JPS6317855Y2 - - Google Patents

Description

[Detailed description of the invention] This invention is a steering linkage for automobiles, etc.
It is used for suspensions, etc., and is intended to stabilize the operating torque of ball studs in particular.
The dimensional error of the component parts is absorbed by the change in the volume of the bearing, and the change in the volume of the bearing is further absorbed by the recess provided in the inclined surface of the ball joint socket. Further, since a reaction force in the bending direction of the slope portion of the bearing positioned opposite to the recessed portion is obtained, a resilient force higher than the resilient force possessed by the bearing material is obtained, and a stable operating resistance is obtained for the ball stud. Furthermore, since the bottom of the ball stud of the ball stud is pressed, even if the stud ball wears out, it always follows suit and maintains an appropriate operating torque for the ball stud.

As shown in FIG. 1, the ball joint that has been commonly used in the past consists of the ball part 2 of the ball stud 1,
A bearing 4 is press-fitted between the ball joint sockets 3, but since the bearing 4 is made of a highly wear-resistant plastic material, the bearing 4 is a so-called low-elasticity member that is not easily deformed by the assembly load. , the change in elastic force is large for small dimensional errors in component accuracy. Therefore, unless the dimensional accuracy of the bearing and press-fit parts is improved, the elastic force generated by deformation of the bearing after assembly will vary greatly, the operating torque of the ball stud will vary, and it will be difficult to obtain an appropriate operating torque. . In addition, when the ball joint is assembled, the pressing force of the plate 5 can be adjusted and the assembly can be performed by caulking 6, but this is not perfect.

The device of the present invention not only allows for pressure adjustment and caulking assembly of the plate, but also provides a downward portion for absorbing dimensional errors of component parts by providing a recess in the inclined surface of the bearing fitting portion of the socket.
It is possible to stabilize the operating torque of the ball stud.

Figure 2 shows an embodiment of the present invention, in which 1 is a ball stud, 2 is a ball part, 3 is a socket, 4 is a bearing, 5 is a plate, 6 is a caulking part, and 7 is a bearing fitting part. The component structure is the same as that of the conventionally known one.

8 is a recess provided in the inclined surface between the cylindrical surface and the bottom of the bearing fitting part of the socket 3, and the recess 8 has a square cross section as shown in FIG. 3 or a round cross section as shown in FIG. They are appropriately selected and arranged in a dotted, band-like, ring-like, etc. manner. The sloped surface of the bearing protrudes into the recess 8 by the dimensional error of not only the bearing portion facing the recess 8 but also the component parts, which prevents the operating torque of the ball stud from becoming too high, and thereby prevents the operation torque of the ball stud from becoming too high. It will exhibit higher explosive power.

Next, the operation of the present invention will be explained with reference to the graph shown in FIG.

Figure 5 shows the operating torque of the ball stud with respect to the bearing press-fit allowance when the bearing is assembled with the ball stud by circumferential caulking.Curve A shows the characteristics of the conventional device shown in Figure 1; B represents the characteristic according to the present invention.

In other words, conventional ball joints use low-elasticity members as bearing members and are structured to press the entire surface of the bearing, so the change in operating torque with respect to the press-fitting allowance of the bearing is due to the increase in the elastic force of the bearing member as the press-fitting allowance increases. is large, resulting in the change shown in curve A. For example, if the dimensional accuracy range of the bearing press-fit allowance caused by the assembly configuration, that is, the dimensional variation falls within the range K shown by the arrow, then point a ₁ and point a ₂ on curve A There is a variation in the operating torque that corresponds to the length of the vertical axis.

On the other hand, in the ball joint of the present invention, as shown in the embodiment shown in Fig. 2, a low compression part is provided by providing a recess in the inclined surface part of the bearing fitting part of the socket, which reduces the bearing press-fitting allowance. The change in the operating torque with respect to the increase is small, and after the sloped portion of the bearing is press-fitted into the recess until it fills, the state becomes similar to that of a conventional ball joint, and the operating torque increases. Therefore, for the same dimensional variation in the bearing press-fitting allowance as in the conventional case shown in Fig. 5, only a variation in the operating torque corresponding to the length of the vertical axis between points b ₁ and b ₂ of curve B occurs. The variation in operating torque is sufficiently small compared to conventional devices.

Therefore, in the ball joint of the present invention,
A bearing structure is created in which a high compression part and a low compression part are combined in the inclined surface part, and the pressing force of the high compression part is distributed in the vertical and horizontal directions and presses the ball part 2 almost uniformly over the circumference through the bearing. At the same time, variations in the bearing press-fit allowance are absorbed to some extent in the low compression section, making it easier to select dimensions and accuracy, making it easier to select bearings 4 and ball joint sockets 3.
An appropriate operating torque within a predetermined range can be obtained without increasing the dimensional accuracy of the ball portion 2 of the ball stud, the operating torque after assembly is stabilized, and quality is significantly improved. Also, the overhang into the recess will also give a reaction force in the bending direction,
Very advantageous.

Although the recess shapes shown in Figs. 3 and 4 are used as examples, it is believed that other shapes that facilitate cold forging of ball joint sockets can have the same effect as long as they are recess shapes. Needless to say.

[Brief explanation of drawings]

Figure 1 is a vertical cross-sectional view of a conventional ball joint.
FIG. 2 is a longitudinal cross-sectional view of an embodiment of the present invention, and FIGS. 3 and 4 are enlarged cross-sectional views of a recess applied to the present invention. FIG. 5 is a diagram illustrating the relationship between the conventional ball stud operating torque and the ball stud operating torque with respect to the bearing press-fitting allowance during caulking and assembling, comparing the conventional one and the one of the present invention. 1... Ball stud, 2... Ball, 3... Socket, 4... Bearing, 5... Plate, 6
...Crimping part, 7...Bearing fitting part, 8...
recess.

Claims (1)

[Scope of utility model registration request] In ball joints for automobiles, etc., especially ball joints that use an integral ball seat and generate operating resistance in the ball stud, the ball joint socket is installed on the inclined surface between the cylindrical surface and the bottom of the bearing fitting part of the ball joint socket. A ball joint characterized by having several recesses and generating stable operating resistance in a ball stud by the reaction force in the bending direction of the bearing slope portion located above the recesses.