WO2020090186A1 - Réducteur de vitesse de type à rouleaux et dispositif à soupapes variable pour moteur à combustion interne - Google Patents

Réducteur de vitesse de type à rouleaux et dispositif à soupapes variable pour moteur à combustion interne Download PDF

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Publication number
WO2020090186A1
WO2020090186A1 PCT/JP2019/032018 JP2019032018W WO2020090186A1 WO 2020090186 A1 WO2020090186 A1 WO 2020090186A1 JP 2019032018 W JP2019032018 W JP 2019032018W WO 2020090186 A1 WO2020090186 A1 WO 2020090186A1
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WIPO (PCT)
Prior art keywords
roller
speed reducer
bearing
rotating body
eccentricity
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Application number
PCT/JP2019/032018
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English (en)
Japanese (ja)
Inventor
佐藤　正
淳史 山中
Original Assignee
日立オートモティブシステムズ株式会社
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Publication of WO2020090186A1 publication Critical patent/WO2020090186A1/fr

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    • 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
    • F01L1/352—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 using bevel or epicyclic gear

Definitions

  • the present invention relates to a roller speed reducer that decelerates the rotation of an input shaft and transmits it to an output shaft, and a variable valve operating device for an internal combustion engine using the roller speed reducer.
  • a roller speed reducer includes an eccentric rotating body which is an input shaft, a bearing provided on the outer periphery of the eccentric rotating body, an annular member provided on the outer periphery of the bearing, and an inner periphery of the annular member.
  • An inner peripheral meshing portion having a hollow portion, a plurality of rollers provided between the inner peripheral meshing portion and the outer ring of the bearing, and a radial direction of the entire roller that separates the rollers. It has a retainer that allows movement and is also an output shaft.
  • Patent Document 1 discloses a detailed structure as a "reduction mechanism 8".
  • the roller reducer having such a configuration has a thin reduction in the axial direction and a small number of parts, and yet has a high reduction ratio capable of setting a large reduction ratio of 30 or more, which is a rotation speed ratio of the input shaft and the output shaft. Is.
  • the "retainer 41" that is the output shaft is fastened and fixed to the camshaft shaft of the variable valve operating device of the internal combustion engine. Therefore, when the torque generated by the camshaft shaft fluctuates, a relatively large impact striking sound is generated between the outer peripheral surface of each rolling element and the meshing portion provided on the inner periphery of the annular member due to the clearance (backlash). Therefore, there is a problem that quietness is deteriorated. Further, if the torque acting on the cage is excessive due to the cam torque, the surface pressure of the meshing portion that comes into contact with the rolling elements increases, and the durability deteriorates.
  • the backlash of the reduction gear is reduced by optimizing the amount of eccentricity, which is the distance between the center of the eccentric rotating body and the bearing center, and the collision striking sound between the rolling element and the meshing portion is reduced. It is intended to improve the durability by reducing the surface pressure acting on the rolling element and the meshing portion.
  • the roller speed reducer of the present invention is a roller speed reducer that amplifies a drive torque input to an eccentric rotating body that is an input shaft and outputs the amplified torque from a retainer that is an output shaft,
  • the eccentric rotating body having an arcuate cam portion eccentric in the radial direction from the center of rotation on the outer periphery, a bearing arranged on the outer periphery of the eccentric rotating body and rotatably supporting the eccentric rotating body, and an outer periphery of the bearing.
  • An annular member having corrugated internal teeth on the inner peripheral surface thereof, and an outer periphery of the bearing and an inner periphery of the annular member, which are arranged at substantially equal intervals in the circumferential direction, for eccentric rotation of the eccentric rotating body.
  • a roller deceleration device that realizes quietness by reducing a collision hitting sound between a rolling element and an engaging portion and improvement of durability by reducing a surface pressure acting between the rolling element and an engaging portion. Can be provided.
  • FIG. 1 is a front view of a roller speed reducer 10 of the present embodiment
  • FIG. 2 is an enlarged view of a main part of FIG. 1
  • FIG. 3 is a side view (cross-sectional view) of FIG. 1
  • FIG. 4 is a roller holding hole 3a of a cage 3.
  • the roller reduction device 10 includes an eccentric rotating body 5, a medium diameter ball bearing 1 that is a bearing provided on the outer periphery of the eccentric rotating body 5 and rotatably supporting the eccentric rotating body 5.
  • An annular member 4 provided on the outer periphery of the medium diameter ball bearing 1, a plurality of rollers 2 provided between an inner peripheral surface of the annular member 4 and an outer ring of the medium diameter ball bearing 1, and a space between the rollers 2.
  • a retainer 3 that allows the entire roller 2 to move in the radial direction while being separated, and amplifies and transmits the drive torque of the eccentric rotating body 5 that is the input shaft to the retainer 3 that is the output shaft. It is a speed reducer.
  • the eccentric rotating body 5 is an input shaft that is rotatable in both forward and reverse directions around the point O, and the outer peripheral surface of the eccentric rotating body 5 is centered around the point O ′.
  • the arc-shaped cam portion is formed.
  • the axis Y of the cam portion is eccentric from the axis X of the eccentric rotating body 5 in the radial direction by a slight eccentric amount a.
  • the medium-diameter ball bearing 1 is press-fitted and fastened to a cam portion on the outer circumference of the eccentric rotating body 5, and is composed of an inner ring 1a, an outer ring 1b, and a plurality of balls 1c interposed between the two wheels. Since the inner ring 1a of the medium diameter ball bearing 1 is press-fitted and coupled to the outer peripheral surface of the eccentric rotating body 5, it rotates integrally with the eccentric rotating body 5 which is the input shaft. On the other hand, as shown in FIG. 3, in the outer ring 1b of the medium diameter ball bearing 1, both the input side end surface and the output side end surface are free from contact with other parts. Further, as shown in FIG.
  • an annular retainer 3 having a roller retaining hole 3a in which a roller 2 whose outer peripheral surface rotatably abuts is housed in a roller retaining hole 3a is arranged on the outer periphery of the outer ring 1b with a gap C1. ..
  • the roller holding holes 3a of the cage 3 for accommodating the rollers 2 are formed in the rib portion 3b of the cage 3 at regular intervals.
  • the annular member 4 has corrugated internal teeth 4a centered on the point O on the inner peripheral surface.
  • Each of the rollers 2 arranged between the outer ring 1b and the annular member 4 moves in the radial direction with the eccentric movement of the medium diameter ball bearing 1 and has internal teeth 4a formed on the inner peripheral surface of the annular member 4. It is adapted to be fitted and to be oscillated in the radial direction while being guided in the circumferential direction by both side edges of the roller holding hole 3a.
  • each component of the roller reduction gear transmission 10 described above is formed of metal (for example, iron-based metal), and the movable parts such as the medium diameter ball bearing 1 and the roller 2 inside the roller reduction gear transmission 10 are lubricated and lubricated.
  • the part is designed to supply sufficient lubricating oil.
  • roller speed reducer 10 of this embodiment will be described below with reference to FIGS. 1 to 4.
  • the roller speed reducer 10 amplifies the driving torque of the eccentric rotating body 5 which is the input shaft and transmits it to the cage 3 which is the output shaft. That is, when the eccentric rotating body 5 is rotationally driven by a power source such as a drive motor, each of the plurality of rollers 2 is circumferentially guided by both side edges in the roller holding hole 3a for each rotation of the eccentric rotating body 5. While moving, it moves over one inner tooth 4a provided on the inner circumference of the annular member 4 while rolling while moving to the adjacent inner tooth 4a, and by sequentially repeating this, rolling contact is successively made in the circumferential direction.
  • a power source such as a drive motor
  • the cage 3 as an output shaft is decelerated with respect to the rotation speed of the eccentric rotating body 5 and is driven in a predetermined rotation direction.
  • the reduction ratio which is the absolute value of the relative rotational phase ratio of the eccentric rotation body 5 and the cage 3 with respect to the annular member 4, and the rotation direction of the cage 3 depending on the rotation direction of the eccentric rotation body 5 are the number of internal teeth 4a.
  • the shape of the inner teeth 4a can be arbitrarily set.
  • the value obtained by adding one to the number of teeth of the internal teeth 4a is the reduction ratio
  • the input shaft and the output When the rotation direction of the shaft is opposite, the value obtained by subtracting 1 from the number of teeth of the inner teeth 4a is the reduction ratio.
  • the speed reduction ratio n of the roller speed reducer 10 is 30 to 100.
  • the input shaft (eccentric rotor 5) is driven to rotate, and is arranged in the circumferential direction on the side opposite to the rotational direction of the retainer 3 about 45 degrees with respect to the axis Y direction which is the eccentric direction of the eccentric rotor 5.
  • the plurality of rollers 2 are lifted in the radial direction in a state in which the circumferential direction is restricted by both side edges of the roller holding hole 3a.
  • the plurality of rollers 2 come into contact with each other at three points: the outer peripheral surface of the outer ring 1b of the medium diameter ball bearing 1, the inner peripheral surface of the inner teeth 4a of the annular member 4, and the circumferential retaining surface of the roller retaining hole 3a. In contact with each other, an acting force is generated on the outer peripheral surface of the roller 2 and the contact surface.
  • FIG. 5 illustrates the action force when four rollers abut at three points.
  • the acting force between each roller 2 and the outer circumferential surface of the outer ring 1b is Fa1 to Fa4
  • the acting force between the roller 2 and the inner circumferential surface of the inner tooth 4a is Fb1 to Fb4
  • the circumferential force of the roller 2 and the roller holding hole 3a is Fc1 to Fc4.
  • the acting force at each contact point differs depending on the contact position with the inner peripheral surface of the inner tooth 4a with which each roller 2 contacts. Therefore, the action force is generated when the roller 2 comes into contact with the three points, and the action force gradually increases as the roller 2 rolls, reaches the maximum, and then decreases. It becomes zero.
  • rollers in which the acting force is generated are sequentially switched in the circumferential direction, so that a constant number of rollers is always provided. An acting force is generated on the roller 2.
  • the acting torque Ts for rotationally driving the output shaft is the sum of the acting forces Fc1 to Fc4 of the holding surface in the circumferential direction of the roller holder hole 3a of the roller 2 abutting at three points and the holder. It is the product of the point O, which is the center of rotation of 3, and the radius of the rib portion 3b.
  • the outer peripheral surface of the outer ring 1b of the medium diameter ball bearing 1, the inner peripheral surface of the inner teeth 4a of the annular member 4, and the roller holding hole are passed through the outer peripheral surfaces of the rollers 2.
  • the deceleration operation is performed while the acting force is generated at three points on the circumferential holding surface of 3a.
  • the acting torque Ts generated on the cage 3 by the sum of the acting forces Fc1 to Fc4 on the holding surface in the circumferential direction of the roller holding hole 3a from the roller 2 is equal to or larger than the load torque received by the holder 3 from the outside of the roller reduction device 10. Need to be
  • the roller length Lr that most affects the axial thickness of the roller speed reducer 10 and the load torque that acts on the cage 3 are the same, the larger the outer diameter of the cage 3, the more the roller 2 becomes. The acting force at the three contact points becomes smaller. Since the outer diameter of the cage 3 determines the outer diameter of the roller speed reducer 10, in order to reduce the diameter of the roller speed reducer 10, it is necessary to design the roller 2 in consideration of the increase in the surface pressure of the meshing portion. is there.
  • a backlash ⁇ is generated in the cage 3 due to the gap between the roller 2 in the roller holding hole 3a (CL2 described below) and the gap between the inner teeth 4a and the roller 2 (CL1 described below).
  • this backlash ⁇ is large, the load torque acting on the cage 3 alternates, and the impact striking sound between the roller 2 and the holding surface of the roller holding hole 3a increases. In this way, if the backlash ⁇ is large, the quietness is lowered due to the impact striking sound, so it is necessary to design in consideration of the backlash ⁇ .
  • the surface pressure acting on the meshing portion between the roller 2 and the internal teeth 4a which affects the durability
  • the backlash ⁇ which affects the quietness
  • the shape of the inner teeth 4a is determined by the reduction ratio n, the number of teeth Z, the radius of the medium diameter ball bearing 1 (hereinafter referred to as "bearing radius R"), the roller radius r, and the eccentricity a.
  • the bearing is limited by the reduction ratio n of the roller reduction gear 10, the number of teeth Z depending on the difference between the input and output rotation directions, and the outer diameter of the roller reduction gear 10. Even after various specifications of the radius R and the roller radius r are determined, the roller deceleration device 10 can be downsized while maintaining durability and quietness by optimizing the eccentricity a. it can.
  • FIG. 8 shows the relationship between the maximum Hertzian stress p max and the eccentricity a, which affect the durability, and the ease of locking (the state in which the roller 2 is sandwiched between the cage 3 and the annular member 4 and cannot roll).
  • the stress p max and the vertical axis (right side) are the roller engagement ratio Lt / Lr.
  • the maximum Hertz stress p max is a stress that acts on the inner peripheral surfaces of the roller 2 and the inner teeth 4a of the annular member 4, and the smaller the stress is, the more durable the roller speed reducer 10 is.
  • the medium diameter ball bearing 1 having a bearing radius R of about 30 mm has been used, but in recent years, the bearing radius R is 25 mm or less due to the demand for further downsizing of the roller reduction gear.
  • the adoption of the medium diameter ball bearing 1 is also being considered. Therefore, the optimum value of the eccentricity a obtained below is a value that can achieve various performances comparable to the current state even if the bearing radius R is the medium diameter ball bearing 1 of 25 mm or less.
  • various characteristics will be examined below for three types of medium-diameter ball bearings 1 having bearing radii R of 31.5, 27.5, and 23.5 mm. In the following graphs, the value of the bearing radius R of 31.5 mm is shown by a dotted line, the value of 27.5 mm by a broken line, and the value of 23.5 mm by a solid line.
  • the outer diameter of the roller reduction gear device 10 is mainly determined by the bearing radius R, the roller radius r, and the eccentricity a, but the bearing radius R is dominant.
  • the number of required rollers 2 is determined from the divisor of the reduction ratio n for the roller radius r, and the value of the roller radius r is generally determined by arranging the rollers 2 on the outer peripheral surface of the medium diameter ball bearing 1 at equal intervals. The size is decided.
  • the roller radius r is sufficiently smaller than the bearing radius R. Since the eccentricity a is also sufficiently smaller than the bearing radius R, the outer diameter of the roller reduction device 10 is substantially determined by the size of the bearing radius R. Therefore, it can be said that the bearing radius R shown in FIG. 8 compares the sizes of the roller reduction gears 10.
  • the maximum Hertz stress p max decreases slightly as the bearing radius R decreases under the same load torque condition. This is because the acting force Fb acting on the inner peripheral surface of the inner tooth 4a generally increases as the bearing radius R is reduced, but the curvature of the inner tooth 4a is changed to a small value in the smaller diameter, so that the outer peripheral surface of the roller 2 is reduced. This is because the maximum Hertzian stress p max is slightly reduced by increasing the contact width of the inner peripheral surface of the inner tooth 4a. Moreover, when the amount of eccentricity a is increased, the maximum Hertz stress p max decreases in a quadratic curve. This is also because the curvature of the inner teeth 4a changes in a small manner as the eccentricity a increases, and the contact width between the outer peripheral surface of the roller 2 and the inner peripheral surface of the inner teeth 4a increases.
  • the roller engagement ratio Lt / Lr is a value that affects the ease of locking, and the smaller the roller engagement ratio Lt / Lr, the more difficult the roller reduction device 10 is to lock.
  • the definition of the roller engagement ratio Lt / Lr will be described with reference to FIG. 7.
  • FIG. 7 is a side of symmetry with respect to the axis X, which is the center of rotation of the eccentric rotary body 5, about the axis Y of the cam shaft of the eccentric rotary body 5, and the outer circumferential surface of the outer ring 1b of the medium diameter ball bearing 1 and the cage 3.
  • the enlarged view of the position where the gap C1 between and is maximum is shown.
  • the thickness of the rib portion 3b of the cage 3 is Lt
  • the distance that the roller 2 engages with the cage 3 when there is no gap between the roller 2 and the outer ring 1b of the medium diameter ball bearing 1 is Lr.
  • Lt / Lr is defined as the roller engagement ratio.
  • the roller engagement ratio Lt / Lr represents the ratio of the minimum value in which the roller 2 is accommodated in the radial direction of the roller holding hole 3a with respect to the thickness Lt of the rib portion 3b. This means that the maximum amount of protrusion of the roller 2 from the roller 3a is large, and if this is small, it means that the maximum amount of protrusion of the roller 2 from the roller holding hole 3a is small.
  • the roller deceleration device 10 the distance Lr with which the roller 2 is engaged with the retainer 3 with respect to the thickness Lt of the roller holding hole 3a is set to a certain value or more (for example, Lr is 1/4 or more of Lt). Size). That is, when expressed by the roller engagement ratio Lt / Lr, it is necessary to set Lt / Lr to a certain value or less (for example, Lt / Lr is 4 or less).
  • the optimum range of the eccentricity a is 0.5 to 1.2 mm when the examination result on the maximum Hertz stress p max surface and the examination result on the roller engagement ratio Lt / Lr surface according to FIG. 8 are combined.
  • the eccentricity a is set to 0.7 to 1.2 mm, which is higher. It is desirable to achieve durability.
  • FIG. 9 is an example of a graph for determining the optimum value of the eccentricity amount a from a viewpoint different from that of FIG. 8, and the backlash ⁇ due to the clearance that affects the magnitude of the impact striking sound when the roller reduction device 10 is operating.
  • the horizontal axis represents the eccentricity a as in FIG. 8, and the vertical axis (left side) represents the backlash ⁇ due to CL1.
  • the clearance will be described in detail with reference to FIG.
  • CL1 is a gap generated between the outer peripheral surface of the roller 2 and the outer peripheral surface 1b of the medium diameter ball bearing 1 and the inner peripheral surface of the inner tooth 4a of the annular member 4.
  • CL2 is a gap generated between both side edges of the roller holding hole 3a and the roller 2. Due to the values of the clearances CL1 and CL2, backlash ⁇ , which is the amount of rotation of the cage 3 in the circumferential direction with the eccentric rotating body 5 and the annular member 4 fixed, occurs. In particular, the value of the clearance CL1 increases the backlash ⁇ by about 3 times that of CL2. Further, CL2 is determined by the dimensional tolerance between the roller 2 and the roller holding hole 3a, and is little affected by the physique of the roller speed reducer 10. Therefore, regarding the quietness related to the outer diameter of the roller speed reducer 10, the vertical axis (left side) of FIG. 9 shows the relationship of the backlash ⁇ when CL1 is a constant value.
  • the optimum eccentricity amount a for suppressing the impact striking sound generated by the influence of the backlash ⁇ is 0.5 mm or more, so that the roller engagement rate Lt / on the vertical axis (right side) described in FIG.
  • the optimum range of the eccentricity a based on FIG. 9 is 0.5 to 1.2 mm.
  • FIG. 10 shows the relationship between the tooth height h of the inner tooth 4a obtained by subtracting the radius of the tip circle from the radius of the root circle of the inner tooth 4a of the annular member 4 shown in FIG. Similar to FIGS. 8 and 9, the horizontal axis and the vertical axis (right side) show the eccentricity amount a and the roller engagement ratio Lt / Lr, and the vertical axis (left side) shows the tooth height h.
  • the tooth height h decreases as the bearing radius R decreases, and increases by increasing the eccentricity a.
  • the size of the tooth height h affects the cause of tooth jump during deceleration operation and the strength between teeth. Therefore, it is necessary to set the pressure to a certain value or more from the surface pressure or the like that acts on the meshing portion of the inner tooth surface by the load torque that acts on the cage 3 that is the output shaft.
  • the tooth height h decreases, but the tooth height h can be increased by increasing the eccentricity a.
  • the optimum eccentricity a is 0.5 to 1.2 mm.
  • FIGS. 8 and 9 are replaced with a / R values obtained by dividing the eccentricity a by the bearing radius R, and the horizontal axes of FIGS. 11, 12 and 10 are changed to the bearing radius R.
  • the replaced FIG. 13 will be described. Even when the horizontal axis is expressed separately, the following conclusion can be obtained by following FIGS. 8 to 10.
  • the optimum a / R value increases as the bearing radius R becomes smaller in order to keep the roller engagement ratio Lt / Lr on the vertical axis (right side) at a predetermined value or less.
  • the maximum Hertz stress p max shown in FIG. 11 has a small difference due to the bearing radius R, and the a / R value is preferably 0.021 or more.
  • the backlash ⁇ due to CL1 shown in FIG. 12 increases as the bearing radius R decreases, so that the a / R value increases. Therefore, the optimum range of a / R when the bearing radius R is 23.5 mm is 0.021 to 0.046. In this way, the optimum range of the a / R value increases and the optimum range decreases when the diameter of the roller reduction device 10 is reduced.
  • the eccentricity a is in the range of 0.5 to 1.2 mm.
  • the durability of the inner teeth 4a can be ensured to the same extent as in the conventional case, and it can be designed so that problems such as locking do not occur.
  • roller speed reducer 10 described above can be applied to mechanical parts that require a speed reducer. In particular, it is effective when applied to a high reduction ratio that requires a reduction ratio of 30 or more and a mechanical component that requires downsizing.
  • FIG. 14 shows a side view of a valve timing control device 20 to which the roller speed reducer 10 is applied
  • FIG. 15 shows an external view of the roller speed reducer 10 applied to the valve timing control device 20.
  • a timing sprocket 14 which is a driving rotating body that is rotationally driven by a rotational force from a crankshaft of an internal combustion engine (not shown), is transmitted by a timing belt or a timing chain, and a bearing on a cylinder head (not shown).
  • Cam shaft 21, which is rotatably supported by the timing sprocket 14 and is rotated by the rotational force transmitted from the timing sprocket 14, a roller speed reducer 10 integrally formed on the timing sprocket 14, and an electric motor whose rotational state is controlled according to a control signal.
  • a possible valve timing control device 20 is constructed.
  • the controller 13 controls the rotation of the electric motor 11 so as to synchronize with the timing sprocket 14.
  • the rotation speed of the electric motor 11 is relatively rotated with respect to the timing sprocket 14 so that the roller speed reducer 10 integrally formed with the timing sprocket 14 rotates.
  • the relative rotation of the eccentric rotating body 5 and the annular member 4 makes it possible to adjust the phases of the timing sprocket 14 and the cage 3 that is fastened and fixed to the camshaft 21.
  • the roller speed reducer 10 mounted on the valve timing control device 20 generates an alternating torque via the camshaft 21 as the intake valve and the exhaust valve (engine valve) of the internal combustion engine urged in the closing direction by the valve spring move up and down. receive. Durability due to the surface pressure acting on the meshing portion between the roller and the inner teeth due to the alternating torque, and noise due to the impact striking sound between the roller and the inner teeth are generated. Therefore, by using the roller speed reducer 10 to which the optimum eccentricity a of the present invention is applied, it is possible to provide a valve timing control device with reduced durability and noise.
  • valve timing control device when the valve timing control device is applied to both the intake valve and the exhaust valve, it is necessary to reduce the diameter to prevent interference. Similarly, as the diameter of the roller speed reducer 10 is reduced, the valve timing control device with high reliability can be provided by setting the optimum eccentricity a of the present invention.
  • the present invention is not limited to the valve timing control device 20 described as an example, but can be applied to all devices equipped with a speed reducer. In particular, it is possible to improve reliability even in a device having a large load torque to be controlled.
  • roller reducer 1 Medium diameter ball bearing 1a ... Inner ring of medium diameter ball bearing 1b ... Outer ring of medium diameter ball bearing 1c ... Ball between inner ring and outer ring 2 ... Roller 3 ... Retainer 3a ... Roller holding hole 3b ... Rib Part 4 ... Annular member 4a ... Inner teeth 5 ... Eccentric rotating body 11 ... Electric motor 13 ... Controller 14 ... Timing sprocket 15 ... Shaft joint 16 ... Cover member 20 ... Valve timing control device 21 ... Camshaft

Abstract

La présente invention aborde le problème de la réduction du bruit d'entrechoquement des corps de roulement et les parties de mise en prise, par l'optimisation du degré d'excentricité qui est la distance entre le centre d'un corps rotatif excentrique et le centre d'un palier pour réduire le jeu dans un réducteur de vitesse, et également le problème d'obtention d'une durabilité améliorée par la réduction de la pression de surface agissant sur les corps de roulement et les parties de mise en prise. Ce réducteur de vitesse de type à rouleau comprend : un corps rotatif excentrique sur la périphérie extérieure duquel est prévue une partie came arquée circulaire qui est excentrique dans une direction radiale à partir d'un centre de rotation ; un palier disposé sur la périphérie extérieure du corps rotatif excentrique et supportant de façon rotative le corps rotatif excentrique ; un élément annulaire disposé sur la périphérie extérieure du palier et possédant des dents internes ondulées sur la surface périphérique intérieure ; une pluralité de corps de roulement prévus à des intervalles sensiblement égaux dans une direction circonférentielle sur la périphérie extérieure du palier et sur la périphérie intérieure de l'élément annulaire, et configurés de telle sorte que les parties des corps de roulement qui viennent en prise avec les dents internes, se déplacent dans la direction circonférentielle lorsque le corps rotatif excentrique tourne de manière excentrique ; et un élément de retenue pour séparer la pluralité de corps de roulement les uns des autres et permettre aux corps de roulement de se déplacer dans la direction radiale. Si la distance d'excentricité de la partie came à partir du centre de rotation est désignée comme étant un degré d'excentricité a, le degré d'excentricité a se trouve dans la plage de 0,5 à 1,2 mm.
PCT/JP2019/032018 2018-11-01 2019-08-15 Réducteur de vitesse de type à rouleaux et dispositif à soupapes variable pour moteur à combustion interne WO2020090186A1 (fr)

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JP2018-206367 2018-11-01
JP2018206367A JP2020070771A (ja) 2018-11-01 2018-11-01 ローラ減速装置、及び、内燃機関の可変動弁装置

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05231482A (ja) * 1992-02-18 1993-09-07 Sumitomo Heavy Ind Ltd 内接噛合式遊星歯車構造を採用した増減速機シリーズ
JP2012092720A (ja) * 2010-10-26 2012-05-17 Denso Corp 可変バルブタイミング装置
JP2016017417A (ja) * 2014-07-07 2016-02-01 日立オートモティブシステムズ株式会社 バルブタイミング制御装置
DE102016109150A1 (de) * 2016-03-01 2017-09-07 Maul Konstruktionen GmbH Mechanisch geregelte Achsverstellung an Exzentergetrieben

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05231482A (ja) * 1992-02-18 1993-09-07 Sumitomo Heavy Ind Ltd 内接噛合式遊星歯車構造を採用した増減速機シリーズ
JP2012092720A (ja) * 2010-10-26 2012-05-17 Denso Corp 可変バルブタイミング装置
JP2016017417A (ja) * 2014-07-07 2016-02-01 日立オートモティブシステムズ株式会社 バルブタイミング制御装置
DE102016109150A1 (de) * 2016-03-01 2017-09-07 Maul Konstruktionen GmbH Mechanisch geregelte Achsverstellung an Exzentergetrieben

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