JP2006189149A - Differential device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce restriction on loading property into a vehicle and improve degree of freedom in design of a differential device by improving interchangeability with a peripheral member between conveyor differential and differential limit mechanism addition model. <P>SOLUTION: This differential device is provided with a differential mechanism 13 composed of a pair of output members 21, 22 for transmitting driving torque to be inputted into a differential case 2 to a pair of output shafts 52, 52 and a differential member 19 distributing driving torque to be inputted into the differential case 2 to the pair of output members 21, 22 and connecting the pair of output members 21 and 22 so as to rotate relatively and freely and a differential limit mechanism 37 for limiting differential rotation of the differential mechanism 13 and is stored in a carrier. The pair of output members 21, 22 have connection parts 35, 36 connected with the pair of output shafts 52, 52, respectively, and the connection parts 35, 36 on at least one side are formed on inner peripheral sides of first cylindrical parts 25, 26 extended on inner sides in the direction of rotary shafts of the output members 21, 22. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a differential apparatus.

The differential device is mounted on almost all vehicles, and the drive torque transmitted from the drive source is differentially distributed to a pair of output shafts, and is generally called “conventional differential” (hereinafter referred to as “combed differential”). . The conventional convex is functionally driven to the other output shaft when the drive resistance of one of the pair of output shafts (if connected to the wheels, the drive friction resistance between the wheels and the road surface) is lost. Torque is no longer transmitted. In response to such a problem, the running performance of the vehicle can be improved by adding a differential limiting function to the convex. A differential apparatus having a differential limiting function disclosed in Patent Documents 1, 2, and 3 shown below will be described. A differential apparatus described in Patent Document 1 includes a differential case, a pinion shaft, a pinion, and a pair of side gears. This is a normal (conventional) differential device composed of the following: a differential limiting mechanism consisting of a multi-plate clutch is added between the differential case and the pair of side gears. The transmission torque is mechanically controlled intermittently (controlling the engagement torque of the friction clutch) in accordance with the input drive torque.

  The differential device described in Patent Document 2 is a conven- tive device similar to the differential device of Patent Document 1, and a meshing clutch that locks a differential between the differential case and one side gear, and an electromagnetic type that controls this from the outside An actuator is added, and the transmission torque is intermittently controlled as necessary.

The differential device described in Patent Document 3 is also a convex differential, and a differential limiting device including a meshing clutch similar to Patent Document 2 is arranged between the differential case and one side gear, and this meshing clutch is controlled from the outside. The transmission torque is intermittently controlled as required by possible electromagnetic actuators. The electromagnetic actuator is arranged on the opposite side of the differential case in the axial direction from the flange portion.
JP 2002-70985 A JP 2004-100924 A JP 2000-240760 A

  The differential device has a structure based on the convex as described above, and the structure and dimensions of its peripheral members, for example, the dimensions of the carrier that accommodates and supports the differential device, the position of the support portion, and the left and right output shafts The size (length) is determined based on the convex. In addition to this, a differential device in which a differential limiting mechanism is added to a convex is set according to a request from a vehicle user or a request from a vehicle manufacturer for a vehicle system.

  However, if a differential limiting mechanism is added to the convex, not only the entire differential device is enlarged, but also the position of the support portion is moved. For this reason, for example, the carrier is also enlarged and the differential device is supported. Since the interval between the supporting parts becomes wider, or the position of the connecting part with the output shaft moves in the axial direction, the carrier and the output shaft are different from those determined based on the convex as described above. The compatibility with the model for adding the movement limiting mechanism is reduced, and there is a restriction on the mounting property on the vehicle.

  Therefore, the present invention relaxes the restrictions on the mountability on the vehicle by improving the compatibility with the peripheral members between the convex and the differential limiting mechanism addition model, and the degree of freedom in designing the differential device. It is an object of the present invention to provide a differential device that can improve the performance.

  According to the first aspect of the present invention, a differential case that is rotated by a driving force of a drive source, a pair of output members that transmit a drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case A carrier comprising: a differential mechanism that includes a differential member that distributes to the output member and that couples the pair of output members in a relatively rotatable manner; and a differential limiting mechanism that limits the differential rotation of the differential mechanism. In the differential device accommodated in the first and second output devices, the pair of output members have connection portions respectively connected to the pair of output shafts, and at least one of the connection portions extends inward in the rotation axis direction of the output member. It is formed in the inner peripheral side of 1 cylindrical part, It is characterized by the above-mentioned.

  Invention of Claim 2 is the differential apparatus of Claim 1, Comprising: The said differential member is a pinion shaft rotating integrally with the said differential case, and the pinion rotatably supported by this pinion shaft, The connecting portion extends inward in the radial direction of the pinion shaft.

  Invention of Claim 3 is a differential apparatus of Claim 2, Comprising: The said pinion shaft is equipped with the 2nd cylindrical part on the radial inside, and this 2nd cylindrical part is between the said output members. It is characterized by being supported by each other.

  The invention of claim 4 is the differential device according to claim 3, wherein the output member is provided with a recess on the outer surface in the rotational axis direction, the differential case is provided with a side wall and a convex portion on the axial inner side surface of the side wall, The output member is supported with respect to the differential case by fitting the concave portion and the convex portion.

  A fifth aspect of the present invention is the differential apparatus according to the fourth aspect, wherein the differential limiting mechanism is disposed radially outside a connecting portion between the output member and the differential member. .

  According to a sixth aspect of the present invention, there is provided a differential case that is rotated by a driving force of a drive source, a pair of output members that transmit a drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case. A bearing comprising: a differential mechanism that includes a differential member that distributes to the output member and that couples the pair of output members in a relatively rotatable manner; and a differential limiting mechanism that limits differential rotation of the differential mechanism. A pair of output members each having a connection portion connected to a pair of output shafts, wherein at least one of the connection portions is provided outside the output member in the rotation axis direction. It is characterized in that it is formed on the inner peripheral side of the third cylindrical portion formed inside the bearing in the radial direction.

  A seventh aspect of the present invention is the differential apparatus according to the sixth aspect, wherein the differential limiting mechanism includes an actuator that controls differential limiting of the differential mechanism, and the differential case rotates the actuator radially inward. A fourth cylindrical portion supported by the bearing across the actuator in the axial direction is provided, and the fourth cylindrical portion is supported on the outer peripheral side of the connecting portion with respect to the third cylindrical portion. It is characterized by that.

  The invention according to claim 8 is a differential case that is rotated by a driving force of a driving source, a pair of output members that transmit a driving torque input to the differential case to a pair of output shafts, and a driving torque that is input to the differential case. A carrier comprising: a differential mechanism comprising a differential member that distributes to the output member and connects the pair of output members so as to be relatively rotatable; and a differential limiting mechanism that limits the differential rotation of the differential mechanism. A differential device housed in an actuator, wherein the differential limiting mechanism includes an actuator for controlling differential limiting of the differential mechanism, and the differential case is a flange formed by a single member to which driving torque from the engine is input And the actuator is arranged inside the flange in the radial direction.

  A ninth aspect of the present invention is the differential apparatus according to the eighth aspect, characterized in that a rib is formed on the radially outer side of the flange portion.

  A tenth aspect of the present invention is the differential apparatus according to any one of the first, sixth, and eighth aspects, wherein a center of the differential mechanism does not include a differential limiting mechanism mounted on the carrier. 2 is set at a position different from the center of the differential mechanism in the differential unit in the rotational axis direction, and the inner ends of the pair of output shafts in the rotational axis direction are axial directions with respect to the center of the differential mechanism of the second differential unit It arrange | positions in the symmetrical position, It is characterized by the above-mentioned.

  Invention of Claim 11 is a differential apparatus as described in any one of Claim 1,6,8, Comprising: The 1st center between the said connection parts is a 2nd center between a pair of output members. On the other hand, it is displaced in the direction of the rotation axis.

  A twelfth aspect of the present invention is the differential apparatus according to any one of the first, sixth, and eighth aspects, wherein the connecting portion is asymmetric with respect to a second center between the pair of output members. It is characterized by being.

  The invention according to claim 13 is a differential case that is rotated by a driving force of a drive source, a pair of output members that transmit a driving torque input to the differential case to a pair of output shafts, and a driving torque that is input to the differential case. A differential mechanism comprising a differential mechanism that includes a differential member that distributes to the output member and connects the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits the differential rotation of the differential mechanism. The differential limiting device includes an actuator that controls differential limiting of the differential mechanism, and the actuator receives an operation force in an axial direction by an electromagnetic coil and a magnetic force of the electromagnetic coil. An electromagnetic actuator including a plunger, wherein the electromagnetic coil is supported by the carrier, and the differential case is a part of a magnetic path of the electromagnetic coil Configured, the plunger is characterized by being supported by the differential case.

  According to a fourteenth aspect of the present invention, there is provided a differential case that is rotated by a driving force of a drive source, a pair of output members that transmit a drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case. A differential mechanism comprising a differential mechanism that includes a differential member that distributes to the output member and connects the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits the differential rotation of the differential mechanism. The differential limiting device includes an actuator that controls differential limiting of the differential mechanism, and the differential limiting mechanism and the actuator are arranged with respect to an axial center of the differential mechanism. A transmission mechanism is provided which is disposed on each side opposite to the axial direction and transmits the operating force of the actuator to the differential limiting mechanism.

  Since the differential device according to claim 1 is formed on the inner peripheral side of the first cylindrical portion provided with at least one connecting portion on the inner side in the rotation axis direction of the output member, the differential device with the convex and the differential limiting mechanism And the output shaft can be shared with each other, and the carrier can be shared.

  Therefore, it is not necessary to set output shafts and carriers with different dimensions for a convex and a model with a differential limiting mechanism, respectively, and the compatibility with peripheral members is prevented from being lowered, and the restrictions on mounting on a vehicle are eased. The As a result, the degree of freedom in designing the differential device can be improved.

  In the differential apparatus according to the second aspect, since the connecting portion is provided on the radially inner side of the pinion shaft, the axial dimension of the entire differential apparatus can be remarkably reduced.

  Even if the connecting portion between the output shaft and the output gear fluctuates in the axial direction, the connecting portion can be set because the connecting portion is provided on the radially inner side of the pinion shaft.

  In the differential device according to the third aspect, since the second cylindrical portion is supported with the output member, the support of the output member is stable.

  In the differential device according to the fourth aspect, since the concave portion and the convex portion are fitted and the output member is supported with respect to the differential case, the output member can be reliably supported without increasing the size of the differential case to the outside in the axial direction. It becomes.

  In the differential device according to the fifth aspect, since the differential limiting mechanism is disposed on the radially outer side of the connecting portion between the output member and the differential member, the differential case does not increase in size in the axial direction.

  The differential device according to claim 6 is different in that at least one of the connecting portions is formed on the radially inner side of the bearing on the inner peripheral side of the second cylindrical portion provided on the outer side in the rotation axis direction of the output member. Correspondence to the output shaft of the length is improved.

  Therefore, there is no need to set output shafts and carriers with greatly different dimensions for the convex and differential limiting models, preventing a drop in compatibility with peripheral members and reducing restrictions on mounting on vehicles. Is done. As a result, the degree of freedom in designing the differential device can be improved.

  In the differential device according to the seventh aspect, since the second cylindrical portion is supported on the outer peripheral side of the connecting portion with respect to the third cylindrical portion, the support state of the output member is greatly improved.

  In the differential device according to the eighth aspect, since the actuator is disposed radially inward of the flange portion, the output shaft and the carrier can be shared between the convex and the differential device with a differential limiting function.

  Accordingly, it is not necessary to set output shafts and carriers having greatly different dimensions, preventing deterioration of compatibility with peripheral members, eliminating restrictions on vehicle mounting, and improving the degree of freedom in design of the differential device.

  In the differential device according to the ninth aspect, since the rib is formed on the radially outer side of the flange portion, the strength of the flange portion is improved accordingly.

  In the differential device according to claim 10, the center of the differential mechanism is set to a position different from the center of the differential mechanism in the second differential device not including the differential limiting mechanism mounted on the carrier in the rotation axis direction, Since the inner ends of the pair of output shafts in the rotational axis direction are arranged in an axially symmetrical position with respect to the center of the differential mechanism of the second differential device, for example, a long output shaft can be used on one side Therefore, a short output shaft can be used on the other side, and compatibility with output shafts of different lengths is improved, so the output shaft and the carrier are shared between the convex and the differential device with a differential limiting function. This eliminates the need to set output shafts and carriers having greatly different dimensions, prevents the compatibility with peripheral members from being lowered, and restricts the vehicle mountability. There is eliminated, the degree of freedom in design of the differential device can be improved.

  The differential apparatus according to claim 11 is configured such that the first center between the connecting portions is displaced in the direction of the rotation axis with respect to the second center between the pair of output members, whereby the compatibility of the output shafts (different lengths). (Correspondence to the output shaft) is improved accordingly.

  In the differential device according to claim 12, compatibility of the output shaft (correspondence to output shafts of different lengths) is improved by making the connecting portion asymmetric with respect to the second center of the pair of output members. .

  In the differential device according to the thirteenth aspect, the electromagnetic coil is disposed on the differential case so as to be relatively rotatable and is not rotated between the differential coil and the carrier. Instead, the electromagnetic coil is directly supported by the carrier, and the differential case is attached to the magnetic path of the electromagnetic coil. Since the plunger is supported by a differential case, the actuator is reduced in size accordingly.

  Therefore, the actuator does not interfere with the bearing even if it is arranged on the ring gear side.

  In addition, since the actuator is downsized, the offset between the differential mechanism and the differential unit is no longer necessary, or the amount of offset is minimized, minimizing the drop in compatibility of the output shaft and carrier. Can be fastened.

  The differential device according to claim 14 is configured such that the differential limiting mechanism portion and the actuator portion are separated from each other and are arranged on opposite sides in the axial direction with respect to the axial center of the differential mechanism, thereby separating the differential limiting mechanism portion. As a result, the actuator portion is reduced in size.

  Therefore, the actuator does not interfere with the bearing even if it is arranged on the ring gear side.

  In addition, since the actuator is downsized, the offset between the differential mechanism and the differential unit is no longer necessary, or the amount of offset is minimized, minimizing the drop in compatibility of the output shaft and carrier. Can be fastened.

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

(First embodiment)
The first embodiment will be described with reference to FIGS.

  A differential device 1 according to the present embodiment includes a differential case 2 that rotates by a driving force of a drive source, and a pair of output gears (a pair of output members) that transmit drive torque input to the differential case 2 to a pair of output shafts 51 and 52. 21 and 22 and a differential mechanism comprising a pinion 19 that distributes the drive torque input to the differential case 2 to the pair of output gears 21 and 23 and connects the pair of output gears 21 and 22 in a relatively rotatable manner. 13 and a differential limiting mechanism for limiting the differential rotation of the differential mechanism 13 are accommodated in the carrier 53.

  Further, in the differential device 1 of the present embodiment, the pair of output gears 21 and 22 have connecting portions 35 and 36 that are connected to the pair of output shafts 51 and 52, respectively, and at least one of the connecting portions 35 or 36 is an output gear. 21 and 22 are formed on the inner peripheral side of the first cylindrical portion 25 or 26 extending inward in the rotation axis direction. In the differential device of the present embodiment, part of the output gears 21 and 22 is arranged on the inner diameter side of the pinion shaft 14.

  As shown in FIG. 1, the differential case 2 includes a case body 4 and a cover body 3 that closes one side opening of the case body 4, and right and left axles are inserted through the case body 4 and the cover body 3, respectively. Boss portions 5 and 6 are formed. The differential case 2 is rotatably supported inside the differential carrier 53 via bearings by these boss portions 5 and 6. On the inner side in the axial direction of the left and right wall portions 7 and 8 of the differential case 2, annular convex portions 9 and 10 are projected. The annular convex portions 9 and 10 are fitted into the annular concave portions 30 and 31 of the output gears 21 and 22. Oil grooves 11 and 12 for lubricating the differential case 2 and the output gears 21 and 22 are formed on the outer periphery of the annular protrusions 9 and 10. Further, a ring gear (not shown) is fixed to the differential case 2 with a bolt, and the driving force of the engine is transmitted by meshing with a gear of a power transmission system that transmits the driving force of the engine. 2 is driven to rotate and the driving force is transmitted to the left and right axles via the differential mechanism 13.

  The differential mechanism 13 includes a pinion shaft 14, a pinion 19 rotatably supported on the pinion shaft 14, and a pair of coupling portions 35 and 36 that mesh with the pinion 19 and are coupled to a pair of output shafts, respectively. It comprises output gears 21 and 22.

  The pinion shaft 14 is supported on both sides of the end portion 15 by cam rings 39 and 39 splined to the inner periphery of the differential case 2, and is rotationally driven integrally with the differential case 2 and the cam rings 39 and 39. In addition, on the inner diameter side of the pinion shaft 14, support portions (second cylindrical portions) 16 and 17 that support boss portions 25 and 26 of a pair of output gears 21 and 22 described later are formed. A pair of output gears 21 and 22 are positioned and supported by these support portions 16 and 17. As shown in FIG. 2, the pinion shaft 14 has four support portions 18, 18, 18, 18, and the pinions 19, 19, 19, 19 are rotatable on each support portion 18. Each is supported.

  Each pinion 19 has meshing teeth 20 that mesh with meshing teeth 27 and 28 of a pair of output gears 21 and 22, transmits driving force from the engine to the pair of output gears 21 and 22, and outputs a pair of outputs. When differential rotation occurs in the gears 21 and 22, the gears 21 and 22 are driven to rotate.

  As shown in FIG. 1, the pair of output gears 21, 22 includes an output gear main bodies 23, 24 and a boss portion (first cylindrical shape) projecting on the opposed surfaces of the output gear main bodies 23, 24 facing each other. Part) 25 and 26, and meshing teeth 27 and 28 meshing with the meshing teeth 20 of each pinion 19. The meshing teeth 29 and 29 are formed by the meshing teeth 27 and 28 and the meshing teeth 20 of each pinion 19. On the back side of the meshing portion 29, annular concave portions 30 and 31 that fit into the annular convex portions 9 and 10 of the differential case 2 are formed. The annular recesses 30 and 31 and the annular projections 9 and 10 of the differential case 2 form support portions 32 and 33.

  Sliding materials 34 and 34 are arranged on the outer diameter side of the support portions 32 and 33. The sliding members 34 and 34 receive the gear reaction forces of the output gears 21 and 22 and the pinions 19. The boss portions 25 and 26 of the pair of output gears 21 and 22 are supported by the support portions 16 and 17 on the inner diameter side of the pinion shaft 14, and connecting portions 35 and 36 are provided inside the boss portions 25 and 26. The axles connected to the left and right wheels are splined to these connecting portions 35 and 36. And the drive force from an engine is transmitted to the wheel side by the connection parts 35 and 36. FIG. Differential limiting means is provided on the outer periphery of the output gear bodies 23 and 24.

  The differential limiting means is fastened by cam rings 39, 39 provided between the pinion 19 and the inner wall of the differential case 2 and splined to the inner wall of the differential case 2 so as to be axially movable, and by movement of the cam rings 39, 39 in the axial direction. The multi-plate clutches 37 and 37 are configured.

  As shown in FIGS. 1 and 2, four grooves 42, 42, 42, 42 are formed in the cam rings 39, 39 at equal intervals in the circumferential direction. These grooves 42 have inclined surfaces 41, 41 that are inclined toward the central portion 40. The four end portions 15, 15, 15, 15 of the pinion shaft 14 are sandwiched and supported between the grooves 42, 42 of the two cam rings 39, 39, respectively.

When there is no differential in the output gears 21 and 22, the end portions 15 of the pinion shaft 14 are positioned in the central portions 40 of the grooves 42 and 42 of the cam rings 39 and 39. In this state, when a differential occurs in the output gears 21 and 22, each pinion 19 is rotationally driven and a meshing reaction force is generated at the meshing portion 29, and the pinion shaft 14 that supports each pinion 19 is clockwise in FIG. Or move counterclockwise. At this time, each end 15 of the pinion shaft 14 is positioned on the inclined surfaces 41 and 41 of the groove 42 of the cam ring 39. Due to the movement of each end 15 of the pinion shaft 14, a cam thrust force is generated between the end 15 of the pinion shaft 14 and the inclined surfaces 41 and 41 of the grooves 42 and 42 of the left and right cam rings 39 and 39. This cam thrust force causes the cam rings 39, 39 to move outward in the axial direction so that the multi-plate clutch 37,
37 is fastened.

  The multi-plate clutches 37 and 37 include a plurality of outer friction plates 43 splined to the inner periphery of the differential case 2 and a plurality of inner friction plates 38 splined to the outer peripheries of the output gears 21 and 22. 39 is arranged on the outer side in the axial direction of 39 and on the outer diameter side of the meshing portion 29. The multi-plate clutch 37 is fastened by the movement of the cam rings 39, 39 in the axial direction, connects the output gears 21, 22 and the differential case 2, and limits the differential of the differential mechanism 13.

  In the differential device 1 in the present embodiment, the support portions 16 and 17 of the output gears 21 and 22 are provided on the inner diameter side of the pinion shaft 14, and the boss portions 25 and 26 of the output gears 21 and 22 are provided on the inner diameter side of the pinion shaft 14. Since it is arranged, the axial dimension of the entire differential device 1 can be significantly reduced.

  Further, by arranging the boss portions 25 and 26 of the output gears 21 and 22 on the inner diameter side of the pinion shaft 14, even if the connecting portions 35 and 36 between the output shaft and the output gears 21 and 22 fluctuate in the axial direction, the connecting portions Since 35 and 36 can be set, compatibility between members constituting the differential device and the degree of freedom of design of the differential device are improved.

  Furthermore, since the output gears 21 and 22 are supported inside the pinion shaft 14, the support of the output gears 21 and 22 is stabilized. Further, since the connecting portions 35 and 36 between the output shaft and the output gears 21 and 22 are provided on the inner side of the pinion shaft 14, the axial direction of the entire differential device 1 without changing the length of the connecting portions 35 and 36. The dimensions can be reduced.

  Further, since the four pinions 19, 19, 19, 19 are rotatably supported on the pinion shaft 14, the differential device 1 having a small size and high strength can be obtained.

  Further, the output gears 21, 22 are supported by annular convex portions 9, 10 that have annular concave portions 30, 31 on the back side of the meshing portion 29 and project inward in the axial direction from the wall portions 7, 8 of the differential case 2. As a result, the output gears 21 and 22 can be reliably supported without increasing the size of the differential case 2 outward in the axial direction, and the differential device 1 can be made compact.

  A sliding member 34 is disposed between the output gears 21 and 22 and the wall portions 7 and 8 of the differential case 2 on the outer diameter side of the support portions 32 and 33 including the concave portions 30 and 31 and the convex portions 9 and 10. Therefore, the gear reaction force of the output gears 21 and 22 can be received by the sliding member 34. Further, the differential case 2 is provided with support portions for the output gears 21 and 22 so that the gear reaction force of the output gears 21 and 22 is received not by the differential case 2 but directly by the sliding material 34 and the outside of the sliding material 34 is not restricted. Therefore, the surface pressure of the differential case that receives the gear reaction force of the output gears 21 and 22 is reduced, and the sliding characteristics are stabilized.

  Furthermore, since the multi-plate clutch 37 for limiting the differential between the output gears 21 and 22 and the differential case 2 is disposed on the outer diameter side of the meshing portion 29 between the output gears 21 and 22 and each pinion 19, The differential apparatus 1 can be made compact without increasing the size of the differential case 2 in the axial direction.

  Further, since the connecting portions 35, 36, the meshing portion 29, and the multi-plate clutch 37 overlap in the radial direction (because the multi-plate clutch 37 is disposed on the radially outer side of the meshing portion 29). The differential device 1 can be further downsized. Moreover, since the support parts 32 and 33 which consist of the recessed parts 30 and 31 and the convex parts 9 and 10 and the multi-plate clutch 37 overlap in the radial direction, the differential apparatus 1 can be made further compact.

  In the differential apparatus 1 of the present embodiment, the four pinions 19, 19, 19, 19 are used, but two pinions may be used.

(Second Embodiment)
A second embodiment will be described with reference to FIG.

  A differential apparatus 100 according to the present embodiment includes a differential case 101 that is rotated by a driving force of a drive source, and a pair of output gears (output members) 114 that transmit driving torque input to the differential case 101 to a pair of output shafts 151 and 152. 118 and a pinion (differential member) 112 that distributes the drive torque input to the differential case 101 to the pair of output gears 114 and 118 and connects the pair of output gears 114 and 118 in a relatively rotatable manner. A differential mechanism 109 and a differential limiting mechanism for limiting the differential rotation of the differential mechanism 109 are provided in a carrier.

  In addition, the differential apparatus 100 of the present embodiment includes connection portions 129 and 130 that connect the pair of output gears 114 and 118 to the pair of output shafts 151 and 152, respectively, and at least one of the connection portions 129 is the output gear 114. It is formed on the inner peripheral side of a boss portion (first cylindrical portion) 116 extending inward in the rotation axis direction. Also in this embodiment, a part of the output gear 114 is disposed on the inner diameter side of the pinion shaft 110.

  As shown in FIG. 3, the differential case 101 includes a case main body 103 and a cover body 102 that closes one side opening of the case main body 103, and boss portions 104 and 105 through which the left and right axles are inserted are formed. ing. A differential case 101 is rotatably supported inside a differential carrier (not shown) via a bearing on the outer peripheral side of these boss portions 104 and 105. On the inner side in the axial direction of the left wall portion 106 of the differential case 101, an annular convex portion 107 projects. The annular convex portion 107 is fitted into the annular concave portion 124 of the output gear 114. The boss portion 105 of the differential case 101 is formed with a support portion 108 that supports the boss portion 116 of the output gear 114. Further, a ring gear (not shown) is fixed to the differential case 101 with a bolt, and the driving force of the engine is transmitted by meshing with a gear of a power transmission system that transmits the driving force of the engine. The drive force is transmitted to the left and right axles via the differential mechanism 109 by being driven to rotate.

  The differential mechanism 109 includes a pinion shaft 110, a pinion 112 rotatably supported on the pinion shaft 110, and a pair of coupling portions 129 and 130 that mesh with the pinion 112 and are coupled to a pair of output shafts, respectively. It comprises output gears 114 and 118.

  The end of the pinion shaft 110 is connected to the differential case 101 and is driven to rotate integrally with the differential case 101. A pinion 112 is supported on the pinion shaft 110. The pinion 112 has meshing teeth 111 that mesh with meshing teeth 117 and 121 of a pair of output gears 114 and 118, and transmits a driving force from the engine to the pair of output gears 114 and 118, and a pair of output gears 114. , 118 is driven to rotate when a differential rotation occurs. Further, a support portion 113 for supporting the boss portion 116 of the output gear 114 is formed on the inner diameter side of the intermediate portion of the pinion shaft 110. The output gear 114 is positioned and supported by the support portion 113.

  The output gear 114 includes an output gear main body 115, a boss portion 116 that protrudes inward in the axial direction of the output gear main body 115, and meshing teeth 117 that mesh with the meshing teeth 111 of the pinion 112. The output gear 118 includes an output gear main body 119, a boss portion 120 projecting outward in the axial direction of the output gear main body 119, and meshing teeth 121 that mesh with the meshing teeth 111 of the pinion 112. The meshing teeth 122 and 123 are formed by the meshing teeth 117 and 121 of the pair of output gears 114 and 118 and the meshing tooth 111 of the pinion 112.

  On the back side of the meshing portion 122, an annular concave portion 124 that fits into the annular convex portion 107 of the differential case 101 is formed. The annular concave portion 124 and the annular convex portion 107 of the differential case 101 form a support portion 125. A sliding member 126 is disposed on the outer diameter side of the support portion 125.

  A boss portion 120 is formed on the back side of the meshing portion 123 and is supported by the support portion 108 of the differential case 101. A sliding member 128 is disposed between the support portion 108 and the tip portion 127 on the axially outer side of the boss portion 120.

  The sliding materials 126 and 128 receive the gear reaction force of the output gears 114 and 118 and the pinion 112. The boss portion 116 of the output gear 114 is supported by a support portion 113 on the inner diameter side of the pinion shaft 110. Connecting portions 129 and 130 are provided inside the boss portions 116 and 120 of the output gears 114 and 118, and the axles connected to the left and right wheels are splined to these connecting portions 129 and 130. And the driving force from an engine is transmitted to the wheel side by the connection parts 129 and 130. Main clutches 143 and 143 which are differential limiting means are provided on the outer periphery of the output gear main bodies 115 and 119.

  The differential limiting mechanism includes an electromagnet 131, an annular armature 135 disposed so as to be movable in the axial direction by the magnetic attraction force of the electromagnet 131, a pilot clutch 136 that is fastened by movement of the armature 135 in the axial direction, A cam mechanism 139 that generates a thrust force when the pilot clutch 136 is engaged, an annular pressure ring 141 that transmits the thrust force of the cam mechanism 139 to the main clutch 143, and a main that is engaged by movement of the pressure ring 141 in the axial direction. And a clutch 143 for limiting the differential of the differential mechanism 109.

  The electromagnet 131 includes an electromagnetic coil 132 and a core 133, is fixed to the differential carrier, and is supported on the outer periphery of the boss portion 105 of the differential case 101 via a bearing 134. The annular armature 135 is made of a magnetic material and is disposed on one side of the electromagnet 131 with the pilot clutch 136 interposed therebetween.

  The pilot clutch 136 includes a plurality of outer friction plates 137 splined to the inner periphery of the differential case 101 and a plurality of inner friction plates 138 splined to the outer periphery of the cam ring 140, and is disposed between the electromagnet 131 and the armature 135. Is arranged. The pilot clutch 136 is fastened when the armature 135 is attracted to the electromagnet 131 side when the electromagnet 131 is energized, and a differential rotation occurs between the cam ring 140 and the pressure ring 141, thereby causing the cam mechanism 139 to perform a cam thrust force. Is generated.

  The cam mechanism 139 is cam ring 140 fitted to the outer periphery of the boss portion 120 of the output gear 118, and the outer periphery of the boss portion 120 of the output gear 118 can move relative to the output gear 118 in the axial direction and can rotate integrally with the rotation direction. A pressure ring 141 made of a low magnetic material and a cam ball 142 arranged between the cam ring 140 and the pressure ring 141. When the pilot clutch 136 is engaged, a differential rotation occurs between the cam ring 140 and the pressure ring 141 connected to the pilot clutch 136, and the pressure ring 141 is moved to the main clutch 143 side by the cam thrust force of the cam mechanism 139. The main clutches 143 and 143 are engaged.

  The main clutches 143 and 143 include outer friction plates 144 and 144 splined to the inner periphery of the differential case 101 and inner friction plates 145 and 145 splined to the outer periphery of the output gear bodies 115 and 119. The main clutches 143 and 143 are fastened by the pressure ring 141 moved to the main clutch 143 side by the fastening of the pilot clutch 136. When the main clutches 143 and 143 are engaged, the differential case 101 and the output gears 114 and 118 are connected to limit the differential of the differential mechanism 109.

  In the differential device 100 according to the present embodiment, the support portion 113 of the output gear 114 is provided on the inner diameter side of the pinion shaft 110 and the boss portion 116 of the output gear 114 is disposed on the inner diameter side of the pinion shaft 110. The overall axial dimension of 100 can be significantly reduced.

  Further, by arranging the boss portion 116 of the output gear 114 on the inner diameter side of the pinion shaft 110, the connecting portion 129 can be set even if the connecting portion 129 between the output shaft and the output gear 114 varies in the axial direction. The compatibility between members constituting the differential device and the degree of freedom in designing the differential device are improved.

  Furthermore, since the output gear 114 is supported inside the pinion shaft 110, the support of the output gear 114 is stabilized. Further, since the connecting portion 129 between the output shaft and the output gear 114 is provided on the inner side of the pinion shaft 110, the axial dimension of the entire differential device 100 can be reduced without changing the length of the connecting portion 129. it can.

  The output gear 114 has an annular recess 124 on the back side of the meshing portion 122 and is supported by an annular projection 107 that protrudes inward in the axial direction from the wall portion 106 of the differential case 101. The output gear 114 can be reliably supported without increasing the size outward in the axial direction, and the differential device 100 can be made compact.

  Further, since the sliding member 126 is disposed between the output gear 114 and the wall portion 106 of the differential case 101 on the outer diameter side of the support portion 125 including the concave portion 124 and the convex portion 107, the gear of the output gear 114. The reaction force can be received by the sliding material 126. Further, the differential case 101 is provided with a support portion for the output gear 114 so that the gear reaction force of the output gear 114 is not directly received by the differential case 101 but is received by the sliding material 126, and the outside of the sliding material 126 is not restricted. The surface pressure of the differential case that receives the gear reaction force 114 is reduced, and the sliding characteristics are stabilized.

  Further, since the main clutch 143 for limiting the differential between the output gears 114 and 118 and the differential case 101 is disposed on the outer diameter side of the meshing portions 122 and 123 between the output gears 114 and 118 and the pinion 112, The differential apparatus 100 can be made compact without increasing the size of the differential case 101 in the axial direction.

  Furthermore, since the connecting portion 129, the meshing portion 122, and the main clutch 143 overlap in the radial direction, the differential device 100 can be further downsized. Further, since the support portion 125 including the concave portion 124 and the convex portion 107 and the main clutch 143 overlap in the radial direction, the differential device 100 can be further downsized.

  Note that the differential apparatus 100 of the present embodiment may have four pinions. In this case, it is possible to obtain a differential device 100 that is small but has high strength.

(Modification)
In the first and second embodiments, the connecting portions 35, 36, and 129 between the output shaft and the output gears 21, 22, and 114 are arranged on the inner diameter side of the pinion shafts 14 and 110. 4, a support portion 203 that positions and supports the output gear 202 is provided on the inner diameter side of the pinion shaft 201, and a protrusion 204 that is supported by the support portion 203 is provided on the output gear 202. It is good also as only the support part 205 formed by 203 and the protrusion 204. FIG. Also in this case, the strength of the output gear 202 is improved and the axial dimension of the differential device 200 can be reduced.

  4 has the same basic configuration as that of the differential apparatus 100 shown in FIG. 3, and the difference between the differential case 206, the differential mechanism 207 accommodated in the differential case 206, and the differential mechanism 207. And differential limiting means for performing dynamic limiting. The differential limiting means includes an electromagnet 208, an annular armature 209 that is arranged to be movable in the axial direction by the magnetic attraction force of the electromagnet 208, and a pilot clutch 210 that is fastened by movement of the armature 209 in the axial direction. And a cam mechanism 211 that generates a thrust force when the pilot clutch 210 is engaged, an annular pressure ring 212 that transmits the thrust force of the cam mechanism 211 to the main clutch 213, and an axial movement of the pressure ring 212. Main clutches 213 and 213 for limiting the differential of the differential mechanism 207.

(Third embodiment)
A differential apparatus (hereinafter referred to as “rear differential”) 301 (a third embodiment of the present invention) will be described with reference to FIGS. 5 and 12. In the following description, the left and right directions are the four-wheel drive vehicle (FIG. 12) in which the rear differential 1 is used and the left and right directions in FIG.

[Features of rear differential 301]
The rear differential 301 is input to the differential case 307, a differential case 307 that is rotated by a driving force of a drive source, a pair of output members 315 and 317 that transmit drive torque input to the differential case 307 to a pair of output shafts 323 and 325. A differential mechanism 319 including a differential member 309 that distributes driving torque to the pair of output members 315 and 317 and connects the pair of output members 315 and 317 in a relatively rotatable manner, and the differential mechanism 319 A differential limiting mechanism 321 for limiting differential rotation is provided and supported by the carrier via a bearing 303.

  Further, the rear differential 301 of the present embodiment includes connecting portions 327 and 329 that connect the pair of output members 315 and 317 to the pair of output shafts 323 and 325, respectively, and at least one of the connecting portions 329 is the output member 315. Is formed on the inner peripheral side of the first sleeve (third cylindrical portion) 331 that extends outward in the rotation axis direction and on the inner side in the radial direction of the bearing 303.

  In addition, the differential device 301 of the present embodiment includes a first sleeve 331 in which an output member (hereinafter referred to as “side gear”) 317 is positioned (formed) on the outer side in the rotation axis direction with respect to the meshing portion 313, and includes a spline portion 329. Is formed on the inner periphery of the first sleeve 331, the differential limiting device 321 includes an electromagnetic actuator 333 that controls the differential limiting function, and the differential case 307 rotates the actuator 333 radially inward of the actuator 333. A second sleeve (third cylindrical portion) 335 straddling the axial direction is included, and the first sleeve 331 is supported on the outer peripheral side of the spline portion 329 by the second sleeve 335, and the differential limiting device 321 is The outer side in the radial direction of the meshing part 311 of the side gear 315 and the meshing part 313 of the side gear 317, respectively. It is located.

  Further, the side gear 315 has a concave portion 337 on the outer surface in the rotation axis direction, and the side wall of the differential case 307 has a convex portion 339 on the inner surface in the rotation axis direction, and the convex portion 339 and the concave portion 337 engage with each other. A differential case 307 is supported.

  Further, the first center between the spline portions 327 and 329 is displaced in the rotational axis direction with respect to the second center S (intersection of the meshing pitch lines) between the side gears 315 and 317. .

[Configuration of Power System of Four-wheel Drive Vehicle in FIG. 12]
This power system includes a vertically installed engine 801 (prime mover), a transmission 803 and a transfer 805, a 2-4 switching mechanism 807 constituting a part of the transfer 805, a propeller shaft 809 on the front wheel side, and a front differential 811 (prime mover). ), The front axles 813 and 815, the left and right front wheels 817 and 819, the rear wheel side propeller shaft 821, and the rear differential 301 of the first embodiment (drive of the prime mover). And a rear axle 823, 825, left and right rear wheels 827, 829, a controller, and the like.

  The 2-4 switching mechanism 807 intermittently drives the driving force of the engine 801 between the output shaft of the transmission 803 and the front wheel side propeller shaft 809, and the output shaft of the transmission 803 is connected to the rear wheel side propeller shaft 821 via the transfer 805. The driving force is transmitted to

  The front differential 811 includes a differential case 831 that rotates by receiving driving force, a bevel gear type differential mechanism 833 coupled to the differential case 831, and a differential limiting mechanism 835 that limits the differential of the differential mechanism 833. ing. The front wheel side propeller shaft 809 is connected to the differential case 831 via a gear transmission mechanism 837 and the like, and left and right output members of the differential mechanism 833 are connected to left and right front wheels 817 and 819 via front axles 813 and 815, respectively. ing.

  The driving force transmitted to the rear wheel side propeller shaft 821 is transmitted to the differential case 307 of the rear differential 301 via the drive pinion shaft 839 and the direction change gear set 841. The direction change gear set 841 is constituted by bevel gears 843 and 845, the bevel gear 843 is formed on the drive pinion shaft 839, and the bevel gear 845 is fixed to the differential case 307. The output shafts 323 and 325 are part of the rear axles 823 and 825, and the side gears 315 and 317 of the rear differential 301 are connected to the left and right rear wheels 827 and 829 via the rear axles 823 and 825, respectively.

  Hub clutches 847 and 849 are disposed between the front axles 813 and 815 and the left and right front wheels 817 and 819, respectively. The hub clutches 847 and 849 are operated by the controller, and the front axles 813 and 815 are connected to the left and right wheels. The front wheels 817 and 819 are intermittently connected.

  When the vehicle travels on four wheels, the controller connects the 2-4 switching mechanism 807 of the transfer 805 and connects the hub clutches 847 and 849. The driving force of the engine 801 input to the transfer 805 from the transmission 803 is transmitted from the propeller shaft 821 to the rear differential 301 and distributed to the left and right rear wheels 827 and 829, and the 2-4 switching mechanism 807 and the propeller shaft 809 are used. To the front differential 811 and distributed to the left and right front wheels 817 and 819.

  When the vehicle travels by two-wheel drive, the controller releases the connection of the 2-4 switching mechanism 807 and the connection of the hub clutches 847 and 849, respectively, and the vehicle enters the two-wheel drive state of the rear wheel drive.

[Configuration of rear differential 301]
The rear differential 301 includes a differential case 307, a differential mechanism 319, a differential limiting device 321, a return spring 341, a position switch 343, and the like. The differential limiting device 321 includes an electromagnetic actuator 333, a dog It comprises a clutch 345 and a controller.

  The differential case 307 includes a casing body 347 and a left cover 349, and the casing body 347 and the cover 349 are fixed with bolts 351. The differential case 307 is disposed inside the carrier 305, and the boss portion 353 (sleeve) of the cover 349 and the sleeve 337 of the casing body 347 are supported by the carrier 305 via bearings 303 that receive a thrust force. An oil reservoir is formed inside the carrier 305, and the differential case 307 is rotationally driven by the driving force of the engine as described above.

  Each pinion 309 of the differential mechanism 319 is rotatably supported on a plurality of pinion shafts 355 (output members), and the side gears 315 and 317 are engaged with the respective pinions 309. The inner ends of the pinion shafts 355 are engaged with each other by an engaging portion 356, and the outer ends are engaged with a through hole 357 provided in the differential case 307 (casing body 347), and are detached by a spring pin 359. It has been stopped.

  The dog clutch 345 includes a meshing tooth 361 welded to the right side gear 317 and a meshing tooth 365 formed on the clutch ring 363. The clutch ring 363 is prevented from rotating on the differential case 7 side and is arranged to be movable in the axial direction. When the clutch ring 363 moves to the left as in the lower half of FIG. 5, the dog clutch 345 engages and the differential of the differential mechanism 319 is locked, and the clutch ring 363 moves to the right as in the upper half of FIG. Then, the engagement of the dog clutch 345 and the differential lock are released. The return spring 341 is disposed between the right side gear 317 and the clutch ring 363, and urges the clutch ring 363 toward the engagement release side (right side) of the dog clutch 345.

  The electromagnetic actuator 333 includes an electromagnetic coil 367, a coil housing 369 that encloses the electromagnetic coil 367, a plunger 371, and the like. The coil housing 369 and the plunger 371 are made of a magnetic material (S10C) and form a magnetic path of the electromagnetic coil 367.

  A pressure plate 373 is connected to the clutch ring 363 of the dog clutch 345, and the pressing force of the electromagnetic actuator 333 (plunger 371) moves the clutch ring 363 to the right via the pressure plate 373 and attaches the return spring 341. The force pushes the plunger 371 back to the right via the clutch ring 363 and the pressure plate 373.

  The controller performs excitation and excitation stop of the electromagnetic coil 367.

  When the electromagnetic coil 367 is excited, the plunger 371 presses the clutch ring 363 via the pressure plate 373 and engages the dog clutch 345 to lock the differential of the differential mechanism 319. If the differential is locked in a situation where the left and right rear wheels 827 and 829 are likely to idle, such as when traveling on a rough road, escape performance and running performance on a rough road and the like are improved, and vehicle stacking is prevented.

  When excitation of the electromagnetic coil 367 is stopped, the meshing of the dog clutch 345 is released by the return spring 341, and the differential mechanism 319 becomes free.

  The position switch 343 is engaged (0FF-ON) with the movement of the pressure plate 373 when the dog clutch 345 is engaged, and displays the differential lock state of the rear differential 301 on the driver's seat.

[Effect of rear differential 301]
The rear differential 301 has the following effects.

  The spline portion 329 of the side gear 317 is provided on the outer side in the rotation axis direction of the meshing portion 313 with the pinion 309 and on the inner side in the radial direction of the bearing 303, and on the outer side of the meshing portion 313 of the side gear 317 in the rotation axis direction By providing the spline portion 329 on the inner periphery of the first sleeve 331, for example, it is possible to use a short one for the output shaft 325, thereby improving the compatibility with output shafts of different lengths. Therefore, the output shaft and the carrier 305 can be shared between the convex differential and the rear differential 301 which is a differential device with a differential limiting mechanism.

  Therefore, it is not necessary to set the output shaft and the carrier with different dimensions for the convex and the models with the differential limiting mechanism, respectively, the deterioration of compatibility with the peripheral members is prevented, the restriction on the vehicle mounting property is eliminated, and the differential The degree of freedom in designing the device is improved, and cost increases and misassembly are prevented.

  The differential case 307 is provided with a second sleeve 335 extending radially inward of the electromagnetic actuator 333 and straddling the actuator 333 in the axial direction. The sleeve 331 of the side gear 317 is supported by the sleeve 335 on the outer peripheral side of the spline portion 329. As a result, the support state of the side gear 317 is greatly improved.

  Further, the first center between the spline portions 327 and 329 is displaced in the direction of the rotation axis with respect to the second center S between the side gears 315 and 317, so that the compatibility of the output shaft (different) Therefore, the above effects can be more easily obtained.

  Further, the support state of the side gear 315 is greatly improved by being supported by the convex portion 339 of the differential case 7 by the concave portion 337.

  In addition, since the spline portion 329 of the right side gear 317 and the differential limiting device 321 (particularly, the dog clutch 345) overlap in the radial direction, the rear differential 301 is configured so compactly.

(Fourth embodiment)
The rear differential 401 (fourth embodiment of the present invention) will be described with reference to FIGS. A rear differential (differential device) 401 is used in place of the rear differential 301 in the four-wheel drive vehicle of FIG. In the following, the difference between the members having the same functions as those of the rear differential 301 will be described by giving the same reference numerals.

[Features of rear differential 401]
The differential device 401 according to the present embodiment includes a differential case 403 that is rotated by a driving force of a drive source, a pair of output members 315 and 317 that transmit driving torque input to the differential case 403 to a pair of output shafts 323 and 325, A differential mechanism 319 including a differential member 309 that distributes drive torque input to the differential case 403 to the pair of output members 315 and 317 and relatively rotatably connects the pair of output members 315 and 317; And a differential limiting mechanism 321 that limits differential rotation of the differential mechanism 319 and is supported by the carrier 305 via bearings 303 and 303.

  Further, the differential device 401 of this embodiment includes an actuator 333 in which the differential limiting mechanism 321 controls the differential limiting of the differential mechanism 319, and the differential case 403 is formed by a single member to which driving torque from the engine is input. And the actuator 333 is disposed inside the flange 405 in the radial direction.

  Moreover, in the differential apparatus 401 of this embodiment, the rib 407 is formed in the radial direction outer side of the flange part 405. FIG.

[Configuration of rear differential 401]
The differential case 403 is integrally formed and disposed inside the carrier 305, and the left and right boss portions 413 and 415 are supported on the carrier 305 via bearings 303. The differential case 403 is rotationally driven by the driving force of the engine input to the flange 405. The pinion shaft 355 of the differential mechanism 319 engages the outer end with the through hole 417 of the differential case 403.

  The meshing teeth 361 of the dog clutch 345 are welded to the left side gear 315, and the clutch ring 363 is prevented from rotating toward the differential case 403 and is disposed so as to be axially movable.

[Effect of rear differential 401]
The rear differential 401 has the following effects.

  By arranging the electromagnetic actuator 333 radially inside the flange 405 provided in the differential case 403, the output shaft and the carrier can be shared between the convex differential and the rear differential 401 (a differential device with a differential limiting mechanism). Therefore, it is not necessary to set the output shaft and the carrier having different dimensions, the compatibility with the peripheral members is prevented from being lowered, the restrictions on the vehicle mountability are eliminated, and the design freedom of the differential device is improved. Cost rise and misassembly are also prevented.

  Further, the rib 407 provided on the flange 405 improves the strength of the flange 405 accordingly.

  In addition, the rear differential 401 has the same effects as the rear differential 301 except for the effect of displacing the center S of each side gear 315, 317 with respect to the first center of the spline portions 327, 329 in the rotation axis direction. Is obtained.

(Fifth embodiment)
The rear differential 501 (fifth embodiment of the present invention) will be described mainly with respect to the differences from the rear differential 301 with reference to FIGS.

[Features of rear differential 501]
The rear differential 501 of the present embodiment includes a differential case 307 that is rotated by the driving force of a drive source, a pair of output members 315 and 317 that transmit drive torque input to the differential case 307 to a pair of output shafts 323 and 325, and the differential case. A differential mechanism 319 including a differential member 309 that distributes a drive torque input to the output member 307 to the pair of output members 315 and 317 and connects the pair of output members 315 and 317 in a relatively rotatable manner; And a differential limiting mechanism 321 that limits the differential rotation of the moving mechanism 319 and is supported by the carrier 305 via bearings 303 and 303.

  The pair of output members 315 and 317 have connection portions 327 and 329 that are connected to the pair of output shafts 323 and 325, respectively, and at least one of the connection portions 329 is outside the side gear (output member) 317 in the rotation axis direction. Is formed on the inner peripheral side of the third cylindrical portion 331 extending in the radial direction of the bearing 303.

  Further, the differential limiting mechanism 321 includes an actuator 333 that controls the differential limiting of the differential mechanism 319, and the differential case 307 extends over the actuator 333 radially inward and across the actuator 333 across the actuator 333. The fourth cylindrical portion 335 is supported, and the fourth cylindrical portion 335 is supported on the outer peripheral side of the connecting portion 329 with respect to the third cylindrical portion 331.

  Further, the first center G between the connecting portions 327 and 329 is displaced in the rotation axis direction with respect to the second center S between the pair of output members 315 and 317.

  Further, the connecting portions 327 and 329 are formed asymmetrically with respect to the second center S between the pair of output members 315 and 317.

[Configuration of rear differential 501]
The outer end portion of the pinion shaft 505 engages with the through hole 357 of the differential case 307 and is prevented from coming off by a spring pin 359. The sleeve 507 connects the inner end portion of the pinion shaft 505 by each engaging portion 513, and the side gear. The outer periphery of the sleeve 503 is supported by the inner periphery of the sleeve 507.

[Effect of rear differential 501]
The rear differential 501 has the following effects.

  By providing the spline portion 327 of the side gear 315 on the radially inner side of the pinion shaft 505, a long output shaft can be used on one side and a short output shaft can be used on the other side, and output shafts of different lengths can be used. Therefore, the output shaft and the carrier 305 can be shared between the convex differential and the rear differential 501 which is a differential device with a differential limiting mechanism. In addition, it is not necessary to set the carrier and the carrier, the compatibility with the peripheral members is prevented from being lowered, the restriction on the vehicle mountability is eliminated, the degree of freedom in designing the differential device is improved, and the cost increase and misassembly are prevented.

  Further, since the side gear 315 is supported by the sleeve 507 formed on the radially inner side of the pinion shaft 505, the support state of the side gear 315 is greatly improved.

  Further, the center S of the differential mechanism 319 is set at a different position in the axial direction with respect to the center G of the differential mechanism of the second differential device that does not include the differential limiting mechanism. By arranging the ends 209 and 211 at the same distance from the center G, the degree of freedom with respect to the length of the output shaft is further improved.

  In addition, the rear differential 501 can obtain the same effect as the rear differential 301.

(Sixth embodiment)
The rear differential 601 (sixth embodiment of the present invention) will be described with reference to FIGS. 9 and 12 mainly with respect to the differences from the rear differential 301. FIG.

[Features of rear differential 601]
The rear differential 301 according to the present embodiment is supported by a carrier 305 so as to be rotatable by bearings 303 and 303, a differential case 307 to which a driving torque of the engine 801 is input, a pinion 309, and meshing portions 311 and 313 for receiving and transmitting the driving torque. A bevel gear type differential mechanism 319 that includes first and second side gears 315 and 317 that are rotatably coupled to the pinion 19 and that can rotate coaxially with the differential case 307, and restricts differential rotation of the differential mechanism 319. The side gears 315 and 317 include spline portions 327 and 329 connected to the output shafts 323 and 325, respectively. The spline portion 329 of the side gear 317 is on the outer side in the axial direction of the meshing portion 313. It is positioned inside the bearing 303 in the radial direction.

  The side gear 317 has a fourth sleeve 603 formed on the outer side in the axial direction of the meshing portion 313, and the spline portion 329 is formed on the inner periphery of the sleeve 603.

  Further, the differential limiting device 321 includes an actuator 333, and the differential case 307 is formed with a second sleeve 335 straddling the actuator 333 in the radial direction inside the actuator 333, and the sleeve 331 is splined by the sleeve 335. 329 is supported on the outer peripheral side.

  Further, the differential limiting device 321 is disposed on the radially outer side of the meshing portion 311 of the side gear 315 and the meshing portion 313 of the side gear 317, and the side gear 315 has a recess 337 on the outer surface in the rotational axis direction, and the differential case 307. The side wall has a convex portion 339 on the inner surface in the rotation axis direction, and the differential case 307 supports the side gear 315 by the engagement of the convex portion 339 and the concave portion 337.

  The center S of the differential mechanism 319 is set at a different position in the rotational axis direction with respect to the center G of the differential mechanism in the second differential device that does not include the differential limiting device 321, and the output shafts 323 and 325 are connected to the respective axes. The first and second end portions 605 and 607 are provided on the inner side in the direction, and these end portions 605 and 607 are arranged at axially symmetrical positions with respect to the center G, and the first of the spline portions 327 and 329 Is displaced in the rotational axis direction with respect to the second center S of each side gear 315, 317.

[Effect of rear differential 601]
The rear differential 601 can provide the following effects.

  The center S of the differential mechanism 319 is set at a different position in the axial direction with respect to the center G of the differential mechanism of the second differential device that does not include the differential limiting mechanism, and the inner ends 509 of the output shafts 323 and 325 are set. , 511 are equidistant from the center G, a long output shaft can be used on one side and a short output shaft can be used on the other side, improving compatibility with output shafts of different lengths. Therefore, it is possible to share the output shaft and the carrier 305 between the convex differential and the rear differential 601 which is a differential device with a differential limiting mechanism. Therefore, the output shaft and the carrier having different dimensions are set respectively. This eliminates the need for compatibility with surrounding members, eliminates restrictions on vehicle mountability, improves the design freedom of differential devices, and increases costs. DOO wrong assembly is also prevented.

In addition, the rear differential 601 can obtain the same effects as the rear differential 301. (Seventh embodiment)
The rear differential 701 (seventh embodiment of the present invention) will be described with reference to FIG. The rear differential 701 is used in place of the rear differential 301 in the four-wheel drive vehicle of FIG. Hereinafter, the same reference numerals are given to the members having the same functions as the rear differential 1, and the differences will be described.

[Features of rear differential 701]
The rear differential 701 is housed in the carrier 305 and is rotated by a differential case 703 (input member) that can be rotated by an input engine driving torque, a rotatable pinion 309, and meshing portions 311 and 313 that receive and transmit the driving torque. And a differential mechanism 319 that can rotate coaxially with the differential case 703, and a differential limiting device 321 that limits the differential rotation of the differential mechanism 319. The movement limiting device 321 includes an electromagnetic actuator 333 that controls the differential limitation of the differential mechanism 319.

  The differential case 703 includes a flange 705 to which a ring gear 717 to which driving torque from the engine is input is fixed. The actuator 333 includes an annular coil 367 positioned on the outer peripheral side of the boss portion 711 of the differential case 703 and the coil 367. When an electric current is supplied to the electromagnetic solenoid coil 367, an electromagnetic solenoid comprising a coil housing 369 that annularly covers the outer peripheral side, one side wall in the axial direction, and a part of the inner peripheral side is provided. The electromagnetic actuator 333 includes a housing 369, an annular plunger 707, and a plunger 707 that receives a moving operation force in the axial direction by a magnetic force so as to act on a magnetic force line loop that passes through the side wall of the differential case 703. The electromagnetic solenoid is disposed on the ring gear 717 side and is supported by the carrier 305. The side wall of the differential case 703 forms part of the magnetic path of the electromagnetic solenoid, and the plunger 707 is supported on the outer periphery of the boss portion 711 of the differential case 703. It is characterized by being.

  In the above four-wheel drive vehicle, when driving a four-wheel drive, if a 2-4 switching mechanism with a built-in transfer is connected, the driving force of the engine is transmitted from the rear wheel side propeller shaft to the rear differential 701 and distributed to the left and right rear wheels. In addition, it is transmitted to the front differential via the 2-4 switching mechanism and the front wheel side propeller shaft and distributed to the left and right front wheels.

  In addition, when the vehicle travels on two wheels, if the connection of the 2-4 switching mechanism is released, the vehicle enters a two-wheel drive state of rear wheel drive.

[Configuration of rear differential 701]
The differential case 703 is integrally formed, and is disposed inside the carrier 305. The left boss portion 711 is supported by the carrier 305 via a bearing 713, and the right boss portion 715 is supported by a bearing 713. The ring gear 717 is fixed to the flange 705 with bolts, and the differential case 703 is rotationally driven by the driving force of the engine input from the ring gear 717.

  In the differential mechanism 319, the pinion 309 is supported by the pinion shaft 355, and the pinion shaft 355 is engaged with the through hole 719 of the differential case 703 at the outer end, and is prevented from being rotated and prevented by the threaded rod 721. . The rod 721 can be easily pulled out by being threaded, and the pinion shaft 355 can be easily assembled and pulled out (moved outward) by using the threaded rod 721. Further, output shafts 323 and 325 are connected to the spline portions 327 and 329 of the left and right side gears 315 and 317, and the side gears 315 and 317 and the output shafts 323 and 325 are respectively connected to the C clip and the inner periphery of the side gears 315 and 317. It is positioned (prevented from coming off) in the axial direction by grooves 723 and 723 provided on the surface.

  The differential limiting device 321 includes an electromagnetic actuator 333, a dog clutch 345, a return spring 341, a controller, and the like.

  The dog clutch 345 is welded to the meshing teeth 365 provided on the clutch ring 363 (clutch member) disposed on the inner side of the differential case 703 on the axial actuator side and the rear side of the gear portion of the first side gear 315. The meshing teeth 361 formed on the ring fixed integrally with each other are provided opposite to each other in the axial direction. The clutch ring 363 is arranged so that the leg portion 725 is prevented from rotating by the through hole 727 of the differential case 703 and is movable in the axial direction. When the clutch ring 363 moves to the right as in the lower half of FIG. 10, the dog clutch 345 is engaged, and when the clutch ring 363 moves to the left as in the upper half of FIG. 10, the engagement of the dog clutch 345 is released. The return spring 341 is disposed between the left side gear 315 and the clutch ring 363, and urges the clutch ring 363 toward the engagement release side (left side) of the dog clutch 345.

  An opening 709 drawn with a two-dot chain line is provided in the differential case 703, and each internal component (members 319, 345, 341, 361, 363) is assembled from this opening 709. That is, the differential case 703 has a one-piece structure.

  The electromagnetic actuator 333 includes an electromagnetic solenoid, a coil housing 369 that encloses the electromagnetic solenoid, a plunger 707, and the like. The coil housing 369, the plunger 707, and the differential case 703 are made of a magnetic material (for example, JIS 10C), and the magnetic path of the electromagnetic solenoid is formed on these members like a magnetic flux loop. The coil housing 369 (electromagnetic solenoid) is supported by the carrier 305 via a support member 729, is prevented from rotating, and is disposed so as not to move relative to the differential case 703 in the axial direction.

  The plunger 707 is configured such that a plunger main body 733 is integrally fixed to the outer periphery of a guide member 731 made of a non-magnetic material such as stainless steel on the inner peripheral side, and the guide member 731 is formed on the outer periphery of the left boss portion 711 (the differential case 703). It is supported so as to be movable in the axial direction, and its tip can press the end wall surface of the leg 725 of the clutch ring 369 through a through hole 727 formed in the side wall.

  When a current is supplied from the battery to the coil 367 by a command from a controller (not shown), the electromagnetic solenoid is excited, a magnetic flux loop is generated between the coil housing 369 and the side wall of the plunger body 733, and the guide member The left boss portion 711 of the differential case 703 that supports 731 also becomes part of the magnetic path, and the magnetic flux loop is strengthened. The plunger 707 (plunger main body 733) is moved rightward to press the clutch ring 369, and the dog clutch 345 Is engaged to lock the differential of the differential mechanism 319. When the excitation of the electromagnetic solenoid is stopped, the engagement of the dog clutch 345 and the differential lock of the differential mechanism 319 are released by the return spring 341.

[Effect of rear differential 701]
The rear differential 701 has the following effects.

  Since the clutch housing 369 (electromagnetic coil 367) is supported by the carrier 305, the differential case 703 is used as a part of the magnetic path of the electromagnetic coil 367, and the plunger 707 is supported by the differential case 703, the electromagnetic actuator 333 is reduced in size accordingly. ing.

  Therefore, even if the electromagnetic actuator 333 is disposed on the ring gear 717 side of the differential case 703, the electromagnetic actuator 333 does not interfere with the bearing 713, the restriction of the mountable model (differential device) is avoided, and the output shaft by the C clip is avoided. The positioning of 323 and 325 (with the extraction of the pinion shaft 355) is kept possible.

  Further, since the electromagnetic actuator 333 is downsized, the offset between the differential mechanism 319 and the rear differential 701 is not required or the amount of offset is minimized, so that the output shafts 323 and 325, the carrier 305, etc. The compatibility degradation can be kept to a minimum.

(Eighth embodiment)
The rear differential 751 (eighth embodiment of the present invention) will be described with reference to FIG. The rear differential 751 is used in place of the rear differential 301 in the four-wheel drive vehicle of FIG. In the following, the difference between the members having the same functions as those of the rear differential 301 will be described by giving the same reference numerals.

[Features of rear differential 751]
The rear differential 751 is connected to a differential case 753 (input member) that can be rotated by input driving torque; a pinion 309 (differential member) that can rotate; and meshing portions 311 and 313 (torque transmitting portions) that transmit and receive the driving torque. A differential mechanism 319 that includes a side gear 315 and 317 (first and second output members) engaged with the pinion 309 (coupled so as to be relatively rotatable) and can rotate coaxially with the differential case 753; Differential limiting device 321.

  The differential limiting device 321 includes a dog clutch 755 (differential limiting mechanism unit) that limits the differential rotation of the differential mechanism 319 and an electromagnetic actuator 333 (actuator unit) that operates the dog clutch 755. 755 and the electromagnetic actuator 333 are arranged on opposite sides of the axial direction of the differential mechanism 319 in the axial direction, and a plurality of push rods 757 for transmitting the operating force of the electromagnetic actuator 333 to the dog clutch 755. The dog clutch 755 is provided with a clutch ring 774 (first member) coupled to the side gear 315 so as to be integrally rotatable, and a clutch ring 772 (second member) coupled to the differential case 753 so as to be integrally rotatable. Between the side gear 315 and the clutch ring 774. The cam mechanism 775 to enhance the differential limiting force of the dog clutch 755 operates by receiving the differential torque is provided.

[Configuration of rear differential 751]
The differential limiting device 321 includes the dog clutch 755, the electromagnetic actuator 333, the push rod 757, and a controller.

  The differential case 753 is configured by fixing a casing main body 776 and a cover 778 with bolts. The differential case 753 is arranged inside the carrier, and left and right boss portions 759 and 761 formed on the casing main body 776 and the cover 778 are interposed via bearings. Supported by the carrier, a ring gear 717 is fixed to the flange portion 763 with a bolt, and is driven to rotate by a driving force from the engine input to the ring gear 717.

  The pinion shaft 355 of the differential mechanism 319 engages the outer end portion with the through hole 765 of the differential case 753. Output shafts are connected to the spline portions 327 and 329 of the left and right side gears 315 and 317, respectively. The side gears 315 and 317 and the output shaft are C clips, and grooves 767 and 767 provided on the inner periphery of the side gears 315 and 317, respectively. Is positioned in the axial direction.

  The clutch ring 774 on the side gear 315 side is connected to the side gear 315 via the cam mechanism 775 so as to be movable in the axial direction, and the clutch ring 772 on the side of the differential case 753 is connected to the differential case 753 at the connecting portion and restricted to move to the left. The dog clutch 755 includes meshing teeth 773 formed on the side gear 317 side clutch ring 774 and meshing teeth 773 formed on the differential case 753 side clutch ring 772. When the clutch ring 774 moves to the left as in the lower half of FIG. 11, the dog clutch 755 is engaged, and when the clutch ring 774 returns to the right as in the upper half of FIG. 11, the engagement of the dog clutch 755 is released. The return spring 341 is disposed between the clutch rings 772 and 774, and urges the clutch ring 774 toward the engagement release side (right side) of the dog clutch 755.

  The cam mechanism 775 is a self-locking cam for the dog clutch 755. The cam mechanism 775 is activated when a differential torque is received while the dog clutch 755 is engaged, and the generated cam thrust force causes the clutch ring 774 to engage the dog clutch 755 on the engagement side (left And the operating force of the electromagnetic actuator 333 (the differential limiting force of the dog clutch 755) is strengthened.

  The electromagnetic actuator 333 includes an electromagnetic coil 367, a coil housing 369, a plunger 371, a guide member 777 fixed to the outer periphery of the plunger 371, and the like. The coil housing 369 and the plunger 371 are made of a magnetic material (S10C). The magnetic path of the electromagnetic coil 367 is formed on these members. The coil housing 369 (electromagnetic coil 367) is positioned in the axial direction with a guide portion 777 fixed to the inner peripheral side of the coil housing 369 sandwiched between a step portion 779 of the differential case 753 and a washer 781 on the bearing side.

  Each push rod 757, 757 passes through the through hole 783 of the differential case 753, passes between each pinion 309 from the outside in the radial direction of the side gears 315, 317, and presses the clutch ring 774 of the dog clutch 755 leftward at each left end portion. Arranged to be able to. A ring 785 is attached to the right end of each push rod 757, 757, and the guide member 777 of the plunger 371 can press the clutch ring 774 to the left via the ring 785 and each push rod 757. Yes.

  When the electromagnetic coil 367 is energized, the plunger 371 (guide member 777) presses the clutch ring 774 to the left via the ring 785 and each push rod 757 as described above, and the dog clutch 755 is engaged to make a difference. The differential of the moving mechanism 319 is locked. The cam thrust force of the cam mechanism 775 operated at this time biases the clutch ring 774 to the left, and keeps the dog clutch 755 engaged.

  When the excitation of the electromagnetic coil 367 is stopped, the engagement of the dog clutch 755 and the differential lock of the differential mechanism 319 are released by the return spring 341.

[Effect of rear differential 751]
The rear differential 751 has the following effects.

  By separating the dog clutch 755 and the electromagnetic actuator 333 constituting the differential limiting device 321 from each other and disposing them on the opposite side of the axial direction with respect to the axial center of the differential mechanism 319 (dog clutch 755). The electromagnetic actuator 333 is downsized.

  Since the electromagnetic actuator 333 is downsized in this manner, the offset between the differential mechanism 319 and the rear differential 751 becomes unnecessary, or the offset amount is minimized, so that the output shaft and the carrier are compatible. Degradation can be kept to a minimum.

  In addition, the electromagnetic actuator 333 does not interfere with the bearing, so that the restriction of the differential device that can be mounted is avoided, and the positioning of the output shaft by the C clip (with the radially outward movement of the pinion shaft 355) is possible. To be kept.

  The miniaturized electromagnetic actuator 333 can be disposed on the flange portion 763 (ring gear 717) side, and even in such a case, interference with the bearing is prevented. Is avoided, and positioning of the output shaft by the C-clip is possible.

[Other Embodiments Included within the Scope of the Present Invention]
The differential mechanism applicable to the differential device of the present invention is not limited to a bevel gear type differential mechanism, and may be a differential mechanism using another gear mechanism or a differential mechanism not using a gear mechanism.

  Further, the differential limiting mechanism (differential limiting device) is not limited to the one that locks the differential, and may be one that continuously controls the differential limiting force with a friction clutch, for example.

  In addition, the actuator for adjusting the differential limiting force is not limited to the plunger type electromagnetic actuator except the specified one, and may be another type of electromagnetic actuator, or a hydraulic actuator or a pneumatic actuator. .

  Further, unlike the embodiments, the differential device of the present invention is not a rear differential, but a front differential (for example, the front differential 511 in FIG. 8) or a center differential (a differential device that distributes the driving torque of the prime mover to the front and rear wheels. ).

  Further, the differential device of the present invention is a pair of a differential case, a pinion shaft that rotates integrally with the differential case, and a pinion that is rotatably supported by the pinion shaft, and a pair of pinions that rotate when differential rotation occurs. In addition to the differential device including the output gear, a support shaft that rotates integrally with the case, a rotating member that is rotatably supported by the supporting shaft, and a pair of rotating members that rotate the rotating member by causing a differential rotation, It can also be widely applied to general machines equipped with.

It is sectional drawing of the differential apparatus 1 of 1st Embodiment. 2 is a front view of one side of a pinion shaft 14. FIG. It is sectional drawing of the differential apparatus 100 of 2nd Embodiment. It is sectional drawing of the differential apparatus 200 of a modification. It is sectional drawing which shows the differential apparatus 301 of 3rd Embodiment. It is sectional drawing which shows the differential apparatus 401 of 4th Embodiment. FIG. 3 is a view as seen from an arrow A in FIG. 2. It is sectional drawing which shows the differential apparatus 501 of 5th Embodiment. It is sectional drawing which shows the differential apparatus 601 of 6th Embodiment. It is sectional drawing which shows the differential apparatus 701 of 7th Embodiment. It is sectional drawing which shows the differential apparatus 751 of 8th Embodiment. It is a skeleton mechanism figure which shows the motive power system of the four-wheel drive vehicle using differential apparatus 301,401,501,606,751.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,100,200,301,401,501,601,701,751 ... Differential apparatus 2,101,206,307,403,703,753,831 ... Differential case 13,109,207,319,833 ... Differential mechanism 14, 110, 201, 355, 839 ... Pinion shaft 16, 17, 108 ... Bearings 19, 112, 309, ... Pinions 21, 22, 114, 118, 315, 317 ... Output gears 35, 36, 129, 130, ... Connecting part 37 ... Multi-plate clutch 39 ... Cam ring 131, 208 ... Electromagnet 135, 209 ... Armature 136, 210 ... Pilot clutch 139, 211 ... Cam mechanism 141, 212 ... Pressure ring 143, 213 ... Main clutch

Claims (14)

A differential case that is rotated by the driving force of the drive source, a pair of output members that transmit drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case are distributed to the pair of output members, A differential device housed in a carrier having a differential mechanism composed of a differential member that couples the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits the differential rotation of the differential mechanism. Because
The pair of output members have connecting portions that are connected to the pair of output shafts, respectively, and at least one of the connecting portions is formed on the inner peripheral side of the first cylindrical portion that extends inward in the rotation axis direction of the output member. The differential apparatus characterized by the above-mentioned. The differential device according to claim 1,
The differential member is a pinion shaft that rotates integrally with the differential case, and a pinion that is rotatably supported by the pinion shaft, and the connecting portion extends radially inward of the pinion shaft. Feature differential device. A differential device according to claim 2, wherein
The differential device according to claim 1, wherein the pinion shaft includes a second cylindrical portion radially inward, and the second cylindrical portion is supported with the output member. A differential device according to claim 3, wherein
The output member is provided with a concave portion on the outer surface in the rotational axis direction, the differential case is provided with a side wall and a convex portion on the axial inner side surface of the side wall, and the concave portion and the convex portion are fitted to the differential case with respect to the differential case. A differential device characterized in that an output member is supported. A differential device according to claim 4, wherein
The differential device is characterized in that the differential limiting mechanism is disposed radially outside a connecting portion between the output member and the differential member. A differential case that is rotated by the driving force of the drive source, a pair of output members that transmit drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case are distributed to the pair of output members, A differential mechanism composed of a differential member that couples the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits differential rotation of the differential mechanism, and is supported by a carrier via a bearing. Differential device,
The pair of output members have connection portions that are respectively connected to the pair of output shafts, and at least one of the connection portions is on the inner peripheral side of a third cylindrical portion that extends outward in the rotation axis direction of the output member. A differential apparatus, wherein the differential apparatus is formed on an inner side in a radial direction of the bearing. The differential device according to claim 6, comprising:
The differential limiting mechanism includes an actuator that controls differential limiting of the differential mechanism, and the differential case is a fourth cylindrical shape that is supported by the bearing across the actuator radially inward and across the actuator in the rotation axis direction. And the fourth cylindrical part is supported on the outer peripheral side of the connecting part with respect to the third cylindrical part. A differential case that is rotated by the driving force of the drive source, a pair of output members that transmit drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case are distributed to the pair of output members, A differential device housed in a carrier having a differential mechanism composed of a differential member that connects the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits the differential rotation of the differential mechanism. Because
The differential limiting mechanism includes an actuator for controlling differential limiting of the differential mechanism, and the differential case has a flange portion formed by a single member to which driving torque from the engine is input, and the radial direction of the flange portion A differential device characterized in that the actuator is arranged inside. A differential device according to claim 8, wherein
A differential device, wherein a rib is formed on an outer side in a radial direction of the flange portion. The differential device according to any one of claims 1, 6, and 8,
The center of the differential mechanism is set at a position different from the center of the differential mechanism in the second differential device that does not include the differential limiting mechanism mounted on the carrier in the rotation axis direction, and the rotation of the pair of output shafts A differential device characterized in that the axially inner end portion is disposed at a position symmetrical in the axial direction with respect to the center of the differential mechanism of the second differential device. The differential device according to any one of claims 1, 6, and 8,
The differential device according to claim 1, wherein a first center between the connecting portions is displaced in a rotation axis direction with respect to a second center between the pair of output members. The differential device according to any one of claims 1, 6, and 8,
The differential device according to claim 1, wherein the connecting portion is asymmetric with respect to a second center between the pair of output members. A differential case that is rotated by the driving force of the drive source, a pair of output members that transmit drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case are distributed to the pair of output members, A differential device comprising a differential mechanism composed of a differential member that couples the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits the differential rotation of the differential mechanism,
The differential limiting device has an actuator for controlling the differential limitation of the differential mechanism,
The actuator is an electromagnetic actuator including an electromagnetic coil and a plunger that receives a moving operation force in the axial direction by the magnetic force of the electromagnetic coil,
The electromagnetic coil is supported by the carrier;
The differential case constitutes a part of the magnetic path of the electromagnetic coil,
The differential is characterized in that the plunger is supported by the differential case. A differential case that is rotated by the driving force of the drive source, a pair of output members that transmit drive torque input to the differential case to a pair of output shafts, and a drive torque that is input to the differential case are distributed to the pair of output members, A differential device comprising a differential mechanism composed of a differential member that couples the pair of output members so as to be relatively rotatable, and a differential limiting mechanism that limits the differential rotation of the differential mechanism,
The differential limiting device includes an actuator that controls differential limiting of the differential mechanism, and the differential limiting mechanism and the actuator are opposite to each other in the axial direction with respect to the axial center of the differential mechanism. And a transmission mechanism for transmitting the operating force of the actuator to the differential limiting mechanism.

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