WO2019044116A1 - Réducteur de vitesse d'engrenage à ondes et actionneur de mécanisme de liaison pour moteur à combustion interne - Google Patents

Réducteur de vitesse d'engrenage à ondes et actionneur de mécanisme de liaison pour moteur à combustion interne Download PDF

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Publication number
WO2019044116A1
WO2019044116A1 PCT/JP2018/022613 JP2018022613W WO2019044116A1 WO 2019044116 A1 WO2019044116 A1 WO 2019044116A1 JP 2018022613 W JP2018022613 W JP 2018022613W WO 2019044116 A1 WO2019044116 A1 WO 2019044116A1
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WIPO (PCT)
Prior art keywords
wave generator
wave
input shaft
recess
groove
Prior art date
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PCT/JP2018/022613
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English (en)
Japanese (ja)
Inventor
鈴木　健太
真 辺見
健ブライアン 池口
淳一郎 鬼形
Original Assignee
日立オートモティブシステムズ株式会社
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Publication of WO2019044116A1 publication Critical patent/WO2019044116A1/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
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/06—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/06—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers
    • F16D7/10—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers moving radially between engagement and disengagement
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the present invention relates to a wave gear reducer and an actuator of a link mechanism for an internal combustion engine provided with the wave gear reducer.
  • the wave gear reducer includes a rigid internal gear having an internal tooth on the inner side with a perfect circular ring member, a flexible external gear having an external tooth disposed on the inner side of the rigid internal gear, and a flexible external gear. It has an elliptical wave generator fitted inside.
  • the rigid internal gear is fixed so as not to rotate.
  • the flexible external gear is a thin-walled cylindrical member capable of bending and deformation, and is connected to the control shaft of the actuator.
  • the wave generator is rotated by a drive source such as a motor.
  • the number of teeth of the rigid internal gear is greater than the number of teeth of the flexible external gear.
  • the flexible external gear As the wave generator rotates, the flexible external gear is deformed by the wave generator into an elliptical shape inside the rigid internal gear.
  • the flexible external gear rotates relative to the rigid internal gear according to the difference in the number of teeth with the rigid internal gear due to meshing between the rigid internal gear and the teeth while being deformed.
  • the rotation of the input side (wave generator) is decelerated according to the difference in the number of teeth between the rigid internal gear and the flexible external gear.
  • the wave gear reducer includes a flexible external gear which is a thin cylindrical member, and if excessive torque is generated, there is a possibility that breakage such as scraping of the teeth of the gear may occur.
  • the wave generator includes a torque limiter mechanism that limits the torque transmitted from the wave generator to the flexible external gear.
  • the wave generator includes a rigid cam plate, a hub inserted at the center of the rigid cam plate, a torque limiter mechanism having an elastic member and a ball, and the torque limit mechanism is
  • the transmission of the torque is limited by generating a slip in the rotational direction between the rigid cam plate and the hub, thereby avoiding breakage of the wave gear reducer.
  • Patent Document 2 describes an example of an actuator of a link mechanism for an internal combustion engine.
  • the object of the present invention is to provide a wave gear reducer capable of preventing damage due to generation of excessive torque and shortening the time during which the actuator can not be controlled after elimination of excessive torque, and an internal combustion engine equipped with this wave gear reducer. It is providing the actuator of a link mechanism.
  • the wave gear reducer according to the present invention is annular, has a rigid internal gear having a plurality of teeth on its inner circumferential surface, and is cylindrical, has a plurality of teeth on its outer circumferential surface, and is disposed inside the rigid internal gear.
  • a flexible external gear, and an annular ring having an outer periphery that is elliptical and disposed inside the flexible external gear, the outer peripheral surface of which is slid along the inner peripheral surface of the flexible external gear A movable wave generator, an input shaft connected to a central portion of the wave generator, which when rotated rotates the flexible external gear by rotating the wave generator, a plurality of elastic members, the elastic And a plurality of spherical members fixed to one end of the member.
  • the wave generator and the input shaft are provided with a plurality of concave portions opened in a connection surface between the wave generator and the input shaft in the circumferential direction.
  • Each of the elastic members is disposed in one of the recess of the wave generator and the recess of the input shaft, and the spherical member is fixed to the one end on the opening side of the one recess.
  • Each of the spherical members partially enters into the other of the recess of the wave generator and the recess of the input shaft.
  • the present invention it is possible to prevent damage due to the generation of excessive torque, and to reduce the time during which the actuator can not be controlled after elimination of the excessive torque, and a link for an internal combustion engine equipped with this wave gear reducer.
  • An actuator of the mechanism can be provided.
  • FIG. 1 is a schematic view of a link mechanism for an internal combustion engine provided with an actuator according to the present invention. It is sectional drawing of the actuator of the link mechanism for internal combustion engines by Example 1 of this invention.
  • FIG. 1 is an exploded isometric view of a wave gear drive according to a first embodiment of the present invention. It is an axial sectional view of a wave generator and a motor output shaft in Example 1 of the present invention. It is radial direction sectional drawing of a wave generator and a motor output shaft in the connection position of a wave generator and a motor output shaft in Example 1 of this invention. It is an axial direction sectional view of a wave generator and a motor output shaft in Example 2 of the present invention.
  • Example 3 of this invention it is a figure which shows the elastic member installed in space in the normal time in which excessive torque is not acting on a wave gear reduction gear.
  • Example 3 of this invention when an excessive torque acts on a wave gear reduction gear, it is a figure which shows the elastic member installed in space.
  • the wave gear reducer comprises a rigid internal gear, a flexible external gear disposed inside the rigid internal gear, a wave generator disposed inside the flexible external gear, and wave generation.
  • An input shaft connected to a central portion of the vessel, a plurality of elastic members, and a plurality of spherical members each fixed to one end of the elastic member.
  • the wave generator and the input shaft are provided with a plurality of recesses (grooves or recesses described in the embodiment) open in the connecting surface between the wave generator and the input shaft in the circumferential direction.
  • Each of the elastic members is disposed in one of the concave portions of the wave generator and the concave portion of the input shaft (the groove portion described in the embodiment), and one end of the opening side of the one concave portion (groove portion) is a spherical member Is fixed.
  • Each of the spherical members partially enters into the other recess (the recess described in the embodiment) of the recess of the wave generator and the recess of the input shaft.
  • a wave gear reducer according to an embodiment of the present invention and an actuator of a link mechanism for an internal combustion engine including the wave gear reducer will be described with reference to the drawings.
  • FIG. 1 is a schematic view of a link mechanism for an internal combustion engine provided with an actuator according to the present invention.
  • the basic configuration of this link mechanism is described in, for example, Patent Document 2 (especially, FIG. 1 and its description), and therefore will be briefly described here.
  • the upper end of the upper link 3 is rotatably coupled to the piston 1 reciprocating in the cylinder of the cylinder block of the 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 the connection pin 6.
  • a crankshaft 4 is rotatably connected to the lower link 5 via a crankpin 4a.
  • the upper end portion of the first control link 7 is rotatably connected to the lower link 5 via the connection pin 8.
  • the lower end portion of the first control link 7 is connected to a link mechanism 9 having a plurality of link members.
  • the link mechanism 9 is a link mechanism of an internal combustion engine, and includes a first control shaft 10, a second control shaft (control shaft of an actuator) 11, and a second control link 12.
  • the first control shaft 10 extends in parallel with the crankshaft 4 extending in the internal cylinder row direction of the internal combustion engine.
  • the first control shaft 10 has a first journal 10a, a control eccentric shaft 10b, an eccentric shaft 10c, a first arm 10d, and a second arm 10e.
  • the first journal portion 10a is rotatably supported by the internal combustion engine body.
  • the lower end portion of the first control link 7 is rotatably connected to the control eccentric shaft portion 10b, and the control eccentric shaft portion 10b is provided at a position eccentric to the first journal portion 10a by a predetermined amount.
  • the eccentric shaft portion 10c is rotatably connected to one end portion 12a of the second control link 12, and is provided at a position eccentric to the first journal portion 10a by a predetermined amount.
  • One end of the first arm 10 d is connected to the first journal 10 a, and the other end is connected to the lower end of the first control link 7.
  • One end of the second arm 10 e is connected to the first journal 10 a, and the other end is connected to one end 12 a of the second control link 12.
  • One end of the arm link 13 is rotatably connected to the other end 12 b of the second control link 12.
  • the second control shaft 11 is connected to the other end of the arm link 13 such that relative movement is not possible.
  • the arm link 13 is a member separate from the second control shaft 11.
  • the second control shaft 11 is rotatably supported in a housing 20 described later via a plurality of journals.
  • the second control link 12 connects the first control shaft 10 and the second control shaft 11.
  • the second control link 12 is shaped like a lever, one end 12a connected to the eccentric shaft 10c is substantially straight, and the other end 12b connected to the arm link 13 is curved.
  • the distal end portion of the one end portion 12a is provided with an insertion hole through which the eccentric shaft portion 10c is rotatably inserted.
  • the second control shaft 11 is rotated by a torque transmitted from the electric motor via a wave gear reducer provided in an actuator of the link mechanism for an internal combustion engine.
  • the arm link 13 rotates about the second control shaft 11
  • the first control shaft 10 rotates via the second control link 12, and the lower end portion of the first control link 7 Position is changed.
  • the attitude of the lower link 5 changes, the stroke position and the stroke amount of the piston 1 in the cylinder change, and the engine compression ratio changes accordingly.
  • FIG. 2 is a cross-sectional view of the actuator 100 of the link mechanism for an internal combustion engine according to the first embodiment of the present invention.
  • the actuator 100 of the internal combustion engine link mechanism includes an electric motor 22, a wave gear reducer 21, a housing 20, and a second control shaft 11.
  • the electric motor 22 is, for example, a brushless motor, and includes a motor casing 45, a coil 46, a rotor 47, and a motor output shaft 48.
  • the motor casing 45 is a bottomed cylindrical member.
  • the coil 46 is fixed to the inner circumferential surface of the motor casing 45.
  • the rotor 47 is rotatably provided inside the coil 46.
  • the motor output shaft 48 is fixed at the center of the rotor 47, and one end thereof is rotatably supported by a ball bearing 52 provided at the bottom of the motor casing 45.
  • the wave gear reducer 21 reduces the rotational speed of the motor output shaft 48 and transmits the torque of the motor output shaft 48 to the second control shaft 11.
  • the second control shaft 11 is rotatably supported by the housing 20 and has a control shaft 23 and a fixing flange 24.
  • the control shaft 23 extends in the axial direction of the actuator 100.
  • the fixing flange 24 is located at one end of the control shaft 23 and extends radially outward of the control shaft 23.
  • the control shaft 23 and the fixing flange 24 integrally form a second control shaft 11 formed of an iron-based metal material.
  • the fixing flange 24 includes a plurality of bolt insertion holes formed at equal intervals in the circumferential direction of the outer peripheral portion.
  • the fixing flange 24 of the second control shaft 11 is coupled to the flange portion 36 b of the flexible external gear 36 of the wave gear reducer 21 by the bolt inserted into the bolt insertion hole.
  • FIG. 3 is an exploded isometric view of a wave gear reducer 21 according to a first embodiment of the present invention.
  • the wave gear reducer 21 is attached to one end of the electric motor 22 and provided inside the housing 20.
  • the wave gear reducer 21 is bolted to the inside of the opening groove 20 a of the housing 20.
  • a supply hole 20b for supplying lubricating oil from an oil pressure source not shown in FIG. 2 is opened above the wave gear reducer 21 in the direction of gravity.
  • the lubricating oil is supplied to the supply hole 20b, it drips on the lower wave gear reducer 21 and lubricates the respective rotating elements of the wave gear reducer 21.
  • the wave gear reducer 21 includes a rigid internal gear 27, a flexible external gear 36 disposed inside the rigid internal gear 27, a wave generator 37 disposed inside the flexible external gear 36, and a wave generator. It has an input shaft connected to the central part of 37. The input shaft is a motor output shaft 48 of the electric motor 22. Further, an output shaft is connected to the flexible external gear 36. This output shaft is the second control shaft 11 of the actuator 100.
  • the rigid internal gear 27 is a rigid annular member and has a plurality of teeth 27 a on its inner circumferential surface.
  • the rigid internal gear 27 is fixed to the housing 20.
  • the flexible external gear 36 is disposed radially inward of the rigid internal gear 27 and includes a plurality of teeth 36 a on the outer peripheral surface.
  • the teeth 36 a can mesh with the teeth 27 a of the rigid internal gear 27.
  • the flexible external gear 36 is a thin cylindrical member formed of a metal material and having a bottom portion, and is capable of bending deformation.
  • the number of teeth 36 a of the flexible external gear 36 is two less than the number of teeth 27 a of the rigid internal gear 27.
  • the bottom of the flexible external gear 36 is a flange 36 b.
  • the flange portion 36 b is provided with an insertion hole 36 c through which the second control shaft 11 penetrates radially inward.
  • the flexible external gear 36 is connected to the second control shaft 11 of the actuator 100.
  • the second control shaft 11 passes through the insertion hole 36 c of the flexible external gear 36.
  • the flange portion 36 b of the flexible external gear 36 is bolted to the fixing flange 24 of the second control shaft 11. Therefore, the flexible external gear 36 can support the second control shaft 11 with the insertion hole 36c, and can secure the rigidity of the bottom.
  • the wave generator 37 is an annular member with an elliptical outer periphery, and is disposed radially inward of the flexible external gear 36, and the outer peripheral surface slides along the inner circumferential surface of the flexible external gear 36. It is possible.
  • the wave generator 37 includes a wave generating plug 371 and a deep groove ball bearing 372, and an input shaft (motor output shaft 48) is connected to the central portion.
  • the wave generating plug 371 has an elliptical outer periphery, and the motor output shaft 48 is fixed by press-fitting at its central portion.
  • the deep groove ball bearing 372 includes a flexible thin inner and outer ring located between the outer periphery of the wave generating plug 371 and the inner periphery of the flexible outer gear 36, and the thin inner and outer rings are flexible with the wave generating plug 371. Allow relative rotation between the external gears 36.
  • the wave generation plug 371 rotates.
  • the rotation of the wave generation plug 371 causes the flexible external gear 36 to rotate and the second control shaft 11 of the actuator 100 to rotate.
  • the torque of the motor output shaft 48 is transmitted to the second control shaft 11 via the wave gear reducer 21.
  • the arm link 13 rotates about the second control shaft 11 (see FIG. 1).
  • the torque limiter mechanism is flexible from the wave generator 37 in order to prevent the wave gear reducer 21 from being damaged by the excessive torque when the excessive torque is generated on the motor output shaft 48 of the electric motor 22. Limit the torque transmitted to the external gear 36.
  • FIG. 4 is an axial sectional view of the wave generator 37 and the motor output shaft 48 of the wave gear reducer 21 according to the first embodiment of the present invention.
  • FIG. 5 is a radial cross-sectional view of the wave generator 37 and the motor output shaft 48 at the connection position of the wave generator 37 and the motor output shaft 48.
  • the axial direction is the axial direction of the actuator 100, that is, the axial direction of the motor output shaft 48 or the second control shaft 11, and the radial direction is a direction perpendicular to the axial direction.
  • the outer periphery of the wave generating plug 371 of the wave generator 37 is elliptical, and the motor output shaft 48 is fixed at the center thereof.
  • the motor output shaft 48 includes a plurality of torque limiter mechanisms 60 in the circumferential direction.
  • the torque limiter mechanism 60 includes an elastic member 60 a such as a spring and a spherical member 60 b such as a steel ball, and is disposed at equal intervals in the circumferential direction of the motor output shaft 48.
  • the motor output shaft 48 is provided with a groove 48 a on the connecting surface with the wave generating plug 371.
  • the groove portion 48a extends in the radial direction, and the outer side in the radial direction is open (that is, the motor output shaft 48 is opened at the connection surface with the wave generating plug 371), and the elastic member 60a is installed therein.
  • the spherical member 60b is fixed to one end on the radially outer side (that is, the opening side of the groove 48a), the other end abuts on the bottom of the groove 48a, and the elastic force mainly acts in the radial direction.
  • the motor output shaft 48 has a shape in which the diameter of the connection portion with the wave generating plug 371 is larger than the diameter of the other portions in FIG. 4, the motor output shaft 48 may not have such a shape. May have a constant shape.
  • the wave generating plug 371 is provided with a recess 371 a that is recessed radially outward on the inner peripheral surface (that is, the connecting surface with the motor output shaft 48). Under normal conditions in which no excessive torque is acting on the wave gear reducer 21, the groove 48a and the recess 371a have the same circumferential position, and the opening of the groove 48a and the opening of the recess 371a face each other. doing.
  • the spherical member 60b Under normal conditions in which no excessive torque is acting on the wave gear reducer 21, the spherical member 60b partially protrudes from the opening of the groove portion 48a by the elastic force of the elastic member 60a, and this portion is in the recess 371a. I'm stuck. For this reason, the wave generation plug 371 rotates with the motor output shaft 48, and the torque of the motor output shaft 48 is transmitted to the wave generation plug 371.
  • the characteristics and structure of the torque limiter mechanism 60 and the groove 48a and the recess 371a such as the elastic force of the elastic member 60a, the size of the spherical member 60b, the depth of the groove 48a and the recess 371a, and the shape of the recess 371a, are as described above.
  • the spherical member 60b can be defined to be removed from the recess 371a.
  • the predetermined torque is a torque of such a magnitude that the wave gear reducer 21 is not broken, and can be predetermined by the configuration of the wave gear reducer 21.
  • the motor output shaft 48 becomes a so-called idle state, the torque transmitted to the wave gear reducer 21 is limited, and control of the actuator 100 It becomes impossible.
  • the control of the actuator 100 becomes possible when the spherical member 60b reenters the recess 371a.
  • the actuator 100 of the link mechanism for an internal combustion engine it is momentarily that an excessive torque that the torque limiter mechanism 60 acts on the wave gear reducer 21, so the actuator 100 is immediately controlled with the elimination of the excessive torque. It is desirable to be able to do it. That is, it is desirable that the time during which the actuator 100 can not be controlled is as short as possible.
  • a plurality of torque limiter mechanisms 60 are provided at equal intervals in the circumferential direction of the motor output shaft 48. Therefore, after the spherical member 60b comes out of the recess 371a, when the torque of the motor output shaft 48 becomes smaller than the above-mentioned predetermined torque and the excessive torque is eliminated, the spherical member 60b is moved to the recess 371a by the rotation of the motor output shaft 48. Then, the torque of the motor output shaft 48 is transmitted to the wave generating plug 371 to enable control of the actuator 100.
  • the time during which the control of the actuator 100 can not be performed is shortened.
  • the number of torque limiter mechanisms 60 be plural, and the larger the number, the more desirable.
  • the interval in the circumferential direction of the recess 371a becomes short, and it takes time for the spherical member 60b removed from the recess 371a to enter the recess 371a again after the excessive torque is eliminated (that is, the actuator The time when 100 becomes out of control can be shortened. Therefore, as the number of torque limiter mechanisms 60 increases, the actuator 100 can be controlled immediately after the excessive torque is eliminated.
  • the wave gear reducer 21 according to the present embodiment has high reliability because it can prevent damage due to the generation of excessive torque and shorten the time during which the actuator 100 can not be controlled after the excessive torque is eliminated.
  • FIGS. 6 and 7 A wave gear drive 21 according to a second embodiment of the present invention will be described with reference to FIGS. 6 and 7.
  • the wave gear reducer 21 according to the present embodiment has the same configuration as the wave gear reducer 21 according to the first embodiment, the configuration of the torque limiter mechanism 60 is different.
  • the configuration of the torque limiter mechanism 60 in the present embodiment will be described. Description of the same configuration as that of the wave gear reducer 21 according to the first embodiment will be omitted.
  • FIG. 6 is an axial sectional view of a wave generator 37 and a motor output shaft 48 of a wave gear reducer 21 according to a second embodiment of the present invention.
  • FIG. 7 is a radial direction sectional view of the wave generator 37 and the motor output shaft 48 at the connection position of the wave generator 37 and the motor output shaft 48.
  • the wave generation plug 371 is provided with a plurality of torque limiter mechanisms 60 in the circumferential direction.
  • the torque limiter mechanism 60 includes an elastic member 60 a such as a spring and a spherical member 60 b such as a steel ball, and is disposed at equal intervals in the circumferential direction of the wave generating plug 371.
  • the wave generation plug 371 is provided with a groove 371 b on the connection surface with the motor output shaft 48.
  • the groove 371b extends in the radial direction, and the inner side in the radial direction is open (that is, opened at the connection surface of the wave generating plug 371 with the motor output shaft 48), and the elastic member 60a is installed therein.
  • the spherical member 60b is fixed to one end on the radially inner side (that is, the opening side of the groove 371b), the other end abuts on the bottom of the groove 371b, and the elastic force mainly acts in the radial direction.
  • the motor output shaft 48 is provided with a recess 48 b that is recessed radially inward on the outer peripheral surface (that is, the connection surface with the wave generating plug 371).
  • the groove 371b and the recess 48b have the same circumferential position, and the opening of the groove 371b and the opening of the recess 48b face each other under normal conditions where no excessive torque is acting on the wave gear reducer 21. doing.
  • the groove portion 371b may be open at the bottom portion (radially outer end portion), and the plug screw 60c may be provided at the bottom portion of the groove portion 371b so as to close the opening portion.
  • the other end of the elastic member 60a abuts on the plug screw 60c provided at the bottom of the groove 371b.
  • the torque limiter mechanism 60 when the torque limiter mechanism 60 is installed in the wave generation plug 371, the torque limiter mechanism 60 is first inserted from the outer peripheral portion of the wave generation plug 371 into the groove 371b, and then the plug screw 60c is installed in the wave generation plug
  • the torque limiter mechanism 60 can be fixed with the plug screw 60c by screwing the groove 371b from the outer peripheral portion of 371.
  • the elastic force of the elastic member 60 a is large, such a structure makes it easier to install the torque limiter mechanism 60 on the wave generation plug 371.
  • the operation of the torque limiter mechanism 60 at the normal time when no excessive torque is acting on the wave gear reducer 21 and the operation of the torque limiter mechanism 60 when the excessive torque acts on the wave gear reducer 21 are substantially the same as those described in the first embodiment. It is similar. That is, in the normal state, a part of the spherical member 60b is in the recess 48b.
  • the spherical member 60b comes out from the inside of the recess 48b to cause a slip between the motor output shaft 48 and the wave generating plug 371, and the motor output shaft
  • the torque transmitted from 48 to the wave generating plug 371 is limited (a smaller torque than normal is transmitted by the friction between the spherical member 60b and the motor output shaft 48), and the wave gear reducer 21 due to the generation of an excessive torque. Can prevent the damage.
  • the wave gear reducer 21 according to the present embodiment can prevent damage due to generation of excessive torque, and the time during which the control of the actuator 100 can not be performed after elimination of the excessive torque. It has high reliability because it can be shortened.
  • a wave gear reducer 21 according to a third embodiment of the present invention will be described with reference to FIGS. 8, 9 and 10.
  • the configuration of the wave gear reducer 21 according to the present embodiment will be described below based on the configuration of the wave gear reducer 21 according to the first embodiment.
  • the configuration of the wave gear reducer 21 according to the present embodiment can also be obtained based on the configuration of the wave gear reducer 21 according to the second embodiment.
  • the actuator 100 of the link mechanism for an internal combustion engine operates constantly during the operation of the internal combustion engine, and it is momentarily that an excessive torque that the torque limiter mechanism 60 acts is generated in the wave gear reducer 21. For example, such excessive torque is generated by an impact force applied to the piston 1 instantaneously. In order to operate the actuator 100 continuously, it is required that the torque limiter mechanism 60 be returned to the state before the action as soon as possible when the excessive torque is eliminated so that the actuator 100 can be controlled immediately.
  • the control of the actuator 100 becomes impossible. Time can be shortened.
  • the configuration for returning the torque limiter mechanism 60 to the state before acting more quickly when excessive torque is eliminated, and further shortening the time when the control of the actuator 100 becomes impossible Prepare.
  • FIG. 8 is a radial direction sectional view of the wave generator 37 and the motor output shaft 48 at the connection position of the wave generator 37 and the motor output shaft 48 of the wave gear reducer 21 according to the third embodiment of the present invention.
  • the wave generation plug 371 is provided with a groove 62 extending in the circumferential direction on the inner peripheral surface (that is, the connection surface with the motor output shaft 48).
  • the groove 62 opens radially inward (that is, opens at a connection surface of the wave generating plug 371 with the motor output shaft 48).
  • the motor output shaft 48 is provided with a groove 63 extending in the circumferential direction on the outer peripheral surface (that is, the connection surface with the wave generating plug 371).
  • the groove 63 opens radially outward (i.e., opens at a connection surface of the motor output shaft 48 with the wave generating plug 371).
  • the groove 62 and the groove 63 Under normal conditions in which no excessive torque is acting on the wave gear reduction gear 21, that is, when a part of the spherical member 60b is in the recess 371a, the groove 62 and the groove 63 have the same circumferential position.
  • the opening of the groove 62 and the opening of the groove 63 face each other.
  • a space 64 is formed at the connection between the wave generating plug 371 and the motor output shaft 48 by the opening of the groove 62 and the opening of the groove 63 facing each other. Therefore, the wave gear reducer 21 normally includes the space 64 at the connection portion (sliding portion) between the wave generation plug 371 and the motor output shaft 48.
  • the space 64 is formed by the groove portion 62 and the groove portion 63, and extends in the circumferential direction similarly to the groove portions 62 and 63.
  • an elastic member 61 such as a spring is installed so that the elastic force mainly acts in the circumferential direction.
  • FIG. 9 is a view showing the elastic member 61 installed in the space 64 at a normal time when no excessive torque is acting on the wave gear reducer 21.
  • the space 64 has one end 62a of the groove 62 at one end in the circumferential direction and one end 63a of the groove 63 at the other end in the circumferential direction (one end 63a of the groove 63 is opposite to the end 62a of the groove 62 in the circumferential direction).
  • One end of the elastic member 61 abuts on one end 62 a of the groove 62, and the other end abuts on one end 63 a of the groove 63.
  • FIG. 10 is a view showing the elastic member 61 installed in the space 64 when an excessive torque acts on the wave gear reducer 21.
  • the groove 62 and the groove 63 have different circumferential positions, so that the groove 62 One end 62a and one end 63a of the groove 63 approach each other. That is, the space 64 has a reduced length in the circumferential direction.
  • the elastic member 61 is contracted when the circumferential length of the space 64 is shortened, and when the excessive torque is eliminated, the elastic force causes at least one of the wave generating plug 371 and the motor output shaft 48 to rotate, and the groove 62 and the groove 63 Make the circumferential positions of the same as each other. That is, when the excessive torque is eliminated, the relative position of the wave generation plug 371 and the motor output shaft 48 in the circumferential direction is due to the excessive torque acting on the wave gear reducer 21 by the elastic force of the elastic member 61. Automatically (forced) return to no normal position ( Figure 9). Then, the spherical member 60b reenters the recess 371a, the torque of the motor output shaft 48 is transmitted to the wave generation plug 371, and control of the actuator 100 becomes possible.
  • the number of grooves 62, grooves 63 and elastic members 61 is one or more.
  • the characteristics and structure of the groove 62, the groove 63 and the elastic member 61 such as the number of the groove 62, the groove 63 and the number of the elastic members 61, the elastic force of the elastic member 61 and the circumferential length of the groove 62 and the groove 63
  • the elastic member 61 does not shrink to the limit ( That is, the elastic member 61 can be defined so as not to cause so-called bottom sticking.
  • the actuator 100 of the link mechanism for an internal combustion engine is always operating during the operation of the internal combustion engine, so if the excessive torque generated in the wave gear reducer 21 is eliminated (in particular, if the excessive torque generated only for a moment is eliminated) There is a need to be able to control as quickly as possible.
  • the wave gear reducer 21 according to the present embodiment includes the elastic member 61, and by using the elastic force of the elastic member 61, the spherical member 60b that has slipped out of the recess 371a returns to the recess 371a again after the excessive torque is eliminated.
  • the time to entry can be significantly reduced, and after elimination of the excessive torque, the actuator 100 can be controlled more quickly.
  • the wave gear reducer 21 according to the present embodiment can greatly reduce the time during which the control of the actuator 100 can not be performed, and has high reliability.
  • the present invention is not limited to the above embodiments, and various modifications are possible.
  • the above embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to the aspect having all the described configurations.
  • wave gear Speed reducer 22: electric motor, 23: control shaft, 24: fixing flange, 27: rigid internal gear, 27a: teeth, 36: flexible external gear, 36a: teeth, 36b: flange portion, 36c: insertion hole , 37 ... wave generation , 45: motor casing, 46: coil, 47: rotor, 48: motor output shaft, 48a: groove portion, 48b: recess, 52: ball bearing, 60: torque limiter mechanism, 60a: elastic member, 60b: spherical member, 60c ... plug screw 61 elastic member 62 groove portion 62a end of groove portion 63 groove portion 63a end of groove portion 64 space 100 actuator of link mechanism for internal combustion engine 371 wave generating plug 371a ... recessed part, 371b ... groove part, 372 ... deep groove ball bearing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Power Engineering (AREA)
  • Retarders (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

L'invention porte sur un réducteur de vitesse d'engrenage à ondes comprenant: un engrenage interne rigide (27); un engrenage externe flexible (36) disposé à l'intérieur de l'engrenage interne rigide (27); un générateur d'ondes (37) disposé à l'intérieur de l'engrenage externe flexible (36); un arbre d'entrée (48) relié à une partie centrale du générateur d'ondes (37); une pluralité d'éléments élastiques (60a); et une pluralité d'éléments sphériques (60b) fixés chacun à une extrémité d'un élément élastique (60a). Le générateur d'ondes (37) et l'arbre d'entrée (48) sont pourvus, le long de la direction circonférentielle, d'une pluralité d'évidements (48a, 371a) s'ouvrant au niveau de la surface de connexion du générateur d'ondes (37) et de l'arbre d'entrée (48). Chaque élément élastique (60a) est disposé dans un évidement (48a) de l'arbre d'entrée (48), et un élément sphérique (60b) est fixé à l'extrémité de l'élément élastique qui est sur le côté ouvert de l'évidement (48a). Chaque élément sphérique (60b) présente une partie qui fait saillie dans un évidement (371a) du générateur d'ondes (37).
PCT/JP2018/022613 2017-08-29 2018-06-13 Réducteur de vitesse d'engrenage à ondes et actionneur de mécanisme de liaison pour moteur à combustion interne WO2019044116A1 (fr)

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JP2017-164172 2017-08-29
JP2017164172A JP6909102B2 (ja) 2017-08-29 2017-08-29 波動歯車減速機、及び内燃機関用リンク機構のアクチュエータ

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CN112792249B (zh) * 2021-04-02 2021-06-22 浙江易锻精密机械有限公司 一种曲柄压力机过载保护系统

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60201143A (ja) * 1984-03-24 1985-10-11 Matsushita Electric Works Ltd 動力伝達装置
JPH11118003A (ja) * 1997-10-16 1999-04-30 Harmonic Drive Syst Ind Co Ltd 波動歯車装置
JP2004116581A (ja) * 2002-09-24 2004-04-15 Honda Motor Co Ltd 軸部材への部品組付け構造
WO2010142318A1 (fr) * 2009-06-08 2010-12-16 Abb Technology Ab Dispositif permettant de mesurer un couple
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
JP2016098866A (ja) * 2014-11-19 2016-05-30 日本電産シンポ株式会社 波動歯車装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60201143A (ja) * 1984-03-24 1985-10-11 Matsushita Electric Works Ltd 動力伝達装置
JPH11118003A (ja) * 1997-10-16 1999-04-30 Harmonic Drive Syst Ind Co Ltd 波動歯車装置
JP2004116581A (ja) * 2002-09-24 2004-04-15 Honda Motor Co Ltd 軸部材への部品組付け構造
WO2010142318A1 (fr) * 2009-06-08 2010-12-16 Abb Technology Ab Dispositif permettant de mesurer un couple
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
JP2016098866A (ja) * 2014-11-19 2016-05-30 日本電産シンポ株式会社 波動歯車装置

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