GB2075623A

GB2075623A - Disc brakes

Info

Publication number: GB2075623A
Application number: GB8113466A
Authority: GB
Original assignee: Lucas Industries Ltd
Current assignee: ZF International UK Ltd
Priority date: 1980-05-09
Filing date: 1981-05-01
Publication date: 1981-11-18
Also published as: GB2075623B

Abstract

A housing (2) for a disc brake incorporates an expander mechanism (6) whereof plate (9) is formed by separate inner and outer concentric rings (10, 11); in normal braking, an annular piston (16) works in an annular hydraulic cylinder (17) to urge one ring (e.g. 10) into engagement with a friction disc (5). The brake can also be applied mechanically by moving the other ring (e.g. 11) angularly with respect to the plate (8) causing balls (14) to ride out of inclined recesses (15) in adjacent faces of the ring (11) and plate (8). In this manner of operation a servo effect is obtained and helical movement of the annular piston (16) is eliminated. As shown, piston (16) also moves plate (8) of the expander mechanism (16) to act on a single disc (5) - ring (10) acts on a disc stack; plate (8) could alternatively be fast with housing (2). Each of the discs (5) in the stack has concentric rings (26, 27) of lining material carried on a plate (25) - in Fig. 4 the discs are formed from relatively axially movable rings. In Fig. 1 mechanical operation is by a transmission member (23) and an additional hydraulic piston-cylinder assembly (20) is provided. Modifications of such operation are disclosed (see eg Fig. 5). <IMAGE>

Description

SPECIFICATION Improvements in disc brakes This invention relates to disc brakes of the kind in which at least one rotatable friction disc is adapted to co-operate with a radial surface in a stationary housing by means of actuating means within the housing and the actuating means incorporates at least one pressure plate adapted to be subjected to an axial component of brake-applying movement so that the pressure plate can engage with a friction lining on the friction disc to urge it into co-operation with the radial surface.

In some known brakes of the kind set forth balls are located in co-operating oppositely inclined recesses in the pressure plate and in another complementary member and the application of the brake can be initiated either by moving the pressure plate angularly, or by moving it axially. In each case, upon engagement of the pressure plate with the friction disc, the pressure plate will be carried round with the friction disc to produce a servo action causing the balls to tend to ride out of the recesses and enhance the axial component of the brake-applying movement.

The angular movement of the pressure plate can be effected by a lever or link acting on a lug on the pressure plate, suitably for mechanical operation for parking or emergency braking, and the axial movement of the pressure plate can be effected, suitably for service braking, by an annular hydraulic piston and cylinder assembly which is incorporated in an assembly defined by the pressure plate and the said complementary member.

In such a known construction angular movement of the pressure plate can cause the piston to perform a helical movement in the cylinder, which is likely to cause damage to the seals, with the inherant problem of air being sucked into the cylinder upon release of the brake. Helical movement of the piston can be eliminated by providing a bearing between the piston and cylinder assembly and the pressure plate. This is undesirable since the bearing would have to be of substantial diameter and therefore very expensive. In addition it is also desirable to ensure that, irrespective of whether the brake is being applied for parking or emergency braking, or for normal service braking, differing parts of the brake co-operate. This will ensure that fade in one of the two brake-applying modes will not effect operation of the brake when applied in the other of the two modes.

Brakes of the kind described above are commonly used on tractors and like vehicles.

According to our invention in a disc brake of the kind set forth the pressure plate comprises separate inner and outer concentric rings for engagement with complementary inner and outer regions of the friction lining, an hydraulic annular piston and cylinder assembly acts directly on one of the rings to urge it axially into engagement with the disc, and balls are located in complementary oppositely inclined recesses in the other ring and in a complementary member so that upon relative angular movement therebetween the said other ring also moves axially due to the camming effect of the balls, the hydraulic piston and cylinder assembly being operated from a supply of hydraulic fluid, and the said other ring being movable angularly independently of the said one ring for parking or emergency braking by mechanically operable means.

This provides a servo effect for parking or emergency braking and, for normal service braking, can eliminate helical movement of the annular piston, conveniently by slidably coupling the said one ring and the cylinder against relative angular movement. This also provides different regions of the lining material for the different braking modes so that fade of the one does not effect the other.

In addition an hydraulic actuator may be incorporated to act on the said other ring in a direction to urge it angularly. This achieves a servo effect to produce a higher torque output when the brake is operated hydraulically, suitably for use in assisting the vehicle to achieve a "spin-turn" to facilitate steering.

Preferably the annular piston and cylinder assembly acts on the inner concentric ring, and the outer concentric ring has a radial lug on which the hydraulic actuator acts, either directly, or through a suitable linkage, the mechanically operable means also acting on the lug directly or through the linkage.

The radial lug may engage with an adjustable stop on the housing by means of which the angular retracted position of the outer concentric ring can be adjusted to compensate for wear of the friction linings. This then acts as a back-stop for the friction disc and determines the extent by which the outer concentric ring will move back in a retracted direction when the brake is released.

Uneven wear of the two regions of lining material is resisted by the inherent stiffness of the material of the plate carrying the lining material and, in any case, drag-wear may tend to even out the wear throughout the wear life of a friction disc. However, in the event of uneven wear becoming significant, the two concentric regions of lining material can be provided on two separate inner and outer friction rings which are splined together at adjacent edges to permit relative axial movement of the friction rings to take place.

Our brake can be "dry" or it can be of the "oil-immersed" type. In the former case a relatively small number of friction discs are incorporated so that uneven wear will not effect the brake significantly. Any uneven wear is likely only to effect the side of a disc which is remote from the actuating means. In the latter case, in which a plurality of friction discs are incorporated in a stack, lining wear takes place at an insignificant rate and therefore uneven wear is less of a problem. How ever any uneven wear will normally take place on the disc adjacent to the actuator, which may be splined as described above.

Two embodiments of our invention are illustrated in the accompanying drawings in which: Figure 1 is a plan of a disc brake; Figure 2 is a section on the line 2-2 of Fig.

1; Figure 3 is a plan of a friction disc incorporated in the brake of Figs. 1 and 2; Figure 4 is a plan similar to Fig. 3 but showing a modification; and Figure 5 is a view similar to Fig. 1 of a modified brake.

The disc brake illustrated in Figs. 1-4 of the accompanying drawings is adapted for braking a shaft 1 for transmitting drive to a wheel of a vehicle. The brake comprises a housing 2 into which the shaft 1 extends, the housing having at opposite ends radial brak ing surfaces 3, 4 between which are located rotatable friction discs 5. The discs 5 are slidably keyed to the shaft 1.

An expander mechanism 6 is located betwen a single one of the discs 5, and the remainder of the discs 5 which are disposed in a stack with relatively stationary friction discs 7 disposed between adjacent pairs of discs 5 in the stack. The mechanism comprises two relatively angularly movable pressure plates 8, 9 of annular outline with the plate 8 comprising a single member, and the plate 9 comprising separate inner and outer concentric rings 10, 11. The plate 8 and the outer ring 11 are centred on angularly spaced pilots 1 2 in the housing, the inner ring 10 is keyed to the plate 8 for relative axial movement by means of angularly spaced guide pins 13, and the plate 8 is guided against rotation by the engagement of lugs 28 with a pin 29 which acts as a stop abutment and also comprises one of the pilots.Balls 14 are located in oppositely inclined co-operating recesses 1 5 in adjacent faces of the plate 8 and the outer ring 11. An annular piston 1 6 working in an annular hydraulic cylinder 1 7 in the plate 8 acts on the inner ring 10, and hydraulic fluid can be admitted to the cylinder 1 7 through a passage 1 9 in the plate 8.

Helical return springs 1 8 act between the plate 8 and the ring 11 to urge these components towards each other.

An hydraulic piston and cylinder assembly 20 acts at opposite ends between complementary lugs 21, 22 on the plate 8 and on the ring 11 respectively. A transmission member 23 for applying the brake mechanically is coupled to the lug 22 through a lost-motion connection 24.

Each of the friction discs 5 in the stack comprises a metal plate 25 carrying on oppQ- site sides two separate concentric inner and outer rings 26, 27 of lining material which may have different co-efficients of friction and which are substantially superimposed upon the adjacent faces of the rings 10 and 11 which comprise the pressure plate 9.

When the brake is to be applied for normal service braking hydraulic fluid under pressure is supplied to the cylinder 1 7. The piston 1 6 urges the pressure plate 8 and the ring 10 relatively away from each other in an axial direction so that the discs 5 in the stack are urged together, and into engagement with the radial surface 3, and the other remaining disc 5 is urged into engagement with the radial surface 4. No servo-effect occurs since the plate 8 is held against rotation by the pin 29.

Braking is initiated by the engagement of the ring 10 with the ring 26 of lining material.

When the brake is to be applied mechanically, in an emergency or for parking, the transmission member,23 is operative to move the ring 11 angularly with respect to the pressure plate 8 and the balls 14 tend to ride out of the recesses 1 5 to urge the plate 8 and the ring 11 axially apart. This urges the discs 5 in the stack together, and into engagement with the radial surface 3, and the other remaining disc 5 is urged into engagement with the radial surface 4. In this mode of operation, brake application is initiated by the engagement of the ring 11 with the ring 27 of lining material.

When the discs 5 are rotating in a normal forward direction the ring 11 is carried round with the discs 5 to provide a servo action to intensify the braking force.

Should the discs 5 be rotating in the opposite direction when the brake is applied, any angular movement of the outer ring 11 will be arrested by the engagement of the lug 22 with a stop abutment comprising a bolt 30 which is adjustably screwed into the housing 2 through a tapped opening, and any servo effect will be limited by the extent to which the plate 8 can move angularly, which is determined by any clearance between the pin 29 and a respective lug 28. Normally, therefore, no servo effect will occur when the brake is applied mechanically, with the friction discs 5 rotation in an opposite, reverse, direction.

To produce a higher torque output hydraulic ally in order to assist the vehicle achieve a "spin-turn", the hydraulic piston and cylinder assembly 20 is operated to urge the lug 22 relatively away from the lug 21, in consequence moving the ring 11 angularly to apply the brake in the same manner as that described above in connection with the mechanical operation.

Again a servo effect will normally be provided only when the vehicle is travelling with the wheels and the friction discs 5 rotating in a normal forward direction.

Both the cylinder 1 7 and the piston and cylinder assembly 20 may be operated simultaneously so that the servo effect can augment the normal service braking effect. In such a case both rings 10 and 11 engage with their respective rings 26 and 27 of lining material.

The bolt 30 is adjustable to compensate for wear of the friction linings 26 and 27 and acts as a back-stop for the friction discs 5 by determining the extent by which the outer concentric ring 11 can move back in a retracted direction under the influence of the springs 18, when the brake is released.

Uneven wear of the two rings 26, 27 of lining material is resisted by the inherent stiffness of the metal plates 25 and, in any case, drag-wear may tend to even out the wear throughout the wear life of the discs 5 and 7.

The disc brake described above may be of the "oil-immersed" type in which case wear of the linings is minimal. However, in the event of the brake being of the "dry" type in which lining wear, and hence uneven wear, could become more significant, as shown in Fig. 4 the discs 5 may be constructed from two separate inner and outer concentric metal rings 31, 32, each carrying a corresponding ring 26, 27 respectively, of lining material, with the metal rings 31 and 32 being splined together for relative axial movement as shown at 33. In such a construction relative wear of the rings 26, 27 can take place. It is only necessary for the friction disc 5 with which the plate 9 engages directly to be splined and, when the brake is of the "dry-type" such a single friction disc 5 may replace all the friction discs 5 and 7 in the stack.

In the brake described above the transmission member 23, or a similar member, may se coupled to adjacent ends of a pair of toggle links of which the outer ends are coupled to the lugs 22 and 22. In such a construction the member 23 projects from the housing 22 in a radial direction.

In the modified brake illustrated in Fig. 5 the piston and cylinder assembly 20 is omitted and the position of the two lugs 21 and 22 is reversed. The lugs 21 and 22 are coupled to the outer ends of a pair of toggle links 31, 32 of which the inner ends are coupled to a rod 33 provided at its outer end with a part-spherical thrust member 34.

An hydraulic piston 35 of stepped outline working in a cylinder 36 can act at its outer end on the thrust member 34 for service braking, and the rod 33 can be withdrawn through the piston 35 for parking or emergency braking.

When the brake is applied to facilitate a "spin-turn" the cylinder 36 is pressurised so that the plates 8 and 9 are separated axially as described above with relative angular movement being imparted to the plates by the toggle links 31, 32. Similarly, for emergency or parking braking, the brake is applied only by relative angular movement between the plate 8 and the ring 11.

The construction and operation of the brake of Fig. 5 is otherwise the same as that of Figs.

1-4 and corresponding reference numerais have been applied to corresponding parts.

In the brakes described above, keying the pressure plate 8 against angular movement with respect to the housing 2 has the advantage that normal hydraulic pipes can be used to supply fluid to the cylinder 17, rather than flexible hoses which are less satisfactory and would be required if the pressure plate 8 was adapted to move angularly. Also the recesses 1 5 are double ended to provide a servo effect for both direction of disc rotation, as permitted by the arrangement of the pressure plates 8 and 9 which will depend upon whether the brake is to be used with a wheel on a near side or an off side of a vehicle.

In a modification of the brakes described above the friction disc 5 between the expander mechanism 6 and the face 4 can be omitted. In such a construction the pressure plate 8 can be fast with the housing 2 itself or constituted by an end wall of the housing 2 itself.

In another modification the position of the rings 10 and 11 constituting the pressure plate 9 can be reversed so that the piston 1 6 is housed in the then outer rings, and the recesses 1 5 are located in the then inner ring.

Claims

1. A disc brake of the kind set forth in which the pressure plate comprises separate inner and outer concentric rings for engagement with complementary inner and outer regions of the friction lining, an hydraulic annular piston and cylinder assembly acts directly on one of the rings to urge it axially into engagement with the disc, and balls are located in complementary oppositely inclined recesses in the other ring and in a complementary member so that upon relative angular movement therebetween the said other ring also moves axially due to the camming effect of the balls, the hydraulic piston and cylinder assembly being operated from a supply of hydraulic fluid, and the said other ring being movable angularly independently of the said one ring for parking or emergency braking by mechanically operable means.

2. A disc brake as claimed in Claim 1, in which the said one ring and the cylinder of the piston and cylinder assembly are slidably coupled against relative angular movement.

3. A disc brake as claimed in Claim 1 or Claim 2, in which the complementary member comprises another pressure plate and the piston of the piston and cylinder assembly works in an hydraulic cylinder in the said other pressure plate axially apart into engagement with respective friction discs.

4. A disc brake as claimed in Claim 3, in which the said other pressure plate is keyed to the said one ring for relative axial movement by angularly spaced guide pins and is guided against rotation by the engagement of lugs on the said other plate with a stop abutment in the housing.

5. A disc brake as claimed in any preceding claim in which an hydraulic actuator is also incorporated and acts on the said other ring in a direction to urge it angularly relative to the complementary member.

6. A disc brake as claimed in any preceding claim in which the annular piston and cylinder assembly acts on the inner concentric ring and the mechanically operable means acts on a radial lug provided on the outer concentric ring.

7. A disc brake as claimed in Claim 6 as appended to Claim 5, in which the hydraulic actuator also acts on the radial lug on the outer concentric ring

8. A disc brake as claimed in Claim 7, in which the hydraulic actuator and/or the mechanically operable means act directly on the radial lug.

9. A disc brake as claimed in Claim 7, in which a complementary radial lug is provided on the complementary member and a toggle linkage is coupled to the radial lugs, the hydraulic actuator and the mechanically operable means both acting through the linkage to cause the other concentric ring to move angularly relative to the complementary member.

10. A disc brake as claimed in any one of the Claims 6 to 9, in which the radial lug is engageable with an adjustable stop on the housing, the angular retracted position of the outer concentric ring being adjustable by means of the stop to compensate for wear of the friction lining.

11. A disc brake as claimed in any preceding claim in which the friction disc comprises a single plate which carries separate inner and outer concentric rings of friction lining material.

1 2. A disc brake as claimed in any one of the Claims 1 to 10, in which the friction disc comprises separate inner and outer concentric friction rings which are splined together at adjacent edges for relative axial movement, each friction ring carrying a corresponding ring of friction lining material.

1 3. A disc brake as claimed in any one of the Claims 1 to 10 in which a plurality of rotatable friction discs incorporated into a stack are disposed between the pressure plate and the corresponding radial surface, a relatively stationary friction disc being disposed between each adjacent pair of rotatable friction discs in the stack, and each friction disc comprising a metal plate which carries on opposite sides two separate concentric inner and outer rings of friction lining material.

14. A disc brake as claimed in Claim 1 3, in which the rotatable friction disc in the stack which is adjacent to the pressure plate comprises separate inner and outer concentric friction rings which are splined together for relative axial movement, each friction ring carrying a corresponding ring of friction lining material.

1 5. A disc brake as claimed in any one of the preceding Claims 11 to 14, in which the separate concentric rings of lining material have different co-efficients of friction.

16. A disc brake substantially as herein described with reference to and as illustrated in Figs. 1 to 3 of the acicompanying drawings.

1 7. A disc brake as claimed in Claim 1 g, but modified substantially as herein described with reference to and as illustrated in Fig. 4 of the accompanying drawings.

18. A disc brake as claimed in Claim 1 5 or Claim 16, but modified substantially as herein described with reference to and as illustrated in Fig. 5 of the accompanying drawings.