WO2020129661A1 - Actionneur pour mécanisme de compression variable de moteur à combustion interne et réducteur de vitesse - Google Patents

Actionneur pour mécanisme de compression variable de moteur à combustion interne et réducteur de vitesse Download PDF

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Publication number
WO2020129661A1
WO2020129661A1 PCT/JP2019/047554 JP2019047554W WO2020129661A1 WO 2020129661 A1 WO2020129661 A1 WO 2020129661A1 JP 2019047554 W JP2019047554 W JP 2019047554W WO 2020129661 A1 WO2020129661 A1 WO 2020129661A1
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WIPO (PCT)
Prior art keywords
speed reducer
gear
actuator
output shaft
combustion engine
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PCT/JP2019/047554
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English (en)
Japanese (ja)
Inventor
健 ブライアン 池口
正登 真子
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日立オートモティブシステムズ株式会社
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Publication of WO2020129661A1 publication Critical patent/WO2020129661A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear

Definitions

  • the present invention relates to a speed reducer and an actuator of a variable compression mechanism of an internal combustion engine.
  • Patent Document 1 has a control shaft of a variable compression ratio mechanism and an actuator for changing the rotational position of the control shaft, and the actuator has a wave gear deceleration for decelerating the rotational speed of an electric motor and transmitting the decelerated speed to the control shaft. Machine is disclosed.
  • Patent Document 1 has an advantage of having a large torque capacity by obtaining a maximum meshing region because the wave gear device meshes with the rigid internal gear by utilizing the metal elasticity of the elastic external gear. Therefore, the friction loss increases due to the large total contact area of the teeth, that is, the output transmission efficiency of the gear device also decreases. In particular, as the reduction ratio is increased, the total contact area of the teeth is also increased. Therefore, the torque obtained by decelerating the input is also reduced in output due to the increase in loss. There is also a method of increasing the total reduction ratio by combining multi-stage normal rotation type gear mechanism with low loss, but different gear systems must be connected, and there are problems such as enlargement of gear device and increase in the number of parts. Occurs.
  • an input shaft having a sun gear, and a wave generator having a non-circular outer shape in a cross section in a direction perpendicular to a rotating shaft and having first inner teeth on an inner circumference, and the wave generator.
  • a flexible external gear having a flexible tubular body portion that flexes in a non-circular shape by means of, and external teeth provided on an outer peripheral surface of the body portion, and the flexible deformed body portion of the body portion.
  • An internal gear member having second internal teeth that mesh with external teeth, a housing to which the internal gear member is fixed, an output shaft that rotates integrally with the flexible external gear, the output shaft, the housing, or the flexible shaft. It has a plurality of support shafts held by a flexible external gear, and a plurality of planet gears rotatably arranged on the plurality of support shafts and meshing with the sun gear and the second internal teeth.
  • FIG. 1 is a schematic diagram of an internal combustion engine equipped with an actuator of a variable compression mechanism of an internal combustion engine to which the present invention is applied.
  • 3 is a perspective view of an actuator of the variable compression ratio mechanism of Embodiment 1.
  • FIG. FIG. 3 is an exploded perspective view of the speed reducer of the first embodiment.
  • 3 is an exploded perspective view of the planetary gear mechanism of Embodiment 1.
  • FIG. 3 is a perspective view showing a first assembled state (a state in which three support shafts are attached) of the planetary gear according to the first embodiment.
  • FIG. 3 is a perspective view showing a second assembled state (a state in which a planetary gear is attached to a support shaft) of the planetary gear of the first embodiment.
  • FIG. 6 is a perspective view showing a third assembled state (a state in which a cap is attached to the support shaft) of the planetary gear according to the first embodiment.
  • 3 is a sectional view of an actuator of the variable compression ratio mechanism of Embodiment 1.
  • FIG. 9 is a cross-sectional view taken along the line AA of FIG. 8 of the first exemplary embodiment.
  • FIG. 9 is a cross-sectional view taken along line BB of FIG. 8 of the first embodiment.
  • 3 is a schematic diagram showing the relationship between the flexible external gear and the planetary gears of Embodiment 1.
  • FIG. FIG. 7 is a perspective view showing a mounted state of a planetary gear according to the second embodiment.
  • FIG. 1 is a schematic diagram of an internal combustion engine including an actuator of a variable compression mechanism of an internal combustion engine to which the present invention is applied.
  • the basic configuration is the same as that shown in FIG. 1 of Japanese Patent Laid-Open No. 2017-218978, and therefore will be briefly described.
  • An upper end of an upper link 3 is rotatably connected to a piston 1 that reciprocates in a cylinder of a cylinder block of an internal combustion engine via a piston pin 2.
  • the lower link 5 is rotatably connected to the lower end of the upper link 3 via a connecting pin 6.
  • the crankshaft 4 is rotatably connected to the lower link 5 via a crankpin 4a.
  • the upper end of the first control link 7 is rotatably connected to the lower link 5 via a connecting pin 8.
  • the lower end of the first control link 7 is connected to a connecting mechanism 9 having a plurality of link members.
  • the connecting mechanism 9 includes a first control shaft 10, a second control shaft 11 that is an output shaft, and an actuator link 12 that connects the first control shaft 10 and the second control shaft 11.
  • the first control shaft 10 extends parallel to the crankshaft 4 that extends in the cylinder column direction inside the internal combustion engine.
  • the first control shaft 10 includes a first journal portion 10 a rotatably supported by the internal combustion engine body, a control eccentric shaft portion 10 b rotatably connected to a lower end portion of the first control link 7, and an actuator link 12.
  • An eccentric shaft portion 10c having one end portion 12a rotatably connected thereto.
  • One end of the first arm portion 10d is connected to the first journal portion 10a, and the other end thereof is connected to the lower end portion of the first control link 7.
  • the control eccentric shaft portion 10b is provided at a position eccentric to the first journal portion 10a by a predetermined amount.
  • the second arm 10e has one end connected to the first journal 10a and the other end connected to one end 12a of the actuator link 12.
  • the eccentric shaft portion 10c is provided at a position eccentric to the first journal portion 10a by a predetermined amount.
  • the other end 12b of the actuator link 12 is rotatably connected to one end of an arm link 13.
  • the second control shaft 11 is connected to the other end of the arm link 13.
  • the arm link 13 and the second control shaft 11 do not move relative to each other.
  • the second control shaft 11 is rotatably supported in a housing (not shown) via a plurality of journal portions described later.
  • the actuator link 12 has a lever shape, and one end portion 12a connected to the eccentric shaft portion 10c is formed substantially linearly.
  • the rotational position of the second control shaft 11 is changed by the torque transmitted from the drive motor 40 via the speed reducer 20, which is a part of the actuator 200 of the variable compression ratio mechanism described later.
  • the rotation position of the second control shaft 11 is changed, the posture of the second control link 12 is changed and the first control shaft 10 is rotated, so that the position of the lower end portion of the first control link 7 is changed.
  • the posture of the lower link 5 changes, the stroke position and stroke amount of the piston 1 in the cylinder change, and the engine compression ratio changes accordingly.
  • FIG. 2 is a perspective view of the actuator of the variable compression ratio mechanism of the first embodiment
  • FIG. 3 is an exploded perspective view of the speed reducer of the first embodiment
  • FIG. 4 is an exploded view of the planetary gear mechanism of the first embodiment.
  • FIG. 5 is a perspective view showing a first assembled state (a state where three support shafts are attached) of the planetary gear of the first embodiment
  • FIG. 6 is a perspective view of the planetary gear of the first embodiment.
  • FIG. 8 is a perspective view showing a second assembled state (state in which a planetary gear is attached to a support shaft)
  • FIG. 7 is a third assembled state of the planetary gear of Embodiment 1 (state in which a cap is attached to the support shaft). ) Is a perspective view.
  • the actuator 200 of the variable compression ratio mechanism is a housing that houses a drive motor 40 and a speed reducer 20 having a wave gear mechanism and a planetary gear mechanism inside. 30 and the second control shaft 11 and the like. Details will be described later.
  • the speed reducer 20 has a planetary gear mechanism 20a and a wave gear mechanism 20b. That is, the wave gear mechanism 20b includes the internal gear member 24 having a plurality of second internal teeth 24a on its inner peripheral surface and the wave generating plug 23 having a plurality of first internal teeth 23a on its inner peripheral surface forming the wave generator 300. And a deep groove ball bearing 22 in which an inner ring is press-fitted and fixed to the outer peripheral surface 23c of the wave generating plug 23, and an outer peripheral surface of a cylindrical body portion 210 having a body portion first end 210a and a body portion second end 210b. It is composed of a plurality of external teeth 21b provided and a flexible external gear 21 having a female spline 21a provided on the inner peripheral surface.
  • the planetary gear mechanism 20 a includes three planetary gears 31 provided at the tip end on the right side of the second control shaft 11 in the figure, a sun gear 25 a provided at the tip end of the motor output shaft 25, and a wave generator 300. It is composed of a plurality of first internal teeth 23a provided on the inner circumference of the wave generating plug 23.
  • the internal gear member 24 is fixed to the housing 30 by being bolted to the female screw hole 30b of the housing 30 through the through hole 24b.
  • the wave generation plug 23 forming the wave generator 300 has an elliptical shape, and the deep groove ball bearing 22 is flexible to allow relative rotation between the outer circumference of the wave generation plug 23 and the inner circumference of the flexible external gear 21.
  • the inner ring is press-fitted and fixed to the outer peripheral surface 23c.
  • the flexible external gear 21 is provided with a wave generating plug 23 and a deep groove ball bearing 22 which form the wave generator 300 on the inner diameter side thereof, so that the plurality of outer teeth 21b mesh with the plurality of second inner teeth 24a. Is arranged on the inner diameter side of the internal gear member 24.
  • the second control shaft 11 has a male spline 11e on the left side of the three planetary gears 31 in the figure, and the three planetary gears 31 are sun gears 25a provided at the tip of a motor output shaft 25 that is an input shaft.
  • the male spline 11e is provided so as to engage with the female spline 21a of the flexible external gear 21.
  • the bearing 50 is provided between the flange portion 23 b of the wave generating plug 23 and the housing 30 and supports the wave generating plug 23.
  • the female screw hole 30a is provided for mounting and fixing a housing (not shown).
  • the rotation axis P is the rotation axis of the motor output shaft 25, the speed reducer 20, and the second control shaft 11.
  • the planetary gear mechanism 20a is provided on the sun gear 25a provided at the tip of the motor output shaft 25, the three planetary gears 31, and the inner periphery of the wave generation plug 23 forming the wave generator 300. It is composed of a plurality of first internal teeth 23a.
  • the three support shafts 33 which respectively rotatably support the three planetary gears 31 at the small diameter portion 33b, are provided in the three insertion holes 11d provided on the tip end surface of the second control shaft 11 provided with the male spline 11e, The large diameter portion 33a is press-fitted and fixed, and is held by the second control shaft 11.
  • the support shaft 33 may be rotatably held by the second control shaft 11.
  • the reduction gear 20 can be downsized in the direction of the rotation axis P.
  • a step function between the large diameter portion 33a and the small diameter portion 33b can provide a stopper function for restricting the axial movement of the planetary gear 31.
  • Each of the three support shafts 33 rotatably supports the planetary gear 31, and then press-fits and fixes the cap 32 having the three through holes 32a into the small diameter portion 32b of the support shaft 33.
  • the cap 32 can have a stopper function of restricting the axial movement of the planetary gear 31.
  • the second control shaft 11 has a small diameter first journal portion 11c supported by a housing (not shown) on the tip side (left side in the figure) and an intermediate diameter into which the arm link 13 is press-fitted from the first journal portion 11c side. It has a fixed portion 11b and a large diameter second journal portion 11a as a large diameter portion supported by a housing (not shown). Further, a lubricating oil passage 110 is provided at the center of the second control shaft 11 in the rotation axis P direction. The opening 111 of the lubricating oil passage 110 is formed in a tapered shape. The three support shafts 33 that support the planetary gears 31 are fixed and held outside the opening 111 in the radial direction. As a result, the planetary gear 31 can be lubricated. Further, the tapered shape of the opening 111 can be used as a pressing surface when the second control shaft 11 is press-fitted into the arm link 13, and can fulfill a centering function.
  • FIG. 8 is a sectional view of the actuator of the variable compression ratio mechanism of the first embodiment
  • FIG. 9 is a sectional view taken along line AA of FIG. 8 of the first embodiment
  • 10 is a sectional view taken along line BB of FIG. 8 of the first embodiment.
  • the actuator 200 of the variable compression ratio mechanism includes a drive motor 40 and a speed reducer 20 including a planetary gear mechanism 20a and a wave gear mechanism 20b.
  • the drive motor 40 is a brushless motor, and has a bottomed cylindrical motor casing 41, a cylindrical coil 40a fixed to the inner peripheral surface of the motor casing 41, and a rotor rotatably provided inside the coil 40a. 40b and a motor output shaft 25 whose one end 25b is fixed to the center of the rotor 40b.
  • the motor output shaft 25 is rotatably supported by a ball bearing 51 provided on the bottom of the motor casing 41 and a ball bearing 53 provided on the housing 30.
  • the motor casing 41 has four boss portions 41a on the outer circumference of the front end. A bolt insertion hole 41b for inserting a bolt (not shown) is formed through the boss portion 41a.
  • the motor casing 41 When the motor casing 41 is attached to the housing 30, the O-ring 100 is interposed between the housing 30 and the motor casing 41, and the bolt is inserted into the bolt insertion hole 41b of the boss portion 41a. The bolt is fastened to the female screw portion 30d provided on the. As a result, the motor casing 41 is fixed to the housing 30.
  • the motor housing chamber that houses the drive motor 40 by the motor casing 41 and the housing 30 is configured as a drying chamber that does not supply lubricating oil or the like due to the seal member 52 disposed between the housing 30 and the motor output shaft 25.
  • the speed reducer 20 has the planetary gear mechanism 20a and the wave gear mechanism 20a, as described above.
  • the sun gear 25a provided at the tip of the motor output shaft 25 has a small diameter portion of the three support shafts 33 in which the large diameter portion 33a is inserted and fixed in the three insertion holes 11d provided in the end surface of the second control shaft 11. It meshes with three planetary gears 31 rotatably supported by 33b. Further, the three planetary gears 31 also mesh with a plurality of first internal teeth 23 a provided on the inner peripheral surface of the wave generation plug 23 forming the wave generator 300.
  • the rotation of the motor output shaft 25 is decelerated by the reverse rotation and transmitted to the wave generation plug 23 forming the wave generator 300.
  • the support shafts 33 of the three planetary gears 31 are fixed to the tip of the second control shaft 11, but the rotation of the second control shaft 11 is greatly reduced by the wave gear mechanism 20b. Compared with the rotation of the output shaft 25, the rotation is very small (substantially the same as in the stopped state), and there is no influence on the operation of the planetary gear mechanism 20a. Further, the three support shafts 33 may be fixed to the flexible external gear 21 that rotates in the same manner as the second control shaft 11.
  • the meshing positions of the three planetary gears 31 constituting the planetary gear mechanism, the plurality of first internal teeth 23a of the wave generating plug 23, the sun gear 25a of the motor output shaft 25, and the plurality of external teeth of the flexible external gear 21. 21b and the plurality of second internal teeth 24a of the internal gear member 24 are arranged so as to overlap with each other in the direction of the rotation axis P. Thereby, the inclination of the wave generator 300 can be suppressed with respect to the rotation of the motor output shaft 25.
  • the wave gear mechanism 20b includes the wave generator 300, the flexible external gear 21, and the rigid internal gear 24.
  • the wave generation plug 23 has an elliptical outer shape
  • the deep groove ball bearing 22 has a flexible thin inner and outer ring that allows relative rotation between the outer circumference of the wave generation plug 23 and the inner circumference of the flexible external gear 21.
  • the inner ring is press-fitted and fixed to the outer peripheral surface 23c of the wave generation plug 23 to form the wave generator 300.
  • the elliptical wave generation plug 23 is fitted into the inner ring of the deep groove ball bearing 22, and the deep groove ball bearing 22 also follows the elliptical shape.
  • the outer diameter is elliptical.
  • the bearing 50 is provided between the flange portion 23b of the wave generation plug 23 and the housing 30 to support the wave generation plug 23.
  • the size of the radial play ⁇ of the bearing 50 is set smaller than the size of the radial play ⁇ between the three planetary gears 31 and the plurality of first internal teeth 23a.
  • the flexible external gear 21 is provided with a wave generating plug 23 and a deep groove ball bearing 22 forming a wave generator 300 on the inner diameter side, and the outer ring of the deep groove ball bearing 22 is a tubular body of the flexible external gear 21. It fits with the inner peripheral surface of the body 210 that overlaps with the plurality of outer teeth 21b provided on the outer peripheral surface of the portion 210 in the direction of the rotation axis P. Further, the flexible external gear 21 is arranged on the inner diameter side of the internal gear member 24 fixed to the housing 30 so that the plurality of outer teeth 21b mesh with the plurality of second inner teeth 24a of the inner gear member 24. Has been done.
  • the flexible external gear 21 is made of a metal material, and has a body first end 210a and a body second end 210b extending in the direction of the rotation axis P, and a body 210 of the body 210, and a body first end of the body 210.
  • a flexible thin-walled cylindrical member having a bottom portion 211 extending radially inward with respect to the rotation axis P direction from the portion 210a, and a highly rigid flange portion 212 continuously extending from the bottom portion 211 in the same rotation axis P direction as the body portion 210. Is.
  • the number of teeth of the plurality of outer teeth 21b of the flexible outer gear 21 is two less than the number of teeth of the plurality of second inner teeth 24a of the inner gear member 24.
  • An insertion hole 212a having a female spline 21a through which the second control shaft 11 penetrates is provided on the inner periphery of the flange 212 that is provided continuously to the bottom 211 of the flexible external gear 21
  • the wave generating plug 23 and the deep groove ball bearing 22 that form the wave generator 300 are formed in an elliptical shape, and the outer peripheral surface of the outer ring of the deep groove ball bearing 22 slides along the inner peripheral surface of the flexible external gear 21. .. Further, by fitting the wave generating plug 23 forming the wave generator 300 and the deep groove ball bearing 2 into the inner diameter of the flexible external gear 21, the flexible external gear 21 having an initial circular shape also has an elliptical shape. And transform.
  • the flexible external gear 21 bent into an ellipse has two teeth less than the rigid internal gear 24, and therefore meshes due to the deviation of the tooth pitch on the major axis of the ellipse, and the tooth pitch matches on the minor axis of the ellipse. Since the flexible external gear 21 is flexed in the axial direction, the teeth do not overlap with each other and do not interfere with each other.
  • the tooth portion of the flexible external gear 21 is flexible, the flange portion 212 cannot be deformed from the circular shape to take out the output, and is directly fastened to the second control shaft 11 by spline fitting. Therefore, the flange portion 212 is the starting point and the shape is expanded to an elliptical shape toward the thin-walled cylindrical opening end portion. That is, the rotational movement of the flexible external gear 21 extracted from the deformation movement near the opening end can be transmitted from the flange 212 to the second control shaft 11. Since the flexible external gear 21 has two teeth less than the rigid internal gear 24 by the number of teeth of the wave generator 300, the number of tooth differences is two when the wave generator 300 makes one rotation (360 degrees). Only, the flexible external gear 21 rotates in the opposite direction.
  • the rotation of the wave generator 300 is reversed to the flexible external gear 21 (the motor output shaft 25 In the same rotation direction), the speed is reduced at a very large reduction ratio and transmitted, and further transmitted to the second control shaft 11 that is spline-fitted.
  • the wave gear mechanism 20b including the planetary gear mechanism 20a in the two-stage speed reduction configuration a high reduction ratio and high efficiency can be achieved. That is, if a high reduction ratio is realized only by the wave gear mechanism 20b, it is necessary to reduce the internal teeth and the external teeth of the wave gear mechanism 20b, which increases the number of meshed teeth and the contact area accordingly.
  • the transmission efficiency is likely to decrease due to the frictional resistance, but by adopting the two-step speed reduction configuration, a large reduction ratio can be realized without reducing the internal teeth and external teeth of the wave gear mechanism 20b. The efficiency can be improved. Further, since it is not necessary to reduce the inner teeth and the outer teeth of the wave gear mechanism 20b, it is possible to suppress meshing slippage (ratcheting). Further, since the wave generator 300 is integrated with the planetary gear mechanism 20a, the number of parts can be reduced.
  • FIG. 11 is a schematic diagram showing the relationship between the flexible external gear and the planetary gear according to the first embodiment.
  • the distance a from the rotation axis P to the tooth tip on the outermost diameter side of the planetary gear 31 is the distance to the tooth tip on the innermost side of the female spline 21a provided on the inner circumference of the flange portion 212 of the flexible external gear 21. It is set shorter than the distance b.
  • the second control shaft 11 on which the planetary gear 31 is mounted is attached to the inner periphery of the male spline 11e provided on the second control shaft 11 and the flange portion 212 of the flexible external gear 21.
  • the planetary gear 31 and the female spline 21a can be assembled without interfering with each other when inserting and assembling.
  • the speed reducer and the actuator of the variable compression mechanism for the internal combustion engine according to the first embodiment have the operational effects listed below.
  • the speed reducer 20 has a two-stage speed reduction configuration with the wave gear mechanism 20b including the planetary gear mechanism 20a. Therefore, if a high reduction ratio is realized only by the wave gear mechanism 20b, it is necessary to reduce the internal teeth and the external teeth of the wave gear mechanism 20b, which increases the number of meshed teeth and increases the contact area. However, the transmission efficiency is likely to decrease due to the frictional resistance, but by adopting the two-step speed reduction configuration, a large reduction ratio can be realized without reducing the internal teeth and external teeth of the wave gear mechanism 20b.
  • the efficiency can be improved, and since the internal teeth and external teeth of the wave gear mechanism 20b do not have to be made small, slippage (ratcheting) of meshing can be suppressed, and the wave generator 300 is integrated with the planetary gear mechanism 20a. Therefore, the number of parts can be reduced.
  • the three support shafts 33 that respectively rotatably support the three planetary gears 31 at the small diameter portion 33b have three insertion holes provided in the tip end surface of the second control shaft 11 where the male spline 11e is provided.
  • the large-diameter portion 33a is press-fitted and fixed to 11d so as to be held on the second control shaft 11. Therefore, the reduction gear 20 can be downsized in the direction of the rotation axis P.
  • the rotation speed of the motor output shaft 25 is significantly reduced and transmitted to the second control shaft 11 by the planetary gear mechanism 20a and the wave gear mechanism 20b, the support shaft of the planet gear 31 is transmitted to the second control shaft 11.
  • the support shaft 33 By holding (fixing or rotatably holding) 33, the support shaft 33 can be considered without much difference from fixing the support shaft 33 to the housing 30 or the like.
  • the male spline 11e of the second control shaft 11 penetrates the bottom portion 211.
  • the support shaft 33 may be held by the bottom portion 211, or the second control shaft 11 may be held by another member. Is also good.
  • the radial play ⁇ of the bearing 50 supporting the wave generator 300 is set to be smaller than the radial play ⁇ between the three planetary gears 31 and the plurality of first inner teeth 23a. I chose Therefore, even if a radial load acts on the wave generator 300 due to a reverse input from the second control shaft 11, the bearing 50 can receive the load, and the load acts on the three planetary gears 31. Can be suppressed.
  • the distance a from the rotation axis P to the tooth tip on the outermost diameter side of the planetary gear 31 is the innermost tooth of the female spline 21a provided on the inner circumference of the flange portion 212 of the flexible outer gear 21.
  • the distance b to the tip is set to be shorter. Therefore, the second control shaft 11 on which the planetary gear 31 is mounted is fitted to the male spline 11e provided on the second control shaft 11 and the female spline 21a provided on the inner periphery of the flange portion 212 of the flexible external gear 21. In order to make them fit, the planetary gear 31 and the female spline 21a can be assembled without interfering with each other when they are inserted and assembled.
  • the three support shafts 33 rotatably hold the large diameter portion 33a that is fixedly held by the second control shaft 11 and the three planetary gears 31, and the small diameter portion 33b that is smaller in diameter than the large diameter portion 33a. To have. Therefore, a step difference between the large-diameter portion 33a and the small-diameter portion 33b can provide a stopper function of restricting the axial movement of the planetary gear 31.
  • the three support shafts 33 rotatably support the planetary gear 31, and then the cap 32 having the three through holes 32a is press-fitted and fixed to the small diameter portion 33b of the support shaft 33. Therefore, the cap 32 can have a stopper function of restricting the movement of the planetary gear 31 in the axial direction.
  • the meshing positions of the teeth 21b and the plurality of second inner teeth 24a of the inner gear member 24 are arranged so as to overlap in the direction of the rotation axis P. Therefore, the inclination of the wave generator 300 can be suppressed with respect to the rotation of the motor output shaft 25.
  • a lubricating oil passage 110 is provided in the center of the second control shaft 11 in the direction of the rotation axis P, and the three support shafts 33 that support the planetary gears 31 are fixed and held outside the opening 111 in the radial direction. I decided to do it. Therefore, the planetary gear 31 can be lubricated.
  • the opening 111 of the lubricating oil passage 11 is formed in a tapered shape. Therefore, the tapered shape of the opening 111 can be used as a pressing surface when the second control shaft 11 is press-fitted into the arm link 13, and can perform a centering function.
  • FIG. 12 is a perspective view showing a mounted state of a planetary gear according to a second embodiment.
  • the three support shafts 33 that rotatably support the three planetary gears 31 at the small diameter portion 33b are supported by the housing 30.
  • the three support shafts 33 are fixed and held in the housing 30 radially outside the sun gear 25a of the motor output shaft 25. Since the other configurations are the same as those of the first embodiment, the same reference numerals are given to the same configurations and the description thereof will be omitted.
  • the speed reducer and the actuator of the variable compression mechanism of the internal combustion engine according to the second embodiment have the same effects as the first embodiment.
  • the speed reducer has a non-circular outer shape in a cross section in a direction perpendicular to an input shaft having a sun gear and a rotation axis, and a wave generator having first inner teeth on an inner periphery, and the wave generator.
  • a flexible external gear having a flexible tubular body portion that flexes in a non-circular shape by means of, and external teeth provided on an outer peripheral surface of the body portion, and the flexible deformed body portion of the body portion.
  • An internal gear member having second internal teeth that mesh with external teeth, a housing to which the internal gear member is fixed, an output shaft that rotates integrally with the flexible external gear, the output shaft, the housing, or the flexible shaft. It has a plurality of support shafts held by a flexible external gear and a plurality of planetary gears rotatably arranged on the plurality of support shafts and meshing with the sun gear and the first internal teeth.
  • the flexible external gear has the first body portion out of the first body portion end portion and the second body portion end portion that are both end portions of the body portion in the direction of the rotation axis.
  • the output shaft has a bottom portion extending inward in the radial direction from the end portion, the output shaft extends through the bottom portion, and the plurality of support shafts are held by the output shaft.
  • a bearing is further provided between the wave generator and the housing, and a size of radial play of the bearing is equal to that of the plurality of planetary gears and the first internal teeth. It is smaller than the amount of radial play between them.
  • the output shaft has a male spline on the outer circumference
  • the bottom portion has a female spline fitted to the male spline on the inner circumference
  • the plurality of planetary gears are The first distance from the rotation axis of the output shaft to the outermost portion in the direction perpendicular to the rotation axis is the second distance from the rotation axis of the output shaft to the innermost portion in the direction perpendicular to the rotation axis of the female spline. Shorter than the distance.
  • the plurality of support shafts have a large-diameter portion with a large diameter held by the output shaft and the plurality of planetary gears, respectively, and are larger than the large-diameter portion. Also has a small diameter portion with a small diameter.
  • there is a cap that is disposed on the opposite side of the large diameter portion in the axial direction of the plurality of support shafts and restricts the axial movement of the plurality of planetary gears.
  • the plurality of support shafts are held by the housing.
  • an actuator of a variable compression mechanism of an internal combustion engine has a drive motor having a motor shaft provided with a sun gear, a cross section of a cross section in a direction perpendicular to a rotation axis that is non-circular, and a first inner circumference.
  • Flexibility having a wave generator having internal teeth, a flexible cylindrical body that is bent in a non-circular shape by the wave generator, and external teeth provided on the outer peripheral surface of the body.
  • a plurality of support shafts held by the output shaft or the housing or the flexible external gear, and the plurality of support shafts Each is rotatably arranged and has the sun gear and a plurality of planetary gears that mesh with the first internal teeth.
  • the flexible external gear has the first body portion out of the first body portion end portion and the second body portion end portion that are both end portions of the body portion in the direction of the rotation axis.
  • the output shaft has a bottom portion extending inward in the radial direction from the end portion, the output shaft extends through the bottom portion, and the plurality of support shafts are held by the output shaft.
  • a bearing is further provided between the wave generator and the housing, and the radial play of the bearing is the same as that of the plurality of planetary gears and the first gear. It is smaller than the amount of radial play between the inner teeth.
  • the output shaft has an oil passage in an axial direction inside thereof, the oil passage has an opening portion facing the motor shaft, and the plurality of supports are provided. The shaft is arranged radially outside the opening. In a more preferred aspect, in the above aspect, the opening is tapered.
  • the present invention is not limited to the above-described embodiment, and various modifications are included.
  • the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the configurations described.
  • a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Retarders (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un actionneur pour un mécanisme de compression variable d'un moteur à combustion interne et un réducteur de vitesse. Le réducteur de vitesse a une configuration de double réduction formée par un mécanisme d'engrenage ondulé qui comprend un mécanisme d'engrenage planétaire.
PCT/JP2019/047554 2018-12-21 2019-12-05 Actionneur pour mécanisme de compression variable de moteur à combustion interne et réducteur de vitesse WO2020129661A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-239189 2018-12-21
JP2018239189A JP2020101118A (ja) 2018-12-21 2018-12-21 減速機及び内燃機関の可変圧縮機構のアクチュエータ

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WO2020129661A1 true WO2020129661A1 (fr) 2020-06-25

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JP (1) JP2020101118A (fr)
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220112848A1 (en) * 2020-10-12 2022-04-14 Schaeffler Technologies AG & Co., KG Actuation assembly for phaser system
US20220252015A1 (en) * 2021-02-11 2022-08-11 Schaeffler Technologies AG & Co. KG Cranktrain phase adjuster for variable compression ratio
US11428173B2 (en) * 2020-10-06 2022-08-30 Schaeffler Technologies AG & Co. KG Cranktrain phase adjuster for variable compression ratio

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4946374Y1 (fr) * 1971-04-16 1974-12-18
JPS5435630B2 (fr) * 1975-02-17 1979-11-05
JPS6353037U (fr) * 1986-09-24 1988-04-09
JPH07119800A (ja) * 1993-10-23 1995-05-09 Teijin Seiki Co Ltd オイルシール付撓み噛み合い式歯車装置
JP2011220386A (ja) * 2010-04-06 2011-11-04 Canon Inc 波動歯車装置及びロボットアーム
JP2017201207A (ja) * 2016-05-03 2017-11-09 健騰精密機電股▲ふん▼有限公司 複合型減速機
JP2017218978A (ja) * 2016-06-08 2017-12-14 日立オートモティブシステムズ株式会社 内燃機関用リンク機構のアクチュエータ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4946374Y1 (fr) * 1971-04-16 1974-12-18
JPS5435630B2 (fr) * 1975-02-17 1979-11-05
JPS6353037U (fr) * 1986-09-24 1988-04-09
JPH07119800A (ja) * 1993-10-23 1995-05-09 Teijin Seiki Co Ltd オイルシール付撓み噛み合い式歯車装置
JP2011220386A (ja) * 2010-04-06 2011-11-04 Canon Inc 波動歯車装置及びロボットアーム
JP2017201207A (ja) * 2016-05-03 2017-11-09 健騰精密機電股▲ふん▼有限公司 複合型減速機
JP2017218978A (ja) * 2016-06-08 2017-12-14 日立オートモティブシステムズ株式会社 内燃機関用リンク機構のアクチュエータ

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11428173B2 (en) * 2020-10-06 2022-08-30 Schaeffler Technologies AG & Co. KG Cranktrain phase adjuster for variable compression ratio
US20220112848A1 (en) * 2020-10-12 2022-04-14 Schaeffler Technologies AG & Co., KG Actuation assembly for phaser system
US11619182B2 (en) * 2020-10-12 2023-04-04 Schaeffler Technologies AG & Co. KG Actuation assembly for phaser system
US20220252015A1 (en) * 2021-02-11 2022-08-11 Schaeffler Technologies AG & Co. KG Cranktrain phase adjuster for variable compression ratio
US11519342B2 (en) * 2021-02-11 2022-12-06 Schaeffler Technologies AG & Co. KG Cranktrain phase adjuster for variable compression ratio

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