WO2020188967A1 - 摩擦ローラ減速機 - Google Patents

摩擦ローラ減速機 Download PDF

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Publication number
WO2020188967A1
WO2020188967A1 PCT/JP2020/000683 JP2020000683W WO2020188967A1 WO 2020188967 A1 WO2020188967 A1 WO 2020188967A1 JP 2020000683 W JP2020000683 W JP 2020000683W WO 2020188967 A1 WO2020188967 A1 WO 2020188967A1
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WO
WIPO (PCT)
Prior art keywords
roller
input shaft
rolling contact
pair
contact surface
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/JP2020/000683
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English (en)
French (fr)
Japanese (ja)
Inventor
弘志 河原
浩文 板垣
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.)
NSK Ltd
Original Assignee
NSK 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 NSK Ltd filed Critical NSK Ltd
Priority to CN202080021733.7A priority Critical patent/CN113574294B/zh
Priority to US17/440,950 priority patent/US11867262B2/en
Priority to EP20773638.0A priority patent/EP3943779A4/en
Priority to JP2021506189A priority patent/JPWO2020188967A1/ja
Publication of WO2020188967A1 publication Critical patent/WO2020188967A1/ja
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
    • 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
    • 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms

Definitions

  • the present invention relates to a friction roller reducer, for example, which is incorporated in a drive system of an electric vehicle to reduce the rotation of an electric motor (increase torque) and then transmit torque to drive wheels.
  • FIG. 6 shows the friction roller reducer described in Japanese Patent Application Laid-Open No. 2012-207778.
  • the friction roller reducer 100 includes a housing 101, an input shaft 102, an output shaft 103, a solar roller 104, an annular roller 105, a plurality of planetary rollers 106, and a pair of pressing devices 107.
  • the input shaft 102 and the output shaft 103 are supported inside the housing 101 coaxially with each other and capable of relative rotation.
  • the solar roller 104 is a combination of a pair of solar roller elements 108 having a symmetrical shape in the axial direction.
  • a pair of solar roller elements 108 are in a state in which a gap is interposed between the tip surfaces facing each other around the input shaft 102 so as to be coaxial with the input shaft 102 and capable of relative rotation with respect to the input shaft 102. It is supported by.
  • the pair of solar roller elements 108 have a conical surface-shaped inner diameter side rolling contact surface 109 on the outer peripheral surface, in which the outer diameter dimension increases as the distance from each other in the axial direction increases, and the pair of solar roller elements 108 are opposite to each other in the axial direction.
  • the driven side cam surface 110 is provided on the base end surface facing the side (facing the side opposite to the tip surface in the axial direction).
  • the driven-side cam surface 110 is formed by arranging driven-side cam recesses 111 whose axial depth changes with respect to the circumferential direction at a plurality of locations at equal intervals in the circumferential direction.
  • the annular roller 105 is arranged coaxially with the solar roller 104 around the solar roller 104, and is connected to the output shaft 103 so as to be able to transmit torque by a connecting portion 112 having an L-shaped cross section.
  • the annular roller 105 has a cylindrical outer diameter side rolling contact surface 113 on the inner peripheral surface.
  • the planetary roller 106 has a support shaft 114 arranged in parallel with the input shaft 102, and enables rotation (rotation) around the support shaft 114 and displacement of the input shaft 102 in the radial direction. It is supported by the housing 101 so that it cannot rotate (revolve) around the 102.
  • the planet roller 106 has a rolling surface 115 having an arc-shaped bus on the outer peripheral surface.
  • the planetary rollers 106 are arranged at a plurality of locations in the circumferential direction of the annular space between the solar roller 104 and the annular roller 105, and the rolling surfaces 115 are formed on the inner diameter side rolling contact surfaces 109 of the pair of solar roller elements 108. And the outer diameter side rolling contact surface 113 of the annular roller 105 is in rolling contact.
  • the pair of pressing devices 107 comprises a loading cam type pressing device that presses the pair of solar roller elements 108 in a direction approaching each other, and each of the pair of pressing devices 107 includes a cam disk 116 and a plurality of balls. It is provided with 117.
  • the cam disk 116 is externally fitted and fixed to the input shaft 102 so as to be integrally rotatable with the input shaft 102, and is mounted on the drive side on the axial side surface of the solar roller element 108 facing the driven side cam surface 110. It has a cam surface 118.
  • the drive-side cam surface 118 is formed by arranging drive-side cam recesses 119 whose axial depth changes with respect to the circumferential direction at a plurality of locations at equal intervals in the circumferential direction.
  • the ball 117 is between each of the driven side cam recesses 111 forming the driven side cam surface 110 of the solar roller element 108 and each of the driven side cam recesses 119 forming the driven side cam surface 118 of the cam disk 116. It is sandwiched one by one.
  • each of the balls 117 of the pair of pressing devices 107 has an axial depth among the driven side cam recess 111 and the driven side cam recess 119. Ride on the shallow part.
  • the axial dimension of the pair of pressing devices 107 increases, and when the pair of solar roller elements 108 are pressed in the direction approaching each other, the rolling surface of the planetary roller 106 among the inner diameter side rolling contact surfaces 109 The outer diameter of the portion that makes rolling contact with 115 becomes large.
  • the surface pressure of the traction portion (rolling contact portion) between the inner diameter side rolling contact surface 109 of the solar roller element 108 and the rolling surface 115 of the planet roller 106 increases.
  • the balls 117 of the pair of pressing devices 107 come from the bottoms of the driven side cam recess 111 and the driven cam recess 119, respectively.
  • the amount of riding is increased, and the axial dimension of the pair of pressing devices 107 is further increased.
  • the surface pressure of the traction portion between the rolling surface 115 and the inner diameter side rolling contact surface 109 and the outer diameter side rolling contact surface 113 is further increased, and excessive slippage does not occur in each traction portion. A large torque can be transmitted.
  • the surface pressures of the respective traction portions can be adjusted to the input shaft 102 and the output shaft. It is set to be automatically adjusted to an appropriate value according to the torque to be transmitted to and from 103, specifically, a value obtained by multiplying the minimum necessary value by an appropriate safety factor.
  • the limit value (limit traction coefficient ⁇ max ) of (force / normal force) is also affected by parameters other than the torque to be transmitted between the input shaft 102 and the output shaft 103.
  • the traction coefficient changes according to the temperature (oil temperature) of the traction oil supplied to the traction section. More specifically, in a normal temperature environment (for example, in an environment of 0 ° C. or higher), as the oil temperature rises, the viscosity of the traction oil decreases, so that the traction coefficient also decreases. On the other hand, in an extremely low temperature environment (for example, in an environment of less than 0 ° C.), as described in Japanese Patent Application Laid-Open No. 2016-223468, as the oil temperature decreases, the viscosity of the traction oil increases, while the viscosity increases. It is known that the traction coefficient decreases.
  • an object of the present invention is to provide a friction roller reducer having a structure capable of ensuring good transmission efficiency while preventing the occurrence of gloss slip in the traction portion. It is said.
  • the friction roller reducer of the present invention includes an input shaft, an inner diameter side rolling contact surface, an output shaft, a pair of annular roller elements, a plurality of planetary rollers, a carrier, a pressing device, and a controller. Be prepared.
  • the input shaft is rotatably supported by, for example, a housing.
  • the inner diameter side rolling contact surface is composed of an outer peripheral surface of the input shaft or a portion that rotates integrally with the input shaft, for example, an outer peripheral surface such as a solar roller supported and fixed to the input shaft.
  • the output shaft is supported coaxially with the input shaft and can rotate relative to the input shaft.
  • the pair of annular roller elements are arranged so as to be prevented from rotating about the input shaft and to have a gap between the tip surfaces facing each other.
  • Each inner peripheral surface of the pair of annular roller elements faces the inner diameter side rolling contact surface, and from the outer diameter side rolling contact surface inclined in a direction in which the inner diameter dimension increases toward the tip surface side.
  • At least one of the pair of annular roller elements is supported so as to be displaced in the axial direction, and the driven side cam surface is provided on the base end surface facing the opposite side in the axial direction from the tip surface.
  • Each of the plurality of planetary rollers has a rotating shaft arranged in parallel with the input shaft, and a rolling surface that rolls and contacts the inner diameter side rolling contact surface and the outer diameter side rolling contact surface.
  • the carrier supports the plurality of planetary rollers so as to be able to freely rotate around the rotation axis and to be displaced in the radial direction, and is integrally configured with the output shaft or the output. It is composed of members that rotate integrally with the shaft.
  • the pressing device includes a cam disc, a plurality of rolling elements, and a pressing pressure adjusting motor.
  • the cam disc is capable of relative rotation with respect to the input shaft around the input shaft, and is supported so that axial displacement is impossible, and the drive side cam surface is provided on the axial side surface facing the driven side cam surface. Have.
  • the plurality of rolling elements are sandwiched between the driven side cam surface and the driven side cam surface.
  • the push pressure adjusting motor rotates and drives the cam disc. Based on the rotational drive of the cam disk by the pressing force adjusting motor, the pressing device can press the pair of annular roller elements in a direction approaching each other.
  • the controller adjusts the rotational drive of the pressing force adjusting motor to adjust the surface of the traction portion (rolling contact portion) between the rolling surface, the inner diameter side rolling contact surface, and the outer diameter side rolling contact surface.
  • the pressure can be adjusted to the target value.
  • the friction roller reducer of the present invention can be provided with a temperature sensor that measures the temperature of the traction oil supplied to the traction unit.
  • the controller can use the temperature of the traction oil measured by the temperature sensor to calculate the target value.
  • the friction roller reducer of the present invention can be provided with a rotation speed sensor that measures the rotation speed of the output shaft.
  • the controller can use the rotation speed of the output shaft measured by the rotation speed sensor to calculate the target value.
  • the pressing device includes a drive side gear that is rotationally driven by the pressing pressure adjusting motor, and a speed reducer that has a driven side gear that meshes with the driving side gear and rotates integrally with the cam disk.
  • the drive side gear is used as a worm
  • the driven side gear is used as a worm wheel.
  • the speed reducer can be configured by a worm speed reducer.
  • the speed reducer is a worm speed reducer
  • the speed reducer preferably has a self-locking function in which the rotation of the worm wheel is not transmitted to the worm.
  • the controller substantially reduces the surface pressure of the rolling contact portion between the rolling surface and the inner diameter side rolling contact surface based on the rotational drive of the pressing force adjusting motor by adjusting the rotational drive. Can be set to 0.
  • the friction roller reducer of the present invention can be provided with a planet roller urging means that elastically urges the planet roller outward in the radial direction.
  • the friction roller reducer of the present invention may include roller element urging means for elastically urging the pair of annular roller elements in directions away from each other in the axial direction.
  • the surface pressure of the traction portion can be adjusted to an arbitrary value by adjusting the rotation amount and the rotation direction of the push pressure adjusting motor, so that the gloss slip at the traction portion It is possible to ensure good transmission efficiency while preventing the occurrence of.
  • FIG. 1 is a schematic view showing a friction roller reducer of the first example of the embodiment of the present invention in a state during normal running.
  • FIG. 2 is a schematic view showing the friction roller reducer of the first example in a state during coasting.
  • FIG. 3 (A) is a schematic view showing how the rolling element is located in the middle portion in the circumferential direction of the drive-side cam recess and the driven-side cam recess, and
  • FIG. 3 (B) is a rolling diagram.
  • FIG. 3 (C) is a schematic view showing how the moving body has moved from the position shown in FIG. 3 (A) to the side having a higher height in the axial direction among the drive-side cam recess and the driven-side cam recess.
  • FIG. 4 is a diagram similar to FIG. 2 showing the friction roller reducer of the second example of the embodiment of the present invention.
  • FIG. 5 is a diagram similar to FIG. 2 showing a friction roller reducer according to a third example of the embodiment of the present invention.
  • FIG. 6 is a cross-sectional view showing an example of a conventional structure of a friction roller reducer.
  • the friction roller reducer 1 of this example includes a housing 2, an input shaft 3, an output shaft 4, an inner diameter side rolling contact surface 5, a pair of annular roller elements 6a and 6b, and a plurality of planetary rollers 7.
  • a carrier 8, a pressing device 9, and a controller 31 are provided.
  • the input shaft 3 is supported so that the motor output shaft of the electric motor, which is the drive source of the electric vehicle, can rotate coaxially and integrally with the motor output shaft.
  • the input shaft 3 is rotatably supported inside the housing 2 by a bearing device 10.
  • the output shaft 4 is supported coaxially with the input shaft 3 and can rotate relative to the input shaft 3.
  • the output shaft 4 is a circular hollow shaft, which is arranged coaxially with the input shaft 3 around the input shaft 3 and is rotated by a pair of bearings 11a and 11b inside the housing 2. It is supported freely.
  • Each of the pair of bearings 11a and 11b is composed of, for example, an angular contact ball bearing or a tapered roller bearing in which the rolling elements are provided with contact angles in different directions.
  • the inner diameter side rolling contact surface 5 is directly formed by the outer peripheral surface of the tip portion of the input shaft 3.
  • the inner diameter side rolling contact surface 5 may be formed by the outer peripheral surface of the solar roller supported and fixed to the input shaft 3. In any case, the inner diameter side rolling contact surface 5 rotates integrally with the input shaft 3 when the input shaft 3 rotates by rotationally driving the electric motor. Further, in this example, the inner diameter side rolling contact surface 5 is formed by a concave curved surface having a single arc-shaped bus shape. However, the inner diameter side rolling contact surface 5 may be formed by a simple cylindrical surface.
  • the pair of annular roller elements 6a and 6b are coaxial with the input shaft 3 around the input shaft 3 to prevent rotation about the input shaft 3, and a gap between the tip surfaces facing each other. Is supported inside the housing 2 in a state of interposing.
  • Each of the pair of annular roller elements 6a and 6b is inclined toward the inner peripheral surface of the tip portion, facing the inner diameter side rolling contact surface 5, and increasing the inner diameter dimension toward the tip side (toward each other). It has conical surface-shaped outer diameter side rolling contact surfaces 12a and 12b.
  • one of the annular roller elements 6a (on the right side of FIGS. 1 and 2) supports the housing 2 so that it cannot rotate relative to the housing 2 and can be displaced in the axial direction.
  • the annular roller element 6a has a driven side cam surface 13 on a base end surface (right side surface in FIGS. 1 and 2) facing the side opposite to the tip surface in the axial direction.
  • the driven side cam surface 13 has an axial depth deepest at the bottom 14 and becomes shallower toward one side in the circumferential direction (upper side of FIGS. 3A to 3C). It is configured by arranging the cam recesses 15 at a plurality of locations in the circumferential direction.
  • annular roller element 6b can also be configured by a part of the housing 2.
  • Each of the plurality of planetary rollers 7 has a rotation shaft C arranged in parallel with the input shaft 3 so as to be displaced in the radial direction (radiation direction) of the input shaft 3, and has an inner diameter on the outer peripheral surface. It has a rolling surface 16 that makes rolling contact with the side rolling contact surface 5 and the outer diameter side rolling contact surfaces 12a and 12b.
  • the rolling surface 16 is composed of a convex curved surface having a single arcuate generatrix shape having a radius of curvature smaller than the radius of curvature of the generatrix shape of the inner diameter side rolling contact surface 5. Therefore, the rolling surface 16 makes rolling contact with the inner diameter side rolling contact surface 5 at the axial intermediate portion, and also makes rolling contact with the outer diameter side rolling contact surfaces 12a and 12b at both ends in the axial direction.
  • each of the planetary rollers 7 is rotatably supported by a bearing device 18 around a columnar support shaft 17 arranged coaxially with the rotation shaft C.
  • the support shaft 17 is freely supported at both ends in the axial direction with respect to the carrier 8 in the radial direction of the input shaft 3.
  • the carrier 8 freely supports each of the planetary rollers 7 to rotate about the rotation axis C and allows the input shaft 3 to be displaced in the radial direction.
  • the carrier 8 is integrally formed with the output shaft 4.
  • the carrier 8 may be configured to be formed of a member separate from the output shaft 4 and to be coupled and fixed to the output shaft 4. In any case, as the carrier 8 rotates, the output shaft 4 also rotates integrally.
  • the carrier 8 is composed of a pair of annular portions 19 that protrude outward in the radial direction from the outer peripheral surface of the output shaft 4 and are arranged at intervals in the axial direction.
  • Each of the pair of annular portions 19 is provided with recesses 20 having an oval opening shape at a plurality of locations on the inner side surfaces facing each other in the circumferential direction.
  • the recess 20 is formed on the inner side surface of the annular portion 19 so that the long axis is directed in the radial direction centered on the input shaft 3 (central axis O). Further, the recess 20 has a minor axis dimension slightly larger than the outer diameter dimension of the support shaft 17.
  • each of the planetary rollers 7 is arranged (engaged) with both ends of the support shaft 17 in the axial direction inside the recess 20 without rattling in the circumferential direction centered on the input shaft 3.
  • the input shaft 3 is supported so as to be displaced in the radial direction.
  • Each of the planetary rollers 7 is freely configured to rotate (rotate) around the rotation axis C by supporting the planet rollers 7 around the support shaft 17 via a bearing device 18.
  • the planet roller 7 is directly fitted and fixed around the support shaft 17, or the support shaft 17 and the planet roller 7 are integrally formed, and both ends of the support shaft 17 in the axial direction are formed in the recess 20. It is also possible to allow rotation (rotation) of the planetary roller 7 about the rotation axis C by rotatably arranging (engaging) the planet roller 7 by interposing a bearing inside as necessary.
  • both ends of the support shaft 17 in the axial direction are arranged (engaged) inside the recess 20 so as to be displaced in the major axis direction of the recess 20, so that each input shaft of the planetary roller 7 is engaged. It enables displacement in the radial direction of 3.
  • by supporting each of the planetary rollers 7 with respect to the carrier 8 by using a swing frame having a pair of support plate portions it is possible to displace the input shaft 3 in the radial direction.
  • both ends of the support shaft 17 in the axial direction are supported on the inner side surfaces of the pair of support plates facing each other, and the swing frame is rocked around the swing shaft eccentric with respect to the support shaft 17. It enables movement and supports the carrier 8.
  • the pressing device 9 has a function of bringing a pair of annular roller elements 6a and 6b closer to each other in the axial direction, and includes a cam disk 21, a plurality of rolling elements 22, and a pressing pressure adjusting motor 23.
  • the cam disk 21 is supported around the input shaft 3 coaxially with the input shaft 3 so as to be able to rotate relative to the input shaft 3 and the output shaft 4 and to be immovably supported by axial displacement, and is covered by the annular roller element 6a.
  • the drive-side cam surface 24 is provided on the axial side surface (left side surface of FIGS. 1 and 2) facing the drive-side cam surface 13.
  • the drive side cam surface 24 has an axial depth deepest at the bottom 25 and becomes shallower toward the other side in the circumferential direction (lower side of FIGS. 3 (A) to 3 (C)) on the drive side.
  • the cam recesses 26 are arranged at a plurality of locations in the circumferential direction.
  • the cam disc 21 is rotatably supported by a bearing 27 inside the housing 2, and has a driven side gear 28 on the outer peripheral surface.
  • the driven side gear 28 is composed of a helical gear (worm wheel) having a tooth line inclined in the axial direction.
  • Each of the plurality of rolling elements 22 is sandwiched between the driven side cam recess 15 of the driven side cam surface 13 and the drive side cam recess 26 of the drive side cam surface 24.
  • Each of the rolling elements 22 is composed of a ball or a columnar roller.
  • the pressing device 9 rides the rolling element 22 on the shallow side from the bottom 25 of the drive-side cam recess 26 and the bottom 14 of the driven-side cam recess 15 based on the rotational drive of the cam disk 21.
  • the annular roller element 6a By displacing the annular roller element 6a in the axial direction, it is possible to press the pair of annular roller elements 6a and 6b in a direction approaching each other.
  • the push pressure adjusting motor 23 rotates and drives the cam disc 21. Therefore, in this example, the drive side gear 29 that meshes with the driven side gear 28 of the cam disk 21 is supported and fixed to the motor output shaft of the push pressure adjusting motor 23.
  • the drive side gear 29 is composed of a worm having a screw-shaped tooth line. That is, in this example, the cam disk 21 is configured to be rotationally driveable by the push pressure adjusting motor 23 via the worm reducer 30 including the driven side gear 28 and the drive side gear 29.
  • the lead angle of the drive side gear 29, which is a worm is reduced so that the worm reducer 30 has a self-locking function.
  • both the driven side gear 28 and the drive side gear 29 can be spur gears or bevel gears.
  • the cam disc is provided by the push pressure adjusting motor 23. 21 can also be configured to be rotationally driveable.
  • the pressing force adjusting motor 23 is composed of an electric motor capable of positioning control such as a stepping motor and a DC motor.
  • the controller 31 is driven by the rotation of the pressing force adjusting motor 23, specifically, by adjusting the amount of rotation and the direction of rotation, the rolling surface 16 of the planetary roller 7 and the inner diameter side rolling contact of the input shaft 3 It has a function of adjusting the surface pressure of the traction portion with the outer diameter side rolling contact surfaces 12a and 12b of the surfaces 5 and the pair of annular roller elements 6a and 6b to a target value.
  • the controller 31 adjusts the rotation amount and the rotation direction of the pressing force adjusting motor 23 to adjust the rotation amount and the rotation direction of the cam disk 21, and the bottom 25 of the drive-side cam recess 26 of the rolling element 22.
  • the ride volume d 2 from ride amount d 1
  • the driven-side bottom portion 14 of the cam recess 15 from displaces the annular roller elements 6a in the axial direction.
  • the planet roller 7 is displaced in the radial direction of the input shaft 3.
  • the cam disk 21 is rotationally driven in a predetermined direction (above FIG. 3A and FIG. 3B), and the rolling element 22 is driven. of, to increase the ride volume d 2 from the bottom 14 of the ride volume d 1 and driven cam recess 15 from the bottom 25 of the driven cam recess 26, an annular roller elements 6a, approaches the annular roller element 6b Displace in the direction (to the left of FIGS. 1 and 2).
  • a centrifugal force acts on the planet roller 7 with the rotation (revolution) of the planet roller 7 about the input shaft 3, and based on this centrifugal force, the outer diameter side rolling contact from the rolling surface 16.
  • An outward force is applied to the surfaces 12a and 12b with respect to the radial direction of the input shaft 3. Since the outer diameter side rolling contact surfaces 12a and 12b are conical surfaces, an annular force is applied from the rolling surface 16 to the outer diameter side rolling contact surfaces 12a and 12b in the radial direction of the input shaft 3.
  • a component force acts on the roller element 6a in the direction away from the annular roller element 6b (to the right in FIGS. 1 and 2).
  • annular roller elements 6a is a rolling element 22, while reducing the ride volume d 2 from the bottom 14 of the ride volume d 1 and driven cam recess 15 from the bottom 25 of the driven cam recess 26, annular It is displaced in the direction away from the roller element 6b.
  • the planetary roller 7 is allowed to be displaced outward with respect to the radial direction of the input shaft 3, and among the outer diameter side rolling contact surfaces 12a and 12b of the pair of annular roller elements 6a and 6b, the planetary roller 7 is allowed to be displaced outward.
  • the outer diameter of the portion that makes rolling contact with the rolling surface 16 of 7 is increased.
  • the controller 31 has the torque (transmission torque) transmitted between the input shaft 3 and the output shaft 4, as well as the temperature of the traction oil (oil temperature), the input shaft 3, the output shaft 4 and / or the planet. It is configured to set the target value of the surface pressure of each traction unit in consideration of parameters other than the transmission torque such as the rotation speed (rotation speed) of the roller 7. For this purpose, experiments and simulations are conducted in advance on the relationship between the parameter including the transmission torque and the appropriate value of the surface pressure of the traction unit according to the parameter, that is, the value obtained by multiplying the minimum necessary value by an appropriate safety factor. It is obtained by such means, and is stored in the memory of the controller 31 as a map, a calculation formula, or the like.
  • the friction roller reducer 1 When the friction roller reducer 1 is in operation, parameters such as transmission torque and oil temperature are measured by various sensors (not shown), and the output values of these sensors are input to the controller 31.
  • the controller 31 obtains an appropriate value (target value) of the surface pressure of the traction unit according to the output values of various sensors based on a map, a calculation formula, or the like stored in the memory.
  • the controller 31 adjusts the rotation direction and the amount of rotation of the pressing force adjusting motor 23 in order to adjust the surface pressure of the traction portion to the target value thus obtained, and adjusts the axial position of the annular roller element 6a. Adjust.
  • the output torque of the electric motor can be used as the transmission torque among the input parameters to the map and calculation formula.
  • the transmission torque may be obtained by measuring the rotational torque of the input shaft 3 or the output shaft 4 with a torque sensor.
  • a torque sensor for example, a magnetostrictive torque sensor arranged around the input shaft 3 or the output shaft 4, or an encoder is supported at two positions separated from each other in the axial direction of the input shaft 3 or the output shaft 4.
  • a pulse phase difference type torque sensor or the like in which a magnetostrictive element is opposed to each of the encoders can be used.
  • the oil temperature is measured by a temperature sensor installed at an arbitrary position in the traction oil circulation path, such as near a nozzle that sprays traction oil toward the traction section.
  • the rotation speed of the input shaft 3, the output shaft 4 and / or the planet roller 7 is, for example, the rotation of the magnetic detection element facing the encoder supported and fixed to the input shaft 3, the output shaft 4 and / or the planet roller 7. It can be measured by a speed sensor. If the rotation speeds of the input shaft 3, the output shaft 4, and the planet roller 7 are measured independently, the amount of slippage at each traction unit can be obtained, which is preferable.
  • the controller 31 prepares the rotational drive of the push pressure adjusting motor 23 to control the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 of the input shaft 3 and the rolling surface 16 of the planet roller 7.
  • the planet The rolling surface 16 of the roller 7 is separated from the inner diameter side rolling contact surface 5 of the input shaft 3, and a gap 34 is created between the rolling surface 16 and the inner diameter side rolling contact surface 5, so that the output shaft 4 becomes the input shaft 3 It becomes possible to idle.
  • the magnitude of the pressing force generated by the pressing device 9 can be adjusted to an arbitrary value by adjusting the rotational drive amount of the pressing force adjusting motor 23, so that the rolling surface 16
  • the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 and the outer diameter side rolling contact surfaces 12a and 12b can be adjusted to an arbitrary value.
  • the surface pressure of the traction unit is added to the traction oil temperature (oil temperature), the input shaft 3, the output shaft 4 and / or the planetary roller. It can be adjusted to an appropriate value in consideration of parameters other than the transmission torque, such as the rotation speed (rotation speed) of 7. Therefore, it is possible to prevent the occurrence of gloss slip in each traction portion without excessively increasing the safety factor regarding the traction coefficient, and it is possible to ensure good transmission efficiency of the friction roller reducer 1. ..
  • the relationship between conditions such as transmission torque and oil temperature and the target value of the surface pressure of the traction unit according to the conditions is obtained by conducting experiments and simulations in advance. Therefore, it is considered that not only the parameters directly measured by various sensors but also the elastic deformation of each member under the parameters, the slippage in the traction portion, the influence of the skew of the planetary roller 7 and the like can be considered. However, it is also possible to measure the inclination of the rotation axis C of the planetary roller 7 with a displacement sensor and use the output value of the displacement sensor to calculate the target value of the surface pressure of the traction unit.
  • the inclination of the rotation axis C is measured by abutting the tip of the stylus (probe) of the displacement sensor at two positions on the axial side surface of the planetary roller 7, preferably two positions on the opposite side in the radial direction. can do.
  • the worm reducer 30 since the worm reducer 30 has a self-locking function, even if the pressing force adjusting motor 23 is stopped after adjusting the surface pressure of the traction portion to the target value, the ring is formed. The axial position of the roller element 6a can be held.
  • the controller 31 of the friction roller reducer 1 of this example has a function of making the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 of the input shaft 3 and the rolling surface 16 of the planetary roller 7 substantially zero. Has. Therefore, by activating this function when the accelerator is off, such as during high-speed cruising, the mileage due to coasting can be lengthened. That is, when the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 and the rolling surface 16 is substantially set to 0 during coasting, the output shaft 4 rotates as the wheels rotate, and the planet roller 7 rotates. , Rotates (revolves) around the input shaft 3.
  • the planetary roller 7 Due to the action of centrifugal force based on the revolution of the planetary roller 7, the planetary roller 7 is displaced outward in the radial direction while the annular roller element 6a is displaced in the direction away from the annular roller element 6b, and the rolling surface 16 of the planetary roller 7 is displaced. Is separated from the inner diameter side rolling contact surface 5 of the input shaft 3, and a gap 34 is formed between the rolling surface 16 and the inner diameter side rolling contact surface 5.
  • the output shaft 4 can idle with respect to the input shaft 3, the rotational resistance of the wheels can be suppressed low during coasting, and the electric vehicle equipped with the friction roller reducer 1 can be suppressed.
  • the electricity cost performance can be improved.
  • FIG. 4 shows a second example of the embodiment of the present invention.
  • the friction roller reducer 1a of this example further includes a planet roller urging means 32 that elastically urges the planet roller 7 outward in the radial direction of the input shaft 3.
  • the planetary roller urging means 32 of this example has an elastic member such as a compression coil spring between the inner end of the recess 20 in the radial direction of the input shaft 3 and both ends of the support shaft 17 in the axial direction. It is configured by sandwiching it in an elastically compressed state.
  • the planetary roller 7 rolls when the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 and the rolling surface 16 is substantially set to 0 during coasting.
  • the surface 16 can be reliably separated from the inner diameter side rolling contact surface 5 of the input shaft 3.
  • the function of making the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 and the rolling surface 16 substantially zero is activated, and the rolling element 22 is moved to the driven side cam.
  • the output shaft 4 may not idle with respect to the input shaft 3. That is, when the rotation speed of the output shaft 4 is slow, the centrifugal force applied to the planetary roller 7 is small and the axial component force acting on the annular roller element 6a is small, so that the annular roller element 6a is separated from the annular roller element 6b. It may not be displaced in the direction and the rolling surface 16 may not be separated from the inner diameter side rolling contact surface 5.
  • the planet roller urging means 32 elastically urges the planet roller 7 outward in the radial direction of the input shaft 3, so that the inner diameter side
  • the function of making the surface pressure of the traction portion between the rolling contact surface 5 and the rolling surface 16 substantially 0 is activated, the rolling surface 16 is brought into inner diameter side rolling contact regardless of the rotation speed of the output shaft 4. It can be easily separated from the surface 5.
  • the composition and action of other parts are the same as in the first example.
  • FIG. 5 shows a third example of the embodiment of the present invention.
  • the friction roller reducer 1b of this example further includes a roller element urging means 33 that elastically urges the annular roller element 6a in a direction away from the annular roller element 6b.
  • the roller element urging means 33 of this example is configured by sandwiching an elastic member such as a compression coil spring between the tip surfaces of a pair of annular roller elements 6a and 6b in an elastically compressed state. ..
  • the planetary roller 7 rolls when the surface pressure of the traction portion between the inner diameter side rolling contact surface 5 and the rolling surface 16 is substantially zero during coasting.
  • the surface 16 can be easily separated from the inner diameter side rolling contact surface 5 of the input shaft 3.
  • the structure of this example can be implemented in combination with the structure of the second example. That is, the friction roller reducer of the present invention can simultaneously include the planetary roller urging means 32 and the roller element urging means 33.
  • the composition and action of other parts are the same as in the first and second examples.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
PCT/JP2020/000683 2019-03-20 2020-01-10 摩擦ローラ減速機 Ceased WO2020188967A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN202080021733.7A CN113574294B (zh) 2019-03-20 2020-01-10 摩擦辊减速器
US17/440,950 US11867262B2 (en) 2019-03-20 2020-01-10 Frictional roller reducer
EP20773638.0A EP3943779A4 (en) 2019-03-20 2020-01-10 FRICTION ROLLER REDUCER
JP2021506189A JPWO2020188967A1 (https=) 2019-03-20 2020-01-10

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JP2019-053690 2019-03-20
JP2019053690 2019-03-20

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EP (1) EP3943779A4 (https=)
JP (1) JPWO2020188967A1 (https=)
CN (1) CN113574294B (https=)
WO (1) WO2020188967A1 (https=)

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JP7148025B1 (ja) * 2020-12-07 2022-10-05 日本精工株式会社 摩擦ローラ減速機
JP2023066534A (ja) * 2021-10-29 2023-05-16 日本精工株式会社 摩擦ローラ減速機およびその製造方法
CN116601409A (zh) * 2020-12-07 2023-08-15 日本精工株式会社 摩擦辊减速机

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Publication number Priority date Publication date Assignee Title
JP7148025B1 (ja) * 2020-12-07 2022-10-05 日本精工株式会社 摩擦ローラ減速機
CN116601409A (zh) * 2020-12-07 2023-08-15 日本精工株式会社 摩擦辊减速机
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JP2023066534A (ja) * 2021-10-29 2023-05-16 日本精工株式会社 摩擦ローラ減速機およびその製造方法

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CN113574294B (zh) 2024-07-26
CN113574294A (zh) 2021-10-29
US11867262B2 (en) 2024-01-09
EP3943779A4 (en) 2022-11-09
US20220221031A1 (en) 2022-07-14
EP3943779A1 (en) 2022-01-26

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