WO2017061409A1 - Differential device - Google Patents

Differential device Download PDF

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Publication number
WO2017061409A1
WO2017061409A1 PCT/JP2016/079422 JP2016079422W WO2017061409A1 WO 2017061409 A1 WO2017061409 A1 WO 2017061409A1 JP 2016079422 W JP2016079422 W JP 2016079422W WO 2017061409 A1 WO2017061409 A1 WO 2017061409A1
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WO
WIPO (PCT)
Prior art keywords
differential
members
bottomed
transmission
extension
Prior art date
Application number
PCT/JP2016/079422
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French (fr)
Japanese (ja)
Inventor
陽一 柳瀬
Original Assignee
武蔵精密工業株式会社
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Publication date
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Publication of WO2017061409A1 publication Critical patent/WO2017061409A1/en

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    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness

Definitions

  • the present invention relates to a differential gear suitable for a vehicle such as an automobile.
  • a differential case housing the differential mechanism has bearing bosses rotatably supported by the transmission case on both sides of the differential case, and the output member near the bearing boss of the differential mechanism
  • the bottom boss has a bottomed boss, and the bottom boss is connected to the bearing boss with an extension boss inserted from the outer end side of the bearing boss.
  • An oil seal is interposed between the transmission case and a differential device in which a drive shaft that is inserted into an extension boss is spline-fitted to a bottomed boss, as shown in, for example, Patent Document 1 It is.
  • the output member of the output member (side gear) of the differential mechanism is divided into a boss with a bottom and an extended boss so that the output member can be easily manufactured. Moreover, after attaching the differential case incorporating the output member to the transmission case and then connecting the extension boss to the bottom boss of the output member in an oil-tight manner, the outflow of lubricating oil in the differential case and the transmission case is then regulated. . As a result, even if the drive shaft that is spline-fitted to the bottom boss of the output member is pulled out through the extension boss after the differential is assembled, the lubricating oil in the transmission case and differential case will not flow out. There is an advantage of improving the performance and maintainability.
  • extension boss is attached to the bottom boss (bottomed member) of the output member regardless of the constituent material of the extension boss (extension member) (for example, metal or synthetic resin). It is an object of the present invention to provide a differential device in which (extension members) can be easily connected.
  • a differential device has a differential case that houses a differential mechanism, and a bearing member that is rotatably supported by a transmission case on at least one side portion of the differential case,
  • the output member near the bearing member of the differential mechanism has a bottomed member whose inner end is closed, and the bottomed member is inserted into the bearing member from the outer end side of the bearing member.
  • An extension member is connected, an oil seal is interposed between the outer end of the extension member protruding from the bearing member and the transmission case, and the bottomed member has a drive shaft that is inserted into the extension member.
  • the inner cylinder part is fitted to the bottomed member and the extension member, and the other one of the bottomed member and the extension member is fitted to the inner cylinder part.
  • the outer cylinders to be joined A connecting member for connecting the inner cylindrical portion and the outer cylindrical portion to each other and a seal between the inner cylindrical portion and the outer cylindrical portion between the inner cylindrical portion and the outer cylindrical portion.
  • a connecting cylinder part that is fitted and fixed to one of the mutual fitting surfaces of the inner cylinder part and the outer cylinder part, and one end of the connection cylinder part.
  • a recess that elastically locks the elastic locking member is either one of the mating surfaces of the inner cylindrical portion and the outer cylindrical portion. (This is the first feature).
  • the elastic locking member is provided so as to be folded back from the one end to the other end of the connecting tube portion (this is a second feature).
  • an inclined portion or a curved portion that allows the elastic locking member to be engaged and disengaged with respect to the concave portion is provided (this). (Third feature).
  • the extending member is connected to the bottomed member of the output member in the differential mechanism via the connecting member, it is not necessary to elastically deform the extending member when connecting.
  • the extension member can be a bottomed member regardless of the constituent material of the extension member (for example, metal or synthetic resin). Therefore, the degree of freedom in selecting the material for the extension member can be greatly increased.
  • the connecting member having the elastic locking member can be handled as a small component separated and independent from the bottomed member and the extension member, when the elastic locking member is damaged and deteriorated, only the connecting member which is a small component is used. Simply replace it. This can contribute to cost savings.
  • the elastic locking member is provided so as to be folded back from one end to the other end of the connecting cylindrical portion of the connecting member, the locking force of the elastic locking member to the concave portion can be simplified. A sufficient structure can be secured.
  • the both ends of the elastic locking member in the direction along the axis of the connecting cylinder portion are provided with inclined portions or curved portions that allow the elastic locking member to be engaged and disengaged with respect to the recess. Insertion / extraction of the extension member with respect to the bottomed member (that is, fitting from one of the inner tube portion and the outer tube portion to the other) can be performed against a certain resistance force of the elastic locking member. Thereby, the workability of disassembly and assembly of the differential device is enhanced.
  • FIG. 1 is a longitudinal front view of a differential gear according to a first embodiment of the present invention.
  • FIG. 2 is a front view of the differential case of the differential.
  • FIG. 3 is an enlarged cross-sectional view taken along arrow A2 in FIG. 4 is a cross-sectional view taken along line A4-A4 of FIG.
  • FIG. 5 is a single perspective view of the connecting member.
  • FIG. 6 (A) is a diagram corresponding to FIG. 3 showing the second embodiment of the present invention
  • FIG. 6 (B) is a diagram corresponding to FIG. 3 showing the third embodiment of the present invention.
  • FIG. 7 is a longitudinal sectional view of a differential gear according to the fourth embodiment of the present invention.
  • a differential device D is accommodated in a mission case 100 of an automobile.
  • the differential device D includes an integrated differential case 1 and a differential gear mechanism 3 as a differential mechanism accommodated in the differential case 1.
  • a first bearing boss (first bearing member, bearing member) 1 a and a second bearing boss (second bearing member, bearing member) 1 b arranged on the same axis X are integrally formed on the right side and the left side of the differential case 1. Is done.
  • the first and second bearing bosses 1a and 1b are supported on the transmission case 100 via bearings 6 and 6 '.
  • the differential gear mechanism 3 includes a pinion shaft 9 held by the differential case 1 so as to pass through the center C of the differential case 1 while being orthogonal to the axis X, a pair of pinion gears 10 supported by the pinion shaft 9, and a pinion gear 10 And a pair of side gears 11 as output members, and a bottomed boss (bottomed member) 11b integrally connected to the inner peripheral part of the pair of side gears 11, and the first and first And a sleeve 20 as a pair of extension bosses (extension members) that are rotatably supported by the two bearing bosses 1a and 1b.
  • the back surface of each side gear 11 is rotatably supported by the spherical inner surface of the differential case 1.
  • Spiral lubricating grooves 21 are formed on the inner peripheral surfaces of the first and second bearing bosses 1a and 1b.
  • the pinion shaft 9 is held by a pair of support holes 12 on the outer peripheral portion of the differential case 1.
  • a pin hole 13 is provided in the outer peripheral portion of the differential case 1 so as to pass through the outer peripheral portion of the differential case 1 in a direction along the axis X perpendicular to the one support hole 12.
  • the retaining pin (pin) 14 that is press-fitted into the pin hole 13 penetrates the pinion shaft 9, thereby preventing the pinion shaft 9 from being detached from the support hole 12.
  • annular flange 15 is integrally formed at an intermediate portion that is offset from the center C of the differential case 1 toward the second bearing boss 1b.
  • a ring gear 17 that meshes with the output gear 16 of the transmission is fastened to the flange 15 by a bolt 22.
  • the spherical inner surface of the differential case 1 is processed on the peripheral wall of the differential case 1 that is opposed to one diameter line orthogonal to the axis X, and the differential gear mechanism 3 is inserted into the differential case 1.
  • a pair of working windows 18 are provided for ease.
  • the sleeve 20 is configured so that the outer end portion of the sleeve 20 protrudes outward from the corresponding bearing bosses 1a and 1b.
  • An annular oil seal 25 is interposed between the outer end of the sleeve 20 and the mission case 100.
  • the bottom boss 11b integrated with the inner periphery of each side gear 11 is basically formed in a cylindrical shape. And the axial direction inner end side (namely, the side facing the pinion shaft 9) of the bottomed boss 11b is integrally closed by the end wall portion b.
  • the end wall portion b may be manufactured separately from the bottomed boss 11b and fixed or locked to the inner end portion of the bottomed boss 11b later.
  • the opened outer end side of the bottom boss 11b extends outward in the axial direction from the back surface of the side gear 11, and constitutes the inner cylindrical portion Pi of the present invention.
  • the inner peripheral surface of the outer cylindrical portion Po integrally connected to the inner end portion of the sleeve 20 is fitted to the outer peripheral surface of the inner cylindrical portion Pi so as to be detachable.
  • an O-ring 26 are interposed in parallel.
  • the O-ring 26 is attached to an annular seal groove 27 formed on one of the peripheral surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po (in this embodiment, the outer peripheral surface of the inner cylindrical portion Pi).
  • the connecting member J includes a connecting cylinder portion Jp that is press-fitted and fixed to either one of the fitting surfaces of the inner cylinder portion Pi and the outer cylinder portion Po (in this embodiment, the outer peripheral surface of the inner cylinder portion Pi), And a plurality of elastic locking claws (elastic locking members) Jc that are integrally connected to each other at intervals in the circumferential direction.
  • a plurality of elastic locking claws Jc are elastically locked to either one of the fitting surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po (in this embodiment, the inner peripheral surface of the outer cylindrical portion Po).
  • a plurality of locking recesses (recesses) 30 are formed at intervals in the circumferential direction.
  • a small-diameter portion 31 is provided at the outer peripheral surface of the inner cylindrical portion Pi into which the connecting cylindrical portion Jp is press-fitted so that the connecting member J can be easily stored between the fitting surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po. Formed closer. That is, the inner cylinder portion Pi is formed in a stepped cylindrical shape. An annular constricted portion 31 a is formed at the inner end of the small diameter portion 31.
  • Each elastic locking claw Jc is folded back in a U-shaped cross section from one end (in the embodiment, the front end side of the inner cylinder portion Pi) to the other end (in the embodiment, the pinion shaft 9 side) of the connecting cylinder portion Jp. Formed as follows. Then, at both ends of the elastic locking claw Jc in the direction along the axis of the connecting cylinder portion Jp, an inclined portion 32 that allows the elastic locking claw Jc to be engaged and disengaged with respect to the locking recess 30 or a rounded curved portion 33. Is formed.
  • a plurality of elastic locking claws Jc are formed on one end of a metal strip, and then the strip is formed into an annular shape to form an end-connected connecting tube portion Jp. At that time, reduced diameter elasticity is imparted to the connecting tube portion Jp.
  • the side gear 11 and the pinion gear 10 are sequentially assembled into the differential case 1 from the work window 18.
  • the sleeve 20 is not connected to the tip of the bottom boss 11b of the side gear 11, that is, the inner cylinder Pi.
  • the connecting tube portion Jp of the connecting member J is press-fitted and fixed in advance to the small diameter portion 31 of the inner tube portion Pi.
  • an O-ring 26 is attached in advance to the seal groove 27 on the outer periphery of the inner cylindrical portion Pi.
  • each sleeve 20 is fitted into the corresponding bearing boss 1a, 1b of the differential case 1 from the outside of the differential case 1, and the outer cylindrical portion Po of the sleeve 20 is fitted into the inner cylindrical portion Pi of each side gear 11.
  • the some elastic latching claw Jc of the connection member J is each engage
  • the fitting surfaces of the inner cylinder portion Pi and the outer cylinder portion Po are connected via the connecting member J.
  • the differential device D thus assembled is assembled in the mission case 100, and an oil seal 25 is interposed between the outer end of the sleeve 20 and the mission case 100. Thereafter, when lubricating oil is injected into the mission case 100, a part of the lubricating oil flows into the differential case 1 through the work window 18 and is used for lubricating each part of the differential gear mechanism 3.
  • the lubricating oil in the mission case 100 is prevented from flowing out from the outer periphery of the outer end portion of the sleeve 20 by the oil seal 25.
  • the lubricating oil in the differential case 1 is prevented from flowing out from the fitting portion between the bottom boss 11 b of the side gear 11 and the sleeve 20 by the O-ring 26. This means that even if the drive shafts 7 and 8 are extracted from the side gear 11, the lubricating oil in the transmission case 100 and the differential case 1 does not flow out to the outside.
  • the left and right drive shafts 7 and 8 are fitted to the inner periphery of the bottom boss 11b of the corresponding side gear 11 via the spline 29.
  • the rotational torque of the side gear 11 is transmitted to the drive shafts 7 and 8 through the spline 29.
  • the rotation of the side gear 11 is transmitted to the sleeve 20 via the spline 28, so that the side gear 11, the drive shafts 7 and 8, and the sleeve 20 rotate together.
  • the outer peripheral surface of the sleeve 20 is lubricated by the lubricating oil held in the lubricating grooves 21 of the first and second bearing bosses 1a and 1b.
  • the sleeve 20 is connected to the bottom boss 11b of the side gear 11 via the connecting member J, it is necessary to specially elastically deform the sleeve 20 in the radial direction when connecting. Disappear.
  • the sleeve 20 can be made of any of the constituent materials of the sleeve 20 (for example, metal or synthetic resin). Regardless of the case, the bottom boss 11b can be accurately connected. Thereby, the freedom degree of material selection of the sleeve 20 can be raised significantly.
  • the connecting member J having the elastic locking claw Jc can be handled as a small component that is separated and independent from the boss 11b with the bottom and the sleeve 20. Therefore, for example, when the elastic locking claw Jc is damaged and deteriorated, it is only necessary to replace only the connecting member J which is a small part, and the cost can be reduced.
  • the sleeve 20 can be fitted and connected to the bottom boss 11b of the side gear 11 through the bearing bosses 1a and 1b alone (that is, retrofitted). Therefore, it is possible to perform the assembling work of the differential mechanism 3 from the work window 18 to the differential case 1 without being obstructed by the sleeve 20. Thereby, the assembly workability is improved.
  • the elastic locking claw Jc is formed so as to be integrally folded from one end of the connecting cylinder portion Jp of the connecting member J toward the other end. Therefore, it is possible to sufficiently secure the locking force of the elastic locking claw Jc to the locking recess 30 with a simple structure.
  • the connecting member J integrally including the plurality of elastic locking claws Jc can be easily and accurately formed by press forming a metal plate or the like.
  • inclined portions 32 or curved portions 33 that allow the elastic locking claws Jc to be engaged with and disengaged from the locking recesses 30 and can be guided at both ends of the elastic locking claws Jc in the direction along the axis of the connecting cylinder portion Jp. Is formed. Thereby, the insertion / extraction of the sleeve 20 with respect to the boss
  • the open outer end side of the bottomed boss 11b constitutes the outer cylindrical portion Po of the present invention.
  • the outer peripheral surface of the inner cylinder part Pi integrally connected with the inner end part of the sleeve 20 is fitted to the inner peripheral surface of the outer cylinder part Po so that it can be inserted and removed.
  • a connecting member J made of a metal plate and an O-ring 26 are interposed in parallel as in the first embodiment, and the connecting cylinder of the connecting member J is connected.
  • the portion Jp is press-fitted and fixed to the outer peripheral surface of the inner cylindrical portion Pi on the sleeve 20 side.
  • the open outer end side of the bottomed boss 11b constitutes the inner cylindrical portion Pi of the present invention, as in the first embodiment.
  • the inner peripheral surface of the outer cylindrical portion Po integrally connected to the inner end portion of the sleeve 20 is fitted to the outer peripheral surface of the inner cylindrical portion Pi so that it can be inserted and removed.
  • a connecting member J made of a metal plate and an O-ring 26 are interposed in parallel as in the first embodiment, and the connecting cylinder of the connecting member J is connected.
  • the portion Jp is particularly press-fitted and fixed to the inner peripheral surface of the outer cylindrical portion Po on the sleeve 20 side.
  • FIG. 7 shows a fourth embodiment of the present invention. That is, the differential device D1 of the fourth embodiment uses a differential mechanism 130 including a pair of rolling ball type transmission mechanisms. That is, the differential device D1 is eccentric from the differential case 110 integrally including the first transmission member 40 having the first axis X1 as the central axis, the main shaft portion 41j rotating around the first axis X1, and the first axis X1.
  • An eccentric rotating member 41 formed by integrally connecting eccentric shaft portions 41e located on the second axis X2 and a second transmission that is disposed adjacent to the first transmission member 40 and is rotatably supported by the eccentric shaft portion 41e.
  • a first transmission capable of transmitting torque while shifting between the member 42, a third transmission member 43 disposed adjacent to the second transmission member 42 and rotating around the first axis X1, and the first and second transmission members 40, 42.
  • a transmission mechanism T1 and a second transmission mechanism T2 capable of transmitting torque while shifting between the second and third transmission members 42 and 43 are provided.
  • the first speed change mechanism T1 has a wave-like annular shape (in the embodiment, a trochoidal shape or a cycloid shape, the same applies hereinafter) formed on the surface of the first transmission member 40 facing the second transmission member 42 with the first axis X1 as the center.
  • a second transmission in which the wave number is different from that of the first transmission groove 51 in a wave shape formed around the second axis X2 on the surface of the first transmission groove 51 and the second transmission member 42 facing the first transmission member 40.
  • a plurality of ball-shaped first rolling elements 53 that perform the following transmission.
  • the second transmission mechanism T2 includes a third annular transmission groove 54 having an annular shape formed around the second axis X2 on the surface of the second transmission member 42 facing the third transmission member 43, and a third transmission member. 43, a fourth transmission groove 55 having a wave number different from that of the third transmission groove 54 and having a wave number different from that of the third transmission groove 54 formed on the surface facing the second transmission member 42 around the first axis X1, and the third and fourth transmission grooves A plurality of ball-shaped second gears which are interposed in a plurality of overlapping portions of 54 and 55 and perform transmission transmission between the second and third transmission members 42 and 43 while rolling in the third and fourth transmission grooves 54 and 55. 2 rolling elements 56.
  • reference sign W is a balance weight that is disposed radially outward of the second transmission member 42.
  • Reference numeral I denotes a synchronous rotation mechanism that rotates in synchronization with the eccentric rotation member 41 while holding the balance weight W at a position opposite to the eccentric shaft portion 41e with respect to the first axis X1.
  • the wave number of the first transmission groove 51 is Z1
  • the wave number of the second transmission groove 52 is Z2
  • the wave number of the third transmission groove 54 is Z3
  • the wave number of the fourth transmission groove 55 is Z4
  • the rotational force input to the differential case 110 from the vehicle-mounted engine via the transmission is transmitted to the eccentric rotation member 41 and the third transmission member 43 via the first and second transmission mechanisms T1 and T2.
  • the eccentric rotation member 41 and the third transmission member 43 can be rotationally driven while allowing mutual differential rotation.
  • the eccentric rotating member 41 and the third transmission member 43 constitute a pair of output members of the differential mechanism 3.
  • a bottomed boss (bottomed member) 11b is integrally connected to the inner peripheral portions of the eccentric rotating member 41 and the third transmission member 43.
  • the bottom boss 11b and the sleeve 20 as a pair of extension bosses (extension members) are connected by a connection structure using the connection member J, as in the first to third embodiments.
  • the other configurations are substantially the same as those in the first embodiment, and therefore, the portions corresponding to those in the first embodiment are denoted by the same reference numerals in FIG. To do. And also in 4th Embodiment, the effect similar to 1st Embodiment can be achieved fundamentally.
  • welding can be adopted in place of bolt fastening in mutual coupling of the ring gear 17 and the flange 15.
  • welding can be adopted in place of bolt fastening in mutual coupling of the ring gear 17 and the flange 15.
  • welding in the said 4th Embodiment, in the mutual coupling
  • the shape of the inner peripheral surface of the differential case 1,110 may be a box shape, a cylindrical shape, or the like instead of a spherical shape.
  • the sleeve 20 is configured to be fitted into the inner periphery of the bearing bosses 1a and 1b from the outside of the differential case 1 and 110, and is fitted to the corresponding bottomed boss 11b.
  • the left and right sleeves 20 may have different lengths.
  • bearing bosses (bearing members) 1a and 1b that are rotatably supported by the mission case 100 are integrally provided on both sides of the differential case 1 and 110 in the axial direction.
  • the present invention is not limited to this.
  • a bearing boss may be provided continuously only on one side of the differential case 1,110, and the other side may be rotatably supported by the transmission case 100 via another support member.
  • connection cylinder part Jp of the connection member J to the surrounding surface of the inner side cylinder part Pi or the outer side cylinder part Po was shown, this invention is not limited to this. Absent.
  • the connecting tube portion Jp may be fixed by an appropriate fixing means other than press fitting, for example, adhesion, caulking, welding, or the like.
  • the differential devices D and D1 are accommodated in the vehicle mission case 100.
  • the differential devices D and D1 are not limited to the differential devices for vehicles, It can also be implemented as a differential for a mechanical device.
  • the differential devices D and D1 are applied to the left and right wheel transmission systems to distribute power while allowing differential rotation with respect to the left and right drive axles.
  • the invention is not limited to this.
  • the differential device may be applied to a front / rear wheel transmission system in a front / rear wheel drive vehicle to distribute power while allowing differential rotation to the front and rear drive wheels. .
  • the first transmission mechanism 51 includes the first transmission groove 51, the second transmission groove 52, and the first transmission ball 53 interposed between the first and second transmission grooves 51, 52. And a second transmission ball interposed between the third transmission groove 54 and the fourth transmission groove 55 and the third and fourth transmission grooves 54 and 55 as the second transmission mechanism T2.
  • a rolling ball type transmission mechanism comprising 56
  • the present invention is not limited to this.
  • the present invention replaces such a rolling ball type transmission mechanism with various second transmission members that can rotate around the second axis and revolve around the first axis in conjunction with the rotation of the eccentric rotation member, for example.
  • a speed change mechanism for example, an inscribed planetary gear mechanism, a cycloid speed reducer (speed increaser) or a trochoid speed reducer (speed increase speed) of various structures, and at least one of the first speed change mechanism T1 and the second speed change mechanism T2 You may make it apply to.
  • the rolling element may have a roller shape or a pin shape.
  • the first and second transmission grooves 51 and 52 and the third and fourth transmission grooves 54 and 55 are formed on the inner surface so that the roller-like or pin-like rolling elements can roll. Is formed.

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

Abstract

A differential device in which extension members that are inserted through bearing members of a differential case are joined to bottomed members of output members of the differential mechanism and oil seals are interposed between the outer ends of the extension members and the transmission case. In the differential device, inner pipe sections (Pi) are provided in the bottomed members (11b) or the extension members (20) and outer pipe sections (Po) are provided in the other of the bottomed members and the extension members. Between the surfaces of the inner and outer pipe sections (Pi, Po) that are fitted together, joining members (J) and sealing members (26) are interposed. The joining members (J) are provided with a joining pipe section (Jp) that is fitted together with and fixed to one of the surfaces that are fitted together, and an elastic locking member (Jc) that is connected to one end of the joining pipe section (Jp). Recesses (30) for locking the elastic locking member are provided on the other of the surfaces that are fitted together. As a result, in addition to making it possible to secure the advantages that result from special installation of extension members in prior devices, the present invention makes it possible to precisely join the extension members to the bottomed members regardless of the material configuring the extension members, increasing the degree of freedom in selecting materials for the extension members.

Description

差動装置Differential
　本発明は、例えば自動車等の車両に好適な差動装置に関する。 The present invention relates to a differential gear suitable for a vehicle such as an automobile.
　上記差動装置として、例えば差動機構を収容するデフケースが、ミッションケースに回転自在に支持される軸受ボスをデフケースの両側部に有し、差動機構の、軸受ボス寄りの出力部材が、内端側を閉塞した底付きボスを有し、底付きボスには、軸受ボスに軸受ボスの外端側から嵌挿される延長ボスが連結され、延長ボスの、軸受ボスより突出する外端部と、ミッションケースとの間にオイルシールが介装され、底付きボスには、延長ボスに嵌挿されるドライブ軸がスプライン嵌合される差動装置が、例えば特許文献１に示されるように従来公知である。 As the differential device, for example, a differential case housing the differential mechanism has bearing bosses rotatably supported by the transmission case on both sides of the differential case, and the output member near the bearing boss of the differential mechanism The bottom boss has a bottomed boss, and the bottom boss is connected to the bearing boss with an extension boss inserted from the outer end side of the bearing boss. An oil seal is interposed between the transmission case and a differential device in which a drive shaft that is inserted into an extension boss is spline-fitted to a bottomed boss, as shown in, for example, Patent Document 1 It is.
　上記差動装置では、差動機構の出力部材（サイドギヤ）の出力部たるボスを底付きボスと延長ボスとに分割して小部品化することにより、出力部材の製作が容易となる。しかも出力部材を組み込んだデフケースをミッションケースに取り付けた後、出力部材の底付きボスに延長ボスを油密に連結すれば、その後、デフケース内やミッションケース内の潤滑油の外部流出が規制される。これにより、差動装置の組立後、延長ボスを通して出力部材の底付きボスにスプライン嵌合したドライブ軸を引き抜いても、ミッションケース及びデフケース内の潤滑油は依然流出しないため、差動装置の組立性及びメンテナンス性を良好にする利点がある。 In the above differential device, the output member of the output member (side gear) of the differential mechanism is divided into a boss with a bottom and an extended boss so that the output member can be easily manufactured. Moreover, after attaching the differential case incorporating the output member to the transmission case and then connecting the extension boss to the bottom boss of the output member in an oil-tight manner, the outflow of lubricating oil in the differential case and the transmission case is then regulated. . As a result, even if the drive shaft that is spline-fitted to the bottom boss of the output member is pulled out through the extension boss after the differential is assembled, the lubricating oil in the transmission case and differential case will not flow out. There is an advantage of improving the performance and maintainability.
日本特許第５４０４７２７号公報Japanese Patent No. 5404727
　ところが特許文献１の差動装置では、出力部材の底付きボスと延長ボスとの連結に当たり、出力部材の底付きボスの外端部に雌形の鉤状係合部を、また延長ボスの内端部に雄形の鉤状係合部をそれぞれ一体に形成し、雌形及び雄形の鉤状係合部を相互に係合することで、底付きボスと延長ボスとを連結している。そのため、このような連結に当たり、底付きボスと延長ボスの係合直前に、雄形の鉤状係合部を弾性的に半径方向内方へ撓ませる必要があるため、実際には延長ボス全体を耐熱性のある合成樹脂製とする等の制約がある。 However, in the differential device of Patent Document 1, when connecting the bottom boss of the output member and the extension boss, a female hook-like engagement portion is provided at the outer end of the bottom boss of the output member, The bottom boss and the extension boss are connected to each other by forming a male hook-shaped engagement portion integrally at the end and engaging the female and male hook-shaped engagement portions with each other. . Therefore, in this connection, it is necessary to elastically deflect the male hook-shaped engagement portion radially inward immediately before the engagement between the bottom boss and the extension boss. Is made of heat-resistant synthetic resin.
　本発明は、前記利点を維持しながら、延長ボス（延長部材）の構成材料の如何（例えば金属製か合成樹脂製か）を問わず、出力部材の底付きボス（有底部材）に延長ボス（延長部材）を簡単に連結し得るようにした差動装置を提供することを目的とする。 In the present invention, while maintaining the above-mentioned advantages, the extension boss is attached to the bottom boss (bottomed member) of the output member regardless of the constituent material of the extension boss (extension member) (for example, metal or synthetic resin). It is an object of the present invention to provide a differential device in which (extension members) can be easily connected.
　上記目的を達成するために、本発明に係る差動装置は、差動機構を収容するデフケースが、該デフケースの少なくとも一側部に、ミッションケースに回転自在に支持される軸受部材を有し、前記差動機構の、前記軸受部材寄りの出力部材が、内端側を閉塞した有底部材を有し、前記有底部材には、前記軸受部材に該軸受部材の外端側から嵌挿される延長部材が連結され、前記延長部材の前記軸受部材より突出する外端部と前記ミッションケースとの間にオイルシールが介装され、前記有底部材には、前記延長部材に嵌挿されるドライブ軸がスプライン嵌合される差動装置において、前記有底部材及び前記延長部材の何れか一方には内側筒部が、前記有底部材及び前記延長部材の何れか他方には該内側筒部に嵌合する外側筒部が、それぞれ設けられ、前記内側筒部及び前記外側筒部の相互間には、前記内側筒部及び前記外側筒部の相互間を連結する連結部材と、前記内側筒部及び前記外側筒部の相互間をシールするシール部材とが介装され、前記連結部材が、前記内側筒部及び前記外側筒部の相互の嵌合面の何れか一方に嵌合固定される連結筒部と、前記連結筒部の一端に一体に連設される弾性係止部材とを備え、前記弾性係止部材を弾発的に係止させる凹部が、前記内側筒部及び前記外側筒部の相互の嵌合面の何れか他方に設けられる（これを第１の特徴とする）。 In order to achieve the above object, a differential device according to the present invention has a differential case that houses a differential mechanism, and a bearing member that is rotatably supported by a transmission case on at least one side portion of the differential case, The output member near the bearing member of the differential mechanism has a bottomed member whose inner end is closed, and the bottomed member is inserted into the bearing member from the outer end side of the bearing member. An extension member is connected, an oil seal is interposed between the outer end of the extension member protruding from the bearing member and the transmission case, and the bottomed member has a drive shaft that is inserted into the extension member. In the differential device in which the bottom member and the extension member are fitted to each other, the inner cylinder part is fitted to the bottomed member and the extension member, and the other one of the bottomed member and the extension member is fitted to the inner cylinder part. The outer cylinders to be joined A connecting member for connecting the inner cylindrical portion and the outer cylindrical portion to each other and a seal between the inner cylindrical portion and the outer cylindrical portion between the inner cylindrical portion and the outer cylindrical portion. A connecting cylinder part that is fitted and fixed to one of the mutual fitting surfaces of the inner cylinder part and the outer cylinder part, and one end of the connection cylinder part. A recess that elastically locks the elastic locking member is either one of the mating surfaces of the inner cylindrical portion and the outer cylindrical portion. (This is the first feature).
　好適には、前記弾性係止部材は、前記連結筒部の前記一端から他端に向かって折り返されるように設けられる（これを第２の特徴とする）。 Preferably, the elastic locking member is provided so as to be folded back from the one end to the other end of the connecting tube portion (this is a second feature).
　好適には、前記連結筒部の軸線に沿う方向で前記弾性係止部材の両端部には、前記凹部に対する該弾性係止部材の係脱を許容する傾斜部又は湾曲部が設けられる（これを第３の特徴とする）。 Preferably, at both ends of the elastic locking member in a direction along the axis of the connecting cylinder portion, an inclined portion or a curved portion that allows the elastic locking member to be engaged and disengaged with respect to the concave portion is provided (this). (Third feature).
　第１の特徴によれば、差動機構における出力部材の有底部材に連結部材を介して延長部材が連結されるので、連結に際して延長部材を弾性変形させる必要はなくなる。これにより、従来装置の延長部材の特設に伴う前記利点を確保可能とするばかりか、延長部材を、延長部材の構成材料の如何（例えば金属製か合成樹脂製か）を問わず、有底部材に的確に連結可能となり、延長部材の材料選択の自由度を大幅に高めることができる。しかも弾性係止部材を有する連結部材が、有底部材及び延長部材から分離独立した小部品として取り扱い可能となるため、弾性係止部材が破損劣化した場合には、小部品である連結部材だけを単に交換すれば済む。これにより、コスト節減に寄与することができる。 According to the first feature, since the extending member is connected to the bottomed member of the output member in the differential mechanism via the connecting member, it is not necessary to elastically deform the extending member when connecting. As a result, not only can the advantages associated with the special provision of the extension member of the conventional device be ensured, but the extension member can be a bottomed member regardless of the constituent material of the extension member (for example, metal or synthetic resin). Therefore, the degree of freedom in selecting the material for the extension member can be greatly increased. Moreover, since the connecting member having the elastic locking member can be handled as a small component separated and independent from the bottomed member and the extension member, when the elastic locking member is damaged and deteriorated, only the connecting member which is a small component is used. Simply replace it. This can contribute to cost savings.
　また第２の特徴によれば、弾性係止部材は、連結部材の連結筒部の一端から他端に向かって折り返されるように設けられるので、弾性係止部材の凹部への係止力を簡単な構造で十分に確保可能となる。 According to the second feature, since the elastic locking member is provided so as to be folded back from one end to the other end of the connecting cylindrical portion of the connecting member, the locking force of the elastic locking member to the concave portion can be simplified. A sufficient structure can be secured.
　また第３の特徴によれば、連結筒部の軸線に沿う方向で弾性係止部材の両端部には、凹部に対する弾性係止部材の係脱を許容する傾斜部又は湾曲部が設けられるので、有底部材に対する延長部材の抜差し（即ち内側筒部及び外側筒部の一方から他方への嵌合）を、弾性係止部材の一定の抵抗力に抗して行わせることができる。これにより、差動装置の分解組立の作業性が高められる。 According to the third feature, the both ends of the elastic locking member in the direction along the axis of the connecting cylinder portion are provided with inclined portions or curved portions that allow the elastic locking member to be engaged and disengaged with respect to the recess. Insertion / extraction of the extension member with respect to the bottomed member (that is, fitting from one of the inner tube portion and the outer tube portion to the other) can be performed against a certain resistance force of the elastic locking member. Thereby, the workability of disassembly and assembly of the differential device is enhanced.
図１は本発明の第１実施形態に係る差動装置の縦断正面図である。FIG. 1 is a longitudinal front view of a differential gear according to a first embodiment of the present invention. 図２は上記差動装置のデフケースの正面図である。FIG. 2 is a front view of the differential case of the differential. 図３は図１のＡ２矢視部拡大断面図と要部拡大図である。FIG. 3 is an enlarged cross-sectional view taken along arrow A2 in FIG. 図４は図３のＡ４－Ａ４線断面図である。4 is a cross-sectional view taken along line A4-A4 of FIG. 図５は連結部材の単体斜視図である。FIG. 5 is a single perspective view of the connecting member. 図６（Ａ）は本発明の第２実施形態を示す図３対応図、図６（Ｂ）は本発明の第３実施形態を示す図３対応図である。FIG. 6 (A) is a diagram corresponding to FIG. 3 showing the second embodiment of the present invention, and FIG. 6 (B) is a diagram corresponding to FIG. 3 showing the third embodiment of the present invention. 図７は本発明の第４実施形態に係る差動装置の縦断面図である。FIG. 7 is a longitudinal sectional view of a differential gear according to the fourth embodiment of the present invention.
Ｄ，Ｄ１・・・差動装置
Ｊ・・・・・・連結部材
Ｊｐ・・・・・連結筒部
Ｊｃ・・・・・弾性係止爪（弾性係止部材）
Ｐｉ・・・・・内側筒部
Ｐｏ・・・・・外側筒部
１，１１０・・デフケース
１ａ・・・・・第１軸受ボス（第１軸受部材，軸受部材）
１ｂ・・・・・第２軸受ボス（第２軸受部材，軸受部材）
３，１３０・・差動機構
７，８・・・・ドライブ軸
１１・・・・・サイドギヤ（出力部材）
１１ｂ・・・・底付きボス（有底部材）
２０・・・・・スリーブ（延長ボス，延長部材）
２５・・・・・オイルシール
２６・・・・・シール部材
３０・・・・・係止凹部（凹部）
３２・・・・・傾斜部
３３・・・・・湾曲部
４１・・・・・偏心回転部材（出力部材）
４３・・・・・第３伝動部材（出力部材）
１００・・・・ミッションケース D, D1... Differential device J... Connection member Jp... Connection cylinder portion Jc.
Pi... Inner tube portion Po... Outer tube portion 1,110 ..Differential case 1a... First bearing boss (first bearing member, bearing member)
1b... Second bearing boss (second bearing member, bearing member)
3,130 ... Differential mechanism 7,8 ... Drive shaft 11 ... Side gear (output member)
11b ... ・ Bottom boss (bottomed member)
20 ... Sleeve (extension boss, extension member)
25... Oil seal 26... Seal member 30... Locking recess (recess)
32... Inclined portion 33... Curved portion 41... Eccentric rotating member (output member)
43 ... 3rd transmission member (output member)
100 ... Mission case
　本発明の実施形態を添付図面に基づいて以下に説明する。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
　先ず、図１～図４に示す本発明の第１実施形態の説明より始める。図１において、自動車のミッションケース１００内に差動装置Ｄが収容される。差動装置Ｄは、一体型のデフケース１と、デフケース１内に収容される差動機構としての差動ギヤ機構３とを備えている。デフケース１の右側部及び左側部には、同一軸線Ｘ上に並ぶ第１軸受ボス（第１軸受部材，軸受部材）１ａ及び第２軸受ボス（第２軸受部材，軸受部材）１ｂが一体に形成される。そして、第１及び第２軸受ボス１ａ，１ｂは、軸受６，６′を介してミッションケース１００に支承される。 First, the description starts with the description of the first embodiment of the present invention shown in FIGS. In FIG. 1, a differential device D is accommodated in a mission case 100 of an automobile. The differential device D includes an integrated differential case 1 and a differential gear mechanism 3 as a differential mechanism accommodated in the differential case 1. A first bearing boss (first bearing member, bearing member) 1 a and a second bearing boss (second bearing member, bearing member) 1 b arranged on the same axis X are integrally formed on the right side and the left side of the differential case 1. Is done. The first and second bearing bosses 1a and 1b are supported on the transmission case 100 via bearings 6 and 6 '.
　差動ギヤ機構３は、上記軸線Ｘと直交しながらデフケース１の中心Ｃを通るようにしてデフケース１に保持されるピニオン軸９と、ピニオン軸９に支持される一対のピニオンギヤ１０と、ピニオンギヤ１０と噛合する歯部を有する、出力部材としての一対のサイドギヤ１１と、一対のサイドギヤ１１の内周部に一体に連設される底付きボス（有底部材）１１ｂに連結されて第１及び第２軸受ボス１ａ，１ｂにそれぞれ回転自在に支承される一対の延長ボス（延長部材）としてのスリーブ２０と、を有している。各々のサイドギヤ１１の背面は、デフケース１の球状内面で回転自在に支承される。第１及び第２軸受ボス１ａ，１ｂの内周面には、螺旋状の潤滑溝２１が形成される。 The differential gear mechanism 3 includes a pinion shaft 9 held by the differential case 1 so as to pass through the center C of the differential case 1 while being orthogonal to the axis X, a pair of pinion gears 10 supported by the pinion shaft 9, and a pinion gear 10 And a pair of side gears 11 as output members, and a bottomed boss (bottomed member) 11b integrally connected to the inner peripheral part of the pair of side gears 11, and the first and first And a sleeve 20 as a pair of extension bosses (extension members) that are rotatably supported by the two bearing bosses 1a and 1b. The back surface of each side gear 11 is rotatably supported by the spherical inner surface of the differential case 1. Spiral lubricating grooves 21 are formed on the inner peripheral surfaces of the first and second bearing bosses 1a and 1b.
　ピニオン軸９は、デフケース１の外周部の一対の支孔１２により保持される。デフケース１の外周部には、一方の支孔１２と直交してデフケース１の外周部を上記軸線Ｘに沿う方向に貫通するピン孔１３が設けられる。そして、ピン孔１３に圧入嵌合される抜け止めピン（ピン）１４がピニオン軸９を貫通することで、ピニオン軸９の支孔１２からの抜け止めが果たされる。 The pinion shaft 9 is held by a pair of support holes 12 on the outer peripheral portion of the differential case 1. A pin hole 13 is provided in the outer peripheral portion of the differential case 1 so as to pass through the outer peripheral portion of the differential case 1 in a direction along the axis X perpendicular to the one support hole 12. The retaining pin (pin) 14 that is press-fitted into the pin hole 13 penetrates the pinion shaft 9, thereby preventing the pinion shaft 9 from being detached from the support hole 12.
　またデフケース１には、デフケース１の中心Ｃから第２軸受ボス１ｂ側にオフセットした中間部に環状のフランジ１５が一体に形成される。フランジ１５には、変速装置の出力ギヤ１６と噛合するリングギヤ１７がボルト２２により締結される。 In the differential case 1, an annular flange 15 is integrally formed at an intermediate portion that is offset from the center C of the differential case 1 toward the second bearing boss 1b. A ring gear 17 that meshes with the output gear 16 of the transmission is fastened to the flange 15 by a bolt 22.
　図２に示すように、デフケース１の、上記軸線Ｘと直交する一直径線上で対向する周壁には、デフケース１の球状内面を加工するため、並びに差動ギヤ機構３のデフケース１への挿入を容易にするための一対の作業窓１８がそれぞれ設けられる。 As shown in FIG. 2, the spherical inner surface of the differential case 1 is processed on the peripheral wall of the differential case 1 that is opposed to one diameter line orthogonal to the axis X, and the differential gear mechanism 3 is inserted into the differential case 1. A pair of working windows 18 are provided for ease.
　またスリーブ２０は、スリーブ２０の外端部を対応する軸受ボス１ａ，１ｂより外方へ突出するように構成される。そして、スリーブ２０の外端部と、ミッションケース１００との間には環状のオイルシール２５がそれぞれ介装される。 Further, the sleeve 20 is configured so that the outer end portion of the sleeve 20 protrudes outward from the corresponding bearing bosses 1a and 1b. An annular oil seal 25 is interposed between the outer end of the sleeve 20 and the mission case 100.
　各々のサイドギヤ１１の内周部に一体化された上記底付きボス１１ｂは、基本的に円筒状に形成される。そして、底付きボス１１ｂの、軸方向内端側（即ちピニオン軸９に対面する側）が端壁部ｂで一体に閉塞される。尚、端壁部ｂは、底付きボス１１ｂとは別体に製作して、底付きボス１１ｂの内端部に後付けで固着又は係止させるようにしてもよい。 The bottom boss 11b integrated with the inner periphery of each side gear 11 is basically formed in a cylindrical shape. And the axial direction inner end side (namely, the side facing the pinion shaft 9) of the bottomed boss 11b is integrally closed by the end wall portion b. The end wall portion b may be manufactured separately from the bottomed boss 11b and fixed or locked to the inner end portion of the bottomed boss 11b later.
　また底付きボス１１ｂの開放された外端側は、サイドギヤ１１の背面よりも軸方向外方に延出していて、本発明の内側筒部Ｐｉを構成している。内側筒部Ｐｉの外周面には、スリーブ２０の内端部に一体に連設した外側筒部Ｐｏの内周面が抜差可能に嵌合される。 Further, the opened outer end side of the bottom boss 11b extends outward in the axial direction from the back surface of the side gear 11, and constitutes the inner cylindrical portion Pi of the present invention. The inner peripheral surface of the outer cylindrical portion Po integrally connected to the inner end portion of the sleeve 20 is fitted to the outer peripheral surface of the inner cylindrical portion Pi so as to be detachable.
　内側筒部Ｐｉ及び外側筒部Ｐｏの相互の嵌合面間には、相互の嵌合面間を連結する金属板製の連結部材Ｊと、相互の嵌合面間をシールする環状のシール部材としてのＯリング２６とが並列に介装される。尚、Ｏリング２６は、内側筒部Ｐｉ及び外側筒部Ｐｏの何れか一方の周面（本実施形態では内側筒部Ｐｉの外周面）に形成した環状のシール溝２７に装着される。 Between the mutual fitting surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po, a metal plate connecting member J for connecting the mutual fitting surfaces, and an annular sealing member for sealing the mutual fitting surfaces. And an O-ring 26 are interposed in parallel. The O-ring 26 is attached to an annular seal groove 27 formed on one of the peripheral surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po (in this embodiment, the outer peripheral surface of the inner cylindrical portion Pi).
　連結部材Ｊは、内側筒部Ｐｉ及び外側筒部Ｐｏの嵌合面の何れか一方（本実施形態では内側筒部Ｐｉの外周面）に圧入固定される連結筒部Ｊｐと、連結筒部Ｊｐの一端に周方向に間隔をおいて一体に連設される複数の弾性係止爪（弾性係止部材）Ｊｃとを備える。また内側筒部Ｐｉ及び外側筒部Ｐｏの嵌合面の何れか他方（本実施形態では外側筒部Ｐｏの内周面）には、複数の弾性係止爪Ｊｃを弾発的にそれぞれ係止させる複数の係止凹部（凹部）３０が、周方向に間隔をおいて形成される。 The connecting member J includes a connecting cylinder portion Jp that is press-fitted and fixed to either one of the fitting surfaces of the inner cylinder portion Pi and the outer cylinder portion Po (in this embodiment, the outer peripheral surface of the inner cylinder portion Pi), And a plurality of elastic locking claws (elastic locking members) Jc that are integrally connected to each other at intervals in the circumferential direction. A plurality of elastic locking claws Jc are elastically locked to either one of the fitting surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po (in this embodiment, the inner peripheral surface of the outer cylindrical portion Po). A plurality of locking recesses (recesses) 30 are formed at intervals in the circumferential direction.
　尚、連結筒部Ｊｐを圧入させる内側筒部Ｐｉの外周面には、連結部材Ｊを内側筒部Ｐｉ及び外側筒部Ｐｏの嵌合面間に無理なく収納し得るように小径部３１が先端寄りに形成される。即ち、内側筒部Ｐｉは段付き円筒状に形成される。また小径部３１の内端には、環状の括れ部３１ａが形成される。 A small-diameter portion 31 is provided at the outer peripheral surface of the inner cylindrical portion Pi into which the connecting cylindrical portion Jp is press-fitted so that the connecting member J can be easily stored between the fitting surfaces of the inner cylindrical portion Pi and the outer cylindrical portion Po. Formed closer. That is, the inner cylinder portion Pi is formed in a stepped cylindrical shape. An annular constricted portion 31 a is formed at the inner end of the small diameter portion 31.
　各々の弾性係止爪Ｊｃは、連結筒部Ｊｐの一端（実施形態では内側筒部Ｐｉの先端側）から他端（実施形態ではピニオン軸９側）に向かって横断面Ｕ字状に折り返されるように形成される。そして、連結筒部Ｊｐの軸線に沿う方向で弾性係止爪Ｊｃの両端部には、係止凹部３０に対する弾性係止爪Ｊｃの係脱を許容する傾斜部３２又は丸みを帯びた湾曲部３３が形成される。 Each elastic locking claw Jc is folded back in a U-shaped cross section from one end (in the embodiment, the front end side of the inner cylinder portion Pi) to the other end (in the embodiment, the pinion shaft 9 side) of the connecting cylinder portion Jp. Formed as follows. Then, at both ends of the elastic locking claw Jc in the direction along the axis of the connecting cylinder portion Jp, an inclined portion 32 that allows the elastic locking claw Jc to be engaged and disengaged with respect to the locking recess 30 or a rounded curved portion 33. Is formed.
　連結部材Ｊの製作に当たっては、金属製帯板の一側端に複数の弾性係止爪Ｊｃを成形し、その後、帯板を環状に成形して有端の連結筒部Ｊｐを構成する。その際、連結筒部Ｊｐには縮径弾性を付与する。 In manufacturing the connecting member J, a plurality of elastic locking claws Jc are formed on one end of a metal strip, and then the strip is formed into an annular shape to form an end-connected connecting tube portion Jp. At that time, reduced diameter elasticity is imparted to the connecting tube portion Jp.
　図示しない左右の車軸にそれぞれ連なる左右のドライブ軸７、８は、スリーブ２０を貫通してサイドギヤ１１の底付きボス１１ｂの内周にスプライン２９を介して嵌合されている。 Left and right drive shafts 7 and 8 connected to left and right axles (not shown) pass through the sleeve 20 and are fitted to the inner periphery of the bottom boss 11b of the side gear 11 via splines 29.
　次に、第１実施形態の作用について説明する。 Next, the operation of the first embodiment will be described.
　差動装置Ｄの組立てに当たっては、先ず、サイドギヤ１１と、ピニオンギヤ１０とを順次作業窓１８からデフケース１内に組み込む。組み込みの際、スリーブ２０は、サイドギヤ１１の底付きボス１１ｂの先端部、即ち内側筒部Ｐｉに対して未連結状態にある。また、内側筒部Ｐｉの小径部３１には連結部材Ｊの連結筒部Ｊｐが予め圧入固定されている。また、内側筒部Ｐｉの外周のシール溝２７にはＯリング２６が予め装着されている。 In assembling the differential device D, first, the side gear 11 and the pinion gear 10 are sequentially assembled into the differential case 1 from the work window 18. When assembled, the sleeve 20 is not connected to the tip of the bottom boss 11b of the side gear 11, that is, the inner cylinder Pi. Further, the connecting tube portion Jp of the connecting member J is press-fitted and fixed in advance to the small diameter portion 31 of the inner tube portion Pi. In addition, an O-ring 26 is attached in advance to the seal groove 27 on the outer periphery of the inner cylindrical portion Pi.
　次いで、各スリーブ２０をデフケース１の対応する軸受ボス１ａ，１ｂにデフケース１の外方からそれぞれ嵌挿させると共に、各サイドギヤ１１の内側筒部Ｐｉにスリーブ２０の外側筒部Ｐｏを嵌合させる。そして、上記嵌合の際には連結部材Ｊの複数の弾性係止爪Ｊｃを外側筒部Ｐｏの内周面の複数の係止凹部３０にそれぞれ嵌入係止させる。これにより、内側筒部Ｐｉ及び外側筒部Ｐｏの嵌合面間が連結部材Ｊを介して連結される。そのため、内側筒部Ｐｉ及び外側筒部Ｐｏ間の相対回転及び軸方向相対移動（即ちスリーブ２０の底付きボス１１ｂに対する相対回転と軸方向離脱）が規制される。それと同時に、内側筒部Ｐｉの外周のシール溝２７内のＯリング２６を、外側筒部Ｐｏの内周面に密接させる。 Next, each sleeve 20 is fitted into the corresponding bearing boss 1a, 1b of the differential case 1 from the outside of the differential case 1, and the outer cylindrical portion Po of the sleeve 20 is fitted into the inner cylindrical portion Pi of each side gear 11. And in the case of the said fitting, the some elastic latching claw Jc of the connection member J is each engage | inserted and latched by the some latching recessed part 30 of the inner peripheral surface of the outer side cylinder part Po. Thereby, the fitting surfaces of the inner cylinder portion Pi and the outer cylinder portion Po are connected via the connecting member J. Therefore, relative rotation and axial relative movement between the inner cylinder portion Pi and the outer cylinder portion Po (that is, relative rotation and axial separation of the sleeve 20 with respect to the bottomed boss 11b) are restricted. At the same time, the O-ring 26 in the seal groove 27 on the outer periphery of the inner cylindrical portion Pi is brought into close contact with the inner peripheral surface of the outer cylindrical portion Po.
　最後にピニオンギヤ１０を支持するピニオン軸９をデフケース１の支孔１２に嵌挿し、抜け止めピン１４をデフケース１及びピニオン軸９に圧入する。 Finally, the pinion shaft 9 that supports the pinion gear 10 is inserted into the support hole 12 of the differential case 1, and the retaining pin 14 is press-fitted into the differential case 1 and the pinion shaft 9.
　こうして組立てた差動装置Ｄはミッションケース１００に組み込んで、スリーブ２０の外端部とミッションケース１００との間にオイルシール２５を介装する。その後、ミッションケース１００内に潤滑オイルを注入すると、潤滑オイルの一部が作業窓１８を通してデフケース１内に流入して、差動ギヤ機構３の各部の潤滑に供される。 The differential device D thus assembled is assembled in the mission case 100, and an oil seal 25 is interposed between the outer end of the sleeve 20 and the mission case 100. Thereafter, when lubricating oil is injected into the mission case 100, a part of the lubricating oil flows into the differential case 1 through the work window 18 and is used for lubricating each part of the differential gear mechanism 3.
　而して、ミッションケース１００内の潤滑オイルは、オイルシール２５によって、スリーブ２０の外端部外周からの流出が阻止される。またデフケース１内の潤滑オイルは、Ｏリング２６によって、サイドギヤ１１の底付きボス１１ｂ及びスリーブ２０の相互の嵌合部からの流出が阻止される。こうしたことは、サイドギヤ１１からドライブ軸７、８を抜き取っても、ミッションケース１００及びデフケース１内の潤滑オイルが外部に流出しないことを意味する。 Therefore, the lubricating oil in the mission case 100 is prevented from flowing out from the outer periphery of the outer end portion of the sleeve 20 by the oil seal 25. Also, the lubricating oil in the differential case 1 is prevented from flowing out from the fitting portion between the bottom boss 11 b of the side gear 11 and the sleeve 20 by the O-ring 26. This means that even if the drive shafts 7 and 8 are extracted from the side gear 11, the lubricating oil in the transmission case 100 and the differential case 1 does not flow out to the outside.
　差動装置Ｄを収容したミッションケース１００が自動車に搭載されてから、左右のドライブ軸７、８は、対応するサイドギヤ１１の底付きボス１１ｂの内周にスプライン２９を介して嵌合される。 After the transmission case 100 containing the differential device D is mounted on the vehicle, the left and right drive shafts 7 and 8 are fitted to the inner periphery of the bottom boss 11b of the corresponding side gear 11 via the spline 29.
　差動装置Ｄの作動時、サイドギヤ１１の回転トルクは、スプライン２９を介してドライブ軸７、８に伝達する。同時にサイドギヤ１１の回転はスプライン２８を介してスリーブ２０に伝達するので、サイドギヤ１１、ドライブ軸７、８及びスリーブ２０は一体に回転する。その際、スリーブ２０の外周面は、第１及び第２軸受ボス１ａ，１ｂの潤滑溝２１に保持される潤滑オイルにより潤滑される。 During the operation of the differential device D, the rotational torque of the side gear 11 is transmitted to the drive shafts 7 and 8 through the spline 29. At the same time, the rotation of the side gear 11 is transmitted to the sleeve 20 via the spline 28, so that the side gear 11, the drive shafts 7 and 8, and the sleeve 20 rotate together. At that time, the outer peripheral surface of the sleeve 20 is lubricated by the lubricating oil held in the lubricating grooves 21 of the first and second bearing bosses 1a and 1b.
　以上説明した本実施形態の差動装置Ｄでは、サイドギヤ１１の底付きボス１１ｂに連結部材Ｊを介してスリーブ２０が連結されるため、連結に際してスリーブ２０を径方向に特別に弾性変形させる必要はなくなる。これにより、従来装置の、スリーブ（延長ボス，延長部材）２０の特設に伴う利点を確保可能とするばかりか、スリーブ２０を、スリーブ２０の構成材料の如何（例えば金属製か合成樹脂製か）を問わず、底付きボス１１ｂに的確に連結可能となる。これにより、スリーブ２０の材料選択の自由度を大幅に高めることができる。 In the differential device D of the present embodiment described above, since the sleeve 20 is connected to the bottom boss 11b of the side gear 11 via the connecting member J, it is necessary to specially elastically deform the sleeve 20 in the radial direction when connecting. Disappear. As a result, not only can the advantages associated with the special provision of the sleeve (extension boss, extension member) 20 of the conventional apparatus be ensured, but also the sleeve 20 can be made of any of the constituent materials of the sleeve 20 (for example, metal or synthetic resin). Regardless of the case, the bottom boss 11b can be accurately connected. Thereby, the freedom degree of material selection of the sleeve 20 can be raised significantly.
　しかも弾性係止爪Ｊｃを有する連結部材Ｊが、底付きボス１１ｂ及びスリーブ２０から分離独立した小部品として取り扱い可能となる。そのため、例えば弾性係止爪Ｊｃが破損劣化した場合には、小部品である連結部材Ｊだけを単に交換すれば済み、コスト節減が図られる。また、ピニオンギヤ１０やサイドギヤ１１をデフケース１内に装入した後に、スリーブ２０を単独で（即ち後付けで）軸受ボス１ａ，１ｂを通してサイドギヤ１１の底付きボス１１ｂに嵌合連結できる。そのため、スリーブ２０に邪魔されることなく作業窓１８からデフケース１への差動機構３の組付作業を行うことが可能となる。それにより、組立作業性の向上が図られる。 Moreover, the connecting member J having the elastic locking claw Jc can be handled as a small component that is separated and independent from the boss 11b with the bottom and the sleeve 20. Therefore, for example, when the elastic locking claw Jc is damaged and deteriorated, it is only necessary to replace only the connecting member J which is a small part, and the cost can be reduced. Further, after the pinion gear 10 and the side gear 11 are inserted into the differential case 1, the sleeve 20 can be fitted and connected to the bottom boss 11b of the side gear 11 through the bearing bosses 1a and 1b alone (that is, retrofitted). Therefore, it is possible to perform the assembling work of the differential mechanism 3 from the work window 18 to the differential case 1 without being obstructed by the sleeve 20. Thereby, the assembly workability is improved.
　その上、本実施形態では、上記弾性係止爪Ｊｃが連結部材Ｊの円筒状をなす連結筒部Ｊｐの一端から他端に向かって一体に折り返されるように形成されている。そのため、弾性係止爪Ｊｃの係止凹部３０への係止力を簡単な構造で十分に確保可能となる。しかも複数の弾性係止爪Ｊｃを一体に有する連結部材Ｊを金属板のプレス成形等により容易的確に成形可能である。 In addition, in this embodiment, the elastic locking claw Jc is formed so as to be integrally folded from one end of the connecting cylinder portion Jp of the connecting member J toward the other end. Therefore, it is possible to sufficiently secure the locking force of the elastic locking claw Jc to the locking recess 30 with a simple structure. In addition, the connecting member J integrally including the plurality of elastic locking claws Jc can be easily and accurately formed by press forming a metal plate or the like.
　さらに連結筒部Ｊｐの軸線に沿う方向で弾性係止爪Ｊｃの両端部には、係止凹部３０に対する弾性係止爪Ｊｃの係脱を許容し且つガイド可能な傾斜部３２又は湾曲部３３が形成されている。これにより、底付きボス１１ｂに対するスリーブ２０の抜差しを、弾性係止爪Ｊｃの一定の抵抗力に抗して行わせることができる。それにより、差動装置Ｄの分解組立の作業性が一層高められる。 Furthermore, inclined portions 32 or curved portions 33 that allow the elastic locking claws Jc to be engaged with and disengaged from the locking recesses 30 and can be guided at both ends of the elastic locking claws Jc in the direction along the axis of the connecting cylinder portion Jp. Is formed. Thereby, the insertion / extraction of the sleeve 20 with respect to the boss | hub 11b with a bottom can be performed against the fixed resistance of the elastic latching claw Jc. Thereby, workability of disassembly / assembly of the differential device D is further enhanced.
　次に、図６を参照して本発明の第２，第３実施形態について説明する。 Next, second and third embodiments of the present invention will be described with reference to FIG.
　先ず、図６（Ａ）に示す第２実施形態では、底付きボス１１ｂの開放された外端側が本発明の外側筒部Ｐｏを構成している。そして、外側筒部Ｐｏの内周面には、スリーブ２０の内端部に一体に連設した内側筒部Ｐｉの外周面が抜差可能に嵌合される。内側筒部Ｐｉ及び外側筒部Ｐｏの嵌合面間には、第１実施形態と同様に、金属板製の連結部材ＪとＯリング２６とが並列に介装され、連結部材Ｊの連結筒部Ｊｐがスリーブ２０側の内側筒部Ｐｉの外周面に圧入固定される。その他の構成は、第１実施形態と略同様であるので、第１実施形態と対応する部分については図６（Ａ）中に同一の参照符号を付して、重複する説明を省略する。そして、第２実施形態においても、基本的に第１実施形態と同様の作用効果を達成することができる。 First, in the second embodiment shown in FIG. 6A, the open outer end side of the bottomed boss 11b constitutes the outer cylindrical portion Po of the present invention. And the outer peripheral surface of the inner cylinder part Pi integrally connected with the inner end part of the sleeve 20 is fitted to the inner peripheral surface of the outer cylinder part Po so that it can be inserted and removed. Between the fitting surfaces of the inner cylinder portion Pi and the outer cylinder portion Po, a connecting member J made of a metal plate and an O-ring 26 are interposed in parallel as in the first embodiment, and the connecting cylinder of the connecting member J is connected. The portion Jp is press-fitted and fixed to the outer peripheral surface of the inner cylindrical portion Pi on the sleeve 20 side. Since other configurations are substantially the same as those of the first embodiment, portions corresponding to those of the first embodiment are denoted by the same reference numerals in FIG. 6A, and redundant description is omitted. And also in 2nd Embodiment, the effect similar to 1st Embodiment can be achieved fundamentally.
　また図６（Ｂ）に示す第３実施形態では、第１実施形態と同様、底付きボス１１ｂの開放された外端側が本発明の内側筒部Ｐｉを構成している。そして、内側筒部Ｐｉの外周面に、スリーブ２０の内端部に一体に連設した外側筒部Ｐｏの内周面が抜差可能に嵌合される。内側筒部Ｐｉ及び外側筒部Ｐｏの嵌合面間には、第１実施形態と同様に、金属板製の連結部材ＪとＯリング２６とが並列に介装され、連結部材Ｊの連結筒部Ｊｐが特にスリーブ２０側の外側筒部Ｐｏの内周面に圧入固定される。その他の構成は、第１実施形態と略同様であるので、第１実施形態と対応する部分については図６（Ｂ）中に同一の参照符号を付して、重複する説明を省略する。そして、第３実施形態においても、基本的に第１実施形態と同様の作用効果を達成することができる。 In the third embodiment shown in FIG. 6B, the open outer end side of the bottomed boss 11b constitutes the inner cylindrical portion Pi of the present invention, as in the first embodiment. The inner peripheral surface of the outer cylindrical portion Po integrally connected to the inner end portion of the sleeve 20 is fitted to the outer peripheral surface of the inner cylindrical portion Pi so that it can be inserted and removed. Between the fitting surfaces of the inner cylinder portion Pi and the outer cylinder portion Po, a connecting member J made of a metal plate and an O-ring 26 are interposed in parallel as in the first embodiment, and the connecting cylinder of the connecting member J is connected. The portion Jp is particularly press-fitted and fixed to the inner peripheral surface of the outer cylindrical portion Po on the sleeve 20 side. Since other configurations are substantially the same as those of the first embodiment, portions corresponding to those of the first embodiment are denoted by the same reference numerals in FIG. 6B, and redundant description is omitted. And also in 3rd Embodiment, the effect similar to 1st Embodiment can be achieved fundamentally.
　ところで以上の各実施形態では、差動機構３として、サイドギヤ１１及びピニオンギヤ１０を組み合わせたギヤ噛み合い形式のものを例示したが、本発明では、その他の種々の差動機構にも実施可能である。その一例として、例えば図７には、本発明の第４実施形態が示される。即ち、第４実施形態の差動装置Ｄ１は、転動ボール式の一対の変速機構を含む差動機構１３０を用いたものである。即ち、差動装置Ｄ１は、第１軸線Ｘ１を中心軸線とする第１伝動部材４０を一体に有するデフケース１１０と、第１軸線Ｘ１回りに回転する主軸部４１ｊ、および第１軸線Ｘ１から偏心した第２軸線Ｘ２上に位置する偏心軸部４１ｅを互いに一体に連結してなる偏心回転部材４１と、第１伝動部材４０に隣接配置されて偏心軸部４１ｅに回転自在に支持される第２伝動部材４２と、第２伝動部材４２に隣接配置されて第１軸線Ｘ１回りに回転する第３伝動部材４３と、第１及び第２伝動部材４０，４２間で変速しつつトルク伝達可能な第１変速機構Ｔ１と、第２及び第３伝動部材４２，４３間で変速しつつトルク伝達可能な第２変速機構Ｔ２と、を備える。 By the way, in each of the above embodiments, the differential mechanism 3 is exemplified as a gear meshing type in which the side gear 11 and the pinion gear 10 are combined. However, the present invention can also be implemented in various other differential mechanisms. As an example thereof, for example, FIG. 7 shows a fourth embodiment of the present invention. That is, the differential device D1 of the fourth embodiment uses a differential mechanism 130 including a pair of rolling ball type transmission mechanisms. That is, the differential device D1 is eccentric from the differential case 110 integrally including the first transmission member 40 having the first axis X1 as the central axis, the main shaft portion 41j rotating around the first axis X1, and the first axis X1. An eccentric rotating member 41 formed by integrally connecting eccentric shaft portions 41e located on the second axis X2 and a second transmission that is disposed adjacent to the first transmission member 40 and is rotatably supported by the eccentric shaft portion 41e. A first transmission capable of transmitting torque while shifting between the member 42, a third transmission member 43 disposed adjacent to the second transmission member 42 and rotating around the first axis X1, and the first and second transmission members 40, 42. A transmission mechanism T1 and a second transmission mechanism T2 capable of transmitting torque while shifting between the second and third transmission members 42 and 43 are provided.
　第１変速機構Ｔ１は、第１伝動部材４０の、第２伝動部材４２との対向面に第１軸線Ｘ１を中心として形成される波形環状（実施形態ではトロコイド状又はサイクロイド状、以下同様）の第１伝動溝５１と、第２伝動部材４２の、第１伝動部材４０との対向面に第２軸線Ｘ２を中心として形成される波形環状で波数が第１伝動溝５１とは異なる第２伝動溝５２と、第１及び第２伝動溝５１，５２の複数の重なり部に介装され、第１及び第２伝動溝５１，５２を転動しながら第１及び第２伝動部材４０，４２間の変速伝動を行う複数のボール状の第１転動体５３とで構成される。 The first speed change mechanism T1 has a wave-like annular shape (in the embodiment, a trochoidal shape or a cycloid shape, the same applies hereinafter) formed on the surface of the first transmission member 40 facing the second transmission member 42 with the first axis X1 as the center. A second transmission in which the wave number is different from that of the first transmission groove 51 in a wave shape formed around the second axis X2 on the surface of the first transmission groove 51 and the second transmission member 42 facing the first transmission member 40. Between the first and second transmission members 40, 42 while rolling on the first and second transmission grooves 51, 52, interposed between the groove 52 and a plurality of overlapping portions of the first and second transmission grooves 51, 52. And a plurality of ball-shaped first rolling elements 53 that perform the following transmission.
　また、第２変速機構Ｔ２は、第２伝動部材４２の、第３伝動部材４３との対向面に第２軸線Ｘ２を中心として形成される波形環状の第３伝動溝５４と、第３伝動部材４３の、第２伝動部材４２との対向面に第１軸線Ｘ１を中心として形成される波形環状で波数が第３伝動溝５４とは異なる第４伝動溝５５と、第３及び第４伝動溝５４，５５の複数の重なり部に介装され、第３及び第４伝動溝５４，５５を転動しながら第２及び第３伝動部材４２，４３間の変速伝動を行う複数のボール状の第２転動体５６と、で構成される。尚、図７において、符号Ｗは、第２伝動部材４２の径方向外方に配置されるバランスウェイトである。また符号Ｉは、バランスウェイトＷを第１軸線Ｘ１に関し偏心軸部４１ｅとは逆位相の位置に保持しつつ偏心回転部材４１と同期回転させる同期回転機構である。 In addition, the second transmission mechanism T2 includes a third annular transmission groove 54 having an annular shape formed around the second axis X2 on the surface of the second transmission member 42 facing the third transmission member 43, and a third transmission member. 43, a fourth transmission groove 55 having a wave number different from that of the third transmission groove 54 and having a wave number different from that of the third transmission groove 54 formed on the surface facing the second transmission member 42 around the first axis X1, and the third and fourth transmission grooves A plurality of ball-shaped second gears which are interposed in a plurality of overlapping portions of 54 and 55 and perform transmission transmission between the second and third transmission members 42 and 43 while rolling in the third and fourth transmission grooves 54 and 55. 2 rolling elements 56. In FIG. 7, reference sign W is a balance weight that is disposed radially outward of the second transmission member 42. Reference numeral I denotes a synchronous rotation mechanism that rotates in synchronization with the eccentric rotation member 41 while holding the balance weight W at a position opposite to the eccentric shaft portion 41e with respect to the first axis X1.
　そして、第１伝動溝５１の波数をＺ１、第２伝動溝５２の波数をＺ２、第３伝動溝５４の波数をＺ３、第４伝動溝５５の波数をＺ４としたとき、
（Ｚ１／Ｚ２）×（Ｚ３／Ｚ４）＝２　が成立するように各波数が設定される。 When the wave number of the first transmission groove 51 is Z1, the wave number of the second transmission groove 52 is Z2, the wave number of the third transmission groove 54 is Z3, and the wave number of the fourth transmission groove 55 is Z4,
Each wave number is set so that (Z1 / Z2) × (Z3 / Z4) = 2 holds.
　かくして、車載のエンジンから変速装置を経てデフケース１１０に入力された回転力が第１，第２変速機構Ｔ１，Ｔ２を経由して偏心回転部材４１及び第３伝動部材４３に伝達される。これにより、偏心回転部材４１及び第３伝動部材４３は、相互の差動回転を許容しつつ回転駆動可能となる。 Thus, the rotational force input to the differential case 110 from the vehicle-mounted engine via the transmission is transmitted to the eccentric rotation member 41 and the third transmission member 43 via the first and second transmission mechanisms T1 and T2. Thereby, the eccentric rotation member 41 and the third transmission member 43 can be rotationally driven while allowing mutual differential rotation.
　而して、第４実施形態では、偏心回転部材４１及び第３伝動部材４３が差動機構３の一対の出力部材を構成している。また、偏心回転部材４１及び第３伝動部材４３の内周部には、第１～第３実施形態のサイドギヤ１１と同様に、底付きボス（有底部材）１１ｂが一体に連設される。そして、底付きボス１１ｂと、一対の延長ボス（延長部材）としてのスリーブ２０との間が、第１～第３実施形態と同様、連結部材Ｊを用いた連結構造により連結される。 Thus, in the fourth embodiment, the eccentric rotating member 41 and the third transmission member 43 constitute a pair of output members of the differential mechanism 3. Further, similarly to the side gear 11 of the first to third embodiments, a bottomed boss (bottomed member) 11b is integrally connected to the inner peripheral portions of the eccentric rotating member 41 and the third transmission member 43. The bottom boss 11b and the sleeve 20 as a pair of extension bosses (extension members) are connected by a connection structure using the connection member J, as in the first to third embodiments.
　第４実施形態において、その他の構成は、第１実施形態と略同様であるので、第１実施形態と対応する部分については図７中に同一の参照符号を付して、重複する説明を省略する。そして、第４実施形態においても、基本的に第１実施形態と同様の作用効果を達成することができる。 In the fourth embodiment, the other configurations are substantially the same as those in the first embodiment, and therefore, the portions corresponding to those in the first embodiment are denoted by the same reference numerals in FIG. To do. And also in 4th Embodiment, the effect similar to 1st Embodiment can be achieved fundamentally.
　以上、本発明の実施形態を説明したが、本発明は、上述の実施形態に限定されるものではなく、その要旨を逸脱しない範囲で種々の設計変更が可能である。 As mentioned above, although embodiment of this invention was described, this invention is not limited to the above-mentioned embodiment, A various design change is possible in the range which does not deviate from the summary.
　例えば、上記第１～第３実施形態では、リングギヤ１７及びフランジ１５の相互の結合において、ボルト締結に代えて溶接を採用することができる。また、上記第４実施形態では、リングギヤ１７及びデフケース１１０の相互の結合において、溶接に代えてボルト締結を採用することができる。 For example, in the first to third embodiments, welding can be adopted in place of bolt fastening in mutual coupling of the ring gear 17 and the flange 15. Moreover, in the said 4th Embodiment, in the mutual coupling | bonding of the ring gear 17 and the differential case 110, it can replace with welding and can employ | adopt bolt fastening.
　また上述の実施形態において、デフケース１，１１０の内周面の形状は、球状に代えて箱状、円筒状等の形状を採用することもできる。何れの場合でも、スリーブ２０は、デフケース１，１１０の外側から軸受ボス１ａ，１ｂの内周に嵌挿し得るように構成されて、対応する底付きボス１１ｂと嵌合する。また、左右のスリーブ２０は、それぞれの長さを相違させてもよい。 In the above-described embodiment, the shape of the inner peripheral surface of the differential case 1,110 may be a box shape, a cylindrical shape, or the like instead of a spherical shape. In any case, the sleeve 20 is configured to be fitted into the inner periphery of the bearing bosses 1a and 1b from the outside of the differential case 1 and 110, and is fitted to the corresponding bottomed boss 11b. The left and right sleeves 20 may have different lengths.
　また上述の実施形態では、デフケース１，１１０の軸方向両側部に、ミッションケース１００に回転自在に支持される軸受ボス（軸受部材）１ａ，１ｂをそれぞれ一体に連設したものを示したが、本発明は、これに限らない。本発明は、例えばデフケース１，１１０の一側部にだけ軸受ボスを連設し、他側部は、他の支持部材を介してミッションケース１００に回転自在に支持させるようにしてもよい。 In the above-described embodiment, bearing bosses (bearing members) 1a and 1b that are rotatably supported by the mission case 100 are integrally provided on both sides of the differential case 1 and 110 in the axial direction. The present invention is not limited to this. In the present invention, for example, a bearing boss may be provided continuously only on one side of the differential case 1,110, and the other side may be rotatably supported by the transmission case 100 via another support member.
　また上述の実施形態では、内側筒部Ｐｉ又は外側筒部Ｐｏの周面に連結部材Ｊの連結筒部Ｊｐを圧入により嵌合固定するようにしたものを示したが、本発明はこれに限らない。本発明は、圧入以外の適当な固定手段、例えば接着、カシメ、溶接等で連結筒部Ｊｐを固定してもよい。 Moreover, in the above-mentioned embodiment, although what connected and fixed the connection cylinder part Jp of the connection member J to the surrounding surface of the inner side cylinder part Pi or the outer side cylinder part Po was shown, this invention is not limited to this. Absent. In the present invention, the connecting tube portion Jp may be fixed by an appropriate fixing means other than press fitting, for example, adhesion, caulking, welding, or the like.
　また上述の実施形態では、差動装置Ｄ，Ｄ１を自動車のミッションケース１００内に収容しているが、差動装置Ｄ，Ｄ１は自動車用の差動装置に限定されるものではなく、種々の機械装置用の差動装置としても実施することができる。 In the above-described embodiment, the differential devices D and D1 are accommodated in the vehicle mission case 100. However, the differential devices D and D1 are not limited to the differential devices for vehicles, It can also be implemented as a differential for a mechanical device.
　また上述の実施形態では、差動装置Ｄ，Ｄ１を、左・右輪伝動系に適用して、左右の駆動車軸に対し差動回転を許容しつつ動力を分配するものを示したが、本発明はこれに限らない。本発明は、例えば差動装置を、前・後輪駆動車両における前・後輪伝動系に適用して、前後の駆動車輪に対し差動回転を許容しつつ動力を分配するようにしてもよい。 In the above-described embodiment, the differential devices D and D1 are applied to the left and right wheel transmission systems to distribute power while allowing differential rotation with respect to the left and right drive axles. The invention is not limited to this. In the present invention, for example, the differential device may be applied to a front / rear wheel transmission system in a front / rear wheel drive vehicle to distribute power while allowing differential rotation to the front and rear drive wheels. .
　また特に上記第４実施形態では、第１変速機構Ｔ１として、第１伝動溝５１及び第２伝動溝５２、並びに第１，第２伝動溝５１，５２間に介装した第１伝動ボール５３よりなる転動ボール式変速機構を用い、また第２変速機構Ｔ２として、第３伝動溝５４及び第４伝動溝５５、並びに第３，第４伝動溝５４，５５間に介装した第２伝動ボール５６よりなる転動ボール式変速機構を用いたものを示したが、本発明はこれに限らない。本発明はこのような転動ボール式変速機構に代えて、例えば偏心回転部材の回転に連動して第２軸線回りの自転及び第１軸線回りの公転が可能な第２伝動部材を含む種々の変速機構、例えば内接式遊星歯車機構や、種々の構造のサイクロイド減速機（増速機）或いはトロコイド減速機（増速機）を、第１，第２変速機構Ｔ１，Ｔ２のうちの少なくとも一方に適用するようにしてもよい。 Particularly in the fourth embodiment, the first transmission mechanism 51 includes the first transmission groove 51, the second transmission groove 52, and the first transmission ball 53 interposed between the first and second transmission grooves 51, 52. And a second transmission ball interposed between the third transmission groove 54 and the fourth transmission groove 55 and the third and fourth transmission grooves 54 and 55 as the second transmission mechanism T2. Although one using a rolling ball type transmission mechanism comprising 56 is shown, the present invention is not limited to this. The present invention replaces such a rolling ball type transmission mechanism with various second transmission members that can rotate around the second axis and revolve around the first axis in conjunction with the rotation of the eccentric rotation member, for example. A speed change mechanism, for example, an inscribed planetary gear mechanism, a cycloid speed reducer (speed increaser) or a trochoid speed reducer (speed increase speed) of various structures, and at least one of the first speed change mechanism T1 and the second speed change mechanism T2 You may make it apply to.
　また上記第４実施形態では、第１，第２変速機構Ｔ１，Ｔ２の第１及び第２伝動溝５１，５２間、並びに第３及び第４伝動溝５４，５５間に、ボール状の第１及び第２転動体５３，５６を介装したものを示したが、本発明はこれに限らない。本発明は例えば転動体をローラ状又はピン状としてもよい。ただし、この場合には、第１及び第２伝動溝５１，５２、並びに第３及び第４伝動溝５４，５５は、ローラ状又はピン状の転動体が転動し得るように内側面の形状が形成される。 Further, in the fourth embodiment, the first ball-shaped first between the first and second transmission grooves 51 and 52 and between the third and fourth transmission grooves 54 and 55 of the first and second transmission mechanisms T1 and T2. And what showed the 2nd rolling elements 53 and 56 interposed was shown, but this invention is not limited to this. In the present invention, for example, the rolling element may have a roller shape or a pin shape. However, in this case, the first and second transmission grooves 51 and 52 and the third and fourth transmission grooves 54 and 55 are formed on the inner surface so that the roller-like or pin-like rolling elements can roll. Is formed.

Claims (3)

  1. 　差動機構（３，１３０）を収容するデフケース（１，１１０）が、該デフケース（１，１１０）の少なくとも一側部に、ミッションケース（１００）に回転自在に支持される軸受部材（１ａ，１ｂ）を有し、前記差動機構（３，１３０）の、前記軸受部材（１ａ，１ｂ）寄りの出力部材（１１；４１，４３）が、内端側を閉塞した有底部材（１１ｂ）を有し、前記有底部材（１１ｂ）には、前記軸受部材（１ａ，１ｂ）に該軸受部材（１ａ，１ｂ）の外端側から嵌挿される延長部材（２０）が連結され、前記延長部材（２０）の前記軸受部材（１ａ，１ｂ）より突出する外端部と前記ミッションケース（１００）との間にオイルシール（２５）が介装され、前記有底部材（１１ｂ）には、前記延長部材（２０）に嵌挿されるドライブ軸（７，８）がスプライン嵌合される差動装置において、
    　前記有底部材（１１ｂ）及び前記延長部材（２０）の何れか一方には内側筒部（Ｐｉ）が、前記有底部材（１１ｂ）及び前記延長部材（２０）の何れか他方には該内側筒部（Ｐｉ）に嵌合する外側筒部（Ｐｏ）が、それぞれ設けられ、
    　前記内側筒部（Ｐｉ）及び前記外側筒部（Ｐｏ）の相互間には、前記内側筒部（Ｐｉ）及び前記外側筒部（Ｐｏ）の相互間を連結する連結部材（Ｊ）と、前記内側筒部（Ｐｉ）及び前記外側筒部（Ｐｏ）の相互間をシールするシール部材（２６）とが介装され、
    　前記連結部材（Ｊ）は、前記内側筒部（Ｐｉ）及び前記外側筒部（Ｐｏ）の相互の嵌合面の何れか一方に嵌合固定される連結筒部（Ｊｐ）と、前記連結筒部（Ｊｐ）の一端に一体に連設される弾性係止部材（Ｊｃ）と、を備え、
    　前記弾性係止部材（Ｊｃ）を弾発的に係止させる凹部（３０）が、前記内側筒部（Ｐｉ）及び前記外側筒部（Ｐｏ）の相互の嵌合面の何れか他方に設けられる、差動装置。     A differential case (1, 110) that accommodates the differential mechanism (3, 130) is supported at least on one side of the differential case (1, 110) by a bearing member (1a, 1b), and a bottomed member (11b) in which the output member (11; 41, 43) near the bearing member (1a, 1b) of the differential mechanism (3, 130) closes the inner end side. The bottomed member (11b) is connected to the extension member (20) inserted from the outer end side of the bearing member (1a, 1b) to the bearing member (1a, 1b). An oil seal (25) is interposed between the outer end of the member (20) protruding from the bearing member (1a, 1b) and the transmission case (100), and the bottomed member (11b) Drive shafts (7, 7) fitted into the extension members (20) ) In the differential gear is splined,
    One of the bottomed member (11b) and the extension member (20) has an inner cylindrical portion (Pi), and the other of the bottomed member (11b) and the extension member (20) has the inner side. The outer cylinder part (Po) fitted to the cylinder part (Pi) is respectively provided,
    Between the inner cylinder part (Pi) and the outer cylinder part (Po), a connecting member (J) for connecting the inner cylinder part (Pi) and the outer cylinder part (Po), and A seal member (26) that seals between the inner cylinder part (Pi) and the outer cylinder part (Po) is interposed,
    The connecting member (J) includes a connecting tube portion (Jp) fitted and fixed to any one of the mutual fitting surfaces of the inner tube portion (Pi) and the outer tube portion (Po), and the connecting tube. An elastic locking member (Jc) integrally connected to one end of the portion (Jp),
    A recess (30) for elastically locking the elastic locking member (Jc) is provided on either one of the mutual fitting surfaces of the inner cylindrical portion (Pi) and the outer cylindrical portion (Po). Differential.
  2. 　前記弾性係止部材（Ｊｃ）は、前記連結筒部（Ｊｐ）の前記一端から他端に向かって折り返されるように設けられる、請求項１に記載の差動装置。 The differential device according to claim 1, wherein the elastic locking member (Jc) is provided so as to be folded back from the one end to the other end of the connecting tube portion (Jp).
  3. 　前記連結筒部（Ｊｐ）の軸線に沿う方向で前記弾性係止部材（Ｊｃ）の両端部には、前記凹部（３０）に対する該弾性係止部材（Ｊｃ）の係脱を許容する傾斜部（３２）又は湾曲部（３３）が設けられる、請求項２に記載の差動装置。
          At both ends of the elastic locking member (Jc) in a direction along the axis of the connecting cylinder portion (Jp), inclined portions that allow the elastic locking member (Jc) to be engaged and disengaged with respect to the concave portion (30) ( 32) A differential device according to claim 2, wherein 32 or a curved portion (33) is provided.
PCT/JP2016/079422 2015-10-07 2016-10-04 Differential device WO2017061409A1 (en)

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Cited By (2)

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JP2020176714A (en) * 2019-04-22 2020-10-29 トヨタ自動車株式会社 Vehicle differential gear unit
US20220268348A1 (en) * 2019-09-03 2022-08-25 Jing-Jin Electric Technologies Co., Ltd. Electric drive assembly of dry differential and new energy automobile

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* Cited by examiner, † Cited by third party
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JP2015064040A (en) * 2013-09-25 2015-04-09 トヨタ自動車株式会社 Spline positioning tooth-hammering buffer mechanism of vehicle power transmission device
JP2015148313A (en) * 2014-02-07 2015-08-20 武蔵精密工業株式会社 Differential device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015064040A (en) * 2013-09-25 2015-04-09 トヨタ自動車株式会社 Spline positioning tooth-hammering buffer mechanism of vehicle power transmission device
JP2015148313A (en) * 2014-02-07 2015-08-20 武蔵精密工業株式会社 Differential device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020176714A (en) * 2019-04-22 2020-10-29 トヨタ自動車株式会社 Vehicle differential gear unit
US20220268348A1 (en) * 2019-09-03 2022-08-25 Jing-Jin Electric Technologies Co., Ltd. Electric drive assembly of dry differential and new energy automobile

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