JP2019163782A - Differential device - Google Patents

Abstract

To provide a differential device which can increase a transmission capacity of a drive force while suppressing the enlargement of the device and an increase of weight, in the differential device having a moving member which is arranged so as to be movable to an axial direction in a case member by an actuator.SOLUTION: A differential device 1 for outputting a drive force inputted into a differential case 2 which rotates by receiving the drive force of a drive source from a pair of side gears 31, 32 comprises: a clutch rotation number 5 which is arranged so as to be movable to an axial direction in the differential case 2, and can regulate the relative rotation of one side gear 31 with respect to the differential case 2 by movement to one side in an axial direction; and an actuator 10 for moving the clutch ring 5. A plurality of inside raceway grooves 511, 512 are formed at an external peripheral face 51c of the clutch ring 5, a plurality of outside raceway grooves 214., 215 are formed at an internal peripheral face 211a of the differential case 2, and by a plurality of rolling bodies 50 rolling in the grooves, the drive force is transmitted to the clutch ring 5 from the differential case 2.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a differential device capable of outputting a driving force input to a case member while allowing a differential from a pair of output rotating members.

  2. Description of the Related Art Conventionally, in a differential device for a vehicle that can output a driving force input to a case member by allowing a differential from a pair of output rotating members, a movement arranged in an axial direction within the case member by an actuator is provided. Some have a member, and the operation mode of the differential device can be switched by the movement of the moving member (see, for example, Patent Document 1).

  A differential device described in Patent Document 1 includes left and right side gears as a pair of output rotating members, a pinion gear including a plurality of bevel gears meshed with the left and right side gears, a pinion shaft that pivotally supports the pinion gear, and a pinion shaft. A cylindrical inner case that rotates, an outer case that accommodates the inner case, a cam ring (moving member) that is axially movable in the outer case, and an actuator that moves the cam ring in the axial direction. Yes.

  The cam ring includes an annular portion formed in an annular shape, a plurality of meshing teeth formed on one side in the axial direction of the annular portion, and a plurality of engaging convex portions formed so as to protrude on the other axial side of the annular portion. The engaging convex portion engages with an engaging hole formed in the outer case and rotates integrally with the outer case. Further, the cam ring moves in the axial direction between a connection position where the meshing teeth mesh with the inner case and is connected to the inner case in a relatively non-rotatable manner, and a non-connection position where the meshing teeth do not mesh with the inner case. When the cam ring is in the coupling position, the driving force input to the outer case is transmitted from the pair of side gears to the driving shaft via the inner case, and when the cam ring is in the non-coupling position, the transmission of this driving force is cut off. .

JP 2011-241888 A

  In the differential device configured as described above, since the driving force input to the outer case is transmitted from the engaging convex portion to the cam ring, the stress tends to concentrate on the root portion of the engaging convex portion. In addition, if the circumferential width of the engaging protrusion is increased to increase the strength of the engaging protrusion, the opening width of the engaging hole is increased, the strength of the outer case is reduced, and the transmission capacity of the driving force is limited. Will be. In addition, increasing the thickness of the cam ring in the radial direction increases the size and the weight of the device.

  Therefore, the present invention increases the transmission capacity of the driving force while suppressing an increase in the size and weight of the device in a differential device including a moving member arranged to be movable in the axial direction within the case member by an actuator. It is an object of the present invention to provide a differential device that can be used.

  In order to achieve the above object, the present invention includes a case member that rotates around a rotation axis in response to a driving force of a drive source, and a plurality of rotating elements including a pair of output rotating members housed in the case member. A differential device capable of differentially outputting the driving force input to the case member from the pair of output rotation members, wherein the differential force is output along the rotation axis within the case member. A movable member arranged to be movable in a direction and capable of restricting relative rotation of any one of the plurality of rotating elements with respect to the case member by movement in one axial direction; And a plurality of inner raceway grooves are formed on the outer peripheral surface of the moving member, and a plurality of outer raceway grooves are formed on the inner peripheral surface of the case member. Orbit The moving member is guided in the axial direction by a plurality of rolling elements arranged so as to be able to roll in the outer raceway groove, and the driving force of the driving source is transmitted to the moving member via the plurality of rolling elements. A differential device is provided.

  According to the differential device of the present invention, in the differential device including the moving member that is arranged to be movable in the axial direction within the case member by the actuator, the driving force while suppressing the increase in size and weight of the device. It is possible to increase the transmission capacity.

It is sectional drawing which shows the structural example of the differential gear which concerns on embodiment of this invention. It is a disassembled perspective view of a differential. It is a disassembled perspective view which shows the structure inside the differential case of a differential gear. The clutch ring is shown alone, (a) is a front view, (b) is a side view, and (c) is a rear view. It is a perspective view of a clutch ring. (A) And (b) is explanatory drawing which shows the axial direction movement of a clutch ring. It is sectional drawing which shows a part of differential case and a clutch ring.

[Embodiment]
Embodiments of the present invention will be described with reference to FIGS. In addition, although embodiment described below is shown as a suitable specific example in implementing this invention, although there are some parts which have illustrated various technical matters that are technically preferable. The technical scope of the present invention is not limited to this specific embodiment.

  FIG. 1 is a cross-sectional view showing a configuration example of a differential device according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of the differential. FIG. 3 is an exploded perspective view showing the structure inside the differential case of the differential. FIG. 4 shows the clutch ring alone, (a) is a front view, (b) is a side view, and (c) is a rear view. FIG. 5 is a perspective view of the clutch ring. 6A and 6B are explanatory views for explaining the axial movement of the clutch ring. FIG. 7 is a cross-sectional view showing a part of the differential case and the clutch ring in a cross section in a direction perpendicular to the rotation axis.

  The differential device 1 is used to allow a driving force of a driving source of a vehicle including an engine or an electric motor to be distributed to a pair of output shafts while allowing a differential. More specifically, the differential device 1 according to the present embodiment is used as, for example, a differential device that distributes the driving force of a driving source to left and right wheels, and the input driving force is a pair of driving shafts. Distribute to the drive shaft.

  The differential device 1 is supported by a differential carrier 9 fixed to the vehicle body, and includes a differential case 2 as a case member that rotates around the rotation axis O, and first and first output rotary members housed in the differential case 2. Two side gears 31, 32, a plurality of pinion gear sets 40 formed by meshing the first and second pinion gears 41, 42, and a moving member disposed in the differential case 2 so as to be axially movable along the rotation axis O And an actuator 10 that moves the clutch ring 5 in the axial direction with respect to the differential case 2.

  A position sensor 91 that outputs an electrical signal for controlling the actuator 10 is attached to the attachment hole 90 in the differential carrier 9. The electrical signal output from the position sensor 91 is sent to the controller 92. The controller 92 controls the actuator 10 based on the electrical signal from the position sensor 91. The differential carrier 9 is filled with lubricating oil having a viscosity suitable for gear lubrication, and the differential 1 is used in a lubricating environment with this lubricating oil.

  The first and second side gears 31 and 32 are cylindrical, and a spline fitting portion 310 is formed on the inner peripheral surface of the first side gear 31 so that one drive shaft is connected so as not to be relatively rotatable. A spline fitting portion 320 is formed on the inner peripheral surface of the side gear 32 to which the other drive shaft is connected in a relatively non-rotatable manner.

  The differential case 2 is rotatably supported by the differential carrier 9 via a pair of bearings 93 and 94. The differential case 2, the first side gear 31, and the second side gear 32 are disposed so as to be rotatable relative to each other about the rotation axis O. Hereinafter, a direction parallel to the rotation axis O is referred to as an axial direction.

  The differential case 2 is formed with a plurality of holding holes 20 for rotatably holding the first pinion gear 41 and the second pinion gear 42 of each pinion gear set 40. The first pinion gear 41 and the second pinion gear 42 revolve around the rotation axis O, and can rotate within the holding hole 20 with their respective central axes as rotation axes.

  The first and second side gears 31 and 32 have a common outer diameter, and gear portions 311 and 321 made up of a plurality of inclined teeth are formed on the outer peripheral surface, respectively. A center washer 11 is disposed between the first side gear 31 and the second side gear 32. Further, a side washer 12 is disposed on the side of the first side gear 31, and a side washer 13 is disposed on the side of the second side gear 32.

  The first pinion gear 41 integrally includes a long gear portion 411, a short gear portion 412, and a connecting portion 413 that connects the long gear portion 411 and the short gear portion 412 in the axial direction. Similarly, the second pinion gear 42 integrally includes a long gear portion 421, a short gear portion 422, and a connecting portion 423 that connects the long gear portion 421 and the short gear portion 422 in the axial direction.

  In the first pinion gear 41, the long gear portion 411 meshes with the gear portion 311 of the first side gear 31 and the short gear portion 422 of the second pinion gear 42, and the short gear portion 412 has a long gear portion 421 of the second pinion gear 42. Are engaged. In the second pinion gear 42, the long gear portion 421 meshes with the gear portion 321 of the second side gear 32 and the short gear portion 412 of the first pinion gear 41, and the short gear portion 422 is the long gear portion 411 of the first pinion gear 41. Are engaged. In addition, in FIG. 3, illustration of the inclined tooth of each gear part is abbreviate | omitted.

  When the first and second side gears 31 and 32 rotate at the same speed, the first and second pinion gears 41 and 42 revolve together with the differential case 2 without rotating in the holding hole 20. For example, when the rotational speeds of the first and second side gears 31 and 32 are different during turning of the vehicle, the first and second pinion gears 41 and 42 revolve while rotating in the holding hole 20. As a result, the driving force input to the differential case 2 is distributed to the first and second side gears 31 and 32 while allowing a differential.

  The first and second side gears 31 and 32 and the first and second pinion gears 41 and 42 are rotational elements that are disposed in the differential case 2 and are rotatable relative to the differential case 2. When the rotation of any one of the plurality of rotating elements with respect to the differential case 2 is restricted, the first side gear 31 and the second side gear 32 are in a differential lock state in which the relative rotation is impossible. In the present embodiment, the clutch ring 5 restricts the relative rotation of the first side gear 31 with respect to the differential case 2.

  The clutch ring 5 is axially connected between a connecting position where the differential case 2 and the first side gear 31 are connected so as not to rotate relative to each other and a non-connecting position where the relative rotation between the differential case 2 and the first side gear 31 is allowed. It is movable. That is, the clutch ring 5 can restrict the relative rotation of the first side gear 31 with respect to the differential case 2 by moving from the non-connected position to the connected position in one axial direction. FIG. 1 shows a state where the clutch ring 5 is in the non-connected position.

  When the clutch ring 5 is in the coupling position, the differential between the differential case 2 and the first side gear 31 is restricted, so that the first and second pinion gears 41 and 42 cannot rotate, and the differential case 2 and the second side gear 31 are not allowed to rotate. Differential with the side gear 32 is also restricted. The clutch ring 5 is urged toward the unconnected position by the return spring 14 disposed between the clutch ring 5 and the first side gear 31. The return spring 14 is composed of, for example, a disc spring or a wave washer.

  The actuator 10 includes an electromagnetic coil 61 formed by molding a winding 611 with a resin portion 612, a yoke 62 that supports the electromagnetic coil 61, the electromagnetic coil 61 is prevented from being detached from the yoke 62, and the yoke 62 is attached to the differential carrier 9. A stopper ring 63 that prevents rotation, an armature 7 that slides on the outer peripheral surface 61a (see FIG. 2) of the electromagnetic coil 61 and moves in the axial direction, and moves in the axial direction together with the armature 7 to press the clutch ring 5. And a pressing member 8.

  As shown in FIG. 1, the electromagnetic coil 61 has a rectangular cross-sectional shape along the rotation axis O, and a winding 611 is disposed at the center thereof. The outer peripheral surface 61 a and the inner peripheral surface 61 b of the electromagnetic coil 61 and both end surfaces 61 c and 61 d in the axial direction are formed by the resin portion 612. Further, as shown in FIG. 2, the electromagnetic coil 61 is provided with a boss portion 613 protruding from one end surface in the axial direction, and an electric wire 614 for supplying an exciting current to the winding 611 is led out from the boss portion 613. Has been. The controller 92 supplies an excitation current to the winding 611 of the electromagnetic coil 61 via the electric wire 614.

  The yoke 62 is made of a soft magnetic metal such as low carbon steel, and has a cylindrical inner cylinder portion 621 that covers the inner peripheral surface 61b of the electromagnetic coil 61 from the inside, and an outer end from one axial end portion of the inner cylinder portion 621. A side wall portion 622 that protrudes and faces one axial end face of the electromagnetic coil 61 is integrally provided. The inner cylinder portion 621 has an inner diameter slightly larger than the outer diameter of the differential case 2 at the portion facing the inner peripheral surface 621 a of the inner cylinder portion 621, and the yoke in which the differential case 2 is prevented from rotating by the differential carrier 9 It is rotatable with respect to 62.

  On the inner peripheral surface 621a of the inner cylinder portion 621, an annular recess 621b is formed in which a plurality of (three in this embodiment) plates 152 made of a non-magnetic material fixed to the differential case 2 by press-fit pins 151 are fitted. ing. The yoke 62 is restricted from moving in the axial direction with respect to the differential case 2 by fitting the plate 152 into the annular recess 621b. The axial width of the annular recess 621b is formed to be slightly larger than the thickness of the plate 152 so that no rotational resistance is generated with the yoke 62 when the differential case 2 rotates.

  The stopper ring 63 is made of a nonmagnetic metal such as austenitic stainless steel, and includes an annular portion 631 fixed to the yoke 62, a pair of projecting portions 632 projecting axially from the annular portion 631 at two circumferential locations, and a projection A folded portion 633 that is folded at an acute angle from the tip of the portion 632 is integrally provided. The annular portion 631 faces the axial end surface 61 c of the electromagnetic coil 61 and is fixed to the end portion of the yoke 62 opposite to the side wall portion 622 in the inner cylindrical portion 621. The stopper ring 63 is prevented from rotating by a pair of protrusions 632 being locked to a locking portion 900 provided on the differential carrier 9. The differential carrier 9 has two locking portions 900 that lock the pair of protrusions 632, respectively, and one locking portion 900 is shown in FIG.

  The armature 7 is made of a soft magnetic metal such as low carbon steel, and has a cylindrical portion 71 disposed on the outer periphery of the electromagnetic coil 61 and an annular plate extending radially inward from one axial end of the cylindrical portion 71. It has the part 72 integrally. When the electromagnetic coil 61 is energized, the armature 7 moves so that the distance between the annular plate portion 72 of the armature 7 and the axial end surface 621c of the inner cylindrical portion 621 of the yoke 62 is narrowed.

  The annular plate portion 72 of the armature 7 has a plurality of (10 in the example shown in FIG. 2) oil holes 720 through which lubricating oil flows, a first through hole 721 through which the boss portion 613 of the electromagnetic coil 61 is inserted, and Two second through holes 722 through which the pair of protrusions 632 of the stopper ring 63 are inserted are formed. The armature 7 is prevented from rotating with respect to the differential carrier 9 by the protrusion 632 of the stopper ring 63 passing through the second through-hole 722, and is prevented from coming off the stopper ring 63 by the folded-back portion 633.

  The pressing member 8 is formed by press-molding a plate material made of a nonmagnetic metal such as austenitic stainless steel, and has a ring-shaped annular contact portion 81 that contacts the annular plate portion 72 of the armature 7 and an annular contact portion 81. Three extending portions 82 that extend in the axial direction from the front and a fixed portion 83 that protrudes inward from the tip of the extending portion 82 and is fixed to the clutch ring 5. In the pressing member 8, the annular contact portion 81 slides with the annular plate portion 72 of the armature 7 and rotates together with the differential case 2. The fixing portion 83 is formed with an insertion hole 830 through which the press-fit pin 16 for fixing to the clutch ring 5 is inserted.

  The differential case 2 includes a bottomed cylindrical case body 21 fixed to each other by a plurality of screws 200, and a case lid body 22 that closes an opening of the case body 21. The case body 21 includes a cylindrical cylindrical portion 211 that rotatably holds a plurality of pinion gear sets 40, a bottom portion 212 that extends inward from one end of the cylindrical portion 211, and a flange that abuts against the case lid body 22. It has the part 213 integrally. An annular recess 210 in which the electromagnetic coil 61 and the yoke 62 are disposed is formed at a corner between the cylindrical portion 211 and the bottom portion 212. A ring gear (not shown) is fixed to the flange portion 213 of the case body 21. The differential case 2 receives the driving force of the driving source from the ring gear, and rotates about the rotation axis O.

  As shown in FIGS. 2 and 3, a plurality of insertion holes 212 a into which the extension portions 82 and the fixing portions 83 of the pressing member 8 are inserted are formed in the bottom portion 212 of the case body 21. The insertion hole 212a penetrates the bottom 212 in the axial direction. A protrusion 53 of the clutch ring 5 described later is inserted into the insertion hole 212a. In the present embodiment, three insertion holes 212 a are formed at equal intervals along the circumferential direction of the bottom portion 212.

  The clutch ring 5 includes an annular plate-like disc portion 51 having a rectangular cross-sectional shape along the rotational axis O, and one shaft of the disc portion 51 that faces the first side gear 31 in the axial direction. The engaging portion 52 formed on the directional end surface 51 a and the trapezoidal columnar protrusion 53 formed so as to protrude in the axial direction from the other axial end surface 51 b of the disc portion 51 are integrally provided.

  The axial end surface 51 b of the disc part 51 faces the bottom part 212 of the case body 21 in the axial direction. A part of the protrusion 53 is inserted into an insertion hole 212 a formed in the bottom 212 of the case body 21. The meshing portion 52 is formed with a plurality of meshing teeth 521 protruding in the axial direction. The plurality of meshing teeth 521 are formed on a part of the outer peripheral side of the axial end surface 51a on the first side gear 31 side in the disc portion 51, and the return spring 14 is disposed on the axial end surface 51a inside the meshing portion 52. It is formed as a flat receiving surface that abuts and receives a biasing force to the non-connected position.

  As shown in FIG. 1, the first side gear 31 has a plurality of meshing teeth 313 that mesh with a plurality of meshing teeth 521 of the clutch ring 5 on an annular wall portion 312 that projects from the gear portion 311 to the outer peripheral side. Is formed.

  The clutch ring 5 is pressed by the armature 7 via the pressing member 8 and moves to the coupling position, whereby the plurality of meshing teeth 521 of the meshing portion 52 mesh with the plurality of meshing teeth 313 of the first side gear 31. As a result, the differential device 1 enters the differential lock state. On the other hand, when the clutch ring 5 is moved to the non-connection position by the urging force of the return spring 14, the meshing between the meshing teeth 521 and 313 is not meshed, and the differential lock state is released.

  A press-fitting hole 531 into which the press-fitting pin 16 is press-fitted is formed on the distal end surface 53 a of the protrusion 53. The clutch ring 5 is fixed so as to move in the axial direction integrally with the pressing member 8 when the press-fitting pin 16 inserted through the insertion hole 830 formed in the fixing portion 83 of the pressing member 8 is press-fitted into the press-fitting hole 531. The The insertion hole 212a of the bottom portion 212 has a circumferential width wider than the circumferential width of the protrusion 53 of the clutch ring 5, and the circumferential direction gap between the protrusion 53 of the clutch ring 5 and the inner surface of the insertion hole 212a. A gap is formed. Thereby, the driving force of the differential case 2 is not transmitted from the protrusion 53 to the clutch ring 5.

  The position of the clutch ring 5 in the axial direction is detected by a position sensor 91. The position sensor 91 includes a contact 911 that elastically contacts the annular plate portion 72 of the armature 7 and a support 912 that supports the contact 911, and the position of the clutch ring 5 in the axial direction is determined by the position of the armature 7. It detects indirectly by the position of the annular plate part 72. The support body 912 is inserted through the mounting hole 90 of the differential carrier 9.

(Support structure of clutch ring 5 for differential case 2)
The clutch ring 5 is supported so as to be axially movable with respect to the differential case 2 and not relatively rotatable. Next, this support structure will be described in detail with reference to FIGS. 6A and 6B, the cylindrical portion of the case main body 21 facing the outer peripheral surface 51c of the disc portion 51 in the radial direction when the disc portion 51 in the clutch ring 5 is viewed from the radially outer side. It is shown together with an outer raceway groove (described later) formed on an inner peripheral surface 211a (see FIG. 1) 211. In FIGS. 6A and 6B, the outer raceway grooves are indicated by broken lines. 6A and 6B, the vertical direction of the drawing corresponds to the circumferential direction of the disc portion 51 and the case main body 21.

  As shown in FIGS. 4 and 5, a plurality of inner raceways are formed on the outer peripheral surface 51 c of the disc portion 51 in the clutch ring 5. The plurality of inner raceway grooves include a first inner inclined groove 511 inclined to one side in the circumferential direction with respect to the axial direction, and a second inner inclined groove 512 inclined to the other side in the circumferential direction with respect to the axial direction. In the present embodiment, six first inner inclined grooves 511 and second inner inclined grooves 512 are alternately formed in the circumferential direction of the outer peripheral surface 51 c of the disc portion 51. The first inner inclined groove 511 and the second inner inclined groove 512 have a semicircular cross-sectional shape orthogonal to the extending direction.

  A plurality of outer raceway grooves are formed on the inner peripheral surface 211 a of the cylindrical portion 211 of the case body 21. The plurality of outer raceway grooves include a first outer inclined groove 214 inclined to one side in the circumferential direction with respect to the axial direction (the same direction as the inclined direction of the first inner inclined groove 511), and a circumferential direction with respect to the axial direction. The second outer inclined groove 215 is inclined to the other side (the same direction as the inclination direction of the second inner inclined groove 512). In the present embodiment, six first outer inclined grooves 214 and second outer inclined grooves are respectively provided. The grooves 215 are alternately formed in the circumferential direction of the inner peripheral surface 211 a of the cylindrical portion 211. The first outer inclined groove 214 and the second outer inclined groove 215 have a semicircular cross-sectional shape orthogonal to the extending direction.

  The first inner inclined groove 511 and the second outer inclined groove 215, and the second inner inclined groove 512 and the first outer inclined groove 214 intersect in an X shape when viewed in the radial direction. And the spherical rolling element 50 is each arrange | positioned so that rolling is possible at the intersection where these groove | channels cross | intersect. A driving force is transmitted from the differential case 2 to the clutch ring 5 through these rolling elements 50. The clutch ring 5 is guided in the axial direction with respect to the differential case 2 by the rolling of the plurality of rolling elements 50, and relative rotation with respect to the differential case 2 is restricted. When the clutch ring 5 moves in the axial direction, the rolling element 50 rolls in the moving direction of the clutch ring 5 (direction parallel to the rotation axis O).

(Operation and effect of the embodiment)
According to the embodiment of the present invention described above, the clutch ring 5 is moved in the axial direction by the rolling of the plurality of rolling elements 50, so that the actuator 10 can smoothly move the clutch ring 5 in the axial direction. . Further, when the clutch ring 5 is located at the coupling position, the driving force is transmitted to the disc portion 51 of the clutch ring 5 through the plurality of rolling elements 50, so that stress concentrates on the root portion of the protrusion 53, for example. There is nothing to do. As a result, it is possible to increase the transmission capacity of the driving force while suppressing an increase in size and weight of the differential device 1.

  Further, in the present embodiment, a spherical shape is formed between the first inner inclined groove 511 and the second outer inclined groove 215 that are inclined in opposite directions, and between the second inner inclined groove 512 and the first outer inclined groove 214. Therefore, the rolling element 50 is positioned at a position where these grooves intersect. For this reason, it becomes possible to hold | maintain the rolling element 50 in a groove | channel, without providing the member etc. which control that the rolling element 50 slips out from these grooves.

  Furthermore, in the present embodiment, since the plurality of first inner inclined grooves 511 and second inner inclined grooves 512 are alternately formed in the circumferential direction of the outer peripheral surface 51c of the disc portion 51, the rolling element 50 rotates. When rolling in a direction parallel to the axis O, the forces acting in the direction orthogonal to the extending direction of the first inner inclined groove 511 and the second inner inclined groove 512 are canceled by each other, Inclination of the clutch ring 5 with respect to the rotation axis O in the differential case 2 is suppressed. Thereby, the clutch ring 5 moves smoothly in the axial direction.

(Appendix)
As mentioned above, although this invention was demonstrated based on embodiment, these embodiment does not limit the invention which concerns on a claim. In addition, it should be noted that not all the combinations of features described in the embodiments are essential to the means for solving the problems of the invention.

  Further, the present invention can be appropriately modified and implemented without departing from the spirit of the present invention. For example, in the above-described embodiment, the case where the present invention is applied to the differential device in which the first and second pinion gears 41 and 42 are arranged in parallel to the rotation axis O has been described. As in the differential device described in Patent Document 1 described above, the present invention is applied to a differential device having a configuration in which a pinion gear made up of a bevel gear is pivotally supported on a pinion shaft arranged so as to be orthogonal to the rotation axis of the differential case. It is also possible to apply. In this case, the relative rotation of the pinion shaft as the rotating element with respect to the differential case is restricted by the moving member that moves in the axial direction by the actuator.

DESCRIPTION OF SYMBOLS 1 ... Differential gear 2 ... Differential case 211a ... Inner peripheral surface 214 ... 1st outer side inclined groove 215 ... 2nd outer side inclined groove 31 ... 1st side gear 32 ... 2nd side gear 5 ... Clutch ring (moving member)
DESCRIPTION OF SYMBOLS 50 ... Rolling element 51c ... Outer peripheral surface 511 ... 1st inner side inclination groove | channel 512 ... 2nd inner side inclination groove | channel

Claims (3)

A case member that rotates around a rotation axis in response to a driving force of a driving source, and a plurality of rotating elements including a pair of output rotating members housed in the case member, and the driving force input to the case member A differential device capable of allowing and outputting a differential from the pair of output rotating members,
It is arranged in the case member so as to be movable in the axial direction along the rotation axis, and the relative rotation with respect to the case member of any one of the plurality of rotating elements is restricted by movement in one axial direction. A movable member capable of
An actuator for moving the moving member in the axial direction;
The moving member is formed with a plurality of inner raceways on its outer peripheral surface,
The case member has a plurality of outer raceway grooves formed on an inner peripheral surface thereof,
The moving member is guided in the axial direction by a plurality of rolling elements arranged to roll in the inner raceway groove and the outer raceway groove, and the driving force of the drive source is transmitted through the plurality of rolling elements. Transmitted to the moving member,
Differential device. The plurality of inner raceway grooves are composed of a first inner inclined groove inclined to one side in the circumferential direction with respect to the axial direction, and a second inner inclined groove inclined to the other side in the circumferential direction with respect to the axial direction,
The plurality of outer track grooves include a first outer inclined groove inclined to the one side in the circumferential direction with respect to the axial direction, and a second outer inclined groove inclined to the other side in the circumferential direction with respect to the axial direction. ,
The plurality of rolling elements are respectively disposed between the first inner inclined groove and the second outer inclined groove and between the first outer inclined groove and the second inner inclined groove.
The differential device according to claim 1. The plurality of inner raceway grooves, the plurality of first inner inclined grooves and the plurality of second inner inclined grooves are alternately formed in the circumferential direction,
In the plurality of outer raceway grooves, a plurality of the first outer inclined grooves and a plurality of the second outer inclined grooves are alternately formed in the circumferential direction.
The differential device according to claim 2.

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