JP5331658B2 - Tapered roller bearing preload adjustment mechanism - Google Patents

Description

  The present invention relates to a preload adjusting mechanism for a tapered roller bearing.

  As a conventional preload adjusting mechanism for a tapered roller bearing, an outer ring of the tapered roller bearing and an adjusting nut for adjusting an axial load applied to the outer ring of the tapered roller bearing (hereinafter referred to as “preload”) are integrated. After adjusting the preload, there is a type in which the adjusting nut is fixed to a differential carrier (hereinafter referred to as “diff carrier”) with a non-rotating member to restrict the rotation of the adjusting nut (for example, see Patent Document 1).

JP 2001-336606 A

  In the conventional preload adjusting mechanism of the tapered roller bearing described above, a plurality of positioning holes are formed in the adjusting nut, and a detent member is inserted into one of the positioning holes and screwed to the differential carrier. Thus, the adjusting nut was fixed to the differential carrier, and the rotation of the adjusting nut was restricted.

  However, when such a positioning hole is formed in the adjusting nut, it is difficult to narrow the interval between the adjacent positioning holes due to the rigidity of the adjusting nut, manufacturing tolerances, and the like. Therefore, there is a problem that fine adjustment cannot be performed when fixing the adjusting nut, and an appropriate preload cannot be applied to the adjusting nut.

  The present invention has been made paying attention to such a problem, and an object thereof is to apply an appropriate preload to an adjusting nut.

  The present invention is a preload adjusting device for a taper roller bearing that rotatably supports a rotating body housed in a support body including a cylindrical portion having an internal thread formed on an inner peripheral surface thereof with respect to the cylindrical portion. A male screw and a plurality of grooves having a V-shaped cross section are formed on the outer peripheral surface, and the male screw is screwed into a female screw formed on the inner peripheral surface of the cylindrical portion to preload the tapered roller bearing. An adjusting nut to be added, and when the adjusting nut is screwed into the inner peripheral surface of the cylindrical portion, it is formed to penetrate from the outer peripheral surface of the cylindrical portion toward the inner peripheral surface so as to open into the groove. A screw hole, a ball that is fitted into the groove through the screw hole, and a bolt that is screwed into the screw hole and presses the ball against the groove to restrict rotation of the adjusting nut. Features .

  According to the present invention, a plurality of grooves having a V-shaped cross section are formed on the outer peripheral surface of the adjusting nut, and the adjusting nut is fixed to the support body by fitting a ball into the groove and tightening with a bolt. Unlike the case of forming the positioning hole in the adjusting nut, the V-shaped groove can be continuously provided in the outer peripheral surface of the adjusting nut along the circumferential direction. For this reason, the interval between adjacent grooves can be narrowed, and fine adjustment can be performed when fixing the adjusting nut, so that an appropriate preload can be applied to the adjusting nut.

It is the schematic of the power train of the vehicle provided with the final deceleration differential apparatus by this embodiment. It is sectional drawing of the final deceleration differential apparatus by this embodiment. It is a perspective view of an adjusting nut. FIG. 3 is an enlarged view of a portion surrounded by a broken line in FIG. 2. It is VV sectional drawing of FIG. It is a figure explaining the reason the preload adjustment mechanism of the side bearing by this embodiment can make an adjustment rotation angle smaller than a comparative example. It is sectional drawing of the final deceleration differential apparatus by a comparative example. It is an enlarged view of the part enclosed with the broken line of FIG. It is an IX-IX arrow line view of FIG.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 is a schematic diagram of a power train of a vehicle provided with a final deceleration differential 1 according to the present embodiment.

  Engine 100 is mounted in front of the vehicle in a vertically placed state to generate driving force.

  The transmission 101 is mounted behind the engine 100 via the clutch 102. The transmission 101 increases and decelerates the rotation of the engine 100 input from the input shaft 103 at a speed ratio corresponding to the selected shift speed, and outputs it from the output shaft 104.

  The propeller shaft 105 connects the output shaft 104 and the final reduction differential 1 and transmits the rotation of the output shaft 104 to the final reduction differential 1.

  The final deceleration differential 1 is mounted at the rear of the vehicle. The final reduction gear differential 1 is an integration of the final reduction gear device 3 (see FIG. 2) and the differential device 4 (see FIG. 2). Is transmitted to the shaft 106. Further, when it is necessary to create a speed difference between the rotational speeds of the left and right axle shafts 106, such as during a curve run, the speed difference is automatically given to enable smooth running. Rear wheels 107 are attached to the front ends of the left and right axle shafts 106, respectively. Details of the final deceleration differential 1 will be described below with reference to FIG.

  FIG. 2 is a cross-sectional view of the final reduction differential 1.

  The final reduction gear differential 1 includes a differential carrier (support) 2, a final reduction gear 3, and a differential gear 4.

  The differential carrier 2 is a case made of cast iron or aluminum alloy to which the final reduction gear 3 and the differential gear 4 are assembled.

  The final reduction gear 3 includes a drive pinion 31 and a ring gear 32.

  The drive pinion 31 includes a drive pinion shaft 311 and a drive pinion gear 312.

  The tip 311a of the drive pinion shaft 311 is connected to the propeller shaft 105 (see FIG. 1). The drive pinion shaft 311 is rotated by the propeller shaft 105.

  The drive pinion shaft 311 is rotatably supported with respect to the differential carrier 2 by two drive pinion bearings 33 and one pilot bearing 34. Each of the drive pinion bearings 33 is a tapered roller bearing and supports the central portion 311b of the drive pinion shaft 311. The pilot bearing 34 is a roller bearing and supports the rear end 311 c of the drive pinion shaft 311.

  The drive pinion gear 312 is a bevel gear and rotates together with the drive pinion shaft 311.

  The ring gear 32 is a bevel gear having more teeth than the drive pinion gear 312 and meshes with the drive pinion gear 312 so as to intersect at right angles.

  The final reduction gear 3 is configured as described above to increase the driving force by lowering the rotational speed of the ring gear 32 than the rotational speed of the drive pinion 31, and to the rotational axis direction that was in the vehicle longitudinal direction up to the drive pinion 31 Is converted into the vehicle left-right direction.

  The differential device 4 includes a differential case (hereinafter referred to as “difference case”) (rotary body) 41, a pinion shaft 42, two pinion gears 43, and two side gears 44.

  The differential case 41 includes a central base portion 41a, and a cylindrical axle shaft insertion portion 41b that protrudes left and right from the base portion 41a and into which the axle shaft 106 is inserted.

  The ring gear 32 is fixed to the central base portion 41a by a bolt 45. The differential carrier 2 is formed with a cylindrical portion (hereinafter referred to as “diff carrier cylindrical portion”) 21 for supporting the axle shaft insertion portion 41b. The axle shaft insertion portion 41b is connected to the differential carrier cylindrical portion 21 on the side. It is supported via a bearing 46. That is, the differential case 41 is rotatably supported with respect to the differential carrier 2 and rotates integrally with the ring gear 32.

  The side bearing 46 includes an annular inner ring 461, an annular outer ring 462 having a larger diameter than the inner ring 461, and a cylindrical roller 463 that rolls in contact with the outer peripheral surface of the inner ring 461 and the inner peripheral surface of the outer ring 462. These are tapered roller bearings.

  The pinion shaft 42 is fixed to the base 41 a of the differential case 41 and rotates integrally with the differential case 41. The pinion shaft 42 is attached so that the two pinion gears 43 face each other and can freely rotate around the axis of the pinion shaft 42. That is, the two pinion gears 43 rotate (revolve) around the axis of the axle shaft 106 together with the pinion shaft 42 when the ring gear 32 rotates, and can rotate (rotate) around the axis of the pinion shaft 42 as necessary. It is attached to the pinion shaft 42. The pinion gear 43 is a bevel gear.

  The side gear 44 is a bevel gear, and is attached to the base end portions of the left and right axle shafts 106 so as to face each other. The side gears 44 mesh with the two pinion gears 43 and are rotated by the pinion gears 43.

  The differential device 4 is configured as described above, and when the ring gear 32 is rotated by the drive pinion 31, the differential case 41 to which the ring gear 32 is fixed and the pinion shaft 42 fixed to the differential case 41 are integrated. Rotate. Then, the side gear 44 is rotated by the pinion gear 43 attached to the pinion shaft 42, and the left and right axle shafts 106 are rotated.

  When there is no speed difference between the rotational speeds of the left and right axle shafts 106, such as when the vehicle is traveling straight, the pinion gear 43 revolves around the side gear 44 and rotates the side gear 44 without rotating. On the other hand, when it is necessary to create a speed difference between the rotational speeds of the left and right axle shafts 106, such as when the vehicle is traveling on a curve, the pinion gear 43 revolves around the side gear 44 while rotating the side gear 44. Spins and causes the speed difference.

  Here, an annular adjusting nut 51 for applying a preload (axial load) to the outer ring 462 of the side bearing 46 is attached to the inner peripheral surface of the differential carrier cylindrical portion 21. The adjusting nut 51 applies a preload to the outer ring 462 of the side bearing 46 to reduce the radial gap between the roller 463 and the inner ring 461 and between the roller 463 and the outer ring 462, thereby suppressing rotational vibration and rotating the differential case 41 smoothly. It is. Hereinafter, the preload adjusting mechanism 5 of the side bearing 46 including the adjusting nut 51 will be described in detail with reference to FIGS. 3 to 5 in addition to FIG. 2.

  FIG. 3 is a perspective view of the adjusting nut 51.

  As shown in FIG. 3, the adjusting nut 51 has a male screw portion 511 having a male screw formed on the outer peripheral surface and a V-shaped cross section (hereinafter referred to as “V groove”) 52 at a regular interval. A groove portion 512 formed continuously in the direction.

  FIG. 4 is an enlarged view of a portion surrounded by a broken line in FIG. 5 is a cross-sectional view taken along the line VV in FIG.

  As shown in FIG. 4, the adjusting nut 51 is configured such that the male screw formed on the male screw portion 511 is screwed to the female screw 211 formed on the inner peripheral surface of the differential carrier cylindrical portion 21, thereby It is attached to the part 21. The amount of preload applied to the side bearing 46 is adjusted by adjusting the screwing amount of the adjusting nut 51 to the differential carrier cylindrical portion 21.

  The differential carrier cylindrical portion 21 is formed with a threaded hole 53 that opens into the groove portion 512 of the adjusting nut 51 when the adjusting nut 51 is screwed together. The screw hole 53 is formed from the outer peripheral surface of the differential carrier cylindrical portion 21 toward the inner peripheral surface.

  4 and 5, the ball 54 is fitted into the V groove 52 from the screw hole 53 formed in the differential carrier cylindrical portion 21, and then the bolt 55 is screwed into the screw hole 53 so that the ball 54 is screwed. Press against the tapered surface 52 a of the V-groove 52. As a result, the adjusting nut 51 is prevented from being loosened, and the adjusting nut 51 is finally fixed to the differential carrier cylindrical portion 21. That is, the preload adjusting mechanism 5 of the side bearing 46 according to the present embodiment includes the V groove 52 formed on the outer peripheral surface of the adjusting nut 51, the ball 54 inserted from the screw hole 53 into the V groove 52, and the screw hole 53. The adjusting nut 51 is prevented from being loosened by the bolt 55 that is screwed into the V groove 52 and screwed into the V groove 52.

  Here, in order to facilitate understanding of the present invention, the configuration of the final reduction differential 1 according to the comparative example will be described before describing the operation and effect of the preload adjusting mechanism 5 of the side bearing 46 according to the present embodiment. In addition, the part which fulfill | performs the same function is demonstrated using the same code | symbol.

  FIG. 7 is a sectional view of the final reduction differential 1 according to the comparative example. FIG. 8 is an enlarged view of a portion surrounded by a broken line in FIG. 9 is a view taken in the direction of arrows IX-IX in FIG.

  As shown in FIGS. 7 to 9, the final reduction differential 1 according to the comparative example is different from the present embodiment in the shape of the adjusting nut 51 and the mechanism for preventing the adjusting nut 51 from loosening.

  As shown in FIG. 8, the adjusting nut 51 of the comparative example has a male screw portion 511 in the entire outer peripheral surface. On the other hand, as shown in FIG. 9, grooves having a rectangular cross section (hereinafter referred to as “rectangular grooves”) 56 are formed at equal intervals over the entire inner peripheral surface of the adjusting nut 51. Then, the male screw formed on the male screw portion 511 of the adjusting nut 51 is screwed into the female screw 211 formed on the inner peripheral surface of the differential carrier cylindrical portion 21, thereby being attached to the differential carrier cylindrical portion 21.

  Thereafter, the claw portion 57a of the U-shaped lock plate 57 is caught in the rectangular groove 56 of the adjusting nut 51 to prevent the adjusting nut 51 from loosening. The lock plate 57 is fixed to the side surface of the differential carrier cylindrical portion 21 by bolts 58. A screw hole 59 for screwing the bolt 58 is formed on the side surface of the differential carrier cylindrical portion 21.

  In other words, the preload adjusting mechanism 5 of the side bearing 46 according to the comparative example includes a rectangular groove 56 formed on the inner peripheral surface of the adjusting nut 51 and a lock plate 57 that restricts the rotation of the adjusting nut 51 by being hooked on the rectangular groove 56. And the adjusting nut 51 is prevented from being loosened by the bolt 58 that fixes the lock plate 57 to the differential carrier cylindrical portion 21.

  Here, when the adjusting nut 51 is fixed to the differential carrier cylindrical portion 21, in both the present embodiment and the comparative example, the adjusting nut 51 is temporarily applied to the side bearing 46 with an appropriate preload (hereinafter referred to as “appropriate preload”). .) Is tightened to a position where the adjusting nut 51 can be fixed (hereinafter referred to as a “fixable position”). It is necessary to rotate again in the direction of loosening.

  In the present embodiment, the fixable position is a position where the ball 54 can be fitted into the V groove 52 from the screw hole 53. On the other hand, in the case of the comparative example, the lock plate 57 can be fixed by hooking the claw portion 57a of the lock plate 57 into the rectangular groove 56.

  When the rotation angle from the proper tightening position to the fixable position (hereinafter referred to as “adjustment rotation angle”) is increased, the preload applied to the side bearing 46 is correspondingly larger or smaller than the proper preload. If the preload applied to the side bearing 46 is larger than the appropriate preload, a large load is applied to the roller 463 and the like, so that the deterioration of the side bearing 46 is accelerated. On the other hand, if the preload applied to the side bearing 46 is smaller than the appropriate preload, the radial gap becomes large and rotational vibration becomes large.

  In order to reduce the adjustment rotation angle, the number of grooves (V grooves 52 and rectangular grooves 56) formed in the adjusting nut may be increased.

  However, in the comparative example, it is difficult to increase the number of the grooves as compared with the present embodiment, and the adjustment rotation angle is increased as compared with the present embodiment. In other words, the preload adjusting mechanism 5 of the side bearing 46 according to the present embodiment can make the adjustment rotation angle smaller than that of the comparative example. The reason will be described with reference to FIG.

  FIG. 6 is a diagram for explaining the reason why the preload adjusting mechanism 5 of the side bearing 46 according to the present embodiment can make the adjustment rotation angle smaller than that of the comparative example.

  As shown in FIG. 6A, in the case of the comparative example, the width of the rectangular groove 56 is made larger than the width of the claw portion 57a of the lock plate 57, and a gap is formed between the lock plate 57 and the adjusting nut 51. It is necessary to provide. Since the number of the rectangular grooves 56 can be increased as the gap is reduced, the adjustment rotation angle can be reduced.

  However, because of the manufacturing method of the adjusting nut 51 (for example, casting), the width of the rectangular groove 56 varies, so that the rectangular groove 56 has a certain margin with respect to the width of the claw portion 57a of the lock play 57. It is necessary to determine the width of. Therefore, it is difficult to reduce the width of the rectangular grooves 56 and it is difficult to increase the number of rectangular grooves 56. Therefore, it is difficult to reduce the adjustment rotation angle.

  On the other hand, as shown in FIG. 6B, in the case of the present embodiment, even if the variation occurs and the inclination of the tapered surface 52a of the V-groove 52 changes, the variation is absorbed by the drop amount of the ball 54. Thus, the adjusting nut 51 can be fixed. That is, even if the width of the V-groove 52 is enlarged or reduced due to the variation, the ball 54 can be adjusted, so that the width of the V-groove 52 can be made smaller than the width of the rectangular groove 56. Therefore, the preload adjusting mechanism 5 of the side bearing 46 according to the present embodiment can increase the number of grooves formed in the adjusting nut 51 as compared with the comparative example, and can reduce the adjustment rotation angle.

  According to the preload adjusting mechanism 5 of the side bearing 46 according to the present embodiment described above, the number of V grooves 52 formed in the adjusting nut 51 can be increased as compared with the comparative example. Therefore, the adjustment rotation angle when adjusting the adjusting nut 51 from the proper tightening position to the fixable position can be reduced. Therefore, since the preload applied to the side bearing 46 can be brought close to the appropriate preload, the deterioration of the side bearing 46 can be suppressed and the rotational vibration can be suppressed.

  In the case of the comparative example, when the preload amount applied to the side bearing 46 is readjusted, the bolt 58 is once extracted from the screw hole 59 and the lock plate 57 is removed, and then the adjusting nut 51 is rotated and locked again. It is necessary to fix the plate 57 with bolts 58. On the other hand, in the case of this embodiment, the adjusting nut 51 can be rotated only by loosening the bolt 55. Therefore, the preload amount can be readjusted easily.

  Note that the present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea.

  For example, in the present embodiment, the preload adjusting mechanism 5 is applied to adjust the preload of the side bearing 46 of the final reduction differential 1, but is applied to adjust the preload of any tapered roller bearing that supports the rotating body. it can.

  In the present embodiment, the V-groove 52 is formed on the outer peripheral surface of the adjusting nut 51, but the shape is not limited to this and may be a conical shape.

2 Differential carrier (support)
5 Preload adjustment mechanism 21 Differential carrier cylindrical part (cylindrical part)
41 Differential case (rotating body)
41b Axle shaft insertion part 46 Side bearing (taper roller bearing)
51 Adjusting nut 52 V groove (groove)
53 Screw hole 54 Ball 55 Bolt 106 Axle shaft 211 Female screw 511 Male screw part (Male screw)

Claims (2)

A taper roller bearing preload adjustment mechanism for rotatably supporting a rotating body housed in a support body including a cylindrical portion having an internal thread formed on an inner peripheral surface thereof, with respect to the cylindrical portion,
An adjuster for preloading the tapered roller bearing by forming a male screw and a plurality of grooves having a V-shaped cross section on the outer peripheral surface, and screwing the male screw into a female screw formed on the inner peripheral surface of the cylindrical portion. A sting nut,
When the adjusting nut is screwed into the inner peripheral surface of the cylindrical portion, a screw hole formed so as to penetrate from the outer peripheral surface of the cylindrical portion toward the inner peripheral surface so as to open to the groove;
A ball fitted into the groove through the screw hole;
A bolt that is screwed into the screw hole and presses the ball against the groove to restrict rotation of the adjusting nut;
A preload adjusting mechanism for a taper roller bearing. The rotating body is a differential case of a final reduction differential equipped with a cylindrical axle shaft insertion portion for inserting an axle shaft,
The support is a differential carrier of a final reduction differential that supports the axle shaft insertion portion via the tapered roller bearing.
The preload adjusting mechanism for a tapered roller bearing according to claim 1.

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