JP2013151969A - Ball joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a positioning means to function without fail even if mutual alignment is not performed when attaching a bearing seat to a housing.SOLUTION: A rotation preventing means 13 for preventing relative rotation between a housing 5 and a bearing seat 4 is configured of: a plurality of protrusions 15 formed on the outer surface of the bearing seat 4 and arranged at an equal pitch on one circumference C with an axis Y of the housing 5 as a center; and a plurality of recessed parts 16 formed on the inner surface of the housing 5 and arranged at an equal pitch on the one circumference C, in which the number of recessed parts 16 is set to a number twice or more than the number of protrusions 15, and which is not divided by the number of protrusions 15, and when attaching the bearing seat 4 to the housing 5, at least one protrusion 15 is engaged with one of the recessed parts 16, and the other protrusions 15 not engaged with the recessed parts 16 are crushed.

Description

  The present invention relates to a ball joint mainly used for a suspension device and a steering device of an automobile, and in particular, a cylindrical housing, a ball stud including a ball portion and a stud portion protruding from the ball portion, and the stud portion. Synthetic resin bearing seats that hold the ball portion and can be swung within the housing so as to be able to swing, and provided between the housing and the bearing seat, and the relative rotation of the housing and the bearing seat. The present invention relates to an improvement in a ball joint provided with a detent means for preventing the rotation.

  In such a ball joint, the rotation prevention means between the housing and the bearing seat prevents the ball stud from rotating together with the ball seat when the ball stud swings, thereby stabilizing the bearing function for the ball portion of the bearing seat. It is effective in making it happen.

  By the way, in the conventional ball joint, as disclosed in the following Patent Document 1, the same number of engaging portions that engage with each other are provided on the opposing peripheral surfaces of the housing and the bearing seat as the detent means. .

Japanese Patent No. 4498124

  In the conventional ball joint, when the bearing seat is mounted on the housing, it is necessary to align the plurality of engaging portions on the housing side and the plurality of engaging portions on the bearing seat side. Since it reduces the assembly efficiency of ball joints, it is an obstacle to reducing product costs.

  The present invention has been made in view of such circumstances, and when the bearing seat is mounted on the housing, the positioning means can function reliably without performing alignment between the housing and the bearing seat. The object is to provide a ball joint.

  In order to achieve the above object, the present invention includes a cylindrical housing, a ball stud including a ball portion and a stud portion protruding from the ball portion, and the ball portion being capable of swinging the stud portion. A ball joint comprising: a synthetic resin bearing seat mounted in the housing with a tightening margin; and a detent means provided between the housing and the bearing seat to prevent relative rotation of the housing and the bearing seat. A plurality of protrusions formed on an outer surface of the bearing seat that receives a tightening force from the housing and arranged at an equal pitch on a circumference around the axis of the housing; and the housing Formed on the inner surface that gives a clamping force to the bearing seat, etc. And the number of the recesses is set to a number that is not less than twice the number of the projections and is not divisible by the number of projections. The first feature is that at the time of mounting, at least one of the protrusions engages with any one of the recesses, and the other protrusions not engaged with the recesses are crushed.

  In addition to the first feature, the present invention provides that the half angle of the remainder when the pitch angle of the protrusion is divided by the pitch angle of the recess is the edge of the recess and the circumference. The second feature is that the size of the recess is set to be smaller than one half of the central angle with respect to the two intersections.

  Furthermore, in addition to the first or second feature, the present invention is provided with a stud port in which a stud portion is disposed at one end and a stepped mounting port at the other end. A cylindrical housing body whose peripheral surface serves as a support surface for the bearing seat inserted from the mounting opening, and a plug fitted and fixed to the mounting opening while pressing the end face of the bearing seat with a predetermined tightening margin; The housing is constructed, and the projection is formed on the end surface of the bearing seat, the recess is formed in the plug, and the outer surface of the projection and the inner surface of the recess are formed in a spherical shape. And

  Furthermore, in the present invention, in addition to the first or second feature, the housing is formed in a bottomed cylindrical shape with one end surface opened as a stud port in which the stud portion is disposed, and is formed on the inner peripheral surface of the housing. While forming the recess, the protrusion is formed on the outer peripheral surface of the bearing seat that is press-fitted together with the ball portion from the stud opening on the inner peripheral surface of the housing, and the front end of the protrusion in the press-fitting direction is tapered. The fourth feature is that it is formed in a shape.

  According to the first aspect of the present invention, if the bearing seat is mounted on the housing without considering the alignment of the bearing seat with respect to the housing, at least one protrusion of the bearing seat is connected to any one of the plurality of recesses of the housing. Therefore, when the ball stud swings, the bearing seat can properly exert a bearing function with respect to the ball portion without causing any co-rotation with the ball portion. In addition, since the alignment of the bearing seat with respect to the housing is not required, the number of assembling steps of the ball joint is reduced correspondingly, which can greatly contribute to cost reduction.

  According to the second feature of the present invention, even in the maximum deviation state between the protrusion and the recess, the outermost recess of the plurality of recesses disposed within the one pitch angle is within one pitch angle of the protrusion. The apex of one protrusion faces the inner surface, and therefore one protrusion with the apex facing the inner surface of the outermost recess is forced to the outermost recess by the mounting force of the bearing seat on the housing. Can be engaged.

  According to the third feature of the present invention, even when there is a slight deviation between the projection to be engaged and the recess when the plug is fitted and fixed to the mounting opening of the housing body, They can be smoothly engaged with each other by the inductive action of the spherical surfaces facing each other.

  According to the fourth feature of the present invention, when the bearing seat is press-fitted into the housing from the stud opening, even if there is a slight deviation between the protrusion to be engaged and the recess, the protrusion and the recess are The tapered tips can be smoothly engaged with each other by the guiding action.

The longitudinal cross-sectional view of the ball joint which concerns on 1st Embodiment of this invention. The 2A-2A arrow end view of FIG. 1 of the bearing seat in the free state in the ball joint. 2B-2B is an end view of the plug in the ball joint as viewed in the direction of the arrow 2B-2B in FIG. The longitudinal cross-sectional view of the ball joint which concerns on 2nd Embodiment of this invention. 4-4 sectional drawing of the bearing seat in the free state in the ball joint of FIG. 4-4 sectional drawing of the housing in the ball joint of FIG. The shape of the projection is shown in FIG. The longitudinal cross-sectional view of the ball joint which concerns on a state.

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

  First, the description starts with the description of the first embodiment of the present invention shown in FIGS. In FIG. 1, the ball joint J includes a ball portion 2 and a metal ball stud 1 formed integrally with the ball portion 2 and protruding outwardly from the ball portion 2. A synthetic resin bearing seat 4 that holds the ball portion 2 and a cylindrical housing 5 that accommodates the ball portion 2 together with the bearing seat 4 and applies a clamping force to the bearing seat 4. It is the main component. The housing 5 is composed of a cylindrical housing body 6 and a flat plug 7, and the housing body 6 is integrally formed with a support arm 8 extending to one side thereof.

  The housing body 6 is provided with a stud port 10 in which the stud portion 3 is disposed at one end and a stepped mounting port 11 at the other end, and an intermediate inner surface thereof is inserted from the mounting port 11. It becomes the support surface 12 with respect to the bearing sheet 4 made.

  The support surface 12 has a cylindrical shape in which the half on the side of the mounting port 11 has a cylindrical shape and the half on the side of the stud 10 has a small diameter toward the stud 3, and the bearing that holds the ball 2 The sheet 4 is press-fitted from the mounting opening 11 into the support surface 12 with a predetermined tightening allowance.

  The plug 7 is fitted into the mounting port 11 so as to close the mounting port 11 while pressing the flat end surface 4a of the bearing seat 4 with a predetermined tightening after press-fitting the bearing seat 4 into the support surface 12. And it is clamped and fixed by the step part 11a and the caulking part 6a of the housing body 6.

  Between the bearing seat 4 and the plug 7 is provided a rotation preventing means 13 for preventing their relative rotation. As shown in FIGS. 1, 2 </ b> A, and 2 </ b> B, the anti-rotation means 13 is formed on a flat end surface 4 a that faces the mounting opening 11 of the bearing seat 4, and is centered on the axis Y of the cylindrical housing 5. A plurality of protrusions 15 arranged at an equal pitch on one circumference C and a plurality of recesses 16 formed on the inner surface of the plug 7 and arranged at an equal pitch on the one circumference C. The outer surface and the inner surface of the recess 16 are formed in a spherical shape.

  The number of the recesses 16 is set to be more than twice the number of the projections 15 and not divisible by the number of the projections 15, and at least one of the plurality of projections 15 when the plug 7 is fitted into the mounting opening 11. Is engaged with any one of the plurality of recesses 16, and the other protrusions 15 not engaged with the recesses 16 are crushed by the plug 7.

  Specifically, the number of the recesses 16 is set to a number that is more than twice the number of the protrusions 15 and is not divisible by the number of the protrusions 15, and the pitch angle α of the protrusions 15 is divided by the pitch angle β of the recesses 16. The diameter of the recess 16 is set so that the half of the remainder angle is smaller than half of the central angle θ with respect to the two intersections P, P of the periphery of the recess 16 and the circumference C. Is set.

  Specific examples are shown in FIGS. 2A and 2B.

  That is, the number of protrusions 15 on one circumference C is set to five. Therefore, the pitch angle α of the protrusions 15 is 72 °. On the other hand, the number of recesses 16 on the same circumference C is set to 16 times 3.2 times the number of protrusions 15. Therefore, the pitch angle β of the recesses 16 is 22.5 °. Further, the central angle θ with respect to the two intersections P, P between the peripheral edge of the recess 16 and the one circumference C is set to 5 °.

  Here, in order to obtain the number of recesses 16 disposed within one pitch angle α of the protrusions 15, that is, between two adjacent protrusions 15, the pitch angle α of the protrusions 15 is set to 72 °. If the angle β is divided by 22.5 °, three pieces are obtained, and the remainder is 4.5 °. The remainder of 4.5 ° is obtained when the outermost one concave portion 16 of the three concave portions 16 arranged within one pitch angle α of the projection 15 matches the other outermost portion. This is a shift angle generated between one recess 16 and another projection 15. Therefore, assuming the maximum displacement state, the three recesses 16 are concentrated at the center between the two adjacent projections 15, and the outermost recesses 16 at this time and the projections 15 adjacent thereto are arranged. Is a half of 4.5 °, which is 2.25 °, which is the center of the two concave points 16 and the circumference C of the two intersections P and P. Angle θ: smaller than half of 5 °. This means that the apex of one protrusion 15 faces the inner surface of the outermost recess 16. Moreover, in practice, there is usually a slight difference in the deviation angle on both outer sides of the plurality of recesses 16, so that when the plug 7 presses the end surface 4 a of the bearing seat 4, the deviation angle is small. The recesses 16 and the projections 15 on the side are smoothly engaged with each other by the inductive action of the opposing spherical surfaces, and the projections 15 that cannot engage with the other recesses 16 are crushed by the plug 7. .

  Thus, if the plug 7 is fitted and fixed to the mounting opening 11 of the housing body 6 without considering the alignment of the plug 7 with respect to the bearing seat 4, at least one protrusion 15 of the bearing seat 4 is connected to the plurality of plugs 7. Therefore, when the ball stud 1 swings, the bearing seat 4 does not co-rotate with the ball portion 2 and has an appropriate bearing function for the ball portion 2. Can be demonstrated. In addition, since the alignment of the bearing seat 4 with respect to the housing 5 is not required, the number of assembling steps of the ball joint J is reduced correspondingly, which can greatly contribute to cost reduction.

  Next, a second embodiment of the present invention shown in FIGS. 3 to 4B will be described.

  In FIG. 3, the ball joint J includes a ball part 2, a metal ball stud 1 formed integrally with the ball part 2 and protruding outwardly of the ball part 2, and the swing of the stud part 3. Mainly includes a synthetic resin bearing seat 4 that holds the ball portion 2 and a cylindrical housing 5 that houses the ball portion 2 together with the bearing seat 4 and applies a clamping force to the bearing seat 4. As a component. The housing 5 has a bottomed cylindrical shape with one end surface opened as a stud port 10, and a connecting bolt 20 is integrally formed on the outer end surface of the bottom portion.

  In the housing 5, the bearing seat 4 holding the ball portion 2 is press-fitted from the stud port 10, and then the stud port 10 side of the housing 5 is caulked along the shape of the ball portion 2. By the press-fitting and caulking, a tightening force is applied to the bearing seat 4 with a predetermined tightening allowance.

  As shown by a two-dot chain line in the enlarged portion in FIG. 3, of the inner peripheral surface of the housing 5 before caulking, one half of the connecting bolt 20 side is a conical surface 5a and a large conical surface 5a. The other half is a large-diameter cylindrical surface 5d connected to the cylindrical surface 5b through a tapered step portion 5c. The cylindrical surface 5b and the cylindrical surface 5b are connected to the cylindrical surface 5b. Between the bearing seats 4 is provided anti-rotation means 13 that prevents their relative rotation.

  As shown in FIGS. 3, 4 A, and 4 B, the anti-rotation means 13 is formed on the outer peripheral surface of the bearing seat 4 that receives a pressing force from the cylindrical surface 5 b of the housing 5, and is centered on the axis Y of the housing 5. And a plurality of protrusions 115 arranged at an equal pitch on one circumference C and a plurality of recesses 116 formed on the cylindrical surface 5b of the housing 5 and arranged at an equal pitch on the one circumference C. . Each protrusion 115 extends along the press-fitting direction of the bearing seat 4 to the housing 5, the cross section thereof forms a partial cylindrical shape, and the front end portion 115 a in the press-fitting direction has a tapered shape. The recess 116 also has a shape corresponding to the projection 115.

  The number of the recesses 116 is set to be more than twice the number of the protrusions 115 and is not divisible by the number of the protrusions 115. When the bearing seat 4 is press-fitted into the housing 5, at least one of the plurality of protrusions 115 is The other protrusions 115 that are engaged with any one of the plurality of groove-like recesses 116 and are not engaged with the recesses 116 are crushed.

  Specifically, the number of the recesses 116 is set to a number that is more than twice the number of the protrusions 115 and is not divisible by the number of the protrusions 115, and the pitch angle α of the protrusions 115 is divided by the pitch angle β of the recesses 116. So that the half angle of the remainder of the angle is smaller than half of the central angle θ with respect to the two intersections P, P between the both side edges of the groove-like recess 116 and the one circumference C, The width of the recess 116 is set.

  Specific examples are shown in FIGS. 4A and 4B.

  That is, the number of protrusions 115 on one circumference C is set to three. Therefore, the pitch angle α of the protrusions 115 is 120 °. On the other hand, the number of recesses 116 on the same circumference C is set to 25, which is 8.33. Therefore, the pitch angle β of the recesses 116 is 14.4 °. Further, the central angle θ with respect to the two intersections P, P between the side edges of the recess 116 and the one circumference C is set to 5 °.

  Here, in order to obtain the number of recesses 116 disposed within one pitch angle α of the protrusions 115, that is, between two adjacent protrusions 115, the pitch angle α of the protrusions 115 is set to 120 °. If the angle β is divided by 14.4 °, it becomes 8 and the remainder is 4.8 °. The remainder of 4.8 ° is obtained when the outermost one concave portion 116 of the eight concave portions 116 arranged within one pitch angle α of the projection 115 is aligned with one projection 115 and the other outermost portion. This is a deviation angle generated between one recess 116 and another projection 115. Therefore, assuming the maximum displacement state, the three concave portions 116 are concentrated at the center between two adjacent projections 115. At this time, both outermost concave portions 116 and the adjacent projections 115 are arranged. Is 2.4 °, which is a half of 4.8 °, which is relative to the two intersections P and P between the side edges of one recess 116 and the circumference C. Center angle θ: smaller than half of 5 °. This means that the apex of one protrusion 115 faces the inner surface of the outermost recess 116. Moreover, in practice, there is usually a slight difference between the deviation angles on both outer sides of the plurality of recesses 116. Therefore, when the bearing seat 4 is press-fitted into the housing 5, the recesses on the side with the smaller deviation angle are used. 116 and the projection 115 are forced to be engaged, and in particular, the concave portion 116 and the projection 115 are smoothly engaged by the guiding action of the tapered tip portion 115 a of the projection 115, and the other concave portion 116 is engaged. The projection 115 that cannot be crushed is crushed by the cylindrical surface 5 b of the housing 5.

  Thereafter, the periphery of the stud opening 10 of the housing 5 is squeezed by caulking.

  Thus, as in the first embodiment, if the bearing seat 4 is press-fitted into the housing 5 without considering the alignment of the bearing seat 4 with respect to the housing 5, at least one protrusion 115 of the bearing seat 4 is inserted into the housing 5. Can be engaged with any of the plurality of recesses 116 of the cylindrical surface 5b.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the scope of the present invention.

C ... Circumference J ... Ball joint P ... Intersection Y ... Housing axis α ... Projection pitch angle β ... Recess pitch angle θ ... · Center angle 1 ··· Ball stud 2 ··· Ball portion 3 ··· Stud portion 4 ··· Bearing seat 4a · · · Bearing seat end surface 5 · · · Housing 6 ··· Housing body 7 ··· Plug 10 ··· Stud port 11 ··· Mounting port 12 ··· Support surface 13 · · · Anti-rotation means 15 and 115 · · · projection 16 and 116 · · · recess 115a ··· Protrusion tip

  The present invention relates to a ball joint mainly used for a suspension device and a steering device of an automobile, and in particular, a cylindrical housing, a ball stud including a ball portion and a stud portion protruding from the ball portion, and the stud portion. Synthetic resin bearing seats that hold the ball portion and can be swung within the housing so as to be able to swing, and provided between the housing and the bearing seat, and the relative rotation of the housing and the bearing seat. The present invention relates to an improvement in a ball joint provided with a detent means for preventing the rotation.

  In such a ball joint, the rotation prevention means between the housing and the bearing seat prevents the ball stud from rotating together with the ball seat when the ball stud swings, thereby stabilizing the bearing function for the ball portion of the bearing seat. It is effective in making it happen.

  By the way, in the conventional ball joint, as disclosed in the following Patent Document 1, the same number of engaging portions that engage with each other are provided on the opposing peripheral surfaces of the housing and the bearing seat as the detent means. .

Japanese Patent No. 4498124

  In the conventional ball joint, when the bearing seat is mounted on the housing, it is necessary to align the plurality of engaging portions on the housing side and the plurality of engaging portions on the bearing seat side. Since it reduces the assembly efficiency of ball joints, it is an obstacle to reducing product costs.

  The present invention has been made in view of such circumstances, and when the bearing seat is mounted on the housing, the positioning means can function reliably without performing alignment between the housing and the bearing seat. The object is to provide a ball joint.

  In order to achieve the above object, the present invention includes a cylindrical housing, a ball stud including a ball portion and a stud portion protruding from the ball portion, and the ball portion being capable of swinging the stud portion. A ball joint comprising: a synthetic resin bearing seat mounted in the housing with a tightening margin; and a detent means provided between the housing and the bearing seat to prevent relative rotation of the housing and the bearing seat. A plurality of protrusions formed on an outer surface of the bearing seat that receives a tightening force from the housing and arranged at an equal pitch on a circumference around the axis of the housing; and the housing Formed on the inner surface that gives a clamping force to the bearing seat, etc. And the number of the recesses is set to a number that is not less than twice the number of the projections and is not divisible by the number of projections. The first feature is that at the time of mounting, at least one of the protrusions engages with any one of the recesses, and the other protrusions not engaged with the recesses are crushed.

  In addition to the first feature, the present invention provides that the half angle of the remainder when the pitch angle of the protrusion is divided by the pitch angle of the recess is the edge of the recess and the circumference. The second feature is that the size of the recess is set to be smaller than one half of the central angle with respect to the two intersections.

  Furthermore, in addition to the first or second feature, the present invention is provided with a stud port in which a stud portion is disposed at one end and a stepped mounting port at the other end. A cylindrical housing body whose peripheral surface serves as a support surface for the bearing seat inserted from the mounting opening, and a plug fitted and fixed to the mounting opening while pressing the end face of the bearing seat with a predetermined tightening margin; The housing is constructed, and the projection is formed on the end surface of the bearing seat, the recess is formed in the plug, and the outer surface of the projection and the inner surface of the recess are formed in a spherical shape. And

  Furthermore, in the present invention, in addition to the first or second feature, the housing is formed in a bottomed cylindrical shape with one end surface opened as a stud port in which the stud portion is disposed, and is formed on the inner peripheral surface of the housing. While forming the recess, the protrusion is formed on the outer peripheral surface of the bearing seat that is press-fitted together with the ball portion from the stud opening on the inner peripheral surface of the housing, and the front end of the protrusion in the press-fitting direction is tapered. The fourth feature is that it is formed in a shape.

  According to the first aspect of the present invention, if the bearing seat is mounted on the housing without considering the alignment of the bearing seat with respect to the housing, at least one protrusion of the bearing seat is connected to any one of the plurality of recesses of the housing. Therefore, when the ball stud swings, the bearing seat can properly exert a bearing function with respect to the ball portion without causing any co-rotation with the ball portion. In addition, since the alignment of the bearing seat with respect to the housing is not required, the number of assembling steps of the ball joint is reduced correspondingly, which can greatly contribute to cost reduction.

  According to the second feature of the present invention, even in the maximum deviation state between the protrusion and the recess, the outermost recess of the plurality of recesses disposed within the one pitch angle is within one pitch angle of the protrusion. The apex of one protrusion faces the inner surface, and therefore one protrusion with the apex facing the inner surface of the outermost recess is forced to the outermost recess by the mounting force of the bearing seat on the housing. Can be engaged.

  According to the third feature of the present invention, even when there is a slight deviation between the projection to be engaged and the recess when the plug is fitted and fixed to the mounting opening of the housing body, They can be smoothly engaged with each other by the inductive action of the spherical surfaces facing each other.

  According to the fourth feature of the present invention, when the bearing seat is press-fitted into the housing from the stud opening, even if there is a slight deviation between the protrusion to be engaged and the recess, the protrusion and the recess are The tapered tips can be smoothly engaged with each other by the guiding action.

The longitudinal cross-sectional view of the ball joint which concerns on 1st Embodiment of this invention. The 2A-2A arrow end view of FIG. 1 of the bearing seat in the free state in the ball joint. 2B-2B is an end view of the plug in the ball joint as viewed in the direction of the arrow 2B-2B in FIG. The longitudinal cross-sectional view of the ball joint which concerns on 2nd Embodiment of this invention. 4-4 sectional drawing of the bearing seat in the free state in the ball joint of FIG. 4-4 sectional drawing of the housing in the ball joint of FIG. The shape of the projection is shown in FIG .

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

  First, the description starts with the description of the first embodiment of the present invention shown in FIGS. In FIG. 1, the ball joint J includes a ball portion 2 and a metal ball stud 1 formed integrally with the ball portion 2 and protruding outwardly from the ball portion 2. A synthetic resin bearing seat 4 that holds the ball portion 2 and a cylindrical housing 5 that accommodates the ball portion 2 together with the bearing seat 4 and applies a clamping force to the bearing seat 4. It is the main component. The housing 5 is composed of a cylindrical housing body 6 and a flat plug 7, and the housing body 6 is integrally formed with a support arm 8 extending to one side thereof.

  The housing body 6 is provided with a stud port 10 in which the stud portion 3 is disposed at one end and a stepped mounting port 11 at the other end, and an intermediate inner surface thereof is inserted from the mounting port 11. It becomes the support surface 12 with respect to the bearing sheet 4 made.

  The support surface 12 has a cylindrical shape in which the half on the side of the mounting port 11 has a cylindrical shape and the half on the side of the stud 10 has a small diameter toward the stud 3, and the bearing that holds the ball 2 The sheet 4 is press-fitted from the mounting opening 11 into the support surface 12 with a predetermined tightening allowance.

  The plug 7 is fitted into the mounting port 11 so as to close the mounting port 11 while pressing the flat end surface 4a of the bearing seat 4 with a predetermined tightening after press-fitting the bearing seat 4 into the support surface 12. And it is clamped and fixed by the step part 11a and the caulking part 6a of the housing body 6.

  Between the bearing seat 4 and the plug 7 is provided a rotation preventing means 13 for preventing their relative rotation. As shown in FIGS. 1, 2 </ b> A, and 2 </ b> B, the anti-rotation means 13 is formed on a flat end surface 4 a that faces the mounting opening 11 of the bearing seat 4, and is centered on the axis Y of the cylindrical housing 5. A plurality of protrusions 15 arranged at an equal pitch on one circumference C and a plurality of recesses 16 formed on the inner surface of the plug 7 and arranged at an equal pitch on the one circumference C. The outer surface and the inner surface of the recess 16 are formed in a spherical shape.

  The number of the recesses 16 is set to be more than twice the number of the projections 15 and not divisible by the number of the projections 15, and at least one of the plurality of projections 15 when the plug 7 is fitted into the mounting opening 11. Is engaged with any one of the plurality of recesses 16, and the other protrusions 15 not engaged with the recesses 16 are crushed by the plug 7.

  Specifically, the number of the recesses 16 is set to a number that is more than twice the number of the protrusions 15 and is not divisible by the number of the protrusions 15, and the pitch angle α of the protrusions 15 is divided by the pitch angle β of the recesses 16. The diameter of the recess 16 is set so that the half of the remainder angle is smaller than half of the central angle θ with respect to the two intersections P, P of the periphery of the recess 16 and the circumference C. Is set.

  Specific examples are shown in FIGS. 2A and 2B.

  That is, the number of protrusions 15 on one circumference C is set to five. Therefore, the pitch angle α of the protrusions 15 is 72 °. On the other hand, the number of recesses 16 on the same circumference C is set to 16 times 3.2 times the number of protrusions 15. Therefore, the pitch angle β of the recesses 16 is 22.5 °. Further, the central angle θ with respect to the two intersections P, P between the peripheral edge of the recess 16 and the one circumference C is set to 5 °.

  Here, in order to obtain the number of recesses 16 disposed within one pitch angle α of the protrusions 15, that is, between two adjacent protrusions 15, the pitch angle α of the protrusions 15 is set to 72 °. If the angle β is divided by 22.5 °, three pieces are obtained, and the remainder is 4.5 °. The remainder of 4.5 ° is obtained when the outermost one concave portion 16 of the three concave portions 16 arranged within one pitch angle α of the projection 15 matches the other outermost portion. This is a shift angle generated between one recess 16 and another projection 15. Therefore, assuming the maximum displacement state, the three recesses 16 are concentrated at the center between the two adjacent projections 15, and the outermost recesses 16 at this time and the projections 15 adjacent thereto are arranged. Is a half of 4.5 °, which is 2.25 °, which is the center of the two concave points 16 and the circumference C of the two intersections P and P. Angle θ: smaller than half of 5 °. This means that the apex of one protrusion 15 faces the inner surface of the outermost recess 16. Moreover, in practice, there is usually a slight difference in the deviation angle on both outer sides of the plurality of recesses 16, so that when the plug 7 presses the end surface 4 a of the bearing seat 4, the deviation angle is small. The recesses 16 and the projections 15 on the side are smoothly engaged with each other by the inductive action of the opposing spherical surfaces, and the projections 15 that cannot engage with the other recesses 16 are crushed by the plug 7. .

  Thus, if the plug 7 is fitted and fixed to the mounting opening 11 of the housing body 6 without considering the alignment of the plug 7 with respect to the bearing seat 4, at least one protrusion 15 of the bearing seat 4 is connected to the plurality of plugs 7. Therefore, when the ball stud 1 swings, the bearing seat 4 does not co-rotate with the ball portion 2 and has an appropriate bearing function for the ball portion 2. Can be demonstrated. In addition, since the alignment of the bearing seat 4 with respect to the housing 5 is not required, the number of assembling steps of the ball joint J is reduced correspondingly, which can greatly contribute to cost reduction.

  Next, a second embodiment of the present invention shown in FIGS. 3 to 4B will be described.

  In FIG. 3, the ball joint J includes a ball part 2, a metal ball stud 1 formed integrally with the ball part 2 and protruding outwardly of the ball part 2, and the swing of the stud part 3. Mainly includes a synthetic resin bearing seat 4 that holds the ball portion 2 and a cylindrical housing 5 that houses the ball portion 2 together with the bearing seat 4 and applies a clamping force to the bearing seat 4. As a component. The housing 5 has a bottomed cylindrical shape with one end surface opened as a stud port 10, and a connecting bolt 20 is integrally formed on the outer end surface of the bottom portion.

  In the housing 5, the bearing seat 4 holding the ball portion 2 is press-fitted from the stud port 10, and then the stud port 10 side of the housing 5 is caulked along the shape of the ball portion 2. By the press-fitting and caulking, a tightening force is applied to the bearing seat 4 with a predetermined tightening allowance.

  As shown by a two-dot chain line in the enlarged portion in FIG. 3, of the inner peripheral surface of the housing 5 before caulking, one half of the connecting bolt 20 side is a conical surface 5a and a large conical surface 5a. The other half is a large-diameter cylindrical surface 5d connected to the cylindrical surface 5b through a tapered step portion 5c. The cylindrical surface 5b and the cylindrical surface 5b are connected to the cylindrical surface 5b. Between the bearing seats 4 is provided anti-rotation means 13 that prevents their relative rotation.

  As shown in FIGS. 3, 4 A, and 4 B, the anti-rotation means 13 is formed on the outer peripheral surface of the bearing seat 4 that receives a pressing force from the cylindrical surface 5 b of the housing 5, and is centered on the axis Y of the housing 5. And a plurality of protrusions 115 arranged at an equal pitch on one circumference C and a plurality of recesses 116 formed on the cylindrical surface 5b of the housing 5 and arranged at an equal pitch on the one circumference C. . Each protrusion 115 extends along the press-fitting direction of the bearing seat 4 to the housing 5, the cross section thereof forms a partial cylindrical shape, and the front end portion 115 a in the press-fitting direction has a tapered shape. The recess 116 also has a shape corresponding to the projection 115.

  The number of the recesses 116 is set to be more than twice the number of the protrusions 115 and is not divisible by the number of the protrusions 115. When the bearing seat 4 is press-fitted into the housing 5, at least one of the plurality of protrusions 115 is The other protrusions 115 that are engaged with any one of the plurality of groove-like recesses 116 and are not engaged with the recesses 116 are crushed.

  Specifically, the number of the recesses 116 is set to a number that is more than twice the number of the protrusions 115 and is not divisible by the number of the protrusions 115, and the pitch angle α of the protrusions 115 is divided by the pitch angle β of the recesses 116. So that the half angle of the remainder of the angle is smaller than half of the central angle θ with respect to the two intersections P, P between the both side edges of the groove-like recess 116 and the one circumference C, The width of the recess 116 is set.

  Specific examples are shown in FIGS. 4A and 4B.

  That is, the number of protrusions 115 on one circumference C is set to three. Therefore, the pitch angle α of the protrusions 115 is 120 °. On the other hand, the number of recesses 116 on the same circumference C is set to 25, which is 8.33. Therefore, the pitch angle β of the recesses 116 is 14.4 °. Further, the central angle θ with respect to the two intersections P, P between the side edges of the recess 116 and the one circumference C is set to 5 °.

Here, in order to obtain the number of recesses 116 disposed within one pitch angle α of the protrusions 115, that is, between two adjacent protrusions 115, the pitch angle α of the protrusions 115 is set to 120 °. If the angle β is divided by 14.4 °, it becomes 8 and the remainder is 4.8 °. The remainder of 4.8 ° is obtained when the outermost one concave portion 116 of the eight concave portions 116 arranged within one pitch angle α of the projection 115 is aligned with one projection 115 and the other outermost portion. This is a deviation angle generated between one recess 116 and another projection 115. Therefore, assuming the maximum displacement state, the eight concave portions 116 are concentrated at the center between two adjacent projections 115, and the outermost concave portions 116 at this time and the projections 115 adjacent thereto are arranged. Is 2.4 °, which is a half of 4.8 °, which is relative to the two intersections P and P between the side edges of one recess 116 and the circumference C. Center angle θ: smaller than half of 5 °. This means that the apex of one protrusion 115 faces the inner surface of the outermost recess 116. Moreover, in practice, there is usually a slight difference between the deviation angles on both outer sides of the plurality of recesses 116. Therefore, when the bearing seat 4 is press-fitted into the housing 5, the recesses on the side with the smaller deviation angle are used. 116 and the projection 115 are forced to be engaged, and in particular, the concave portion 116 and the projection 115 are smoothly engaged by the guiding action of the tapered tip portion 115 a of the projection 115, and the other concave portion 116 is engaged. The projection 115 that cannot be crushed is crushed by the cylindrical surface 5 b of the housing 5.

  Thereafter, the periphery of the stud opening 10 of the housing 5 is squeezed by caulking.

  Thus, as in the first embodiment, if the bearing seat 4 is press-fitted into the housing 5 without considering the alignment of the bearing seat 4 with respect to the housing 5, at least one protrusion 115 of the bearing seat 4 is inserted into the housing 5. Can be engaged with any of the plurality of recesses 116 of the cylindrical surface 5b.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the scope of the present invention.

C ... Circumference J ... Ball joint P ... Intersection Y ... Housing axis α ... Projection pitch angle β ... Recess pitch angle θ ... · Center angle 1 ··· Ball stud 2 ··· Ball portion 3 ··· Stud portion 4 ··· Bearing seat 4a · · · Bearing seat end surface 5 · · · Housing 6 ··· Housing body 7 ··· Plug 10 ··· Stud port 11 ··· Mounting port 12 ··· Support surface 13 · · · Anti-rotation means 15 and 115 · · · projection 16 and 116 · · · recess 115a ··· Protrusion tip

Claims (4)

A cylindrical housing (5), a ball stud (1) consisting of a ball part (2) and a stud part (3) protruding from the ball part (2), and the swinging of the stud part (3) are possible. A synthetic resin bearing seat (4) is provided between the housing (5) and the bearing seat (4). In the ball joint comprising the rotation preventing means for preventing the relative rotation of the housing (5) and the bearing seat (4),
The rotation preventing means (13) is formed on an outer surface of the bearing seat (4) that receives a tightening force from the housing (5) and has a circumference around the axis (Y) of the housing (5) ( C) a plurality of protrusions (15, 115) arranged at an equal pitch on the inner surface of the housing (5) that gives a tightening force to the bearing seat (4) and on the circumference (C). A plurality of recesses (16, 116) arranged at equal pitches, and the number of the recesses (16, 116) is more than twice the number of the projections (15, 115) and the protrusions (15, 116). 115), when the bearing seat (4) is mounted on the housing (5), at least one of the protrusions (15, 115) is formed in the recess (16, 116). Engage with any , Ball joints, characterized in that the other of said protrusions of said recess (16, 116) and disengaged (15, 115) is that to be crushed. The ball joint according to claim 1,
The half angle of the remainder when the pitch angle (α) of the protrusions (15, 115) is divided by the pitch angle (β) of the recesses (16, 116) is the recess (16, 116). The size of the recess (16, 116) was set to be smaller than half of the central angle (θ) with respect to two intersections (P, P) of the edge of the circle and the circumference (C). A ball joint characterized by The ball joint according to claim 1 or 2,
A stud port (10) in which the stud portion (3) is disposed is provided at one end portion, and a stepped mounting port (11) is provided at the other end, and an inner peripheral surface between them is a mounting port ( 11) While pressing the cylindrical housing body (6) serving as a support surface (12) for the bearing seat (4) inserted from 11) and the end surface (4a) of the bearing seat (4) with a predetermined allowance. The housing (5) is constituted by the plug (7) fitted and fixed to the mounting opening (11), the protrusion (15) is formed on the end surface (4a) of the bearing seat (4), and the plug ( The ball joint is characterized in that the concave portion (16) is formed in 7), and the outer surface of the projection (15) and the inner surface of the concave portion (16) are formed in a spherical shape. The ball joint according to claim 1 or 2,
The housing (5) is formed in a bottomed cylindrical shape with one end face open as a stud port (10) in which the stud portion (3) is disposed, and the recess (116) is formed on the inner peripheral surface of the housing (5). The protrusion (115) is formed on the outer peripheral surface of the bearing seat (4) press-fitted together with the ball portion (2) from the stud port (10) on the inner peripheral surface of the housing (5), A ball joint characterized in that the tip (115a) of the protrusion (115) forward in the press-fitting direction is tapered.

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