WO2020129661A1 - Actuator for variable compression mechanism of internal combustion engine and speed reducer - Google Patents

Actuator for variable compression mechanism of internal combustion engine and speed reducer 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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WO
WIPO (PCT)
Prior art keywords
speed reducer
gear
actuator
output shaft
combustion engine
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PCT/JP2019/047554
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French (fr)
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/en

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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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Abstract

Regarding an actuator for a variable compression mechanism of an internal combustion engine and a speed reducer according to the present invention, the speed reducer has a double reduction configuration formed by a wave gear mechanism that includes therein a planetary gear mechanism.

Description

減速機及び内燃機関の可変圧縮機構のアクチュエータActuator of reduction gear and variable compression mechanism of internal combustion engine
　本発明は、減速機及び内燃機関の可変圧縮機構のアクチュエータに関する。 The present invention relates to a speed reducer and an actuator of a variable compression mechanism of an internal combustion engine.
　この種の技術としては、下記の特許文献１に記載の技術が開示されている。特許文献１には、可変圧縮比機構の制御軸と、この制御軸の回転位置を変更するアクチュエータを有し、アクチュエータには電動モータの回転数を減速して前記制御軸へ伝達する波動歯車減速機が開示されている。 As this type of technology, the technology described in Patent Document 1 below is disclosed. 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.
特開２０１２－２５１４４６号公報JP 2012-251446 A
　特許文献１に記載の技術では、波動歯車装置が弾性外歯車の金属弾性を利用して剛性内歯車とかみ合わせるため、極大かみ合い領域を得られることによる大トルク容量を有する利点があるが、一方で歯の総接触面積が大きいことによる摩擦損失の増大、すなわち歯車装置の出力伝達効率の低下も大きい。特に減速比を大きくするほど歯の総接触面積も大きくなっていくため、入力を大きく減速させて得られたトルクも損失の増大により出力が低くなる。損失が少ない通常回転系の歯車機構を多段に組み合わせて総減速比を大きくする手法も取られるが、異なる歯車系を接続させなければならず、歯車装置の大型化や部品点数の増大といった課題が生じる。 The technique described in 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.
　本発明は、歯車装置の大型化や部品点数の増大を抑制した減速機及び内燃機関の可変圧縮機構のアクチュエータを提供することを一つの目的とする。
　本発明の好ましい態様によれば、太陽歯車を有する入力軸と、回転軸の直角方向断面の外形が非円形であって、内周に第１内歯を有する波動発生器と、前記波動発生器により非円形に撓む可撓性を有する筒状の胴部と、前記胴部の外周面に設けられた外歯と、を有する可撓性外歯車と、撓み変形された前記胴部の前記外歯と噛み合う第２内歯を有する内歯車部材と、前記内歯車部材が固定されるハウジングと、前記可撓性外歯車と一体に回転する出力軸と、前記出力軸又は前記ハウジング又は前記可撓性外歯車に保持された複数の支持軸と、前記複数の支持軸にそれぞれ回転可能に配置され、前記太陽歯車と前記第２内歯と噛み合う複数の遊星歯車と、を有する。 It is an object of the present invention to provide a reduction gear and an actuator for a variable compression mechanism of an internal combustion engine that suppresses an increase in the size of a gear device and an increase in the number of parts.
According to a preferred aspect of the present invention, 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.
　よって、本発明の好ましい態様によれば、歯車装置の大型化や部品点数の増大を抑制することができる。 Therefore, according to a preferred aspect of the present invention, it is possible to suppress an increase in the size of the gear device and an increase in the number of parts.
本発明が適用される内燃機関の可変圧縮機構のアクチュエータを備えた内燃機関の概略図である。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. 実施形態１の可変圧縮比機構のアクチュエータの斜視図である。3 is a perspective view of an actuator of the variable compression ratio mechanism of Embodiment 1. FIG. 実施形態１の減速機の分解斜視図である。FIG. 3 is an exploded perspective view of the speed reducer of the first embodiment. 実施形態１の遊星歯車機構の分解斜視図である。3 is an exploded perspective view of the planetary gear mechanism of Embodiment 1. FIG. 実施形態１の遊星歯車の第１の組付け状態（３つの支持軸を取付けた状態）を示す斜視図である。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. 実施形態１の遊星歯車の第２の組付け状態（支持軸に遊星歯車を取付けた状態）を示す斜視図である。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. 実施形態１の遊星歯車の第３の組付け状態（支持軸にキャップを取付けた状態）を示す斜視図である。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. 実施形態1の可変圧縮比機構のアクチュエータの断面図である。3 is a sectional view of an actuator of the variable compression ratio mechanism of Embodiment 1. FIG. 実施形態1の図８のＡ－Ａ断面図である。FIG. 9 is a cross-sectional view taken along the line AA of FIG. 8 of the first exemplary embodiment. 実施形態1の図８のＢ－Ｂ断面図である。FIG. 9 is a cross-sectional view taken along line BB of FIG. 8 of the first embodiment. 実施形態１の可撓性外歯車と遊星歯車の関係を示す模式図である。3 is a schematic diagram showing the relationship between the flexible external gear and the planetary gears of Embodiment 1. FIG. 実施形態２の遊星歯車の取付け状態を示す斜視図である。FIG. 7 is a perspective view showing a mounted state of a planetary gear according to the second embodiment.
　〔実施形態１〕　図１は、本発明が適用される内燃機関の可変圧縮機構のアクチュエータを備えた内燃機関の概略図である。
　基本的な構成は、特開２０１７－２１８９７８号公報の図１に記載されているものと同じであるため、簡単に説明する。 First 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.
　内燃機関のシリンダブロックのシリンダ内を往復運動するピストン１には、ピストンピン２を介してアッパリンク３の上端が回転自在に連結されている。アッパリンク３の下端には、連結ピン６を介してロアリンク５が回転自在に連結されている。ロアリンク５には、クランクピン４ａを介してクランクシャフト４が回転自在に連結されている。
　また、ロアリンク５には、連結ピン８を介して第一制御リンク７の上端部が回転自在に連結されている。第一制御リンク７の下端部は、複数のリンク部材を有する連結機構９と連結されている。連結機構９は、第１制御軸１０と、出力軸である第２制御軸１１と、第１制御軸１０及び第２制御軸１１とを連結するアクチュエータリンク１２と、を有する。
　第１制御軸１０は、内燃機関内部の気筒列方向に延在するクランクシャフト４と平行に延在する。第１制御軸１０は、内燃機関本体に回転自在に支持される第一ジャーナル部１０ａと、第一制御リンク７の下端部が回転自在に連結される制御偏心軸部１０ｂと、アクチュエータリンク１２の一端部１２ａが回転自在に連結された偏心軸部１０ｃと、を有する。
　第一アーム部１０ｄは、一端が第一ジャーナル部１０ａと連結され、他端が第一制御リンク７の下端部と連結される。制御偏心軸部１０ｂは、第一ジャーナル部１０ａに対して所定量偏心した位置に設けられる。第二アーム部１０ｅは、一端が第一ジャーナル部１０ａと連結され、他端がアクチュエータリンク１２の一端部１２ａと連結される。
　偏心軸部１０ｃは、第一ジャーナル部１０ａに対して所定量偏心した位置に設けられる。アクチュエータリンク１２の他端部１２ｂは、アームリンク１３の一端が回転自在に連結されている。アームリンク１３の他端には、第２制御軸１１が連結されている。アームリンク１３と第２制御軸１１は相対移動しない。第２制御軸１１は、不図示のハウジング内に後述する複数のジャーナル部を介して回転自在に支持されている。
　アクチュエータリンク１２は、レバー形状であり、偏心軸部１０ｃに連結された一端部１２ａは、略直線的に形成されている。 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.
　第２制御軸１１は、後述する可変圧縮比機構のアクチュエータ２００の一部である減速機２０を介して駆動モータ４０から伝達されたトルクによって回転位置が変更される。第２制御軸１１の回転位置が変更されると、第二制御リンク１２の姿勢が変化して第一制御軸１０が回転し、第一制御リンク７の下端部の位置を変更する。これにより、ロアリンク５の姿勢が変化し、ピストン１のシリンダ内におけるストローク位置やストローク量を変化させ、これに伴って機関圧縮比を変更する。 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. When 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. As a result, 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.
　図２は、実施形態１の可変圧縮比機構のアクチュエータの斜視図であり、図３は、実施形態１の減速機の分解斜視図であり、図４は、実施形態１の遊星歯車機構の分解斜視図であり、図５は、実施形態１の遊星歯車の第１の組付け状態（３つの支持軸を取付けた状態）を示す斜視図であり、図６は、実施形態１の遊星歯車の第２の組付け状態（支持軸に遊星歯車を取付けた状態）を示す斜視図であり、図７は、実施形態１の遊星歯車の第３の組付け状態（支持軸にキャップを取付けた状態）を示す斜視図である。 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, and 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, and 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), and 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.
　［可変圧縮比機構のアクチュエータの構成］　可変圧縮比機構のアクチュエータ２００は、図２に示すように、駆動モータ４０と、内部に波動歯車機構と遊星歯車機構とを有する減速機２０を収容するハウジング３０と、第２制御軸１１等から構成されている。
　詳細については、後述する。 [Structure of Actuator of Variable Compression Ratio Mechanism] As shown in FIG. 2, 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.
　（減速機の構成）　図３の減速機の分解斜視図に基づき、簡単に説明する。 (Structure of reduction gear) A brief explanation will be given based on the exploded perspective view of the reduction gear shown in FIG.
　減速機２０は、遊星歯車機構２０ａと波動歯車機構２０ｂとを有する。
　すなわち、波動歯車機構２０ｂは、内周面に複数の第２内歯２４ａを有する内歯車部材２４と波動発生器３００を構成する内周面に複数の第１内歯２３ａを有する波動発生プラグ２３と波動発生プラグ２３の外周面２３ｃに内輪が圧入され固定される深溝玉軸受２２と、胴部第１端部２１０ａと胴部第２端部２１０ｂを有する筒状の胴部２１０の外周面に設けられた複数の外歯２１ｂと内周面に設けられた雌スプライン２１ａを有する可撓性外歯車２１とから構成されている。
　また、遊星歯車機構２０ａは、第２制御軸１１の図示右側の先端部に設けられた３つの遊星歯車３１とモータ出力軸２５の先端に設けられた太陽歯車２５ａと、波動発生器３００を構成する波動発生プラグ２３の内周に設けられた複数の第１内歯２３ａから構成されている。 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.
In addition, 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.
　内歯車部材２４は、貫通孔２４ｂを介して、ハウジング３０の雌ねじ穴３０ｂにボルトで結合され、ハウジング３０に固定されている。
　波動発生器３００を構成する波動発生プラグ２３は、楕円形状であり、深溝玉軸受２２は、波動発生プラグ２３の外周および可撓性外歯車２１の内周間の相対回転を許容する可撓性の薄肉内外輪を有しており、波動発生プラグ２３の外周面２３ｃに、内輪が圧入され固定されている。
　可撓性外歯車２１は、その内径側に波動発生器３００を構成する波動発生プラグ２３と深溝玉軸受２２が配置され、複数の外歯２１ｂが、複数の第２内歯２４ａと噛合うように、内歯車部材２４の内径側に配置される。
　なお、第２制御軸１１は、３つの遊星歯車３１の図示左側に雄スプライン１１ｅを有しており、３つの遊星歯車３１が入力軸であるモータ出力軸２５の先端に設けられた太陽歯車２５ａと噛合い、雄スプライン１１ｅが可撓性外歯車２１の雌スプライン２１ａと嵌合するように、設けられる。
　軸受５０は、波動発生プラグ２３のフランジ部２３ｂとハウジング３０の間に設けられ、波動発生プラグ２３を支持している。
　雌ねじ孔３０ａは、不図示のハウジングを取付け固定するために設けられている。
　回転軸線Ｐは、モータ出力軸２５、減速機２０、第２制御軸１１の回転軸線である。 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. Of the wave generating plug 23, 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.
　（遊星歯車機構の構成）　図４―図７に基づき、遊星歯車機構２０ａの構成を説明する。 (Structure of planetary gear mechanism) The structure of the planetary gear mechanism 20a will be described with reference to FIGS. 4 to 7.
　遊星歯車機構２０ａは、前述したようにモータ出力軸２５の先端に設けられた太陽歯車２５ａと、３つの遊星歯車３１と、波動発生器３００を構成する波動発生プラグ２３の内周に設けられた複数の第１内歯２３ａから構成されている。
　３つの遊星歯車３１を小径部３３ｂにて回転可能にそれぞれ支持する３つの支持軸３３が、第２制御軸１１の雄スプライン１１ｅが設けられた先端面に設けられた３つの挿通孔１１ｄに、大径部３３ａが圧入固定され、第２制御軸１１に保持されている。
　なお、支持軸３３は、第２制御軸１１に回転可能に、保持されてもよい。
　これにより、減速機２０の回転軸線Ｐ方向の小型化が可能となる。
　また、大径部３３ａと小径部３３ｂとの段差により、遊星歯車３１の軸方向の移動を規制するストッパ機能を持たせることができる。
　３つの支持軸３３は、それぞれ遊星歯車３１を回転可能に支持させた後に、３つの貫通孔３２ａを有するキャップ３２を、支持軸３３の小径部３２ｂに、圧入固定する。
　これにより、キャップ３２に、遊星歯車３１の軸方向の移動を規制するストッパ機能を持たせることができる。
　また、第２制御軸１１は、図示しないハウジングに支持される先端部側（図示左側）の小径な第１ジャーナル部１１ｃと、アームリンク１３が第１ジャーナル部１１ｃ側から圧入される中径な固定部１１ｂと、図示しないハウジングに支持される大径部としての大径な第２ジャーナル部１１ａとを有する。
　さらに、第２制御軸１１の中心には、回転軸線Ｐ方向に潤滑油路１１０が設けられている。
　また、その潤滑油路１１０の開口部１１１は、テーパ形状に形成している。
　遊星歯車３１を支持する３つの支持軸３３は、開口部１１１の径方向外側に固定・保持されている。
　これにより、遊星歯車３１への潤滑が可能となる。
　また、開口部１１１のテーパ形状は、第２制御軸１１をアームリンク１３へ圧入する際の押圧する面として使え、センタリング機能を果たすことができる。 As described above, 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.
As a result, the reduction gear 20 can be downsized in the direction of the rotation axis P.
Further, 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.
As a result, 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.
　（可変圧縮比機構のアクチュエータの構成）　図８は、実施形態1の可変圧縮比機構のアクチュエータの断面図であり、図９は、実施形態1の図８のＡ－Ａ断面図であり、図１０は、実施形態1の図８のＢ－Ｂ断面図である。 (Structure of Actuator of Variable Compression Ratio Mechanism) FIG. 8 is a sectional view of the actuator of the variable compression ratio mechanism of the first embodiment, and 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.
　可変圧縮比機構のアクチュエータ２００は、駆動モータ４０と、遊星歯車機構２０ａと波動歯車機構２０ｂからなる減速機２０から構成されている。
　駆動モータ４０は、ブラシレスモータであり、有底円筒状のモータケーシング４１と、モータケーシング４１の内周面に固定された筒状のコイル４０ａと、コイル４０ａの内側に回転自在に設けられたロータ４０ｂと、一端部２５ｂがロータ４０ｂの中心に固定されたモータ出力軸２５とを有する。
　モータ出力軸２５は、モータケーシング４１の底部に設けられたボールベアリング５１とハウジング３０に設けられたボールベアリング５３により回転可能に支持されている。モータケーシング４１は、前端外周に４つのボス部４１ａを有する。ボス部４１ａには、不図示のボルトを挿通するボルト挿通孔４１ｂが貫通形成されている。 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.
　モータケーシング４１をハウジング３０に取り付ける際は、ハウジング３０とモータケーシング４１との間にＯリング１００を介在させつつ、ボス部４１ａのボルト挿通孔４１ｂにボルトを挿通し、ハウジング３０の駆動モータ４０側に設けられた雌ねじ部３０ｄにボルトを締め付ける。これにより、モータケーシング４１をハウジング３０に固定する。モータケーシング４１及びハウジング３０によって駆動モータ４０を収容するモータ収容室は、ハウジング３０とモータ出力軸２５間に配置されたシール部材５２により、潤滑油等を供給しない乾燥室として構成する。 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.
　次に、減速機２０の構成を説明する。
　減速機２０は、前述したように、遊星歯車機構２０ａと波動歯車機構２０ａを有している。
　モータ出力軸２５の先端部に設けられた太陽歯車２５ａは、第２制御軸１１の端面に設けられた３つの挿入孔１１ｄに大径部３３ａが挿入固定された３つの支持軸３３の小径部３３ｂに回転可能に支持された３つの遊星歯車３１と噛合っている。
　また、３つの遊星歯車３１は、波動発生器３００を構成する波動発生プラグ２３の内周面に設けられた複数の第１内歯２３ａとも噛合っている。
　これにより、波動発生器３００を構成する波動発生プラグ２３には、モータ出力軸２５の回転が、逆回転で減速されて伝達されることになる。
　なお、３つの遊星歯車３１の支持軸３３は、第２制御軸１１の先端部に固定してあるが、第２制御軸１１の回転は、波動歯車機構２０ｂにより、大きく減速されるので、モータ出力軸２５の回転と比較すると、非常に小さな回転となり（実質的に停止状態と同様）、遊星歯車機構２０ａの作動には、まったく影響はない。
　また、３つの支持軸３３は、第２制御軸１１と同じ回転を行う可撓性外歯車２１に固定するようにしてもよい。
　さらに、遊星歯車機構を構成する３つの遊星歯車３１と波動発生プラグ２３の複数の第１内歯２３ａとモータ出力軸２５の太陽歯車２５ａの噛み合い位置と可撓性外歯車２１の複数の外歯２１ｂと内歯車部材２４の複数の第２内歯２４ａの噛み合い位置は回転軸線Ｐの方向において、オーバーラップするように配置されている。
　これにより、モータ出力軸２５の回転に対して、波動発生器３００の傾きを抑制することができる。 Next, the configuration of the speed reducer 20 will be described.
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.
As a result, 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.
Further, 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.
　波動歯車機構２０ｂは、前述したように、波動発生器３００、可撓性外歯車２１、剛性内歯車２４から構成されている。
　波動発生プラグ２３は、外形が楕円形状であり、深溝玉軸受２２は、波動発生プラグ２３の外周および可撓性外歯車２１の内周間の相対回転を許容する可撓性の薄肉内外輪を有しており、波動発生プラグ２３の外周面２３ｃに、内輪が圧入固定され、波動発生器３００を構成している。
　すなわち、楕円形状である波動発生プラグ２３は、深溝玉軸受２２の内輪へ嵌合されて、深溝玉軸受２２も楕円形状へと倣うため、深溝玉軸受２２も楕円形状となり、波動発生器３００の外径は、楕円形状となる。 As described above, 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, and 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.
In other words, 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.
　また、前述したように、波動発生プラグ２３のフランジ部２３ｂとハウジング３０の間には、軸受５０が設けられ、波動発生プラグ２３を支持している。
　なお、軸受５０の径方向ガタαの大きさは、３つの遊星歯車３１と複数の第１内歯２３ａ間の径方向ガタβの大きさよりも、小さく設定している。
　これにより、第２制御軸１１からの逆入力によって波動発生器３００に径方向の荷重が作用しても、軸受５０によってその荷重を受けることができ、３つの遊星歯車３１へ荷重が作用するのを抑制することができる。
　可撓性外歯車２１は、その内径側に波動発生器３００を構成する波動発生プラグ２３と深溝玉軸受２２が配置され、深溝玉軸受２２の外輪が可撓性外歯車２１の筒状の胴部２１０の外周面に設けられた複数の外歯２１ｂと回転軸線Ｐの方向でオーバーラップする胴部２１０の内周面と嵌合している。
　また、ハウジング３０に固定された内歯車部材２４の内径側に、複数の外歯２１ｂが、内歯車部材２４の複数の第２内歯２４ａと噛合うように、可撓性外歯車２１が配置されている。
　可撓性外歯車２１は、金属材料によって形成され、回転軸線Ｐ方向に延びる胴部第１端部２１０ａと胴部第２端部２１０ｂを有する胴部２１０、胴部２１０の胴部第１端部２１０ａから回転軸線Ｐ方向に関して半径方向内方に延びる底部２１１、底部２１１から胴部２１０と同じ回転軸線Ｐ方向に連続して延びる剛性の高いフランジ部２１２を有する撓み変形可能な薄肉円筒状部材である。
　可撓性外歯車２１の複数の外歯２１ｂの歯数は、内歯車部材２４の複数の第２内歯２４ａの歯数より２歯少ない。
　可撓性外歯車２１の底部２１１に連続して設けられたフランジ部２１２内周には、第２制御軸１１が貫通する雌スプライン２１ａが設けられた挿通孔２１２ａが設けられている。 Further, as described above, 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 α of the bearing 50 is set smaller than the size of the radial play β between the three planetary gears 31 and the plurality of first internal teeth 23a.
As a result, 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 loads act on the three planetary gears 31. Can be suppressed.
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.
　波動発生器３００を構成する波動発生プラグ２３と深溝玉軸受２２は、楕円形状に形成され、深溝玉軸受２２の外輪の外周面が可撓性外歯車２１の内周面に沿って摺動する。
　また、可撓性外歯車２１の内径へ波動発生器３００を構成する波動発生プラグ２３と深溝玉軸受２を嵌合することにより、初期状態が円形である可撓性外歯車２１も楕円形状へと変形する。
　楕円へ撓ませられた可撓性外歯車２１は剛性内歯車２４より２歯少ない歯数であるため、楕円長軸上で歯ピッチのずれにより噛み合い、楕円短軸上では歯ピッチは一致するが、可撓性外歯車２１が軸方向へと撓められているために歯が重なることはなく干渉しない。 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.
　可撓性外歯車２１の歯部は可撓性であるが、フランジ部２１２は出力を取り出すために円形状から変形させることはできず、第２制御軸１１とスプライン嵌合により直接締結されるため、フランジ部２１２を起点として薄肉円筒開口端部に向かって楕円形状へと広がる形となる。
　すなわち、開口端部付近での変形運動から取り出される可撓性外歯車２１の回転運動をフランジ部２１２から第２制御軸１１へと伝達できる。
　なお、波動発生器３００の回転は、可撓性外歯車２１は剛性内歯車２４より２歯少ない歯数であるため、波動発生器３００が１回転（３６０度）すると、歯数差２枚分だけ、可撓性外歯車２１は逆方向へ回転する。
　すなわち、波動歯車機構を構成する波動発生器３００、可撓性外歯車２１、剛性内歯車２４により、可撓性外歯車２１には、波動発生器３００の回転が、逆回転（モータ出力軸２５と同じ回転方向）で非常に大きな減速比で減速されて伝達され、さらに、スプライン嵌合する第２制御軸１１に伝達されることになる。
　このように、遊星歯車機構２０ａを内包した波動歯車機構２０ｂにより、２段減速構成とすることで、高減速比かつ高効率化が可能となる。
　すなわち、波動歯車機構２０ｂのみで高減速比を実現すると、波動歯車機構２０ｂの内歯、外歯を小さくする必要があり、そうすると噛合っている歯数が多くなり、それだけ接触面積が大きくなって、摩擦抵抗により伝達効率が低下しやすくなるが、２段減速構成とすることにより、波動歯車機構２０ｂの内歯、外歯を小さくせずに、大きな減速比を実現することができるので、伝達効率を向上することができる。
　さらに、波動歯車機構２０ｂの内歯、外歯を小さくせずに済むので、噛み合いの滑り（ラチェティング）が抑制できる。
　また、波動発生器３００が遊星歯車機構２０ａと一体化していることにより、部品点数も少なくすることができる。 Although 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.
That is, due to the wave generator 300, the flexible external gear 21, and the rigid internal gear 24 that constitute the wave gear mechanism, 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.
As described above, by using 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. 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.
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.
　図１１は、実施形態１の可撓性外歯車と遊星歯車の関係を示す模式図である。 FIG. 11 is a schematic diagram showing the relationship between the flexible external gear and the planetary gear according to the first embodiment.
　回転軸線Ｐから遊星歯車３１の最も外径側の歯先までの距離ａは、可撓性外歯車２１のフランジ部２１２の内周に設けられた雌スプライン２１ａの最も内径側の歯先までの距離ｂより、短く設定されている。
　これにより、図６に示すように、遊星歯車３１を装着した第２制御軸１１を、第２制御軸１１に設けられた雄スプライン１１ｅと可撓性外歯車２１のフランジ部２１２の内周に設けられた雌スプライン２１ａを嵌合させるために、挿入して組付ける際に、遊星歯車３１と雌スプライン２１ａが干渉することなく、組み付けることができる。 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.
As a result, as shown in FIG. 6, 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. In order to fit the provided female spline 21a, the planetary gear 31 and the female spline 21a can be assembled without interfering with each other when inserting and assembling.
　次に、作用効果を説明する。
　実施形態１の減速機及び内燃機関の可変圧縮機構のアクチュエータにおいては、以下に列挙する作用効果を奏する。 Next, the function and effect will be described.
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.
（１）減速機２０を、遊星歯車機構２０ａを内包した波動歯車機構２０ｂによる、２段減速構成とした。
　よって、波動歯車機構２０ｂのみで高減速比を実現すると、波動歯車機構２０ｂの内歯、外歯を小さくする必要があり、そうすると噛合っている歯数が多くなり、それだけ接触面積が大きくなって、摩擦抵抗により伝達効率が低下しやすくなるが、２段減速構成とすることにより、波動歯車機構２０ｂの内歯、外歯を小さくせずに、大きな減速比を実現することができるので、伝達効率を向上することができるとともに、波動歯車機構２０ｂの内歯、外歯を小さくせずに済むので、噛み合いの滑り（ラチェティング）が抑制でき、波動発生器３００が遊星歯車機構２０ａと一体化していることにより、部品点数も少なくすることができる。 (1) 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.
（２）３つの遊星歯車３１を小径部３３ｂにて回転可能にそれぞれ支持する３つの支持軸３３が、第２制御軸１１の雄スプライン１１ｅが設けられた先端面に設けられた３つの挿通孔１１ｄに、大径部３３ａが圧入固定され、第２制御軸１１に保持するようにした。
　よって、減速機２０の回転軸線Ｐ方向の小型化が可能となる。特に、第２制御軸１１は遊星歯車機構２０ａと波動歯車機構２０ｂによりモータ出力軸２５の回転数が大幅に減速されて伝達しているため、この第２制御軸１１に遊星歯車３１の支持軸３３を保持（固定又は回転可能に保持）させることによって支持軸３３をハウジング３０などに固定するのと大差なく考慮することが可能となる。本実施形態では第２制御軸１１の雄スプライン１１ｅが底部２１１を貫通しているが、例えば支持軸３３を底部２１１に保持させたり、第２制御軸１１に他の部材を介して保持させても良い。 (2) 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. In particular, since 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. 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. In this embodiment, the male spline 11e of the second control shaft 11 penetrates the bottom portion 211. However, for example, 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.
（３）波動発生器３００を支持する軸受５０の径方向ガタαの大きさは、３つの遊星歯車３１と複数の第１内歯２３ａ間の径方向ガタβの大きさよりも、小さく設定するようにした。
　よって、第２制御軸１１からの逆入力によって波動発生器３００に径方向の荷重が作用しても、軸受５０によってその荷重を受けることができ、３つの遊星歯車３１へ荷重が作用するのを抑制することができる。 (3) The radial play α of the bearing 50 supporting the wave generator 300 is set to be smaller than the radial play β 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.
（４）回転軸線Ｐから遊星歯車３１の最も外径側の歯先までの距離ａは、可撓性外歯車２１のフランジ部２１２の内周に設けられた雌スプライン２１ａの最も内径側の歯先までの距離ｂより、短く設定するようにした。
　よって、遊星歯車３１を装着した第２制御軸１１を、第２制御軸１１に設けられた雄スプライン１１ｅと可撓性外歯車２１のフランジ部２１２の内周に設けられた雌スプライン２１ａを嵌合させるために、挿入して組付ける際に、遊星歯車３１と雌スプライン２１ａが干渉することなく、組み付けることができる。 (4) 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.
（５）３つの支持軸３３は、第２制御軸１１に固定されて保持される大径部３３ａと３つの遊星歯車３１を回転自在に保持する、大径部３３ａより直径が小さい小径部３３ｂを有するようにした。
　よって、大径部３３ａと小径部３３ｂとの段差により、遊星歯車３１の軸方向の移動を規制するストッパ機能を持たせることができる。 (5) 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.
（６）３つの支持軸３３は、それぞれ遊星歯車３１を回転可能に支持させた後に、３つの貫通孔３２ａを有するキャップ３２を、支持軸３３の小径部３３ｂに、圧入固定するようにした。
　よって、キャップ３２に、遊星歯車３１の軸方向の移動を規制するストッパ機能を持たせることができる。 (6) 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.
（７）遊星歯車機構を構成する３つの遊星歯車３１と波動発生プラグ２３の複数の第１内歯２３ａとモータ出力軸２５の太陽歯車２５ａの噛み合い位置と可撓性外歯車２１の複数の外歯２１ｂと内歯車部材２４の複数の第２内歯２４ａの噛み合い位置は回転軸線Ｐの方向において、オーバーラップするように配置するようにした。
　よって、モータ出力軸２５の回転に対して、波動発生器３００の傾きを抑制できる。 (7) The three planetary gears 31 constituting the planetary gear mechanism, the plurality of first internal teeth 23a of the wave generating plug 23, the meshing positions of the sun gear 25a of the motor output shaft 25, and the plurality of outer portions of the flexible external gear 21. 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.
（８）第２制御軸１１の中心には、回転軸線Ｐ方向に潤滑油路１１０が設けられ、遊星歯車３１を支持する３つの支持軸３３は、開口部１１１の径方向外側に固定・保持するようにした。
　よって、遊星歯車３１への潤滑が可能となる。 (8) 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.
（９）潤滑油路１１の開口部１１１は、テーパ形状に形成するようにした。
　よって、開口部１１１のテーパ形状は、第２制御軸１１をアームリンク１３へ圧入する際の押圧する面として使え、センタリング機能を果たすことができる。 (9) 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.
　［実施形態２］　図１２は、実施形態２の遊星歯車の取付け状態を示す斜視図である。 [Second Embodiment] FIG. 12 is a perspective view showing a mounted state of a planetary gear according to a second embodiment.
　実施形態１とは、異なり、３つの遊星歯車３１を小径部３３ｂにて回転可能にそれぞれ支持する３つの支持軸３３は、ハウジング３０にて支持するようにした。
　なお、３つの支持軸３３は、モータ出力軸２５の太陽歯車２５ａの径方向外側のハウジング３０に固定し、保持するようにした。
　その他の構成は、実施形態１と同じ構成であるため、同じ構成には同一符号を付して、説明は省略する。 Unlike the first 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.
　次に、作用効果を説明する。
　実施形態２の減速機及び内燃機関の可変圧縮機構のアクチュエータにおいては、実施形態１と同様の作用効果を奏する。 Next, the function and effect will be described.
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.
　〔他の実施例〕　以上、本発明を実施形態１、実施形態２に基づいて説明してきたが、各発明の具体的な構成は実施形態１、実施形態２に限定されるものではなく、発明の要旨を逸脱しない範囲の設計変更等があっても、本発明に含まれる。 [Other Examples] The present invention has been described above based on the first and second embodiments, but the specific configuration of each invention is not limited to the first and second embodiments. Even if there is a design change or the like within the scope of the present invention, it is included in the present invention.
　以上説明した実施形態から把握し得る技術的思想について、以下に記載する。
　減速機は、その一つの態様において、太陽歯車を有する入力軸と回転軸線の直角方向断面の外形が非円形であって、内周に第１内歯を有する波動発生器と、前記波動発生器により非円形に撓む可撓性を有する筒状の胴部と、前記胴部の外周面に設けられた外歯と、を有する可撓性外歯車と、撓み変形された前記胴部の前記外歯と噛み合う第２内歯を有する内歯車部材と、前記内歯車部材が固定されるハウジングと、前記可撓性外歯車と一体に回転する出力軸と、前記出力軸又は前記ハウジング又は前記可撓性外歯車に保持された複数の支持軸と、前記複数の支持軸にそれぞれ回転可能に配置され、前記太陽歯車と前記第１内歯と噛み合う複数の遊星歯車と、を有する。
　より好ましい態様では、上記態様において、前記可撓性外歯車は、回転軸線の方向の前記胴部の両端部である胴部第１端部および胴部第２端部のうち前記胴部第１端部から半径方向の内方に延びる底部を有し、前記出力軸は前記底部を貫通しており、前記複数の支持軸は、前記出力軸に保持されている。
　別の好ましい態様では、上記態様において、前記波動発生器と前記ハウジングの間に軸受を更に有し、前記軸受の径方向のガタの大きさは、前記複数の遊星歯車と前記第１内歯の間の径方向のガタの大きさよりも小さい。
　別の好ましい態様では、上記態様のいずれかにおいて、前記出力軸は外周に雄スプラインを有し、前記底部は内周に前記雄スプラインに嵌合する雌スプラインを有し、前記複数の遊星歯車は、前記出力軸の回転軸線から回転軸線の直角方向の最も外側の部分までの第１距離が、前記出力軸の回転軸線から前記雌スプラインの回転軸線の直角方向の最も内側の部分までの第２距離よりも短い。 The technical idea that can be understood from the embodiment described above will be described below.
In one aspect thereof, 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.
In a more preferred aspect, in the above aspect, 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.
In another preferred aspect, in the above aspect, 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.
In another preferred aspect, in any one of the above aspects, 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, and 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.
　別の好ましい態様では、上記態様のいずれかにおいて、前記複数の支持軸は、前記出力軸に保持される直径の大きい大径部と、前記複数の遊星歯車がそれぞれ保持され、前記大径部よりも直径の小さい小径部と、を有する。
　より好ましい態様では、上記態様において、前記複数の支持軸の軸方向の前記大径部と反対側に配置され、前記複数の遊星歯車の軸方向移動を規制するキャップを有する。
　さらに別の好ましい態様では、上記態様のいずれかにおいて、前記第２内歯と前記可撓性外歯車の前記外歯との噛み合い位置と、前記第１内歯と前記複数の遊星歯車との噛み合い位置は、前記入力軸の回転軸線の方向においてオーバーラップしている。
　さらに別の好ましい態様では、上記態様のいずれかにおいて、前記複数の支持軸は、前記ハウジングに保持されている。 In another preferred aspect, in any one of the above aspects, 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.
In a more preferred aspect, in the above aspect, 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.
In still another preferred aspect, in any one of the above aspects, a meshing position between the second internal tooth and the external tooth of the flexible external gear, and a meshing between the first internal tooth and the plurality of planetary gears. The positions overlap in the direction of the axis of rotation of the input shaft.
In yet another preferred aspect, in any one of the above aspects, the plurality of support shafts are held by the housing.
内燃機関の可変圧縮機構のアクチュエータは、その一つの態様において、太陽歯車が設けられたモータ軸を有する駆動モータと、回転軸線の直角方向断面の外形が非円形であって、内周に第１内歯を有する波動発生器と、前記波動発生器により非円形に撓む可撓性を有する筒状の胴部と、前記胴部の外周面に設けられた外歯と、を有する可撓性外歯車と、撓み変形された前記胴部の前記外歯と噛み合う第２内歯車を有する内歯車部材と、前記内歯車部材が固定されるハウジングと、前記可撓性外歯車と一体に回転すると共に、回転によって前記内燃機関の可変圧縮比機構の姿勢を変更する出力軸と、前記出力軸又は前記ハウジング又は前記可撓性外歯車に保持された複数の支持軸と、前記複数の支持軸にそれぞれ回転可能に配置され、前記太陽歯車と前記第１内歯と噛み合う複数の遊星歯車と、を有する。
　より好ましい態様では、上記態様において、前記可撓性外歯車は、回転軸線の方向の前記胴部の両端部である胴部第１端部および胴部第２端部のうち前記胴部第１端部から半径方向の内方に延びる底部を有し、前記出力軸は前記底部を貫通しており、前記複数の支持軸は、前記出力軸に保持されている。 In one aspect thereof, 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. An external gear, an internal gear member having a second internal gear that meshes with the flexibly deformed external teeth of the body, a housing to which the internal gear member is fixed, and a flexible external gear that rotates together. Together with the output shaft that changes the attitude of the variable compression ratio mechanism of the internal combustion engine by rotation, 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.
In a more preferred aspect, in the above aspect, 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.
　さらに別の好ましい態様では、上記態様のいずれかにおいて、前記波動発生器と前記ハウジングの間に軸受を更に有し、前記軸受の径方向のガタの大きさは、前記複数の遊星歯車と前記第１内歯の間の径方向のガタの大きさよりも小さい。
　さらに別の好ましい態様では、上記態様のいずれかにおいて、前記出力軸は、内部に軸方向に油路を有し、前記油路は前記モータ軸と対向する開口部を有し、前記複数の支持軸は、前記開口部の径方向外側に配置されている。
　より好ましい態様では、上記態様において、前記開口部はテーパ状になっている。 In still another preferred aspect, in any one of the above aspects, 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.
In still another preferred aspect, in any one of the above aspects, 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.
　尚、本発明は上記した実施形態に限定されるものではなく、様々な変形例が含まれる。例えば、上記した実施形態は本発明を分かりやすく説明するために詳細に説明したものであり、必ずしも説明した全ての構成を備えるものに限定されるものではない。また、ある実施形態の構成の一部を他の実施形態の構成に置き換えることが可能であり、また、ある実施形態の構成に他の実施形態の構成を加えることも可能である。また、各実施形態の構成の一部について、他の構成の追加・削除・置換をすることが可能である。 It should be noted that the present invention is not limited to the above-described embodiment, and various modifications are included. For example, 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. Further, 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. Further, it is possible to add/delete/replace other configurations with respect to a part of the configurations of the respective embodiments.
　本願は、２０１８年１２月２１日付出願の日本国特許出願第２０１８－２３９１８９号に基づく優先権を主張する。２０１８年１２月２１日付出願の日本国特許出願第２０１８－２３９１８９号の明細書、特許請求の範囲、図面、及び要約書を含む全開示内容は、参照により本願に全体として組み込まれる。 This application claims priority based on Japanese Patent Application No. 2018-239189 filed on December 21, 2018. The entire disclosure of Japanese Patent Application No. 2018-239189 filed on Dec. 21, 2018, including the specification, claims, drawings, and abstract, is incorporated herein by reference in its entirety.
１１　　　第２制御軸（出力軸）１１ｅ　　雄スプライン１１０　　潤滑油路１１１　　開口部２０　　　減速機２００　　内燃機関の可変圧縮機構のアクチュエータ２１　　　可撓性外歯車２１ａ　　雌スプライン２１ｂ　　外歯２１０　　胴部２１０ａ　胴部第１端部２１０ｂ　胴部第２端部２１１　　底部３００　　波動発生器２２　　　深溝玉軸受（波動発生器）２３　　　波動発生プラグ（波動発生器）２３ａ　　第１内歯２４　　　内歯車部材２４ａ　　第２内歯２５　　　モータ出力軸（入力軸）２５ａ　　太陽歯車３０　　　ハウジング３１　　　遊星歯車３２　　　キャップ３３　　　支持軸３３ａ　　大径部３３ｂ　　小径部４０　　　駆動モータ５０　　　軸受ａ　　　　第１距離ｂ　　　　第２距離Ｐ　　　　回転軸線α　　　　軸受５０の径方向のガタβ　　　　遊星歯車３１と第１内歯２３ａの間の径方向のガタ 11 Second control shaft (output shaft) 11e Male spline 110 Lubricating oil passage 111 Opening 20 Reducer 200 Actuator 21 of variable compression mechanism of internal combustion engine Flexible external gear 21a Female spline 21b External tooth 210 Body 210a Body part No. 1 end 210b body 2nd end 211 bottom 300 wave generator 22 deep groove ball bearing (wave generator) 23 wave generation plug (wave generator) 23a first internal tooth 24 internal gear member 24a second internal tooth 25 motor Output shaft (input shaft) 25a, sun gear 30, housing 31, planetary gear 32, cap 33, support shaft 33a, large diameter part 33b, small diameter part 40, drive motor 50, bearing a, first distance b, second distance P, rotary shaft line α, radial direction of bearing 50. β Radial play between the planetary gear 31 and the first internal teeth 23a

Claims (14)

  1. 　減速機であって、該減速機は、
    　太陽歯車を有する入力軸と、
    　前記減速機の回転軸線の直角方向断面の外形が非円形であって、内周に第１内歯を有する波動発生器と、
    　前記波動発生器により非円形に撓む可撓性を有する筒状の胴部と、前記胴部の外周面に設けられた外歯と、を有する可撓性外歯車と、
    　撓み変形された前記胴部の前記外歯と噛み合う第２内歯を有する内歯車部材と、
    　前記内歯車部材が固定されるハウジングと、
    　前記可撓性外歯車と一体に回転する出力軸と、
    　前記出力軸又は前記ハウジング又は前記可撓性外歯車に保持された複数の支持軸と、
    　前記複数の支持軸にそれぞれ回転可能に配置され、前記太陽歯車と前記第１内歯と噛み合う複数の遊星歯車と、を有する、
    　ことを特徴とする減速機。     A speed reducer, wherein the speed reducer is
    An input shaft having a sun gear,
    A wave generator having a non-circular outer shape in a cross section in the direction perpendicular to the rotation axis of the speed reducer and having first inner teeth on the inner circumference;
    A flexible external gear having a tubular body having flexibility that bends in a non-circular shape by the wave generator, and external teeth provided on an outer peripheral surface of the body,
    An internal gear member having second internal teeth that mesh with the external teeth of the flexibly deformed body,
    A housing to which the internal gear member is fixed,
    An output shaft that rotates integrally with the flexible external gear,
    A plurality of support shafts held by the output shaft or the housing or the flexible external gear,
    Each of the plurality of support shafts is rotatably arranged and has a plurality of planetary gears that mesh with the sun gear and the first inner teeth.
    A speed reducer characterized by that.
  2. 　請求項１に記載の減速機であって、
    　前記可撓性外歯車は、該可撓性外歯車の回転軸線の方向の前記胴部の両端部である胴部第１端部および胴部第２端部のうち前記胴部第１端部から半径方向の内方に延びる底部を有し、
    　前記出力軸は前記底部を貫通しており、
    　前記複数の支持軸は、前記出力軸に保持されている、
    　ことを特徴とする減速機。     The speed reducer according to claim 1,
    The flexible external gear is the body first end of the body first end and the body second end that are both ends of the body in the direction of the rotation axis of the flexible external gear. Has a bottom extending radially inwardly from
    The output shaft passes through the bottom,
    The plurality of support shafts are held by the output shaft,
    A speed reducer characterized by that.
  3. 　請求項１に記載の減速機であって、
    　前記減速機は、前記波動発生器と前記ハウジングの間に軸受を更に有し、
    　前記軸受の径方向のガタの大きさは、前記複数の遊星歯車と前記第１内歯の間の径方向のガタの大きさよりも小さい、
    　ことを特徴とする減速機。     The speed reducer according to claim 1,
    The speed reducer further has a bearing between the wave generator and the housing,
    The size of the radial play of the bearing is smaller than the size of the radial play between the plurality of planetary gears and the first internal teeth,
    A speed reducer characterized by that.
  4. 　請求項１に記載の減速機であって、
    　前記出力軸は外周に雄スプラインを有し、前記底部は内周に前記雄スプラインに嵌合する雌スプラインを有し、
    　前記複数の遊星歯車は、前記出力軸の回転軸線から該回転軸線の直角方向の最も外側の部分までの第１距離が、前記出力軸の回転軸線から前記雌スプラインの回転軸線の直角方向の最も内側の部分までの第２距離よりも短い、
    　ことを特徴とする減速機。     The speed reducer according to claim 1,
    The output shaft has a male spline on the outer circumference, and the bottom portion has a female spline fitted to the male spline on the inner circumference,
    In the plurality of planetary gears, 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 maximum distance in the direction perpendicular to the rotation axis of the female spline from the rotation axis of the output shaft. Shorter than the second distance to the inner part,
    A speed reducer characterized by that.
  5. 　請求項１に記載の減速機であって、
    　前記複数の支持軸は、前記出力軸に保持される直径の大きい大径部と、前記複数の遊星歯車がそれぞれ保持され、前記大径部よりも直径の小さい小径部と、を有する、
    　ことを特徴とする減速機。     The speed reducer according to claim 1,
    The plurality of support shafts have a large diameter part having a large diameter held by the output shaft, and a plurality of planetary gears are respectively held, and a small diameter part having a smaller diameter than the large diameter part,
    A speed reducer characterized by that.
  6. 　請求項５に記載の減速機であって、
    　前記減速機は、前記複数の支持軸の軸方向の前記大径部と反対側に配置され、前記複数の遊星歯車の軸方向移動を規制するキャップを有する、
    　ことを特徴とする減速機。     The speed reducer according to claim 5,
    The speed reducer is arranged on the side opposite to the large diameter portion in the axial direction of the plurality of support shafts, and has a cap that restricts axial movement of the plurality of planetary gears,
    A speed reducer characterized by that.
  7. 　請求項１に記載の減速機であって、
    　前記第２内歯と前記可撓性外歯車の前記外歯との噛み合い位置と、前記第１内歯と前記複数の遊星歯車との噛み合い位置は、前記入力軸の回転軸線の方向においてオーバーラップしている、
    　ことを特徴とする減速機。     The speed reducer according to claim 1,
    The meshing position between the second internal tooth and the external tooth of the flexible external gear and the meshing position between the first internal tooth and the plurality of planetary gears overlap in the direction of the rotation axis of the input shaft. doing,
    A speed reducer characterized by that.
  8. 　請求項１に記載の減速機であって、
    　前記複数の支持軸は、前記ハウジングに保持されている、
    　ことを特徴とする減速機。     The speed reducer according to claim 1,
    The plurality of support shafts are held by the housing,
    A speed reducer characterized by that.
  9. 　内燃機関の可変圧縮比機構のアクチュエータであって、
    　太陽歯車が設けられたモータ軸を有する駆動モータと、
    　前記アクチュエータの回転軸線の直角方向断面の外形が非円形であって、内周に第１内歯を有する波動発生器と、
    　前記波動発生器により非円形に撓む可撓性を有する筒状の胴部と、前記胴部の外周面に設けられた外歯と、を有する可撓性外歯車と、
    　撓み変形された前記胴部の前記外歯と噛み合う第２内歯車を有する内歯車部材と、
    　前記内歯車部材が固定されるハウジングと、
    　前記可撓性外歯車と一体に回転すると共に、回転によって前記内燃機関の可変圧縮比機構の姿勢を変更する出力軸と、
    　前記出力軸又は前記ハウジング又は前記可撓性外歯車に保持された複数の支持軸と、
    　前記複数の支持軸にそれぞれ回転可能に配置され、前記太陽歯車と前記第１内歯と噛み合う複数の遊星歯車と、を有する、
    　ことを特徴とする内燃機関の可変圧縮比機構のアクチュエータ。     An actuator of a variable compression ratio mechanism of an internal combustion engine,
    A drive motor having a motor shaft provided with a sun gear,
    A wave generator having a non-circular outer shape in a cross section in a direction perpendicular to a rotation axis of the actuator and having first inner teeth on an inner circumference;
    A flexible external gear having a tubular body having flexibility that bends in a non-circular shape by the wave generator, and external teeth provided on an outer peripheral surface of the body,
    An internal gear member having a second internal gear that meshes with the external teeth of the body portion that has been flexibly deformed;
    A housing to which the internal gear member is fixed,
    An output shaft that rotates integrally with the flexible external gear and that changes the attitude of the variable compression ratio mechanism of the internal combustion engine by rotation.
    A plurality of support shafts held by the output shaft or the housing or the flexible external gear,
    Each of the plurality of support shafts is rotatably arranged and has a plurality of planetary gears that mesh with the sun gear and the first inner teeth.
    An actuator for a variable compression ratio mechanism of an internal combustion engine, characterized in that:
  10. 　請求項９に記載の内燃機関の可変圧縮比機構のアクチュエータであって、
    　前記可撓性外歯車は、該可撓性外歯車の回転軸線の方向の前記胴部の両端部である胴部第１端部および胴部第２端部のうち前記胴部第１端部から半径方向の内方に延びる底部を有し、
    　前記出力軸は前記底部を貫通しており、
    　前記複数の支持軸は、前記出力軸に保持されている、
    　ことを特徴とする内燃機関の可変圧縮比機構のアクチュエータ。     An actuator of a variable compression ratio mechanism for an internal combustion engine according to claim 9,
    The flexible external gear is the body first end of the body first end and the body second end that are both ends of the body in the direction of the rotation axis of the flexible external gear. Has a bottom extending radially inwardly from
    The output shaft passes through the bottom,
    The plurality of support shafts are held by the output shaft,
    An actuator for a variable compression ratio mechanism of an internal combustion engine, characterized in that:
  11. 　請求項９に記載の内燃機関の可変圧縮比機構のアクチュエータであって、
    　前記波動発生器と前記ハウジングの間に軸受を更に有し、
    　前記軸受の径方向のガタの大きさは、前記複数の遊星歯車と前記第１内歯の間の径方向のガタの大きさよりも小さい、
    　ことを特徴とする内燃機関の可変圧縮比機構のアクチュエータ。     An actuator of a variable compression ratio mechanism for an internal combustion engine according to claim 9,
    Further comprising a bearing between the wave generator and the housing,
    The size of the radial play of the bearing is smaller than the size of the radial play between the plurality of planetary gears and the first internal teeth,
    An actuator for a variable compression ratio mechanism of an internal combustion engine, characterized in that:
  12. 　請求項９に記載の内燃機関の可変圧縮比機構のアクチュエータであって、
    　前記出力軸は、内部に軸方向に油路を有し、前記油路は前記モータ軸と対向する開口部を有し、前記複数の支持軸は、前記開口部の径方向外側に配置されている、
    　ことを特徴とする内燃機関の可変圧縮比機構のアクチュエータ。     An actuator of a variable compression ratio mechanism for an internal combustion engine according to claim 9,
    The output shaft has an oil passage therein in the axial direction, the oil passage has an opening facing the motor shaft, and the plurality of support shafts are arranged radially outside the opening. Is
    An actuator for a variable compression ratio mechanism of an internal combustion engine, characterized in that:
  13. 　請求項１２に記載の内燃機関の可変圧縮比機構のアクチュエータであって、
    　前記開口部はテーパ状になっている、
    　ことを特徴とする内燃機関の可変圧縮比機構のアクチュエータ。     An actuator of a variable compression ratio mechanism for an internal combustion engine according to claim 12,
    The opening is tapered,
    An actuator for a variable compression ratio mechanism of an internal combustion engine, characterized in that:
  14. 　請求項９に記載の内燃機関の可変圧縮比機構のアクチュエータであって、
    　前記可撓性外歯車は、該可撓性外歯車の回転軸線の方向の前記胴部の両端部である胴部第１端部および胴部第２端部のうち前記胴部第１端部から半径方向の内方に延びる底部を有し、
    　前記複数の支持軸は、前記底部若しくは前記底部を貫通した前記出力軸に保持されている、
    　ことを特徴とする内燃機関の可変圧縮比機構のアクチュエータ。
    　     An actuator of a variable compression ratio mechanism for an internal combustion engine according to claim 9,
    The flexible external gear is the body first end of the body first end and the body second end that are both ends of the body in the direction of the rotation axis of the flexible external gear. Has a bottom extending radially inwardly from
    The plurality of support shafts are held by the output shaft that penetrates the bottom portion or the bottom portion,
    An actuator for a variable compression ratio mechanism of an internal combustion engine, characterized in that:
PCT/JP2019/047554 2018-12-21 2019-12-05 Actuator for variable compression mechanism of internal combustion engine and speed reducer WO2020129661A1 (en)

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