WO2010004880A1 - Démultiplicateur et dispositif de distribution à soupape variable l'utilisant - Google Patents

Démultiplicateur et dispositif de distribution à soupape variable l'utilisant Download PDF

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Publication number
WO2010004880A1
WO2010004880A1 PCT/JP2009/061616 JP2009061616W WO2010004880A1 WO 2010004880 A1 WO2010004880 A1 WO 2010004880A1 JP 2009061616 W JP2009061616 W JP 2009061616W WO 2010004880 A1 WO2010004880 A1 WO 2010004880A1
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WO
WIPO (PCT)
Prior art keywords
output shaft
shaft
ball
housing
input
Prior art date
Application number
PCT/JP2009/061616
Other languages
English (en)
Japanese (ja)
Inventor
光司 佐藤
隆英 齋藤
大介 今田
雅文 中小路
哲 山形
恵介 数野
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
Priority claimed from JP2008215547A external-priority patent/JP5376288B2/ja
Priority claimed from JP2009091204A external-priority patent/JP5180135B2/ja
Priority claimed from JP2009093892A external-priority patent/JP5354186B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to DE112009001645T priority Critical patent/DE112009001645T5/de
Publication of WO2010004880A1 publication Critical patent/WO2010004880A1/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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/022—Chain drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34409—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by torque-responsive means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/10—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing
    • F16D41/105—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing the intermediate members being of circular cross-section, of only one size and wedging by rolling movement not having an axial component between inner and outer races, one of which is cylindrical
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
    • F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2301/00—Using particular materials
    • F01L2301/02—Using ceramic materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the present invention relates to a speed reducer that decelerates rotation of an input shaft and transmits it to an output shaft, and a variable valve timing device to which this is applied.
  • a speed reducer is known as a device that drives a counterpart machine connected to an output shaft by decelerating and transmitting the rotation of an input shaft that receives a driving force from a drive source such as an electric motor.
  • an input shaft 72 and an output shaft 73 rotatably supported by a housing 71 as shown in FIG. 23 and an internal gear 74 fixed in the housing 71 are arranged coaxially.
  • a plurality of rollers 76 are arranged between a ball bearing 78 and an internal gear 74 mounted on the outer periphery of an eccentric shaft portion 75 provided on the input shaft 72 (see Patent Document 1). ).
  • the number of rollers 76 between the eccentric shaft portion 75 and the internal gear 74 is smaller than the number of teeth of the internal gear 74, and is provided on the outer periphery of the eccentric shaft portion 75 by the roller retainer portion 77.
  • the output shaft 73 and the roller retainer portion 77 are integrated with each other so as to be in contact with the ball bearing 78 at intervals in the circumferential direction.
  • each roller 76 is one tooth in the other direction with respect to the teeth of the internal gear 74. Only revolve. Due to the revolution of the roller 76, the rotation of the reduction ratio corresponding to the number of teeth of the internal gear 74 is transmitted to the output shaft 73 via the roller holder 77.
  • the cage for holding the balls of the ball bearing 78 includes two annular holding plates in which concave portions having spherical inner surfaces are formed at regular intervals in the circumferential direction. And the opening side of the concave portion of the other annular holding plate is opposed to each other, and a pocket for accommodating the balls is formed between the concave portions.
  • the inner surface of the recess is spherical and is in surface contact with the surface of the ball.
  • speed reducers that decelerate the rotation of the input shaft that receives driving force from a drive source such as an electric motor and transmit it to the output shaft are used in many fields.
  • a reduction gear is applied to obtain a large force that changes the relative phase between a crankshaft and a camshaft that drives an intake valve and an exhaust valve.
  • a camshaft that drives a valve of an engine and a sprocket that receives rotation from the engine and drives the camshaft to rotate are arranged coaxially so that they can rotate relative to each other.
  • the rotation of the output shaft of the electric motor placed on the same axis as the shaft is transmitted to the camshaft through the speed reduction mechanism, and the camshaft is rotated relative to the sprocket to change the rotational phase difference between the two, thereby opening and closing the valve.
  • variable valve timing device to which the speed reduction device described in Patent Document 1 is applied as a speed reduction mechanism
  • the reverse input torque is output to the output shaft of the electric motor. And its output shaft is rotated.
  • the electric motor is continuously energized so that the output shaft of the electric motor does not rotate and the input torque is applied or the output shaft of the electric motor is not rotated continuously. It is necessary to energize.
  • an object of the present invention is to prevent the reverse input torque that has acted on the output shaft of the speed reducer from being transmitted to the input shaft.
  • the speed reducer includes an input shaft and an output shaft that are rotatably supported by a housing, and an internal gear that is fixed to the housing, and is arranged coaxially.
  • a plurality of rollers are arranged between the eccentric shaft portion having a circular cross section provided on the shaft and the internal gear, and each of these rollers is rotatably held by a roller holder portion that rotates integrally with the output shaft,
  • the decelerating device that transmits the rotation of the input shaft to the output shaft via a roller cage section, the output shaft against the reverse input torque acting on the output shaft between the input shaft and the output shaft.
  • a configuration is provided in which locking means for locking the housing to the housing and unlocking means for releasing the locked state by the locking means with respect to the input torque acting on the input shaft are employed.
  • the locking means and unlocking means are provided between the input shaft and the output shaft, when the load is applied to the output shaft and reverse input torque is applied to the output shaft, the output shaft is It is possible to lock and prevent transmission to the input shaft. On the other hand, the input torque from the input shaft is released by the lock release means, and the input torque is transmitted to the output shaft.
  • the locking means forms a plurality of wedge-shaped spaces narrowing in both circumferential directions between the housing and the output shaft, and a pair of engagement elements in the respective wedge-shaped spaces by the engagement cage retainer.
  • the lock release means is connected to the housing and the output shaft so as to be detachable, and the engagement holder portion is connected to rotate integrally with the roller holder portion, and an input torque is applied to the input shaft.
  • the engagement holder portion presses one of the pair of engagement elements toward the wide side of the wedge-shaped space to release the engagement with the housing and the output shaft. It is possible to adopt a configuration that is the same.
  • the rotation of the output shaft to which reverse input torque has been applied causes the engagement member at the rear in the rotation direction of the pair of engagement elements in the wedge-shaped space to engage with the output shaft and the housing by the wedge effect.
  • the output shaft is locked with respect to the housing, and it is possible to reliably prevent the reverse input torque acting on the output shaft from being transmitted to the input shaft.
  • the engagement holder portion since the engagement holder portion is connected so as to rotate integrally with the roller holder portion, the engagement piece holder portion rotates as the roller holder portion rotates.
  • the rotating retainer retainer portion presses the engagement element rearward in the rotation direction of the pair of engagement elements toward the wide side of the wedge-shaped space, and the engagement state by the engagement element is released.
  • the output shaft and the roller holder unit can be integrated as in the conventional reduction gear. You may form integrally with a holder
  • the output shaft that transmits the rotation of the input shaft through the integral holder is the roller holder like the output shaft of the conventional speed reducer. No complicated processing is required to make the structure integral with the part. For this reason, a processing cost is suppressed and the manufacturing cost of the reduction gear is suppressed.
  • an elastic member is disposed between the pair of engaging elements, and the elastic members are used to press the engaging elements on both sides toward the narrow side of the wedge-shaped space so as to be engaged with the housing and the output shaft. You may employ
  • the elastic member disposed between the pair of engaging elements presses the engaging elements on both sides in the direction in which the engaging elements on both sides are engaged with the housing and the output shaft, that is, the direction in which the wedge-shaped space is narrowed. For this reason, when the output shaft rotates, the output shaft is immediately locked with respect to the housing, and the function of locking the output shaft to the housing is stabilized.
  • the locking means of the speed reducer includes an engaging portion in which a coil spring is fitted into a position of the inner periphery of the housing facing the outer periphery of the output shaft, and the output shaft can be engaged with both ends of the coil spring.
  • the engaging portion of the output shaft engages with either one of the ends of the coil spring to expand the diameter of the coil spring.
  • the lock releasing means is provided with a protrusion protruding in the axial direction on the roller retainer portion, and when the input torque is applied to the input shaft, the protrusions are arranged at both ends of the coil spring. The structure which presses any one edge part of these and shrinks the diameter of the coil spring is employable.
  • this locking means when the reverse input torque acts and the output shaft tries to rotate, the engaging portion engages with one end of the coil spring and presses the coil spring in the direction of expanding the diameter. .
  • a frictional resistance is generated between the coil spring whose diameter has been expanded by the pressing and the inner peripheral surface of the housing, and the output shaft is locked to the housing, so that the rotation of the output shaft on which reverse input torque acts can be prevented. .
  • this unlocking means when the roller cage part rotates by the rotation of the input shaft, the protrusion engages with one of the two end parts of the coil spring.
  • the protrusion engaged with the end of the coil spring presses the coil spring in a direction to reduce the diameter of the coil spring, and releases the locked state between the housing and the output shaft due to the diameter expansion of the coil spring.
  • the said structure WHEREIN The edge part of the said coil spring pressed by the protrusion of the said roller holder
  • retainer part is provided so that engagement with the engaging part of the said output shaft is possible, and the said protrusion is via the edge part of the said coil spring. You may make it press the engaging part of the said output shaft.
  • the input torque is transmitted to the output shaft through the end of the coil spring by the protrusion of the roller holder portion that unlocks the output shaft, so that the transmission of the input torque to the output shaft is performed.
  • the locking means in the speed reducer includes a cam plate that rotates integrally with the output shaft so as to be axially displaceable, and rotates integrally with the roller retainer portion facing the cam plate.
  • An annular rotating body connected coaxially, a circumferential cam groove formed on both surfaces of the cam plate and the annular rotating body, and rolling between the cam grooves to rotate the cam plate and the annular rotation.
  • the lock release means engages the ball with the cam plate and the annular rotating body when an input torque is applied to the input shaft, and the cam plate Is displaced in the other axial direction is spaced apart from the contact surface of the internal gear, the said cam plate and said annular rotary body it is possible to adopt a configuration is intended to be integrally rotated.
  • the cam plate when reverse input torque is applied to the output shaft, the cam plate is pressed in the axial direction by the elastic member and pressed against the contact surface formed on the internal gear, thereby generating frictional resistance on the cam plate.
  • the cam plate is fixed to the internal gear, and the rotation of the output shaft on which the reverse input torque acts can be prevented.
  • the unlocking means when input torque is applied to the input shaft, the ball is engaged with the annular rotating body and the cam plate, so that the cam plate is displaced in the other axial direction so that the contact surface of the internal gear Separate. As a result, the annular rotating body and the cam plate rotate integrally, and the rotation of the input shaft is transmitted to the output shaft.
  • the internal gear has the contact surface at the other axial end, the contact surface is tapered, and the cam plate has a tapered shape along the contact surface at a position opposed to the contact surface.
  • the tapered pressing surface of the cam plate is pressed against the tapered contacting surface of the internal gear, so that the contact area between the contact surface and the pressing surface can be further increased.
  • the annular rotating body is formed integrally with the roller holder part, the number of parts can be reduced, the manufacturing cost of the speed reducer can be suppressed, and the structure can be simplified.
  • the internal gear having a plurality of cam ridges formed at equal pitches in the circumferential direction is provided on the inner diameter surface of the cylindrical portion of the housing so as to face the eccentric shaft portion, and the opposed eccentric shafts.
  • the output shaft having the roller holder portion that holds the plurality of rollers that are in rolling contact with the outer diameter surface of the portion and the internal gear is disposed, and the roller holder portion is divided at an equal pitch in the circumferential direction.
  • Pockets for holding the rollers are provided at positions where all or some of the dividing points differ from the number of the cam crests by one, and a portion corresponding to one pitch of the cam crests is provided.
  • rollers are matched with the outer diameter side envelope of the trajectory in which the roller held in the pocket revolves along the outer diameter surface of the eccentric shaft portion when the input shaft is rotated.
  • a reverse input inhibition means inhibits the reverse input to the input shaft.
  • the reverse input suppression means As the reverse input suppression means, a negative clearance is set in the rolling bearing that supports the input shaft, and rotational resistance is applied to the rolling bearing, and the reverse input suppression means is a rolling that supports the input shaft. Provided with a contact seal on the bearing to provide rotational resistance to the rolling bearing, or to provide rotational resistance to the roller by making the width of the pocket of the roller cage part equal to or less than the diameter of the roller Can be adopted.
  • the inventor of the present invention analyzes the reduction gear, and as a result, in order to effectively improve the torque transmission efficiency of the reduction gear, the rotation of a ball bearing provided on the outer periphery of the eccentric shaft portion It has been found that reducing the torque is very important.
  • the following configuration may be adopted for the ball bearing.
  • a ball bearing is provided on the outer periphery of the eccentric shaft portion, and as a cage for holding the ball of the ball bearing, two concave portions having inner surfaces formed by a plurality of planes are formed at regular intervals in the circumferential direction. Adopting an annular holding plate, forming an opening side of the concave portion of one annular holding plate and an opening side of the concave portion of the other annular holding plate to form a pocket having a polygonal cross section between the concave portions, The ball is stored in the pocket.
  • a cage comprising two annular holding plates in which concave portions having a spherical inner surface are formed at regular intervals in the circumferential direction, and the opening side of the concave portion of one of the annular holding plates is adopted.
  • a pocket for accommodating the ball may be formed between the concave portions of the other annular holding plate facing each other, and a protrusion that makes point contact with the ball may be formed on the inner surface of the concave portion.
  • the above-mentioned cage one comprising two annular holding plates formed with concave portions at a constant interval in the circumferential direction is adopted, and the opening side of the concave portion of one of the annular holding plates and the other annular holding plate are adopted.
  • the part which the ball contacts in the part where the opening side of the concave part of the plate is made to face and the pocket for accommodating the ball is formed between the concave parts, and the ball on the inner surface of the concave part does not contact when the ball bearing rotates.
  • a through-hole may be formed at a site that is in a direction opposite to the traveling direction of the balls.
  • lubricant tends to accumulate due to the centrifugal force caused by the rotation of the ball from the part that contacts the ball on the inner surface of the recess to the direction opposite to the traveling direction of the ball, and the ball bearing rotates due to the viscous resistance of the lubricant.
  • the torque tends to increase. Therefore, when the through-hole is formed, the lubricant accumulated between the inner surface of the recess and the ball is pushed out of the through-hole by the centrifugal force due to the rotation of the ball, and the viscous resistance of the lubricant is suppressed.
  • the rotational torque of the ball bearing is less likely to increase even when subjected to centrifugal force due to the center deviation.
  • each of the recesses so as to be symmetrical on the front side and the rear side in the traveling direction of the balls.
  • a through-hole is formed at a portion close to the ball traveling direction from the portion where the ball on the inner surface of the recess contacts. Yes, the lubricant accumulated between the inner surface of the recess and the ball is effectively discharged from the through hole by the centrifugal force caused by the rotation of the ball.
  • a variable valve timing device includes a camshaft that drives at least one of an intake valve and an exhaust valve of an engine, rotation transmitted from the engine, and rotation of the camshaft.
  • a sprocket to be driven is arranged coaxially so as to be relatively rotatable, and the rotation of the output shaft of the electric motor arranged coaxially with the camshaft is transmitted to the camshaft via a reduction mechanism,
  • the speed reduction mechanism is the speed reduction device described above, and the output shaft of the electric motor and the camshaft are A configuration using the input shaft and the output shaft of the reduction gear can be employed.
  • the eccentric shaft portion revolves around the shaft center of the output shaft of the electric motor in the same direction, and each roller has one tooth relative to the teeth of the internal gear.
  • the roller holder part that revolves by the amount and holds these rollers rotates.
  • variable valve timing device In general, in a variable valve timing device, if the drive source for operating the speed reduction mechanism is an electric motor, the camshaft is loaded for some reason and reverse input torque is applied to the output shaft of the electric motor. Torque is transmitted and its output shaft is rotated. For this reason, it is necessary to keep the electric motor energized and to apply the input torque so that the output shaft does not rotate.
  • variable valve timing device of the present invention can perform the deceleration of the rotation of the output shaft of the electric motor and the transmission of the decelerated rotation to the camshaft by the above-described reduction device that is a reduction mechanism.
  • the structure can be simplified.
  • locking means and unlocking means for releasing the locked state by the locking means, and suppressing reverse input to the output shaft of the electric motor. Since the speed reduction device provided with the reverse input suppression means is applied, transmission of the reverse input torque to the output shaft of the electric motor can be prevented.
  • Sectional drawing which shows 1st Embodiment of the reduction gear device which concerns on this invention Sectional view along the line AA in FIG. Sectional view along the line BB in FIG.
  • Sectional drawing which shows 2nd Embodiment same as the above Sectional view along line CC in FIG. The perspective view which shows the principal part of 2nd Embodiment of a reduction gear.
  • Expanded sectional view showing the locked state of the output shaft The expanded sectional view which shows the lock release state of an output shaft same as the above Sectional drawing which shows 3rd Embodiment of a reduction gear device
  • FIG. 15A A Main part expanded sectional view which shows the locked state along the DD line of FIG. 10, (b) Main part expanded sectional view which shows the lock release state same as the above. Partially omitted vertical sectional view showing a modification of the ball bearing supporting the input shaft of the first embodiment of the reduction gear
  • the cross-sectional enlarged view which shows the roller holding state of a roller holder part same as the above 1 is an enlarged cross-sectional view of the vicinity of a deep groove ball bearing mounted on the outer periphery of the eccentric shaft portion of FIG. 15A is a cross-sectional view along a cylindrical surface passing through the center of each ball of the deep groove ball bearing of FIG. 15, and FIG.
  • 15B is an enlarged cross section in the vicinity of the inner surface of the recess showing the state of the deep groove ball bearing shown in FIG. Figure (A) Sectional drawing which shows the modification of the deep groove ball bearing of FIG. 16, (b) The expanded sectional view of the protrusion vicinity of the inner surface of the recessed part which shows the state at the time of rotation of the deep groove ball bearing shown to (a) (A) Sectional drawing which shows the modification of the deep groove ball bearing of FIG. 16, (b) The expanded sectional view of the through-hole vicinity of the inner surface of the recessed part which shows the state at the time of rotation of the deep groove ball bearing shown to (a) (A) Sectional drawing which shows the modification of the deep groove ball bearing of FIG.
  • the reduction gear 10 of the first embodiment includes an input shaft 12 and an output shaft 13 that are rotatably supported by a cylindrical housing 11, and an internal gear 14 that is fixed to the housing 11. It is arranged coaxially.
  • the housing 11 is formed by fitting cylindrical bodies divided in the axial direction by known means such as bolts (not shown), and the input shaft 12 and the output shaft 13 are rotatably supported at both ends thereof on the same axis. Has been.
  • the input shaft 12 is rotatably supported by a pair of bearings 15 and 16 at one end portion of the housing 11 and the large-diameter portion 13b of the output shaft 13. Between the bearings 15 and 16 of the input shaft 12, a pair of eccentric shaft portions 17 and 17 are provided integrally with the input shaft 12 at two locations in the axial direction.
  • the bearing 15 that supports the input shaft 12 is provided with contact seals 15c at both ends of the outer ring 15a.
  • contact seals 15c By bringing these contact seals 15c into contact with the inner ring 15b, rotational resistance is imparted to the bearing 15, and reverse input from the output shaft 13 to the input shaft 12 is suppressed.
  • the contact-type seal 15c can be attached only to one axial direction.
  • Each eccentric shaft portion 17 has a circular cross section, the center of the circle of each eccentric shaft portion 17 is at a position shifted from the axis of the input shaft 12, and the center of the circle of one eccentric shaft portion 17 and the other eccentricity.
  • the shaft portion 17 is eccentric so as to sandwich the axis of the input shaft 12 between the center of the circle of the shaft portion 17.
  • a deep groove ball bearing 18 is mounted on the outer periphery of each eccentric shaft portion 17 by press fitting.
  • the internal gear 14 is fixed in the housing 11, and is coaxially disposed with respect to the input shaft 12 at a position opposed to the outer periphery of the deep groove ball bearing 18 of the pair of eccentric shaft portions 17.
  • Fifty teeth 19 are formed at a constant pitch in the circumferential direction on the inner peripheral portion of the internal gear 14, and the tooth gap between the teeth 19 has a curved cross-sectional shape.
  • a plurality of rollers 21 are held at a constant circumferential pitch by a cylindrical roller cage portion 22 between the inner circumferential portion of the internal gear 14 and the deep groove ball bearing 18 of both eccentric shaft portions 17. .
  • the pockets 23 for holding these rollers 21 are provided at 13 positions which are thinned out every third with respect to the dividing points when the roller cage portion 22 is divided into 51 equal parts in the circumferential direction. The number of points is one more than the teeth 19.
  • the shape of the tooth gap between the teeth 19 (the tooth gap corresponding to one pitch of the teeth 19) is such that when the input shaft 12 is rotated, the roller 21 held in the pocket 23 is This coincides with the outer diameter side envelope of the trajectory revolving along the outer peripheral portion of the outer ring of the deep groove ball bearing 18 fitted to the outside. Further, all the rollers 21 are in contact with the outer periphery of the deep groove ball bearing 18, and a part thereof is in contact with the teeth 19 of the internal gear 14.
  • the relationship between the number of teeth of the internal gear 14 and the number of rollers 21 is not limited to the case shown in FIG. 2, but is set based on the reduction ratio determined by experiment and actual operation.
  • the roller retainer portion 22 has pockets 23 for accommodating the rollers 21 in a rollable manner in the circumferential direction, and the formed pockets 23 are arranged in two rows in the axial direction with a half-pitch deviation from the fixed pitch. (See FIG. 4).
  • the circumferential width of the pocket 23 of the roller holder 22 is formed such that the roller 21 to be held can roll, as shown in FIG.
  • the size may be set to be equal to or less than the diameter of the roller 21, and a rotational resistance may be applied to the roller 21 to indirectly suppress reverse input from the output shaft 13 to the input shaft 12.
  • the output shaft 13 is integrally formed with a small-diameter portion 13a at one end thereof (an end facing the input shaft 12) and a large-diameter portion 13b positioned on the tip side of the small-diameter portion 13a.
  • the small diameter portion 13a is rotatably supported by bearings 24 at two axial positions on the other end of the housing 11.
  • the large-diameter portion 13b of the output shaft 13 has a cylindrical shape, and the other end portion of the input shaft 12 is rotatably supported by a bearing 16 provided on the inner peripheral portion thereof.
  • the large-diameter portion 13b is provided with a hole 13d penetrating in the axial direction, and the switch pin 20 is fitted into the hole 13d so as to partially protrude toward the small-diameter portion 13a.
  • cam surfaces 13 c are formed at equal intervals in four circumferential directions on the outer peripheral portion of the large diameter portion 13 b of the output shaft 13.
  • the cam surface 13c is flat and forms a wedge-shaped space 25 that gradually narrows in both circumferential directions between the housing 11 and the large-diameter portion 13b of the output shaft 13.
  • the wedge-shaped space 25 may be formed by providing a cam surface 13 c on the inner peripheral portion of the housing 11.
  • each wedge-shaped space 25 a pair of rollers 26 as engaging members are arranged with a leaf spring 27 as an elastic member interposed therebetween, and the pair of rollers 26 engages / disengages with the housing 11 and the large diameter portion 13b of the output shaft 13. It is possible.
  • the leaf spring 27 presses the rollers 26 on both sides thereof toward the narrowed side (narrow side) of the wedge-shaped space 25 and biases it in a direction to engage with the housing 11 and the large diameter portion 13b of the output shaft 13. ing.
  • a cylindrical engagement cage portion 28 is disposed between the large diameter portion 13b of the output shaft 13 and the housing 11.
  • This engagement holder portion 28 constitutes a lock release means, and a pocket 29 is formed at a position corresponding to the wedge-shaped space 25, and a pair of rollers 26 has a gap in the pocket 29 with respect to the inner wall in the circumferential direction of the pocket 29. Is housed.
  • a pair of sprags can be used in place of the pair of rollers 26 as engaging elements in order to securely lock the output shaft 13 against the reverse input torque. That is, when a plurality of pairs of sprags are tiltably held between the output shaft 13 and the housing 11 by the engaging cage holder 28 and the output shaft 13 rotates, either one of the pair of sprags is output shaft 13. And may engage with the housing 11.
  • the roller cage portion 22 and the engagement cage portion 28 are formed as an integrated cage 30 that is coaxially integrated by, for example, pressing.
  • the integrated retainer 30 By forming the integrated retainer 30 by press working, the engagement retainer portion 28 can be rotated integrally with the roller retainer portion 22, the number of parts can be reduced, and the manufacturing cost can be suppressed.
  • a radially inward flange 31 is formed at the other end of the integral retainer 30 on the side of the engagement cage portion 28, and the flange 31 has a radially outward cutout groove 32.
  • the switch pin 20 fitted to the output shaft 13 is engaged with the notch groove 32 (see FIG. 1).
  • the deep groove ball bearing 18 on the outer periphery of the eccentric shaft portion 17 holds an inner ring 50, an outer ring 51, a plurality of balls 52 incorporated between the inner ring 50 and the outer ring 51, and the balls 52.
  • a cage 53 is composed of two annular retaining plates 54 and 54 formed in a corrugated annular shape whose waveform is repeated in the circumferential direction by press forming of a steel plate.
  • each annular holding plate 54 is provided with a recess 56 having an inner surface 55 formed by three continuous planes at regular intervals in the circumferential direction.
  • the inner surface 55 of the recess 56 includes an inner bottom surface 55a and two inner side surfaces 55b and 55b that form an obtuse angle with the inner bottom surface 55a.
  • the inner bottom surfaces 55a and 55a facing each other between the recesses 56 and 56 are parallel, and the distance between the inner bottom surfaces 55a and 55a is larger than the diameter of the ball 52.
  • the inner side surface 55b of one of the concave portions 56 facing each other is parallel to the inner side surface 55b of the inner side surface 55b, 55b of the other concave portion 56 at a position sandwiching the center of the ball 52, and the inner side surface 55b, The distance between 55b is larger than the diameter of the ball 52.
  • the ball 52 contacts the central portion of the inner surface 55b of the recess 56 when the deep groove ball bearing 18 rotates.
  • a low friction film 58 is formed on the entire surface of the annular holding plate 54, and this low friction film 58 reduces the friction between the cage 53 and the ball 52.
  • the low friction film 58 include a ceramic film such as a boron nitride film, a DLC (diamond-like carbon) film, a carbon nitride film, and a PTFE (polytetrafluoroethylene) film.
  • the low friction film 58 may be formed only on the inner surface 55 of the recess 56.
  • the rotation of the roller cage section 22 is a rotation of a reduction ratio (50: 1 in the case of FIG. 2) corresponding to the number of teeth 19 of the internal gear 14 with respect to the rotation of the input shaft 12.
  • Rotation of the roller holder unit 22 causes the engagement holder unit 28 formed integrally with the roller holder unit 22 to rotate counterclockwise.
  • the clockwise roller 26 in the wedge-shaped space 25 resists the elastic force of the leaf spring 27 in the circumferential direction of the pocket 29 of the engagement holder portion 28. Pressed against the inner wall.
  • the roller 26 in the clockwise direction (rear in the rotational direction) is released from the engagement state on the narrow side of the wedge-shaped space 25 in that direction, and the output shaft 13 is locked. Is released. At this time, the roller 26 in the counterclockwise direction (forward in the rotational direction) is not engaged on the narrow side of the wedge-shaped space 25 in that direction, and the output shaft 13 can rotate in the counterclockwise direction.
  • the output shaft 13 that has become rotatable has the switch pin 20 fixed to the large-diameter portion 13 b engaged with the notch groove 32 of the engagement holder portion 28. For this reason, when the input shaft 12 further rotates in the clockwise direction, the output shaft 13 is counterclockwise based on the reduction ratio via the integrated holder 30 including the roller holder portion 22 and the engagement holder portion 28. Rotate. When an input torque in the counterclockwise direction is input to the input shaft 12, the output shaft 13 rotates in the clockwise direction by an operation reverse to the above.
  • the input torque in the forward and reverse rotation directions from the input shaft 12 is transmitted to the output shaft 13 via the integrated cage 30, and the output shaft 13 rotates in both the forward and reverse rotation directions.
  • the pair of rollers 26 returns to the position shown in FIG. 3 by the elastic restoring force of the leaf spring 27.
  • the eccentric shaft portion 17 when the eccentric shaft portion 17 is rotated by the input torque from the input shaft 12, the eccentric shaft portion 17 is located at a position where the rotation center is deviated from the center of the circle. The same occurs in the deep groove ball bearing 18 on the outer periphery of the portion 17. As a result, in the deep groove ball bearing 18, the friction between the cage 53 and the ball 52 is likely to be larger than the other bearings 15, 16, 24.
  • the inner surface 55 of the concave portion 56 of the cage 53 is formed by a plurality of planes, and the inner surface 55 of the concave portion 56 and the ball 52 are in point contact.
  • the friction generated between the balls 52 is small and the rotational torque is small. Therefore, this reduction gear has high transmission efficiency of torque transmitted from the input shaft 12 to the output shaft 13.
  • the shape of the pocket 57 of the cage 53 is not limited to this embodiment, and may be a polygonal cross section such as an octagonal cross section.
  • the cross section refers to a cross section along a cylindrical surface passing through the center of each ball 52.
  • this reduction gear has the low friction film 58 formed on the inner surface 55 of the recess 56, the friction generated between the cage 53 and the ball 52 is small. Therefore, this reduction gear has high transmission efficiency of torque transmitted from the input shaft 12 to the output shaft 13.
  • the speed reducer using the deep groove ball bearing 18 in which the inner surface 55 of the recess 56 is formed by a plane that makes point contact with the ball 52 in order to increase the transmission efficiency of torque transmitted from the input shaft 12 to the output shaft 13, the speed reducer using the deep groove ball bearing 18 in which the inner surface 55 of the recess 56 is formed by a plane that makes point contact with the ball 52.
  • a speed reducer in which the deep groove ball bearing shown in FIG. 17A is mounted on the outer periphery of the eccentric shaft portion 17 may be employed.
  • portions corresponding to the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
  • each annular holding plate 54 recesses 60 having spherical inner surfaces 59 are formed at regular intervals in the circumferential direction.
  • the two annular holding plates 54 are coupled in a state where the opening side of the concave portion 60 of one annular holding plate 54 and the opening side of the concave portion 60 of the other annular holding plate 54 face each other. , 60 accommodates balls 52 in pockets 61 formed between them.
  • a protrusion 62 that contacts the ball 52 is formed on the inner surface 59 of the recess 60.
  • the protrusion 62 is formed in a hemispherical shape, and is in point contact with the surface of the ball 52.
  • the protrusions 62 are formed at two positions in each recess 60, and the two protrusions 62, 62 are arranged so as to be symmetrical with the deepest position of the recess 60 in the circumferential direction.
  • the protrusions 62 are provided on the front side in the traveling direction of the balls 52 so that the balls 52 are in contact with the protrusions 62. It has become.
  • a low friction film 58 similar to that of the first embodiment is formed on the inner surface 59 of the recess 60.
  • the inner surface 59 of the recess 60 gradually increases in distance from the center C of the pocket 61 to the inner surface 59 of the recess 60 as approaching the opening edge of the recess 60 from the deepest position. It is formed in a spherical shape.
  • the inner surface 59 may be formed in a spherical shape with a constant distance from the center C of the pocket 61 to the inner surface 59 of the recess 60.
  • this deep groove ball bearing has a protrusion 62 that makes point contact with the ball 52 on the inner surface 59 of the concave portion 60 of the cage 53, the friction generated between the cage 53 and the ball 52 is small and eccentric as in the first embodiment. Even if the centrifugal force due to the shift of the rotation center of the shaft portion 17 is received, the rotational torque is not easily increased.
  • a deep groove ball bearing shown in FIG. 18 (a) may be adopted.
  • This deep groove ball bearing is a spherical surface in which the distance from the center C of the pocket 61 gradually increases as the inner surface 59 of the recess 60 approaches the opening edge of the recess 60 from the deepest position of the recess 60, as in the deep groove ball bearing shown in FIG. 18B, when the deep groove ball bearing rotates, the ball 52 comes into contact with a position shifted in the circumferential direction from the deepest position of the inner surface 59 of the recess 60. As shown in FIG. Yes.
  • the inner surface 59 of the recess 60 has a portion that is not in contact with the ball 52 during rotation of the deep groove ball bearing, a portion that is offset from the portion in contact with the ball 52 in the direction opposite to the traveling direction of the ball 52, that is, the inner surface of the recess 60.
  • a through-hole 63 is formed at a portion closer to the deepest side of 59. As shown in FIG. 18A, two through holes 63 are formed in each recess 60, and the two through holes 63, 63 sandwich the deepest position of the inner surface 59 of the recess 60.
  • the balls 52 are arranged so as to be symmetrical on the front side in the traveling direction and the rear side in the traveling direction.
  • a low friction film 58 similar to that of the first embodiment is formed on the inner surface 59 of the recess 60.
  • the lubricant may accumulate between the inner surface 59 of the recess 60 and the ball 52.
  • the lubricant tends to accumulate in the portion of the inner surface 59 of the recess 60 that is in the direction opposite to the traveling direction of the ball 52 from the portion where the ball 52 contacts, due to the centrifugal force caused by the rotation of the ball 52.
  • the rotational resistance of the deep groove ball bearing may increase due to viscous resistance.
  • this deep groove ball bearing is arranged so that the two through holes 63, 63 of each recess 60 are symmetrical on the front side in the traveling direction and the rear side in the traveling direction of the ball 52.
  • the lubricant accumulated in the middle is effectively discharged from the through hole 63.
  • the through hole 64 can be formed in the inner surface 55 of the concave portion 56 forming the pocket 57.
  • this deep groove ball bearing has an inner surface 55 of the concave portion 56 composed of an inner bottom surface 55a and two inner side surfaces 55b and 55b.
  • bowl 52 contacts the center part of the inner surface 55b.
  • the through hole 64 is a portion of the inner surface 55b of the concave portion 56 that is not in contact with the ball 52, a portion that is offset from the portion in contact with the ball 52 in the direction opposite to the traveling direction of the ball 52, that is, the inner bottom surface 55a of the concave portion 56. It is formed in the part which approached to the side. Further, as shown in FIG. 19 (a), the through hole 64 is formed at one place on each inner side surface 55b, and the through hole 63 sandwiches the inner bottom surface 55a between the front side in the traveling direction of the ball 52. Are arranged symmetrically with respect to the rear side in the traveling direction. A low friction film 58 similar to that of the first embodiment is formed on the inner surface 55 of the recess 56.
  • the roller 21 may revolve clockwise when input torque is input clockwise to the input shaft 12.
  • the input torque in the forward and reverse rotational directions from the input shaft 12 is transmitted to the output shaft 13 via the integrated retainer 30, and the output shaft 13 is rotated in the forward and reverse rotational directions. Rotate to.
  • the speed reduction device 10 includes a lock unit that is provided between the output shaft 13 and the input shaft 12 and that locks the output shaft 13 to the housing 11 against reverse input torque that acts on the output shaft 13.
  • the lock release means for releasing the locked state by the lock means with respect to the input torque acting on the shaft 12 is different from that of the first embodiment.
  • Other configurations are the same as those of the first embodiment, and the same reference numerals are used for the same configurations, and the description thereof is omitted.
  • a coil spring 33 is disposed between the housing 11 and the large diameter portion 13 b of the output shaft 13.
  • the coil spring 33 is fitted so as to come into contact with the inner peripheral portion of the housing 11 in a natural state, and both end portions 33a and 33b protrude radially inward.
  • the coil spring 33 is fitted in the housing 11 so that the diameter of the coil spring 33 is reduced when both end portions 33a and 33b are pressed inward in the circumferential direction, and the diameter of the coil spring 33 is expanded when pressed outward in the circumferential direction.
  • an axial groove 35 is formed on the outer peripheral portion of the large-diameter portion 13 b of the output shaft 13, and both groove walls of the groove 35 are at both end portions 33 a and 33 b of the coil spring 33. It is located on the outer side in the circumferential direction.
  • one groove wall 35 a is an engaging portion that can be engaged with the end portion 33 a of the coil spring 33 and the other groove wall 35 b is engageable with the end portion 33 b of the coil spring 33.
  • a protrusion 34 formed by press working integrally with the roller retainer portion 22 is disposed, and the protrusion 34 becomes a coil spring by the rotation of the roller retainer portion 22. It is possible to engage with either one of both end portions 33a and 33b of 33.
  • the locking means described above is composed of a coil spring 33 and groove walls 35 a and 35 b as engaging portions of the output shaft 13, and the groove wall 35 a (35 b) is rotated by the rotation of the output shaft 13. Engage with the end 33a (33b) of the coil spring 33 and press the coil spring 33 in the direction of expanding the diameter (see FIG. 8).
  • the roller cage portion 22 rotates counterclockwise as in the first embodiment described above.
  • the protrusion 34 as the unlocking means engages with the end portion 33a of the coil spring 33 and presses the coil spring 33 in a direction to reduce the diameter (see FIG. 9).
  • the input torque in the forward and reverse rotational directions from the input shaft 12 is transmitted to the output shaft 13 via the roller retainer unit 22, and the output shaft 13 is in both the forward and reverse directions. Rotate in the direction of rotation.
  • the speed reduction device 10 according to the third embodiment includes a locking unit that is provided between the output shaft 13 and the input shaft 12 and locks the output shaft 13 to the housing 11 against reverse input torque that acts on the output shaft 13.
  • the lock release means for releasing the locked state by the lock means with respect to the input torque acting on the input shaft 12 is different from that in the first embodiment.
  • Other configurations are the same as those of the first embodiment, and the same reference numerals are used for the same configurations, and the description thereof is omitted.
  • the output shaft 13 has a small-diameter portion 13a and a large-diameter portion 13b that are formed separately, and is provided on one end side outer peripheral portion of the small-diameter portion 13a and the inner peripheral portion of the large-diameter portion 13b.
  • the splines are formed so as to be integrally rotatable by engagement of the formed splines.
  • a cam plate 36 that is a large-diameter portion 13b that rotates integrally with the output shaft 13 and is displaceable in the axial direction, and an annular rotator 37 that is connected to rotate integrally with the roller retainer portion 22. It is provided coaxially so as to face each other.
  • the annular rotator 37 can be formed integrally with the roller holder 22.
  • the cam plate 36 is biased in one axial direction by an elastic member 39 provided between the inner surface of the other end of the housing 11 and includes a pressing surface 36 c facing the one axial direction on the outer peripheral portion of the cam plate 36. .
  • the pressing surface 36c is formed in a taper shape extending toward the other axial direction, and is opposed to the tapered contact surface 14b formed on the other axial end of the internal gear 14 and facing the other axial direction.
  • the cam plate 36 biased by the elastic member 39 has a pressing surface 36 c pressing the contact surface 14 b of the internal gear 14.
  • the annular rotating body 37 is supported so as to be relatively rotatable with respect to the internal gear 14 by a bearing 38 provided between the inner peripheral portion of the cylindrical portion 14 a formed on the other axial end side of the internal gear 14.
  • a plurality of cam grooves 40 in the circumferential direction are formed at opposite positions in the circumferential direction on both opposing surfaces of the cam plate 36 and the annular rotator 37. It is formed in a mortar shape having a small depth (shallow), and a ball 41 is interposed between the cam grooves 40 so as to allow rolling.
  • the locking means includes a cam plate 36, an annular rotator 37 facing the cam plate 36, cam grooves 40 on both opposing surfaces of the cam plate 36 and the annular rotator 37, and these cam grooves 40.
  • a ball 41 that rolls between the cam plate 36 and the annular rotator 37 and is detachably interposed is provided.
  • the ball 41 is axially disposed between the other circumferential end of the cam groove 40 of the annular rotating body 37 and one circumferential end of the cam groove 40 of the cam plate 36. It is in an engaged state.
  • the locked state of the cam plate 36 with respect to the internal gear 14 due to the reverse input torque is such that when the input torque is applied to the input shaft 12, the ball 41 is engaged with the cam plate 36 and the annular rotating body 37, and the axial direction
  • the cam plate 36 displaced to the other side is separated from the contact surface 14b of the internal gear 14, and can be released by integrally rotating the cam plate 36 and the annular rotating body.
  • FIG. 20 shows a fourth embodiment of a reduction gear 10 according to the present invention.
  • differences from the first embodiment will be mainly described, and the same reference numerals will be used for the same conceivable configurations.
  • the other end side cylindrical portion of the housing 11 is formed on the sprocket 42 that rotates integrally with the one end side cylindrical portion, and one end surface of the sprocket 42 (the end surface on the housing 11 side). ), A cylindrical portion 42a coaxial with the output shaft 13 is integrally formed.
  • the cylindrical part of the one end side of the housing 11 is press-fitted and fixed to the outer periphery of the cylindrical part 42a, and the small diameter part 13a of the output shaft 13 is rotatably supported by the inner peripheral part of the sprocket 42.
  • the input shaft 12 has a large-diameter portion 12a rotatably supported by a bearing 15 at one end in the housing 11, and an eccentric shaft portion 17 formed integrally with the large-diameter portion 12a in one axial direction. Yes.
  • the output shaft 13 has a small-diameter portion 13a and a large-diameter portion 13b formed separately, and can rotate integrally by engaging splines formed on one end side outer peripheral portion of the small-diameter portion 13a and the inner peripheral portion of the large-diameter portion 13b. Is provided.
  • the large-diameter portion 13b is fitted in a radial hole 13d formed in the outer peripheral portion thereof so that the switch pin 20 protrudes from the outer peripheral portion, and can rotate integrally with the engaging cage portion 28 of the integrated cage 30. Is engaged. For this reason, the rotation of the input torque acting on the input shaft 12 is transmitted from the integrated cage 30 to the small diameter portion 13a via the large diameter portion 13b (intermediate shaft). Further, cam surfaces 13 c are formed at equal intervals in the circumferential direction on the outer peripheral portion of the large diameter portion 13 b of the output shaft 13 that faces the cylindrical portion 42 a of the sprocket 42.
  • the internal gear 14 is provided with a bearing 43 between a cylindrical portion 14a formed on the other end side in the axial direction and the engaging cage portion 28. Further, the projection 14 c formed at one end portion in the axial direction of the internal gear 14 engages with the axial engagement recess portion 11 a formed in the housing 11, whereby the internal gear 14 is fixed to the housing 11.
  • the eccentric shaft portion 17 is provided only in one place, and the output shaft 13 is supported by the sprocket 42. Therefore, the axial dimension is compared with that in the first embodiment. Can be small.
  • a fifth embodiment of the reduction gear according to the present invention will be described with reference to FIG.
  • the speed reducer 10 according to the fifth embodiment is different from the second embodiment in the configuration of the housing 11, the input shaft 12, the output shaft 13, and the internal gear 14, and the other configurations are the same as those in the second embodiment. Therefore, the same reference numerals are used for the same configuration, and the description thereof is omitted. It has the following configuration.
  • the other end side cylindrical portion of the housing 11 is formed on the sprocket 42, the sprocket 42 rotates integrally with the one end side cylindrical portion of the housing 11, and the small diameter portion 13 a of the output shaft 13 can be rotated by the inner peripheral portion of the sprocket 42. It is supported by.
  • the input shaft 12 has a large-diameter portion 12a rotatably supported by a bearing 15 at one end in the housing 11, and an eccentric shaft portion 17 formed integrally with the large-diameter portion 12a in one axial direction. Yes.
  • the output shaft 13 has a small-diameter portion 13a and a large-diameter portion 13b formed separately, and can rotate integrally by engaging splines formed on one end side outer peripheral portion of the small-diameter portion 13a and the inner peripheral portion of the large-diameter portion 13b. Is provided.
  • a groove 35 is formed in the outer peripheral portion of the large diameter portion 13b, and rotation of the input torque acting on the input shaft 12 is reduced from the protrusion 34 of the roller retainer portion 22 through the large diameter portion 13b (intermediate shaft). Is transmitted to the unit 13a.
  • the internal gear 14 is provided with a bearing 43 between a cylindrical portion 14a formed on the other end side in the axial direction and the engaging cage portion 28. Further, the projection 14 c formed at one end portion in the axial direction of the internal gear 14 engages with the axial engagement recess portion 11 a formed in the housing 11, whereby the internal gear 14 is fixed to the housing 11.
  • the eccentric shaft portion 17 is provided only in one place, and the output shaft 13 is supported by the sprocket 42, so that the axial dimension is the same as in the fourth embodiment. It can be made smaller than in the case of the second embodiment.
  • a sixth embodiment of the reduction gear according to the present invention will be described with reference to FIG.
  • the speed reducer 10 according to the sixth embodiment is different from the third embodiment in the configuration of the housing 11, the input shaft 12, the output shaft 13, and the internal gear 14, and the other configurations are the same as those in the third embodiment. Therefore, the same reference numerals are used for the same configuration, and the description thereof is omitted.
  • the other end side cylindrical portion of the housing 11 is formed on the sprocket 42, the sprocket 42 rotates integrally with the one end side cylindrical portion of the housing 11, and the small diameter portion 13 a of the output shaft 13 can be rotated by the inner peripheral portion of the sprocket 42. It is supported by.
  • the input shaft 12 has a large-diameter portion 12a rotatably supported by a bearing 15 at one end in the housing 11, and an eccentric shaft portion 17 formed integrally with the large-diameter portion 12a in one axial direction. Yes.
  • the output shaft 13 has a small-diameter portion 13a and a large-diameter portion 13b formed separately, and can rotate integrally by engaging splines formed on one end side outer peripheral portion of the small-diameter portion 13a and the inner peripheral portion of the large-diameter portion 13b. Is provided.
  • the large-diameter portion 13b is a cam plate 36, and has a pressing surface 36c facing radially one side outward in the radial direction.
  • the large-diameter portion 13b is pivoted between the large-diameter portion 13b and the sprocket 42.
  • An elastic member 39 that biases in one direction is provided. For this reason, the rotation of the input torque acting on the input shaft 12 is transferred to the small diameter portion 13a via the large diameter portion 13b (intermediate shaft) which is the cam plate 36 which is cam-engaged from the roller holder portion 22 to the annular rotating body 37. Communicated.
  • the internal gear 14 is provided with a bearing 43 between a cylindrical portion formed on the other end side in the axial direction and the engaging cage portion 28. Further, the projection 14 c formed at one end portion in the axial direction of the internal gear 14 engages with the axial engagement recess portion 11 a formed in the housing 11, whereby the internal gear 14 is fixed to the housing 11.
  • the eccentric shaft portion 17 is provided only in one place, and the output shaft 13 is supported by the sprocket 42, so that the axial dimension is the same as in the fourth embodiment. Compared to the case of the third embodiment, it can be made smaller.
  • variable valve timing device in this embodiment includes a camshaft 44 that drives at least one of an intake valve and an exhaust valve (not shown), and a drive rotation that is transmitted from the drive shaft of the engine.
  • the sprocket 42 as a body is provided so as to be relatively rotatable coaxially, and the rotation of the output shaft 46 disposed coaxially with the camshaft 44 of the electric motor 45 is transmitted to the camshaft 44 via the speed reduction mechanism.
  • the opening / closing timing of the valve is changed by changing the rotational phase difference of the 44 with respect to the sprocket 42.
  • the speed reduction device 10 in the first embodiment described above can be applied. That is, a sprocket 42 as a drive rotor is provided on the outer periphery of the housing 11 of the speed reducer 10, the input shaft 12 of the speed reducer 10 is used as the output shaft 46 of the electric motor 45, and the output shaft 13 of the speed reducer 10 is a cam.
  • the shaft 44 is used. Thereby, between the output shaft 46 of the electric motor 45 and the camshaft 44, a lock unit and a lock release unit that prevent reverse input torque included in the speed reduction device 10 are provided.
  • the speed reduction of the output shaft 46 (input shaft 12) of the electric motor 45 and the transmission of the reduced speed rotation to the camshaft 44 (output shaft 13) can be performed by the speed reduction device 10.
  • the rotation of the camshaft 44 (output shaft 13) to which reverse input torque is applied by the locking means of the speed reducer 10 causes the rearwardly rotating roller 26 of the pair of rollers 26 in the wedge-shaped space 25 to be housed by the wedge effect. 11 and the camshaft 44 to engage with each other. By this engagement, the camshaft 44 is locked with respect to the housing 11, and it is possible to reliably prevent the reverse input torque acting on the camshaft 44 from being transmitted to the output shaft 46 of the electric motor 45.
  • the integrated holder 30 is formed by the engagement holder portion 28 and the roller holder portion 22, the input is input to the output shaft 46 (input shaft 12) of the electric motor 45.
  • the engagement cage holder 28 rotates integrally with the rotation of the roller cage 22.
  • the rotating retainer holder 28 presses the rear roller in the rotational direction of the pair of rollers 26 toward the wide side of the wedge-shaped space 25, and the engagement state by the roller 26 is released.
  • variable valve timing device A second embodiment of the variable valve timing device according to the present invention will be described with reference to FIG.
  • the variable valve timing device according to the second embodiment applies the second embodiment of the speed reduction device 10 described above as a speed reduction mechanism.
  • Other configurations are the same as those of the above-described first embodiment of the variable valve timing device, and the same reference numerals are used for the same possible configurations, and the description thereof is omitted.
  • the unlocking means when the input torque is applied to the output shaft 46 (input shaft 12) of the electric motor 45, the protrusion 34 of the roller holder portion 22 that rotates rotates the end portion 33a (33b) of the coil spring 33. Is pressed to reduce the diameter, and the camshaft 44 is released from the inner surface of the housing 11.
  • variable valve timing apparatus is an application of the third embodiment of the reduction gear 10 described above as a reduction mechanism.
  • Other configurations are the same as those of the above-described first embodiment of the variable valve timing device, and the same reference numerals are used for the same possible configurations, and the description thereof is omitted.
  • the cam plate 36 when reverse input torque is applied to the camshaft 44 by the locking means of the third embodiment of the reduction gear 10, the cam plate 36 is pressed in one axial direction by the elastic member 39, and By pressing the formed contact surface 14b, a frictional resistance is generated in the cam plate 36, and the cam plate 36 is fixed to the internal gear 14 to prevent the rotation of the cam shaft 44 to which the reverse input torque is applied. be able to.
  • variable valve timing device A fourth embodiment of the variable valve timing device according to the present invention will be described with reference to FIG.
  • the fourth embodiment of the speed reduction device 10 described above is applied as a speed reduction mechanism
  • the input shaft 12 of the speed reduction device 10 is used as the output shaft 46 of the electric motor 45
  • the speed reduction mechanism The output shaft 13 of the device 10 is a camshaft 44.
  • Other configurations are the same as those of the first embodiment of the variable valve timing device described above. In the following, differences from the first embodiment will be mainly described, and the same reference numerals will be used for configurations that can be considered the same.
  • variable valve timing device the rotation of the output shaft 46 of the electric motor 45 is decelerated by the speed reducer 10 and transmitted to the camshaft 44 (output shaft 13). Further, between the output shaft 46 of the electric motor 45 and the camshaft 44, there are provided locking means for preventing reverse input torque provided in the speed reducer 10 and unlocking means.
  • variable valve timing device the structure of the housing 11 and the like is changed in the fourth embodiment of the speed reducer 10 applied thereto, compared to the first embodiment of the speed reducer 10 described above. Accordingly, the locking means and unlocking means of the speed reduction device 10 in this variable valve timing device are the same as those in the case of the variable valve timing device in the first embodiment, to which the first embodiment of the speed reduction device 10 is applied. Works.
  • the integrated retainer 30 is formed by the engagement retainer portion 28 and the roller retainer portion 22, so that input torque acts on the output shaft 46 (input shaft 12) of the electric motor 45.
  • the engagement holder 28 rotates as a unit.
  • the rotating retainer holder 28 presses the rear roller in the rotational direction of the pair of rollers 26 toward the wide side of the wedge-shaped space 25, and the engagement state by the roller 26 is released.
  • variable valve timing device A fifth embodiment of the variable valve timing device according to the present invention will be described with reference to FIG.
  • the fifth embodiment of the speed reduction device 10 described above is applied as a speed reduction mechanism, and the input shaft 12 of the speed reduction device 10 is used as the output shaft 46 of the electric motor 45 to reduce the speed.
  • the output shaft 13 of the device 10 is a camshaft 44.
  • variable valve timing device the rotation of the output shaft 46 of the electric motor 45 is decelerated by the speed reducer 10 and transmitted to the camshaft 44 (output shaft 13). Further, between the output shaft 46 of the electric motor 45 and the camshaft 44, there are provided locking means for preventing reverse input torque provided in the speed reducer 10 and unlocking means.
  • the fifth embodiment of the speed reduction device 10 applied to the variable valve timing device is obtained by changing the structure of the housing 11 and the like with respect to the second embodiment of the speed reduction device 10 described above. Therefore, the locking means and the unlocking means of the speed reduction device 10 in this variable valve timing device are the same as those in the case of the variable valve timing device in the second embodiment, to which the second embodiment of the speed reduction device 10 is applied. Works.
  • the unlocking means when the input torque is applied to the output shaft 46 (input shaft 12) of the electric motor 45, the protrusion 34 of the roller holder portion 22 that rotates rotates the end portion 33a (33b) of the coil spring 33. ) To reduce the diameter, and the camshaft 44 is released from the inner surface of the housing 11.
  • variable valve timing device A sixth embodiment of the variable valve timing device according to the present invention will be described with reference to FIG.
  • the sixth embodiment of the speed reduction device 10 described above is applied as a speed reduction mechanism
  • the input shaft 12 of the speed reduction device 10 is used as the output shaft 46 of the electric motor 45
  • the speed reduction mechanism The output shaft 13 of the device 10 is a camshaft 44.
  • variable valve timing device the rotation of the output shaft 46 of the electric motor 45 is decelerated by the speed reducer 10 and transmitted to the camshaft 44 (output shaft 13). Further, between the output shaft 46 of the electric motor 45 and the camshaft 44, there are provided locking means for preventing reverse input torque provided in the reduction gear device 10 and unlocking means.
  • variable valve timing device the sixth embodiment of the speed reduction device 10 applied to the variable valve timing device is obtained by changing the structure of the housing 11 and the like with respect to the third embodiment of the speed reduction device 10 described above. Therefore, the locking means and unlocking means of the speed reduction device 10 in this variable valve timing device are the same as those of the variable valve timing device in the third embodiment described above, to which the third embodiment of the speed reduction device 10 is applied. Works.

Abstract

Selon l’invention, un couple d'entrée inverse qui est entré dans l'arbre de sortie d'un dispositif de démultiplication doit être empêché d'être transmis à l'arbre d'entrée du dispositif de démultiplication. Le démultiplicateur comprend un boîtier (11), l'arbre d'entrée (12) et l'arbre de sortie (13), un engrenage interne (14) fixé au boîtier (11), et des rouleaux (21) maintenus entre des sections d'arbre excentrées (17) formées sur l'arbre d'entrée (12) et l'engrenage interne (14) de façon à pouvoir rouler dans une section de retenue de rouleau (22). Un moyen de blocage destiné à maintenir une paire d'éléments en prise (26) par une section de retenue d'élément de prise (28), de façon à être aptes à venir en prise avec et à se découpler du boîtier (11) et de l'arbre de sortie (13), et un moyen de libération de blocage pour libérer la prise du boîtier (11) et de l'arbre de sortie (13) par pression de l'un quelconque de la paire d'éléments de prise (26) vers le côté croissant d'un espace en forme de coin (25) par la section de retenue d'élément de prise (28) lorsqu'un couple d'entrée agit sur l'arbre d'entrée (12), sont installés dans une pluralité d'espaces en forme de coin (25) formés entre le boîtier (11) et l'arbre de sortie (13).
PCT/JP2009/061616 2008-07-09 2009-06-25 Démultiplicateur et dispositif de distribution à soupape variable l'utilisant WO2010004880A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009001645T DE112009001645T5 (de) 2008-07-09 2009-06-25 Drehzahlminderer und Vorrichtung zur variablen Ventilzeitsteuerung unter Verwendung des Drehzahlminderers

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP2008-179223 2008-07-09
JP2008179223 2008-07-09
JP2008207833 2008-08-12
JP2008-207833 2008-08-12
JP2008215547A JP5376288B2 (ja) 2008-08-25 2008-08-25 可変バルブタイミング装置
JP2008-215547 2008-08-25
JP2009091204A JP5180135B2 (ja) 2008-08-12 2009-04-03 可変バルブタイミング装置およびこの可変バルブタイミング装置に組み込まれるローラ減速機
JP2009-091204 2009-04-03
JP2009-093892 2009-04-08
JP2009093892A JP5354186B2 (ja) 2008-07-09 2009-04-08 減速装置

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CN102762891A (zh) * 2010-04-21 2012-10-31 Ntn株式会社 减速装置
CN103133627A (zh) * 2013-02-25 2013-06-05 田达 一种传动带旋摆轮减速器
EP2615328A1 (fr) * 2010-09-09 2013-07-17 NTN Corporation Dispositif de décélération
US20130206530A1 (en) * 2010-06-22 2013-08-15 Rotork Controls Limited Anti back-drive couplings
CN103917805A (zh) * 2011-09-22 2014-07-09 Ntn株式会社 减速装置
US20150308499A1 (en) * 2014-04-29 2015-10-29 Hyundai Motor Company Noise reducing structure of speed reduction device for electric cvvt
WO2017038202A1 (fr) * 2015-08-28 2017-03-09 株式会社ミクニ Unité de réglage de phase et dispositif de modification de réglage des soupapes
EP3106697A4 (fr) * 2014-02-14 2017-03-15 NTN Corporation Embrayage anti entrée inversée
EP3101314A4 (fr) * 2014-01-28 2017-04-12 NTN Corporation Engrenage réducteur doté d'un frein
CN107971671A (zh) * 2017-11-24 2018-05-01 重庆冠亨汽车配件有限公司 用于制造曲线形汽车配件用的定位装置
CN114270074A (zh) * 2019-09-05 2022-04-01 池田昌幸 齿轮变速装置
CN114810848A (zh) * 2021-01-18 2022-07-29 杜泽儒 齿轮双向离合机构

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JPS6293565A (ja) * 1985-10-18 1987-04-30 Ntn Toyo Bearing Co Ltd 減速装置
JP2002357224A (ja) * 2001-03-27 2002-12-13 Nsk Ltd ころ軸受
JP2005299685A (ja) * 2002-03-01 2005-10-27 Nsk Ltd 車輪支持用転がり軸受ユニット
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JP2006057688A (ja) * 2004-08-18 2006-03-02 Ntn Corp 逆入力遮断装置
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US8684878B2 (en) 2010-04-21 2014-04-01 Ntn Corporation Speed reducer
CN102762891A (zh) * 2010-04-21 2012-10-31 Ntn株式会社 减速装置
US20130206530A1 (en) * 2010-06-22 2013-08-15 Rotork Controls Limited Anti back-drive couplings
US8950565B2 (en) * 2010-06-22 2015-02-10 Rotork Controls Limited Anti back-drive couplings
EP2824365A3 (fr) * 2010-09-09 2016-05-11 NTN Corporation Réducteur de vitesse
EP2615328A1 (fr) * 2010-09-09 2013-07-17 NTN Corporation Dispositif de décélération
EP2615328A4 (fr) * 2010-09-09 2014-03-26 Ntn Toyo Bearing Co Ltd Dispositif de décélération
CN103917805A (zh) * 2011-09-22 2014-07-09 Ntn株式会社 减速装置
CN103133627A (zh) * 2013-02-25 2013-06-05 田达 一种传动带旋摆轮减速器
EP3101314A4 (fr) * 2014-01-28 2017-04-12 NTN Corporation Engrenage réducteur doté d'un frein
EP3106697A4 (fr) * 2014-02-14 2017-03-15 NTN Corporation Embrayage anti entrée inversée
US10359083B2 (en) 2014-02-14 2019-07-23 Ntn Corporation Reverse input blocking clutch
US20150308499A1 (en) * 2014-04-29 2015-10-29 Hyundai Motor Company Noise reducing structure of speed reduction device for electric cvvt
WO2017038202A1 (fr) * 2015-08-28 2017-03-09 株式会社ミクニ Unité de réglage de phase et dispositif de modification de réglage des soupapes
CN107971671A (zh) * 2017-11-24 2018-05-01 重庆冠亨汽车配件有限公司 用于制造曲线形汽车配件用的定位装置
CN114270074A (zh) * 2019-09-05 2022-04-01 池田昌幸 齿轮变速装置
CN114270074B (zh) * 2019-09-05 2024-02-20 池田昌幸 齿轮变速装置
CN114810848A (zh) * 2021-01-18 2022-07-29 杜泽儒 齿轮双向离合机构

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