JP2011226587A - Sliding constant velocity universal joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To certainly reduce a play occurring in a fitting part between an inside joint member and a shaft by a simple means without providing a torsion angle in a spline.SOLUTION: In the sliding constant velocity universal joint which includes an outside joint member 10 and the inside joint member 20 transmitted with torque while permitting axial direction displacement and angle displacement between the inside joint member 20 and the outside joint member 10, and wherein the shaft 50 is inserted into a hole 22 of the inside joint member 20 and is fitted therein in a state of allowing torque transmission, the fitting part 60 between the inside joint member 20 and the shaft 50 is disposed on an insertion side of the shaft 50, and a fixing part 70 imparting an axial direction load on the fitting part 60 is disposed on an opposite-insertion side of the shaft 50. The fitting part 60 includes a structure wherein a spline 23 is formed in a taper-like opening part of the hole 22 of the inside joint member 20 and wherein a spline 53 is formed in a taper-like part of the outer circumferential face of the shaft 50. The fixing part 70 includes: a screw 52 formed on the outer circumferential face of the shaft 50; and a nut 72 tightening and fixing the inside joint member 20 to the shaft 50 by screwing on the screw 52.

Description

  The present invention is used in power transmission systems of automobiles, airplanes, ships, and various industrial machines, and is incorporated into a drive shaft, a propeller shaft, etc. used in, for example, a 4WD vehicle, an FR vehicle, etc. The present invention relates to a sliding type constant velocity universal joint that allows axial displacement and angular displacement between them.

  For example, there are two types of constant velocity universal joints, such as fixed constant velocity universal joints and sliding constant velocity universal joints, that are built into drive shafts and propeller shafts that transmit rotational force from automobile engines to wheels at constant speed. is there. Both of these constant velocity universal joints have a structure in which two shafts on the driving side and the driven side are connected so that rotational torque can be transmitted at a constant speed even if the two shafts have an operating angle.

  A drive shaft that transmits power from an automobile engine to a driving wheel needs to cope with an angular displacement and an axial displacement caused by a change in a relative positional relationship between the engine and the wheel. Side) and a fixed type constant velocity universal joint on the drive wheel side (outboard side), and a structure in which both constant velocity universal joints are connected by a shaft.

  One of the sliding type constant velocity universal joints assembled on the engine side of the drive shaft is a roller type tripod type constant velocity universal joint (TJ) using a roller as a torque transmission member. Another sliding constant velocity universal joint includes a ball type double offset constant velocity universal joint (DOJ) using a ball as a torque transmission member. The fixed constant velocity universal joint assembled on the drive wheel side of the drive shaft includes a Rzeppa type constant velocity universal joint (BJ) and an undercut free type constant velocity universal joint (UJ).

  These various constant velocity universal joints have a structure in which the shaft end portion of the shaft is inserted into the hole of the inner joint member and is spline-fitted. That is, the spline is formed on the inner peripheral surface of the hole of the inner joint member, the spline is formed on the outer peripheral surface of the shaft end portion of the shaft, and the shaft end portion of the shaft is inserted into the hole of the inner joint member. Torque can be transmitted by fitting the splines of the joint member and the splines of the shaft.

  In constant velocity universal joints used for drive shafts, there are various means for suppressing backlash generated at the fitting portion between the spline of the inner joint member and the spline of the shaft in order to improve the NVH (Noise Vibration Harshness) characteristics of the automobile. (See, for example, Patent Document 1). In the constant velocity universal joint disclosed in Patent Document 1, a shaft spline is provided with a torsion angle, and the shaft spline having the torsion angle is fitted to the spline of the inner joint member, thereby generating in the fitting portion. The play is reduced.

Japanese Utility Model Publication No. 6-33220

  By the way, as described above, the conventional constant velocity universal joint disclosed in Patent Document 1 has a shaft spline for the purpose of reducing backlash generated at the fitting portion between the spline of the inner joint member and the spline of the shaft. Has a structure in which a twist angle is provided.

  However, if the torsion angle of the shaft spline is set to be large in order to tighten the spline fitting between the inner joint member and the shaft, a large load must be applied when the shaft is inserted into the hole of the inner joint member. It becomes difficult to connect the inner joint member and the shaft by spline fitting.

  In order to avoid this, if the twist angle of the spline of the shaft is set to be small, loose spline fitting is likely to occur, and it becomes difficult to completely eliminate the play generated in the fitting portion. Thus, it is very difficult to optimally set the twist angle of the spline.

  Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to provide a fitting portion between the inner joint member and the shaft by a simple means without providing a twist angle in the spline. An object of the present invention is to provide a sliding type constant velocity universal joint that can surely reduce the generated play.

  As technical means for achieving the aforementioned object, the present invention includes an outer joint member and an inner joint member to which torque is transmitted while allowing axial displacement and angular displacement between the outer joint member. A sliding type constant velocity universal joint that is inserted into the hole of the inner joint member and is fitted so that torque can be transmitted, and the fitting portion between the inner joint member and the shaft member is inserted into the shaft member. And a fixing portion that applies an axial load to the fitting portion is provided on the opposite side of the shaft member. Here, “the insertion side of the shaft member” means the side where the shaft member is inserted along the axial direction with respect to the inner joint member, and “the anti-insertion side of the shaft member” means the inner joint member. On the other hand, it means the opposite side to the side where the shaft member is inserted along the axial direction.

  In the present invention, the fitting portion between the inner joint member and the shaft member is disposed on the insertion side of the shaft member, and the fixing portion disposed on the non-insertion side of the shaft member is used to connect the shaft to the aforementioned fitting portion. Apply directional load. Due to the application of the axial load, the fitting portion can closely contact the fitting surface that forms an angle with the axial direction, thereby reducing axial and radial play.

  The fitting portion in the present invention is formed so that the hole of the inner joint member is opened in a tapered shape, a spline is formed in the tapered opening portion, and the outer peripheral surface of the shaft member is opposed to the tapered opening portion. A structure in which a spline is formed in the tapered portion and the spline of the inner joint member and the spline of the shaft member are fitted is desirable. In this way, the spline formed at the tapered opening portion of the inner joint member and the spline formed at the tapered portion of the shaft member can be tightly fitted by applying an axial load by the fixing portion. it can.

  Further, the fitting portion according to the present invention forms the concave and convex stripes radially at the opening end face portion of the hole of the inner joint member, and the concave and convex strips at the end face portion facing the opening end face portion of the flange formed on the outer periphery of the shaft member. May be a structure in which the concave and convex strips of the inner joint member and the concave and convex strips of the shaft member are fitted. In this way, the concave and convex strip formed on the opening end surface portion of the hole of the inner joint member and the concave and convex strip formed on the end surface portion of the flange of the shaft member are tightly fitted by applying an axial load by the fixing portion. Can be combined.

  The fixing portion in the present invention is preferably composed of a screw formed on the outer peripheral surface of the shaft member and a nut that fastens and fixes the inner joint member to the shaft member by screwing with the screw. If it does in this way, an axial load can be given to a fitting part by tightening and fixing an inner joint member to a shaft member with a nut.

  In addition, as for the nut in this invention, it is desirable that it is a self-locking nut. Here, the “self-locking nut” means a nut having a locking structure against vibration and the like. By using such a self-locking nut, the inner joint member is firmly fixed to the shaft member, and loosening due to vibration or the like can be prevented in advance.

  In the present invention, a structure in which a chamfer surface with which the nut abuts is formed at the opening end surface portion of the hole of the inner joint member is desirable. If it does in this way, it will become easy to give an axial load to a fitting part by making a nut contact a chamfer surface and screwing.

  Further, the fixing portion in the present invention forms an annular gap between the inner diameter of the inner joint member and the outer diameter of the shaft member, and presses the pushing member into the annular gap to thereby fix the inner joint member to the shaft member. It may be a fixed structure. If it does in this way, an axial load can be given to a fitting part by press-fitting a pushing member in the annular crevice between an inner joint member and a shaft member.

  The pushing member in the present invention is desirably press-fitted over the entire circumference of the annular gap. If it does in this way, an axial load can be equally provided over the perimeter of a fitting part by a pushing member. The pushing member may be press-fitted at a plurality of locations in the circumferential direction of the annular gap.

  In the present invention, a structure in which a chamfer surface with which the pushing member abuts is formed at the opening end surface portion of the hole of the inner joint member is desirable. If it does in this way, it will become easy to give an axial load to a fitting part by making a pushing member contact and touch a chamfer surface.

  In the outer joint member of the present invention, three track grooves extending in the axial direction are formed on the inner peripheral surface, and roller guide surfaces facing each other are formed on the inner wall of each track groove. It is a tripod member having three leg shafts, the tip of which is inserted into the track groove. The tripod member is rotatably supported by the leg shaft and is inserted into the track groove of the outer joint member to be guided along the roller guide surface. It is desirable to have a structure with rollers. That is, the present invention can be applied to a roller type tripod type constant velocity universal joint having the above-described structure.

  Further, in the outer joint member of the present invention, linear track grooves extending in the axial direction are formed at a plurality of locations on the inner peripheral surface, and the inner joint member has linear track grooves extending in the axial direction as track grooves of the outer joint member. A pair of balls formed at a plurality of locations on the outer peripheral surface and arranged between the track groove of the outer joint member and the track groove of the inner joint member, and the inner peripheral surface of the outer joint member and the outer peripheral surface of the inner joint member A structure having a cage for holding a ball interposed between the two and the like is desirable. That is, the present invention can be applied to a ball type double offset constant velocity universal joint having such a structure.

  According to the present invention, the fitting portion between the inner joint member and the shaft member is disposed on the insertion side of the shaft member, and the above-described fitting portion is provided by the fixing portion disposed on the opposite side of the shaft member. Axial load is applied to. Due to the application of the axial load, the fitting portion can closely contact the fitting surface that forms an angle with the axial direction, thereby reducing axial and radial play.

  As a result, the inner joint member and the shaft member can be tightly coupled to each other by a fitting means by a simple means without providing a twist angle in the spline as in the prior art. A constant velocity universal joint can be provided.

In embodiment of this invention, it is a principal part expanded sectional view which shows the coupling structure of an inner joint member and a shaft. It is a longitudinal cross-sectional view which shows the whole structure of the tripod type | mold constant velocity universal joint in embodiment of FIG. It is the arrow view seen from the A direction of FIG. It is a longitudinal cross-sectional view which shows the whole structure of the double offset type constant velocity universal joint in embodiment of FIG. It is the arrow view seen from the B direction of FIG. It is principal part expanded sectional drawing which shows the coupling structure of an inner joint member and a shaft in other embodiment of this invention. It is a longitudinal cross-sectional view which shows the whole structure of the tripod type | mold constant velocity universal joint in embodiment of FIG. It is a longitudinal cross-sectional view which shows the whole structure of the double offset type constant velocity universal joint in embodiment of FIG. It is principal part expanded sectional drawing which shows the coupling structure of an inner joint member and a shaft in other embodiment of this invention. It is a longitudinal cross-sectional view which shows the whole structure of the tripod type | mold constant velocity universal joint in embodiment of FIG. It is a longitudinal cross-sectional view which shows the whole structure of the double offset type constant velocity universal joint in embodiment of FIG. It is principal part expanded sectional drawing which shows the coupling structure of an inner joint member and a shaft in other embodiment of this invention. It is a longitudinal cross-sectional view which shows the whole structure of the tripod type | mold constant velocity universal joint in embodiment of FIG. It is a longitudinal cross-sectional view which shows the whole structure of the double offset type constant velocity universal joint in embodiment of FIG. It is a partial side view which shows the fixing | fixed part which uses a cyclic | annular pushing member. It is a partial side view which shows the fixing | fixed part which uses a rod-shaped pushing member.

  Embodiments of the sliding type constant velocity universal joint according to the present invention will be described in detail below. In the following embodiments, a roller type tripod type constant velocity universal joint and a ball type double offset type constant velocity universal joint will be exemplified. In addition to the single roller type tripod type constant velocity universal joint, the present invention can also be applied to a double roller type tripod type constant velocity universal joint capable of reducing vibration during operation.

  2 and 3 show a basic configuration of a roller type tripod type constant velocity universal joint, FIG. 2 is a longitudinal sectional view with respect to the axis of the joint, and FIG. 3 is an arrow view of the joint of FIG. (However, only one roller 30 is shown in cross section). As shown in FIGS. 2 and 3, the tripod type constant velocity universal joint according to this embodiment includes a main part including an outer joint member 10, an inner joint member 20 that is a tripod member, and a roller 30.

  The outer joint member 10 has a cup shape with one end opened, and three linear track grooves 11 extending in the axial direction are formed on the inner peripheral surface at equal intervals in the circumferential direction. Each track groove 11 has a pair of roller guide surfaces 12 opposed to each other on both inner walls thereof. The roller guide surface 12 has an arc-shaped cross section and extends linearly in the axial direction of the outer joint member 10. Inside the outer joint member 10, an inner joint member 20 and a roller 30 are accommodated so as to be slidable in the axial direction. The inner joint member 20 is formed by integrally forming three leg shafts 21 radially at equal intervals in the circumferential direction (120 ° intervals) on the outer peripheral surface of a cylindrical boss. The tip of the leg shaft 21 extends in the radial direction to the vicinity of the bottom of the track groove 11, and the outer peripheral surface thereof is generally a cylindrical surface.

  A roller 30 is rotatably disposed via a needle roller 40 between the roller guide surface 12 of the track groove 11 of the outer joint member 10 and the outer peripheral surface of the leg shaft 21. The outer peripheral surface of the roller 30 has an arc shape in vertical section, and may contact with the roller guide surface 12 at two locations by angular contact or contact at one location by circular contact. On the other hand, the inner peripheral surface of the roller 30 is formed in a cylindrical shape. A plurality of needle rollers 40 are disposed between the roller 30 and the leg shaft 21 in a so-called single row full roller state without a cage. The outer peripheral surface of the leg shaft 21 constitutes the inner rolling surface of the needle roller 40, and the inner peripheral surface of the roller 30 constitutes the outer rolling surface of the needle roller 40.

  4 and 5 show the basic configuration of a ball type double offset constant velocity universal joint, FIG. 4 is a longitudinal sectional view with respect to the axis of the joint, and FIG. 5 is an arrow view of the joint of FIG. is there. As shown in FIGS. 4 and 5, the double offset type constant velocity universal joint according to this embodiment includes an outer joint member 110, an inner joint member 120, a ball 130, and a cage 140.

  This constant velocity universal joint has a cup shape with one end opened, and an outer joint member 110 in which linear track grooves 111 extending in the axial direction are formed at a plurality of locations on the inner peripheral surface, and linear track grooves extending in the axial direction. 121 is formed between the track groove 111 of the outer joint member 110 and the track groove 121 of the inner joint member 120. And a cage 140 that is interposed between the inner peripheral surface of the outer joint member 110 and the outer peripheral surface of the inner joint member 120 and holds the ball 130.

  In this embodiment, a six-ball constant velocity universal joint (see FIG. 5) is illustrated, but the present invention can also be applied to an eight-ball constant velocity universal joint, and the number of balls 130 is arbitrary. Inside the outer joint member 110, an inner joint member 120, a ball 130, and a cage 140 are accommodated so as to be axially slidable.

  In the tripod type constant velocity universal joint of FIG. 2 and the double offset type constant velocity universal joint of FIG. 4, shafts 50 and 150 as shaft members are coupled to the holes 22 and 122 of the inner joint members 20 and 120 with the following structure. Has been. The coupling structure between the inner joint members 20 and 120 and the shafts 50 and 150 will be described below in common for the tripod type constant velocity universal joint and the double offset type constant velocity universal joint.

  In the coupling structure of the inner joint members 20, 120 and the shafts 50, 150, as shown in FIGS. 2 and 4, the fitting portions 60, 160 between the inner joint members 20, 120 and the shafts 50, 150 are connected to the shaft 50, 150 is arranged on the insertion side (left side in the figure), and fixing parts 70 and 170 for applying an axial load to the fitting parts 60 and 160 are arranged on the opposite insertion side (right side in the figure) of the shafts 50 and 150. Set up.

  In this coupling structure, after the shaft end portions 51 and 151 of the shafts 50 and 150 are inserted into the holes 22 and 122 of the inner joint members 20 and 120 and connected by the fitting portions 60 and 160 so that torque can be transmitted, the outer joint member An axial load is applied to the fitting parts 60 and 160 by the fixing parts 70 and 170 located on the back side of the 10,110. Therefore, the coupling structure of the inner joint members 20 and 120 and the shafts 50 and 150 has the shafts 50 and 150 in the holes 22 and 122 of the inner joint members 20 and 120 to which the rollers 30 (the balls 130 and the cage 140) are attached. After assembling by inserting and fitting, the assembly can be realized by assembling the sliding constant velocity universal joint in which the assembly body is accommodated in the outer joint members 10 and 110. The connecting operation between the inner joint members 20 and 120 and the shafts 50 and 150 is performed before the assembly body is accommodated in the outer joint members 10 and 110.

  As shown in FIG. 1, the fitting portions 60 and 160 in the coupling structure of the inner joint members 20 and 120 and the shafts 50 and 150 open the holes 22 and 122 of the inner joint members 20 and 120 in a tapered shape, Splines 23 and 123 are formed in a tapered opening portion whose diameter increases toward the outside in the axial direction (left side in the figure), and the shafts 50 and 150 are formed so as to face the tapered opening portion on the outer peripheral surface. Splines 53 and 153 are formed in tapered portions that expand toward the outside in the direction (left side in the figure), and the splines 23 and 123 of the inner joint members 20 and 120 and the splines 53 and 153 of the shafts 50 and 150 are fitted. The structure is provided. These splines 23 and 123 and splines 53 and 153 are ridges extending in the axial direction.

  Further, the fixing portions 70 and 170 in the coupling structure of the inner joint members 20 and 120 and the shafts 50 and 150 include screws 52 and 152 formed on the outer peripheral surfaces of the shaft end portions 51 and 151 of the shafts 50 and 150, and The nuts 72 and 172 are configured to fasten and fix the inner joint members 20 and 120 to the shafts 50 and 150 by screwing with the screws 52 and 152. Furthermore, chamfer surfaces 24 and 124 with which the nuts 72 and 172 abut are formed at the open end surface portions of the holes 22 and 122 of the inner joint members 20 and 120.

  In the nuts 72 and 172, chamfer surfaces 74 and 174 are formed at portions facing the chamfer surfaces 24 and 124 of the inner joint members 20 and 120. Thus, the nuts 72 and 172 can be stably pushed in by bringing the chamfer surfaces 74 and 174 of the nuts 72 and 172 into contact with the chamfer surfaces 24 and 124 of the inner joint members 20 and 120.

  In the coupling structure of the inner joint members 20 and 120 and the shafts 50 and 150, the shaft end portions 51 and 151 of the shafts 50 and 150 are inserted into the holes 22 and 122 of the inner joint members 20 and 120, and the inner joint members 20 and 120 are inserted. The splines 53 and 153 of the tapered portions of the shafts 50 and 150 are fitted into the splines 23 and 123 of the 120 tapered opening portions. In this manner, the fitting portions 60, 160 between the inner joint members 20, 120 and the shafts 50, 150 are disposed on the insertion side of the shafts 50, 150.

  Then, nuts 72 and 172 are screwed onto the screws 52 and 152 of the shaft end portions 51 and 151 of the shafts 50 and 150, and the inner joint members 20 and 120 are attached to the shafts 50 and 150 by the nuts 72 and 172. Tighten and fix. At this time, the nuts 72 and 172 are pushed in with the chamfer surfaces 74 and 174 of the nuts 72 and 172 in contact with the chamfer surfaces 24 and 124 of the inner joint members 20 and 120. An axial load is applied to the aforementioned fitting portions 60 and 160 by tightening and fixing with the nuts 72 and 172. In this manner, the fixing portions 70 and 170 that apply the axial load to the fitting portions 60 and 160 are disposed on the opposite side of the shafts 50 and 150.

  The splines 23 and 123 formed at the tapered opening portions of the inner joint members 20 and 120 are fitted to the splines 53 and 153 formed at the tapered portions of the shafts 50 and 150, and the inner joints are formed by the nuts 72 and 172. The members 20 and 120 are fastened and fixed to the shafts 50 and 150. By applying an axial load to the fitting portions 60 and 160 by tightening the nuts 72 and 172, the fitting portions 60 and 160 have splines 23 and 123 and splines 53 that form an angle (taper angle) with the axial direction. , 153 can be brought into close contact with each other to reduce backlash in the axial direction and the radial direction, and the inner joint members 20, 120 and the shafts 50, 150 can be tightly coupled. In addition, in the fitting parts 60 and 160, if the width dimension of the protruding line in the splines 23 and 123 and the splines 53 and 153 is set larger than the width dimension of the recessed line, the inner joint members 20 and 120 and the shafts 50 and 150 Can be fitted more tightly.

  In the above embodiment, the splines 23 and 123 are formed in the tapered opening portions of the inner joint members 20 and 120 and the splines 53 and 153 are formed in the tapered portions of the shafts 50 and 150. 6 may be the fitting portions 61 and 161 having the structure shown in FIG. The fitting portions 61 and 161 are formed with ridges 25 and 125 radially at the opening end surface portions of the holes 22 and 122 of the inner joint members 20 and 120, and flanges 54 and 150 formed on the outer circumferences of the shafts 50 and 150. The concave and convex strips 55 and 155 are formed radially on the end surface portion of the 154, and the concave and convex strips 25 and 125 of the inner joint members 20 and 120 and the concave and convex strips 55 and 155 of the shafts 50 and 150 are fitted.

  7 illustrates a case where it is applied to a tripod type constant velocity universal joint, and FIG. 8 illustrates a case where it is applied to a double offset type constant velocity universal joint. 7 and FIG. 8, the same parts as those in FIG. 2 and FIG.

  As described above, the concave and convex strips 25 and 125 formed at the opening end surface portions of the holes 22 and 122 of the inner joint members 20 and 120 and the concave and convex strips 55 and 155 formed at the end surface portions of the flanges 54 and 154 of the shafts 50 and 150 are formed. And the inner joint members 20 and 120 are fastened and fixed to the shafts 50 and 150 by the nuts 72 and 172, thereby applying an axial load to the fitting portions 61 and 161. In the portions 61 and 161, the fitting surfaces of the concave and convex strips 25 and 125 and the concave and convex strips 55 and 155 that form an angle (90 °) with the axial direction can be in close contact with each other to reduce axial and radial play. The joint members 20 and 120 and the shafts 50 and 150 can be tightly coupled. In the fitting portions 61 and 161, the inner joint members 20 and 120 and the shaft 50, if the width of the projections on the projections and depressions 25 and 125 and the projections and depressions 55 and 155 are set larger than the width of the depressions. 150 can be fitted more tightly.

  The nuts 72 and 172 of the fixing portions 70 and 170 shown in FIG. 1 have a general structure in which only an internal thread is engraved on the inner diameter, but the nuts 72 and 172 shown in FIG. As described above, the self-locking nuts 73 and 173 may be used. The self-locking nuts 73 and 173 are nuts having a structure for preventing loosening against vibrations. By using such self-locking nuts 73 and 173, the inner joint members 20 and 120 are firmly fixed to the shafts 50 and 150, and loosening due to vibration or the like can be prevented in advance. There are various types of self-locking nuts 73 and 173 such as a structure in which a nylon ring or a caulking plate is added to a female screw.

  10 illustrates a case where it is applied to a tripod type constant velocity universal joint, and FIG. 11 illustrates a case where it is applied to a double offset type constant velocity universal joint. In FIG. 10 and FIG. 11, the same parts as those in FIG. 2 and FIG. Further, the self-locking nuts 73 and 173 described above are applied not only to the fitting portions 60 and 160 shown in FIG. 9 but also to the fitting portions 61 and 161 having the structure shown in FIG. Is possible.

  In the above-described embodiment, the shaft ends 51 and 151 of the shafts 50 and 150 are constituted by the screws 52 and 152 and the nuts 72 and 172 (self-locking nuts 73 and 173) screwed to the screws 52 and 152. Although the fixing portions 70 and 170 have been described, the fixing portions 71 and 171 having the structure shown in FIG. 12 may be used instead of the screws 52 and 152 and the nuts 72 and 172 (self-locking nuts 73 and 173).

  The fixing portions 71 and 171 are formed by forming an annular gap m between the inner diameter of the inner joint members 20 and 120 and the outer diameter of the shafts 50 and 150, and press-fitting the pushing members 75 and 175 into the annular gap m. The inner joint members 20 and 120 are fixed to the shafts 50 and 150. Furthermore, chamfer surfaces 26 and 126 with which the pushing members 75 and 175 abut are formed at the open end portions of the holes 22 and 122 of the inner joint members 20 and 120. Chamfer surfaces 76, 176 are also formed on the pushing members 75, 175. As described above, the chamfer surfaces 76 and 176 of the push-in members 75 and 175 are brought into contact with the chamfer surfaces 26 and 126 of the inner joint members 20 and 120, whereby the push-in members 75 and 175 are stably pushed in by the wedge action. It becomes possible.

  The splines 23 and 123 formed at the tapered opening portions of the inner joint members 20 and 120 and the splines 53 and 153 formed at the tapered portions of the shafts 50 and 150 are fitted, and the pushing members 75 and 175 are annularly formed. The inner joint members 20 and 120 are fixed to the shafts 50 and 150 by press-fitting into the gap m, thereby applying an axial load to the fitting portions 60 and 160. Thereby, in the fitting parts 60 and 160, the fitting surfaces of the splines 23 and 123 and the splines 53 and 153 forming an angle with the axial direction (taper angle) are in close contact to reduce axial and radial play. The inner joint members 20 and 120 and the shafts 50 and 150 can be tightly coupled.

  13 illustrates a case where the present invention is applied to a tripod type constant velocity universal joint, and FIG. 14 illustrates a case where the present invention is applied to a double offset type constant velocity universal joint. In FIG. 13 and FIG. 14, the same parts as those in FIG. 2 and FIG. Further, the pushing members 75 and 175 described above can be applied not only to the fitting portions 60 and 160 shown in FIG. 12 but also to the fitting portions 61 and 161 having the structure shown in FIG. It is.

  Further, the above-described fixing portions 71 and 171 have a structure in which annular pushing members 75 and 175 are press-fitted over the entire circumference of the annular gap m (see FIG. 15). By using the annular pushing members 75 and 175 in this way, the axial load can be uniformly applied over the entire circumference of the fitting portions 60 and 160 by the pushing members 75 and 175. As shown in FIG. 16, the other fixing portions 71 and 171 have a structure in which rod-like pushing members 77 and 177 are press-fitted into a plurality of circumferential positions (four locations in the figure) of the annular gap m. It is also possible.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

10, 110 Outer joint member 20, 120 Inner joint member 22, 122 Hole 23, 123 Spline 24, 124 Chamfer surface 25, 125 Concavity and convexity 26, 126 Chamfer surface 50, 150 Shaft member (shaft)
52,152 Screw 53,153 Spline 55,155 Concavity and convexity 60,160 Fitting part 61,161 Fitting part 70,170 Fixing part 71,171 Fixing part 72,172 Nut 73,173 Self-locking nut 75,175 Pushing member m Annular gap

Claims (12)

  An outer joint member and an inner joint member that transmits torque while allowing axial displacement and angular displacement between the outer joint member and inserting the shaft member into the hole of the inner joint member to transmit torque A sliding type constant velocity universal joint that is fitted to each other, wherein a fitting portion between the inner joint member and the shaft member is disposed on an insertion side of the shaft member, and an axial load is applied to the fitting portion. A sliding type constant velocity universal joint, characterized in that a fixing portion for imparting a pressure is disposed on the opposite side of the shaft member.   The fitting portion is formed such that the hole of the inner joint member is opened in a tapered shape, a spline is formed in the tapered opening portion, and the outer peripheral surface of the shaft member is opposed to the tapered opening portion. The sliding constant velocity universal joint according to claim 1, wherein a spline is formed in a tapered portion, and the spline of the inner joint member and the spline of the shaft member are fitted.   The fitting portion radially forms concave and convex strips on the opening end surface portion of the hole of the inner joint member, and radially forms concave and convex strips on the end surface portion of the flange formed on the outer periphery of the shaft member. The sliding type constant velocity universal joint according to claim 1, wherein the concave and convex strips of the inner joint member and the concave and convex strips of the shaft member are fitted to each other.   The said fixing | fixed part is comprised with the screw formed in the outer peripheral surface of a shaft member, and the nut which clamp | tightens and fixes an inner joint member with respect to a shaft member by screwing with the said screw. A sliding type constant velocity universal joint according to claim 1.   The sliding type constant velocity universal joint according to claim 4, wherein the nut is a self-locking nut.   The sliding type constant velocity universal joint according to claim 4 or 5, wherein a chamfer surface with which the nut abuts is formed at an opening end portion of the hole of the inner joint member.   The fixing portion forms an annular gap between the inner diameter of the inner joint member and the outer diameter of the shaft member, and fixes the inner joint member to the shaft member by press-fitting a pushing member into the annular gap. The sliding type constant velocity universal joint as described in any one of Claims 1-3.   The sliding type constant velocity universal joint according to claim 7, wherein the pushing member is press-fitted over the entire circumference of the annular gap.   The sliding type constant velocity universal joint according to claim 7, wherein the push-in member is press-fitted into a plurality of locations in the circumferential direction of the annular gap.   The sliding type constant velocity universal joint according to any one of claims 7 to 9, wherein a chamfer surface with which the pushing member abuts is formed at an opening end portion of the hole of the inner joint member.   In the outer joint member, three track grooves extending in the axial direction are formed on the inner peripheral surface, and roller guide surfaces facing each other are formed on the inner side wall of each track groove. A tripod member having three leg shafts inserted into the track groove, rotatably supported by the leg shaft, and inserted into the track groove of the outer joint member to be guided along the roller guide surface. The sliding type constant velocity universal joint according to claim 1, further comprising a roller.   In the outer joint member, linear track grooves extending in the axial direction are formed at a plurality of locations on the inner peripheral surface, and in the inner joint member, the linear track grooves extending in the axial direction are paired with the track grooves of the outer joint member. The ball formed between the track groove of the outer joint member and the track groove of the inner joint member, the inner peripheral surface of the outer joint member, and the outer peripheral surface of the inner joint member. A sliding type constant velocity universal joint according to any one of claims 1 to 10, further comprising a cage interposed between the cage and the cage for holding the ball.

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