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WO2018179788A1 - Dispositif de transmission et dispositif différentiel planétaires - Google Patents

Dispositif de transmission et dispositif différentiel planétaires Download PDF

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Publication number
WO2018179788A1
WO2018179788A1 PCT/JP2018/002817 JP2018002817W WO2018179788A1 WO 2018179788 A1 WO2018179788 A1 WO 2018179788A1 JP 2018002817 W JP2018002817 W JP 2018002817W WO 2018179788 A1 WO2018179788 A1 WO 2018179788A1
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WO
WIPO (PCT)
Prior art keywords
transmission
plate
planetary
shaft
planetary plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/002817
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English (en)
Japanese (ja)
Inventor
和樹 渡
慎弥 松岡
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Musashi Seimitsu Industry Co Ltd
Original Assignee
Musashi Seimitsu Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Musashi Seimitsu Industry Co Ltd filed Critical Musashi Seimitsu Industry Co Ltd
Publication of WO2018179788A1 publication Critical patent/WO2018179788A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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 planetary transmission device and a differential device to which the planetary transmission device is applied.
  • first and second transmission shafts arranged so as to be relatively rotatable on a main axis line, and integrally connected to the first transmission shaft.
  • An eccentric shaft disposed on an eccentric axis that is eccentric with respect to the main axis, a first transmission plate disposed on the main axis, and a planetary plate that is rotatably supported by the eccentric shaft and faces the first transmission plate
  • a second transmission plate connected to the second transmission shaft so as to face the planetary plate on the opposite side of the first transmission plate, and a first transmission mechanism interposed between the first transmission plate and the planetary plate And a second speed change mechanism interposed between the planetary plate and the second transmission plate.
  • the first speed change mechanism is formed on a side surface of the first transmission plate facing the planetary plate and has an annular waveform on the main axis.
  • the first transmission groove is centered on the surface of the planetary plate and is formed on one side of the planetary plate facing the first transmission plate, and has a wave number different from that of the first transmission groove.
  • the second transmission mechanism is formed on the other side of the planetary plate, is formed on the side of the second transmission plate facing the planetary plate, and a third transmission groove centered on the eccentric axis in an annular waveform.
  • the first and fourth transmission grooves to be arranged on the main axis and the coaxial accuracy and the eccentric axis are arranged due to manufacturing errors and assembly errors of the first and second transmission mechanisms.
  • a large frictional resistance is generated in each transmission mechanism, causing transmission.
  • the efficiency will be reduced. Therefore, high precision is required for manufacturing and assembling the first and second transmission mechanisms in order to avoid such inconvenience, but this requirement causes an increase in manufacturing cost.
  • the present invention has been made in view of such circumstances, and even if there is some deviation as described above due to manufacturing errors and assembly errors of the first and second transmission mechanisms, the deviation is absorbed and smooth operation is possible. It is an object of the present invention to provide a planetary transmission device that can suppress an increase in manufacturing cost and a differential device to which the planetary transmission device is applied.
  • first and second transmission shafts arranged so as to be relatively rotatable on a main axis, and integrally connected to the first transmission shaft,
  • An eccentric shaft disposed on an eccentric eccentric axis, a first transmission plate disposed on the main axis, a planetary plate supported rotatably on the eccentric shaft and opposed to the first transmission plate, and the planet
  • a second transmission plate facing the plate on the opposite side to the first transmission plate and coupled to the second transmission shaft
  • a first transmission mechanism interposed between the first transmission plate and the planetary plate
  • a second transmission mechanism interposed between the planetary plate and the second transmission plate, and the first transmission mechanism is formed on a side surface of the first transmission plate facing the planetary plate, A first transmission groove centered on the main axis in an annular waveform, and a side surface of the planetary plate facing the first transmission plate;
  • a second transmission mechanism formed on the other side of the planetary plate and centered on the eccentric axis in an annular waveform, and a second transmission mechanism.
  • a fourth transmission groove formed on a side surface of the second transmission plate facing the planetary plate and having a wave number different from that of the third transmission groove and centered on the main axis, and the third and fourth transmission grooves.
  • a planetary transmission device including a plurality of second rolling transmission members that are rotatably inserted in the transmission grooves at an overlapping portion of the transmission grooves, wherein the planetary plates are arranged in the axial direction; Divided into two planetary plate halves and the first and second planetary plate halves Only the planetary plate half is rotatably supported on the eccentric shaft, and the first and second planetary plate halves are elastic members that allow relative displacement in the radial direction of the first and second planetary plate halves.
  • the first feature is that they are connected to each other.
  • the first and second transmission shafts respectively correspond to first and second output shafts 19 and 20 in the embodiments of the present invention described later, and the first and second transmission plates are the input plate 12 and the output.
  • the first and second rolling transmission members respectively correspond to the plates 15 and correspond to the first and second transmission balls 37 and 38, respectively.
  • the first and second transmission shafts are arranged so as to be rotatable relative to each other on the main axis, and are arranged on an eccentric axis that is integrally connected to the first transmission shaft and eccentric with respect to the main axis.
  • An eccentric shaft a first transmission plate disposed on the main axis, a planetary plate supported by the eccentric shaft so as to be able to rotate, and facing the first transmission plate, and the planetary plate with the first transmission plate A second transmission plate facing the opposite side of the plate and coupled to the second transmission shaft; a first transmission mechanism interposed between the first transmission plate and the planetary plate; the planetary plate and the A second transmission mechanism interposed between the second transmission plates, wherein the first transmission mechanism is formed on a side surface of the first transmission plate facing the planetary plate and has an annular waveform on the main axis.
  • a first transmission groove located at the center and one side surface of the planetary plate facing the first transmission plate;
  • a second transmission groove centered on the eccentric axis with an annular waveform having a wave number different from that of the first transmission groove, and a plurality of second transmission grooves interposed between the first and second transmission grooves so as to roll freely.
  • the second transmission mechanism is formed on the other side surface of the planetary plate, and has a third transmission groove centered on the eccentric axis in an annular waveform, and the second transmission plate, A fourth transmission groove formed on a side surface opposite to the planetary plate and centered on the main axis in an annular waveform having a wave number different from that of the third transmission groove;
  • a planetary transmission device including a plurality of second rolling transmission members interposed rotatably in a transmission groove, wherein the planetary plate is divided into first and second planetary plate halves arranged in the axial direction. And at least the first planetary plate half is rotatably supported on the eccentric shaft. It said first and second planetary plate halves, the second feature to be connected to each other via the elastic member to allow rotation direction of the relative displacement of the first and second planetary plate halves.
  • the elastic member in addition to the first or second feature, is provided with a preload that urges the first and second planetary plate halves in a direction away from each other in the axial direction. This is the third feature.
  • an accommodation space is provided between the first and second planetary plate halves, and the accommodation space includes the first transmission shaft.
  • a fourth feature is that a counterweight that is attached and suppresses rotational unbalance of an eccentric rotating body including the eccentric shaft and the planetary plate is arranged.
  • a differential device to which any one of the first to fourth features is applied, wherein the first and second cylinder shafts that are rotatably supported by the transmission case on the main axis are respectively centered.
  • a differential case that has first and second case side walls formed thereon, and receives rotational power from the outside; and an input plate as the first transmission plate that is coupled to the first case side wall so as to be integrally rotatable;
  • First and second output shafts as the first and second transmission shafts disposed on the main axis line in the differential case, and rotational power received in the differential case and transmitted from the differential case to the input plate.
  • a differential mechanism that distributes to the first and second output shafts, and the differential mechanism is supported by the eccentric shaft that is integrally connected to the first output shaft, and rotatably supported by the eccentric shaft.
  • the planetary plate facing the input plate
  • An output plate as the second transmission plate, opposed to the planet plate on the opposite side of the input plate, and supported in the axial direction on the second case side wall while being connected to the second output shaft;
  • the first speed change mechanism interposed between the input plate and the planetary plate; and the second speed change mechanism interposed between the planetary plate and the output plate.
  • a fifth drive shaft is rotatably connected to the first tube shaft, and a second drive shaft rotatably connected to the second tube shaft is connected to the second output shaft. It is characterized by.
  • the coaxial accuracy of the first transmission groove and the fourth transmission groove to be arranged on the main axis, and the eccentric axis If the coaxial accuracy of the second transmission groove and the third transmission groove that are to be arranged in the first and second transmission grooves is somewhat out of order, the first and second planetary plate halves are elastically deformed to cause the first and second planetary plate halves to be elastically deformed. The second planetary plate half is relatively displaced in the radial direction to absorb the deviation. For this reason, the smooth operation of the first and second transmission mechanisms can be ensured without being interfered by the deviation. As a result, the manufacturing accuracy and assembly accuracy of each transmission mechanism are eased, and an increase in manufacturing cost can be suppressed.
  • the phase of the second transmission groove and the third transmission groove is somewhat out of order due to manufacturing errors or assembly errors of the first and second transmission mechanisms
  • Due to the elastic deformation of the elastic member that connects the second planetary plate halves the first and second planetary plate halves are relatively displaced in the direction of rotation, and the deviation is absorbed.
  • the smooth operation of the first and second speed change mechanisms can be ensured without being interfered with by the deviation.
  • the manufacturing accuracy and assembly accuracy of each transmission mechanism are eased, and an increase in manufacturing cost can be suppressed.
  • the backlash of the first and second transmission mechanisms is made zero by the axial preload applied to the elastic member connecting the first and second planetary plate halves, Alternatively, the two speed change mechanisms can be operated more smoothly.
  • the counterweight attached to the first transmission shaft is disposed by using the accommodation space provided between the first and second planetary plate halves, thereby providing the counterweight.
  • the planetary transmission can be made compact.
  • the offset amount of the center of gravity of the counterweight on the main axis with respect to the center of gravity of the eccentric rotating body including the eccentric shaft and the planetary plate can be reduced, and the couple caused by the centrifugal force acting on both the centers of gravity can be kept small.
  • the planetary transmission device can be applied to a differential device. Therefore, the differential device can exhibit the same effect as the planetary transmission device.
  • FIG. 1 is a longitudinal front view of a differential device according to Embodiment 1 of the present invention.
  • FIG. 2 is a sectional view taken along line 2-2 of FIG.
  • FIG. 3 is a sectional view taken along line 3-3 in FIG. 1.
  • FIG. 4 is a sectional view taken along line 4-4 of FIG.
  • FIG. 5 is a sectional view taken along line 5-5 in FIG.
  • the longitudinal section front view of the differential which concerns on Example 2 of this invention.
  • FIG. 7 is a cross-sectional view taken along line 7-7 in FIG.
  • a differential device D as a planetary transmission is housed in a transmission case 1 of a vehicle together with a transmission, and rotational power output from the transmission is connected to left and right drive wheels of the vehicle. It is used for distributing to the first and second drive shafts S1, S2.
  • the differential case 2 of the differential device D includes a pair of left and right first and second case side walls 2a and 2b that are opposed to each other at an interval, and the outer peripheral ends of the first and second case side walls 2a and 2b are integrally formed. And a ring gear 4 connected to the. Therefore, the ring gear 4 is a component of the differential case 2.
  • the ring gear 4 meshes with the output gear 3 of the transmission to receive the output of the transmission.
  • first and second case side walls 2a, 2b are connected means between the first and second case side walls 2a, 2b and the ring gear 4, but bolts, caulking, or the like can also be used.
  • the first and second case side walls 2a and 2b are provided with a plurality of through holes 44 and 45 for allowing lubricating oil to flow between the differential case 2 and the transmission case 1, respectively.
  • the first and second case side walls 2a and 2b integrally have first and second cylinder shafts 5 and 6 that protrude outward and are aligned on the main axis X1, and these first and second cylinders are integrated.
  • the shafts 5 and 6 are rotatably supported by the mission case 1 via first and second ball bearings 7 and 8.
  • the first and second drive shafts S1 and S2 are rotatably supported by the first and second cylinder shafts 5 and 6, respectively.
  • the transmission case 1 includes first and second oil seals 10 and 11 for bringing a seal lip into close contact with the outer periphery of the first and second drive shafts S1 and S2 outside the first and second ball bearings 7 and 8, respectively. Installed.
  • a plurality of first and second spiral grooves 49 and 50 capable of transferring lubricating oil are formed on the inner peripheral surfaces of the first and second cylindrical shafts 5 and 6.
  • the differential case 2 is splined to the first drive shaft S1 and disposed on the main axis X1, and the first output shaft 19 is splined to the second drive shaft S2 and disposed on the main axis X1.
  • a second output shaft 20 and a planetary differential mechanism 21 that distributes rotational power input from the output gear 3 to the ring gear 4 to the first and second output shafts 20 are accommodated.
  • the differential mechanism 21 includes an input plate 12 that is integrally coupled to the first case side wall 2a, and an eccentric axis X2 that is integrally connected to the first output shaft 19 and is eccentric by a predetermined distance e from the main axis X1.
  • the first transmission mechanism 26 interposed between the first planetary plate 14 and the planetary plate 14 on the opposite side of the input plate 12 and the annular output plate 15 connected to the second output shaft 20, and the planetary plate 14 and And a second speed change mechanism 27 interposed between the output plates 15.
  • the output plate 15 is axially supported on the inner surface of the second case side wall 2b via the annular first thrust washer 31. .
  • a second thrust washer 32 for adjusting a gap between the first case side wall 2a and the first output shaft 19 in the axial direction is interposed.
  • a plurality of radially extending oil grooves 46, 47 are provided on the inner surfaces of the first and second case side walls 2a, 2b that are in contact with the first and second thrust washers 31, 32.
  • the first case side wall 2a and the input plate 12 are integrally formed as a single part, but they may be individually configured and connected to each other by a spline or the like.
  • the first speed change mechanism 26 includes an annular wave-shaped first transmission groove 33 formed on a side surface of the input plate 12 facing the planetary plate 14, and the input plate of the planetary plate 14.
  • 12 is formed on one side surface opposite to the first transmission groove 33 and has an annular corrugated second transmission groove 34 having a wave number smaller than that of the first transmission groove 33, and both the transmission grooves 33, in the overlapping portion of the first and second transmission grooves 33, 34, 34, a plurality of first transmission balls 37 that are rotatably arranged and arranged at equal intervals, and a first annular ball that is rotatably disposed between the input plate 12 and the planetary plate 14 and holds the first transmission balls 37.
  • a retainer plate 39 has the same number of holding holes 39a as the first transmission balls 37 and are arranged at equal intervals on the same circumference, and the first transmission balls 37 are rotatably held by these holding holes 39a. It is like that.
  • the second speed change mechanism 27 includes a ring-shaped third transmission groove 35 formed on the other side of the planetary plate 14 facing the output plate 15, and the output plate 15.
  • An annular corrugated fourth transmission groove 36 formed on a side surface facing the planetary plate 14 and having a wave number smaller than that of the third transmission groove 35, and both transmission grooves 35 in the overlapping portion of the third and fourth transmission grooves 35, 36.
  • 2 retainer plates 40 The second retainer plate 40 has the same number of holding holes 40a as the second transmission balls 38 and is arranged at equal intervals on the same circumference, and the first transmission balls 37 are rotatably held by these holding holes 40a. It is like that.
  • the first transmission groove 33 and the third transmission groove 35 are formed along an endless hypocycloid curve or hypotrochoid curve
  • the second transmission groove 34 and the fourth transmission groove 36 are endless epicycloid curves.
  • it is formed along an epitrochoid curve.
  • the first transmission groove 33 and the fourth transmission groove 36 are centered on the main axis X1
  • the second transmission groove 34 and the third transmission groove 35 are centered on the eccentric axis X2.
  • the wave number of the first transmission groove 33 is Z1
  • the wave number of the second transmission groove 34 is Z2
  • the wave number of the third transmission groove 35 is Z3
  • the wave number of the fourth transmission groove 36 is Z4
  • the four transmission grooves 33 to 36 are formed so as to satisfy the following expressions (1) to (3).
  • (Z1 / Z2) ⁇ (Z3 / Z4) 2 (1)
  • Z1-Z2 2 (2)
  • Z3-Z4 2 (3)
  • the eight-wave first transmission groove 33 and the six-wave second transmission groove 34 are overlapped at seven locations, and the seven transmission grooves 33 and 34 have seven grooves at the seven overlapping portions.
  • the first transmission ball 37 is interposed, and the six-wave third transmission groove 35 and the four-wave fourth transmission groove 36 overlap at five locations, and the five transmission grooves 35 and 36 overlap with the five overlapping portions.
  • Five second transmission balls 38 are interposed.
  • the planetary plate 14 is divided into a first planetary plate half 14 a and a second planetary plate half 14 b aligned in the axial direction, and only the first planetary plate half 14 a is formed on the eccentric shaft 13.
  • the third ball bearing 9 is rotatably supported.
  • the planetary plate halves 14 a and 14 b are connected via an elastic member 18.
  • the elastic member 18 is molded from rubber or elastic synthetic resin.
  • the second transmission groove 34 is formed on the outer surface of the first planetary plate half 14a
  • the third transmission groove 35 is formed on the outer surface of the second planetary plate half 14b.
  • a plurality of pin-shaped convex portions 16 arranged at equal intervals in the circumferential direction are provided on the surface of the first planetary plate half 14a facing the second planetary plate half 14b, while the second planetary plate
  • a plurality of concave portions 17 that receive the convex portions 16 are provided on the surface of the half body 14 b facing the first planetary plate half body 14 a so as to be arranged at equal intervals in the circumferential direction, and a cap is provided between the convex portions 16 and the concave portions 17.
  • a shaped elastic member 18 is interposed. At that time, the phases of the second transmission groove 34 and the third transmission groove 35 are matched as prescribed.
  • a gap g is provided between the opposing surfaces of both planetary plate halves 14a and 14b.
  • the elastic member 18 is disposed so as to allow constant relative displacement in the radial direction, the rotation direction, and the axial direction of the planetary plate halves 14a and 14b by elastic deformation thereof.
  • the elastic member 18 is given an axial preload that urges the first and second planetary half halves 14a and 14b in a direction to separate them from each other. Specifically, the elastic member 18 is axially compressed and deformed between the tip surface of the convex portion 16 and the bottom surface of the concave portion 17, and the repulsive force causes the first and second planetary plate halves 14 a and 14 b to interact with each other. It will be energized in the direction to separate.
  • the second planetary plate half 14 b is formed between the first and second planetary plate halves 14 a, 14 b with a bottomed cylinder comprising a cylindrical portion 22 and an end wall portion 23.
  • the storage space 42 is provided by comprising in a shape.
  • An inner end portion of the first output shaft 19 extends toward the accommodation space 42, and a counterweight 43 fixed to the inner end portion is accommodated in the accommodation space 42.
  • the weight portion 43a of the counterweight 43 is disposed in an opposite phase to the eccentric shaft 13 with the main axis X1 interposed therebetween.
  • the cylindrical portion 22 of the first planetary plate half 14a is provided with a plurality of lightening holes 29.
  • the recess 17 is provided on the end surface of the cylindrical portion 22, and the third transmission groove 35 is provided on the outer surface of the end wall portion 23.
  • the ring gear 4 When the ring gear 4 is rotated by the input from the output gear 3, the rotation is transmitted to the input plate 12 integral with the differential case 2, and therefore the first case side wall 2a, and the input plate 12 rotates around the main axis X1.
  • the eight-wave first transmission groove 33 of the input plate 12 drives the six-wave second transmission groove 34 of the first planetary plate half body 14a via the first transmission ball 37, and Since the driving force is simultaneously transmitted to the second planetary plate half 14b via the elastic member 18, the input plate 12 has the speed increase ratio of 8/6, that is, the first and second planetary plate halves 14a, 14b,
  • the planetary plate 14 is rotated about the eccentric axis X2.
  • the sixth transmission groove 35 of the planetary plate 14 drives the fourth transmission groove 36 of the output plate 15 via the second transmission ball 38.
  • the output plate 15 is rotated with a speed increasing ratio of 6/4.
  • the second output shaft 20 is fixed by fixing the second drive shaft S2 and rotational power is input to the ring gear 4 from the output gear 3 of the transmission.
  • the input plate 12 When the input plate 12 is rotated by the input from the ring gear 4, the input plate 12 is driven to the planetary plate 14 (first and second planetary plate halves 14 a and 14 b), and the planetary plate 14 is driven to the stationary output plate 15. Due to the reaction force, the planetary plate 14 revolves around the main axis X1 while rotating around the eccentric shaft 13, thereby rotating the eccentric shaft 13 around the main axis X1. As a result, the input plate 12 rotates the first output shaft 19 with a double speed increasing ratio.
  • the differential mechanism 21 can exhibit a differential function in which the rotational speed of the input plate 12 and the average value of the rotational speeds of the first and second output shafts 19 and 20 are always equal. Means. Thus, the differential mechanism 21 can distribute the rotational power of the input plate 12 to the first and second output shafts 19 and 20 according to their loads.
  • the rotational torque of the input plate 12 is applied to the planetary plate 14 (first and second planetary plate halves 14a and 14b) via the first transmission groove 33, the plurality of first transmission balls 37 and the second transmission groove 34.
  • the rotational torque of the planetary plate 14 is transmitted to the output plate 15 through the third transmission groove 35, the plurality of second transmission balls 38 and the fourth transmission groove 36, respectively.
  • torque transmission is performed in a distributed manner at a plurality of locations where the first and second transmission balls 37 and 38 are present, and the durability of the differential mechanism 21 is improved. It is possible to reduce the weight and contribute to the provision of the differential device D that can withstand a high load while being small.
  • the first and second retainer plates 39 and 40 hold a plurality of first and second transmission balls 37 and 38 to restrict their equidistant arrangement, and also part of the first transmission during torque transmission.
  • rampage occurs in the ball 37 or the second transmission ball 38, it cooperates with the other plurality of first transmission balls 37 or the second transmission ball 38 to suppress the rampage of the part of the transmission balls. , Smooth torque transmission by the first and second transmission balls 37 and 38 is ensured.
  • the planetary plate 14 is divided into first and second planetary plate halves 14a and 14b arranged in the axial direction, and only the first planetary plate half 14a is rotatably supported by the eccentric shaft 13, and
  • the first and second planetary plate halves 14a and 14b are elastic members interposed between the plurality of convex portions 16 of the first planetary plate half 14a and the plurality of concave portions 17 of the second planetary plate half 14b.
  • the planetary plate halves 14 a and 14 b are connected so as to allow relative displacement in the radial direction and the rotation direction.
  • the elastic member 18 is subjected to compression deformation in the rotation direction of the planetary plate 14.
  • the first and second planetary plate halves 14a and 14b are relatively displaced in the direction of rotation, so that the above-mentioned deviation is absorbed.
  • the smooth operation of the first and second transmission mechanisms 26 and 27 and the differential mechanism 21 can be ensured without being interfered by the various deviations as described above. Therefore, the manufacturing accuracy and assembly accuracy of each of the transmission mechanisms 26 and 27 are eased, and an increase in manufacturing cost can be suppressed.
  • the output plate 15 is connected to the second case side wall. 2b, the first transmission ball 37 is in pressure contact with the first and second transmission grooves 33, 34, and the second transmission ball 38 is in the third and fourth transmission grooves 35, 36, each of which is always maintained in a pressure contact state with 36, thereby eliminating the play in the axial direction of the output plate 15, reducing the backlash of the first and second transmission mechanisms 26, 27, and differentially.
  • the mechanism 21 can be operated more smoothly.
  • the output plate 15 is kept in pressure contact with the second case side wall 2b, so that the first thrust washer 31 interposed between the output plate 15 and the second case side wall 2b has a shim function. Therefore, the first thrust washer 31 can be omitted.
  • the elastic member 18 is useful for absorbing torque fluctuations caused by fluctuations in input power and load.
  • a counterweight 43 attached to the first output shaft 19 is arranged in the accommodating space 42 provided between the first and second planetary plate halves 14a and 14b, so that the planetary difference with the counterweight 43 is provided.
  • the moving device D can be configured compactly.
  • the offset s of the center of gravity G2 of the counterweight 43 on the main axis X1 with respect to the center of gravity G1 of the eccentric rotating body including the eccentric shaft 13 and the planetary plate 14 can be made zero or small. Couples due to centrifugal force acting on G2 can be suppressed.
  • one of the first and second planetary plate halves 14a and 14b has an inner cylindrical portion having an uneven outer peripheral surface 24a. 24 is provided, and on the other side, an outer cylinder portion 25 having an uneven inner peripheral surface 25a is provided.
  • the inner cylinder portion 24 and the outer cylinder portion 25 are inlay-fitted with each other so as to sandwich an elastic member 18 ′ having an L-shaped cross section between the concave / convex outer peripheral surface 24 a and the concave / convex inner peripheral surface 25 a.
  • the phases of the second transmission groove 34 and the third transmission groove 35 are matched as prescribed. Since the other configuration is the same as that of the first embodiment, the same reference numerals are given to the portions corresponding to the first embodiment in FIGS. 6 and 7, and the detailed description thereof will be omitted.
  • the differential device D can be applied to a central differential device (center differential) for driving front and rear wheels in a front and rear wheel drive vehicle.
  • the differential case 2 is configured as a stationary gear case
  • the first output shaft 19 is a drive shaft connected to, for example, an electric motor
  • the second output shaft 20 is a driven shaft connected to a load.
  • the present invention can be applied to a speed reducer or a speed increasing device.
  • the first and second transmission balls 37 and 38 can be replaced by rollers, respectively.

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

Abstract

Selon la présente invention, une plaque planétaire (14) est divisée en des première et seconde demi-plaques planétaires (14a, 14b), et seule la première demi-plaque planétaire (14a) est supportée sur un arbre excentrique (13). Les première et seconde demi-plaques planétaires (14a, 14b) sont couplées l'une à l'autre par l'intermédiaire d'un élément élastique (18) qui permet un déplacement relatif des demi-plaques planétaires (14a, 14b) dans la direction radiale. L'écart entre la précision coaxiale d'une première rainure de transmission (33) et d'une quatrième rainure de transmission (36) et la précision coaxiale d'une deuxième rainure de transmission (34) et d'une troisième rainure de transmission (35) est absorbé par le déplacement relatif des demi-plaques planétaires (14a, 14b) dans la direction radiale conjointement avec une déformation élastique de l'élément élastique (18).
PCT/JP2018/002817 2017-03-29 2018-01-30 Dispositif de transmission et dispositif différentiel planétaires Ceased WO2018179788A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017064743A JP2018168876A (ja) 2017-03-29 2017-03-29 遊星式伝動装置及び差動装置
JP2017-064743 2017-03-29

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WO2018179788A1 true WO2018179788A1 (fr) 2018-10-04

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PCT/JP2018/002817 Ceased WO2018179788A1 (fr) 2017-03-29 2018-01-30 Dispositif de transmission et dispositif différentiel planétaires

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61119869A (ja) * 1984-11-15 1986-06-07 Toshiba Corp 動力伝達装置
JPH02249768A (ja) * 1989-03-24 1990-10-05 Nissan Motor Co Ltd 平行軸の連結構造
WO2016013315A1 (fr) * 2014-07-25 2016-01-28 武蔵精密工業株式会社 Dispositif differentiel
WO2016199708A1 (fr) * 2015-06-08 2016-12-15 武蔵精密工業株式会社 Dispositif de transmission
JP2017053378A (ja) * 2015-09-07 2017-03-16 武蔵精密工業株式会社 伝動装置及び差動装置

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JPH02249768A (ja) * 1989-03-24 1990-10-05 Nissan Motor Co Ltd 平行軸の連結構造
WO2016013315A1 (fr) * 2014-07-25 2016-01-28 武蔵精密工業株式会社 Dispositif differentiel
WO2016199708A1 (fr) * 2015-06-08 2016-12-15 武蔵精密工業株式会社 Dispositif de transmission
JP2017053378A (ja) * 2015-09-07 2017-03-16 武蔵精密工業株式会社 伝動装置及び差動装置

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