WO2017154898A1 - Dispositif de transmission de puissance - Google Patents

Dispositif de transmission de puissance Download PDF

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Publication number
WO2017154898A1
WO2017154898A1 PCT/JP2017/008980 JP2017008980W WO2017154898A1 WO 2017154898 A1 WO2017154898 A1 WO 2017154898A1 JP 2017008980 W JP2017008980 W JP 2017008980W WO 2017154898 A1 WO2017154898 A1 WO 2017154898A1
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WO
WIPO (PCT)
Prior art keywords
transmission
axis
casing
transmission member
facing
Prior art date
Application number
PCT/JP2017/008980
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English (en)
Japanese (ja)
Inventor
慎弥 松岡
隆憲 野口
Original Assignee
武蔵精密工業株式会社
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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 WO2017154898A1 publication Critical patent/WO2017154898A1/fr

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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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
    • 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
    • F16H48/12—Differential gearings without gears having orbital motion
    • F16H48/14—Differential gearings without gears having orbital motion with cams

Definitions

  • the present invention relates to a transmission device, in particular, a first transmission member having a first axis as a central axis, a first transmission shaft rotating around the first axis, and an eccentric having a second axis eccentric from the first axis as a central axis.
  • An eccentric rotating member integrally connected to the shaft, a second transmission member that is rotatably supported by the eccentric shaft around the second axis, and that rotates around the first axis.
  • a third transmission member connected coaxially to the second transmission shaft and facing the second transmission member; a first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members; and second and second transmission members.
  • the present invention relates to a transmission apparatus including a second transmission mechanism capable of transmitting torque while shifting between three transmission members, and a casing that houses first to third transmission members.
  • the transmission device is conventionally known as disclosed in, for example, Patent Document 1.
  • the first speed change mechanism is located on a surface of the first transmission member facing the second transmission member, and the first axis is arranged.
  • a plurality of first transmission gears and a plurality of first transmission gears that are interposed between a plurality of intersections of the first and second transmission grooves and perform transmission between the first and second transmission members while rolling the first and second transmission grooves.
  • a third transmission groove that is on the surface of the second transmission member facing the third transmission member and that is centered on the second axis, and the second transmission mechanism has a first rolling element.
  • a wave-shaped annular member having a wave number different from that of the third transmission groove on the surface of the member facing the second transmission member and centering on the first axis.
  • a plurality of first transmission grooves and a plurality of second transmission gears which are interposed at a plurality of intersections of the third and fourth transmission grooves and perform the transmission between the second and third transmission members while rolling the third and fourth transmission grooves.
  • the first transmission member and the first transmission member are integrated with one side wall of the casing, while the first transmission shaft and the third transmission member are supported on the casing via bearings, respectively.
  • the three coaxial arrangements of the transmission shaft and the third transmission member (second transmission shaft) are secured in association with the casing.
  • the present invention has been made in view of such circumstances, and provides a transmission device that can increase the transmission efficiency of the first and second transmission mechanisms without requiring a particularly high machining accuracy in the support portion. Objective.
  • the present invention is centered on a first transmission member having a first axis as a central axis, a first transmission shaft rotating around the first axis, and a second axis eccentric from the first axis.
  • An eccentric rotating member integrally connected to an eccentric shaft portion serving as an axis, a second transmission member that is rotatably supported by the eccentric shaft portion around a second axis, and faces the first transmission member;
  • a third transmission member that is coaxially connected to a second transmission shaft that rotates about one axis and that faces the second transmission member, and a first gear that can transmit torque while shifting between the first and second transmission members.
  • a plurality of first rolling elements for performing transmission transmission, and the second transmission mechanism is located on a surface of the second transmission member facing the third transmission member and has a corrugated annular shape centering on a second axis.
  • the second and second transmission grooves are interposed at a plurality of intersections of the third and fourth transmission grooves and roll on the third and fourth transmission grooves.
  • a plurality of second rolling elements for performing transmission transmission between transmission members, performing transmission transmission between the first and second transmission shafts, or applying rotational torque from the casing to the first and second transmission shafts.
  • the first transmission member is configured separately from the casing, and is connected to the casing so as to be axially movable relative to the casing and to be relatively non-rotatable.
  • a biasing means for biasing the first to third transmission members toward the other side wall of the casing is interposed between the first transmission member and one side wall of the casing facing the first transmission member.
  • the present invention has a second feature that the first transmission member is given play in a radial direction with respect to the casing.
  • an initial biasing force of the biasing means is provided between the other side wall of the casing and the third transmission member facing the other side wall.
  • a third feature is that a shim for adjusting the load is interposed.
  • the present invention has a fourth feature that the third transmission member is given play in the radial direction with respect to the casing.
  • an external shaft supported rotatably on the other side wall of the casing around the first axis is spline-fitted to the second transmission shaft so as to be freely movable in the radial direction.
  • the present invention provides a first transmission member having a first axis as a central axis, a first transmission shaft that rotates about the first axis, and a second axis that is eccentric from the first axis.
  • An eccentric rotation member integrally connected to an eccentric shaft portion serving as a central axis, a second transmission member that is rotatably supported by the eccentric shaft portion around a second axis, and faces the first transmission member;
  • a third transmission member that is coaxially connected to a second transmission shaft that rotates about the first axis and that faces the second transmission member, and a first gear that is capable of transmitting torque while shifting between the first and second transmission members.
  • a first transmission mechanism a second transmission mechanism capable of transmitting torque while shifting between the second and third transmission members, and a casing that houses the first to third transmission members, wherein the first transmission mechanism
  • the first transmission member is located on a surface facing the second transmission member.
  • the first transmission groove having an annular shape centered on the first axis and the first transmission groove of the second transmission member facing the first transmission member, and the first wave number having a waveform shape centering on the second axis.
  • a second transmission groove different from the transmission groove and a plurality of intersecting portions of the first and second transmission grooves are interposed between the first and second transmission members while rolling the first and second transmission grooves.
  • a plurality of first rolling elements that perform the transmission of the first speed, and the second speed change mechanism is a waveform of the second power transmission member on a surface facing the third power transmission member and centering on the second axis.
  • An annular third transmission groove and a fourth transmission groove on the surface of the third transmission member facing the second transmission member and having a wave shape centered on the first axis and having a wave number different from that of the third transmission groove And interposed between a plurality of intersections of the third and fourth transmission grooves, while rolling the third and fourth transmission grooves, the second and second A plurality of second rolling elements for performing transmission transmission between transmission members, performing transmission transmission between the first and second transmission shafts, or applying rotational torque from the casing to the first and second transmission shafts.
  • the first transmission shaft is supported on one side wall of the casing so as to be rotatable around a first axis
  • the second transmission shaft is
  • the second outer shaft is supported on the other side wall of the casing so as to be rotatable about the first axis.
  • the first transmission member is configured separately from the casing.
  • the first transmission member has radial play with respect to the casing
  • the second transmission shaft has radial play with respect to the second external shaft.
  • connection between the first transmission member and the casing allows mutual relative movement in the axial direction, and the first transmission member,
  • a biasing means for biasing the first to third transmission members toward the other side wall of the casing is interposed between the one side wall of the casing facing the seventh side.
  • the first transmission member is configured separately from the casing, and is connected to the casing so as to be relatively movable in the axial direction and not to be rotatable relative to the casing.
  • an urging means for urging the first to third transmission members toward the other side wall of the casing are interposed between the opposite side wall of the casing and the urging means.
  • the first and second transmission mechanisms can be used without requiring a particularly high machining accuracy for the support portion of the first transmission member, the first transmission shaft, and the third transmission member (second transmission shaft) to the casing. Therefore, it is possible to contribute to the reduction of the manufacturing cost of the apparatus. Moreover, since the urging means is interposed between the casing and the first transmission member that are connected so as not to rotate relative to each other, the urging means hardly rubs against the casing and the first transmission member even during transmission. The wear is avoided and high durability can be secured.
  • the first transmission member is given play in the radial direction with respect to the casing, so that the first rolling element and the first and second transmission grooves by the biasing means are Due to the biasing engagement, the first transmission member can be automatically aligned with the second transmission member without being affected by the casing, so that the plurality of first rolling elements and the first and second transmission grooves are appropriate.
  • the transmission efficiency of the first speed change mechanism can be further improved.
  • a shim for adjusting the initial load of the biasing force of the biasing means is interposed between the other side wall of the casing and the third transmission member facing the other side wall.
  • the initial load of the urging force can be easily adjusted by selecting the thickness of the shim.
  • the shim can also function as a washer that reduces rotational friction between the third transmission member and the other side wall of the casing, and thus can contribute to improving the durability of the third transmission member and the casing.
  • the third transmission member is provided with play in the radial direction with respect to the casing, so that the second rolling element by the biasing means and the third and fourth transmission grooves are provided.
  • the third transmission member can be automatically aligned with the second transmission member without being affected by the casing, so that the plurality of second rolling elements and the third and fourth transmission grooves are appropriate.
  • the transmission efficiency of the second speed change mechanism is further improved.
  • the second transmission shaft is spline-fitted with an external shaft rotatably supported around the first axis on the other side wall of the casing so as to be freely movable in the radial direction.
  • the torque can be transmitted from the second transmission shaft to the external shaft supported by the other side wall of the casing, and the second transmission shaft has play in the radial direction with respect to the external shaft. It can be avoided that the self-aligning action is hindered by the external shaft.
  • the first transmission member is configured separately from the casing, and is connected to the casing so as not to rotate relative to the casing.
  • the first transmission member has a radial direction relative to the casing. Since play is imparted, the first transmission member can be automatically aligned with the second transmission member opposed thereto via the first transmission mechanism, and the plurality of first rolling elements and the first and second transmission grooves are provided. And the transmission efficiency of the first speed change mechanism is improved.
  • the second transmission shaft is provided with play in the radial direction with respect to the second external shaft, the third transmission member that rotates coaxially with the second transmission shaft has a second speed change mechanism with respect to the second transmission member that faces the second transmission shaft.
  • the plurality of second rolling elements and the third and fourth transmission grooves are properly engaged with each other, and the transmission efficiency of the second speed change mechanism is improved. As a result, a transmission device having high transmission efficiency as a whole can be obtained.
  • the mutual connection between the first transmission member and the casing allows the relative movement in the axial direction of the first transmission member and faces the first transmission member. Since biasing means for biasing the first to third transmission members toward the other side wall of the casing is interposed between one side wall of the casing and the biasing force by the biasing means is the first and second. It is possible to automatically eliminate the backlash between the transmission groove and the rolling elements in each transmission mechanism by acting on the transmission mechanism, and this backlash elimination effect and the automatic operation of the first and third transmission members with respect to the second transmission member described above. Combined with the alignment effect, the transmission efficiency of the first and second transmission mechanisms can be further improved.
  • FIG. 1 is a longitudinal front view of a differential according to an embodiment of the present invention.
  • (First embodiment) 2 is a cross-sectional view taken along line 2-2 of FIG.
  • (First embodiment) 3 is a cross-sectional view taken along line 3-3 of FIG.
  • (First embodiment) 4 is a cross-sectional view taken along line 4-4 of FIG. (First embodiment)
  • A1, A2, ... 1st and 2nd drive axles (1st and 2nd external shafts) C: Differential case (casing) Ca, Cb .. 1st and 2nd side wall (one side wall, other side wall) D ... Differential device (transmission device) S1, S2, ⁇ First and second transmission shafts SP1 to SP3 ⁇ Spline fitting (connection) T1, T2,..., First and second transmission mechanisms X1, X2,..., First and second axis 5 ... first transmission member 6 ... eccentric rotation member 6e ... eccentric shaft 8 ... 2nd transmission member 9 ... 3rd transmission member 15 ... Thrust washer (shim) 21, 22... First and second transmission grooves 23, 26... First and second balls (first and second rolling elements) 24, 25 .. Third and fourth transmission grooves 50... Disc spring (biasing means)
  • a differential device D as a transmission device is housed in a transmission case 1 of an automobile together with a transmission.
  • the left and right first and second drives are arranged so that the rotation of the ring gear Cm that rotates in conjunction with the output side of the transmission device can be relatively rotated on the central axis of the differential device D, that is, the first axis X1.
  • Distributing the axles A1 and A2 that is, the first and second external shafts
  • the drive axles A1, A2 and the transmission case 1 are sealed with seal members 4, 4 '.
  • the differential device D includes a differential case C that is supported by the mission case 1 so as to be rotatable about the first axis X1, and a differential mechanism 3 described later that is accommodated in the differential case C.
  • the differential case C includes a short cylindrical ring gear Cm integrally having a helical gear portion on the outer periphery, and a pair of left and right first and second side walls Ca and Cb whose outer peripheral end portions are respectively joined to both axial ends of the ring gear Cm. Is provided.
  • the joint surfaces between the outer peripheral ends of the first and second side walls Ca and Cb and the ring gear Cm are integrally joined by appropriate joining means such as welding, adhesion, and caulking.
  • the first and second side walls Ca and Cb integrally have cylindrical boss-like first and second bearings B1 and B2 that extend outward in the axial direction at the inner peripheral ends of the first and second side walls Ca and Cb, respectively.
  • the outer peripheral portions of the second bearings B1 and B2 are supported by the transmission case 1 via the outer bearings 2 and 2 'so as to be rotatable around the first axis X1.
  • first and second drive axles A1 and A2 having a first axis X1 as a rotation axis are rotatably fitted and supported on inner peripheral portions of the first and second bearings B1 and B2, respectively.
  • An inner bearing separate from the differential case C is mounted on the inner peripheral portion of the first and second bearings B1 and B2, and the first and second drive axles A1 and A2 are rotatably supported by the inner bearing. You may let them.
  • the differential mechanism 3 includes a ring plate-shaped first transmission member 5 having the first axis X1 as a central axis, a first transmission shaft S1 having the first axis X1 as a central axis, and a predetermined amount e from the first axis X1.
  • An eccentric rotating member 6 integrally having an eccentric shaft portion 6e whose center axis is the second axis line X2 that is eccentric, and one side portion of the first transmission member 5 are opposed to each other, and the eccentric shaft portion 6e is interposed via a bearing B3.
  • the first transmission mechanism T1 capable of transmitting torque while shifting between the second transmission members 5 and 8 and the second transmission mechanism T2 capable of transmitting torque while shifting between the second and third transmission members 8 and 9 are mainly used. This is a component.
  • the first transmission member 5 is accommodated in an annular recess 51 provided on the inner surface of the first side wall Ca of the differential case C.
  • the first transmission member 5 is connected to the first side wall Ca so as to rotate integrally, and a radial play with respect to the differential case C is imparted to the first transmission member 5 at the connecting portion. That is, the outer peripheral end inner surface of the annular recess 51 is spline-fitted SP3 so that the outer peripheral portion of the first transmission member 5 can move in the radial direction and can slide in the axial direction.
  • a connecting means between the first transmission member 5 and the first side wall Ca that is capable of torque transmission is capable of radial movement, and is capable of axial relative movement
  • a meshing means using dog teeth, clutch teeth or the like may be employed.
  • the circumferential direction that is, the rotational direction
  • a slight play is also set.
  • the first transmission shaft S1 which is the main shaft portion of the eccentric rotating member 6, has a cylindrical shape, and the inner peripheral surface of the first drive axle A1 is coaxially connected to the inner peripheral surface thereof (this embodiment). Then, spline fitting SP1) is performed. In addition, the play of radial direction may be provided in the spline fitting SP1 site
  • the third transmission member 9 has a first axis X1 as a central axis, and a cylindrical second transmission shaft S2 extending axially outward is coaxially connected to an inner peripheral end portion thereof ( In this embodiment, they are integrally formed).
  • the coupling body of the third transmission member 9 and the second transmission shaft S2 is provided with radial play with respect to the differential case C, that is, a radial clearance allowing the play is provided between the coupling body and the differential case C. Is set.
  • the play range is limited by the radial play range of the second transmission shaft S2 at the spline fitting SP2 portion between the second transmission shaft S2 and the second drive axle A2, which will be described next.
  • the inner peripheral surface of the second transmission shaft S2 is spline-fitted SP2 so that the outer periphery of the inner end portion of the second drive axle A2 can move in the radial direction.
  • the circumferential direction that is, the rotational direction
  • a slight play is also set.
  • the second transmission member 8 is rotatably supported around the second axis X2 by the eccentric shaft 6e integrated with the first transmission shaft S1 having the first axis X1 as the central axis, thereby providing the second
  • the transmission member 8 rotates to the first transmission shaft S1 while rotating about the second axis X2 with respect to the eccentric shaft portion 6e as the eccentric rotation member 6 (that is, the first transmission shaft S1) rotates about the first axis X1.
  • it can revolve around the first axis X1.
  • the second transmission member 8 has an annular first half 8a that is rotatably supported by the eccentric shaft portion 6e of the eccentric rotating member 6 via the bearing B3, and an interval between the first half 8a.
  • the first transmission mechanism T1 is provided between the first half 8a and the first transmission member 5
  • the second transmission mechanism T2 is provided between the second half 8b and the third transmission member 9. It is done.
  • the differential mechanism 3 rotates with the eccentric shaft portion 6e of the eccentric rotating member 6 and the total center of gravity of the second transmission member 8 opposite in phase across the first axis X1 and larger than the rotational radius of the total center of gravity.
  • a balance weight 7 having a radius is provided in the internal space of the second transmission member 8.
  • the balance weight 7 is attached so as to rotate integrally with the first transmission shaft S ⁇ b> 1 that is the main shaft portion of the eccentric rotation member 6.
  • the second transmission member 8 is formed with a plurality of openings 11 that can be used for attaching the balance weight 7 and ensuring the flow of the lubricating oil on the peripheral wall of the connecting member 8c.
  • first and second transmission mechanisms T1 and T2 will be described in order.
  • a corrugated first transmission groove 21 centered on the first axis X1 is formed on the inner surface of the first transmission member 5 facing the one side surface (that is, the first half 8a) of the second transmission member 8.
  • the first transmission groove 21 extends in the circumferential direction along a hypotrochoidal curve having a virtual circle centered on the first axis X1 as a base circle.
  • a corrugated annular second transmission groove 22 centering on the second axis X2 is formed on one side surface (first half 8a) of the second transmission member 8 facing the first transmission member 5.
  • the second transmission groove 22 extends in the circumferential direction along an epitrochoidal curve having a virtual circle centered on the second axis X2 as a base circle, and has a wave number smaller than the wave number of the first transmission groove 21. And intersects the first transmission groove 21 at a plurality of locations.
  • a plurality of first balls 23 as first rolling elements are interposed at intersections (that is, overlapping portions) of the first transmission groove 21 and the second transmission groove 22.
  • the inner surfaces of the first and second transmission grooves 21 and 22 can freely roll.
  • annular flat first holding member H1 capable of holding the plurality of first balls 23 rotatably is provided. Intervened.
  • a wavy annular third transmission groove 24 centered on the second axis X2 is formed on the other side surface of the second transmission member 8 (that is, the second half body 8b). In the example shown, it extends in the circumferential direction along a hypotrochoid curve having a virtual circle centered on the second axis X2 as a base circle.
  • a wavy annular fourth transmission groove 25 centering on the first axis X ⁇ b> 1 is formed on the surface of the third transmission member 9 facing the second transmission member 8.
  • the fourth transmission groove 25 extends in the circumferential direction along an epitrochoid curve having a virtual circle centered on the first axis X1 as a base circle, and has a wave number smaller than the wave number of the third transmission groove 24. And intersect with the third transmission groove 24 at a plurality of locations.
  • a plurality of second balls 26 as second rolling elements are interposed at intersections (overlapping portions) of the third transmission groove 24 and the fourth transmission groove 25, and each second ball 26 has a third and a second 4
  • the inner surfaces of the transmission grooves 24 and 25 can roll freely.
  • annular flat second holding member H2 capable of rotatably holding the plurality of second balls 26 is provided. Intervened.
  • the wave number of the first transmission groove 21 is Z1
  • the wave number of the second transmission groove 22 is Z2
  • the wave number of the third transmission groove 24 is Z3
  • the wave number of the fourth transmission groove 25 is Z4, the following equation is established.
  • the first to fourth transmission grooves 21, 22, 24, 25 are formed.
  • the eight-wave first transmission groove 21 and the six-wave second transmission groove 22 intersect at seven locations, and seven first balls 23 are formed at the seven intersection portions (overlapping portions).
  • the six-wave third transmission groove 24 and the four-wave fourth transmission groove 25 intersect at five locations, and five second balls 26 are interposed at the five intersection portions (overlapping portions). Be dressed.
  • first transmission groove 21, the second transmission groove 22, and the first ball 23 cooperate with each other so that torque can be transmitted while shifting between the first transmission member 5 and the second transmission member 8.
  • the third transmission groove 24, the fourth transmission groove 25, and the second ball 26 constitute the mechanism T1, and can transmit torque while shifting between the second transmission member 8 and the third transmission member 9 in cooperation with each other.
  • a second transmission mechanism T2 is configured.
  • the first transmission member 5 is formed separately from the first side wall Ca of the differential case C. Between the first transmission member 5 and the first side wall Ca, the first to third transmission members 5 are formed. , 8 and 9 are interposed as disc springs 50 as biasing means for biasing them toward the second side wall Cb.
  • the disc spring 50 is held in an appropriate elastic compression state between the first transmission member 5 and the first side wall Ca so as to generate a predetermined urging force in a set state.
  • the urging means is not limited to the disc spring as in the present embodiment, and various elastic members that can be interposed between the first transmission member 5 and the first side wall Ca and can exert the urging force. For example, rubber, wave washers, leaf springs or the like may be used.
  • a thrust washer 15 that can slide relative to at least one of the opposing surfaces is interposed.
  • the thrust washer 15 is fitted and held in an annular recess provided on the outer surface of the third transmission member 9 in the present embodiment, but the annular recess for fitting and holding the thrust washer 15 on the inner side surface of the second side wall Cb. May be provided.
  • the thrust washer 15 is interposed between the opposing surfaces of the second side wall Cb and the third transmission member 9, rotational friction (and hence wear) between the opposing surfaces can be reduced. The durability of the opposing surfaces is improved.
  • the thrust washer 15 can also function as a shim for adjusting the initial load of the biasing force of the disc spring 50.
  • a plurality of types of thrust washers 15 having different thicknesses are prepared in advance. The initial load of the biasing force of the disc spring 50 can be adjusted easily and accurately by selecting an arbitrary thrust washer 15 from among them.
  • the ring gear Cm is driven by the power from the engine, and the differential case C and therefore the first case.
  • the transmission member 5 is rotated about the first axis X 1
  • the eight-wave first transmission groove 21 of the first transmission member 5 passes through the six-wave second transmission groove 22 of the second transmission member 8 via the first ball 23. Therefore, the first transmission member 5 drives the second transmission member 8 with a speed increasing ratio of 8/6.
  • the six-wave third transmission groove 24 of the second transmission member 8 passes the four-wave fourth transmission groove 25 of the third transmission member 9 via the second ball 26. Therefore, the second transmission member 8 drives the third transmission member 9 with a speed increasing ratio of 6/4.
  • the amount of rotation and the amount of revolution of the second transmission member 8 change steplessly, and the eccentric rotation
  • the average value of the rotational speeds of the member 6 and the third transmission member 9 is equal to the rotational speed of the first transmission member 5.
  • the rotation of the first transmission member 5 is distributed to the eccentric rotation member 6 and the third transmission member 9, so that the rotational force transmitted from the ring gear Cm to the differential case C can be distributed to the left and right drive axles A1, A2. it can.
  • the rotational torque of the first transmission member 5 is transmitted to the second transmission member 8 via the first transmission groove 21, the plurality of first balls 23 and the second transmission groove 22, and to the second Since the rotational torque of the transmission member 8 is transmitted to the third transmission member 9 via the third transmission groove 24, the plurality of second balls 26, and the fourth transmission groove 25, respectively, the first transmission member 5 and the second transmission member are transmitted.
  • torque transmission is performed in a distributed manner at a plurality of locations where the first and second balls 23 and 26 are present. It is possible to increase the strength and reduce the weight of each transmission element such as the three transmission members 5, 8, 9 and the first and second balls 23, 26.
  • the first transmission member 5 is configured separately from the differential case C, and is connected to the differential case C so as to be axially slidable and non-rotatable (spline fitting SP3). Between the first transmission member 5 and the first side wall Ca of the differential case C facing the first transmission member 5, the first to third transmission members 5, 8, and 9 are biased toward the second side wall Cb. A disc spring 50 as a means is interposed. Then, the elastic urging force of the disc spring 50 acts on the first and second transmission mechanisms T1 and T2, and the transmission grooves 21 and 22 (24 and 25) and the ball 23 in each transmission mechanism T1 (T2). Since the backlash between (26) is automatically eliminated, the transmission efficiency of each transmission mechanism T1, T2 is increased.
  • the first transmission member 5, the first transmission shaft S 1, and the third transmission member 9 (second transmission shaft S 2) can be shifted at both speeds without requiring a particularly high machining accuracy for the support portion of the differential case C. Since the transmission efficiency of the mechanisms T1 and T2 is increased, the manufacturing cost of the differential device D can be reduced.
  • the disc spring 50 is interposed between the differential case C and the first transmission member 5 that are connected so as not to rotate relative to each other, the disc spring 50 is in friction with the differential case C and the first transmission member 5 even during transmission. The wear is avoided and high durability is ensured.
  • the disc spring 50 Due to the urging engagement between the first ball 23 and the first and second transmission grooves 21 and 22, the first transmission member 5 is not affected by the differential case C with respect to the second transmission member 8 and the first transmission mechanism T ⁇ b> 1.
  • automatic alignment that is, the rotation axes of the first and second transmission members 5 and 8 maintain a predetermined amount of eccentricity while maintaining a parallel opposing positional relationship
  • the plurality of first balls 23 and the first and second transmission grooves 21 and 22 can be properly engaged with each other, so that the transmission efficiency of the first transmission mechanism T1 can be further improved.
  • the second ball 26 and the third and fourth transmission grooves 24, 25 are biased by the disc spring 50. Due to the engagement, the third transmission member 9 is automatically aligned with the second transmission member 8 through the second transmission mechanism T2 without being affected by the differential case C (that is, the first transmission member 5 and the second transmission member 8).
  • the rotation axis lines can maintain a predetermined amount of eccentricity and maintain a parallel opposing positional relationship).
  • the plurality of second balls 26 and the third and fourth transmission grooves 24 and 25 can be properly engaged with each other, so that the transmission efficiency of the second speed change mechanism T2 can be further improved.
  • the second drive shaft S2 is spline-fitted with a second drive axle A2 that is rotatably supported on the second side wall Cb (that is, the second bearing B2) of the differential case C so as to be radially movable. Therefore, torque can be transmitted from the second transmission shaft S2 to the second drive axle A2 extending outside the differential case C, and the second transmission shaft S2 has a diameter relative to the second drive axle A2 at the spline fitting SP2 portion. Since there is play in the direction, it is possible to avoid the above-described self-aligning action of the third transmission member 9 from being obstructed by the second drive axle A2.
  • the differential device D is exemplified as the transmission device, and the power input from the power source to the differential case C (first transmission member 5) is transmitted via the first and second transmission mechanisms T1 and T2.
  • the first and second transmission shafts S1 and S2 are distributed while allowing differential rotation, the present invention can be applied to various transmission devices other than the differential device.
  • a casing corresponding to the differential case C of the above embodiment is a fixed transmission case, one of the first and second transmission shafts S1, S2 is an input shaft, and one of the other is an output shaft.
  • the differential device D of the embodiment can be diverted as a transmission (decelerator or speed increaser) that can change (decelerate or increase speed) the rotational torque input to the input shaft and transmit it to the output shaft.
  • a transmission (reduction gear or speed increaser) is the transmission device of the present invention.
  • the transmission may be a transmission for a vehicle or a transmission for various mechanical devices other than the vehicle.
  • the differential device D as a transmission device is accommodated in the mission case M of a motor vehicle for vehicles, the differential device D is not limited to the differential device for motor vehicles. It can also be implemented as a differential for various mechanical devices.
  • the differential device D as a transmission device is applied to the left / right wheel transmission system to distribute power while allowing differential rotation to the left and right drive axles A1, A2.
  • the differential device as a transmission device is applied to the front / rear wheel transmission system in the front / rear wheel drive vehicle to allow power to be driven while allowing differential rotation to the front and rear drive wheels. You may make it distribute.
  • the second transmission member 8 of the above embodiment has a structure in which the first and second halves 8a and 8b and the connecting member 8c are manufactured separately, and then the three members are integrally coupled.
  • the second transmission member 8 is constituted by an integrated body (for example, a sintered product) in which the first and second half bodies 8a and 8b and the connecting member 8c are integrally formed (not shown) (not shown). N) is also assumed.
  • the second transmission member 8 may be configured in a flat plate shape in the axial direction.
  • each transmission groove 21,22; 24,25 of 1st, 2nd transmission mechanism T1, T2 is made into the corrugated cyclic
  • these transmission grooves are embodiment.
  • it may be a wave-shaped wave groove along a cycloid curve.
  • the first and second ball-shaped first and second transmission grooves 21 and 22 and the third and fourth transmission grooves 24 and 25 of the first and second transmission mechanisms T1 and T2 are provided.
  • the rolling elements 23 and 26 may be in the form of a roller or a pin.
  • the first and second transmission grooves 21 and 22, and the third and fourth The transmission grooves 24 and 25 are formed in an inner surface shape so that a roller-like or pin-like rolling element can roll.
  • the first and second holding members H1 and H2 are used to smoothly roll the first and second balls 23 and 26.
  • the first and second holding members are used.
  • the first and second holding members H1 and H2 may be omitted.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un dispositif de transmission de puissance qui comprend : un premier élément de transmission de puissance ayant un axe central aligné sur un premier axe ; un élément rotatif ayant, relié à celui-ci, un premier arbre de transmission de puissance autour du premier axe, l'élément rotatif ayant également, reliée à celui-ci, une section d'arbre excentrée ayant un axe central aligné sur un second axe ; un deuxième élément de transmission de puissance porté de façon à pouvoir tourner par la section d'arbre excentrée ; un troisième élément de transmission de puissance relié à un second arbre de transmission de puissance qui tourne autour du premier axe, et faisant face au deuxième élément de transmission de puissance ; un premier mécanisme de changement de vitesses disposé entre les premier et deuxième éléments de transmission de puissance ; un second mécanisme de changement de vitesses disposé entre les deuxième et troisième éléments de transmission de puissance. Le premier élément de transmission de puissance (5) est relié à un boîtier (C) de façon à pourvoir se déplacer de façon axiale par rapport au boîtier (C) et à ne pas pourvoir tourner par rapport au boîtier (C). Un moyen de pression (50) est disposé entre le premier élément de transmission de puissance (5) et une surface latérale (Ca) du boîtier, le moyen de pression (50) pressant les premier à troisième éléments de transmission de puissance (5, 8, 9) vers l'autre surface latérale (Cb) du boîtier, le premier élément de transmission de puissance (5) ayant un jeu radial. En résultat, le rendement de transmission de puissance de chacun des mécanismes de changement de vitesses peut être augmenté sans nécessiter que des sections du premier élément de transmission de puissance, du troisième élément de transmission de puissance, etc.soient usinées avec une grande précision, les sections étant portées par le boîtier.
PCT/JP2017/008980 2016-03-08 2017-03-07 Dispositif de transmission de puissance WO2017154898A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016044464A JP2019094910A (ja) 2016-03-08 2016-03-08 伝動装置
JP2016-044464 2016-03-08

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WO2017154898A1 true WO2017154898A1 (fr) 2017-09-14

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH072661U (ja) * 1993-06-18 1995-01-13 株式会社椿本チエイン ボール式減速機の弾性体によるボール受け構造
JPH1163159A (ja) * 1997-08-15 1999-03-05 Hitachi Metals Ltd 差動装置
JP2005076861A (ja) * 2003-09-03 2005-03-24 Tochigi Fuji Ind Co Ltd デファレンシャル装置
JP2005168191A (ja) * 2003-12-03 2005-06-23 Tochigi Fuji Ind Co Ltd 電磁式アクチュエータ
US20080188341A1 (en) * 2007-02-06 2008-08-07 Gm Global Technology Operations, Inc. Cycloid limited slip differential and method
WO2016013315A1 (fr) * 2014-07-25 2016-01-28 武蔵精密工業株式会社 Dispositif differentiel

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH072661U (ja) * 1993-06-18 1995-01-13 株式会社椿本チエイン ボール式減速機の弾性体によるボール受け構造
JPH1163159A (ja) * 1997-08-15 1999-03-05 Hitachi Metals Ltd 差動装置
JP2005076861A (ja) * 2003-09-03 2005-03-24 Tochigi Fuji Ind Co Ltd デファレンシャル装置
JP2005168191A (ja) * 2003-12-03 2005-06-23 Tochigi Fuji Ind Co Ltd 電磁式アクチュエータ
US20080188341A1 (en) * 2007-02-06 2008-08-07 Gm Global Technology Operations, Inc. Cycloid limited slip differential and method
WO2016013315A1 (fr) * 2014-07-25 2016-01-28 武蔵精密工業株式会社 Dispositif differentiel

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