GB2106173A

GB2106173A - Ball and socket joints

Info

Publication number: GB2106173A
Application number: GB08225749A
Authority: GB
Inventors: Alan Norman Ebbutt; Paul Frederick Lidstone
Original assignee: Automotive Products PLC
Current assignee: Automotive Products PLC
Priority date: 1981-09-22
Filing date: 1982-09-09
Publication date: 1983-04-07
Also published as: GB2106173B

Abstract

A ball and socket joint for a vehicle steering and suspension system in which the head (12) of the ball pin (13) is mounted in a bearing cup (14) in the socket (11). The bearing cup (14) is surrounded by a compressed elastomeric bush (15) that surrounds the cup in equatorial region (E-E) of the head (12) to bias the cup (14) against the head (12) to exert a torque load thereon. The torque load can be altered by changing the hardness of the elastomeric material from which the bush is made. <IMAGE>

Description

SPECIFICATION Ball and socket joints This invention relates to ball and socket joints for, but not exclusively for, use on motor vehicle steering and suspension systems.

A typical ball and socket joint has a ball pin, the head of which is mounted for rotation in a bearing cup located within a socket housing.

Such a joint is shown in British Patent 1 097 120, in which the head of the ball pin rotates in a pair of opposed bearing cups which are biased onto the spherical head by elastomeric load rings located one at each of the polar ends of the respective bearing cups. The load rings in this applications serve two functions, (a) they each load their respective bearing cups against the head of the ball pin to apply a torque load to the head, and (b) they act as seals to prevent lubricant from escaping from the joint and also prevent an ingress of dirt.

Because of the position of the loading rings and their dual function they are not able to exert either a predictable or a sufficiently high torque load on the ball joint.

Also there is provided a method of altering the torque control load exerted on the head of the ball pins by the bush by changing the hardness of the material of the elastomeric bush.

The invention will be described by way of example and with reference to the accompanying drawings in which: Fig. 1 shows in longitudinal section on one side of a centre line C,, a steering joint ball and socket assembly having a ball pin with a single shank protruding from a socket housing, and on the other side of the centre file, a torque control arm assembly having a ball pin with two shanks extending in opposite directions; Fig. 2 is an isometric drawing of a bearing cup as is used in Fig. 1; Fig. 3 shows one part of an alternative construction of bearing cup; and Fig. 4 shows a section through a resilient bush as is used in Fig. 1.

With reference to Figs. 1, 2 and 4 a ball and socket joint comprises a steel forged socket housing 11 having a cavity 10 therein in which the spherical head 12 of a ball pin 13 is housed. The head 1 2 is mounted for rotation in the socket in a bearing cup 14 which is moulded from acetal resin or nylon 6 or 66. The bearing cup 14 locates against a shoulder 18 formed in the mouth 20 of the cavity and is surrounded by a compressed resilient elastomeric bush 1 5. The bush 1 5 is shown in its unloaded state in Fig. 4. The mouth of the cavity is closed by an elastomeric boot 1 6.

On one side of the centre line C, is shown a ball pin having a single shank 25 extending from the mouth 20 of the cavity. The base of the cavity is closed by an end cover 1 7 which is swaged into position. This is a steering joint type assembly. On the other side of the centre line C, is shown a ball pin having two shanks 25 and 25A extending in opposite directions. In this case the cup 14 and bush 1 5 are held in position by a washer 21 also swaged into the base of the cavity, which is then sealed with a second boot 26. This is a typical torque control arm assembly.

The bearing cup 14 is a snap over bearing extending on both sides of the equator E-E of the head 12 of the ball pin and has an internal spherical surface for accommodating the head 12 and its external surface is also spherical and has two outwardly projecting annular flanges 31 located one at each end portion thereof. The flanges 31 each project along a line of latitude with respect to the ball and the upper flange rests against the shoulder 1 8 and the lower flange is adjacent the end cover 1 7 or washer 21. The outer peripheral edge of each of the flanges 31 is spaced away from the internal surface of the housing 11 so that in use the bearing cup is capable of limited movement towards the housing.Circumferentially spaced slots 32 extend alternately from one end of the cup and the other around the circumference of the cup, and extend to just beyond the equator of the ball. This is to make the walls of the cup 14 flexible to allow it to snap-over the head 12 of the pin.

The bearing cup is surrounded by the bush 14 that extends for substantially the length of the socket cavity 10 and is located between the flange 31 to exert a load primarily on the equatorial region E-E of the head 1 2 of the pin.

The resilient bush 1 5 (Fig. 4) is formed from a polyurethane elastomer and has an internal spherical surface 35 that accommodates the external surface of the bearing cup 14. The external surface 36 of the bush is waisted, i.e. it is generally cylindrical in shape but the diameter tapers radially inwards from each end to a minimum diameter waist 37 which is in a position equivalent to the equator of the ball pin. The external dimension of the bush 1 5 are oversize relative to the cavity in the housing 11 so that when the bush is inserted therein the bush is compressed down to have an external cylindrical shape as shown in Fig. 1. The diameter of the waist 37 is almost the same as the internal diameter of the housing cavity.The bush 1 5 is split longitudinally into two symmetrical halves along the line Y-Y to enable it to be easily assembled between the two flanges 31 of the bush 1 5, prior to the assembled bush, bearing cup and ball pin being inserted into the housing.

When the joint is assembled the compressed bush 1 5 loads the bearing cup against the head 12 of the pin. This exerts a controlled predetermined torque load on the head of the pin to vibrations in the steering system and to give the driver the correct 'feel'.

As an alternative to the one piece bearing cup shown in Fig. 2, they can be formed from two identical parts 40, one of which is shown in Fig. 4, which are split equatorially relative to the ball.

Each half of the bearing cup has projections 41 thereon that overlie the equator of the ball and interengage with like recesses 42 on the other half of the bearing cup so that when the two parts are assembled together the projections 41 are interdigitated and each projection overlies the equator of the ball.

The torque load exerted by the bush 1 5 on the head 12 of the ball pin can be varied by using different grades of polyurethane elastomer having different hardness characteristics.

Claims

1. A ball and socket joint in which the head of the ball pin is mounted for rotation in a bearing cup whose external surface is in contact with a compressed resilient annular member located within a cavity in the socket housing and which biases the bearing cup against the head of the pin, wherein the resilient member is an elastomeric bush that surrounds the equatorial region of the head of the ball pin on both sides of the equator and extends for substantially the length of the cavity in the socket to exert and overall load on the head.

2. A joint as claimed in Claim 1 , wherein the resilient bush before insertion into the housing is of the form of a waisted cylinder and has an external surface such that the external diameter of the bush gradually tapers radially inwards from the ends thereof towards a minimum diameter waist adjacent the equator of the ball.

3. A joint as claimed in Claim 2, wherein the diameter of the waist is substantially equal to the internal diameter of the cavity in the housing.

4. A joint as claimed in any preceding claim, wherein the bearing cup has an outwardly projecting flange at each end portion thereof to limit radially outward movement of the bearing cup in the cavity.

5. A joint as claimed in Claim 4, wherein the flanges each project along a line of latitude with respect to the head of the ball pin.

6. A joint as claimed in Claim 5 or claim 6, wherein the compressed bush extends along the length of the cavity between the two flanges.

7. A joint as claimed in any one of Claims 1 to 6, wherein the bearing cup is a one piece cup having circumferentially spaced slots therein extending alternately from one end of the cup and the other, and each slot extends to overlie the equator of the head of the pin.

8. A joint as claimed in any one of Claims 1 to 6, wherein the bearing cup is divided into two parts around the equatorial region of the head and said two parts are interdigitated by respective portions that overlie the equator.

9. A ball and socket joint substantially as described herein with reference to Figs. 1, 2 and 4 of the accompanying drawings or substantially as described with reference to Figs. 1, 2 and 4 and modified as described with reference to Fig. 3 of the accompanying drawings.

1 0. A method of altering the torque load exerted on the head of a ball pin in a joint as claimed in any preceding claim, wherein the torque control is altered by changing the hardness of the material of the elastomeric bush.