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WO2018180802A1 - Dispositif de transmission - Google Patents

Dispositif de transmission Download PDF

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Publication number
WO2018180802A1
WO2018180802A1 PCT/JP2018/011137 JP2018011137W WO2018180802A1 WO 2018180802 A1 WO2018180802 A1 WO 2018180802A1 JP 2018011137 W JP2018011137 W JP 2018011137W WO 2018180802 A1 WO2018180802 A1 WO 2018180802A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
pinion
housing
gears
transmission device
Prior art date
Application number
PCT/JP2018/011137
Other languages
English (en)
Japanese (ja)
Inventor
森　裕之
Original Assignee
武蔵精密工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 武蔵精密工業株式会社 filed Critical 武蔵精密工業株式会社
Publication of WO2018180802A1 publication Critical patent/WO2018180802A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases

Definitions

  • the present invention relates to a transmission device mounted on a vehicle such as a four-wheeled vehicle.
  • Patent Document 1 a transmission device having a structure without a differential case mounted on a vehicle such as a four-wheeled vehicle is known (for example, Patent Document 1).
  • Patent Document 2 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).
  • the bearing 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.
  • the present invention has been made in view of the above circumstances, and an object thereof is to provide a transmission device that can reduce the thrust load of a bearing.
  • one transmission device 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.
  • the driven member includes a driven gear member and a carrier member, and the carrier member abuts directly or indirectly on the output gear.
  • 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.
  • the driven member has a first protrusion on the opposite side of the gear teeth
  • the housing has a second protrusion that supports the first protrusion
  • the driven member has a first convex portion on the opposite side of the gear teeth
  • 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.
  • the thrust load of the bearing can be reduced.
  • FIG. 1 is a cross-sectional view schematically showing the overall configuration of the transmission according to the first embodiment of the present invention.
  • FIG. 2 is an enlarged partial cross-sectional view of a transmission device according to a second embodiment of the present invention.
  • FIG. 3 is a cross-sectional view schematically showing the overall configuration of the transmission according to the third embodiment of the present invention.
  • 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.
  • the differential gear mechanism 12 is arrange
  • 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.
  • 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.
  • each pinion gear 19 is comprised with the bevel gear which tapers, for example, so that it approaches the central axis CL.
  • 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.
  • the gear tooth portion 26 a plurality of gear teeth are annularly arranged around the axis of the pinion shaft 21.
  • 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.
  • 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, for example, formed in a cylindrical body coaxial with the center axis CL of the output shafts 14a and 14b.
  • 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.
  • the output shafts 14a and 14b are inserted into the individual shaft portions 29 of the first side gear 16a and the second side gear 16b, respectively.
  • 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.
  • 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, for example.
  • 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.
  • a receiving surface 39a is formed on the inner peripheral surface of the cylindrical portion 36a, for example, 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
  • 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 partly 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.)
  • the outer ring of the bearing member (second bearing member) 45 is fitted on the radially inner 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.
  • 2nd convex part 46 is arrange
  • 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.
  • a tapered roller bearing can be used as the bearing member 45.
  • the third convex portion 47 slides on the annular flat surface 48 of the side gears 16a and 16b, for example, when the side gears 16a and 16b rotate. 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.
  • the ring gear member 35b has, for example, 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.
  • 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.
  • the washer 42 and the first side gear 16a are placed in the first member 36 of the pinion carrier member 35a.
  • 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.
  • 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.
  • the pinion shaft 21 is inserted into the second bearing hole 38, the shaft hole 24, and the first bearing hole 34 from the outside in the radial direction of the side gears 16a and 16b.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 through the bearing member 33b and the bearing member 45.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • the annular first convex portion 37b is formed on the opposite side of the gear teeth 44 in the combined body of the pinion carrier members 35a. 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 is an enlarged view of a part of the 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, 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.
  • 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).
  • the gear tooth portion 55 has, for example, a gear tooth 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.)
  • 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.
  • the washer 42 and the second side gear 16b are arranged at appropriate positions inside the first disc portion 53 of the pinion carrier member 51a.
  • the second side gear 16b is connected to the second half 13b of the housing 13 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.
  • 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.
  • the collar 22 is set on the radially inner side of the side gears 16 a and 16 b of the pinion gear 19.
  • 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.
  • 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.
  • 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.
  • the washer 42 is set on the back surface of the first side gear 16a.
  • 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.
  • the pinion carrier member 51a and the ring gear member 51b are connected using appropriate fastening means such as welding.
  • the first side gear 16a is connected to the first half 13a of the housing 13 via a bearing member 33a.
  • the drive pinion gear 15 is meshed with the gear teeth 44 of the ring gear member 51b.
  • 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.
  • the same effect as the first embodiment can be obtained.
  • 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 device 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.
  • the differential gear mechanism 12 is arrange
  • 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.
  • 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.
  • 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.
  • 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.
  • the gear tooth portion 26 a plurality of gear teeth are annularly arranged around the axis of the pinion shaft 21.
  • a slide surface 27 is formed that extends from the peripheral edge of the shaft hole 24 outward in the radial direction of the pinion gear 19 and is received by the inner peripheral surface of the annular body 223.
  • 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.
  • 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.
  • the individual shaft portions 29 are 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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 arranged annularly 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 helical gears that mesh with each other, for example.
  • 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 gear 68 on the side gears 16a and 16b.
  • 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.
  • a tapered roller bearing can be used for the bearing member 45.
  • 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.
  • the cylindrical portion 62a of the pinion carrier member 61a 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
  • 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.
  • the transmission 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,
  • 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.
  • the transmission device 11c of 3rd Embodiment is the assembly method of the transmission device 11 of 1st Embodiment, and the transmission device of 2nd Embodiment. 11b, a known transmission device, etc. can be assembled.
  • 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

L'invention concerne un dispositif de transmission (11) comprenant : un boîtier (13) ; un engrenage d'entraînement (15) supporté par le boîtier (13) ; un élément entraîné (23) supporté par le boîtier (13) et comprenant des dents d'engrenage (44) qui s'engrènent avec l'engrenage d'entraînement (15) ; une pluralité d'engrenages différentiels (19) supportés de façon rotative par l'élément entraîné (23) ; une paire d'engrenages de sortie (16a, 16b) qui viennent chacun en prise avec la pluralité d'engrenages différentiels (19) ; et une paire d'éléments de palier (33a, 33b) fixés à chacun des engrenages de sortie (16a, 16b), respectivement, et raccordant de manière rotative les engrenages de sortie (16a, 16b) au boîtier (13). L'élément entraîné (23) vient directement ou indirectement en contact avec au moins l'un des engrenages de sortie (16b) sur un côté de surface arrière d'une section où au moins un engrenage de sortie (16b) s'engrène avec un engrenage différentiel (19). Par conséquent, l'invention concerne un dispositif de transmission qui est capable de réduire une charge de poussée de palier.
PCT/JP2018/011137 2017-03-29 2018-03-20 Dispositif de transmission WO2018180802A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017066245A JP2018168937A (ja) 2017-03-29 2017-03-29 伝動装置
JP2017-066245 2017-03-29

Publications (1)

Publication Number Publication Date
WO2018180802A1 true WO2018180802A1 (fr) 2018-10-04

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ID=63675615

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Application Number Title Priority Date Filing Date
PCT/JP2018/011137 WO2018180802A1 (fr) 2017-03-29 2018-03-20 Dispositif de transmission

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JP (1) JP2018168937A (fr)
WO (1) WO2018180802A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7624847B2 (ja) 2021-03-04 2025-01-31 住友重機械工業株式会社 伝達装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2061009A (en) * 1934-11-24 1936-11-17 Gen Motors Corp Rear axle construction
JPS5043630A (fr) * 1973-08-08 1975-04-19
JPS6440738A (en) * 1987-08-03 1989-02-13 Toyoda Machine Works Ltd Drive force distributor with differential limiting mechanism
JPH10220558A (ja) * 1997-02-04 1998-08-21 Kanzaki Kokyukoki Mfg Co Ltd デフギア装置
WO2016006117A1 (fr) * 2014-07-11 2016-01-14 日産自動車株式会社 Dispositif d'entraînement final

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2061009A (en) * 1934-11-24 1936-11-17 Gen Motors Corp Rear axle construction
JPS5043630A (fr) * 1973-08-08 1975-04-19
JPS6440738A (en) * 1987-08-03 1989-02-13 Toyoda Machine Works Ltd Drive force distributor with differential limiting mechanism
JPH10220558A (ja) * 1997-02-04 1998-08-21 Kanzaki Kokyukoki Mfg Co Ltd デフギア装置
WO2016006117A1 (fr) * 2014-07-11 2016-01-14 日産自動車株式会社 Dispositif d'entraînement final

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