DE2657356A1 - CLAMPING DEVICE FOR FRICTION BRAKES - Google Patents

Description

Ilünchen, November 2nd, 1976 TP11-si

" ¹⁵⁸⁸ " 2657355

KNORR-BHEMSE GmbH, 8000 Mönchen 40, Moosacher Strasse 80

Application device for friction brakes

The invention relates to an application device for friction brakes in particular of rail vehicles, with an annular body rotatable via a drive element between two non-rotatable, mutually axially displaceable abutments, wherein between the ring body and at least one of the abutments is coaxial with the axis of the ring body Spiral track sections guided rolling bodies are arranged.

Such application devices are already widely known, for example from DT-OS 24-534-97. With these the rolling bodies are designed as balls, which are guided in running grooves that flatten in a rolling direction. With exact mitigation, the balls run in the grooves with line contact, the required clamping forces for the Friction brake therefore require despite multiple arrangement of the Balls high surface pressure at the ball contact points. Furthermore, the application stroke is always smaller than the diameter the relatively small balls; the application stroke is sufficient to operate disc brakes, but not

- 2 809-825 / 0301

Block brakes for rail vehicles. Finally, the Kihrungsrillen for the balls have the same over the entire length Incline, the clamping devices thus have a constant power transmission over the entire stroke.

The invention is based on the output, an application device of the type indicated at the outset so that they are efficient and with little wear is as versatile as possible.

This object is achieved according to the invention in that the collars on the part carrying the helical sections opposite part - ring body or abutment about axes extending radially to the axis of rotation of the ring body are rotatably mounted rollers.

In a further embodiment of the invention, it is useful if the rollers are mounted on the ring body and are continue to be located only between the ring body and one of the abutments, while the ring body has an axial roller bearing is supported against the other abutment.

The abutments on both sides of the ring body can be non-rotatably guided; for this it is particularly advantageous when one of the abutments has a cylindrical extension on which the ring body is rotatably mounted is and which is in the area of the other abutment by means of an elongated hole running in an axis spar] 2el

809825/0309 ~ ³ "

2657358

engaging, radial bolt is rotatably guided on the other abutment. A particularly advantageous arrangement results when the ring body mounted on the outer circumference of the cylindrical extension is the other abutments, also mounted on the outer circumference, radially outwards, at least partially in the axial direction covered and if the rollers are arranged in an annular space between the ring body and the outer circumference. Here is a good protection of the spiral track sections as well as the rollers and also the storage of the ring body and the other Abutment possible.

In a further embodiment of the invention, it is possible that the spiral track sections in the application stroke of the friction brake Corresponding contact area for the rollers has a large spiral gradient in the plague brake area of the friction brake corresponding contact area for the rollers have a low helical pitch. This achieves that the application device in the application stroke area a large path translation, in the lestbremshubbereich one has a large power transmission and thus only a short stroke on your drive device for clamping which requires brakes.

An expedient embodiment of the application device can also be achieved in that at least on the ring body a radially projecting lever arm is provided to which a drive device is articulated. It is

.309826 / 0309 '-4-

it is advantageous if at least one of the abutments carries a counter bearing for the drive device. This results in a closed force circuit and supports for reaction forces of the drive device are provided dispensable.

A particularly advantageous construction is obtained when at least approximately diametrically on the ring body oppositely arranged 2 radially projecting lever arms are, on one of which is a spring accumulator and on the other a release cylinder that can be locked by pressure is hinged for the spring accumulator. If the articulation point of the spring accumulator and / or the Release cylinder on the lever arm is designed to be adjustable in its longitudinal direction, it is possible to avoid tolerance deviations of the spring accumulator in relation to the application force that can be exerted by the application device and / or in Balance the relation to the release force exerted by the release cylinder.

A particularly advantageous arrangement is obtained if, according to the further invention, the housing of the spring accumulator and the release cylinder are arranged next to one another with their mutually parallel axes being in a plane perpendicular to the axis of rotation. Through this is a particularly narrow construction of the entire application device possible.

809825/0309 _ ₅ _

Finally, it is according to the invention to avoid crushing and to achieve a low friction The course of the rollers according to the invention is expedient if the rollers are designed as tapered rollers with lying in the axis of rotation Conical tip are formed.

In the drawing are some exemplary embodiments of according to the invention designed application devices shown, namely shows:

Pig Λ a cut image,

Pig 2 a view and

Pig 5 a detail in a modified version of a clamping device,

Pig 4- a clamping device designed as a brake pad unit partially cut in view and

Pig 5 partially cut in front view,

Pig 6 cut an application device designed as a handbrake device and

Pig 7 in. Front view,

Pig 8 a modified version of the handbrake device in section,

Pig 9 a spring-loaded application device partly in section,

Pig 10 the. Application device according to Pig 9 as a disc brake unit and

Pig 11 a modified version of the disc brake unit.

809825/0309 -6-

- Any -

2657358

In Fig. 1, the reference numeral 1 is essentially a tubular abutment shown, which with a radially outer Plansch 2 and a radially inner Splash 3 is provided. A slack adjuster 4, which is only partially shown, is supported on the flange 3 friction brake not shown leads. The flange 2 is provided with an axial annular groove 5 into which a rotatably and axially displaceably mounted on the outer circumference 6 of a tubular extension 1 'of the abutment 1 Ring body 7 is able to intervene. The radial wall of the flange 2 radially outside the annular groove 5 is at diametrical opposite points provided with two spiral track sections, on which rollers 9 are able to run, as especially can be clearly seen from FIG. However, there can also be more than 2 spiral track sections 8 and rollers 9 over the Perimeter of the flange 2 be arranged distributed. The rollers have an axial direction perpendicular to the axis of rotation 10 of the ring body 7 rotatably mounted on bolts 11 projecting radially outward from the ring body 7. The roles are useful 9 forms as pushed onto the bolt 11 rolling bearings aus.

The end face of the ring body 7 facing away from the flange 2 is against a pipe section via an axial roller bearing 12 13 of a second abutment 14 is supported. The pipe section 13 is longitudinally displaceable on the outer circumference 6 of the extension 1 '; he's in opposite places each with a slot-like groove 15

- 7 -809825/0309

provided, in which evidence is used as a sliding block, on a radial bolt 16 of the abutment 1 mounted roller 17 engages. The abutment 1 is hereby non-rotatably but axially displaceably guided on the abutment 14.

The abutment 14 is facing away from the abutment 1 Side provided with bearing eyes 18, with which it receives the application device and their Reaction force dissipating component, not shown, can be fastened. The ring body 7 has a radial cantilevered lever arm 19 is provided, at the end of which by means of a fork lever 20 a not shown in Pig 1 and 2 Drive device for rotating the ring body 7 is articulated.

If the drive device, not shown, exercises a fork lever 20 directed into the plane of the drawing according to Pig 2 Force on the lever arm 19, the ring body 7 ™ rotates its axis of rotation 10, whereby about the bolts 11, the rollers 9 are taken along and run onto the spiral track sections 8 in the process. The rotatably held abutment 1 is according to the slope of the spiral track sections 8 according to Pig 1 and Pig 2 are printed to the right, whereby it is over the slack adjuster 4 the friction brake applies and applies. The reaction force directed to the left is thereby provided by the “ring body 7 via the axial roller bearing 12 and the abutment 14

SO9825 / Q309 _ ₈ _

265735S

directs.

Palls the application device for actuating a friction brake is provided with a large ventilation clearance, for example a block brake for rail vehicles, it may be useful to design the spiral track sections with a kinked slope according to Hg 3: When the brake is released, the roller 9 rests against a region 21 of the spiral path section 8, which is a has a large helix pitch. When the brakes are actuated, the roller 21 arrives shortly before the end of the application stroke the friction brake to a kink 22 of the spiral path section 8, at which the area 21 is larger Helical pitch merges into a region 23 with a low helical pitch. During the rest of the mooring stroke and during the entire Pestbremshubes the roller 21 runs in the area 23 of low helical pitch. It results thus that during the major part of the application stroke of the friction brake on the ring body 7 Torque exerted with great excess displacement on the friction brake is transmitted and causes their rapid application, and that shortly before the end of the application the great way into a great transmission of force, passes over, so that during the Pestbremshubes the friction brake can be applied with great force.

In Pig 4 and 5 is the design of the applicator shown according to Pig 1 to 3 to a block brake unit.

809825 / 03OS - 9 -

-Ύ-

The abutment 14 is attached to a vehicle-fixed carrier 24 and carries a brake cylinder 25, the piston rod 26 ends with the fork 20 after 'Pig 2'. The brake cylinder 25 is in the inclined position shown in Pig 5 the abutment 14 saddled with the piston rod direction approximately tangential to this; this results in a particularly space-saving arrangement of the individual parts of the brake pad unit. On the side facing away from the carrier 24 carries the abutment 14 has a cantilevered support arm 27, at its free end a pendulum extending to the brake pad 28 29 is hinged. The ring body 7 is rotatably mounted in the abutment 14 and carries the helical path sections 8, on which the rollers 9 mounted on the abutment 1 by means of bolts 11 rest. The abutment 1 is together with the Slack adjuster 4 mounted displaceably in the abutment 14; the bolts 11 engage through those arranged in the abutment 14 Elongated holes 15 and thus secure the non-rotatable guidance of the abutment 1. The front end of the slack adjuster 4 is on a plunger 30 protruding from the abutment 14 Brake pad 28 articulated.

The application device according to Pig 1 to 3 is also well suited as a hand brake device combined with a brake cylinder to be used:

In Pig 6, a brake cylinder 31 is part of a Piston rod guide tube 32 fixed to the housing, a piston and a piston rod tube 34 are shown. The abutment 14 is formed by an annular body which is fixedly arranged on the piston rod guide tube 32 and against which it extends

809825/0309

- 10 -

the roller bearing 12 is supported by the ring body 7 rotatably mounted on the piston rod guide tube 32. The free end the lever arm 19 of the ring body 7 is articulated via the fork piece 20 to a Bowden cable 35, the jacket hose is supported against an abutment 37 attached to the brake cylinder 31, as can be seen from FIG. The abutment 1 is than mounted on the piston rod guide tube 32 Ring formed, from which the bolt 16 protrudes radially inward and in elongated holes 15 and 38 of the piston rod guide tube 32 or the piston rod tube 34 engages. Secured by the guide in the piston rod guide tube 32 the bolt 16 the non-rotatable guide of the abutment 1. The elongated hole 38 enables on the one hand a displacement of the piston rod tube 34 when the brake cylinder piston 33 is pressurized to the left as shown in FIG. 6, the abutment 1 can remain in peace; on the other hand, when the bolt 16 rests against the left boundary of the elongated hole 38 the piston rod tube 34 · taken along when turning the Annular body 7, the abutment 1 is moved to the left.

A particularly expedient design is obtained when, according to FIG. 8, the ring body 7 is L-shaped in cross section and is mounted on the piston rod guide tube 32 in such a way that between the ring body 7 and the piston rod guide tube 32 an annular space 39, which is open toward the side facing away from the piston, is created. The ones about the

- 11 -

809825/0300

Bolts 11 on the ring body 7 mounted rollers 9 are "in the annular space 39" in which from the open side also the ring-like abutment 1 engages. The rest of the training corresponds to that according to Pig 6. With this design, a protected arrangement of the rollers 9 and the spiral track sections 8 is achieved; It is also possible to use a bellows extending from the annular abutment 14 to the annular body 7 40 and another, from the ring body 7 to not shown piston rod head of the brake cylinder 1 extending bellows 41 to be arranged. There is thus the possibility of complete coverage of all movable ones Parts of the brake cylinder 31 given with a manually operated application device, so that these parts are also under not soiled under unfavorable conditions of use and thus can wear out more.

When using the application device as a spring-loaded brake unit it is expedient to place another, in FIG. 3, on the ring body 7 opposite the lever arm 19 Provide lever arm 42 shown in phantom. The abutment 14 is shown in FIG. 9 with a carrier provided on which a cylinder-like spring accumulator 44 and a pressurized medium Release cylinders 45 are attached side by side in such a way that that their axes 46 and 47, which are parallel to one another, are located in a plane perpendicular to the axis of rotation 10. Of the

809825/0309

Spring accumulator 44 has a storage spring in a housing 48 49, which is supported against a spring plate 50 guided displaceably in the housing 48. The spring plate 50 is via a rod 51 at the free end of the Lever arm 19 a steered. The release cylinder 45 has a pressurized piston 52, the piston rod 55 is articulated at the free end of the lever arm 42. The articulation point 54 of the rod 51 on the lever arm 19 and the Articulation point 55 of the piston rod 53 on the lever arm 42 are each designed to be adjustable in the longitudinal direction of the lever arm 19 or 42 * By appropriate adjustment of the Distance b of the articulation point 54 from the axis of rotation 10 can be the torque exerted by the storage spring 49 on the ring body 7 and thus that of the application device exertable application force can be precisely adjusted; even large tolerances of the force exerted by the accumulator spring 49 can thereby be compensated for without difficulty will. Storage springs 49 which can be produced cheaply can thus be used.

The distance a of the articulation point 55 from the axis of rotation 10 is then adjusted in such a way that at full Pressurization of the piston 52 with the available standing release pressure that exerted by the piston 52 The force is just sufficient to use the lever arms 42 and 19 to use the Peder plate 50 to tension the accumulator spring 49 to push back. The exerted by the clamping device

9825/0309 -13-

The actual application force K results from K = P ₁ , xbxi,

where Ρ ™ is the force that can be exerted by the accumulator spring 49, b the distance of the articulation point 54- from the axis of rotation 10 and e is the transmission factor of the application device determined by the pitch angle of the helical path sections 8 mean · The pressure medium pressure required to release or, if it is fixed, the distance a the Articulation parts 55 of the axis of rotation 10 can then from the relationship

I ¹ XCXa = Pj ₁ Xb

determine, where F is the area of piston 52 and C denotes Mean release pressure of the pressure medium.

The application device according to Eig 9 can, as from 10 can be seen, particularly advantageous for clamping a brake caliper with the caliper levers 56 and 57 as well use the yoke 58: the abutment 14 of FIG with the end facing away from the brake disk 59 of the one brake lever 57 and the abutment 1 or the slack adjuster A to connect to the corresponding end of the other brake lever 56. Those in supervision after 10 superposed housings of the spring accumulator 44 and the release cylinder 45 are related on the axis of rotation 10 on the one facing away from the brake disc 59 Page.

- 14 80982B / 0309

In the arrangements according to Fig. 9 and Fig. 10, the rotation exerted when the application device is actuated is » mmment from the ring body 7 to the abutment 1 and from this transmitted through its non-rotatable guide on the abutment 14 and the carrier 43; it thus follows a closed flow of force within the application device and the brake calliper 56, 57 »58 can in the usual way attached to or hung on the vehicle.

In a modification of the embodiment described above, it is also possible, the carrier 43 not with the To connect abutment 14, but to be separately rotatable about the axis of rotation 10. When using such Application device in connection with a disc brake, it is necessary, as shown in Fig. 11, the spring store 44 near its bottom by means of a pendulum 60 articulated on both sides with the vehicle frame 61 to connect. The yoke 58 and the brake shoes which can be pressed against the brake disk 59 by the brake lever 57 62 are also fastened or mounted on the vehicle frame 61. The reaction forces of the spring accumulator 44 or the release cylinder 45 when the application device is actuated are here via the pendulum 60, the vehicle frame 61, the yoke 58 and the brake lever 56 are transmitted. Otherwise, the arrangement according to FIG. 11 corresponds to that according to Fig. 10.

- 15 -809825/0309

With the clamping devices according to Fig. 4 to Pig 11 ' changes with the rotation of the ring body 7 the effective lever length of the lever arm 19 or 42. It is possible to change the resulting change in the rotating body 7 to compensate for the effective torque by a corresponding change in the slope of the helical path sections 8, in such a way that that the application device is independent of at least in the area of the braking stroke of the friction brake the respective rotational position of the ring body 7 always emits a constant force. It is also possible by a corresponding change in the slope of the helical path sections 8, the clamping force of the decreasing with the stroke Memory spring 49 in the versions according to Pig 9 bis Fig 11 to compensate.

In all the arrangements described above, the rollers 9 are guided on a circular path around the axis of rotation 10; Since the rollers 9 have a considerable radial extension in relation to the axis of rotation 10, an exact rolling process results on the rollers only at one point, while this is superimposed on the other contact points of the rollers 9 on the spiral track sections 8 by, however, only slight sliding processes. To avoid the increased stress on rollers 9 and spiral track sections 8 caused by these sliding processes, the rollers can be designed as tapered rollers 9 ¹ according to lig 6: The outer surfaces of rollers 9 ¹ belong to cones 63 shown in dotted lines, their tips

8O982B / 0309

- 16 -

lie in the axis of rotation 10. By training the Rolls 9 as tapered rollers 9 'result over their entire ■■ Width an exact rolling on the spiral track sections 8th.

8O982B / 0309

Claims (1)

-1388- 2657355 Claims 1. -, application device for friction brakes in particular of rail vehicles, with an annular body that can be rotated via a drive element between two non-rotatable, mutually axially displaceable abutments, wherein between the ring body and at least one of the abutments arranged on coaxial spiral track sections guided on the axis of the ring body are, characterized in that the rolling bodies on which the spiral track sections (8) carry part opposing part -ring body (7) or abutment (1) - to radially to the axis of rotation (10) of the Axles running through the ring body are rotatably mounted rollers (9). 2. Application device according to claim 1, characterized in that that the rollers (9) are mounted on the ring body (7). 3 * application device according to claim 1 or 2, characterized in that the rollers (9) are arranged only between the ring body (7) and one of the abutments (1) and that the ring body via an axial roller bearing (12) against the other abutment (14 ) is supported. - 18 - 809825/0309 2657358 4. application device according to claim 3, characterized in that the abutments (1 and 14) on both sides of the Ring body (7) are guided non-rotatably against each other. 5. Application device according to claim 4, characterized in that one of the abutments (1 or 14) has a cylindrical extension (1 ¹ ) on which the annular body (7) is rotatably mounted and which in the region of the other abutment (14 or 1) is guided in a rotationally fixed manner on the other abutment by means of a radial bolt (16) engaging in an axially parallel elongated hole (15). 6. application device according to claim 5 »characterized in that that the ring body mounted on the outer circumference of the cylindrical extension (Eolbenstangen guide tube 32) (7) the other abutment (14 or 1), which is also mounted on the outer circumference, at least partially radially on the outside covered in the axial direction and that the rollers (9) in an annular space (39) between the ring body and the outer circumference are arranged. 7. application device according to claim 1, characterized in that the helical path sections (8) in the application stroke the contact area (21) corresponding to the friction brake for the rollers (9) has a large spiral slope in the fixed braking area the contact area (23) corresponding to the friction brake for the rollers has a slight helical pitch exhibit. 809825/0309 -19- 8. Application device according to A.1, dad. gek. That on the ring body (7) at least one radially projecting lever arm (19) is provided on which a drive device (25, 35) is articulated. 9. Application device according to A.8, dad. GEK. that at mi nd one of the abutments (14) a counter bearing (37) carries for the drive device (35). 10. Application device according to A.8 or 9 »dad, k., That on Ring body (7) at least approximately diametrically opposite two radially projecting lever arms (19 and 42) are arranged, on one of which there is a spring accumulator (44) and on the other of which a pressure medium can be acted upon Release cylinder (45) is hinged for the spring accumulator. 11. Application device according to A.10, dad. gek. that the articulation point (54 or 55) of the spring accumulator (44) and / or the release cylinder (45) on the lever arm (19 or 42) is adjustable in its longitudinal direction. 12. Application device according to A.10, dad. gek. that the housing (48) of the spring accumulator (44) and the release cylinder (45) are arranged next to one another, wherein their mutually parallel axes are located in a plane perpendicular to the axis of rotation (10). - 20 809825/0309 -sell 2657358 13. Application device according to claim 1, characterized in that that the lobes are designed as tapered rollers (9 ') with a cone tip lying in the axis of rotation (10) are. 809825/0309