WO2019167553A1 - Actionneur pour mécanisme à taux de compression variable pour moteur à combustion interne et actionneur utilisé dans un dispositif pour moteur à combustion interne - Google Patents

Actionneur pour mécanisme à taux de compression variable pour moteur à combustion interne et actionneur utilisé dans un dispositif pour moteur à combustion interne Download PDF

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Publication number
WO2019167553A1
WO2019167553A1 PCT/JP2019/003791 JP2019003791W WO2019167553A1 WO 2019167553 A1 WO2019167553 A1 WO 2019167553A1 JP 2019003791 W JP2019003791 W JP 2019003791W WO 2019167553 A1 WO2019167553 A1 WO 2019167553A1
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WO
WIPO (PCT)
Prior art keywords
actuator
combustion engine
internal combustion
compression ratio
variable compression
Prior art date
Application number
PCT/JP2019/003791
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English (en)
Japanese (ja)
Inventor
正登 真子
健 ブライアン 池口
Original Assignee
日立オートモティブシステムズ株式会社
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Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Publication of WO2019167553A1 publication Critical patent/WO2019167553A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • 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

Definitions

  • the present invention relates to an actuator for a variable compression ratio mechanism of an internal combustion engine and an actuator used for an internal combustion engine device.
  • Patent Document 1 discloses an actuator that reduces the rotational speed of an electric motor by a wave gear reducer and transmits it to the control shaft as an actuator that changes the rotational position of the control shaft of the variable compression ratio mechanism.
  • the flexible external gear of the wave gear reducer includes a cylindrical body, a diaphragm that closes one end of the body, and a boss that is integrally formed at the center of the diaphragm and is connected to the control shaft.
  • One of the objects of the present invention is to provide an actuator for a variable compression ratio mechanism of an internal combustion engine and an actuator used for an internal combustion engine device that can shorten the axial length.
  • At least a part of the boss portion extends in the axial direction from the bottom portion and is connected to the control shaft.
  • the shaft length of the actuator can be shortened.
  • FIG. 1 is a schematic view of an internal combustion engine including an actuator of a variable compression ratio mechanism according to Embodiment 1.
  • FIG. 3 is an exploded perspective view of an actuator 40 of the variable compression ratio mechanism according to the first embodiment.
  • FIG. 3 is a side view of an actuator 40 of the variable compression ratio mechanism according to the first embodiment.
  • FIG. 4 is a cross-sectional view taken along line S4-S4 in FIG. 3. It is a figure which shows the flexible external gear 36 of Embodiment 1.
  • FIG. FIG. 5 is an enlarged view of a main part of FIG. 4 showing the actuator 40 of the first embodiment.
  • FIG. 5 is an enlarged view of a main part of FIG. 4 showing an actuator 40 according to a second embodiment.
  • FIG. 6 is a cross-sectional view taken along the line cc in FIG. 5A showing a flexible external gear 36 according to the third embodiment. It is a figure which shows the flexible external gear 36 of Embodiment 4.
  • FIG. 1 is a schematic view of an internal combustion engine provided with an actuator of a variable compression ratio mechanism according to a first embodiment.
  • the basic configuration is the same as that described in FIG. 1 of Japanese Patent Application Laid-Open No. 2011-169251, for example, and will be described briefly.
  • the piston 1 reciprocates in a cylinder of a cylinder block in an internal combustion engine (gasoline engine).
  • the upper end of the upper link 3 is rotatably connected to the piston 1 via a piston pin 2.
  • a lower link 5 is rotatably connected to the lower end of the upper link 3 via a connecting pin 6.
  • a crankshaft 4 is rotatably connected to the lower link 5 via a crankpin 4a.
  • the connection mechanism 9 includes a first control shaft 10, a second control shaft (control shaft) 11, a second control link 12, and an arm link 13.
  • the first control shaft 10 is disposed in parallel with the crankshaft 4 disposed along the cylinder row direction inside the internal combustion engine.
  • the first control shaft 10 includes a first journal portion 10a, a control eccentric shaft portion 10b, an eccentric shaft portion 10c, a first arm portion 10d, and a second arm portion 10e.
  • the first journal portion 10a is rotatably supported by the internal combustion engine body.
  • the control eccentric shaft portion 10b is rotatably connected to the lower end portion of the first control link 7.
  • the eccentric shaft portion 10c is rotatably connected to one end portion 12a of the second control link 12.
  • One end of the first arm portion 10d is connected to the first journal portion 10a.
  • the other end of the first arm portion 10d is connected to the control eccentric shaft portion 10b.
  • the control eccentric shaft portion 10b is located at a position offset by a predetermined amount with respect to the first journal portion 10a.
  • One end of the second arm portion 10e is connected to the first journal portion 10a.
  • the other end of the second arm portion 10e is connected to the eccentric shaft portion 10c.
  • the eccentric shaft portion 10c is at a position that is eccentric by a predetermined amount with respect to the first journal portion 10a.
  • One end of the arm link 13 is rotatably connected to the other end portion 12b of the second control link 12.
  • the other end of the arm link 13 is connected to the second control shaft 11.
  • the arm link 13 and the second control shaft 11 do not move relative to each other.
  • the second control shaft 11 is rotatably accommodated in a housing 20 described later.
  • the second control link 12 has a lever shape, and one end portion 12a connected to the eccentric shaft portion 10c is formed substantially linearly.
  • FIG. 2 is an exploded perspective view of the actuator 40 of the variable compression ratio mechanism according to the first embodiment
  • FIG. 3 is a side view of the actuator 40
  • FIG. 4 is a sectional view taken along line S4-S4 in FIG.
  • the other end portion 12 b of the second control link 12 is curved and the arm link 13 is connected.
  • An insertion hole 12c through which the eccentric shaft portion 10c is rotatably inserted is formed through the distal end portion of the one end portion 12a of the second control link 12.
  • the other end portion 12b has a tip end portion 12d.
  • a connecting hole 12e is formed through the tip portion 12d.
  • the arm link 13 is formed separately from the second control link 12.
  • the arm link 13 has an annular portion 13d and a pair of arm portions 13b1 and 13b2.
  • a press-fitting hole 13a is formed through the annular portion 13d.
  • a fixing portion 11b formed between the journal portions 11c and 11d of the second control shaft 11 is press-fitted.
  • the pair of arm portions 13b1 and 13b2 are formed in a bifurcated shape protruding from the annular portion 13d toward the outer periphery.
  • a pair of connecting holes 13c is formed through the pair of arm portions 13b1 and 13b2.
  • a distal end portion 12d of the second control link 12 is inserted between the pair of arm portions 13b1 and 13b2.
  • connection pin 14 is inserted into each connection hole 12e, 13c, 13c.
  • the center of each of the connection holes 12e, 13c, 13c (the axis of the connection pin 14) is eccentric by a predetermined amount with respect to the axis of the second control shaft 11.
  • the actuator 40 includes a drive motor 22, a wave gear reducer 50, a housing 20, and a second control shaft 11.
  • a direction along the rotation axis O of the motor shaft 48 of the drive motor 22 is referred to as an axial direction
  • a radial direction of the rotation axis O is referred to as a radial direction
  • a direction around the rotation axis O is referred to as a circumferential direction.
  • the X axis is set in the axial direction, and in the X axis direction, the direction from the motor shaft 48 side to the second control shaft 11 side is the positive direction, and from the second control shaft 11 side to the motor shaft 48 side.
  • the direction to go is defined as the negative X-axis direction.
  • the actuator 40 changes the rotational position of the second control shaft 11 by decelerating the rotational speed of the drive motor 22 by the wave gear reducer 50 and transmitting it to the second control shaft 11.
  • the rotational position of the second control shaft 11 is changed, the attitude of the second control link 12 is changed, the first control shaft 10 is rotated, and the position of the lower end portion of the first control link 7 is changed.
  • the posture of the lower link 5 changes, and the stroke position and stroke amount of the piston 1 in the cylinder change.
  • the engine compression ratio of the internal combustion engine can be changed.
  • the drive motor 22 is a DC brushless motor, for example, and has a motor casing 45, a coil 46, a rotor 47, and a motor shaft 48.
  • the motor casing 45 is formed in a bottomed cylindrical shape and is fixed to the second housing 20 b of the housing 20.
  • the coil 46 is fixed to the inner peripheral surface of the motor casing 45.
  • the rotor 47 is rotatably disposed inside the coil 46.
  • the motor shaft 48 is fixed at the center of the rotor 47.
  • the motor shaft 48 is rotatably provided to the second housing 20b and the motor casing 45 through two ball bearings 51 and 52.
  • the ball bearing 51 is fixed to the second housing 20b.
  • Ball bearing 52 is fixed to the bottom of motor casing 45.
  • the tip 48a of the motor shaft 48 on the X axis positive direction side penetrates the second housing 20b and is connected to the wave generating plug 371 of the wave generator 37 of the wave gear reducer 50.
  • the second control shaft 11 is located on the X axis positive direction side of the motor shaft 48 and is coaxial with the motor shaft 48. That is, the second control shaft 11 and the motor shaft 48 have the same rotation axis O.
  • An end (control shaft first end) 11a on the X axis negative direction side of the second control shaft 11 is connected to a boss portion 363 of the flexible external gear 36 of the wave gear reducer 50.
  • the motor casing 45 has a plurality of boss portions 45a. Each boss portion 45a is formed with a bolt hole 45b through which the bolt 49 is passed.
  • the motor casing 45 is fixed to the second housing 20b by screwing the bolt 49 into the female screw portion 20b1 formed in the second housing 20b.
  • the interior of the motor casing 45 and the second housing 20b is maintained by a seal 100 in a drying chamber that does not supply lubricating oil or the like.
  • the wave gear reducer 50 is accommodated in the housing 20.
  • the wave gear reducer 50 includes a rigid internal gear (internal gear) 38, a flexible external gear 36, and a wave generator 37.
  • the rigid internal gear 38 is a rigid annular member having a plurality of internal teeth 38a on the inner periphery.
  • the rigid internal gear 38 is fixed to the first housing 20 a of the housing 20.
  • the flexible external gear 36 is disposed on the radially inner side of the rigid internal gear 38.
  • 5A and 5B are diagrams showing the flexible external gear 36 according to the first embodiment, where FIG. 5A is a front view, FIG. 5B is a right side view, and FIG. 5C is a cross-sectional view taken along line cc in FIG. is there.
  • the flexible external gear 36 is formed of a metal material, and has a body part 361, a bottom part 362, and a boss part (first boss part) 363.
  • the body 361 is formed in a thin cylindrical shape that can be bent and deformed.
  • the X-axis negative direction end (body second end) 361b is opened.
  • External teeth 364 are formed on the X axis negative direction side of the outer peripheral surface of the body portion 361.
  • the external teeth 364 mesh with the internal teeth 38a of the rigid internal gear 38.
  • the number of external teeth 364 is two fewer than the number of internal teeth 38a.
  • the bottom portion 362 extends radially inward from the X axis positive direction end portion (body first end portion) 361a of the body portion 361.
  • the thickness of the bottom portion 362 substantially matches the thickness of the body portion 361.
  • the boss portion 363 is formed in a cylindrical shape extending from the bottom portion 362 to the X axis negative direction side.
  • the X-axis negative direction end of the boss portion 363 is located on the X-axis positive direction side with respect to the X-axis negative direction end of the body portion 361. That is, the boss portions 363 are all located inside the trunk portion 361.
  • the boss portion 363 partially overlaps the external teeth 364 in the X-axis direction on the X-axis negative direction side.
  • the boss 363 has a hole 363a on the inner periphery thereof.
  • the hole portion 363a has a plurality of wavy grooves (groove portions) 363a1 arranged in the circumferential direction on the inner peripheral surface thereof.
  • the hole portion 363a is a spline hole, and the wavy groove 363a1 is each groove of the spline hole.
  • the end 11a of the second control shaft 11 is inserted into the hole 363a.
  • the end portion 11a has a plurality of wavy protrusions (protrusion portions) 11a1 that are arranged in the circumferential direction and can be fitted in the wavy groove 363a1 on the outer peripheral surface thereof. That is, the end portion 11a is a spline shaft, and the wavy projection 11a1 is each projection of the spline shaft.
  • the wavy groove 363a1 and the wavy protrusion 11a1 mesh the second control shaft 11 and the boss portion 363 in the circumferential direction, and allow the relative movement between the second control shaft 11 and the boss portion 363 in the X-axis direction. It is.
  • the shape of the cross section orthogonal to the rotation axis O of the wavy groove 363a1 and the wavy protrusion 11a1 is formed using an involute curve. That is, the coupling unit 101 is an involute spline.
  • the wavy groove 363a1 and the wavy protrusion 11a1 are engaged with each other with a predetermined play in the radial direction. For this reason, the end portion 11a can move relative to the hole portion 363a by a predetermined range in the radial direction.
  • the outer peripheral surface of the wave generator 37 slides along the inner peripheral surface of the flexible external gear 36.
  • the wave generator 37 has a wave generating plug 371 and a ball bearing (rolling bearing) 372.
  • the wave generating plug 371 has an elliptical outer shape in a cross section orthogonal to the rotation axis O, and has an elliptical outer shape having a major axis portion with the largest radius and a minor axis portion with the smallest radius about the rotation axis O. .
  • the wave generating plug 371 is supported rotatably with respect to the second housing 20b via a ball bearing 37a.
  • the wave generating plug 371 has a through hole 371b at the center.
  • the tip 48a of the motor shaft 48 is press-fitted into the through hole 371b.
  • the end surface of the wave generating plug 371 on the X axis positive direction side is an abutting surface 371a.
  • the abutting surface 371a abuts on the boss portion 363 and restricts the movement of the boss portion 363 in the negative direction of the X axis. Therefore, as shown in FIG. 6, in the X-axis direction, the clearance ⁇ D1 between the boss portion 363 and the abutting surface 371a is larger than the clearance ⁇ D2 between the X-axis negative direction end portion 361b of the body 361 and the ball bearing 37a. It is set small.
  • the ball bearing 372 allows relative rotation between the outer periphery of the wave generating plug 371 and the inner periphery of the flexible external gear 36.
  • the ball bearing 372 includes an inner ring 372a, an outer ring 372b, a plurality of balls 372c, and a cage 372d.
  • the inner ring 372a is formed integrally with the outer peripheral surface of the wave generating plug 371.
  • the outer ring 372b is formed in a thin annular shape having flexibility, and is in contact with the inner periphery of the flexible external gear 36.
  • the plurality of balls 372c are formed in a spherical shape and are disposed between the inner ring 372a and the outer ring 372b.
  • the cage 372d is disposed between the inner ring 372a and the outer ring 372b, and keeps the interval between the balls 372c constant.
  • the housing 20 has a first housing 20a and a second housing 20b, and is formed in a substantially cubic shape by an aluminum alloy material.
  • a large-diameter annular opening groove 20c is formed on the X-axis negative direction side of the first housing 20a (see FIG. 4).
  • the opening groove 20c is closed by the second housing 20b.
  • the second housing 20b has a motor shaft through hole 20d through which the motor shaft 48 penetrates at a central position, and four boss portions 20e having a diameter expanded toward the radially outer peripheral side.
  • the first housing 20a and the second housing 20b are fastened by a bolt 35 inserted through the boss portion 20e.
  • an opening (not shown) for the second control link 12 connected to the arm link 13 is formed on the side surface closer to the X-axis positive direction than the opening groove 20c.
  • a storage chamber 29 serving as an operation region of the arm link 13 and the second control link 12 is formed (see FIG. 4).
  • a support hole 30b through which the second journal portion 11d of the second control shaft 11 passes is formed between the opening groove portion 20c and the storage chamber 29 in the X-axis direction.
  • a support hole 30a through which the first journal portion 11c of the second control shaft 11 passes is formed on the X axis positive direction side of the storage chamber 29.
  • a bearing 301 as a bearing portion is disposed between the inner peripheral surface of the support hole 30a and the outer peripheral surface of the first journal portion 11c.
  • a bearing 304 as a bearing portion is disposed between the inner peripheral surface of the support hole 30b and the outer peripheral surface of the second journal portion 11d.
  • the radial play between the bearing 301 and the first journal part 11c and the radial play between the bearing 304 and the second journal part 11d are smaller than the radial play between the wavy groove 363a1 and the wavy projection 11a1.
  • a retainer receiving hole 31 is formed on the positive side of the support hole 30a in the X-axis direction. The inner diameter of the retainer receiving hole 31 is larger than the inner diameter of the support hole 30a.
  • the retainer accommodation hole 31 and the support hole 30a are connected by a step surface 31a.
  • the step surface 31a is orthogonal to the rotation axis O.
  • a retainer 350 is accommodated in the retainer accommodation hole 31.
  • the retainer 350 is formed in an annular shape, and the second control shaft 11 is press-fitted therein. The retainer 350 restricts the movement of the second control shaft 11 in the negative X-axis direction by contacting the step surface 31a in the X-axis direction.
  • An angle sensor 32 is attached to the X axis positive direction end of the housing 20.
  • the angle sensor 32 detects the rotation angle of the second control shaft 11.
  • the rotation angle detected by the angle sensor 32 is sent to a control unit (not shown) of the drive motor 22 housed in the motor casing 45.
  • the angle sensor 32 has a sensor holder 32a attached so as to close the retainer receiving hole 31 from the outside of the housing 20.
  • the sensor holder 32a has a flange portion 32a1 for fixing to the first housing 20a with a bolt 321.
  • a seal ring 33 is installed between the sensor holder 32a and the first housing 20a. The seal ring 33 ensures liquid tightness between the retainer receiving hole 31 and the outside.
  • a sensor cover 32c for closing the retainer receiving hole 31 is provided outside the sensor holder 32a.
  • a seal ring 323 is installed between the sensor cover 32c and the sensor holder 32a. The seal ring 323 ensures liquid tightness between the retainer receiving hole 31 and the outside.
  • the sensor cover 32c is fastened to the sensor holder 32a by a bolt 34.
  • the rotor 32b of the angle sensor 32 is formed in an elliptical ring shape, and is fixed to an end portion (control shaft second end portion) 11e of the second control shaft 11 on the X axis positive direction side.
  • the angle sensor 32 is a so-called resolver, and detects a change in the distance between the inner periphery of the sensor holder 32a and the outer periphery of the rotor 32b due to the rotation of the rotor 32b by a change in inductance of a detection coil (not shown). Thereby, the rotational position of the rotor 32b, that is, the rotational angle of the second control shaft 11 is detected.
  • a flange (restricting portion) 11f is formed on the X axis positive direction side of the end portion 11a.
  • the flange 11f abuts on the boss portion 363 of the flexible external gear 36 and restricts the movement of the flexible external gear 36 in the positive direction of the X axis.
  • the outer diameter of the flange 11f is smaller than the outer diameter of the boss portion 363.
  • the end portion 11a has an annular relief groove (groove) 11g recessed inward in the radial direction at a connection portion with the flange 11f.
  • the second control shaft 11 has a supply oil passage 111.
  • the supply oil passage 111 has an axial oil passage 111a and a radial oil passage 111b.
  • the shaft center oil passage 111a extends in the X-axis direction from the center of the second control shaft 11 and opens at the X-axis negative direction end of the second control shaft 11.
  • Lubricating oil pumped from an oil pump (not shown) is introduced into the shaft center oil passage 111a through an oil passage (not shown) formed in the first housing 20a.
  • An orifice 111c is attached to the end of the axial center oil passage 111a in the negative X-axis direction. Lubricating oil that has flowed out of the second control shaft 11 from the X axis negative direction end of the shaft center oil passage 111a (orifice 111c) is used for lubrication of the wave generator 37 and the coupling portion 101.
  • the radial oil passage 111b extends radially outward from the axial oil passage 111a and opens into the escape groove 11g.
  • the lubricating oil that has flowed out of the second control shaft 11 from the shaft center oil passage 111a is used for lubrication of the wave generator 37 and the coupling portion 101.
  • the effect of Embodiment 1 is demonstrated.
  • the boss portion 363 extends from the bottom portion 362 to the X axis negative direction side and is connected to the second control shaft 11. That is, at least a part of the boss portion 363 is located on the radially inner side of the body portion 361.
  • the axial length of the flexible external gear 36 can be shortened in the direction along the rotational axis of the body portion 361 as compared with the conventional actuator in which the boss portion is disposed on the opposite side of the body portion 361 across the bottom portion. .
  • the shaft length of the actuator 40 can be shortened, and the degree of freedom of the vehicle mounting layout can be improved.
  • the distance from the meshing position of the inner teeth 38a and the outer teeth 364 in the X-axis direction to the boss portion 363 can be shortened. Therefore, when the flexible external gear 36 is deformed elliptically, the distance in the X-axis direction to the force point (the boss portion 363) can be shortened when the meshing position of the internal teeth 38a and the external teeth 364 is used as a fulcrum. As a result, as shown in FIG. 6, the elliptical deformation stress acting on the connecting portion (corner R portion) A between the bottom portion 362 and the boss portion 363, which is the weakest strength portion in the flexible external gear 36, can be suppressed. As a result, the allowable torque increases and a strength corresponding to a higher torque is obtained, which is advantageous as an actuator for a variable compression ratio mechanism of an internal combustion engine.
  • the actuator 40 includes a coupling portion 101 that is provided on the second control shaft 11 and the boss portion 363, and the second control shaft 11 and the boss portion 363 are engaged with each other.
  • the explosive force in the expansion stroke of the internal combustion engine applies a radial load to the second control shaft 11 via the variable compression ratio mechanism.
  • the body of the flexible external gear The part 361 is inclined with respect to the rotation axis.
  • the coupling portion 101 can absorb the radial displacement of the end portion 11a.
  • the inclination of the external gear 36 is suppressed.
  • the meshing between the outer teeth 364 and the inner teeth 38a can be maintained satisfactorily, and the load acting on the ball bearing 372 can be reduced, so that a decrease in transmission efficiency can be suppressed.
  • the transmission loss of the output torque of the drive motor 22 is reduced, so that the power consumption of the drive motor 22 can be suppressed.
  • the coupling portion 101 includes a wavy protrusion 11a1 provided on the outer peripheral surface of the second control shaft 11, and a wavy groove 363a1 provided on the inner peripheral surface of the boss portion 363.
  • the wavy protrusion 11a1 and the wavy groove 363a1 are , Have play in the radial direction. Thereby, the coupling portion 101 can absorb the radial displacement of the end portion 11a caused by the deflection of the second control shaft 11 due to the radial play.
  • the coupling portion 101 allows relative movement in the X-axis direction between the second control shaft 11 and the boss portion 363.
  • the second control shaft 11 receives a reverse input from the variable compression ratio mechanism due to the explosive force in the expansion stroke of the internal combustion engine.
  • the reverse input torque is canceled by the output torque of the drive motor 22 in order to maintain the current compression ratio
  • the body 361 is twisted to generate a load in the X-axis direction.
  • the boss 363 fixed to the second control shaft does not move in the X-axis direction. There is a possibility that stress concentration may occur at the corner of the connecting portion with the boss portion 363.
  • the boss portion 363 can move in the X-axis direction with respect to the second control shaft 11, the boss portion 363 can follow the body portion 361 and be displaced in the X-axis direction. Thereby, the stress concentration generated in the connecting portion A between the bottom portion 362 and the boss portion 363 can be relaxed.
  • the wavy projections 11a1 are each projection of the spline shaft (end portion 11a), and the wavy grooves 363a1 are each groove of the spline hole (hole portion 363a). That is, the connection between the second control shaft 11 and the boss portion 363 is a spline fitting. Since spline fitting has a large number of meshing portions in the circumferential direction, the second control shaft 11 can be rotated forward and backward with a torque input from the internal combustion engine side as in a variable compression ratio mechanism, or at a fixed angle. For example, the torque transmission state between the second control shaft 11 and the boss portion 363 can be maintained regardless of the inclination or radial displacement of the second control shaft 11.
  • the boss portion 363 is located on the opposite side of the body portion 361 across the bottom portion, stress is concentrated on the connecting portion between the body portion 361 and the boss portion 363 when the flexible external gear is deformed elliptically. Almost damaged.
  • the boss portion 363 By installing the boss portion 363 on the inside, the impact load is absorbed by the flexible external gear 36 while satisfying the strength in spline fitting, and abnormal noise generated in each meshing portion can be reduced.
  • the end 11a and the hole 363a are involute splines. As a result, when the second control shaft 11 is rotated forward and backward or maintained at a constant angle, when a torque load is applied to the flexible external gear 36, the rotation axis of the second control shaft 11 is flexible.
  • a force in a direction to match the rotation axis of the external external gear 36 is applied to perform self-alignment.
  • wear at each meshing portion of the spline fitting can be suppressed.
  • the second control shaft 11 and the flexible external gear 36 are automatically aligned even during assembly, axial misalignment between the second control shaft 11 and the flexible external gear 36 can be suppressed, resulting in stable performance. Is excellent.
  • the end 11a of the second control shaft 11 is inserted into the hole 363a of the boss 363 on the radially inner side of the body 361. That is, since the coupling portion 101 between the second control shaft 11 and the boss portion 363 overlaps the body portion 361 in the X-axis direction, the axial length of the actuator 40 can be shortened.
  • the boss portion 363 can come into contact with the wave generator 37 when moved in the negative direction of the X axis.
  • the boss 363 functions as a retainer for the flexible external gear 36 and can prevent the flexible external gear 36 from falling off from the end 11a.
  • the wave generator 37 has an abutment surface 371a that restricts the movement of the boss portion 363 in the negative direction of the X axis. Accordingly, the movement range can be restricted while allowing the flexible external gear 36 to move in the negative direction of the X-axis, and the flexible external gear 36 can be prevented from falling off from the end portion 11a.
  • the second control shaft 11 has a flange 11f that restricts the movement of the bottom 362 in the positive direction of the X axis. Thereby, the movement range can be regulated while allowing the flexible external gear 36 to move in the positive direction of the X-axis. As a result, it is possible to prevent deterioration of the control function of the engine compression ratio and damage of the sliding contact portion due to the sliding contact of the flexible external gear 36 with the housing 20 or the bearing 304. Since the second control shaft 11 and the flexible external gear 36 rotate integrally, the engine compression ratio control function is not lowered and the sliding contact portion is not damaged.
  • the outer diameter of the flange 11f is smaller than the outer diameter of the boss portion 363.
  • the boss portions 363 are all on the radially inner side of the body portion 361. That is, since the boss 363 overlaps the body 361 in the X-axis direction over the entire length, the axial length of the actuator 40 can be shortened.
  • the second control shaft 11 has a supply oil passage 111 that opens to the inside of the body 361 in the radial direction and supplies lubricating oil to the inside of the body 361 in the radial direction. Accordingly, the lubricating oil can be supplied from the radially inner side of the flexible external gear 36 to the meshing position of the external teeth 364 and the internal teeth 38a and the ball bearing 372 of the wave generator 37.
  • the boss portion 363 is located on the radially inner side of the body portion 361, the distance between the end portion 11a of the second control shaft 11 and the lubricated portion can be reduced in the X-axis direction.
  • the supply oil path 111 can supply the lubricating oil to the coupling portion 101 via the radial play between the wavy groove 363a1 and the wavy projection 11a1, it is possible to suppress wear at each meshing portion of the spline fitting.
  • the end portion 11a of the second control shaft 11 has an annular relief groove 11g that is recessed inward in the radial direction at a connection portion with the flange 11f.
  • a relief shape such as a chamfer or an R portion
  • the thickness of the portion close to the connection with the thin portion (bottom portion 362) becomes thin, and the strength may be reduced.
  • the escape groove 11g on the second control shaft 11 side, it is possible to secure the wall thickness at the root portion (X-axis positive direction end portion) of the boss portion 363 and suppress the strength reduction of the boss portion 363. . Further, since the contact area of the boss portion 363 with the flange 11f is increased, durability against thrust load can be improved.
  • the boss portion 363 at least partially overlaps the external teeth 364 in the X-axis direction. Thereby, the axial length of the actuator 40 can be shortened. Further, since the distance from the meshing position of the inner teeth 38a and the outer teeth 364 in the X-axis direction to the boss portion 363 can be shortened, the elliptical deformation stress acting on the connecting portion A between the bottom portion 362 and the boss portion 363 can be suppressed.
  • the radial play between the wavy groove 363a1 and the wavy projection 11a1 is larger than the radial play between the bearing 301 and the first journal part 11c and the radial play between the bearing 304 and the second journal part 11d. As a result, even when the second control shaft 11 is bent, the tip of the wave-like protrusion 11a1 does not hit the bottom of the wave-like groove 363a1, so that a reduction in transmission efficiency can be suppressed.
  • FIG. 7 is an enlarged view of a main part of FIG. 4 showing the actuator 40 of the second embodiment.
  • the clearance ⁇ D1 between the boss portion 363 and the abutting surface 371a is set larger than the clearance ⁇ D2 between the X-axis negative direction end portion 361b of the body portion 361 and the ball bearing 37a. .
  • the X-axis negative direction end 361b of the body 361 is on the X-axis positive direction side of the outer ring 37a1 of the ball bearing 37a. Abutting against the abutting surface 37a1a, which is an end surface, is restricted from moving in the negative direction of the X axis.
  • the housing 20 of the second embodiment has an abutment surface 37a1a that restricts the movement of the body 361 in the negative X-axis direction. Accordingly, the movement range can be restricted while allowing the flexible external gear 36 to move in the negative direction of the X-axis, and the flexible external gear 36 can be prevented from falling off from the end portion 11a.
  • FIG. 8 is a cross-sectional view taken along the line cc of FIG. 5 (a) showing the flexible external gear 36 of the third embodiment.
  • the flexible external gear 36 has a first boss portion 3632 extending from the bottom portion 362 to the X axis negative direction side, and a second boss portion 3633 extending from the bottom portion 362 to the X axis positive direction side.
  • the outer diameter of the first boss portion 3632 and the second boss portion 3633 and the length in the X-axis direction from the bottom portion 362 are the same.
  • the first boss portion 3632 and the second boss portion 3633 have a hole 363a on the inner periphery thereof.
  • the hole 363a has a wave-like groove (groove) 363a1 on the inner peripheral surface thereof.
  • a first boss portion 3632 extending from the bottom portion 362 to the X axis negative direction side, and a second boss extending from the bottom portion 362 to the X axis positive direction side and coupled to the second control shaft 11 together with the first boss portion 3632.
  • Part 3363 As a result, compared to the case where the second boss portion 3633 is not provided, the connecting portion of the flexible external gear 36 to the second control shaft 11 can be made longer in the X-axis direction. Can be improved.
  • FIG. 9A and 9B are diagrams showing the flexible external gear 36 according to the fourth embodiment, where FIG. 9A is a front view, FIG. 9B is a right side view, and FIG. 9C is a sectional view taken along line cc in FIG. is there.
  • FIG. 9A shows a front view of the end portion 11 a of the second control shaft 11.
  • the end portion 11a has four keys (projections) 11a2 on the outer peripheral surface thereof.
  • the keys 11a2 are arranged at equal intervals in the circumferential direction.
  • the key 11a2 is formed in a rectangular shape and extends in the X-axis direction.
  • the hole portion 363a has four key grooves (groove portions) 363a2 on the inner peripheral surface thereof.
  • the key grooves 363a2 are arranged at equal intervals in the circumferential direction.
  • Each keyway 363a2 is fitted with the corresponding key 11a2.
  • the key 11a2 and the key groove 363a2 are coupling portions 101 that mesh the second control shaft 11 and the boss portion 363 in the circumferential direction and allow relative movement between the second control shaft 11 and the boss portion 363 in the X-axis direction. is there.
  • the coupling portion 101 since the coupling portion 101 has the key 11a2 and the key groove 363a2 that fits with the key 11a2, the second control shaft 11 and the boss portion 363 can move relative to each other in the radial direction compared to the spline fitting.
  • a structure capable of transmitting the rotational force can be easily formed. Since there are a plurality of keys 11a2 and key grooves 363a2 in the circumferential direction, the load acting on each key 11a2 and key grooves 363a2 can be dispersed when the second control shaft 11 is held at a specific rotation angle. As a result, the durability of each key 11a2 and keyway 363a2 can be improved.
  • the embodiment for carrying out the present invention has been described above, the specific configuration of the present invention is not limited to the configuration of the embodiment, and there are design changes and the like within the scope not departing from the gist of the invention. Are also included in the present invention.
  • any combination or omission of each constituent element described in the claims and the specification is possible within a range where at least a part of the above-described problems can be solved or a range where at least a part of the effect is achieved.
  • the actuator of the present invention is particularly suitable as an actuator for a variable compression ratio mechanism of an internal combustion engine.
  • a valve timing adjustment for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft is also applicable to the device.
  • a supply oil passage for supplying lubricating oil to the flexible external gear may be provided in the housing.
  • the outer diameter of the wave generating plug is not necessarily limited to an elliptical shape, and may be a polygonal shape such as a triangular shape with corners formed in an arc shape.
  • an actuator for a variable compression ratio mechanism of an internal combustion engine has a drive motor that rotates a motor shaft, and an outer shape of a cross section that rotates integrally with the motor shaft and is orthogonal to the rotation axis of the motor shaft.
  • a non-circular wave generator and a bottomed cylindrical flexible external gear coupled to a control shaft that changes the attitude of the variable compression ratio mechanism of the internal combustion engine by rotating within a predetermined angular range;
  • a flexible external gear having a body portion, a bottom portion, external teeth, and a first boss portion.
  • the barrel portion is formed in a cylindrical shape having flexibility that can be deformed and deformed in a non-circular shape by rotation of the wave generator, and the bottom portion has the axial direction when the direction along the rotation axis is an axial direction.
  • the first end and the second end of the body which are both ends of the body, and the external teeth are configured such that the radial direction of the rotation axis is a radial direction.
  • at least a part of the first boss portion extends in the axial direction from the bottom portion toward the second end portion of the trunk portion, and is provided on the radially outer surface of the trunk portion.
  • the actuator further includes an internal gear that meshes with the external teeth of the body part that is deformed by bending.
  • the first boss portion has, on its inner periphery, the control shaft among the control shaft first end portion and the control shaft second end portion which are both end portions of the control shaft in the axial direction. A shaft first end portion is inserted, and the control shaft first end portion is inserted inside the body portion in the radial direction.
  • the connection between the first boss portion and the control shaft is achieved by spline fitting.
  • the first boss portion can contact the wave generator in the axial direction.
  • the control shaft is a restricting portion capable of contacting the first boss portion in the axial direction, and the body portion from the body second end portion.
  • a restricting portion for restricting movement of the flexible external gear toward the side toward the first end portion is provided.
  • the restriction portion is a flange capable of contacting the bottom portion, and in the radial direction, an outer diameter of the flange is equal to or less than an outer diameter of the first boss portion. It is.
  • the first boss part is entirely inside the trunk part in the radial direction.
  • the flexible external gear is a second boss portion that extends in the axial direction from the bottom portion toward the body first end portion, and It has the 2nd boss
  • the wave generator includes a rolling bearing that is in contact with an inner periphery of the flexible external gear in the radial direction, and the control shaft is A supply oil passage for supplying lubricating oil to the inside of the body portion is provided.
  • control shaft includes a restriction portion that restricts movement of the flexible external gear in the axial direction, and a side of the body portion second end from the restriction portion.
  • a first end portion of the control shaft extending into the first boss portion, and the first end portion of the control shaft has a groove recessed inward in the radial direction at a connecting portion with the restricting portion.
  • at least a part of the first boss portion overlaps the external teeth in the axial direction.
  • an actuator used for an internal combustion engine device has a drive motor that rotates a motor shaft and a cross section that rotates integrally with the motor shaft and is orthogonal to the rotation axis of the output shaft.
  • a non-circular wave generator and a bottomed cylindrical flexible external gear coupled to a control shaft that changes the attitude of the internal combustion engine device by rotating within a predetermined angular range,
  • a flexible external gear having a portion, a bottom portion, external teeth, and a first boss portion.
  • the barrel portion is formed in a cylindrical shape having flexibility that can be deformed and deformed in a non-circular shape by rotation of the wave generator, and the bottom portion has the axial direction when the direction along the rotation axis is an axial direction.
  • the actuator further includes an internal gear that meshes with the external teeth of the body part that is deformed by bending.

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

Abstract

L'invention concerne un actionneur pour un mécanisme à taux de compression variable pour un moteur à combustion interne et un actionneur utilisé dans un dispositif pour un moteur à combustion interne, avec lesquels il est possible de raccourcir la longueur de l'arbre. Au moins une partie d'une première partie de bossage d'un engrenage externe flexible s'étend dans la direction axiale à partir de son fond et est reliée à l'arbre de commande.
PCT/JP2019/003791 2018-03-01 2019-02-04 Actionneur pour mécanisme à taux de compression variable pour moteur à combustion interne et actionneur utilisé dans un dispositif pour moteur à combustion interne WO2019167553A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-036291 2018-03-01
JP2018036291A JP2019152111A (ja) 2018-03-01 2018-03-01 内燃機関の可変圧縮比機構のアクチュエータおよび内燃機関用機器に用いられるアクチュエータ

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WO2019167553A1 true WO2019167553A1 (fr) 2019-09-06

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PCT/JP2019/003791 WO2019167553A1 (fr) 2018-03-01 2019-02-04 Actionneur pour mécanisme à taux de compression variable pour moteur à combustion interne et actionneur utilisé dans un dispositif pour moteur à combustion interne

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010151088A (ja) * 2008-12-26 2010-07-08 Nissan Motor Co Ltd 内燃機関の可変圧縮比装置
WO2014027497A1 (fr) * 2012-08-13 2014-02-20 日産自動車株式会社 Dispositif de commande et procédé de commande pour moteurs à combustion interne à taux de compression variable
WO2017141673A1 (fr) * 2016-02-16 2017-08-24 日立オートモティブシステムズ株式会社 Actionneur de mécanismes de liaison pour moteurs à combustion interne

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010151088A (ja) * 2008-12-26 2010-07-08 Nissan Motor Co Ltd 内燃機関の可変圧縮比装置
WO2014027497A1 (fr) * 2012-08-13 2014-02-20 日産自動車株式会社 Dispositif de commande et procédé de commande pour moteurs à combustion interne à taux de compression variable
WO2017141673A1 (fr) * 2016-02-16 2017-08-24 日立オートモティブシステムズ株式会社 Actionneur de mécanismes de liaison pour moteurs à combustion interne

Also Published As

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