WO2018110197A1 - Module d'entraînement - Google Patents

Module d'entraînement Download PDF

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Publication number
WO2018110197A1
WO2018110197A1 PCT/JP2017/041302 JP2017041302W WO2018110197A1 WO 2018110197 A1 WO2018110197 A1 WO 2018110197A1 JP 2017041302 W JP2017041302 W JP 2017041302W WO 2018110197 A1 WO2018110197 A1 WO 2018110197A1
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WO
WIPO (PCT)
Prior art keywords
rotor shaft
output
shaft
planetary
rotor
Prior art date
Application number
PCT/JP2017/041302
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English (en)
Japanese (ja)
Inventor
佑介 大畑
大場　浩量
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018110197A1 publication Critical patent/WO2018110197A1/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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
    • F16H13/08—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion with balls or with rollers acting in a similar manner
    • 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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/10—Means for influencing the pressure between the members
    • F16H13/14—Means for influencing the pressure between the members for automatically varying the pressure mechanically
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility

Definitions

  • the present invention relates to a drive module, and more particularly to a drive module in which a motor having a stator portion and a rotor portion and a speed reducer are integrated.
  • a combination of a motor and a speed reducer (that is, a drive module) may be used for the purpose of reducing the size and price of the motor.
  • a traction drive mechanism may be used for such a drive module speed reducer (deceleration mechanism).
  • the traction drive mechanism is used in such a drive module by taking advantage of low noise and low vibration.
  • Traction drive reducer uses traction grease to lubricate the bearing and applies a preload to the bearing to provide the traction drive function.
  • Patent Document 1 a microtraction has been proposed in which a steel ball is used as a rolling element, and the outer ring, the ball of the steel ball, and the inner ring resist the thrust in the direction opposite to the input shaft.
  • Patent Document 1 the outer ring is shrink-fitted so that a plurality of balls arranged on the inner ring raceway surface are pressed against each other at the outer ring raceway surface.
  • a normal force which is a pressure contact force in the normal direction is strongly applied.
  • FIG. 2 of Patent Document 1 describes a housing in which the center of the housing surrounding the central axis is configured by an elastic outer ring.
  • the elastic outer ring has a channel-shaped cross section, and the outer ring raceway surface of the elastic outer ring is elastically deformed in the inner circumferential direction by tightening bolts and nuts, and a plurality of balls arranged on the inner ring raceway surface. Are pressed against the outer ring raceway surface.
  • Patent Document 1 includes a first taper ring having a first taper surface, a second taper ring having a second taper surface, and a fastening structure for fastening the first taper ring and the second taper ring. And a configuration in which the interval between the first taper ring and the second taper ring is adjusted by a fastening structure.
  • the first taper ring and the second taper ring constitute an outer ring, and each taper ring is formed with a taper surface, and the pair of taper surfaces form an outer ring raceway surface including a V groove. For this reason, a plurality of balls arranged on the inner ring raceway surface are brought into pressure contact with the outer ring raceway surface by adjustment by the fastening structure.
  • Patent Document 1 The one shown in FIG. 4 of Patent Document 1 is provided with a first spring that is urged in an expanding direction between the output side end portion in the housing and the outer ring, and expands between the pair of inner rings.
  • a second spring that biases in the direction is arranged. For this reason, a 1st spring pushes an inner ring
  • the second spring pushes the inner ring of the input shaft support bearing in the direction opposite to the input shaft, and pushes the outer ring through the ball.
  • a pair of tapered roller bearings are provided, and a spring that biases the outer ring of the output side tapered roller bearing toward the input side is provided.
  • the normal force of this spring acts on the contact surface between the roller and the outer ring raceway surface and the inner ring raceway surface, so that a plurality of rollers roll without slipping with the inner ring raceway surface and the outer ring drive surface. It is configured to move.
  • a rotating body that revolves around the central axis of the input shaft and a pressing ring disposed around the axis of the input shaft or the output shaft are provided.
  • An inclined surface is provided.
  • the inclined surface of the pressing ring causes the relative pressing in the rotation direction between the inner ring provided on the input shaft and the outer ring whose rotation direction is fixed with respect to the housing when the pressing ring is rotated. It is an inclined surface that adjusts the pressure. That is, the preload is applied to the microtraction by the inclined surface that allows the relative pressing force of the inner ring and the outer ring in the direction of the rotating body to be adjusted.
  • Patent Document 2 has a structure in which the preload is changed by a load torque using an inclined surface.
  • this mechanism has a structure with a large size in the axial direction and cannot be a compact speed reducer.
  • the present invention provides a drive module which is a compact flat motor-integrated speed reducer with low initial torque and high durability.
  • the drive module of the present invention is a drive module in which a motor having a stator part and a rotor part and a speed reducer are integrated, and includes a first output shaft and a rotor shaft input that rotates as the rotor part rotates. And a rotor shaft having a rotor shaft output portion that rotates as the rotor shaft input portion rotates, and the rotational drive force of the rotor shaft output portion is decelerated at a predetermined reduction ratio to the first output shaft.
  • a first transmission mechanism configured by a traction drive mechanism for transmission, and provided between the rotor shaft input unit and the rotor shaft output unit, and a relative push between the rotor shaft input unit and the rotor shaft output unit;
  • a pressing structure for adjusting the pressure.
  • Rotation of the rotor shaft input unit changes the relative rotational phase between the rotor shaft input unit and the rotor shaft output unit.
  • the first transmission mechanism is A traction force is generated in the traction drive mechanism, and the rotation from the rotor shaft input portion is decelerated as a microtraction drive and output to the first output shaft.
  • the rotor shaft input portion has an input portion side corresponding surface facing the rotor shaft output portion
  • the rotor shaft output portion has an output portion side corresponding surface facing the rotor shaft input portion
  • the pressing structure portion includes the input portion A torque cam groove provided so as to face the side corresponding surface and the output portion side corresponding surface, and a rolling element disposed between the corresponding torque cam grooves, when rotational torque is applied to the rotor shaft input portion, It is preferable to provide each torque cam groove with an inclined surface on which the rolling element rides and adjusts the relative pressing force between the rotor shaft input portion and the rotor shaft output portion.
  • the rolling element climbs the inclined surface by the change in the relative rotational phase due to the change in the relative rotational phase between the rotor shaft input portion and the rotor shaft output portion.
  • the moving force generates a pressing force in a direction in which the distance between the rotor shaft input shaft and the rotor shaft output shaft is increased, and a load is applied to the bearing that supports the rotor shaft at both ends. This load increases as the power of the rotor portion increases.
  • the rolling element of the pressing means moves in the rotation direction, the rolling element moves up the inclined surface and moves in a direction in which the distance between the rotor shaft input portion and the rotor shaft output portion is increased. This amount of movement increases as the torque increases.
  • the first transmission mechanism includes an inner ring fixed to the rotor shaft output portion, an outer ring fixed to the casing, a rolling element disposed between the rolling surface of the inner ring and the rolling surface of the outer ring, an inner ring, It is preferable that a cage is provided between the outer ring and the rolling element to hold the rolling elements, and the cage is set so as to form an integral structure with the first output shaft.
  • the traction mechanism of the first transmission structure can be configured by a bearing, compactness can be adopted, and the cage is integrally formed with the first output shaft. Rotational force transmission from to the first output shaft is stabilized.
  • a second transmission mechanism uses the first output shaft integrated with the retainer as an input shaft and transmits the rotational driving force of the input shaft to the second output shaft by decelerating at a predetermined reduction ratio.
  • the transmission mechanism engages and rotates with the solar member provided on the first output shaft, the planetary member engaged with the solar member, the annular member engaged with the planetary member, and the planetary member.
  • a planetary structure including a carrier that transmits a rotational driving force to the second output shaft can be configured.
  • the second transmission mechanism can reduce the transmission driving force of the input shaft constituted by the first output shaft by a predetermined reduction ratio and transmit it to the second output shaft, By having two transmissions, a desired reduction ratio can be obtained with certainty.
  • the second transmission mechanism is a planetary gear mechanism in which the sun member is a sun gear, the planetary member is a planetary gear, and the annular member is a ring gear, the sun member is a sun roller,
  • the planetary member may be a planetary roller, and the annular member may be a planetary traction drive using a ring roller. That is, the second transmission mechanism can be configured by a planetary gear mechanism or a planetary traction drive. If it is a planetary gear mechanism, it is efficient, and if it is a planetary traction drive, an output with low noise and low vibration is possible.
  • a compact, flat motor-integrated speed reducer with small initial torque and high durability can be configured.
  • the drive module according to the present invention has a motor 3 having a stator portion 1 and a rotor portion 2 and a speed reducer 4 integrated with each other, and the motor 3 and the speed reducer 4 are accommodated in a casing 5. .
  • the casing 5 includes a first part 5a, a second part 5b, and a third part 5c. That is, the first part 5 a has a short cylinder part 6 and a lid part 7 that closes the opening on the opposite side of the short cylinder part 6.
  • the second part 5b is made of a short cylinder
  • the third part 5c has a short cylinder part 8 and a thick inner collar part 9 provided on the output side of the short cylinder part 8.
  • the stator portion 1 of the motor 3 is fixed to an intermediate portion in the axial direction of the casing 5, and is formed with a stator core 1a formed of a plurality of electromagnetic steel plates laminated in the axial direction, a bobbin 1b made of an insulating material attached to the stator core 1a, And a stator coil (not shown) wound around 1b.
  • the rotor unit 2 includes an annular rotor core 2a and a plurality of magnets 2b attached to the outer periphery of the rotor core 2a. That is, the motor 3 is constituted by an electric motor in which the rotor portion 2 is arranged so as to face the inner side in the radial direction of the stator portion 1 with a gap. In this embodiment, a radial gap type is illustrated as an example of the electric motor.
  • the drive module is divided into a rotor shaft input portion 10 that rotates as the rotor portion 2 of the motor 3 rotates and a rotor shaft output portion 11 that rotates as the rotor shaft input portion 10 rotates.
  • the rotor shaft 12 is provided.
  • the rotor shaft input unit 10 includes an intermediate disk part 13 whose axis is disposed on the axis of the casing 5, a cylindrical part 14 provided continuously to the outer peripheral part of the intermediate disk part 13, and the intermediate disk part 13. There is a shaft portion 15 that protrudes from the center portion to the output side.
  • the rotor portion 2 of the motor 3 is fitted and fixed to the cylindrical portion 14.
  • the rotor shaft output portion 11 is externally fitted to the shaft portion 15 via a bearing (needle roller bearing) 16.
  • the shaft portion 15 includes a boss portion 15a on the intermediate disk portion 13 side and a main body shaft 15b projecting from the boss portion 15a, and a needle roller bearing 16 is externally fitted to the main body shaft 15b.
  • the rotor shaft output portion 11 includes a cylindrical main body portion 11a and a ring-shaped outer flange portion provided on the intermediate disk portion 13 side of the rotor shaft input portion 10 of the main body portion 11a. 11b.
  • the end surface of the outer flange portion 11b on the side of the intermediate disk portion 13 becomes an output portion side corresponding surface 19 where the rotor shaft output portion 11 faces the rotor shaft input portion 10, and faces the output portion side corresponding surface 19.
  • the end surface of the intermediate disk portion 13 of the rotor shaft input portion 10 becomes an input portion side corresponding surface 18 where the rotor shaft input portion 10 faces the rotor shaft output portion 11.
  • the rotor shaft input portion 10 has a ring-shaped recess 20 formed by an end portion on the output side of the cylindrical portion 14, an intermediate disk portion 13 of the rotor shaft input portion, and a boss portion 15 a of the first output shaft 15.
  • the outer flange portion 11 b of the rotor shaft output portion 11 is loosely fitted in the recess 20.
  • a pressing structure M described later is provided between the input portion side corresponding surface 18 and the output portion side corresponding surface 19.
  • a support shaft portion 21 is provided at the center of the inner surface of the lid portion 7 of the casing 5.
  • the support shaft portion 21 includes a base large-diameter portion 21a, an intermediate-diameter portion 21b in the axial intermediate portion, and a small-diameter portion 21c at the end.
  • the base large-diameter portion 21a is embedded in the lid portion 7 of the casing 5. It has become.
  • a bearing 22 is fitted on the small diameter portion 21 c of the support shaft portion 21.
  • the bearing 22 is disposed between an inner ring 23 having a raceway surface 23 a on the outer diameter surface, an outer ring 24 having a raceway surface 24 a on the inner diameter surface, and the inner ring 23 and the outer ring 24 so as to be able to roll.
  • This is an angular ball bearing including a rolling element (ball) 25 and a cage (not shown).
  • a circumferential cutout 26 is provided on the inner diameter surface of the cylindrical portion 14 on the lid portion 7 side of the intermediate disc portion 13 of the rotor shaft input portion 10, and the outer ring 24 of the bearing 22 is fitted into the circumferential cutout 26. is doing.
  • a bearing 28 is externally fitted to the main body 11a of the rotor shaft output part 11.
  • the bearing 28 is rotatably disposed between the inner ring 29 having a raceway surface 29 a formed on the outer diameter surface, the outer ring 30 having the raceway surface 30 a formed on the inner diameter surface, and the inner ring 29 and the outer ring 30.
  • An angular ball bearing includes a rolling element (ball) 31 and a cage 32 that holds the ball 31.
  • a circumferential notch 33 is provided on the inner diameter surface of the inner flange 9 in the third portion 5 c of the casing 5, and the outer ring 30 of the bearing 28 is fitted into the circumferential notch 33.
  • the retainer 32 has an integral structure with the first output shaft 35 of the drive module as shown in FIGS. That is, a disc-shaped flange 36 extending in the outer diameter direction is provided at the input side end of the first output shaft 35, and a short cylindrical portion 37 protruding from the outer diameter end of the flange 36 toward the input side. Are continuously provided, and pockets 38 formed of a plurality of notches are formed in the short cylindrical portion 37 at a predetermined pitch along the circumferential direction. For this reason, the short cylindrical portion 37 constitutes a cage 32 having pockets 38 for holding the balls 31 at a predetermined pitch along the circumferential direction.
  • the rotor shaft 12 having a structure divided into the rotor shaft input portion 10 and the rotor shaft output portion 11 that rotates as the rotor shaft input portion 10 rotates includes a pair of bearings 22, At 28, it is pivotally supported by the casing 5.
  • the axis of the rotor shaft 12, that is, the axis of the rotor shaft input unit 10 and the rotor shaft output unit 11, the axis of the support shaft 21, and the axis of the output shaft 35 are on the same axis.
  • the axis forms the axis of the drive module.
  • the input side end face 23b of the inner ring 23 of the bearing 22 abuts on a step part 21d between the small diameter part 21c and the medium diameter part 21b of the support shaft part 21, and the output side end face 24c of the outer ring 24 of the bearing 22 is
  • the rotor shaft input portion 10 is in contact with the end face 26 a of the circumferential cutout portion 26.
  • the input side end face 29 b of the inner ring 29 of the bearing 28 abuts on the output side end face 40 of the outer flange part 11 b of the rotor shaft output part 11, and the output side end face 30 c of the outer ring 30 of the bearing 28 is the third end of the casing 5. It abuts against the end face 33a of the circumferential notch 33 of the inner flange portion 9 of the portion 5c.
  • the pressing structure portion M is provided with a plurality of torque cam grooves 41, 42 provided at a predetermined pitch along the circumferential direction so as to face the input portion side corresponding surface 18 and the output portion side corresponding surface 19. And rolling elements (balls) 43 disposed between the corresponding torque cam grooves 41, 42.
  • the torque cam grooves 41 and 42 are provided with inclined surfaces 41a and 42a. That is, the shape of the cross section perpendicular to the axial direction of the torque cam grooves 41 and 42 is a flat semi-elliptical shape in which the radius of curvature on the opening side is larger than the radius of curvature of the bottom.
  • a ball as one rolling element 43 is arranged at 41, 42.
  • the rolling elements ride on the inclined surfaces 41a and 42a. That is, the ball 43 moves up the inclined surfaces 41a and 42a by a change in the relative rotational phase between the rotor shaft input unit 10 and the rotor shaft output unit 11. Accordingly, a pressing force is generated in a direction (axial direction) in which the distance between the rotor shaft input unit 10 and the rotor shaft output unit 11 is increased, and the rotor shaft configured by the rotor shaft input unit 10 and the rotor shaft output unit 11 A load is applied to bearings 22 and 28 that support 12 at both axial ends. This load becomes larger as the power of the rotor unit 2 is larger.
  • the upper diagram of FIG. 5 shows the position of the rolling element 43 when no torque is input.
  • the arrangement with a slight preload is suitable for suppressing the generation of abnormal noise.
  • the lower figure of FIG. 5 has shown the position of the rolling element 43 when a torque acts.
  • the rolling element (ball) 43 of the pressing structure M moves in the rotation direction, the rolling element 43 climbs the inclined surfaces 41a and 42a, and the distance between the rotor shaft input unit 10 and the rotor shaft output unit 11 increases in the direction X.
  • X is a value that increases as the torque increases.
  • the speed reducer 4 can be configured by the first transmission mechanism T1 of the microtraction mechanism including the bearing 28.
  • a pressing force to the output side acts on the bearing 28 in the pressing structure portion M, and the end surface 29b of the inner ring 29 of the bearing 28 is pressed to the output side in the outer flange portion 11b of the rotor shaft output portion 11, This pressing force is transmitted to the outer ring 30 via the ball 31. Therefore, a pressure contact force is applied to the raceway surface 29 a of the inner ring 29 and the raceway surface 30 a of the outer ring 30.
  • the bearing 28 is filled with traction grease. For this reason, traction is generated in the bearing 28 and is decelerated and output as a microtraction drive.
  • the traction grease has increased viscosity resistance so as to increase the torque at the time of rotation, and lithium soap grease using lithium soap as a thickener is common.
  • the drive module has a configuration in which the hollow motor 3 and the microtraction speed reducer 4 are combined.
  • the output-side bearing 28 constitutes a microtraction speed reducer.
  • a member (rotor shaft input portion 10) that rotates integrally with the rotor portion 2 of the motor 3 and the rotor shaft output portion 11 on the input side of the microtraction speed reducer.
  • the torque cam grooves 41 and 42 having the inclined surfaces 41a and 42a are arranged. Therefore, it is possible to provide a compact flat motor-integrated hybrid speed reducer with small initial motion torque and high durability.
  • the traction mechanism of the first transmission mechanism T1 can be configured by the bearing 28, and the compactness can be adopted. Moreover, since the cage 32 is integrated with the first output shaft 35, the first transmission mechanism T1 is changed to the first transmission mechanism T1. 1 Rotational force transmission to the output shaft 35 is stabilized.
  • the drive module shown in FIG. 1 is further provided with another second transmission mechanism T2.
  • the outer casing 50 is provided in the third part 5 c of the casing 5, and the end casing 52 on the output side is provided in the outer casing 50 via the intermediate short cylindrical body 51, whereby the sub casing 53 is provided.
  • the second transmission mechanism T2 is accommodated in the sub casing 53.
  • the outer flange 50, the intermediate short cylinder 51, and the end cylinder 52 are provided with through holes 50a, 51a, 52a, respectively, and bolt members (not shown) are provided in the through holes 50a, 51a, 52a. Is inserted, and the third portion 5c, the short cylindrical body 51, and the end cylindrical body 52 are integrated.
  • the second transmission mechanism T2 includes a sun member 55 provided on the first output shaft 35, a planet member 56 that engages with the sun member 55, an annular member 57 that engages with the planet member 56, and the planet member. 56 and a carrier 59 that transmits the rotational driving force to the second output shaft 58 by engaging with and rotating. For this reason, the rotational force from the first output shaft 35 is decelerated by the second transmission mechanism T ⁇ b> 2 and transmitted to the second output shaft 35.
  • the second transmission mechanism T2 shown in FIG. 6 includes a planetary traction drive in which the sun member 55 is a sun roller 55A, the planetary member 56 is a planetary roller 56A, and the annular member 57 is a ring roller 57A.
  • the first output shaft 35 (35A) in this case has a large-diameter main body portion 35a and an end small-diameter portion 35b, and an annular sun roller 55A is fitted and fixed to the main body portion 35a.
  • the second output shaft 58 is formed of a disk-shaped body 61 having a concave portion 61a into which the small-diameter portion 35b is fitted on the inner surface, and a plurality of protrusions projecting to the inner surface on the outer diameter side of the disk-shaped body 61.
  • a carrier 59 having a shaft 60 is provided.
  • a planetary roller 56 ⁇ / b> A is externally fitted to each protruding shaft 60 via a bearing 62.
  • the second output shaft 58 is rotatably supported by the sub casing 53 by a pair of bearings 64 and 65.
  • the bearing 64 is rotatably disposed between an inner ring 66 having a raceway surface 66 a formed on the outer diameter surface, an outer ring 67 having a raceway surface 67 a formed on the inner diameter surface, and the inner ring 66 and the outer ring 67.
  • a rolling element (ball) 68 and a retainer (not shown) that holds the ball 68 are provided.
  • the bearing 65 is disposed between the inner ring 69 having the raceway surface 69 a on the outer diameter surface, the outer ring 70 having the raceway surface 70 a on the inner diameter surface, and the inner ring 69 and the outer ring 70 so as to be able to roll.
  • Rolling elements (balls) 71 and a retainer (not shown) that holds the balls 71 are provided.
  • a ring-shaped recess 73 is provided on the output side end surface of the third portion 5 c of the casing 5, and a bearing 64 is fitted in the recess 73.
  • the bearing support member 74 is attached to the end surface 75 of the protruding shaft 60 of the carrier 59.
  • the bearing support member 74 includes a thin ring body 74a and a thick short cylindrical body 74b protruding from the ring body 74a. With the ring body 74a in contact with the end surface 75 of the projecting shaft 60, the screw member 76 is screwed into the screw hole provided in the end surface 75 of the projecting shaft 60 through the through hole provided in the ring body 74a. By wearing, the bearing support member 74 can be attached to the protruding shaft 60.
  • the outer cylindrical surface of the short cylindrical body 74 b is provided with a notch 77, and the inner ring 66 of the bearing 64 is fitted therein, and the outer ring 67 of the bearing 64 is fitted into the notch 78 on the outer peripheral side inner surface of the recess 73.
  • a notch 80 is provided on the input side of the outer peripheral surface of the second output shaft 58, the inner ring 69 of the bearing 65 is fitted, and a notch 81 is provided on the input side of the inner peripheral surface of the end cylinder 52.
  • the outer ring 70 of the bearing 65 is fitted in the notch 81.
  • a notch portion 82 is provided on the output side of the outer peripheral surface of the output shaft 58, and the seal member (sealing device) 83 is fitted into the notch portion 82. The gap between the outer peripheral surface of the output side and the output side end cylindrical body 52 is sealed.
  • a bearing 85 is mounted on the small diameter portion 35b of the first output shaft 35 (35A) inserted into the concave portion 61a of the second output shaft 58.
  • the bearing 85 is rotatably disposed between an inner ring 86 having a raceway surface 86 a formed on the outer diameter surface, an outer ring 87 having a raceway surface 87 a formed on the inner diameter surface, and the inner ring 86 and the outer ring 87.
  • a rolling element (ball) 88 and a retainer (not shown) that holds the ball 88 are provided.
  • the inner ring 86 of the bearing 85 is fitted on the small diameter portion 35b of the first output shaft 35 (35A), and the outer ring 87 of the bearing 85 is fitted on a notch 89 provided on the peripheral wall of the recess 61a of the second output shaft 58.
  • the ring roller 57A which is the annular member 57, is provided with a flat convex ridge 90 on its inner surface, and the outer diameter surface 56a of the planetary roller 56A, which is the planetary member 56, is in pressure contact with the flat convex ridge 90.
  • the other configuration of the drive module shown in FIG. 6 is the same as the configuration of the drive module shown in FIG. 1, and therefore, the configuration will be described with reference to FIG. Omitted.
  • the first output shaft 35 rotates when the motor 3 is driven, as in the drive module shown in FIG. For this reason, the first output shaft 35 becomes an input shaft of the second transmission mechanism T2 configured by the planetary traction drive. Further, when the first output shaft 35 that is the input shaft of the second transmission mechanism T2 rotates, the sun roller 55A that is the sun member 55 rotates along with the rotation of the input shaft. Due to the rotation of the sun roller 55A, the planetary roller 56A as the planetary member 56 revolves while rotating. As a result, the second output shaft is decelerated and rotated.
  • the second transmission mechanism T2 decelerates the driving force of the input shaft constituted by the first output shaft 35 with a predetermined reduction ratio and transmits it to the second output shaft 58. Therefore, it is possible to reliably obtain a desired reduction ratio by having two transmissions.
  • the second transmission mechanism T2 is configured by a planetary traction drive in which the sun member 55 is a sun roller 55A, the planetary member 56 is a planetary roller 56A, and the annular member 57 is a ring roller 57A.
  • the sun member 55 is a sun gear 55B
  • the planetary member 56 is a planetary gear 56B supported by a carrier 59 (59B)
  • the annular member 57 is a ring gear 57B.
  • the planetary gear mechanism is efficient, and the planetary traction drive enables low noise and low vibration output.
  • the pressing structure portion M corresponds to the input portion side corresponding surface 18 and the output portion side.
  • Torque cam grooves 41 and 42 provided so as to face the surface 19 and rolling elements 43 provided between the corresponding torque cam grooves 41 and 42 are provided.
  • the pair of opposing torque cam grooves 41 and 42 are arranged at a predetermined pitch along the circumferential direction, but the number thereof can be arbitrarily set.
  • the angular ball bearing is used as the bearing 28 used in the first transmission mechanism T1, but similarly, a tapered roller bearing that can load a radial load and an axial load in one direction may be used. Good.
  • the second transmission mechanism T2 the number of planetary members 56 can be arbitrarily set.
  • a motor and a speed reducer can be used for a drive mechanism such as an electric vehicle.
  • a transmission mechanism including a traction drive mechanism is provided.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Friction Gearing (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

Module d'entraînement pourvu d'un arbre (12) de rotor ayant une structure divisée en une partie d'entrée (10) d'arbre de rotor et une partie de sortie (11) d'arbre de rotor, d'un premier mécanisme de transmission (T1) qui réduit la force d'entraînement en rotation de la partie de sortie (11) d'arbre de rotor à un rapport de réduction prescrit et transmet la force réduite à un arbre de sortie (35), et d'une partie de mécanisme de pression (M) qui est interposée entre la partie d'entrée (10) d'arbre de rotor et la partie de sortie (11) d'arbre de rotor et qui ajuste la force de pression relative entre la partie d'entrée (10) d'arbre de rotor et la partie de sortie (11) d'arbre de rotor.
PCT/JP2017/041302 2016-12-14 2017-11-16 Module d'entraînement WO2018110197A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016242214A JP2018096470A (ja) 2016-12-14 2016-12-14 駆動モジュール
JP2016-242214 2016-12-14

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WO2018110197A1 true WO2018110197A1 (fr) 2018-06-21

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WO (1) WO2018110197A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1172152A (ja) * 1997-07-02 1999-03-16 Nippon Seiko Kk 摩擦ローラ式変速機
JP2003065209A (ja) * 2001-08-27 2003-03-05 Ntn Corp 風力発電機用変速機
JP2012197930A (ja) * 2011-03-09 2012-10-18 Nsk Ltd 摩擦ローラ式減速機及び電気自動車用駆動装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1172152A (ja) * 1997-07-02 1999-03-16 Nippon Seiko Kk 摩擦ローラ式変速機
JP2003065209A (ja) * 2001-08-27 2003-03-05 Ntn Corp 風力発電機用変速機
JP2012197930A (ja) * 2011-03-09 2012-10-18 Nsk Ltd 摩擦ローラ式減速機及び電気自動車用駆動装置

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