WO2017131141A1 - Dispositif de transmission - Google Patents

Dispositif de transmission Download PDF

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Publication number
WO2017131141A1
WO2017131141A1 PCT/JP2017/002898 JP2017002898W WO2017131141A1 WO 2017131141 A1 WO2017131141 A1 WO 2017131141A1 JP 2017002898 W JP2017002898 W JP 2017002898W WO 2017131141 A1 WO2017131141 A1 WO 2017131141A1
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WO
WIPO (PCT)
Prior art keywords
transmission
axis
transmission member
groove
grooves
Prior art date
Application number
PCT/JP2017/002898
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English (en)
Japanese (ja)
Inventor
翔平 坂田
Original Assignee
武蔵精密工業株式会社
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Publication date
Application filed by 武蔵精密工業株式会社 filed Critical 武蔵精密工業株式会社
Publication of WO2017131141A1 publication Critical patent/WO2017131141A1/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

Definitions

  • the present invention is centered on a transmission device, particularly a first transmission member arranged so that the first axis is a central axis, a main shaft portion rotatable 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 supported on the eccentric shaft portion so as to be rotatable about the second axis, and having one side surface facing the first transmission member;
  • a third transmission member disposed so as to have one axis as a central axis and facing the other side surface of the second transmission member;
  • a first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members;
  • the present invention relates to a transmission device including a second transmission mechanism capable of transmitting torque while shifting between the second and 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 at a plurality of intersecting portions of the first and second transmission grooves and perform the 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 second transmission gears that are interposed at a plurality of intersections of the transmission groove and the third and fourth transmission grooves, and that perform speed change transmission between the second and third transmission members while rolling the third and fourth transmission grooves. 2 rolling elements.
  • the second and third transmission grooves formed on both side surfaces of the plate-like second transmission member are the second and third transmission grooves as viewed from the projection plane orthogonal to the second axis. Are arranged so as to overlap each other. Therefore, the thickness of the second transmission member between the bottoms of the second and third transmission grooves inevitably decreases, which is disadvantageous in increasing the strength of the second transmission member.
  • each transmission groove in the first and second transmission mechanisms receives a load in the expansion direction from the corresponding rolling element, and stress concentration occurs at the bottom of the groove.
  • the thickness of the second transmission member between the two grooves is reduced due to the formation of the second and third transmission grooves, there is a problem that the portion is likely to be deformed and damaged due to the stress concentration. is there.
  • the conventional apparatus sets the thickness of the entire second transmission member to be thick in anticipation of the reduction in the thickness, which increases the weight of the second transmission member and thus the weight of the transmission device. Not only does this increase the axial width of the transmission, but also a factor.
  • the present invention has been made in view of such circumstances, and even if the thickness of the plate-like second transmission member is not set to be particularly thick, the second transmission member is formed on both side surfaces without causing insufficient strength. It is an object of the present invention to provide a transmission device that can form second and third transmission grooves and can effectively suppress an increase in axial width.
  • the present invention provides a first transmission member arranged so that the first axis is a central axis, a main shaft portion rotatable around the first axis, and a first shaft eccentric from the first axis.
  • An eccentric rotating member in which an eccentric shaft portion having two axes as a central axis is integrally connected, and a plate that is supported by the eccentric shaft portion so as to be rotatable about a second axis and has one side faced to the first transmission member.
  • a second transmission member having a shape, a third transmission member disposed so as to have the first axis as a central axis, and facing the other side of the second transmission member, and a speed change between the first and second transmission members
  • the first transmission mechanism includes a first transmission member of the first transmission member.
  • a second annular transmission having a wave shape different from that of the first transmission groove and having a wave shape centered on the second axis and located on the surface of the second transmission member facing the first transmission member, the first transmission groove having an annular shape.
  • a plurality of first gears that are interposed in a plurality of intersecting portions of the groove and the first and second transmission grooves, and perform transmission transmission between the first and second transmission members while rolling the first and second transmission grooves.
  • the second transmission mechanism is located on a surface of the second transmission member facing the third transmission member and has a wave-shaped annular third transmission groove centered on the second axis;
  • 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 third and fourth transmissions Shifting between the second and third transmission members while rolling through the third and fourth transmission grooves, which are interposed at a plurality of intersections of the grooves.
  • a plurality of second rolling elements wherein the second and third transmission grooves do not overlap each other when the transmission grooves are viewed on a projection plane orthogonal to the second axis,
  • the first feature is that one of the transmission grooves is disposed so as to surround the other transmission groove.
  • the present invention has a second feature that the one transmission groove has a higher wave number than the other transmission groove surrounded by the one transmission groove.
  • the present invention further includes a casing that houses the first to third transmission members and supports the first transmission member so as not to be relatively rotatable.
  • One of the input shaft and the output shaft arranged side by side is connected to the main shaft portion, and the other is connected to the third transmission member.
  • the second and third transmission grooves formed on both side surfaces of the second transmission member do not overlap each other when the transmission grooves are viewed on the projection plane orthogonal to the second axis.
  • the one transmission groove is disposed so as to surround the other transmission groove, the thickness reduction of the second transmission member between the bottoms of the second and third transmission grooves can be minimized.
  • the second transmission member can accurately form the second and third transmission grooves on both side surfaces without causing insufficient strength. Therefore, it is possible to contribute to the weight reduction of the second transmission member and thus to the weight reduction of the transmission device, and further, it is possible to contribute to the flat size reduction by suppressing the increase in the axial width of the transmission device.
  • the one transmission groove has a higher wave number than the other transmission groove surrounded by the one transmission groove, so that the two transmission grooves do not overlap each other when viewed on the projection plane.
  • the arrangement in which one of the transmission grooves surrounds the other transmission groove can be easily and easily performed.
  • the casing includes the casing that houses the first to third transmission members and supports the first transmission member so that the first transmission member cannot be relatively rotated, and the input shaft and the output shaft that are aligned on the first axis. Since either one of them is connected to the main shaft portion of the eccentric rotating member and the other one is connected to the third transmission member, the transmission device is compact in the axial direction between the input shaft and the output shaft arranged on the same axis. It can be configured as a speed reducer or speed increaser that can be deployed in the vehicle.
  • FIG. 1 is a longitudinal sectional view of an essential part showing an example of a power unit for a motorcycle including a transmission (reduction gear) according to a first embodiment of the present invention.
  • FIG. 2 is an enlarged cross-sectional view of an essential part of the first embodiment (enlarged view taken along the arrow 2 in FIG. 1).
  • (First embodiment) 3 is a cross-sectional view taken along the line 3-3 in FIG.
  • (First embodiment) 4 is a cross-sectional view taken along arrow 4-4 of FIG.
  • FIG. 5 is an overall longitudinal sectional view of a transmission device (differential device) according to the second embodiment. (Second Embodiment)
  • a power unit P of a motorcycle includes an electric motor M as a drive source and a speed reducer R as a transmission device that decelerates the driving force and transmits it to the wheels (rear wheels W).
  • the power unit P is mounted on the rear end of a swing arm (not shown) that is pivotally supported on the motorcycle body so as to swing up and down so that it can swing together with the swing arm.
  • the speed reducer R decelerates the rotation of the first transmission shaft S1 that also serves as the output shaft of the electric motor M via the first and second transmission mechanisms T1 and T2 and transmits the reduced speed to the second transmission shaft S2.
  • the rear wheel W is coupled to the second transmission shaft S2 so as to rotate integrally.
  • the first and second transmission shafts S1 and S2 rotate around the first axis X1 through the pair of first and second bearings B1, B1 '; B2, B2' in the unit case Pc of the power unit P, respectively. Supported as possible.
  • the electric motor M includes a motor case 1, a stator 2 that is fixed to the inner surface of the outer peripheral wall of the case 1, and a rotor 3 that is located inside the stator 2 and is fixed to the first transmission shaft S1.
  • the motor case 1 is divided into two parts, for example, a bottomed cylindrical case body and a lid that closes its open end.
  • the speed reducer R cooperates with the motor case 1 to form a hollow casing C that constitutes a unit case Pc of the power unit P, and first, second, and second housings that are accommodated in the casing C in an axial state in series. 3 between the transmission members 5, 8, 9, the eccentric rotation member 6 housed in the casing C and surrounded by the annular first and second transmission members 5, 8, and the first and second transmission members 5, 8.
  • the first transmission mechanism T1 capable of transmitting torque while shifting and the second transmission mechanism T2 capable of transmitting torque while shifting between the second and third transmission members 8 and 9 are main components.
  • the electric motor M is coupled to the speed reducer R on the same axis (first axis X1), and the casing C and the motor case 1 of the speed reducer R are combined and integrated.
  • the adjacent end portions of each other are fastened by a plurality of bolts 10.
  • one side wall 1a of the motor case 1 separates the internal spaces of the speed reducer R and the electric motor M, and also functions as one side wall Ca of the casing C of the speed reducer R.
  • the first transmission shaft S1 is rotatably supported on one side wall Ca of the casing C and the other side wall 1b of the motor case 1 via first bearings B1 and B1 ′ (for example, ball bearings).
  • the first bearing B1 near the speed reducer R has its inner race adjacent to the rotor 3 of the electric motor M with the collar 40 in between, and the first bearing B1, the collar 40 and the rotor 3 are connected to the first transmission shaft. It is clamped and fastened between the intermediate step portion of S1 and the nut 4 screwed to the outer end portion of the shaft S1.
  • An annular seal member 11 is interposed between one side wall Ca of the casing C and the outer periphery of the collar 40.
  • An annular seal member 41 is also interposed between the inner periphery of the collar 40 and the first transmission shaft S1.
  • the first transmission member 5 is disposed adjacent to the inner surface of the one side wall Ca of the casing C with the first axis X1 as the central axis, and the outer peripheral portion of the first transmission member 5 is splined on the inner peripheral surface of the outer peripheral wall of the casing C. It is fitted SP1. Further, a gap adjusting shim 12 is interposed between the opposing surfaces of the inner surface Ca of the casing C and the outer surface of the first transmission member 5.
  • the eccentric rotating member 6 integrally includes a main shaft portion 6j having the first axis line X1 as a central axis, and an eccentric shaft portion 6e having a second axis line X2 eccentric from the first axis line X1 by a predetermined eccentric amount e as a central axis line.
  • the first transmission shaft S1 is coaxially connected to the main shaft portion 6j (coupled integrally in the present embodiment).
  • the eccentric shaft portion 6e supports the inner peripheral portion of the annular second transmission member 8 via a third bearing B3 (for example, a ball bearing) so as to be rotatable around the second axis X2.
  • One side surface of the second transmission member 8 faces the inner side surface of the first transmission member 5.
  • the eccentric rotating member 6 and the first transmission shaft S1 may be formed separately and connected so as to rotate together (for example, spline fitting).
  • the third transmission member 9 is coaxially connected to the second transmission shaft S2 that rotates about the first axis X1.
  • the inner side surface of the third transmission member 9 faces the other side surface of the second transmission member 8.
  • the second transmission member 8 rotates about the second axis X2 with respect to the eccentric shaft portion 6e as the eccentric rotation member 6 (first transmission shaft S1) rotates about the first axis X1, while rotating about the second axis X2. Revolve around the first axis X1 with respect to one transmission shaft S1.
  • the position of the total center of gravity of the eccentric shaft portion 6e of the eccentric rotating member 6 and the second transmission member 8 is unevenly distributed at a position spaced in the direction from the first axis X1 to the second axis X2. Therefore, when the second transmission member 8 revolves while rotating as described above, the centrifugal force of the eccentric rotation system acts in a specific direction (on the offset side of the second axis X2) with respect to the first axis X1.
  • the rotation of the eccentric rotation system is in an unbalanced state, but in order to eliminate or reduce the unbalanced state, a rotation radius that is opposite in phase to the total center of gravity and larger than the rotation radius of the total center of gravity is used.
  • the balance weight 7 is integrally connected to the main shaft portion 6j of the eccentric rotating member 6.
  • the second transmission shaft S2 includes a long shaft body 13 that also serves as an axle, and a cylindrical shaft 14 that is fitted and fixed (for example, welded) to the outer periphery of the inner end portion of the shaft body 13.
  • the outer end portion 13o of the shaft body 13 is a wheel mounting portion having a spline groove on the outer periphery, and a wheel hub Wh of the rear wheel W is detachably coupled to the wheel body Wh by fastening means such as a nut n and the like so as not to be relatively rotatable.
  • the second transmission shaft S2 has a first axis line through a pair of second bearings B2 and B2 '(for example, a ball bearing and a roller bearing) on the inner wall of the casing C in the intermediate portion of the shaft body 13 and the cylindrical shaft 14. It is supported rotatably around X1.
  • An annular seal member 15 is interposed between the inner periphery of the casing C and the outer periphery of the shaft body 13 between the second bearings B2 and B2 ′.
  • the outer periphery of the inner end portion of the cylindrical shaft 14 is spline-fitted SP2 to the inner peripheral surface of a connecting cylindrical portion 9a that protrudes in a cylindrical shape on the outer surface of the third transmission member 9.
  • a wavy annular first transmission groove 21 centering on the first axis X ⁇ b> 1 is formed, and the first transmission groove 21 is illustrated in the illustrated example. Then, it extends in the circumferential direction along a hypotrochoid 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 of the second transmission member 8 facing the first transmission member 5.
  • the second transmission groove 22 extends in the circumferential direction along an epitrochoid curve having a virtual circle centered on the second axis X2 as a base circle, and is different from the wave number Z1 of the first transmission groove 21. Crosses the first transmission groove 21 at a plurality of locations with a wave number Z2 (for example, small).
  • 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, and each of the first balls 23 is a first one.
  • the inner surface of the 2nd transmission grooves 21 and 22 can roll freely.
  • annular flat first holding member H1 capable of rotatably holding the plurality of first balls 23 is interposed.
  • a wavy annular third transmission groove 24 centering on the second axis X2 is formed, and the third transmission groove 24 is In the illustrated example, it extends in the circumferential direction along a hypotrochoidal 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 inner 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 epitrochoidal curve having a virtual circle centered on the first axis X1 as a base circle, and is different from the wave number Z3 of the third transmission groove 24. It intersects with the third transmission groove 24 at a plurality of locations with a wave number Z4 (for example, less).
  • a plurality of second balls 26 as second rolling elements are interposed at the intersecting portion (overlapping portion) of the third transmission groove 24 and the fourth transmission groove 25, and each second ball 26 has a third and a third one. 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 interposed.
  • the second and third transmission grooves 22 and 24 that are formed on both side surfaces of the second transmission member 8 and have a corrugated annular shape are overlapped with each other when the grooves 22 and 24 are viewed on the projection plane orthogonal to the second axis X2.
  • the first transmission groove (for example, the second transmission groove 22) is arranged so as to surround the other transmission groove (for example, the third transmission groove 24).
  • the one transmission groove (for example, the second transmission groove 22) is formed to have a higher wave number than the other transmission groove (for example, the third transmission groove 24) that surrounds the one transmission groove.
  • first transmission groove 21, the second transmission groove 22, and the first ball 23 constitute a first transmission mechanism T1 that cooperates with each other to perform a first-stage speed change (deceleration), and a third transmission.
  • the groove 24, the fourth transmission groove 25, and the second ball 26 constitute a second transmission mechanism T2 that cooperates with each other to perform a second-stage speed change (deceleration).
  • an on-vehicle electronic control unit controls energization to the electric motor M (and hence rotation of the motor M) based on the driver's accelerator operation.
  • the eccentric shaft portion 6e of the eccentric rotation member 6 integral with the first transmission shaft S1 revolves around the first axis X1, and accordingly, the eccentric shaft portion 6e.
  • the upper second transmission member 8 also revolves around the first axis X1. According to this revolution, both the first transmission groove 21 of the first transmission member 5 and the second transmission groove 22 of the second transmission member 8, both of which are spline-fitted into the casing C and are restricted in rotation, are connected to each other.
  • the first balls 23 engaged at the intersections of the grooves 21 and 22 roll on the grooves 21 and 22, so that the second transmission member 8 is rotated about the second axis X2 on the eccentric shaft portion 6 e. Rotate.
  • the third transmission member 9 is driven to rotate about the first axis X1.
  • the rotation driving force is transmitted to the second transmission shaft S2 that is spline-fitted SP2 to the third transmission member 9.
  • the rotation of the first transmission shaft S1 driven by the electric motor M is transmitted to the second transmission shaft S2 by decelerating to the second transmission shaft S2 through the first and second transmission mechanisms T1 and T2 in sequence, and thus the second transmission shaft S2.
  • the wheel W can be driven to decelerate by the electric motor M.
  • 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
  • torque transmission between the first transmission member 5 and the second transmission member 8 is performed by the first transmission groove 21, the plurality of first balls 23, and the second transmission groove. 22, and torque transmission between the second transmission member 8 and the third transmission member 9 is performed via the third transmission groove 24, the plurality of second balls 26, and the fourth transmission groove 25.
  • torque transmission is carried out to a plurality of places where the 1st and 2nd balls 23 and 26 exist. Since it is performed in a distributed manner, the strength and weight of each transmission element such as the first to third transmission members 5, 8, 9 and the first and second balls 23, 26 can be increased.
  • the first to third transmission members 5, 8, and 9 are each formed in a plate shape and arranged in the axial direction so that the transmission can be easily flattened in the axial direction (reduction gear R). Can be provided.
  • the corrugated annular second and third transmission grooves 22 and 24 formed on both side surfaces of the second transmission member 8 are projection planes in which both grooves 22 and 24 are orthogonal to the second axis X2.
  • the second and third transmission grooves are arranged so that one of the transmission grooves (for example, the second transmission groove 22) surrounds the other transmission groove (for example, the third transmission groove 24) without overlapping each other.
  • the thickness reduction of the second transmission member 8 between the groove bottoms 22 and 24 is minimized.
  • the second transmission member 8 has the second and third transmission grooves 22 and 24 on both side surfaces without causing insufficient strength. Therefore, it is possible to reduce the weight of the second transmission member 8, thereby reducing the transmission device (reduction gear R), and effectively increasing the axial width of the transmission device (reduction gear R).
  • the flatness and miniaturization of the device can be achieved.
  • the one transmission groove (for example, the second transmission groove 22) has a higher wave number than the other transmission groove (for example, the third transmission groove 24) that surrounds the one transmission groove.
  • the two transmission grooves 22 and 24 do not overlap each other when viewed on the projection plane, and one of the transmission grooves (for example, the second transmission groove 22) is the other transmission groove (for example, the third transmission groove 24). ) Is increased, and such non-overlapping transmission grooves 22 and 24 can be easily and easily arranged.
  • the rolling ball type reduction gear R is exemplified as the transmission device, but the transmission device of the second embodiment is exemplified as the rolling ball type differential device D.
  • the differential device D is housed in a transmission case 100 together with a transmission (not shown), and a pair of drive axles arranged on the first axis X1 to rotate the ring gear Cg linked to a power source such as an engine via the transmission. Distribution is performed while allowing differential rotation between the drive axles S1 and S2 with respect to S1 and S2 (that is, the first and second transmission shafts).
  • the drive axles S1, S2 and the transmission case 100 are sealed with a seal member 101.
  • the differential device D includes a casing C that is supported by the mission case 100 so as to be rotatable about the first axis X1, and a differential mechanism Dm described later that is housed in the casing C.
  • the casing C functions as a differential case, and a cylindrical casing main body Cm having a ring gear Cg made of a helical gear on the outer peripheral portion and an outer peripheral end portion integrally joined to both axial end portions of the casing main body Cm. And a pair of left and right first and second side walls Ca and Cb.
  • Both side walls Ca and Cb integrally have cylindrical boss-like first and second bearings B1 and B2 extending outward in the axial direction at the respective inner peripheral ends.
  • the outer peripheral portions of the first and second bearings B1 and B2 are supported by the transmission case 100 so as to be rotatable around the first axis X1 via an outer bearing 102 (for example, a ball bearing).
  • the first and second drive axles S1 and S2 are rotatably fitted and supported on the inner peripheral surfaces (that is, bearing surfaces) of the first and second bearings B1 and B2, respectively.
  • a spiral groove 121 is provided on the inner peripheral surfaces of the first and second bearings B1 and B2 for pressure-feeding and guiding the lubricating oil in the transmission case 100 into the casing C with relative rotation with the drive axles S1 and S2. , 122 are recessed.
  • the differential mechanism Dm includes first, second, and third transmission members 5, 8, and 9 that are accommodated in the axial direction in the casing C, and an annular first and second that are accommodated in the casing C.
  • the second transmission mechanism T2 capable of transmitting torque while shifting between the nine gears is a main component.
  • the first transmission member 5 is disposed adjacent to the inner surface of the one side wall Ca of the casing C with the first axis X1 as the central axis, and the outer periphery of the first transmission member 5 is an annular recess of the inner surface of the one side wall Ca of the casing C. Spline fitting SP1 is performed on the inner peripheral surface. Further, a gap adjusting shim 12 is interposed between opposing surfaces of the inner surface Ca of the casing C and the outer surface of the first transmission member 5.
  • the eccentric rotating member 6 integrally includes a main shaft portion 6j having the first axis line X1 as a central axis, and an eccentric shaft portion 6e having a second axis line X2 eccentric from the first axis line X1 by a predetermined eccentric amount e as a central axis line.
  • the inner end portion of the first drive axle S1 as the first transmission shaft is coaxially connected to the main shaft portion 6j (in the present embodiment, spline fitting 111).
  • a second transmission member 8 is supported on the eccentric shaft portion 6e via a third bearing B3 (for example, a ball bearing) so as to be rotatable about the second axis X2, and one side surface of the second transmission member 8 is 1 It faces the inner surface of the transmission member 5.
  • a third bearing B3 for example, a ball bearing
  • the third transmission member 9 is coaxially connected to the second drive axle S2 that rotates about the first axis X1 via the cylindrical shaft 114, and rotates about the first axis X1 together with the second drive axle S2. Further, the inner side surface of the third transmission member 9 faces the other side surface of the second transmission member 8.
  • the cylindrical shaft 114 is formed in a bottomed cylindrical shape whose inner end is closed, and the closed wall 114b faces the outer surface of the third transmission member 9. Further, the outer periphery of the inner end portion of the cylindrical shaft 114 is spline-fitted SP2 to the inner peripheral surface of the connecting cylindrical portion 9a projecting from the outer surface of the third transmission member 9. Further, the inner peripheral surface of the cylindrical portion 114a of the cylindrical shaft 114 is coaxially connected to the inner end portion of the second drive axle S2 (in this embodiment, spline fitting 112).
  • the second transmission member 8 has the second axis X2 with respect to the eccentric shaft portion 6e as the eccentric rotation member 6 (first drive axle S1) rotates about the first axis X1. Revolving around the first axis X1 relative to the first drive axle S1 while rotating around.
  • the structure of the first and second speed change mechanisms T1 and T2 of the second embodiment is basically the same as the structure of the first and second speed change mechanisms T1 and T2 of the first embodiment.
  • the description of the mechanism is omitted only by attaching the same reference numerals.
  • the first transmission member 5 when the first and second speed change mechanisms T1 and T2 rotate the casing C with the eccentric rotating member 6 (first driving axle S1) fixed, the first transmission member 5 is used.
  • the third transmission member 9 is configured to be driven with a double speed increasing ratio.
  • 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 eight-wave first transmission groove 21 and the six-wave second transmission groove 22 intersect at seven locations, and seven first balls 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 formed at the five intersections (overlapping portions). Is installed.
  • the ring gear Cg is driven by the power from the engine, and the casing C (and therefore the first shaft).
  • the first transmission member 5 is rotated about the first axis X1
  • the first transmission groove 21 of the first transmission member 5 and the second transmission groove 22 of the second transmission member 8 are replaced by 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 third transmission member 9 is driven with the speed increasing ratio.
  • 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 Cg to the differential case C can be distributed to the left and right drive axles S1, S2. it can.
  • the first to third transmission members 5, 8, 9 are each formed in a plate shape and arranged in the axial direction so that the differential device D that can be easily flattened and reduced in the axial direction can be obtained. It can be provided.
  • the transmission device the transmission gear of the vehicle (rear wheel W) implemented on the vehicle speed reducer R for driving the electric motor M to reduce the speed is illustrated, but the transmission device of the present invention is exemplified. May be used for driving wheels of vehicles other than motorcycles, for example, four-wheeled vehicles, or may be used as a speed reducer for various mechanical devices other than vehicles.
  • the drive source may be an electric motor, an engine or a hydraulic motor, and the drive source case and the transmission casing may be combined and integrated as in the present embodiment. However, it may be configured separately.
  • the drive source (electric motor) is not directly connected to the transmission device (reduction gear R) and is spaced forward from the rear wheel.
  • the drive source may be linked to the transmission device (reduction gear R) via an endless transmission mechanism such as a chain transmission mechanism, a drive shaft mechanism, or the like.
  • the reduction gear R using the first transmission shaft S1 as the input shaft and the second transmission shaft S2 as the output shaft is shown as the transmission device.
  • the transmission device may be the first transmission shaft S1.
  • the speed increasing device may be used.
  • the differential device D as a transmission device is accommodated in the transmission case 1 of the automobile.
  • the differential device D is not limited to the differential apparatus for an automobile, It can be implemented as a differential for a mechanical device.
  • the differential device D is applied to the left / right wheel transmission system to distribute power while allowing differential rotation to the left and right drive axles S1, S2.
  • 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. .
  • 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.
  • first and second holding members H1 and H2 that rotatably hold the first and second balls 23 and 26 are shown. If the first and second balls 23 and 26 can smoothly roll without H2, the first and second holding members H1 and H2 may be omitted.
  • the first transmission member 5 is formed separately from the casing C, and is connected to the casing C so as not to be relatively rotatable (for example, spline fitting). May be formed integrally with the casing C (for example, one side wall Ca).

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

Abstract

L'invention concerne un dispositif de transmission comprenant un premier élément de transmission dont la ligne axiale centrale est une première ligne axiale, un élément de rotation excentrique dans lequel une partie d'arbre principal pouvant tourner autour de la première ligne axiale et une partie d'arbre excentrique dont la ligne axiale centrale est une seconde ligne axiale sont reliés en faisant corps, un deuxième élément de transmission de forme plate porté en rotation sur la partie d'arbre excentrique, un troisième élément de transmission dont la ligne axiale centrale est la première ligne axiale et qui fait face au deuxième élément de transmission, un premier mécanisme de changement de vitesse entre les premier et deuxième éléments de transmission, et un second mécanisme de changement de vitesse entre les deuxième et troisième éléments de transmission, des deuxième et troisième rainures (22, 24) de transmission disposées des deux côtés du deuxième élément (8) de transmission ne se chevauchant pas l'une l'autre, vu dans un plan projeté perpendiculaire à la seconde ligne axiale (X2), et l'une de ces rainures est disposée de façon à entourer l'autre. Il est ainsi possible de réduire au minimum la réduction en épaisseur du deuxième élément de transmission entre la seconde rainure de transmission du premier mécanisme de changement de vitesse et le fond de la troisième rainure de transmission du second mécanisme de changement de vitesse, pour éviter une résistance insuffisante du deuxième élément de transmission sans avoir à définir l'épaisseur du deuxième élément de transmission pour qu'elle soit épaisse, et réduire la dimension axiale du dispositif.
PCT/JP2017/002898 2016-01-29 2017-01-27 Dispositif de transmission WO2017131141A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-015809 2016-01-29
JP2016015809A JP2017133660A (ja) 2016-01-29 2016-01-29 伝動装置

Publications (1)

Publication Number Publication Date
WO2017131141A1 true WO2017131141A1 (fr) 2017-08-03

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JP (1) JP2017133660A (fr)
WO (1) WO2017131141A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112020004757T5 (de) * 2019-10-03 2022-06-15 Sumitomo Electric Sintered Alloy, Ltd. Sinterglied und elektromagnetische Kuppelung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010014214A (ja) * 2008-07-04 2010-01-21 Kamo Seiko Kk 転動ボール式差動変速装置
JP4814351B2 (ja) * 2009-02-23 2011-11-16 加茂精工株式会社 転動ボール式二段低変速装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010014214A (ja) * 2008-07-04 2010-01-21 Kamo Seiko Kk 転動ボール式差動変速装置
JP4814351B2 (ja) * 2009-02-23 2011-11-16 加茂精工株式会社 転動ボール式二段低変速装置

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