 depression, bore

81, 82 guide opening, rectangular channel

83, 84 centerlines

85 duct wall, front

86 KanaIwandung, behind

88 return springs, return spring element,

Helical compression spring

91, 92 cylindrical rollers, rolling elements; Wedge gear part 93 Cylindrical rollers, rolling elements; Wedge gear part

95 device carrier

96 tapped holes

97 Sliding hole

98 sliding pins

99 elastomer body 100 spring accumulator housing

101 spring guide holes

102 support bolts

103 Support bolt flange

105 coil spring, outside

106 coil spring, inside

108 screws

a distance between the center lines (83, 84) of the rolling elements (91, 93) of two adjacent guide openings (81, 82)

alpha wedge angle of the pressure pad wedge surface (55) n number of rolling elements (91, 93) per guide breakthrough (81, 82)

r radius of the smaller rolling elements (91)

R radius of larger rolling elements (93)

Claims

Claims:

1. Brake and / or clamping device on at least one

Rail guided slide,

- wherein the device comprises at least one, via a wedge gear (50) actuated, Reibgehemme (51, 52), which has at least one of the rail (7) can be pressed friction jaws (53),

in which the wedge gear parts (45, 54, 71, 72, 91-93) moved by means of external energy are used to load and unload the individual friction stop (51, 52) per loading and unloading direction by means of at least one actuator (60). or by means of a spring system, wherein the spring system comprises at least one spring element (68, 88, 105, 106), characterized

- that the wedge gear (50) has at least one cage (71, 72) which is drivable between at least one friction jaw (53) and at least one adjusting element (45) transversely to the friction jaw (53) from the actuator (60),

- That the at least one cage (71, 72) transversely to its direction of displacement (2) at least one guide opening (81, 82) in which two or multiples of two juxtaposed contacting rolling elements (91 - 93) are arranged and

in that the friction jaw (53) and / or the adjusting element (45) has an end face facing the cage (71, 72), which at least partially has a surface (55) or groove whose inclination relative to the displacement direction (2) lies between 0, 2 and 5 degrees.

2. Device according to claim 1, characterized in that in the case of a cage (71, 72) with more than one guide opening (81, 82) the radius (R) of the respective larger rolling elements (93) of two successively arranged guide openings (81, 82) is calculated from a sum with a first and a second summand. The first addend is the radius (r) of the smaller rolling elements (91). The second addend is a major break with a major dividend and a major diver. The main dividend is composed of two factors, the first factor being the distance (a) of the center lines (83, 84) of the two adjacent guide apertures (81, 82). The second factor of the main dividend is the tangent of the wedge angle (alpha). The main divisor consists of a sum. The first main divisor margin is a subtraction whose minuend consists of twice the number of rolling elements (n), while the subtrahend is the number one. The second main divisor bucket is a fraction whose counter represents the number 1. The denominator of the fraction is the cosine of the wedge angle (alpha).

3. Device according to at least one of the preceding claims, characterized in that the cage (71, 72) is a part of the actuator (60).

4. The device according to at least one of the preceding claims, characterized in that the at least one guide opening (81, 82) at least one direction of displacement (2) at least approximately normal channel wall (85, 86) which has a wear-resistant surface coating.

5. The device according to claim 1, characterized in that the friction jaw (53) is mounted against rotation in the base body (10).

6. The device according to claim 1, characterized in that the adjusting element (45) is an integral part of the base body (10).

7. The device according to claim 1, characterized in that the actuator (60) is a cylinder-piston unit whose piston (61) and the cylinder (22) has a non-circular cross section.

8. The device according to claim 1, characterized in that the cage (71, 72) for releasing the friction pad (53) by a loaded spring accumulator (88) is driven.