WO2013008307A1 - 車両用動力伝達装置の遊星歯車装置 - Google Patents

車両用動力伝達装置の遊星歯車装置 Download PDF

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Publication number
WO2013008307A1
WO2013008307A1 PCT/JP2011/065827 JP2011065827W WO2013008307A1 WO 2013008307 A1 WO2013008307 A1 WO 2013008307A1 JP 2011065827 W JP2011065827 W JP 2011065827W WO 2013008307 A1 WO2013008307 A1 WO 2013008307A1
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WO
WIPO (PCT)
Prior art keywords
carrier
gear
planetary gear
power transmission
outer peripheral
Prior art date
Application number
PCT/JP2011/065827
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
知厚 岩佐
Original Assignee
トヨタ自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Priority to JP2013523731A priority Critical patent/JP5626467B2/ja
Priority to PCT/JP2011/065827 priority patent/WO2013008307A1/ja
Priority to CN201180072168.8A priority patent/CN103649585B/zh
Publication of WO2013008307A1 publication Critical patent/WO2013008307A1/ja
Priority to US14/268,612 priority patent/US9188195B2/en

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Classifications

    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution 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
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/101—Power split variators with one differential at each end of the CVT
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the present invention relates to a planetary gear device of a type in which a carrier is fitted and fixed to a case so as not to be relatively rotatable in a vehicle power transmission device, and in particular, due to uneven load distribution due to the inclination of the carrier.
  • the present invention relates to a technique for suppressing vibration.
  • a planetary gear device that includes a carrier that rotatably supports a pinion meshed with a sun gear and a ring gear in a state of being housed in a case.
  • a carrier that rotatably supports a pinion meshed with a sun gear and a ring gear in a state of being housed in a case.
  • Patent Documents 1 to 3 those described in Patent Documents 1 to 3.
  • the carrier since the carrier is merely fitted to the case and is not completely fixed, the reaction force from the counter drive gear that meshes with the outer peripheral teeth of the cylindrical output member.
  • the carrier that rotatably supports the pinion gear that meshes with the ring gear formed on the inner peripheral surface of the cylindrical output member is inclined, and the load distribution of the pinion gear becomes uneven due to the inclination of the carrier, causing vibration and noise. there were.
  • Patent Documents 2 and 3 a structure for fixing a carrier to a case by fastening bolts has been proposed.
  • a nut is screwed into the shaft end portion that penetrates the case of the pinion shaft that rotatably supports the pinion gear, and the axial direction is extra by the dimension of the nut head. Since the dimension is required, the axial dimension is not shortened and it is difficult to apply to a power transmission device having a severe axial dimension.
  • a nut is screwed at the shaft end of a bolt that penetrates both a hole formed on the outer peripheral side of the pinion shaft that rotatably supports the pinion gear of the carrier and the case.
  • the carrier is fixed from the axial position where the carrier is fixed by fastening the bolt, that is, from the position of the corresponding surface of the case where the carrier is pressed by fastening the bolt, or the position of the pressing surface to the friction plate sandwiched between the opposing surfaces of the case.
  • Load point that is, the length to the meshing position of the pinion gear that the carrier rotatably supports is relatively long. However, there is a problem in that it is inevitable to enlarge the bolt.
  • the present invention has been made against the background of the above circumstances.
  • the object of the present invention is to suppress the axial dimension of the type in which the carrier is fitted to the case so as not to rotate in the circumferential direction.
  • An object of the present invention is to provide a planetary gear device for a vehicle power transmission device that can suppress the inclination of the vehicle.
  • the present inventor has made various studies on the background of the above circumstances, and in a planetary gear device of a vehicle power transmission device of a type in which the carrier is fitted into the case so as not to be relatively rotatable, the carrier is fitted into the case and fixed.
  • the dimension in the axial direction between the counter gear and the meshing position between the counter gear and the outer peripheral teeth of the cylindrical output member by the reaction force generated by torque transmission, that is, the arm We found the fact that the shorter the length, the better the load distribution of the pinion gear and the less the generation of noise and vibration.
  • the present invention has been made based on such knowledge.
  • the gist of the present invention is that: (a) a carrier that rotatably supports a pinion gear meshed with a sun gear and a ring gear, and an outer periphery that is formed on the inner circumferential surface and meshes with a power transmission gear at a subsequent stage.
  • a planetary gear device for a vehicle power transmission device in which a cylindrical output member having an output tooth formed on an outer peripheral surface is provided concentrically around an axial center line, and the carrier is supported on a fixed support wall so as not to be relatively rotatable.
  • the carrier is fixed to the support wall at a fixed position within a tooth width of the outer peripheral output gear in the axial center line direction.
  • the fixing position of the carrier with the support wall is located within the tooth width of the outer peripheral output gear in the axial center line direction.
  • the reaction force from the power transmission gear that meshes with the outer peripheral output teeth of the cylindrical output member, that is, the radial load, is supported by the carrier in which the support position by the support wall is located within the tooth width of the outer peripheral output gear. Is suppressed.
  • the load distribution of the pinion gears due to the inclination of the carrier becomes uneven, and the occurrence of vibrations and noises is preferably eliminated.
  • the carrier includes a support pin that rotatably supports the pinion gear, and a carrier body in which one end portion of the support pin is fitted and is fitted to the support wall so as not to be relatively rotatable.
  • a carrier cover that is integrally connected to a connecting portion projecting from the carrier body and to which the other end portion of the support pin is fitted, and
  • the support wall includes: A support arm that protrudes in a direction parallel to the axial center line and abuts against the carrier cover; (e) the carrier cover is fixed to the support arm by a fixture; In this way, the reaction force from the power transmission gear that meshes with the outer peripheral output teeth of the cylindrical output member, that is, the radial load, is located within the tooth width of the outer peripheral output gear or the power transmission gear that meshes with the carrier.
  • the inclination of the carrier is suppressed.
  • the load distribution of the pinion gear due to the inclination of the carrier becomes uneven, and the occurrence of vibrations and noises is preferably eliminated.
  • the fixing device includes a shaft portion on which a male screw is formed and a head having a diameter larger than that of the shaft portion, and the shaft portion is screwed into the support arm portion.
  • the carrier cover is formed with a through hole through which the shaft portion of the fastening bolt penetrates, and an opening on the opposite side of the through hole from the carrier body with a larger diameter than the through hole. And a counterbore hole for burying the head of the fastening bolt.
  • the fastening bolt for fastening the carrier cover constituting a part of the carrier to the support arm portion of the support wall is used, and the head of the fastening bolt is a seat formed on the carrier body. Since it is located in the counterbore, there is an advantage that the axial dimension does not increase.
  • a plurality of engaging teeth respectively formed in a flange shape are formed on the outer peripheral portion of the carrier main body so as to protrude to the outer peripheral side at a symmetric portion with respect to the axial center line.
  • the support wall has a shape similar to the outer peripheral shape of the carrier body having the plurality of engagement teeth, and is formed with a fitting hole into which the carrier body is fitted so as not to be relatively rotatable. It is characterized by that. In this way, a plurality of engaging teeth are formed on the outer peripheral portion of the carrier main body that is fitted into the fitting hole so as not to rotate relative to each other.
  • a plurality of engaging teeth are formed on the outer peripheral portion of the carrier body so as to be eccentric to one side with respect to the rotation center line.
  • the carrier moves so as to rotate about the contact portion with the support wall of the transaxle case by the resultant force of the reaction force received by each engagement tooth.
  • the contact portion between the engaging tooth and the engaging groove formed in the outer peripheral portion of the fitting hole into which the engaging tooth is fitted wears to change the circumferential position between the carrier and the support wall of the transaxle case, so that the pinion In some cases, the tooth contact with the ring gear and sun gear deteriorates and vibration and noise occur.
  • the present invention since the plurality of engaging teeth formed at the symmetric parts with respect to the rotation center line are formed, the resultant force of the reaction force received by each engaging tooth cancels out. As a result, the above inconvenience is prevented.
  • the carrier body includes a boss portion protruding to the opposite side of the carrier cover, and an inner peripheral surface of the boss portion is provided on an outer peripheral surface of the rotating shaft on which the sun gear is mounted.
  • a third bearing for fitting and supporting it rotatably is fitted.
  • the third shaft bearing for supporting the rotating shaft for supporting the sun gear for example, the rotor shaft for supporting the rotor of the electric motor, is fitted to the inner peripheral surface of the carrier body. Is further shortened.
  • the outer peripheral surface of the carrier cover is fitted to a portion of the inner peripheral surface of the cylindrical output member corresponding to the outer peripheral output teeth and is rotatably supported.
  • the first bearing is fitted. If it does in this way, the 1st bearing for fitting in the site
  • reaction force from the power transmission gear that meshes with the outer peripheral output teeth of the cylindrical output member that is, the radial load
  • the reaction force from the power transmission gear that meshes with the outer peripheral output teeth of the cylindrical output member is positioned within the tooth width of the outer peripheral output gear or the power transmission gear that meshes with the outer peripheral output gear.
  • FIG. 1 is a skeleton diagram illustrating a configuration of a vehicle power transmission device having a planetary gear device according to an embodiment of the present invention. It is an II-II arrow line view of FIG. 1, Comprising: It is a figure which notches and shows the 2nd carrier with which the support wall part of the transaxle was mounted
  • FIG. 1 is a skeleton diagram illustrating a configuration of a vehicle power transmission device 10 according to an embodiment of the present invention.
  • a vehicle power transmission device 10 is provided between an engine 12 and drive wheels 14 in, for example, an FF (front engine / front drive) type hybrid vehicle.
  • the vehicle power transmission device 10 is disposed in a transaxle case 16, an input shaft 20 connected to an output shaft (crankshaft) of the engine 12 via a damper device 18, and concentric with the input shaft 20.
  • a first motor generator MG1, a power distribution planetary gear device 22, a reduction planetary gear device 24, and a second motor generator MG2 are provided in this order from the damper device 18 side.
  • the oil pump OP is disposed on a common axis center line C.
  • the transaxle case 16 corresponds to the case in the present invention, and is die-cast from, for example, an aluminum alloy.
  • the reduction planetary gear unit 24 corresponds to the planetary gear unit of the present invention.
  • the power distribution planetary gear unit 22 includes a first sun gear S1 mounted by sputter line fitting on the shaft end of the first rotor support shaft RS1 of the first motor generator MG1, a power distribution planetary gear unit 22, and a reduction planetary gear.
  • the power distribution planetary gear unit 22 functions as a power distribution mechanism that mechanically distributes the power from the engine 12 to the first motor generator MG1 and the cylindrical output member 26. It is provided adjacent to the damper device 18 side of the reduction planetary gear device 24 on the inner peripheral side.
  • the power of the engine 12 distributed to the first motor generator MG1 by the power distribution planetary gear unit 22 is used to drive the first motor generator MG1 as a generator.
  • the power of the engine 12 distributed to the cylindrical output member 26 by the power distribution planetary gear unit 22 is used to rotationally drive the drive wheels 14.
  • the first ring gear R1 of the power distribution planetary gear device 22 and the second ring gear R2 of the reduction planetary gear device 24 in the axial center line C direction A first drive gear 28 that functions as an outer peripheral output tooth is provided integrally.
  • the first motor generator MG1 is caused to function as a generator by being driven by the engine 12 through the planetary gear unit 22 for power distribution, and charges the electric energy generated by regeneration to a power storage device such as a battery.
  • the first motor generator MG1 is caused to function as an electric motor (engine starter) by driving the engine 12 via the power distribution planetary gear unit 22 at the time of engine startup, for example.
  • the differential state of the power distribution planetary gear unit 22 is continuously changed by controlling the regenerative state of the first motor generator MG1. Therefore, the power distribution planetary gear unit 22 and the first motor generator MG1 are cylindrical by controlling the operating state of the first motor generator MG1 and continuously changing the differential state of the power distribution planetary gear unit 22.
  • An electric transmission unit that changes the rotation speed of the output member 26 steplessly is configured.
  • the first drive gear 28 formed on the cylindrical output member 26 functions as an output gear of the electric transmission unit.
  • the reduction planetary gear unit 24 includes a second sun gear S2 mounted by spline fitting on the shaft end of the second rotor support shaft RS2 of the second motor generator MG2, and the reduction planetary gear unit 24 side of the cylindrical output member 26.
  • a plurality of second ring gears R2 that are integrally provided at the end of the second ring gear, and a plurality of second gears meshed with the second sun gear S2 and the second ring gear R2 on the outer peripheral side of the second sun gear S2 and the inner peripheral side of the second ring gear R2, respectively ( (Four in this embodiment) second pinions P2, and a second carrier CA2 that is non-rotatably fitted to the first wall 16a of the transaxle case 16 and rotatably supports the plurality of second pinions P2.
  • the reduction planetary gear unit 24 functions as a reduction gear that reduces the rotation of the second motor generator MG2 and transmits it to the second ring gear R2.
  • the second sun gear S2, the second ring gear R2, the second pinion P2, and the second carrier CA2 correspond to the sun gear, ring gear, pinion gear, and carrier in the present invention.
  • the second motor generator MG2 is caused to function as an electric motor that rotates the drive wheels 14 alone or together with the engine 12. Further, the second motor generator MG2 is caused to function as a generator by being driven by the drive wheels 14 when the vehicle is decelerated, for example, and charges electric energy generated by the power generation to a power storage device such as a battery. .
  • the cylindrical output member 26 is a cylindrical member disposed on the outer peripheral side of the power distribution planetary gear device 22 and the reduction planetary gear device 24 provided adjacent to each other on the axial center line C.
  • the planetary gear unit for reduction 24 and the transaxle are arranged via a first bearing 30 and a second bearing 32 which are respectively arranged on the inner side of the cylindrical output member 26 in the axial center line C direction and on the outer side of the end portion on the engine 12 side.
  • the case 16 is supported so as to be rotatable around the axial center line C direction.
  • the first bearing 30 is fitted on the outer peripheral side of the second carrier CA2 of the reduction planetary gear unit 24 fixed to the first wall 16a.
  • the second bearing 32 is fitted to a second wall portion 16 b extending from the inner wall surface of the transaxle case 16 to the inner circumferential side on the outer circumferential side of the power distribution planetary gear device 22.
  • a first ring gear R1 and a second ring gear R2 are integrally provided on the inner peripheral side of both ends of the cylindrical output member 26 in the axial center line C direction, and the axial center line of the cylindrical output member 26 is also provided.
  • a first drive gear 28 and a parking lock gear 34 are integrally provided on the outer peripheral side of the intermediate portion in the C direction.
  • the cylindrical output member 26 is a composite gear member in which a first ring gear R1, a second ring gear R2, a first drive gear 28, and a parking lock gear 34 are integrally provided.
  • the vehicle power transmission device 10 further allows a reduction gear device 36 connected to the cylindrical output member 26 and the power transmitted from the reduction gear device 36 to the pair of left and right axles 38 to allow a rotational difference therebetween. And a differential gear device 40 that distributes the same.
  • the reduction gear device 36 transmits the output from the cylindrical output member 26 to the differential gear device 40 while reducing the output, and is provided integrally with a counter shaft 42 provided in parallel with the input shaft 20.
  • the second carrier CA2 has a fitting hole, which will be described later, formed at the end on the second motor generator MG2 side so as to penetrate the first wall portion (support wall) 16a of the transaxle case 16.
  • the end portion on the first motor generator MG1 side is fitted into the non-rotatable state in 16c, and a support projecting in a direction parallel to the axial center line C direction from the first wall portion (support wall) 16a.
  • the cylindrical output member 26 is rotatably supported via a third bearing 52 while being fixed and supported at the tip of the arm portion 16d.
  • FIG. 2 is a view taken along the line II-II in FIG.
  • FIG. 1 for explaining the mounting state of the second carrier CA2, in which the first bearing 30, the second sun gear S2, the second rotor support shaft RS2, and the pump drive shaft 25 are removed. Only the carrier CA2, the second pinion P2, and a part of the first wall 16a of the transaxle 16 are shown.
  • 3 is a diagram showing a cross-section taken along the line III-III in FIG.
  • the support structure of the second carrier CA2 will be described in detail with reference to FIG. 2 and FIG.
  • the second carrier CA2 includes a carrier body 56 and a carrier cover 58 that respectively support both ends of a carrier pin 54 that rotatably supports the second pinion P2.
  • the carrier body 56 and the carrier cover 58 are welded, Alternatively, they are formed integrally with each other by molding using a sintered alloy.
  • the carrier body 56 protrudes toward the second motor generator MG2 and has a cylindrical boss portion 56a in which a third bearing 52 that supports one end portion of the second rotor shaft RS2 is fitted on the inner peripheral side, and the boss portion.
  • the end of the second motor generator MG2 side of the carrier pin 54 that extends radially outward from the end of the second pinion P2 side of 56a and is arranged in the circumferential direction (four in this embodiment).
  • Each of the disc-shaped plate portions 56b to be supported, and seven sprite teeth formed so as to protrude radially outward from the outer peripheral portion of the plate portion 56b, are positioned symmetrically with respect to the axial center line C direction.
  • a pair of notches 56d formed so as to be positioned between the two groups of engagement teeth 56c in the plate portion 56b, and a pair of notches 56d in the circumferential direction. while It is projected from the plate portion 56b so as to be positioned and a connecting portion 56e to reach the carrier cover 58.
  • the carrier cover 58 is integrally fixed to the front end of the connecting portion protruding from the plate portion 56b of the carrier body 56, and supports the end portions of the carrier pins 54 on the first motor generator MG1 side.
  • a counterbore 58d of a predetermined depth formed in the portion is integrally fixed to the front end of the connecting portion protruding from the plate portion 56b of the carrier body 56, and supports the end portions of the carrier pins 54 on the first motor generator MG1 side.
  • An engagement groove 16e is formed in the first wall portion rod (support wall) rod 16a of the transaxle case 16 so as to protrude from the outer peripheral edge of the fitting hole 16c formed therethrough.
  • the engaging grooves 16e are externally similar to the engaging teeth 56c so that seven groups of two engaging teeth 56c formed on the outer periphery of the plate portion 56b of the carrier body 56 can be fitted. It has a shape and a depth similar to the thickness dimension of the engaging teeth 56c.
  • the two engaging teeth 56c of the seven groups formed on the outer periphery of the plate portion 56b of the carrier body 56 are fitted into the engaging grooves 16e, so that the second carrier CA2 cannot be rotated relative to the second carrier CA2. It is adapted to be fitted to one wall portion ridge (support wall) ridge 16a and positioned concentrically with the axial center line C direction.
  • a support arm portion 16d that protrudes from the first wall portion rod (support wall) rod 16a and projects in a direction parallel to the direction of the axial center line C is a notch portion 56d formed in the plate portion 56b of the carrier body 56. And reaches the carrier cover 58.
  • a female screw hole 62 is formed in the front end surface 60 of the support arm portion 16d that contacts the carrier cover 58, and a fastening hole 58c formed in the plate portion 58b of the carrier cover 58 is passed through the female screw hole 62.
  • the second carrier CA2 is supported by the fastening bolt 64 being screwed together.
  • the second carrier CA2 is supported on the back surface of the carrier cover 58 that is in contact with the front end surface 60 of the support arm portion 16d by the first wall portion rod (support wall) rod 16a of the transaxle case 16 whose position is fixed.
  • the fastening bolt 64 includes a shaft portion 64a on which a male screw is formed, and a head portion 64b having a diameter larger than that of the shaft portion 64a and shorter than the depth of the counterbore hole 58d.
  • the cylindrical output member 26 includes a first bearing 30 fitted on the outer periphery of the carrier cover 58 of the second carrier CA2 whose position is fixed, and a second bearing 32 fitted on the second wall portion 16b of the transaxle case 16.
  • the first drive gear 28 that functions as an outer peripheral output gear is provided outside the first bearing 30.
  • the support position SP of the second carrier CA ⁇ b> 2 which is the back surface of the carrier cover 58, and the position BP of the first bearing 30 in the axial center line C direction It is located within the tooth width W.
  • the first drive gear 28 and the first driven gear 44 are positioned within the meshing width. Thereby, the arm length from the support position SP of the second carrier CA2, that is, the fixed position, to the first drive gear 28 that receives the radial load from the first driven gear 44 is shortened as much as possible. *
  • the second carrier in which the reaction force from the driven gear (power transmission gear) 44, that is, the radial load, is located within the tooth width W of the first drive gear 28 at the support position SP by the first wall portion rod (support wall) rod 16a. Since it is supported by CA2, the inclination of the second carrier CA2 is suppressed. In addition, the load distribution of the second pinion (pinion gear) P2 due to the inclination of the second carrier CA2 becomes uneven, and vibration and noise are preferably eliminated.
  • the second carrier CA2 is fitted with a carrier pin (support pin) 54 that rotatably supports the second pinion (pinion gear) P2 and one end of the carrier pin 54.
  • a carrier body 56 that is fitted to one wall portion (support wall) 16a so as not to rotate relatively, and a connecting portion 56e that protrudes from the carrier body 56 are integrally connected, and the other end portion of the carrier pin 54 is fitted.
  • the first wall portion (support wall) 16a includes a support arm portion 16d that protrudes in a direction parallel to the axial center line C direction and abuts on the carrier cover 58.
  • the carrier cover 58 is fixed to the support arm portion 16d by a fixing tool (fastening bolt 64).
  • the reaction force that is, the radial load from the first driven gear (power transmission gear) 44 that meshes with the first drive gear (outer peripheral output gear) 28 of the cylindrical output member 26 is within the tooth width W of the first drive gear 28.
  • the inclination of the second carrier CA2 is suppressed.
  • the load distribution of the second pinion (pinion gear) P2 due to the inclination of the second carrier CA2 becomes uneven, and vibration and noise are preferably eliminated.
  • the fixture includes a shaft portion 64a on which a male screw is formed and a head portion 64b having a diameter larger than that of the shaft portion 64a, and the shaft portion 64a is screwed onto the support arm portion 16d.
  • the carrier cover 58 includes a fastening hole 58c through which the shaft portion 64a of the fastening bolt 64 passes, and a fastening hole 58c at an opening of the fastening hole 58c opposite to the carrier body 56. And a counterbore hole 58d that is formed to have a larger diameter than that of the head 64b of the fastening bolt 64.
  • a fastening bolt 64 for screwing the tip end surface 60 of the support arm portion 16d protruding from the first wall portion rod (support wall) rod 16a and fastening the carrier cover 58 is used. Since the head 64b is positioned in a counterbore 58d formed in the carrier cover 58, there is an advantage that the axial dimension does not increase.
  • the outer peripheral portion of the carrier body 56 is provided with a plurality of engaging teeth 56c each formed in a flange shape so as to protrude to the outer peripheral side at a symmetrical portion with respect to the axial center line C direction.
  • the formed first wall portion rod (support wall) rod 16a has a shape similar to the outer peripheral shape of the plate portion 56b of the carrier body 56 having the plurality of engaging teeth 56c, and the carrier body 56 is relatively rotated.
  • An engaging groove 16e that is impossible to fit is formed on the outer periphery of the fitting hole 16c.
  • a plurality of engagements are formed on the outer peripheral portion of the carrier main body 56, which are fitted in the fitting holes 16c and the engaging grooves 16e so as not to rotate relative to each other, in symmetrical portions with respect to the axial center line C direction. Since the teeth 56c are formed, the resultant force of the reaction force received by each engagement tooth 56c is canceled and becomes small, so that the vibration of the carrier body 56 is further suppressed.
  • the carrier body 56 includes the boss portion 56a protruding to the opposite side of the carrier cover 58, and the second sun gear S2 is mounted on the inner peripheral surface of the boss portion 56a.
  • a third bearing 52 for fitting to the outer peripheral surface of the rotor support shaft (rotary shaft) RS2 and rotatably supporting it is fitted. For this reason, since the third bearing 52 that supports the second rotor support shaft (rotary shaft) RS2 to which the second sun gear S2 is mounted is fitted on the inner peripheral surface of the carrier body 56, the planetary gear unit for reduction ( The axial dimension of the planetary gear unit 24 is further shortened.
  • the carrier cover 58 is fitted on the outer peripheral surface of the cylindrical output member 26 corresponding to the first drive gear (outer output gear) 28 of the inner peripheral surface.
  • a first bearing 30 for rotatably supporting is fitted.
  • the first bearing 30 for fitting to the portion corresponding to the first drive gear (outer peripheral output gear) 28 on the inner peripheral surface of the cylindrical output member 26 and rotatably supporting it is the carrier cover. Since it is fitted to the outer peripheral surface of 58, the axial dimension of the planetary gear unit for reduction (planetary gear unit) 24 is further shortened.
  • a reaction force, that is, a radial load, from the first driven gear (power transmission gear) 44 that meshes with the first drive gear (outer peripheral output gear) 28 of the cylindrical output member 26 is within the tooth width W of the first drive gear 28.
  • the second carrier CA2 of the above-described reduction planetary gear unit 24 includes four second pinions P2 rotatably supported by four carrier pins 54, and the first wall by the two fastening bolts 64.
  • the carrier body 56 is supported by the portion (support wall) 16a and is connected to each other via the two connecting portions 56e.
  • the number of second pinions P2, the number of fastening bolts 64, and the number of connecting portions 56e are as follows. It is one example, and the number or number of them can be changed.
  • the number of the engaging teeth 56c and the engaging grooves 16e into which the engaging teeth 56c are fitted is formed at seven portions symmetrical with respect to the axial center line C direction.
  • it may be any of about 2 to 8.
  • the cylindrical output member 26 is fitted between the outer peripheral surface of the carrier cover 38 and the inner peripheral surface of the cylindrical output member 26 at an intermediate position in the axial center line C direction.
  • the bearing 30 and the second bearing 32 fitted on the outer peripheral surface on the power distribution planetary gear unit 22 side are rotatably supported, the first bearing 30 is a reduction planet of the cylindrical output member 26. You may provide between the outer peripheral surface by the side of the gear apparatus 24, and the 1st wall part 16a.
  • Vehicle power transmission device 16 Transaxle case (case) 16a: 1st wall part (support wall) 16c: fitting hole 16d: support arm portion 16e: engagement groove 24: Planetary gear device for reduction (planetary gear device) 26: cylindrical output member 28: first drive gear (outer periphery output teeth) 30: First bearing 44: First driven gear (power transmission gear) 52: Third bearing 54: Carrier pin (support pin) 56: Carrier body 56a: Boss portion 56b: Plate portion 56c: Engagement tooth 56e: Connection portion 58: Carrier cover 58c: Fastening hole 58d: Counterbore hole 60: Tip face 64: Fastening bolt (fixing tool) 64a: shaft portion 64b: head C: shaft center line CA2: second carrier (carrier) MG1: first motor generator RS1: first rotor shaft MG2: second motor generator RS2: second rotor shaft P2: second pinion (pinion gear) R2: Second ring gear (ring gear) S2: Second sun gear (sun gear (s

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
PCT/JP2011/065827 2011-07-11 2011-07-11 車両用動力伝達装置の遊星歯車装置 WO2013008307A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2013523731A JP5626467B2 (ja) 2011-07-11 2011-07-11 車両用動力伝達装置の遊星歯車装置
PCT/JP2011/065827 WO2013008307A1 (ja) 2011-07-11 2011-07-11 車両用動力伝達装置の遊星歯車装置
CN201180072168.8A CN103649585B (zh) 2011-07-11 2011-07-11 车辆用动力传递装置的行星齿轮装置
US14/268,612 US9188195B2 (en) 2011-07-11 2014-05-02 Planetary gear device for vehicle power transmission device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/065827 WO2013008307A1 (ja) 2011-07-11 2011-07-11 車両用動力伝達装置の遊星歯車装置

Related Child Applications (2)

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US14131966 A-371-Of-International 2011-07-11
US14/268,612 Continuation US9188195B2 (en) 2011-07-11 2014-05-02 Planetary gear device for vehicle power transmission device

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WO2013008307A1 true WO2013008307A1 (ja) 2013-01-17

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Publication number Priority date Publication date Assignee Title
JP6286460B2 (ja) * 2016-02-18 2018-02-28 本田技研工業株式会社 遊星歯車機構及び変速機
DE102018218976A1 (de) * 2018-11-07 2020-05-07 Zf Friedrichshafen Ag Schmierstofftransferring mit mehreren Kammern

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01122542U (zh) * 1988-02-16 1989-08-21
JP2004116737A (ja) * 2002-09-27 2004-04-15 Toyota Motor Corp 遊星歯車装置およびパワートレーン

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3893960B2 (ja) * 2001-01-12 2007-03-14 トヨタ自動車株式会社 動力伝達装置
DE102004006723A1 (de) * 2004-02-11 2005-09-01 Zf Friedrichshafen Ag Planetenradgetriebe
JP4293263B2 (ja) * 2007-04-19 2009-07-08 トヨタ自動車株式会社 車両用動力伝達装置
JP4656118B2 (ja) * 2007-10-05 2011-03-23 トヨタ自動車株式会社 変速機および動力伝達装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01122542U (zh) * 1988-02-16 1989-08-21
JP2004116737A (ja) * 2002-09-27 2004-04-15 Toyota Motor Corp 遊星歯車装置およびパワートレーン

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JPWO2013008307A1 (ja) 2015-02-23
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CN103649585B (zh) 2016-05-11

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