JP5912336B2 - Differential equipment - Google Patents

Description

  The present invention relates to a differential device used for an automobile or the like.

2. Description of the Related Art Conventionally, there is a differential device in which a leaf spring bent between side gears is interposed in order to obtain initial torque. (Patent Document 1)
In this differential device, the back surface of the side gear biased by the leaf spring slides against the inner surface side of the differential device during differential rotation to generate initial torque.

  However, in such a conventional differential device, the back surface of the side gear that slides during differential rotation and the inner surface of the differential case are flat surfaces orthogonal to the rotation axis of the side gear. If the size is not increased, the increase in the friction radius is limited, which is disadvantageous for wear resistance.

  In addition, since the spring force of the leaf spring is proportional to the differential limiting force, it is necessary to increase the spring force accordingly in order to generate the initial torque required by such a surface. There was a problem with sex.

US7270026 Publication

  The problem to be solved is that unless the size of the device is increased, the increase in the friction radius is limited, which is disadvantageous in terms of wear resistance, and in order to generate the necessary initial torque, the spring force is accordingly increased. There is a problem in the formation and durability of the spring.

In the present invention, in order to facilitate the formation of the spring and to improve the durability, the differential case that is rotatably supported and the pinion shaft that is rotatably supported in the differential case A pinion gear and a pair of side gears rotatably supported in the differential case and meshing with the pinion gear, and the pinion gear and the side gear on the inner surface of the differential case. Spherical pinion gear recesses that form opposing spherical convex back portions and support the spherical convex back portions of the pinion gear and side gear on the inner surface of the differential case so as to be able to rotate and slide. the support surface portion and side gears concave support surface forming a spring is interposed between the side gears, said side gears, the fitting convex portion of the rotation axis around provided, wherein the spring member Integrally includes spring end facing said side gears, said spring end, a fitting hole to be fitted into the fitting convex portion is provided, the spherical convex rear portion of the side gears The side gear concave support surface portion is biased.

  Since the invention of the present application is configured as described above, the spherical convex back surface portion of the side gear that is slidably contacted by the biasing force of the spring member has a structure that is in sliding contact with the spherical side gear concave support surface portion of the differential case. Even if the size of the device is not increased, the setting to increase the friction radius is easy, the wear resistance is improved, and the spring force of the spring member can be set low, making the formation of the spring easy and durable. It becomes possible to improve the property.

It is sectional drawing of the differential apparatus shown by the direction along a pinion shaft. Example 1 FIG. 2 is a cross-sectional view taken along the line II-II in FIG. Example 1 It is sectional drawing corresponding to FIG. 1 which shows arrangement | positioning of a spring member. Example 1 It is a top view which shows arrangement | positioning of a spring member. Example 1 It is a perspective view of a spring member. Example 1 It is a side view of a spring member. Example 1 It is a top view which shows the expansion | deployment state of a spring member. Example 1 It is a graph of the relationship between a spring force and initial torque. Example 1 It is sectional drawing of the differential apparatus which an up-and-down half section differs 90 degree | times, an upper half section shows in the direction along a pinion shaft, and the lower half section shows in the direction orthogonal to the same. (Example 2) FIG. 3 is a cross-sectional view of a differential device corresponding to FIG. (Example 2) It is sectional drawing of the spring member shown in the direction orthogonal to a pinion shaft. (Example 2) It is principal part sectional drawing which shows arrangement | positioning of a spring member in the direction along a pinion shaft. Example 3 It is principal part sectional drawing which shows arrangement | positioning of a spring member in the direction orthogonal to a pinion shaft. Example 3 It is a side view of the spring member shown in the direction along the pinion shaft. Example 3 It is sectional drawing which shows arrangement | positioning of the spring member which abbreviate | omits one side gear and is shown in the direction orthogonal to a pinion shaft. Example 4 It is a front view of the spring member shown in the direction along the pinion shaft. Example 4 It is a perspective view of a spring member. Example 4 It is sectional drawing of the differential apparatus which an up-and-down half section differs 90 degree | times, an upper half section shows in the direction along a pinion shaft, and the lower half section shows in the direction orthogonal to the same. (Example 5)

  Spherical side gear convex back surface and differential case spherical side gear concave support for the purpose of facilitating increased friction radius, ease of spring formation and improved durability Realized by the spring part between the face part and the side gear.

[Overall configuration of differential device]
1 is a cross-sectional view of a differential device shown in a direction along a pinion shaft, and FIG. 2 is a cross-sectional view taken along line II-II in FIG.

  As shown in FIGS. 1 and 2, the differential device 1 includes a differential case 3 that is rotatably supported, and pinion gears 7 and 8 that are rotatably supported by a pinion shaft 5 in the differential case 3. And a pair of side gears 9 and 11 which are supported in the differential case 3 so as to be relatively rotatable and mesh with the pinion gears 7 and 8.

  The differential case 3 has a one-piece structure formed as a single unit, and has a flange portion 15 for attaching a ring gear to the outer surface of the case wall portion 13 integrally in a circular shape. Pinion gear concave support surface portions 17 and 19 and side gear concave support surface portions 21 and 23 are formed on the inner surface of the differential case 3. The pinion gear concave support surface portions 17 and 19 and the side gear concave support surface portions 21 and 23 constitute a part of a concentric spherical surface having a center of curvature C. The center of curvature C is the intersection of the rotation axes of the pinion gears 7 and 8 and the side gears 9 and 11 in the differential case 3.

  “A part of the concentric spherical surface” means that the pinion gear concave support surface portions 17 and 19 and the side gear concave support surface portions 21 and 23 are processed into a spherical surface with a required area of the inner surface of the differential case 3, The inner surface of the differential case 3 has a slightly large diameter, which means a form of machining relief. However, it is possible to form the entire inner surface of the differential case 3 with an integral spherical surface.

  The pinion gears 7 and 8 and the side gears 9 and 11 are supported by the spherical pinion gear concave support surface portions 17 and 19 and the side gear concave support surface portions 21 and 23 of the differential case 3, A gear set using gears.

  Boss portions 25 and 27 are formed on both sides of the case wall 13 in the rotation axis direction, and can be rotatably supported by a differential carrier (not shown) as a stationary side member via a bearing. On the inner periphery of the boss portions 25 and 27, spiral grooves 25a and 27a are formed in opposite directions, respectively. The spiral grooves 25 a and 27 a are for introducing lubricating oil sealed in the differential carrier into the differential case 3.

  Support holes 29 and 31 of the pinion shaft 5 are formed concentrically through the case wall portion 13 at the center of the pair of pinion gear concave support surface portions 17 and 19 facing each other.

  In the case wall 13, a pair of windows 33 (however, only one appears in FIG. 2 and the other is out of the drawing in the direction orthogonal to the drawing) in the direction perpendicular to the pinion shaft 5. Adjacent to each other.

  The pair of windows 33 are formed so as to oppose each other in the rotational radius direction of the differential case 3 and have a weight balance. Through this window 33, it is possible to insert a turning tool and rotate the differential case 3 around a turning axis center line passing through the center of curvature C around the turning tool.

  The differential case 3 is sandwiched between lathe chuck jigs and rotated about the processing rotation axis center line to turn the pinion gear concave support surface portions 17 and 19 and the side gear concave support surface portions 21 and 23. .

  The pinion gears 7 and 8 have spherical convex back surfaces 7a and 8a supported by concentric spherical pinion gear concave support surface portions 17 and 19 through spherical pinion washers 35 and 36 so as to be slidable and rotatable. Has been.

  The pinion gears 7 and 8 are rotatably supported by the pinion shaft 5, and the pinion shaft 5 is fitted and supported in the support holes 29 and 31, and is prevented from being detached and prevented from being rotated by the spring pin 39. Yes.

  The side gears 9 and 11 mesh with the pinion gears 7 and 8, and the spherical convex back surfaces 9 a and 11 a are concentric spherical side gear concave support surfaces 21 and 23, and spherical side washers 41 and 43. Is supported so as to be slidable and rotatable.

  The side gears 9 and 11 are provided with tooth portions 47 on the outer peripheral side of the boss portion 45. An inner spline 49 is formed on the inner periphery of the boss portion 45.

  The root 51 of the tooth portion 47 is formed in a conical shape from the inner diameter side bent in the axial direction to the outer diameter side bent in the radial direction, and the tooth tip 53 of the tooth portion 47 is conical from the inner diameter side to the outer diameter side. Is formed. A pitch cone line 55 formed in a conical shape is located at an intermediate diameter between a tooth bottom 51 formed in a conical shape and a tooth tip 53 formed in a conical shape.

  The convex back surface portions 9a and 11a are formed on the tooth portion 47, and are formed across the pitch cone line 55 from the inner diameter side to the outer diameter side from the outer end side of the tooth base 51 to the outer end side of the tooth tip 53. ing. The convex back surface portions 9 a and 11 a are formed so as to extend closer to the inner diameter side than the outer end of the tooth bottom 51 of the tooth portion 47. In addition, the extension formation to the inner diameter side of the convex back surface parts 9a and 11a can also be omitted.

  An annular recess 57 is formed on the inner diameter side of the convex back surface portions 9a and 11a so as to form a space around the side gear concave support surface portions 21 and 23.

  The side washers 41, 43 are formed with a radial width corresponding to the entire width of the convex back surface portions 9a, 11a, and the inner diameter edge edges 41a, 43a are bent into the annular recess 57, and are slightly formed on the vertical back surface 57a. They are arranged so as to be able to be engaged with a certain interval.

  Therefore, the effective friction radius between the convex back surface portions 9a and 11a and the side washers 41 and 43 is set between the tooth bottom 51 outer end side and the tooth tip 53 outer end side of the tooth portion 47 of the side gears 9 and 11. ing.

At the time of differential rotation, the effective friction radius between the convex back surface portions 9a and 11a and the side washers 41 and 43 is such that the tooth base 47 outer end side and the tooth tip 53 outer end side of the tooth portion 47 of the side gears 9 and 11 By establishing a gap, it is possible to perform differential limiting with good response in conjunction with the power system, and to establish a differential device with an appropriate differential limiting function that can improve startability and climbability in ordinary vehicles. be able to.
[Spring member]
3 is a sectional view corresponding to FIG. 1 showing the arrangement of the spring member, FIG. 4 is a plan view showing the arrangement of the spring member, FIG. 5 is a perspective view of the spring member, and FIG. 6 is a side view of the spring member. FIG. 7 is a plan view showing a developed state of the spring member.

  As shown in FIGS. 1 to 4, the spring member 59 is interposed between the side gears 9 and 11. The spring member 59 urges the spherical convex back surface portions 9 a and 11 a of the side gears 9 and 11 against the side gear concave support surface portions 21 and 23.

  As shown in FIGS. 5 to 7, the spring member 59 is formed of a bent leaf spring. The spring member 59 has spring end portions 61 and 63 facing the side gears 9 and 11. The side gears 9 and 11 are provided with fitting convex portions 9b and 11b around the rotation axis as shown in FIGS. The spring end portions 61 and 63 are provided with fitting hole portions 61a and 63a, the fitting convex portions 9b and 11b are fitted with the fitting hole portions 61a and 63a, and the spring member 59 is connected to the side gears 9 and 11 respectively. It is locked in between.

  Between the spring end portions 61 and 63, there are elastic portions 65 and 67 bent in an S-shaped cross section. The mutual interval between the elastic portions 65 and 67 is slightly larger than the outer diameter of the pinion shaft 5 as shown in FIG.

Accordingly, as shown in FIGS. 1 and 2, the fitting holes 61a and 63a of the spring end portions 61 and 63 are fitted into the fitting convex portions 9b and 11b of the side gears 9 and 11, and the elastic portions 65 and 67 are fitted. Are arranged on both sides of the pinion shaft 5.
[Built-in differential gear]
The side gears 9 and 11 in which the side washers 41 and 43 are arranged on the convex back surface portions 9a and 11a are inserted into any of the windows 33 with respect to the differential case 3, and the side gears 9 and 11 are The side gear concave support surface portions 21 and 23 are arranged via the side washers 41 and 43.

  Next, the spring member 59 is disposed between the side gears 9 and 11, the spring end portions 61 and 63 are opposed to the side gears 9 and 11, and the fitting holes 61a and 63a are fitted to the side gears 9 and 11. It is made to fit in the joint convex part 9b, 11b. In this assembled state, the spring member 59 bends as shown by the solid line from the two-dot chain line shown in FIG.

  The side gears 9 and 11 are urged by the bending of the spring member 59, and the convex back surface portions 9 a and 11 a are pressed against the side gear concave support surface portions 21 and 23 via the side washers 41 and 43, Maintained.

  Next, the pinion gears 7 and 8 having the pinion washers 35 and 36 engaged with the convex back surface portions 7a and 8a are inserted separately from both windows 33 and meshed with the side gears 9 and 11, respectively.

  The differential gear composed of the pinion gears 7 and 8 and the side gears 9 and 11 is rotated by 90 ° with respect to the differential case 3 around the rotational axis of the differential case 3 to obtain the arrangement shown in FIG. At this point, the pinion shaft 5 is not assembled.

A differential gear composed of pinion gears 7 and 8 and side gears 9 and 11 is shown in FIG.
In this arrangement state, the pinion shaft 5 is inserted from the support hole 29 or the support hole 31 of the differential case 3 to the position shown in FIGS. 1 and 2 to complete the installation of the differential gear. Thereafter, a spring pin 39 is assembled between the differential case 3 and the pinion shaft 5 to prevent the pinion shaft 5 from coming off and preventing rotation.

The differential device 1 assembled in this way is inserted into the inner periphery of the bosses 25 and 27 of the differential case 3 by inserting the side shafts on the axle side when assembled to the automobile. The spline is connected to the spline 49.
[Differential rotation]
The differential rotation of the two axles when the vehicle is running is allowed by differential rotation of both side gears 9 and 11 by the rotation of the pinion gears 7 and 8, and the convex back surfaces 9a and 11a are side- The pressing to the side gear concave support surface portions 21 and 23 through the washers 41 and 43 becomes strong, and a differential limiting force is generated.

  At the initial stage of the differential, the side gears 9 and 11 are biased by the bending of the spring member 59, and the convex back surface portions 9 a and 11 a are pressed against the side gear concave support surface portions 21 and 23 via the side washers 41 and 43. Therefore, initial torque is generated.

  Therefore, the differential limiting force can be generated from the initial stage of the differential rotation by the initial torque.

  In this case, the friction between the spherical convex back surface portions 9a and 11a of the side gears 9 and 11 and the spherical side gear concave support surface portions 21 and 23 of the differential case 3 without increasing the size of the device. The radius can be easily increased as compared with the sliding contact on the conventional vertical surface, and the spring force can be reduced correspondingly to improve the wear resistance.

  Further, according to the so-called spherical differential of the embodiment of the present invention, the vertical load of the friction surface is amplified with respect to the axial load of the spring member 59 disposed between the pair of side gears 9 and 11, and accordingly, the spring It becomes possible to set the spring force of the member 59 low, making the formation of the spring easy and improving the durability.

  The relationship between the clutch torque (Tc) and the initial torque (Ti) is as follows.

・ Clutch torque (Tc) = {spring load (Fs) / inclination angle from rotation axis (Sinθ)} × friction force (μ) × effective diameter of friction surface (R)
-Initial torque (Ti) = Clutch torque (Tc) x Torque bias ratio (TBR) + Clutch torque (Tc)
FIG. 8 is a graph of the relationship between spring force and initial torque.

  In FIG. 8, the solid line is the result of the so-called spherical differential of the embodiment of the present invention, and the broken line is the result of the comparative example in which sliding contact is made on a flat surface perpendicular to the conventional rotational axis.

  As can be seen from FIG. 8, in the so-called spherical differential according to the embodiment of the present invention to obtain the same initial torque, the spring load of the spring member 59 can be easily reduced to about 1/3.

  Since the spring load is small, the wear of the friction surfaces such as the side gear concave support surface portions 21 and 23 is reduced, and the friction characteristics are stabilized. Generation of wear powder can also be suppressed.

  Since generation of wear powder can be suppressed, a change with time of the spring member 59 is small, and the pressing force of the spring member 59 is always stable.

Therefore, the initial torque characteristic change is stable, the performance is stable, and the differential device can have high durability.
[Effect of Example 1]
The differential device 1 according to the first embodiment of the present invention includes a differential case 3 that is rotatably supported, pinion gears 7 and 8 that are rotatably supported by a pinion shaft 5 in the differential case 3, and a differential case 3. A pair of side gears 9 and 11 which are supported in the case 3 so as to be relatively rotatable and mesh with the pinion gears 7 and 8, and the pinion gears 7 and 8 and the side gears 9 and 11 have the differential case 3 Spherical convex back surfaces 9a and 11a facing the inner surface are formed, and the spherical convex back surfaces 7a, 8a and 9a of the pinion gears 7 and 8 and side gears 9 and 11 are formed on the inner surface of the differential case 3. Spherical pinion gear concave support surface portions 17 and 19 and side gear concave support surface portions 21 and 23 that respectively support 11a so as to be able to rotate and slide are formed, and a spring member 59 is interposed between the side gears 9 and 11. And Biasing spherical convex rear portion 9a of Ido gears 9 and 11, the 11a relative to the side gear concave support surface 21, 23.

  Therefore, in order to increase the friction radius, the shape of the sliding portion between the differential case 3 and the side gears 9 and 11 is increased to the outer diameter side without increasing the size of the device, thereby increasing the size of the device. The friction radius between the 11 spherical convex back surface portions 9a and 11a and the spherical side gear concave support surface portions 21 and 23 of the differential case 3 is compared with the sliding contact on the conventional vertical surface. Can be bigger. In addition, the spring force of the spring member 59 can be set low, and the establishment of the spring can be facilitated and the durability can be improved.

  The spring member 59 is formed of a bent plate spring.

  For this reason, it can be arranged without difficulty between the side gears 9 and 11.

  The side gear 3 is provided with fitting convex portions 9b and 11b around the rotation axis, and the spring member 59 has spring end portions 61 and 63 facing the side gears 9 and 11, and the spring end portion 61, 63, fitting hole portions 61a and 63a for fitting into the fitting convex portions 9b and 11b are provided.

  For this reason, the arrangement of the spring member 59 can be positioned, and the initial torque can be set accurately.

  9 to 11 relate to a second embodiment of the present invention, and FIG. 9 shows a direction in which the upper and lower half sections are different by 90 degrees and the upper half section is along the pinion shaft, and the lower half section is in the same direction. 10 is a cross-sectional view of the differential device corresponding to FIG. 2, and FIG. 11 is a cross-sectional view of the spring member shown in a direction orthogonal to the pinion shaft. The basic configuration is the same as that of the first embodiment, and the same components are denoted by the same reference numerals, the corresponding components are denoted by A, and redundant description is omitted.

  In the differential device 1A of the second embodiment, the pinion shaft 5A is locked to the spring member 59A.

  That is, an engagement portion 5Aa formed with a two-sided width is formed on the outer periphery of the pinion shaft 5A, and the spring member 59A has an engagement portion 59Aa having a fitting and holding shape including an opposing wall 59Aaa and a connection wall 59Aab. Is formed. The length of the engaging portion 5Aa in the axial direction of the pinion shaft 5A corresponds to the width of the spring member 59A in the axial direction of the pinion shaft 5A. The opposing wall 59Aaa of the locking portion 59Aa is continuous with the elastic portions 65A and 67A having a curved back shape by the inclined wall 59Ac. The elastic portions 65A and 67A are continuous with the spring end portions 61A and 63A.

  Therefore, the spring member 59A is incorporated by fitting the fitting holes 61Aa and 63Aa of the spring end portions 61A and 63A into the fitting convex portions 9b and 11b of the side gears 9 and 11, and the pinion gears 7 and 8 are incorporated. Later, the pinion shaft 5A is inserted from the axial direction end in the same procedure as in the first embodiment, and the engaging portion 5Aa is click-fitted between the engaging portions 59Aa using elasticity. This fitted and clamped state is maintained by a stopper preventing the inclined walls 59Ac from engaging with the pinion shaft 5A.

  Therefore, the pinion shaft 5A is engaged with the engaging portion 59Aa of the spring member 59A at the end portion (cut portion) having a two-surface width of the engaging portion 5Aa, and is prevented from coming off in the axial direction. Further, the opposing wall of the locking portion 59Aa is fitted into the two surface widths of the pinion shaft 5A, so that the pinion shaft 5A is prevented from rotating.

  Thus, in the second embodiment, in addition to the effects of the first embodiment, the spring pin for preventing the pinion shaft 5A from coming off and preventing the rotation can be omitted.

  FIGS. 12 to 14 relate to the third embodiment of the present invention, FIG. 12 is a cross-sectional view of the main part showing the arrangement of the spring members in the direction along the pinion shaft, and FIG. 13 is the direction orthogonal to the pinion shaft. FIG. 14 is a side view of the spring member shown in a direction along the pinion shaft. The basic configuration is the same as that of the first embodiment. The same components are denoted by the same reference numerals, the corresponding components are denoted by the same reference characters B, and redundant description is omitted.

  Also in the differential device 1B of the third embodiment, the pinion shaft 5B is locked to the spring member 59B.

  A concave engagement portion 5Ba is formed on one side of the outer peripheral surface of the pinion shaft 5B, and a curved locking portion 59Ba is formed on the spring member 59B. The length of the engaging portion 5Ba in the axial direction of the pinion shaft 5B corresponds to the width of the spring member 59B in the axial direction of the pinion shaft 5B. The locking portion 59Ba is continuous with the spring end portions 61B and 63B via the elastic portions 65B and 67B having a folded curved shape.

  Therefore, the spring member 59B is incorporated by fitting the fitting hole portions 61Ba, 63Ba of the spring end portions 61B, 63B to the fitting convex portions 9b, 11b of the side gears 9, 11, and the same procedure as in the first embodiment is performed. Then, the pinion shaft 5B is inserted from the end in the axial direction, and the engaging portion 5Ba is click-engaged with the locking portion 59Ba using elasticity.

  Therefore, the pinion shaft 5B is engaged with the locking portion 59Ba of the spring member 59B at the engaging portion 5Ba, and is prevented from coming off in the axial direction. Further, the pinion shaft 5B is prevented from rotating by the locking portion 59Ba elastically hitting the flat surface of the engaging portion 5Ba.

  Thus, in the third embodiment, in addition to the effects of the first embodiment, the spring pin for preventing the pinion shaft 5B from being sewn off and preventing the rotation can be omitted.

  15 to 17 relate to a fourth embodiment of the present invention, and FIG. 15 is a cross-sectional view showing the arrangement of spring members in which one side gear is omitted in a direction orthogonal to the pinion shaft, and FIG. FIG. 17 is a front view of the spring member shown in a direction along the pinion shaft, and FIG. 17 is a perspective view of the spring member. The basic configuration is the same as that of the first embodiment, and the same components are denoted by the same reference numerals, and the corresponding components are denoted by the same reference numerals with C, and redundant description is omitted. . Refer to FIGS. 9 and 10 for the entire structure of the differential apparatus 1C.

  The differential device 1C of the fourth embodiment also has the pinion shaft 5C engaged with the spring member 59C.

  The pinion shaft 5C is formed with an engaging portion 5Ca formed with a width of two surfaces, and the spring member 59C is formed with a curved locking portion 59Ca. The locking portion 59Ca is continuous to the spring end portions 61C and 63C via the elastic portions 65C and 67C having a bent curved shape.

  Therefore, the spring member 59C is incorporated by fitting the fitting hole portions 61Ca, 63Ca of the spring end portions 61C, 63C with the fitting convex portions 9b, 11b of the side gears 9, 11, and the same procedure as in the first embodiment is performed. Then, the pinion shaft 5C is inserted from the axial end portion, and the locking portion 59Ca is fastened to the engaging portion 5Ca by the bolt 59Cb from the window 33.

  Therefore, the pinion shaft 5C is coupled to the locking portion 59Ca of the spring member 59C by the engagement portion 5Ca, and is prevented from coming off and rotating in the axial direction.

  Thus, in the fourth embodiment, in addition to the effects of the first embodiment, the spring pin for preventing the pinion shaft 5B from coming off and preventing the rotation can be omitted.

  FIG. 18 is a cross-sectional view of a differential device according to the fifth embodiment of the present invention, in which the upper and lower half cross sections are 90 degrees and the upper half cross section is shown in the direction along the pinion shaft and the lower half cross section is shown in the orthogonal direction. is there. Note that the basic configuration is the same as that of the first embodiment, the same components are denoted by the same reference numerals, the corresponding components are denoted by the same reference numerals, and redundant description is omitted.

  In the differential device 1D of the fifth embodiment, the spring member 59D has the same form as that of the second embodiment, and the spherical convex back surface portions 9Da and 11Da of the side gears 9D and 11D and the spherical side surface of the differential case 3D are arranged. The form with gear concave support surface parts 21D and 23D was changed.

  That is, the convex back surface portions 9Da and 11Da of the side gears 9D and 11D that slide toward the side gear concave support surface portions 21D and 23D of the differential case 3D are located on the inner diameter side of the tooth portions 47 of the side gears 9D and 11D. Formed.

  Even in this case, the vertical load on the friction surface is amplified with respect to the axial load of the spring member 59D disposed between the pair of side gears 9 and 11, and the same effect as the above embodiment can be obtained.

1, 1A, 1B, 1C, 1D Differential device 3, 3D differential case 5, 5B, 5C, 5D Pinion shaft 5Aa, 5Ba, 5Ca, 5Da Engaging portion 7, 8 Pinion gears 9, 9D, 11, 11D Side gear 9a, 9Da, 11a, 11Da Convex back surface part 17, 19 Pinion gear concave support surface part 21, 21D, 23, 23D Side gear concave support surface part 7a, 8a, 9a, 11a Convex back surface part 59, 59A, 59B , 59C, 59D Spring member 59Aa, 59Ba, 59Ca, 59Da Locking portion 61, 61A, 61B, 61C, 63, 63A, 63B, 63C Spring end portion 61a, 61Aa, 61Ba, 61Ca, 63a, 63Aa, 63Ba, 63Ca Joint hole 9b, 11b Fitting projection

Claims (6)

A differential case that is rotatably supported, a pinion gear that is rotatably supported by a pinion shaft in the differential case, and a pinion gear that is rotatably supported in the differential case and meshes with the pinion gear. With a pair of side gears,
Forming a spherical convex back surface facing the inner surface of the differential case on the pinion gear and side gear,
A spherical pinion gear concave support surface portion and a side gear concave support surface portion are provided on the inner surface of the differential case to support the spherical convex back surface portions of the pinion gear and the side gear so as to be able to rotate and slide. ,
A spring member is interposed between the side gears,
The side gear is provided with a fitting projection around the rotation axis,
The spring member integrally has a spring end facing the side gear,
The spring end portion is provided with a fitting hole portion that fits into the fitting convex portion,
Urging the spherical convex back surface portion of the side gear against the side gear concave support surface portion;
A differential device characterized by that. The differential device according to claim 1,
The spring member is formed of a bent plate spring.
A differential device characterized by that. A differential device according to claim 2 , wherein
The pinion shaft is provided with an axial engagement portion,
The engagement member is locked to the spring member,
A differential device characterized by that. A differential device according to any one of claims 1 to 3 ,
The differential case is formed as a single unit,
A differential device characterized by that. A differential device according to any one of claims 1 to 4 ,
A convex back surface portion of the side gear that slides on the side gear concave support surface portion side of the differential case is formed on a tooth portion of the side gear.
A differential device characterized by that. A differential device according to any one of claims 1 to 4 ,
The convex portion of the side gear that slides to the side gear concave support surface portion side of the differential case is formed on the inner diameter side of the tooth portion of the side gear.
A differential device characterized by that.

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