JP2015129555A - Drive force distribution device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive force distribution device capable of sharing a carrier.SOLUTION: In a drive force distribution device 1 including a differential mechanism 7 differentially rotatably outputting drive force to a pair of output members 3, 5, a pair of distribution mechanisms 9, 11 disposed at both axial ends of the differential mechanism 7 and capable of adjusting the drive force output to the pair of output members 3, 5, and a casing 13 accommodating the differential mechanism 7 and the distribution mechanisms 9, 11, the casing 13 has a carrier 21 accommodating the differential mechanism 7, and provided with positioning members 19, 19 for positioning bearings 15, 17 rotatably supporting the differential mechanism 7, first cover members 25, 25 assembled to openings 23, 23 at a side of the positioning members 19, 19, of the carrier, and second cover members 27, 27 assembled to the first cover members 25, 25 to form accommodation spaces of the distribution mechanisms 9, 11.

Description

  The present invention relates to a driving force distribution device applied to a vehicle.

  Conventionally, as a driving force distribution device, a differential device as a differential mechanism that outputs a driving force differentially rotatable with respect to an intermediate shaft as a pair of output members, and a pair of differential devices arranged on both sides in the axial direction of the differential device A yaw control device as a distribution mechanism capable of adjusting the driving force output to the intermediate shaft of the motor and a casing that houses the differential device and the yaw control device are known (for example, Patent Documents) 1).

  In this driving force distribution device, the casing includes a differential carrier that houses the differential device, a bearing support member that is attached to both sides of the differential carrier by bolts, and a housing semi-constituent member.

  In the interior defined by the bearing support member and the housing semi-constituting member, members such as a gear of a speed increasing gear set and a multi-plate clutch in the yaw control device are accommodated.

  Such a driving force distribution device drives an electric motor to drive a speed reduction mechanism and a cam mechanism that constitute an actuator. When a multi-plate clutch is engaged, additional torque is transmitted from the differential case to the intermediate shaft. Is done.

JP 2008-215584 A

  By the way, in the driving force distribution device of Patent Document 1, through portions are formed on both the left and right output portions of the differential carrier, and a pair of bearing support members are attached.

  In general, a vehicle including a driving force distribution device having a yaw control device as described in Patent Document 1 has only a low ratio in the entire vehicle.

  However, in the driving force distribution device as in the above-mentioned Patent Document 1, in order to provide the bearing support member in the casing, the hole shape of the differential carrier has a large diameter, and the final reduction device having a conventional conventional differential It became difficult to plan to share.

  Accordingly, an object of the present invention is to provide a driving force distribution device capable of sharing a carrier.

  The present invention corresponds to a differential mechanism that outputs a driving force so as to be differentially rotatable with respect to a pair of output members, and a corresponding one of the pair of output members that is disposed on at least one side of the differential mechanism in the axial direction. A driving force distribution device comprising: a distribution mechanism capable of adjusting a driving force output to one side; and a casing for housing the differential mechanism and the distribution mechanism, wherein the casing includes the differential mechanism. A carrier in which a positioning member that positions and accommodates a bearing that rotatably supports the differential mechanism is disposed, a first cover member that is assembled to an opening on the positioning member side of the carrier, and the first cover member And a second cover member that is assembled to form a housing space for the distribution mechanism.

  In this driving force distribution device, since the positioning member for positioning the bearing is disposed on the carrier, the differential mechanism can be rotatably accommodated by the carrier alone through the bearing.

  For this reason, a 1st cover member can be assembled | attached to a carrier, without making a 1st cover member assembled | attached to a carrier support a bearing, and without enlarging the opening shape of a carrier.

  Therefore, in such a driving force distribution device, when applying a carrier to a final reduction gear having a conventional differential, it is not necessary to change the design of the carrier, and the carrier can be shared.

  According to the present invention, there is an effect that it is possible to provide a driving force distribution device capable of sharing a carrier.

It is sectional drawing of the driving force distribution apparatus which concerns on embodiment of this invention. It is a side view when one 2nd cover member in the casing of the driving force distribution apparatus which concerns on embodiment of this invention is removed.

  A driving force distribution device according to an embodiment of the present invention will be described with reference to FIGS.

  A driving force distribution device 1 according to the present embodiment is arranged on a differential mechanism 7 that outputs a driving force so as to be differentially rotatable with respect to a pair of output members 3 and 5, and on both sides in the axial direction of the differential mechanism 7. A pair of distribution mechanisms 9 and 11 capable of adjusting the driving force output to the pair of output members 3 and 5, and a casing 13 that houses the differential mechanism 7 and the distribution mechanisms 9 and 11 are provided.

  And the casing 13 accommodates the differential mechanism 7 and the carrier 21 in which positioning members 19 and 19 for positioning the bearings 15 and 17 for rotatably supporting the differential mechanism 7 are arranged, and the positioning member 19 and 19 of the carrier. First cover members 25, 25 assembled to the openings 23, 23 on the 19th side, and second cover members 27, 27 assembled to the first cover members 25, 25 to form accommodation spaces for the distribution mechanisms 9, 11. And have.

  In the casing 13, a first seal member 29 and a second seal member 31 that are arranged in parallel and partition the differential mechanism 7 side and the distribution mechanisms 9 and 11 side are provided. The second seal member 31 is disposed on the first cover member 25.

  Further, a first through hole 33 is provided between the first seal member 29 and the second seal member 31, and a second through hole communicating with the first through hole 33 is provided in the first cover member 25. A portion 35 is provided, and the second through-hole portion 35 is open to the atmosphere outside the casing 13.

  Further, the opening 37 on the atmosphere side of the second through-hole portion 35 is inclined rearward in the vehicle traveling direction, and the opening 39 on the inner side of the casing 13 of the second through-hole portion 35 corresponds to the first seal member 29 and the The two seal members 31 are positioned below the lower end of the outer diameter.

  Further, between the differential mechanism 7 and the distribution mechanisms 9, 11, hollow shaft-shaped connection members 41, 41 that connect the differential mechanism 7 and the distribution mechanisms 9, 11 are provided. Are arranged so that the lip between the first seal member 29 and the second seal member 31 slides, and is arranged in parallel on the inner periphery of the connecting member 41 and the differential mechanism 7 side and the distribution mechanisms 9 and 11. A third seal member 43 and a fourth seal member 45 are provided, and a third through hole portion 47 is provided in the connecting member 41, and the first through hole portion 33, the third seal member 43, and the second seal member 43 are provided. The four seal members 45 communicate with each other.

  In addition, the carrier 21 and the first cover member 25 are fixed to each other in the rotational direction by two fixing members 49 (called knock pins) that are inserted in the axial direction and aligned with each other in the axial direction. Is assembled from the inside of the first cover member 25 toward the carrier 21, and a fifth seal member 51 that partitions the inside and the outside of the casing 13 is provided between the carrier 21 and the first cover member 25. It has been. The fifth seal member 51 is preferably a liquid gasket applied to the mating surface of the carrier 21 and the first cover member 25, but may be a rubber seal material such as an O-ring, or a metal or non-metal packing.

  Furthermore, a breather mechanism 53 is provided in the accommodation space of the differential mechanism 7 of the casing 13 and the accommodation space of the pair of distribution mechanisms 9 and 11.

  The carrier 21 includes a first carrier member 57 and a second carrier member 59 that include a dividing surface 55 located on a line parallel to the rotational axis of the differential mechanism 7.

  As shown in FIGS. 1 and 2, the differential mechanism 7 includes a differential case 61, a pinion shaft 63, a pinion 65, and a pair of side gears 67 and 69.

  The differential case 61 is accommodated in the carrier 21 of the casing 13 and is rotatably supported on the casing 13 via bearings 15 and 17 by boss portions formed on both sides in the axial direction. The differential case 61 is formed with a flange portion in which the ring gear 71 is fixed by a bolt. The ring gear 71 meshes with a drive pinion 73 that transmits a driving force, and the ring gear 71 and the drive pinion 73 constitute a gear set 75. ing.

  The gear set 75 is configured to be driven by a bevel gear set including a large-diameter ring gear 71 and a small-diameter drive pinion 73, and changes the direction of the driving force transmitted from the drive source side. The small-diameter drive pinion 73 constituting the gear set 75 is formed as one member continuous with the input shaft 77 on one end side in the axial direction of the input shaft 77, and changes the direction of the driving force input from the input shaft 77 to the differential case. 61.

  The input shaft 77 is arranged in a direction orthogonal to the rotational axis of the differential case 61 and is rotatably supported by the carrier 21 of the casing 13 via two bearings 79 and 81 arranged in the axial direction. . A spline-shaped connecting portion 83 is formed on the outer periphery of the input shaft 77 on the other end side, and a connecting member 85 connected to a propeller shaft (not shown) for transmitting driving force from the driving source side can be integrally rotated. It is connected.

  The axial position of the connecting member 85 is fixed by screwing a nut 87 to the end of the input shaft 77, and a preload is applied to the bearings 79 and 81 to position the axial position of the input shaft 77. A seal member 89 that partitions the inside and the outside of the casing 13 is disposed between the connecting member 85 and the carrier 21 in the radial direction, and a dust cover 91 that protects the seal member 89 is provided on the outer periphery of the connecting member 85. Is arranged.

  The driving force transmitted to the input shaft 77 via the connecting member 85 is transmitted to the differential case 61 via the gear set 75, and the pinion shaft 63, the pinion 65, the pair of side gears 67, 69.

  The pinion shaft 63 is engaged with the differential case 61 at its end and is prevented from being detached and prevented from rotating by a pin, and is rotationally driven integrally with the differential case 61. A pinion 65 is supported on the pinion shaft 63.

  A plurality of pinions 65 are arranged at equal intervals in the circumferential direction of the differential case 61, supported by the pinion shaft 63, and revolved by the rotation of the differential case 61. A spherical washer is disposed between the back side of the pinion 65 and the differential case 61 to receive radial movement that occurs when the pinion 65 revolves.

  The pinion 65 is rotatably supported by the pinion shaft 63 so as to transmit a driving force to the pair of side gears 67 and 69 and to be rotated when a differential rotation occurs between the pair of side gears 67 and 69 engaged with each other. Yes.

  The pair of side gears 67 and 69 are supported by the differential case 61 at their respective bosses so as to be relatively rotatable, and mesh with the pinion 65. In addition, a thrust washer that receives movement in the axial direction of the side gears 67 and 69 due to the meshing reaction force with the pinion 65 is arranged between the back side of the side gears 67 and 69 and the differential case 61.

  The pair of side gears 67 and 69 have spline-shaped connecting portions 93 and 95 formed on the inner peripheral side, and a pair of output members 3 connected to a pair of axles (not shown) respectively connected to the left and right wheels. 5 is connected to the side gears 67 and 69 so as to be integrally rotatable, and outputs the driving force input to the differential case 61 to the left and right wheels.

  The pair of output members 3 and 5 are each formed in a shaft shape, one end side is connected to the connecting portions 93 and 95 of the pair of side gears 67 and 69 so as to be integrally rotatable, and the outer periphery on the other end side is interposed through bearings 97 and 99. The second cover member 27 of the casing 13 is rotatably supported.

  The pair of output members 3 and 5 are formed with spline-shaped connecting portions 101 and 103 to which a pair of axles are connected to the inner periphery on the other end side. Further, between the outer periphery of the pair of axles and the inner periphery of the second cover member 27 of the casing 13, seal members 105 and 107 that partition the inside and the outside of the casing 13 are disposed.

  The pair of output members 3 and 5 can adjust the driving force output from the differential mechanism 7 by the pair of distribution mechanisms 9 and 11 provided on the left and right sides of the differential mechanism 7 in the axial direction. ing. In addition, since a pair of distribution mechanism 9 and 11 is a right-and-left symmetrical structure, below, one distribution mechanism 9 is demonstrated and the other distribution mechanism 11 shows the same code | symbol.

  The distribution mechanism 9 includes two sun gears 109 and 111 housed in the first cover member 25 and the second cover member 27 of the casing 13, a pinion gear 113, a multi-plate clutch 115, a speed reduction mechanism 117 as an actuator, A cam mechanism 119 and an electric motor 121 assembled outside the second cover member 27 are provided.

  The two sun gears 109 and 111 are arranged in parallel in the axial direction, are formed to have the same pitch diameter, and have different numbers of teeth. One sun gear 109 of the two sun gears 109 and 111 is connected to the output member 3 through a spline-shaped connecting portion 123 formed on the outer periphery of the output member 3 so as to be integrally rotatable.

  The other sun gear 111 is connected to the connecting member 41 via a spline-shaped connecting portion 125 formed on the outer periphery of one end of the connecting member 41 formed in a hollow shaft shape so as to be integrally rotatable. The connecting member 41 is inserted into the differential case 61 through a spline-shaped connecting portion 127 formed on the outer periphery of the other end side, with the output member 3 inserted therein so as to be relatively rotatable. For this reason, the other sun gear 111 is connected to the differential case 61 via the connecting member 41 so as to be integrally rotatable.

  The pinion gear 113 is supported so as to be able to revolve by rotation of the carrier 129 via a pin 131 with respect to the carrier 129 arranged rotatably. Further, the pinion gear 113 is provided with a gear portion having a different number of teeth in parallel in the axial direction, meshes with the two sun gears 109 and 111, and can rotate on the pin 131 by rotation of the two sun gears 109 and 111. It is supported by.

  The multi-plate clutch 115 is a friction clutch including a plurality of control-type clutch plates capable of intermediate control of transmission torque with sliding friction, and is provided between the carrier 129 and the second cover member 27 of the casing 13. The rotation of the carrier 129 relative to the casing 13 is controlled. The multi-plate clutch 115 is intermittently operated by an electric motor 121 as an actuator, a speed reduction mechanism 117, and a cam mechanism 119.

  The electric motor 121 is assembled to the outside of the second cover member 27 of the casing 13 via a plurality of bolts, and the motor shaft 133 is disposed inside the casing 13. The electric motor 121 is connected to a controller (not shown) as control means and is controlled by the controller. The rotation output from the motor shaft 133 of the electric motor 121 is decelerated by the decelerating mechanism 117.

  The reduction mechanism 117 includes a first reduction gear set 135 and a second reduction gear set 137. A closing member that closes the casing 13 is provided at an opening portion of the casing 13 where the speed reduction mechanism 117 of the second cover member 27 is disposed.

  The first reduction gear set 135 includes a motor shaft 133 of the electric motor 121 and a first large-diameter gear portion 139. The first large-diameter gear portion 139 is provided in a first intermediate gear that is rotatably supported in the casing 13 via a first intermediate shaft, and meshes with the motor shaft 133 of the electric motor 121. The first reduction gear set 135 decelerates the rotation of the electric motor 121 and transmits it to the second reduction gear set 137 via the first intermediate gear.

  The second reduction gear set 137 includes a second small diameter gear portion 141 and a second large diameter gear portion 143. The second small diameter gear portion 141 is provided on the first intermediate gear adjacent to the first large diameter gear portion 139 and meshes with the second large diameter gear portion 143. The second large-diameter gear portion 143 is provided in a second intermediate gear rotatably supported in the casing 13 via a second intermediate shaft, and the gear portion 145 provided on the outer diameter of the cam ring 147 of the cam mechanism 119. Are engaged. The second reduction gear set 137 reduces the rotation from the first intermediate gear and rotates the cam ring 147 via the second intermediate gear.

  In this way, the speed reduction mechanism 117 has a two-stage power transmission path from the electric motor 121 to the cam mechanism 119, and the cam ring 147 of the cam mechanism 119 is rotated by the reduced speed rotation. The rotation of the cam ring 147 is converted into an axial operation force by the cam mechanism 119.

  The cam mechanism 119 is a ball cam mechanism, and includes a cam ball 151 interposed between these cam surfaces with a cam ring 147 and a pressing member 149 facing a plurality of cam surfaces formed in the circumferential direction.

  The cam ring 147 is arranged such that the inner diameter side can be rotated by an engaging portion 153 provided at a corner portion of the second cover member 27 of the casing 13 and can be moved in the axial direction. The engaging portion 153 is a ball cam mechanism in which a cam ball is interposed between a plurality of cam surfaces formed in a circumferential direction between a fixed member fixed to the corner of the second cover member 27 so as not to rotate and a cam ring 147. Yes.

  The cam ring 147 is rotated by the rotation reduced by the speed reduction mechanism 117 by the operation of the electric motor 121, is converted into an axial thrust by the engaging portion 153, is moved in the axial direction toward the pressing member 149, and the pressing member 149. A rotational difference is produced between

  The pressing member 149 is disposed adjacent to the multi-plate clutch 115 in the axial direction, and is disposed on the second cover member 27 of the casing 13 so as to be movable in the axial direction. A pressure receiving plate 155 is disposed on the opposite side of the pressing member 149 and the multi-plate clutch 115 so as not to move in the axial direction on the second cover member 27 of the casing 13. A biasing member 157 is provided between the pressure receiving plate 155 and the pressing member 149 in the axial direction to bias the pressing member 149 toward the cam ring 147, that is, in the direction of releasing the engagement of the multi-plate clutch 115.

  Thus, by constantly urging the pressing member 149 in the fastening release direction of the multi-plate clutch 115 by the biasing member 157, the pressing member 149 is not moved in the fastening direction of the multi-plate clutch 115. The pressing member 149 does not press the multi-plate clutch 115, and the generation of drag torque in the multi-plate clutch 115 can be reduced.

  A plurality of cam surfaces formed in the circumferential direction are formed on the axially opposed surfaces of the pressing member 149 and the cam ring 147, and cam balls 151 are interposed between these cam surfaces.

  The cam ball 151 generates a cam thrust force that axially moves the pressing member 149 toward the multi-plate clutch 115 side by causing a differential rotation between the pressing member 149 and the cam ring 147 due to the rotation of the cam ring 147.

  In such a cam mechanism 119, the cam ring 147 is rotated by the rotation reduced by the reduction mechanism 117 by the operation of the electric motor 121. The rotation of the cam ring 147 causes a differential rotation with the pressing member 149, and the pressing member 149 is converted into an axial thrust that moves in the axial direction toward the multi-plate clutch 115 against the biasing force of the biasing member 157. . At this time, the cam ring 147 is axially moved toward the pressing member 149 by the engaging portion 153, whereby the axial thrust of the pressing member 149 is increased.

  By the axial movement of the pressing member 149, the plurality of clutch plates of the multi-plate clutch 115 are pressed between the pressing member 149 and the pressure receiving plate 155, the multi-plate clutch 115 is fastened, and the carrier 129 in the distribution mechanism 9 is the casing. The second cover member 27 is braked and the rotation of the carrier 129 is restricted.

  In the driving force distribution device 1 configured as described above, when it is necessary to control the turning performance of the vehicle, for example, when the vehicle is cornering, the controller operates while controlling the energization of the electric motor 121. Then, it is converted to axial thrust by the cam mechanism 119 via the speed reduction mechanism 117, the multi-plate clutch 115 is fastened, and the rotation of the carrier 129 in the distribution mechanisms 9 and 11 is controlled.

  Due to the rotation control of the carrier 129 in the distribution mechanisms 9 and 11, the rotation of the differential case 61 is increased by the two sun gears 109 and 111 and the pinion gear 113 in the distribution mechanisms 9 and 11. Transmitted independently.

  By controlling the electric motors 121 and 121 in the pair of distribution mechanisms 9 and 11 arranged on the left and right sides of the differential mechanism 7, the driving force transmitted to the pair of output members 3 and 5 is respectively controlled. It is possible to control the yaw moment of the vehicle and improve the turning performance of the vehicle.

  The casing 13 in such a driving force distribution device 1 includes a carrier 21, first cover members 25 and 25, and second cover members 27 and 27. The first cover members 25 and 25 and the second cover members 27 and 27 assembled on the left and right sides of the carrier 21 have a left-right symmetrical structure. Therefore, in the following, mainly the first cover member 25 and the second cover members 25 and 27 will be mainly described below. The second cover member 27 will be described, and the other first cover member 25 and the second cover member 27 are denoted by the same reference numerals.

  The carrier 21 mainly accommodates the differential mechanism 7, the input shaft 77, and the gear set 75, and positions the axial positions of the bearings 15 and 17 that rotatably support the differential case 61 of the differential mechanism 7. Positioning members 19, 19 such as are fixed.

  Other functional parts such as screw nuts, caulking rings, and welding rings may be used as long as the bearings 15 and 17 can be positioned.

  The positioning members 19 and 19 are fixed in openings 23 and 23 provided on the left and right sides of the carrier 21 through which the connecting members 41 and 41 and the pair of output members 3 and 5 are inserted. For this reason, the differential mechanism 7 can be rotatably accommodated with respect to the carrier 21, the bearings 15 and 17 do not need to be supported by the first cover members 25 and 25, and the openings 23 and 23 of the carrier 21 are large. There is no diameter reduction.

  Therefore, when the carrier 21 is applied to a final reduction gear having a normal conventional differential, the first cover members 25 and 25 are not required, and the carrier 21 can be easily shared.

  Such a carrier 21 includes a first carrier member 57 and a second carrier member 59 that are divided by a dividing surface 55 that is located on a line parallel to the rotational axis of the differential mechanism 7. Therefore, when each member is accommodated in the carrier 21, first, the input shaft 77 is accommodated in the first carrier member 57, and then the differential mechanism 7 is accommodated so as to mesh the gear set 75. In addition, the second carrier member 59 is assembled to the first carrier member 57 at the dividing surface 55. In the carrier 21, the first cover member 25 is assembled in the openings 23 and 23.

  The first cover member 25 is assembled via an inlay portion in which a cylindrical outer diameter side is inserted on the inner diameter side of the opening 23 of the carrier 21, and a plurality of knock pins, bolts, and the like are provided in the circumferential direction on the outer peripheral side of the opening 23. The fixing member 49 is fixed to the carrier 21 by inserting it in the axial direction.

  The plurality of fixing members 49 for fixing the first cover member 25 to the carrier 21 are assembled from the inner side (distribution mechanisms 9 and 11 side) of the first cover member 25 toward the carrier 21 side. For this reason, the first cover member 25 can be assembled to the carrier 21 in a state where each accommodating member such as the differential mechanism 7 is assembled in the carrier 21. The second cover member 27 is assembled to the first cover member 25 as described above.

  The second cover member 27 is assembled to the first cover member 25 to form an accommodation space therein together with the first cover member 25, and mainly accommodates the distribution mechanisms 9, 11, the cam mechanism 119, and the speed reduction mechanism 117. The electric motor 121 is assembled outside.

  The second cover member 27 is fixed to the first cover member 25 by inserting a plurality of fixing members 159 such as knock pins and bolts in the axial direction in the circumferential direction on the outer peripheral side of the opening on the first cover member 25 side. .

  The casing 13 composed of the carrier 21, the first cover member 25, and the second cover member 27 has a housing space on the differential mechanism 7 side, a pair of distribution mechanisms 9, and a plurality of seal members inside. The housing is divided into 11 accommodating spaces, and different types of lubricating oil for lubricating and cooling the sliding portions and the meshing portions of the gears in the respective accommodating spaces are enclosed.

  Among the plurality of seal members, the first seal member 29 and the second seal member 31 are arranged in parallel in the axial direction between the outer circumference of the connecting member 41 and the inner circumference of the first cover member 25. .

  The first seal member 29 is disposed on the differential mechanism 7 side to prevent leakage of lubricating oil from the differential mechanism 7 side to the distribution mechanisms 9 and 11 side, and the second seal member 31 is disposed on the distribution mechanism 9 and 11 side. It prevents the leakage of lubricating oil from the distribution mechanisms 9 and 11 side to the differential mechanism 7 side.

  The first seal member 29 and the second seal member 31 are press-fitted into the inner peripheral surface of the first cover member 25. However, the present invention is not limited to this. For example, the first seal member 29 is attached to the carrier 21. The second seal member 31 may be disposed on the first cover member 25 by being press-fitted into the inner peripheral surface of the first cover member 25.

  By arranging the first seal member 29 and the second seal member 31 in this way, when the pair of distribution mechanisms 9 and 11 are not required, the inside and the outside of the carrier 21 are separated by the first seal member 29. Thus, the carrier 21 can be shared.

  Between the axial direction of this 1st seal member 29 and the 2nd seal member 31, the 1st through-hole part 33 penetrated to radial direction is provided. The first through-hole portion 33 communicates with a second through-hole portion 35 that penetrates the inside and the outside provided in the first cover member 25, and communicates with the atmosphere outside the casing 13 through the second through-hole portion 35. It is open.

  In this way, the first through-hole portion 33 provided between the first seal member 29 and the second seal member 31 is opened to the atmosphere, thereby suppressing an increase in pressure in the first through-hole portion 33. It is possible to prevent misalignment between the first seal member 29 and the second seal member 31, and to maintain the sealing performance between the first seal member 29 and the second seal member 31.

  Here, in FIG. 2, the left side is the front in the traveling direction of the vehicle, and the right side is the rear in the traveling direction of the vehicle. For this reason, the opening 37 on the atmosphere side of the second through-hole portion 35 is inclined toward the rear in the vehicle traveling direction, as shown in FIG.

  By inclining the second through-hole portion 35 in this way, it is possible to prevent foreign matter from entering the second through-hole portion 35 from the opening 37 on the air side when the vehicle is traveling. 33 can be stably opened to the atmosphere.

  On the other hand, the opening 39 inside the casing 13 of the second through-hole portion 35 is positioned below the lower end of the outer diameter of the first seal member 29 and the second seal member 31 as shown in FIG. Thus, by setting the opening 39 inside the casing 13 of the second through-hole portion 35, even if water or the like enters the first through-hole portion 33, the water enters the opening 39 of the second through-hole portion 35. And the like can be reliably guided and discharged from the second through-hole portion 35.

  In addition, the opening 39 of the second through-hole portion 35 does not interfere with the outer diameters of the first seal member 29 and the second seal member 31, and prevents damage to the first seal member 29 and the second seal member 31. can do.

  The first seal member 29 and the second seal member 31 provided with the first through-hole portion 33 communicating with the second through-hole portion 35 include the differential mechanism 7 and the pair of distribution mechanisms 9 and 11. On the outer periphery of the connecting member 41 to be connected, the differential mechanism 7 side and the pair of distribution mechanisms 9 and 11 side are partitioned.

  On the other hand, a third seal member 43 and a fourth seal member 45 are disposed between the inner periphery of the connecting member 41 and the outer periphery of the pair of output members 3 and 5, and the pair of differential mechanisms 7 and the pair The distribution mechanisms 9 and 11 are partitioned.

  The third seal member 43 and the fourth seal member 45 are arranged on the inner peripheral surface of the connecting member 41 in parallel in the axial direction between the inner periphery of the connecting member 41 and the outer periphery of the pair of output members 3 and 5. It is placed by press fitting.

  The third seal member 43 is disposed on the differential mechanism 7 side to prevent leakage of lubricating oil from the differential mechanism 7 side to the distribution mechanisms 9 and 11 side, and the fourth seal member 45 is on the distribution mechanism 9 and 11 side. It prevents the leakage of lubricating oil from the distribution mechanisms 9 and 11 side to the differential mechanism 7 side.

  A gap is provided between the third seal member 43 and the fourth seal member 45 in the axial direction. The portion of the connection member 41 where the gap is located penetrates the connection member 41 in the radial direction, and the third seal A third through-hole portion 47 that communicates with the gap between the member 43 and the fourth seal member 45 is provided. The third through hole portion 47 communicates with the first through hole portion 33 formed between the first seal member 29 and the second seal member 31.

  Therefore, the gap between the third seal member 43 and the fourth seal member 45 in the axial direction is communicated with the second through-hole portion 35 via the third through-hole portion 47 and the first through-hole portion 33. And open to the atmosphere.

  Accordingly, it is possible to suppress an increase in pressure between the third seal member 43 and the fourth seal member 45, to prevent positional displacement between the third seal member 43 and the fourth seal member 45, and to 43 and the fourth seal member 45 can be kept sealed.

  On the other hand, a fifth seal member 51 such as a gasket that partitions the inside and the outside of the casing 13 is provided on the mating surface of the carrier 21 and the first cover member 25. The fifth seal member 51 can prevent the lubricating oil accommodated in the accommodating space on the differential mechanism 7 side from leaking to the outside of the casing 13. A sealing member such as a gasket may be provided on the mating surface between the first cover member 25 and the second cover member 27.

  Here, as shown in FIG. 2, a plate 161 is fixed to the differential mechanism 7 side inside the first cover member 25. Lubricating oil for lubricating and cooling the pair of distribution mechanisms 9 and 11 is circulated on the front surface and the back surface of the plate 161. The first cover member 25 where the lower end side of the plate 161 is located is provided with an oil passage 163 through which lubricating oil is circulated.

  The oil passage 163 is formed along the axial direction of the first cover member 25 and communicates with an oil passage formed along the axial direction of the second cover member 27 (not shown). Thus, by providing the plate 161 and the oil passage 163 in the first cover member 25 and the second cover member 27, the lubricity in the casing 13 can be improved.

  The housing space of the differential mechanism 7 and the housing space of the pair of distribution mechanisms 9 and 11 in the casing 13 partitioned by such a plurality of seal members are operated by an abnormal increase in internal pressure in each housing space. A breather mechanism 53, 53, 53 is provided for opening to the atmosphere.

  Thus, by providing the breather mechanism 53 in each accommodating space of the differential mechanism 7 and the pair of distribution mechanisms 9 and 11, the internal pressure in each accommodating space can be normally maintained independently. In addition, when the pair of distribution mechanisms 9 and 11 are not required, the internal pressure of only the carrier 21 can be normally maintained, and the carrier 21 can be shared.

  In such a driving force distribution device 1, since the positioning members 19 and 19 for positioning the bearings 15 and 17 are arranged on the carrier 21, the differential mechanism 7 can be rotated via the bearings 15 and 17 only by the carrier 21. Can be accommodated.

  For this reason, the bearings 15 and 17 are not supported by the first cover members 25 and 25 assembled to the carrier 21, and the first cover member 25 and 25 are not attached to the carrier 21 without increasing the diameter of the opening of the carrier 21. 25 can be assembled.

  Therefore, in such a driving force distribution device 1, when applying the carrier 21 to the final reduction gear having a conventional differential, it is not necessary to change the design of the carrier 21, and the carrier 21 can be shared. .

  In the casing 13, a first seal member 29 and a second seal member 31 that are arranged in parallel and partition the differential mechanism 7 side and the distribution mechanisms 9 and 11 side are provided. Since the second seal member 31 is disposed on the first cover member 25, when the pair of distribution mechanisms 9 and 11 is applied, the first cover member 25 is assembled to the carrier 21, so that the differential can be easily performed. The mechanism 7 side and the distribution mechanisms 9 and 11 side can be partitioned.

  Further, a first through hole 33 is provided between the first seal member 29 and the second seal member 31, and a second through hole communicating with the first through hole 33 is provided in the first cover member 25. Since the portion 35 is provided and the second through-hole portion 35 is open to the atmosphere outside the casing 13, it is possible to suppress an increase in the pressure in the first through-hole portion 33. Misalignment with the second seal member 31 can be prevented, and the sealing performance between the first seal member 29 and the second seal member 31 can be maintained.

  In addition, since the opening 37 on the atmosphere side of the second through-hole portion 35 is inclined toward the rear in the vehicle traveling direction, the opening 37 on the atmosphere side enters the second through-hole portion 35 from the atmosphere side when the vehicle travels. Intrusion of foreign matter can be prevented, and the first through-hole portion 33 can be stably opened to the atmosphere.

  Furthermore, the opening 39 inside the casing 13 of the second through hole portion 35 is located below the lower end of the outer diameter of the first seal member 29 and the second seal member 31, so Even if water or the like enters, water or the like can be reliably guided to the opening 39 of the second through-hole portion 35 and discharged from the second through-hole portion 35. In addition, the opening 39 of the second through-hole portion 35 does not interfere with the outer diameters of the first seal member 29 and the second seal member 31, and prevents damage to the first seal member 29 and the second seal member 31. can do.

  In addition, the connecting member 41 that connects the differential mechanism 7 and the distribution mechanisms 9 and 11 includes the first through-hole portion 33 and a third seal member that partitions the differential mechanism 7 side and the distribution mechanisms 9 and 11 side. 43 and the fourth seal member 45 are provided with the third through-hole portion 47, so that an increase in pressure between the third seal member 43 and the fourth seal member 45 can be suppressed. It is possible to prevent the positional deviation between the third seal member 43 and the fourth seal member 45, and to maintain the sealing performance between the third seal member 43 and the fourth seal member 45.

  Further, the carrier 21 and the first cover member 25 are fixed to each other in the rotational direction by a fixing member 49 inserted in the axial direction, and the fixing member 49 is assembled from the inside of the first cover member 25 toward the carrier 21. As a result, the first cover member 25 can be assembled to the carrier 21 in a state where each accommodating member such as the differential mechanism 7 is assembled in the carrier 21, and the assembling property can be improved. .

  Further, since the fifth seal member 51 that partitions the inside and the outside of the casing 13 is provided between the carrier 21 and the first cover member 25, the lubricating oil is supplied between the carrier 21 and the first cover member 25. Leakage from the mating surface to the outside of the casing 13 can be prevented, and the inside of the casing 13 can be sealed.

  Furthermore, since the breather mechanism 53 is provided in the accommodation space of the differential mechanism 7 of the casing 13 and the accommodation space of the pair of distribution mechanisms 9 and 11, the internal pressure in each of the accommodation spaces can be made normal independently. Can be held. In addition, when the pair of distribution mechanisms 9 and 11 are not required, the internal pressure of only the carrier 21 can be normally maintained, and the carrier 21 can be shared.

  Further, since the carrier 21 includes the first carrier member 57 and the second carrier member 59 including the dividing surface 55 located on a line parallel to the rotation axis of the differential mechanism 7, the carrier 21 can be easily differentially provided with respect to the carrier 21. The mechanism 7 can be accommodated and the assembling property can be improved.

  In the driving force distribution device according to the embodiment of the present invention, a pair of distribution mechanisms are provided on both sides of the differential mechanism. However, the present invention is not limited to this, and adjustment of the driving force is required among the pair of output members. A configuration in which at least a distribution mechanism is provided on the corresponding output member side may be employed.

  In addition, the distribution mechanism is a planetary gear mechanism, but is not limited to this, for example, an axle disconnect that interrupts the driving force transmitted from one of the output members, or a slip provided on the pair of output members. Any mechanism that can adjust the driving force transmitted to the output member, such as a pair of intermediate control type multi-plate clutches with friction, may be used.

  Furthermore, the actuator of the multi-plate clutch is a motor / gear / cam mechanism. However, the actuator is not limited to this, and an electromagnetic actuator, hydraulic pressure, etc. using a motor / gear / screw mechanism, electromagnetic attraction, electromagnetic force, electromagnetic solenoid, etc. Various control means such as a cylinder / piston mechanism, a motor / shift rod mechanism, an air diaphragm, and a fluid flow path ON-OFF valve can be employed.

DESCRIPTION OF SYMBOLS 1 ... Driving force distribution apparatus 3, 5 ... Output member 7 ... Differential mechanism 9, 11 ... Distribution mechanism 13 ... Casing 15, 17 ... Bearing 19, 19 ... Positioning member 21 ... Carrier 23 ... Opening 25 ... 1st cover member 27 ... 2nd cover member 29 ... 1st seal member 31 ... 2nd seal member 33 ... 1st through-hole part 35 ... 2nd through-hole part 37, 39 ... Opening of 2nd through-hole part 41 ... Connecting member 43 ... 3rd Seal member 45 ... 4th seal member 47 ... 3rd through-hole part 49 ... Fixing member 51 ... 5th seal member 53 ... Breather mechanism 55 ... Dividing surface 57 ... 1st carrier member 59 ... 2nd carrier member

Claims (8)

A differential mechanism that outputs a driving force so as to be differentially rotatable with respect to the pair of output members, and an output to one of the pair of output members that is disposed on at least one side of both sides in the axial direction of the differential mechanism A driving force distribution device comprising: a distribution mechanism capable of adjusting the driving force to be adjusted; and a casing for housing the differential mechanism and the distribution mechanism,
The casing includes a carrier on which a positioning member for positioning a bearing that houses the differential mechanism and rotatably supports the differential mechanism is disposed, and a first cover that is assembled to the opening on the positioning member side of the carrier A driving force distribution device comprising: a member; and a second cover member that is assembled to the first cover member and forms a housing space for the distribution mechanism. The driving force distribution device according to claim 1,
In the casing, a first seal member and a second seal member that are arranged in parallel and partition the differential mechanism side and the distribution mechanism side are provided,
At least one of the first seal member and the second seal member is disposed on the first cover member. The driving force distribution device according to claim 2,
A first through hole is provided between the first seal member and the second seal member,
The first cover member is provided with a second through hole portion communicating with the first through hole portion,
The driving force distribution device, wherein the second through hole is open to the atmosphere outside the casing. The driving force distribution device according to claim 3,
The opening on the atmosphere side of the second through hole is inclined toward the rear in the vehicle traveling direction,
The drive force distribution device, wherein the opening of the second through-hole portion on the inner side of the casing is positioned below the lower end of the outer diameter of the first seal member and the second seal member. The driving force distribution device according to claim 3 or 4,
Between the differential mechanism and the distribution mechanism, a hollow shaft-shaped connection member that connects the differential mechanism and the distribution mechanism is provided,
On the outer periphery of the connecting member, the first seal member and the second seal member are disposed,
A third seal member and a fourth seal member that are arranged in parallel and partition the differential mechanism side and the distribution mechanism side are provided on the inner periphery of the connecting member,
The connecting member is provided with a third through-hole portion that communicates the first through-hole portion with the third seal member and the fourth seal member. apparatus. The driving force distribution device according to any one of claims 1 to 5,
The carrier and the first cover member are fixed to each other in the rotational direction by a fixing member inserted in the axial direction,
The fixing member is assembled from the inside of the first cover member toward the carrier,
Between the carrier and the first cover member, there is provided a fifth seal member that partitions the inside and the outside of the casing. The driving force distribution device according to any one of claims 1 to 6,
A pair of the distribution mechanisms are provided on the left and right sides of the differential mechanism,
A drive force distribution device, wherein a breather mechanism is provided in an accommodation space of the differential mechanism of the casing and an accommodation space of the pair of distribution mechanisms. The driving force distribution device according to any one of claims 1 to 7,
The driving force distribution device according to claim 1, wherein the carrier includes a first carrier member and a second carrier member including a dividing surface located on a line parallel to the rotation axis of the differential mechanism.

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