JPS60104821A - Hydraulically operated cylinder assembly for car brake - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic cylinder assembly for use in a type of vehicle brake in which a piston operating within a bore of a clamp is movable within the bore in response to hydraulic pressure generated during brake application. Concerning solids.

Hydraulic cylinders of the type described herein may incorporate or be associated with a slack adjuster that determines the retracted position of the piston in the retracted and brake-off position to determine the brake clearance. The problem is arranging the slack adjuster so that it does not react to the deflection of the brake element when the brakes are applied. Otherwise, the slack adjuster would tend to "over-adjust" and excessive brake clearance would have to be provided to compensate for such "over-adjustment."

According to the invention, the invention extends to a hydraulically actuated tube of the type described herein incorporating an assembly acting as a strut for determining the retracted position of the piston, said assembly comprising: a first clamp that moves with the piston; including a parting and a regulator member;
d cooperating with the clamping member to form a releasable pawl in conjunction with a resilient device which normally acts between the piston and the clamping member to bias the engaging parts into engagement; When the hub member moves in the axial direction relative to the piston in the outer brake application direction in response to the brake application hydraulic pressure in the hole cavity, the engagement of the engaging parts is weakened. The constructed and arranged retaining ramps are adapted to cause the adjuster members to cooperate when movement of the piston portion adjuster member in the direction of brake application exceeds a distance sufficient to eliminate the braking gap. A load stop is provided within the bore so that additional movement of the clamp member in the same direction causes the clamp member to move axially relative to the adjuster member, increasing the effective length of the strut and braking. The screw when changing the pressure by 1! - defines an adjusted retracted position for the tooth IE, and the tooth IE is released against the false force until the engagement force of the retaining part exceeds the force of the spring-loaded clasp at a predetermined point; , at which point the pawl re-engages and prevents further relative axial movement between the two members, after which further movement of the strut in conjunction with the piston is prevented by the pawl resisting the spring load. It has come to be covered by movement.

The predetermined point is the point at which the brake is fully applied, after which the brake element begins to deflect.

The present regulator adjusts only as a result of excessive piston movement due to brake lining wear and does not respond to excessive piston movement due to brake element deflection after full braking has been applied. The regulator can be said to be load insensitive.

The clamping member is housed within the bore within the piston and includes a piston portion operable within the bore and a plurality of angularly spaced integral resilient fingers extending toward an open end of the bore. It carries at its free end a pawl that engages axially spaced teeth on the regulator member, both of which are provided with ramps that engage ramps on the piston.

When the actuating barrel has a pair of opposed-acting pistons operating within the bore of the housing, a spring load stop is received within the bore of the second piston into which the regulator member protrudes and adjusts. A head is supported on the free end of the instrument member, the outer end of which defines a stop for engaging a surface at the inner end of the bore cavity to determine the relative retraction position # of the two pistons; The inner end of the section is adapted to abut a spring loaded catch.

The spring-loaded catch has a compression spring that is held in a partially compressed restraint by a cage, and a radial flange at the inner end of the cage that has a V? : The entire contact part that engages with the head of the paulownia regulator part is formed.

Some embodiments of the present invention will be described below with reference to the accompanying drawings.

The brake illustrated in FIGS. 1 and 2 is of the conventional extended type, in which a rotatable grinding disc 1 with a grinding lining is mounted on the Igl of the disc 1 and fixed pylons +-s.
, 6 , 7 a pressure plate 3, centrally positioned by .
4 for engaging oppositely spaced radial surfaces within the housing 2. on the adjacent side of the pressure plate 6.4,
The spheres are contained in cooperating, counter-sloping depressions.

The application of the brake is initiated by moving the pressure plates 6.4 in all angular opposite directions, the forward direction of the sphere climbing the slope defined by the end faces of the recess, causing the pressure plates to move relatively away from each other. is moved axially. This forces the grinding circle 1 to engage the surface of the housing 2. The pressure plate 6.4 then rotates with the disk until one is locked in engagement with the lug 8.9 on each of the bands 6.4, after which continued angular movement of the other band is prevented. Provides servo action.

For parking or in case of an emergency, a pair of toggle links 12 extending through the radial opening 11'fc1 of the housing 2 and pivotally connected at their inner ends to the respective pressure plate 6.4. The brake is applied mechanically by a tension rod 10 connected to the outer end of the .13.

In normal road braking, the brakes are applied hydraulically by a hydraulic cylinder 15 acting between lugs 16 and 17 on the pressure plate. The lug 16 . 17 is angularly spaced from the toggle link 12 . 13 and the actuating barrel is accessible from a second radial opening 18 in the housing 2 which is closed by a removable plate 19 .

The actuating barrel 15 includes a cylinder 20f with an axial through-bore cavity 21 open at both ends, in which a pair of pistons 22 act in opposite directions to engage the lugs 16.17.
．． 23 works.

Each piston 22, 23 carries a seal 24 near the adjacent outer end of the cylinder 2o and supports a seal 25 near the inner end. A pressure space 26 defined within the bore 21 between adjacent inner ends of the pistons 22, 23 is connected to the main working cylinder by a straight passage 27 in the housing that can be accessed from the outside of the housing 2.

The automatic slack adjuster assembly 30rr1 is housed within the design shaft 15 and is housed in axially opposing bores, 51.32, with pistons 22, 231C, respectively.

The regulator assembly includes a clamp member 6 housed within the bore 61.
6 and a piston portion 34 operating within the bore cavity 6 .
Clamping member 63 has a plurality of axially extending resilient fingers projecting from the open end of 1 to support a forming portion 65, the outer edge of forming portion 65 being sloped to form a complementary sloped surface 37 on piston 22. The inner edge has a pawl 66. A regulator member 68 extends vc through the clamp member 33 into the bore 62 and includes a plurality of axially spaced teeth 39.
The pawl 66 engages with the teeth 69 by the elasticity of the gene ring 40 supported by the piston 22. The free end of the regulator member 68 is connected to the enlarged head 4
1 and the outer end of the head engages the inner end of the bore 32 to limit separation between the inner ends of the pistons 22,23. Thus, the clamp member 66 and the regulator member 6
8 acts as a support post that determines the retracted position in the brake release position @VC and thereby determines the braking clearance.

The spring load L catch 42 is housed in the bore 62. The catch is a restrained compression spring whose ends abut between the circular clip 44 in the bore 62 and the flange 45 at the inner end of the cylindrical cage 46. 43 and a flange 47 at the opposite end of the cylindrical cage.
engages circular crimp 44. Typically, the abutment surface 48 defined by the inner end of the head 41 is spaced from the flange 45 by a distance corresponding to the braking gap and the piston 22.2.
3 is held in the retracted position by the return of pressure plates 6, 4 and springs.

When the brake is applied hydraulically, the high pressure fluid in the pressure space 26 urges the pistons 22, 23 in the opposite direction,
As previously described, the lugs 16,17 are biased relatively away from each other.

During this movement of the piston 22, 2'3, the head 41 moves relative to the flange 45 as the braking gap is removed and the brake is fully applied and pressure is also transferred onto the piston part 64. When the forming portion 65 is urged in the axial direction, the head 41 contacts the flange 45. Due to the wedging action, the gripping force of the pawl defined by the engagement of pawl 66 and tooth 69 is then increased. If the movement of the head 41 relative to the flange 45 is excessive when the actuating barrel is actuated, indicating that adjustment for lining wear is necessary, then the adjuster member 68 moves against the elasticity of the ring 40. It is pulled out from the clamp member 66 to increase the effective length of the strut by a certain amount. This action continues until the pawl due to the pressure on the clamping member 66 exceeds the force of the spring 46, after which it is met by the further contraction of the pistons 22 and 26. It will be done.

The point at which the second tooth is fixed and prevents further elongation of the strut, before the brake is fully applied and the force generated by the braking pressure is absorbed to cause deflection of the brake arm. Toshi-C is selected.

When the brake is released, the pistons 22,23 return to their inactive retracted art, and the inner ends of both pistons are separated by a greater distance determined by the extended length of the strut.

- In order to restore the full initial position l1i7 of the vertically extending strut, the teeth 69 are separated by angularly spaced axial recesses, and the piston 22°23ff: is moved angularly by the appropriate amount. This allows the pawl 66 to fit into the recess, after which the clamping element 63 and the adjuster element 68 can be moved towards each other without resistance.

In an alternative embodiment, the pawls and teeth could be replaced by a male-female threaded formation.

The actuation knob and regulator assembly described above can be used in a drum type brake. For example, it can be used with two leading shoes, or one trailing shoe, or with a 7" rake of the duo-servo type. When the brake is a duo-servo type or operates as a duo-servo type in one mode, when the brake is applied, the first
The support is strong enough to transmit the thrust from the next knee to the second knee.

As shown in FIG. 6, the actuating barrel and regulator assembly is incorporated into the shoe drum brake of the tank. The cylinder 20 is attached to a brake backing plate or torque plate between adjacent shoe ends 50.51 and is connected to a piston 22.23.
The outer end of extends outwardly to form a boss 52.53v.

Notches 54,55 are provided at the outer ends of the bosses 52,53 to receive respective shoe ends 50,51.

Seals 25 are present in close proximity to the inner ends of the two pistons 22, 23, and the 7-rules 24 are omitted. Annular sealing boots 26, 27 are provided at both ends of the cylinder 2B, the inner and outer thickenings or beads of each boot being connected to the boss 5.
2,53 trigrams and are received in respective radial grooves 56, 5'7 at the adjacent ends of the segments 20.

The construction and operation of the actuating tube and regulator are essentially the same as those described above with reference to FIGS. 1 and 2, and corresponding parts have been given corresponding reference numbers. There is.

The old operating cylinder/adjuster assembly is used for vehicle disc brakes,
In particular, it can also be used for actuating cylinders used in disc brakes of the sliding side caliper type. This type of disc brake includes an axially movable clamping member, such as a polishing pan and yoke, within a fixed housing for applying a second polishing pad to an opposing surface of the disc. There are opposing pistons in between.

In another configuration, shown in FIG. 4, the actuating barrel and regulator assembly is incorporated into a side-to-side axially movable caliper disc brake.

The brake has a fixed drag bearing 4f3 +J of a generally mouth-shaped profile (not shown) spanning a rotatable fixed circumference. Opposed abrasive band assemblies that engage both sides of the disc are mounted within the drag-bearing member and approach or exit the drag-bearing disc guide surface on the band assembly when the brake is applied. The band assembly is guided away.

Caliper 6O with opposing prongs 61,622
Ifi Ensaka and the polishing pad m are the same size and are guided to slide in the moving direction on the drag bearing member on circumferentially spaced guide surfaces which can be constituted by guide pins. be done.

The actuating tube/regulator assembly has an axial bore 6 with a stepped shape.
6.

The piston 22 is adapted to operate within the inner portion 64 of the larger diameter bore 66, the piston 26 being omitted, and the bore 62 consisting of the outer portion 651 of the smaller diameter bore 63. The head 41 is attached to a seal 66 at the mouth of the hole 6b.
The outer end of the head 41 is provided with a circular/shaded recess 67, which receives the entire end of the locking dolly or column 6B, and the column 680, etc.
;11■, Accepted in notch 69 of Bregi j commercial 1 draw 7o. 11!1II70 rotates in the bunon 71 inserted into the lateral hole cavity 72 of the prong 62
] It is accepted.

The piston 22 seals the seal 72 in the wall of the bore portion 64.
A resilient sealing boot, similar to sliding boot 26, can also be connected between the vist 722 and the retaining groove 76 at the inner end of the bore 65.

The construction and operation of the actuating node/regulator are otherwise the same as those described with reference to the first centroid and FIG. 2, and corresponding parts have been given corresponding reference numbers. There is.

[Brief explanation of the drawing]

Fig. 1 is an end view of the expandable brake, Fig. 2 is an enlarged scale WL sectional view of the hydraulic joint assembly used in the brake of Fig. 1, and Fig. 6 is an internal section similar to Fig. 2. FIG. 4 is a longitudinal cross-sectional view of a disc brake for a vehicle. 15... Working cylinder 2o... Housing 22.23.
... screws) ~ 31, 32 threaded hole cavity 63... clamp member 34... piston part 65... different surface around 1 6
6...Claw 67...#4 connection 68...Adjuster part 39...Teeth 4o...Elasticity 41...Head 46゛°Spring 45...Flange 46...Cage 48 ...Contact part.

Claims (1)

[Claims] 11) The piston 22 is 7 and the hole 61 in the puffer fish 20
The piston 22 is movable within the bore 61 in response to hydraulic pressure acting therein to generate a brake application force, and is movable within the bore 61 in the retracted position 1 of the piston 22.
Ifk, the entire assembly serving as the strut 33,38 incorporates a hydraulically actuated barrel assembly, said assembly including a first clamping member 66 movable with the piston 22 and a regulator portion 68. and the core members have (1) releasable teeth in cooperation with an elastic device 40 which includes interengaging parts and normally serves to bias and bring the interengaging parts into engagement. said interengaging parts so as to form (-1 mutually cooperating and clamping portions in an outward braking application direction in response to braking application hydraulic pressure within borehole 51) 1';
When A63 moves in the axial direction relative to the piston 22, the structure and arrangement (a
The piston 22 and the clamping member 63 are provided with interengaging inclined surfaces 37, 35, and the bore 6
A spring-loaded IE clasp 42 is provided within the spring loader 1 so that when the movement of the regulator member 68 in the direction of applying the brake exceeds a distance of a light minute to remove the 1ltlJ movement gap [the regulator member 68 is Further movement of the clamping member 66 in said direction causes the clamping member to move axially relative to the regulator member 38, thereby increasing the effectiveness of the strut 33.38. The length of the piston 22 is increased to define a finely adjusted retracted position of the piston 22 when the brake gear pressure is released, and the spring load weight 42 is moved at a predetermined point where the engagement force of the mutually engaging parts is achieved. The pawl is released against the force of the elastic response ii until the force exceeds the predetermined 0
At points Q, J, said pawls re-engage to prevent further relative axial movement of said pistons 22 and H [1 of said mated struts 6 , 68, further movement thereof is covered by movement of said upper cap 42 against a spring load 46. (2) The clamping member 66 is accommodated in the bore 61 of the piston 22, and the piston portion 64 operates within the bore 61 and protrudes toward the open end of the bore 61 to adjust the free end. Clamping member 66 includes a single piece of double angularly spaced resilient fingers supporting pawls 66 that engage axially spaced teeth 69 on member 68. ,
The actuating cylinder assembly according to claim 11, wherein both of the pawls 66 are provided with an inclined surface 65 that engages with the inclined surface 37 on the piston 22. (3) The clamp member 36 includes a piston portion 64 that fits within the bore 61 in the piston 22 and operates within the bore 31, and the clamp member 36 includes the ramp member 66 and the adjustment member 68. A patent claim characterized in that a ridge-shaped acid portion is provided in between, and the piston portion 64 is provided with a sloped groove 5 around 1 which engages with the sloped surface 67 of the piston 22. The actuating cylinder assembly according to item (1). (4) having a pair of counter-acting pistons 22.25 operating within the bore 21 of the housing 20, said spring loaded catch 42 being received within the bore 62 of the second piston 26; 62 into which the adjuster member 68 projects, the free end of the adjuster member 68 supports a head 41, the outer end of which supports a surface at the inner end of the bore 62. engaging with said 2
a stop can be defined for determining the relative retracted position of the two pistons 22, 26, and the inner end of said head 41 is adapted to abut against said spring load stop 42. The actuating cylinder assembly according to claim f''4.
A radial flange 45 at the inner end of the cage 46 engages the head 41 of the regulator member 68 when the actuating barrel is actuated, with a compression spring 46 held in a restrained state for an amount of time. 4. The actuating cylinder assembly according to claim 4, wherein the entire abutting portion 48 is formed.