JP2018168937A - Transmission device - Google Patents

Abstract

To provide a transmission capable of reducing a thrust load of a bearing.SOLUTION: A transmission device 11 comprises: a housing 13; a drive gear 15 which is supported in the housing 13; a driven member 23 including gear teeth 44 that are meshed with the drive gear 15, and supported in the housing 13; multiple differential gears 19 that are supported in a freely rotatable manner by the driven member 23; a pair of output gears 16a and 16b meshed each of the multiple differential gears 19; and a pair of bearing members 33a and 33b mounted on each of the output gears 16a and 16b and connecting the output gears 16a and 16b to the housing 13 in a freely rotatable manner. The driven member 23 is abutted directly or indirectly to at least one output gear 16b at a back side of a meshing part of the at least one output gear 16b with the differential gear 19.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a transmission device mounted on a vehicle such as an automobile.

  2. Description of the Related Art Conventionally, a transmission device configured with a structure without a differential case mounted on a vehicle such as an automobile is known (for example, Patent Document 1). In this case, since the strength of the meshing portion of the side gear (output gear) is affected by the meshing, it is difficult to ensure sufficient strength of the side gear. Therefore, in a transmission device configured with a structure without a differential case, a technique is known in which a back side of a meshing portion of a side gear (output gear) is supported by a bearing (for example, Patent Document 2).

International Application Publication No. 2016/006117 Korean Published Patent No. 10-2012-0001173

  However, in this case, since the bearing receives the load of the meshing load between the side gear (output gear) and the pinion gear (differential gear) directly from the side gear, the bearing may be damaged over time.

  This invention is made | formed in view of the said situation, and it aims at providing the transmission which can reduce the thrust load of a bearing.

  To achieve the above object, one transmission device according to the present invention includes a housing, a drive gear supported by the housing, and a gear tooth meshing with the drive gear, and a driven member supported by the housing. A plurality of differential gears rotatably supported by the driven member, a pair of output gears meshed with the plurality of differential gears, and the output gears attached to the output gears. A pair of bearing members rotatably connected to the housing, wherein the driven member is directly connected to at least one of the output gears on the back side of the meshing portion of the at least one of the output gears with the differential gear. Or it touches indirectly.

  Preferably, the driven member includes a driven gear member and a carrier member, and the carrier member abuts directly or indirectly on the output gear.

  Preferably, the driven member includes a driven gear member and a carrier member, and each of the carrier member and the driven gear member is in direct or indirect contact with the output gear.

  Preferably, the driven member has a first convex portion on the opposite side of the gear teeth, and the housing has a second convex portion that supports the first convex portion.

  Preferably, the driven member has a first convex portion on the opposite side of the gear teeth, and the housing has a second convex portion that supports the first convex portion, and each of the output gears. A plurality of third convex portions to be supported.

  According to the present invention, the thrust load of the bearing can be reduced.

It is sectional drawing which shows roughly the whole structure of the transmission which concerns on 1st Embodiment of this invention. It is an expansion partial sectional view of a transmission concerning a 2nd embodiment of the present invention. It is sectional drawing which shows roughly the whole structure of the transmission which concerns on 3rd Embodiment of this invention.

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

  FIG. 1 schematically shows the overall configuration of the transmission 11 according to the first embodiment of the present invention. The transmission device 11 includes, for example, a differential gear mechanism 12 and a fixed housing 13 that houses the differential gear mechanism 12. In this embodiment, the differential gear mechanism 12 is arrange | positioned beside the engine (not shown) as a power source mounted, for example in a motor vehicle.

  In the housing 13, for example, a pair of left and right output shafts 14a and 14b connected to the axle are supported so as to be rotatable around the center axis CL, and a drive pinion gear (drive gear, drive gear) 15 rotates perpendicularly to the center axis CL. It is supported rotatably about the axis CG. The two output shafts 14 a and 14 b are arranged coaxially with each other and each have one end coupled to the differential gear mechanism 12 within the housing 13. The housing 13 includes, for example, a first half 13a on the one output shaft 14a side and a second half 13b on the other output shaft 14b side.

  The differential gear mechanism 12 is, for example, a plurality of pinion gears (differential gears) 19 that are rotatably supported around a rotation axis 18 orthogonal to the central axis CL, and are rotatably supported around the central axis CL. The first side gear (side gear, output gear) 16a and the second side gear (side gear, output gear) 16b, which are respectively meshed with the plurality of pinion gears 19, are accommodated between the first side gear 16a and the second side gear 16b. The other end of each pinion shaft 21 is mounted on the outer periphery of the side gears 16a and 16b in common with the collar 22 that supports one end (the other end) of the pinion shaft 21 and the first side gear 16a and the second side gear 16b. An annular body 23 that supports the portion (one end portion).

  Each pinion gear 19 includes, for example, a support body 25 having a shaft hole 24 into which a pinion shaft 21 can be rotatably inserted, and a gear tooth portion 26 protruding from the support body 25 outward in the radial direction of the pinion gear 19. Moreover, each pinion gear 19 is comprised with the bevel gear which tapers, for example, so that it approaches the central axis CL. Further, the shaft hole 24 has, for example, a cylindrical shape coaxial with the rotation axis 18. Lubricating oil can enter between the inner wall of the shaft hole 24 and the pinion shaft 21. In the gear tooth portion 26, a plurality of gear teeth are annularly arranged around the axis of the pinion shaft 21.

  On the back surface of the support body 25, for example, a slide surface 27 that extends from the periphery of the shaft hole 24 radially outward of the pinion gear 19 and is received by the inner peripheral surface of the annular body 23 (the radially inner surfaces of the side gears 16 a and 16 b). Is formed. The slide surface 27 may be formed in an axisymmetric shape with respect to the axis of the pinion shaft 21. The slide surface 27 may be defined by a plane orthogonal to the axis of the pinion shaft 21, or may be defined by a partial spherical surface having a center on the axis of the pinion shaft 21.

  The first side gear 16a and the second side gear 16b include, for example, a cylindrical shaft portion 29 having a shaft hole 28 into which the tip ends of the output shafts 14a and 14b are spline-fitted, and the shaft portion 29 to the side gears 16a and 16b. The ring-shaped tooth portion 31 having gear teeth meshing with the plurality of pinion gears 19 and the distal end portion on the axially inner side of the side gears 16a and 16b of the shaft portion 29. A ring plate-like intermediate wall 32 extending radially outward of the side gears 16a and 16b toward the inner peripheral end of the tooth portion 31. For example, the tooth portion 31 is configured as a bevel gear that moves away from the rotation axis 18 of the pinion gear 19 as it moves away from the central axis CL.

  The individual shaft portions 29 of the first side gear 16a and the second side gear 16b are formed in a cylindrical body coaxial with the center axis CL of the output shafts 14a and 14b, for example. Bearing members (first bearing members) 33 a and 33 b are mounted on the outer peripheral surfaces of the individual shaft portions 29. Each shaft portion 29 is fitted into the inner ring of the corresponding bearing member 33a, 33b. The outer rings of the bearing members 33 a and 33 b are fitted into the housing 13. In this way, the individual shaft portions 29 of the first side gear 16 a and the second side gear 16 b are connected to the housing 13 so as to be relatively rotatable.

  Output shafts 14a and 14b are inserted into the respective shaft portions 29 of the first side gear 16a and the second side gear 16b, respectively. In the side gears 16a and 16b, gear teeth are arranged in an annular shape around the central axis CL. The first side gear 16a has, for example, an annular flat surface on the back surface following a first thrust load receiving surface 41 described later. The second side gear 16b has, for example, an annular flat surface on the back surface following a second thrust load receiving surface 43 described later. The first and second side gears 16a and 16b are provided with an annular plane 48 orthogonal to the central axis CL, for example, in accordance with a third convex portion 47 described later.

  The collar 22 has, for example, a first bearing hole 34 that supports one end (the other end) of the pinion shaft 21. The first bearing hole 34 forms a cylindrical space coaxial with the rotation axis 18. The pinion shaft 21 is supported in the first bearing hole 34 so as not to be relatively rotatable.

  The annular body (driven member) 23 includes, for example, a pinion carrier member (carrier member) 35a and a ring gear member (driven gear member) 35b. The pinion carrier member 35a is continuous from the cylindrical portion 36a disposed radially outward of the first side gear 16a and the axially outer ends of the side gears 16a and 16b of the cylindrical portion 36a radially inward of the side gears 16a and 16b. The first member 36 having a first disk portion 36b that extends in the radial direction of the first side gear 16a behind the first side gear 16a, and can be coupled to the cylindrical portion 36a of the first member 36. The second disk portion 37a extends in the radial direction of the second side gear 16b behind the second side gear 16b, and is formed radially outward in the side gears 16a and 16b of the second disk portion 37a. It protrudes toward the inner wall of the second half 13b of the housing 13 in the direction along the axis (the axial direction of the side gears 16a and 16b), and is formed of an annular body coaxial with the central axis CL. It has a first projection 37b, and the second member 37 having a, a being.

  For example, the ring gear member 35b is mounted on the outer periphery of the first member 36 in the axial direction of the side gears 16a and 16b, and on the outer periphery of the second member 37 in the radial direction of the side gears 16a and 16b. The ring gear member 35b may be coupled to the pinion carrier member 35a by fastening means such as welding or bolting.

  The cylindrical portion 36a has, for example, a second bearing hole 38 into which the other end portion (one end portion) of the pinion shaft 21 can be inserted. The second bearing hole 38 is formed in a cylindrical space coaxial with the rotation axis 18. That is, the first bearing hole 34 and the second bearing hole 38 are arranged coaxially. The pinion shaft 21 is supported in the second bearing hole 38 so as not to be relatively rotatable. The collar 22 and the annular body 23 function as a pinion carrier.

  On the inner peripheral surface of the cylindrical portion 36a, for example, a receiving surface 39a is formed following the slide surface 27 of the pinion gear 19. That is, the receiving surface 39a is formed by a plane orthogonal to the axis of the pinion shaft 21, for example. That is, the slide surface 27 of the pinion gear 19 is slidably received by the receiving surface 39a.

  The first disk portion 36b of the first member 36 has, for example, a first thrust load receiving surface 41 that directly or indirectly contacts the first side gear 16a on the back side of the tooth portion 31 of the first side gear 16a. The first thrust load receiving surface 41 is formed by a plane orthogonal to the central axis CL, for example. The first thrust load receiving surface 41 slidably receives the back surface of the first side gear 16a.

  The first thrust load receiving surface 41 is formed, for example, so as to cover part or all (the entire circumference) of the back side of the meshing portion of the first side gear 16a with the pinion gear 19 in the circumferential direction of the side gears 16a and 16b. . A washer 42 may be sandwiched between the first thrust load receiving surface 41 and the first side gear 16a. (In this embodiment, a washer 42 is sandwiched between the first thrust load receiving surface 41 and the first side gear 16a.)

  The second member 37 has, for example, a partial receiving surface 39b that is coupled to the cylindrical portion 36a of the first member 36 and is continuous with the receiving surface 39a. The partial receiving surface 39b cooperates with the receiving surface 39a to support the sliding surface 27 of the pinion gear 19 so as to be slidable. A resin washer may be interposed between the receiving surfaces 39a and 39b and the slide surface 27 of the pinion gear 19. (In this embodiment, no washer is interposed between the receiving surface 39a and partial receiving surface 39b of the annular body 23 and the slide surface 27 of the pinion gear 19.) The second member 37 is welded, bolted, or the like. What is necessary is just to be couple | bonded with the 1st member 36 by the fastening means.

  The second disk portion 37a of the second member 37 has, for example, a second thrust load receiving surface 43 that directly or indirectly contacts the second side gear 16b on the back side of the tooth portion 31 of the second side gear 16b. The second thrust load receiving surface 43 is formed by a plane orthogonal to the central axis CL, for example. The second thrust load receiving surface 43 slidably receives the back surface of the second side gear 16b.

  The second thrust load receiving surface 43 is formed so as to cover the rear surface of the meshing portion of the second side gear 16b with the pinion gear 19 partially or entirely (entirely) over the circumferential direction of the side gears 16a and 16b. A washer 42 may be sandwiched between the second thrust load receiving surface 43 and the second side gear 16b. (In this embodiment, a washer 42 is sandwiched between the second thrust load receiving surface 43 and the second side gear 16b.)

  An outer ring of a bearing member (second bearing member) 45 is fitted on the radially inward side of the side gears 16a and 16b of the first convex portion 37b. The housing 13 includes, for example, an annular second convex portion 46 projecting from the inner wall of the housing 13 in the direction along the central axis CL toward the annular body 23, a bearing member 33a, a bearing member 33b, and a first disc portion. And a third convex portion 47 that protrudes radially inward of the side gears 16a and 16b from the inner wall of the housing 13 between the radial direction of the side gears 16a and 16b with respect to 36b and the second disc portion 37a. The

  The 2nd convex part 46 is arrange | positioned coaxially at the 1st convex part 37b, for example. The diameter of the 2nd convex part 46 is smaller than the diameter of the 1st convex part 37b, for example. The inner ring of the bearing member 45 is fitted on the outer periphery of the second convex portion 46. In this way, the annular body 23 is indirectly supported by the housing 13. For example, a tapered roller bearing can be used as the bearing member 45.

  For example, when the side gears 16a and 16b rotate, the third convex portion 47 slides on the annular plane 48 of the side gears 16a and 16b. Therefore, the 3rd convex part 47 suppresses the displacement of the 1st side gear 16a and the 2nd side gear 16b in the direction of the central axis CL from the back side of the 1st side gear 16a and the 2nd side gear 16b. Moreover, the 3rd convex part 47 supports the 1st side gear 16a and the 2nd side gear 16b indirectly.

  For example, the ring gear member 35b has gear teeth 44 formed of a bevel gear that moves away from the rotation axis CG of the drive pinion gear 15 as the distance from the center axis CL increases. The gear teeth 44 are annularly arranged around the central axis CL. The gear teeth 44 have a predetermined inclination angle with respect to a virtual plane orthogonal to the central axis CL, for example. The gear teeth 44 mesh with the gear teeth 15a of the drive pinion gear 15 that rotates about the rotation axis CG. In this way, the driving force is transmitted between the drive pinion gear 15 and the annular body 23 between the mutually rotating shafts.

  Next, the operation of this embodiment will be described. In the transmission device 11 of the present embodiment, when the power from the engine receives a rotational force from the gear teeth 44 of the ring gear member 35b via the drive pinion gear 15, the pinion gear 19 does not rotate around the rotation axis 18, and the first When revolving around the central axis CL together with the side gear 16a and the second side gear 16b, the left and right side gears 16a and 16b are rotated at the same speed, and the driving force of the side gears 16a and 16b is evenly distributed to the left and right output shafts 14a and 14b. Is transmitted to. Further, when a difference in rotational speed occurs between the left and right output shafts 14a and 14b due to turning of the automobile, etc., the pinion gear 19 revolves around the central axis CL while rotating, so that the pinion gear 19 changes to the left and right side gears 16a and 16b. On the other hand, the rotational driving force is transmitted while allowing differential rotation. The above is the same as the operation of a conventionally known differential.

  Next, an example of assembly of the transmission device 11 will be briefly described. First, the washer 42 and the first side gear 16a are placed in the first member 36 of the pinion carrier member 35a. Next, the pinion gear 19 is set so that the tooth portion 31 of the first side gear 16a and the gear tooth portion 26 of the pinion gear 19 are engaged with each other. Next, the collar 22 is set on the radially inner side of the side gears 16 a and 16 b of the pinion gear 19. At this time, the first bearing hole 34 of the collar 22, the shaft hole 24 of the pinion gear 19, and the second bearing hole 38 of the pinion carrier member 35a are aligned so as to be coaxial.

  Next, the pinion shaft 21 is inserted into the second bearing hole 38, the shaft hole 24, and the first bearing hole 34 from the radially outer side of the side gears 16a and 16b. Next, the ring gear member 35b is mounted on the outer periphery of the first member 36 of the pinion carrier member 35a by using fastening means such as welding. As a result, the pinion shaft 21 is prevented from coming off.

  Next, the first side gear 16a, the first member 36 of the pinion carrier member 35a, the washer 42, the pinion gear 19, the pinion shaft 21 and the collar 22 are assembled in the first half 13a of the housing 13. The first side gear 16a, the pinion carrier member 35a, the washer 42, the pinion gear 19, the pinion shaft 21 and the collar 22 are connected to the first half body 13a via the bearing member 33a. It is assembled in the first half 13a.

  Next, the tooth portion 31 of the second side gear 16b and the gear tooth portion 26 of the pinion gear 19 are engaged with each other from the axially outer side of the side gears 16a, 16b of the pinion gear 19 on the side opposite to the first side gear 16a. Set to.

  Next, the washer 42 is set on the back surface of the second side gear 16b, and the second member 37 of the pinion carrier member 35a is disposed so as to cover the washer 42 on the back surface of the second side gear 16b. At this time, the second member 37 of the pinion carrier member 35a directly contacts the first member 36 and the ring gear member 35b of the pinion carrier member 35a. Next, the second member 37 of the pinion carrier member 35a is attached to the ring gear member 35b by using fastening means such as welding.

  Next, the second member 37 and the second side gear 16b of the pinion carrier member 35a are fitted into the second half 13b of the housing 13 via the bearing member 33b and the bearing member 45. At this time, the second side gear 16b is connected to the second half 13b of the housing 13 via the bearing member 33b and the third convex portion 47 of the second half 13b of the housing 13, and the second member of the pinion carrier member 35a. 37 is connected to the second half 13 b of the housing 13 through the bearing member 45 and the second convex portion 46 of the second half 13 b of the housing 13.

  Next, the drive pinion gear 15 is assembled in the housing 13 so that the drive pinion gear 15 can be engaged with the gear teeth 44 of the ring gear member 35b. Thereafter, the two output shafts 14a and 14b are inserted into the shaft holes 28 of the first side gear 16a and the second side gear 16b, respectively, and the two output shafts 14a and 14b, the first side gear 16a and the second side gear 16b are respectively fitted with splines. Combine. In this way, the transmission device 11 is assembled.

  According to this embodiment, the annular body 23 covers at least one of the side gears 16a and 16b so as to cover the back surface of the meshing portion (gear tooth 26) with the at least one pinion gear 19 of the first and second side gears 16a and 16b. Are in direct or indirect contact with at least one of the side gears 16a and 16b on the back side of the meshing portion with the pinion gear 19. Thereby, the strength of the side gears 16a and 16b can be increased and the thrust load on the bearing members 33a and 33b can be reduced. As a result, damage to the bearing members 33a and 33b can be reduced.

  According to the present embodiment, the annular body 23 has the annular first convex portion 37 b extending parallel to the central axis CL toward the inner wall of the housing 13, and the housing 13 has the first convex portion via the bearing member 45. It has the cyclic | annular 2nd convex part 46 which supports the part 37b indirectly. Further, the first convex portion 37 b of the annular body 23 is supported by the second convex portion 46 of the housing 13. Therefore, the annular body 23 can be easily connected to the housing 13, and the assemblability of the transmission device 11 can be improved.

  According to the present embodiment, the first convex portion 37 b of the annular body 23 is supported by the second convex portion 46 of the housing 13, and the first and second side gears 16 a and 16 b are supported by the third convex portion 47 of the housing 13. As a result, caselessness can be easily achieved, and the annular body 23 can be easily connected to the housing 13. Therefore, the assemblability of the transmission device 11 can be improved.

  According to this embodiment, the annular first convex portion 37 b is formed on the opposite side of the gear teeth 44 in the combined body of the pinion carrier members 35 a. Therefore, even if a driving force is applied from the drive pinion gear 15 to the annular body 23 in the direction away from the drive pinion gear 15 according to the meshing of the gear teeth 44 of the drive pinion gear 15 and the ring gear member 35b, the driving force is received by the second convex portion 46. It is done. Therefore, the displacement of the gear teeth 44 with respect to the direction of the central axis CL can be prevented.

  FIG. 2 shows an enlarged part of a transmission device 11b according to the second embodiment of the present invention. The annular body (driven member) 123 of the transmission device 11b includes, for example, a pinion carrier member 51a and a ring gear member (driven gear member) 51b.

  The pinion carrier member (carrier member) 51a is formed, for example, continuously from the cylindrical portion 52 disposed radially outward of the side gears 16a and 16b of the second side gear 16b, and the second side gear 16b. And a first disc portion 53 that extends in the radial direction of the second side gear 16b behind.

  The cylindrical portion 52 includes, for example, a second bearing hole 38 into which the pinion shaft 21 can be inserted, a receiving surface 39a that supports the slide surface 27 of the pinion gear 19 so as to be slidable around the rotation axis 18, and radially outer sides of the side gears 16a and 16b. It is formed on the lateral side, protrudes toward the inner wall of the second half 13b of the housing 13 in the direction along the central axis CL (the axial direction of the side gears 16a and 16b), and is configured by an annular body coaxial with the central axis CL. 1st convex part 37b.

  The first disc portion 53 has a second thrust load receiving surface 43 that abuts directly or indirectly on the second side gear 16b on the back side of the tooth portion 31 of the second side gear 16b, for example. The second thrust load receiving surface 43 is formed by a plane orthogonal to the central axis CL, for example. The second thrust load receiving surface 43 slidably receives the back surface of the second side gear 16b. A washer 42 may be sandwiched between the second thrust load receiving surface 43 and the second side gear 16b. (In the second embodiment, a washer 42 is sandwiched between the second thrust load receiving surface 43 and the second side gear 16b.)

  The ring gear member 51b includes, for example, a cylindrical portion 54 that is coaxially connected to the cylindrical portion 52 of the pinion carrier member 51a and a continuous portion from the cylindrical portion 54, and a part of the cylindrical portion 52 of the pinion carrier member 51a on the side gears 16a and 16b. A gear tooth portion 55 that covers from the outside in the radial direction and a second disk portion 56 that continues from the cylindrical portion 54 and extends in the radial direction of the first side gear 16a on the back surface of the first side gear 16a. The ring gear member 51b is connected to the pinion carrier member 51a by appropriate fastening means such as welding or bolt fastening.

  The cylindrical portion 54 has, for example, a partial receiving surface 39b that is flush with the receiving surface 39a. The partial receiving surface 39b cooperates with the receiving surface 39a to support the sliding surface 27 of the pinion gear 19 so as to be slidable. A washer may be interposed between the receiving surface 39 a and the partial receiving surface 39 b and the slide surface 27 of the pinion gear 19. (In the second embodiment, no washer is interposed between the receiving surface 39a and the partial receiving surface 39b of the annular body 123 and the slide surface 27 of the pinion gear 19).

  For example, the gear tooth portion 55 includes gear teeth 44 formed of a bevel gear that moves away from the rotation axis CG of the drive pinion gear 15 as the distance from the center axis CL increases. The gear teeth 44 are annularly arranged around the central axis CL. The gear teeth 44 have a predetermined inclination angle with respect to a virtual plane orthogonal to the central axis CL, for example. The gear tooth portion 55 closes the opening of the second bearing hole 38 and functions to prevent the pinion shaft 21 from coming off.

  The second disc portion 56 has a first thrust load receiving surface 41 that directly or indirectly contacts the first side gear 16a on the back side of the tooth portion 31 of the first side gear 16a, for example. The first thrust load receiving surface 41 is formed by a plane orthogonal to the central axis CL, for example. The first thrust load receiving surface 41 slidably receives the back surface of the first side gear 16a. A washer 42 may be sandwiched between the first thrust load receiving surface 41 and the first side gear 16a. (In the second embodiment, a washer 42 is sandwiched between the first thrust load receiving surface 41 and the first side gear 16a.)

  Next, an example of assembly of the transmission device 11b will be briefly described. First, the pinion carrier member 51 a is fitted into the second half 13 b of the housing 13. The pinion carrier member 51 a is connected to the second convex portion 46 via the bearing member 45.

  Next, the washer 42 and the second side gear 16b are disposed at appropriate positions inside the first disc portion 53 of the pinion carrier member 51a. At this time, the second side gear 16b is connected to the housing 13b via the bearing member 33b. Further, the back surface of the meshing portion of the second side gear 16b with the pinion gear 19 is received by the second thrust load receiving surface 43 of the first disc portion 53 of the pinion carrier member 51a via the washer 42.

  Next, the pinion gear 19 is set so that the tooth portion 31 of the second side gear 16b and the gear tooth portion 26 of the pinion gear 19 are engaged with each other. Next, the collar 22 is set on the radially inner side of the side gears 16 a and 16 b of the pinion gear 19. At this time, the first bearing hole 34 of the collar 22, the shaft hole 24 of the pinion gear 19, and the second bearing hole 38 of the pinion carrier member 51a are aligned so as to be coaxial. Next, the pinion shaft 21 is inserted into the second bearing hole 38, the shaft hole 24, and the first bearing hole 34 from the radially outer side of the side gears 16a and 16b.

  Next, the first side gear 16a is set so that the tooth portion 31 of the first side gear 16a and the gear tooth portion 26 of the pinion gear 19 are engaged with each other. Next, the washer 42 is set on the back surface of the first side gear 16a. Next, the second disk portion 56 of the ring gear member 51b covers the washer 42 located on the back surface of the first side gear 16a, and the gear tooth portion 55 of the ring gear member 51b is the second bearing of the cylindrical portion 52 of the pinion carrier member 51a. The ring gear member 51b is disposed so as to close the hole 38.

  Next, the pinion carrier member 51a and the ring gear member 51b are connected using appropriate fastening means such as welding. Next, the first side gear 16a is connected to the first half 13a of the housing 13 via a bearing member 33a. Next, the drive pinion gear 15 is meshed with the gear teeth 44 of the ring gear member 51b. Thereafter, the two output shafts 14a and 14b are inserted into the shaft holes 28 of the first side gear 16a and the second side gear 16b, respectively, and the two output shafts 14a and 14b, the first side gear 16a and the second side gear 16b are respectively fitted with splines. Combine. In this way, the transmission device 11b is assembled.

  Therefore, according to the second embodiment, the same effect as the first embodiment can be obtained. In addition, according to the second embodiment, the number of parts can be reduced as compared with the first embodiment by providing the ring gear function to one member of the annular body 123 composed of two members. it can.

  FIG. 3 schematically shows the overall configuration of the transmission 11c according to the third embodiment of the present invention. The transmission device 11 c includes a differential gear mechanism 12 and a fixed housing 13 that houses the differential gear mechanism 12. In 3rd Embodiment, the differential gear mechanism 12 is arrange | positioned beside the engine (not shown) as a power source mounted, for example in a motor vehicle.

  The housing 13 is integrated with a transmission case that houses a transmission (not shown). The housing 13 supports a pair of left and right output shafts 14a and 14b that are respectively connected to the axle so as to be rotatable about the central axis CL. The two output shafts 14 a and 14 b are arranged coaxially with each other and each have one end coupled to the differential gear mechanism 12 within the housing 13.

  Annular seal members 57a and 57b are mounted between the housing 13 and the individual output shafts 14a and 14b. The seal members 57a and 57b liquid tightly block between the housing 13 and the rotating output shafts 14a and 14b. The housing 13 includes, for example, a first half 13a on one output shaft 14a side and a second half 13b on the other output shaft 14b side.

  In the third embodiment, an oil pan (not shown) that stores a predetermined amount of lubricating oil facing the internal space of the housing 13 is formed at the bottom of the housing 13. The stored lubricating oil is scooped up and scattered in the inner space of the housing 13 by the rotation of the movable element of the reduction gear mechanism 58 and the first side gear 16a and the second side gear 16b. The mechanical motion portions existing inside and outside the differential gear mechanism 12 are lubricated by the lubricating oil thus scattered.

  The differential gear mechanism 12 is, for example, a plurality of pinion gears (differential gears) 19 that are rotatably supported around a rotation axis 18 orthogonal to the central axis CL, and are rotatably supported around the central axis CL. The first side gear (side gear, output gear) 16a and the second side gear (side gear, output gear) 16b, which are respectively meshed with the plurality of pinion gears 19, are accommodated between the first side gear 16a and the second side gear 16b. The collar 22 that supports one end (the other end) of the pinion shaft (differential gear support member) 21 and the first side gear 16a and the second side gear 16b are mounted on the outer periphery of the side gears 16a and 16b. And an annular body 223 that supports the other end (one end) of each pinion shaft 21.

  Each pinion gear 19 includes, for example, a support body 25 having a shaft hole 24 into which the pinion shaft 21 is rotatably inserted, and a gear tooth portion 26 protruding from the support body 25 outward in the radial direction of the pinion gear 19. Further, the shaft hole 24 has, for example, a cylindrical shape coaxial with the rotation axis 18. Lubricating oil can enter between the inner wall of the shaft hole 24 and the pinion shaft 21. In the gear tooth portion 26, a plurality of gear teeth are annularly arranged around the axis of the pinion shaft 21.

  On the back surface of the support body 25, for example, a slide surface 27 is formed that extends from the peripheral edge of the shaft hole 24 radially outward of the pinion gear 19 and is received by the inner peripheral surface of the annular body 223. For example, the slide surface 27 is formed in an axially symmetric shape with respect to the axis of the pinion shaft 21. The slide surface 27 may be defined by a plane orthogonal to the axis of the pinion shaft 21, or may be defined by a partial spherical surface having a center on the axis of the pinion shaft 21.

  The first side gear 16a and the second side gear 16b include, for example, a cylindrical shaft portion 29 having a shaft hole 28 into which the tip ends of the output shafts 14a and 14b are spline-fitted, and the shaft portion 29 to the side gears 16a and 16b. The annular tooth portion 31 having gear teeth meshing with the plurality of pinion gears 19 and the distal end portion on the axially inner side of the side gears 16a and 16b of the shaft portion 29. A ring plate-like intermediate wall 32 extending radially outward in the side gears 16a, 16b toward the inner peripheral end of the tooth portion 31.

  The first side gear 16 a has an annular plane following the first thrust load receiving surface 41. The second side gear 16 b has an annular plane following the second thrust load receiving surface 43.

  Each shaft portion 29 is formed in a cylindrical body coaxial with the center axis CL of the output shafts 14a and 14b. Bearing members 33 a and 33 b are mounted on the outer periphery of each shaft portion 29. Each shaft portion 29 is fitted into the inner ring of the corresponding bearing member 33a, 33b. The outer rings of the bearing members 33 a and 33 b are fitted into the wall of the housing 13. In this way, the shaft portion 29 is connected to the housing 13 so as to be relatively rotatable. The output shafts 14a and 14b are inserted into the shaft portion 29, respectively. In the side gears 16a and 16b, gear teeth are arranged in an annular shape around the central axis CL.

  The collar 22 has a first bearing hole 34 that can be inserted and supported, for example, at one end (the other end) of the pinion shaft 21. For example, the first bearing hole 34 forms a cylindrical space coaxial with the rotation axis 18. The pinion shaft 21 is supported in the first bearing hole 34 so as not to be relatively rotatable. The collar 22 functions as a pinion carrier.

  The annular body (driven member) 223 includes, for example, a pinion carrier member (carrier member) 61a and a ring gear member (driven gear member) 61b. The pinion carrier member 61a includes, for example, a cylindrical portion 62a disposed radially outward of the side gears 16a and 16b, and one end portion of the cylindrical portion 62a in the axial direction of the side gears 16a and 16b and radially inward of the side gears 16a and 16b. An annular disc portion 62b that is formed continuously and extends in the radial direction of the first side gear 16a on the back surface of the first side gear 16a.

  The cylindrical part 62a has the 2nd bearing hole 38 which can insert and support the other end part (one end part) of the pinion shaft 21, for example. For example, the second bearing hole 38 forms a cylindrical space coaxial with the rotation axis 18. The pinion shaft 21 is supported in the second bearing hole 38 so as not to be relatively rotatable. The annular body 223 functions as a pinion carrier.

  A receiving surface 39a is formed on the inner peripheral surface of the cylindrical portion 62a following the slide surface 27 of the pinion gear 19. That is, the receiving surface 39a is formed by a plane orthogonal to the axis of the pinion shaft 21, for example. Therefore, the slide surface 27 of the pinion gear 19 is slidably received by the receiving surface 39a. A washer 63 may be interposed between the receiving surface 39 a of the annular body 223 and the slide surface 27 of the pinion gear 19. (In the third embodiment, a washer 63 is interposed between the receiving surface 39a of the annular body 223 and the slide surface 27 of the pinion gear 19).

  The disc part 62b has the 1st thrust load receiving surface 41 which contact | abuts directly or indirectly to the 1st side gear 16a on the back side of the tooth | gear part 31 of the 1st side gear 16a, for example. The first thrust load receiving surface 41 is formed by a plane orthogonal to the central axis CL, for example. The first thrust load receiving surface 41 slidably receives the back surface of the first side gear 16a. A washer 42 may be sandwiched between the first thrust load receiving surface 41 and the first side gear 16a. (In this embodiment, a washer 42 is sandwiched between the first thrust load receiving surface 41 and the first side gear 16a.)

  The ring gear member 61b includes, for example, a cylindrical portion 64 disposed radially outward of the side gears 16a and 16b of the cylindrical portion 62a of the pinion carrier member 61a, and one end portion (others) of the side gears 16a and 16b of the cylindrical portion 64 in the axial direction. An abutting portion 65 formed continuously from the end) inward in the radial direction of the side gears 16a, 16b, and receiving the cylindrical portion 62a of the pinion carrier member 61a at the radially outer side of the second side gear 16b. And an annular disc portion 66 formed continuously from the inner side of the second side gear 16b toward the inner side in the radial direction of the second side gear 16b.

  The cylindrical portion 64 is formed, for example, with outward gear teeth 67 formed on the outer peripheral surface of the cylindrical portion 64 and a side surface of the cylindrical portion 64 along the central axis CL (the axial direction of the side gears 16a and 16b). ) Projecting toward the inner wall of the housing 13 and having a first convex portion 68 formed of an annular body coaxial with the central axis CL.

  The gear teeth 67 are annularly arranged coaxially with the central axis CL. Further, the gear teeth 67 of the reduction gear mechanism 58 (drive gear, drive gear) 69 mesh with the gear teeth 67 of the annular body 223. Therefore, engine power is transmitted from the transmission to the annular body 223. Therefore, the annular body 223 functions as a so-called ring gear (driven gear).

  The gear teeth 67 of the ring gear member 61b and the gear teeth 69 of the reduction gear mechanism 58 are constituted by, for example, helical gears that mesh with each other. The gear teeth 67 of the ring gear member 61b are constituted by gear teeth that incline in a delay direction as the distance from the first half 13a of the housing 13 increases with respect to the rotational direction when the vehicle moves forward, for example. The gear teeth 69 of the reduction gear mechanism 58 are delayed in the direction away from the first half 13a of the housing 13 with respect to the rotational direction when the vehicle moves forward so that the gear teeth 67 and the external teeth of the ring gear member 61b are engaged with each other. Consists of inclined gear teeth. A load acts in the thrust direction from the gear teeth 69 of the reduction gear mechanism 58 that rotates when the vehicle moves forward to the ring gear member 61b.

  The outer ring of the bearing member 45 is fitted on the radially inner side of the first convex portion 68 in the side gears 16a and 16b. In the housing 13, for example, an annular second convex portion 71 that protrudes toward the annular body 223 in a direction along the central axis CL from the inner wall of the housing 13 (the axial direction of the side gears 16 a and 16 b) is formed. The inner ring of the bearing member 45 is fitted on the outer periphery of the second convex portion 71. In this way, the annular body 223 is indirectly supported by the housing 13. For the bearing member 45, for example, a tapered roller bearing can be used.

  The contact portion 65 has a support surface 72 with which the end surface of the cylindrical portion 62a of the pinion carrier member 61a contacts, for example. The support surface 72 is formed by a plane orthogonal to the central axis CL, for example. With the cylindrical portion 62a of the pinion carrier member 61a in contact with the support surface 72, the cylindrical portion 62a of the pinion carrier member 61a is coupled to the cylindrical portion 64 of the ring gear member 61b by fastening means such as welding. Further, as a fastening means between the pinion carrier member 61a and the ring gear member 61b, bolting or the like other than welding may be used.

  The disc part 66 has the 2nd thrust load receiving surface 43 which contact | abuts directly or indirectly to the 2nd side gear 16b on the back side of the tooth | gear part 31 of the 2nd side gear 16b, for example. The second thrust load receiving surface 43 is formed by a plane orthogonal to the central axis CL, for example. The second thrust load receiving surface 43 slidably receives the back surface of the second side gear 16b. A washer 42 may be sandwiched between the second thrust load receiving surface 43 and the second side gear 16b.

  Next, the operation of the third embodiment will be described. In the differential device 11c of the third embodiment, when the power from the engine receives a rotational force on the gear teeth 67 of the ring gear via the reduction gear mechanism 58, the pinion gear 19 does not rotate around the rotation axis 18, When revolving around the central axis CL together with the first side gear 16a and the second side gear 16b, the left and right side gears 16a, 16b are driven to rotate at the same speed, and the driving force of the side gears 16a, 16b is evenly distributed to the left and right output shafts 14a, 14b. Further, when a difference in rotational speed occurs between the left and right output shafts 14a and 14b due to turning of the automobile, etc., the pinion gear 19 revolves around the central axis CL while rotating, so that the pinion gear 19 changes to the left and right side gears 16a and 16b. On the other hand, the rotational driving force is transmitted while allowing differential rotation. The above is the same as the operation of a conventionally known differential.

  Moreover, although description of an example in the assembly of the transmission device 11c of the third embodiment is omitted, the transmission device 11c of the third embodiment is an assembly method of the transmission device 11a of the first embodiment and the transmission device of the second embodiment. 11b, a known transmission device, etc. can be assembled.

  According to the third embodiment, the same effect as in the first embodiment can be obtained.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to embodiment mentioned above, A various design change is possible in the range which does not deviate from the summary.

  In addition, “indirect contact” or “indirect contact” in this specification means that they are in direct contact with each other, that is, they are in contact with each other via another object.

  DESCRIPTION OF SYMBOLS 11 ... Transmission device, 11b ... Transmission device, 11c ... Transmission device, 13 ... Housing, 15 ... Drive pinion gear (drive gear, drive gear), 16a ... 1st side gear (one side gear, the other side gear, output gear), 16b ... Second side gear (the other side gear, one side gear, output gear), 19 ... pinion gear (differential gear), 23 ... annular body (driven member), 33a ... bearing member (first bearing member), 33b ... bearing member (First bearing member), 35a ... pinion carrier member (carrier member), 35b ... ring gear member (driven gear member), 37b ... first projection, 44 ... gear teeth, 46 ... second projection, 47 ... third projection 51a ... Pinion carrier member (carrier member), 51b ... Ring gear member (driven gear member), 61a ... Pinion Carrier member (carrier member), 61b ... ring gear member (driven gear member), 67 ... gear teeth, 69 ... gear teeth (drive gear, drive gear), 123 ... annular body (driven member), 223 ... annular body (driven member) .

Claims (5)

A housing (13);
Drive gears (15, 69) supported by the housing (13);
A driven member (23, 123, 223) having gear teeth (44, 67) meshing with the drive gear (15, 69) and supported by the housing (13);
A plurality of differential gears (19) rotatably supported by the driven members (23, 123, 223);
A pair of output gears (16a, 16b) each meshing with the plurality of differential gears (19);
A pair of bearing members (33a, 33b) mounted on the individual output gears (16a, 16b) and rotatably connecting the output gears (16a, 16b) to the housing (13);
Have
The driven member (23, 123, 223) is directly or indirectly connected to at least one of the output gears (16b) on the back side of the meshing portion of at least one of the output gears (16b) with the differential gear (19). Abutting,
Transmission device. The driven member (23) includes a driven gear member (35b) and a carrier member (35a), and the carrier member (35a) is in direct or indirect contact with the output gear (16a, 16b). ,
The transmission device according to claim 1. The driven member (123, 223) includes a driven gear member (51b, 61b) and a carrier member (51a, 61a), and includes the carrier member (51a, 61a) and the driven gear member (51b, 61b). Each abutting directly or indirectly on the output gear (16a, 16b),
The transmission device according to claim 1. The driven member (23, 123) has a first protrusion (37b) on the opposite side of the gear teeth (44), and the housing (13) is a first member that supports the first protrusion (37b). Having two convex portions (46),
The transmission device according to any one of claims 1 to 3. The driven member (23, 123) has a first protrusion (37b) on the opposite side of the gear teeth (44), and the housing (13) is a first member that supports the first protrusion (37b). Two convex portions (46), and a plurality of third convex portions (47) supporting each of the output gears (16a, 16b),
The transmission device according to any one of claims 1 to 4.