JP5626467B2 - Planetary gear device for vehicle power transmission device - Google Patents

Planetary gear device for vehicle power transmission device Download PDF

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JP5626467B2
JP5626467B2 JP2013523731A JP2013523731A JP5626467B2 JP 5626467 B2 JP5626467 B2 JP 5626467B2 JP 2013523731 A JP2013523731 A JP 2013523731A JP 2013523731 A JP2013523731 A JP 2013523731A JP 5626467 B2 JP5626467 B2 JP 5626467B2
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carrier
gear
outer peripheral
planetary gear
power transmission
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JPWO2013008307A1 (en
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知厚 岩佐
知厚 岩佐
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Toyota Motor Corp
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    • 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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Description

本発明は、車両用動力伝達装置において、キャリヤが相対回転不能にケースに嵌めつけられて固定される形式の遊星歯車装置に係り、特に、そのキャリヤの傾きによる荷重分布の不均等やそれに起因する振動を抑制するための技術に関するものである。   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.

車両用動力伝達装置において、サンギヤおよびリングギヤにそれぞれ噛み合わされたピニオンを回転可能に支持するキャリヤをケース内に収容した状態で備える遊星歯車装置が知られている。例えば、特許文献１乃至３に記載されたものがそれである。上記特許文献１の遊星歯車装置においては、キャリヤがケースに対して嵌め付けられているに過ぎず完全に固定されていないため、円筒状出力部材の外周歯と噛み合うカウンタドライブギヤからの反力によって、円筒状出力部材の内周面に形成されたリングギヤと噛み合うピニオンギヤを回転可能に支持するキャリヤが傾き、そのキャリヤの傾きによってピニオンギヤの荷重分布が不均等となり、振動や騒音が発生するという欠点があった。   2. Description of the Related Art In a vehicle power transmission device, a planetary gear device is known that includes a carrier that rotatably supports a pinion meshed with a sun gear and a ring gear in a state of being accommodated in a case. For example, those described in Patent Documents 1 to 3. In the planetary gear device of Patent Document 1, 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.

特開２００２−２７４２０１号公報JP 2002-274201 A 特開２００７−２６３３５４号公報JP 2007-263354 A 特開２００９−０９２１２３号公報JP 2009-092123 A

これに対して、特許文献２および３に示されているように、キャリヤをボルトの締結によってケースに固定する構造が提案されている。しかし、特許文献２に記載されたキャリヤ固定構造では、ピニオンギヤを回転可能に支持するピニオンシャフトのケースを貫通した軸端部にナットが螺合されており、ナットヘッドの寸法分だけ余分に軸方向寸法を必要とするので、軸方向寸法の短縮にならず、軸方向寸法の厳しい動力伝達装置には適用が困難である。また、伝達トルクをボルトの座面の摩擦によってピニオンギヤに生じる反力で支持する構造となっているため、入力トルク変動が常時発生する動力伝達装置においては、座面摩擦の低下が発生してナットの緩みが発生しやすいという、問題があった。   On the other hand, as shown in Patent Documents 2 and 3, there has been proposed a structure in which a carrier is fixed to a case by fastening bolts. However, in the carrier fixing structure described in Patent Document 2, 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. In addition, since the transmission torque is supported by the reaction force generated in the pinion gear by the friction of the bolt seating surface, in a power transmission device in which input torque fluctuations always occur, the seating surface friction decreases and the nut There was a problem that loosening of the surface was likely to occur.

また、特許文献３に記載されたキャリヤ固定構造では、キャリヤのうちピニオンギヤを回転可能に支持するピニオンシャフトの外周側に形成された穴とケースとを共に貫通したボルトの軸端部にナットが螺合されており、ナットヘッドの寸法分だけ余分に軸方向寸法を必要とするので、軸方向寸法の短縮にならず、軸方向寸法の厳しい動力伝達装置には適用が困難である。また、そのボルトの締結によってキャリヤが固定される軸方向位置、すなわちキャリヤがボルトの締結により押圧されるケースの対応面、或いはケースの対抗面に挟まれる摩擦板への押圧面の位置から、キャリヤの荷重点すなわちキャリヤが回転可能に支持するピニオンギヤの噛み合い位置までの長さが、比較的長い為、ボルトに負荷される荷重が大きく、ラジアル荷重が常時入力される動力伝達装置には、全周においてボルトの締結が必要となって、大型化が避けられないなどの問題があった。   Further, in the carrier fixing structure described in Patent Document 3, 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. In addition, since an extra axial dimension is required by the size of the nut head, the axial dimension is not shortened and is difficult to apply to a power transmission device having a severe axial dimension. Further, 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.

本発明は、以上の事情を背景として為されたものであり、その目的とするところは、キャリヤが周方向の回転不能にケースに嵌めつけられる形式の軸方向寸法を抑制できるものにおいて、そのキャリヤの傾きを抑制することができる車両用動力伝達装置の遊星歯車装置を提供することにある。   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.

本発明者は、以上の事情を背景として種々検討を重ねるうち、キャリヤが相対回転不能にケースに嵌めつけられる形式の車両用動力伝達装置の遊星歯車装置において、キャリヤがケースに嵌めつけられて固定されることでそれにより支持される支持位置と、トルク伝達により発生する反力によってカウンタギヤからそのカウンタギヤと円筒状出力部材の外周歯との噛み合い位置との間の軸心方向の寸法すなわちアーム長を短くするほど、ピニオンギヤの荷重分布が改善されて騒音や振動の発生が抑制されるという事実を見いだした。本発明は斯かる知見に基づいて為されたものである。   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.

すなわち、本発明の要旨とするところは、（ａ）サンギヤおよびリングギヤにそれぞれ噛み合わされたピニオンギヤを回転可能に支持するキャリヤと、該リングギヤが内周面に形成され且つ後段の動力伝達歯車と噛み合う外周出力歯が外周面に形成された円筒状出力部材とを軸中心線まわりに同心に備え、位置固定の支持壁に前記キャリヤが相対回転不能に支持された車両用動力伝達装置の遊星歯車装置であって、（ｂ）前記キャリヤの前記支持壁との固定位置が、軸中心線方向において前記外周出力歯車の歯幅内に位置しており、（ｃ）前記キャリヤは、前記ピニオンギヤを回転可能に支持する支持ピンと、該支持ピンの一端部が嵌め着けられ、前記支持壁に相対回転不能に嵌合されたキャリヤ本体と、該キャリヤ本体から突設された連結部に一体的に連結され、前記支持ピンの他端部が嵌め着けられたキャリヤカバーとを備えたものであり、（ｄ）前記支持壁は、前記軸中心線に平行な方向に突き出して前記キャリヤカバーに当接する支持アーム部を備え、（ｅ）該キャリヤカバーは、固定具により該支持アーム部に固定されていることを特徴とする。   That is, the gist of the present invention is as follows: (a) a carrier that rotatably supports a pinion gear meshed with a sun gear and a ring gear, and an outer circumference that is formed on the inner circumferential surface and meshes with a power transmission gear at the 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. And (b) a position where the carrier is fixed to the support wall is located within a tooth width of the outer peripheral output gear in the axial center line direction, and (c) the carrier is capable of rotating the pinion gear. A support pin to be supported, a carrier body fitted with one end of the support pin and fitted to the support wall so as not to rotate relative thereto, and a connection projecting from the carrier body And (d) the support wall protrudes in a direction parallel to the axial center line, and is connected to the carrier pin. And (e) the carrier cover is fixed to the support arm portion by a fixing tool.

本発明の車両用動力伝達装置の遊星歯車装置によれば、前記キャリヤの前記支持壁との固定位置が、軸中心線方向において前記外周出力歯車の歯幅内に位置していることから、円筒状出力部材の外周出力歯と噛み合う動力伝達歯車からの反力すなわちラジアル荷重が、その外周出力歯車の歯幅内に支持壁による支持位置が位置しているキャリヤにより支持されるので、キャリヤの傾きが抑制される。また、そのキャリヤの傾きに起因してピニオンギヤのピニオンギヤの荷重分布が不均等となり、振動や騒音が発生することが、好適に解消される。さらに、円筒状出力部材の外周出力歯と噛み合う動力伝達歯車からの反力すなわちラジアル荷重が、その外周出力歯車又はそれと噛み合う前記動力伝達歯車の歯幅内に位置している、キャリヤカバーに固定具により固定された支持壁の支持アーム部により支持されるので、キャリヤの傾きが抑制される。また、そのキャリヤの傾きに起因してピニオンギヤの荷重分布が不均等となり、振動や騒音が発生することが、好適に解消される。   According to the planetary gear device of the vehicle power transmission device of the present invention, 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. In addition, 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. Further, 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 positioned within the tooth width of the outer peripheral output gear or the power transmission gear that meshes with the outer peripheral output gear. Is supported by the support arm portion of the support wall fixed by, so that the inclination of the carrier is suppressed. In addition, 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.

また、好適には、(ｆ)前記固定具は、雄ねじが形成された軸部と該軸部よりも大径の頭部とを備えて該軸部が前記支持アーム部に螺合される締結ボルトであり、（ｇ）前記キャリヤカバーは、該締結ボルトの軸部を貫通させる貫通穴と、該貫通穴の前記キャリヤ本体とは反対側の開口部に該貫通穴よりも大径に形成されて前記締結ボルトの頭部を埋没させる座ぐり穴とを備えたものである。このようにすれば、キャリヤの一部を構成するキャリヤカバーを支持壁の支持アーム部に締結するための締結ボルトが用いられているが、その締結ボルトの頭部はキャリヤ本体に形成された座ぐり穴内に位置しているので、軸方向寸法が増大しない利点がある。 Preferably, (f) 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. And (g) 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. In this case, 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.

また、好適には、（ｈ）前記キャリヤ本体の外周部には、前記軸中心線に対して対称部位に外周側へ突き出すようにフランジ状にそれぞれ形成された複数個の係合歯が形成され、（ｉ）前記支持壁には、該複数個の係合歯を有するキャリヤ本体の外周形状と同様の形状を有し、該キャリヤ本体を相対回転不能に嵌め入れる嵌合穴が形成されていることを特徴とする。このようにすれば、嵌合穴に相対回転不能に嵌め入れられるキャリヤ本体の外周部には、軸中心線に対して対象部位にそれぞれ形成された複数個の係合歯が形成されている。従来のキャリヤが相対回転不能にケースに嵌めつけられる形式の遊星歯車装置では、キャリヤ本体の外周部には、回転中心線に対して片側に偏心して複数個の係合歯が形成されているため、各係合歯が受ける反力の合力により、キャリヤがトランスアクスルケースの支持壁との接触部位を支点として回動するように動く。また、上記合力の大きさがリングギヤやサンギヤの偏心の影響等で脈動する場合には、キャリヤが、トランスアクスルケースの支持壁との接触部位を支点として各係合歯とそれらを嵌め入れるために嵌合穴の外周部に形成された係合溝との接触部分が相互に擦られるように振動し、その振動においては、上記支点から最も離れている係合歯の振れ量が最大となり、その係合歯とそれを嵌め入れる嵌合穴の外周部に形成された係合溝との接触部分が摩耗してキャリヤとトランスアクスルケースの支持壁との周方向位置が変化することによって、ピニオンとリングギヤおよびサンギヤとの歯当たりが悪化して振動や騒音が発生する場合があった。これに対して、本発明によれば、回転中心線に対して対称部位にそれぞれ形成された複数個の係合歯が形成されていることから、各係合歯が受ける反力の合力は相殺されて小さなものとなるので、上記の不都合が防止される。 Preferably, (h) 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. (I) 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. In a planetary gear device of the type in which a conventional carrier is fitted to a case so as not to be relatively rotatable, 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. Also, when the magnitude of the resultant force pulsates due to the influence of the eccentricity of the ring gear or sun gear, etc., in order for the carrier to fit the engaging teeth and them with the contact portion with the support wall of the transaxle case as a fulcrum The contact portion with the engagement groove formed on the outer peripheral portion of the fitting hole vibrates so that they rub against each other, and in the vibration, the amount of deflection of the engagement tooth that is farthest from the fulcrum is maximized. 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. On the other hand, according to 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.

また、好適には、(ｊ)前記キャリヤ本体は、前記キャリヤカバーとは反対側へ突き出すボス部を備え、該ボス部の内周面には、前記サンギヤが装着される回転軸の外周面に嵌合してそれを回転可能に支持するための第３軸受が、嵌め着けられていることを特徴とする。このようにすれば、サンギヤが装着される回転軸たとえば電動機のロータを支持するロータ軸を支持する第３軸受がキャリヤ本体の内周面に嵌め着けられているので、遊星歯車装置の軸方向寸法が一層短縮される。 Preferably, (j) 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. According to this configuration, 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.

また、好適には、(ｋ)前記キャリヤカバーの外周面には、前記円筒状出力部材の内周面のうち前記外周出力歯に対応する部位に嵌合してそれを回転可能に支持するための第１軸受が嵌め着けられている。このようにすれば、円筒状出力部材の内周面のうち前記外周出力歯に対応する部位に嵌合してそれを回転可能に支持するための第１軸受がキャリヤカバーの外周面に嵌め着けられているので、遊星歯車装置の軸方向寸法が一層短縮される。また、円筒状出力部材の外周出力歯と噛み合う動力伝達歯車からの反力すなわちラジアル荷重が、その外周出力歯車又はそれと噛み合う前記動力伝達歯車の歯幅内に位置している、キャリヤが固定される支持壁によりその軸受けを介して直接的に支持される利点がある。 Preferably, (k) 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 | part corresponding to the said outer periphery output tooth among the inner peripheral surfaces of a cylindrical output member and rotatably supporting it will fit on the outer peripheral surface of a carrier cover. Therefore, the axial dimension of the planetary gear device is further shortened. In addition, 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 positioned within the tooth width of the outer peripheral output gear or the power transmission gear that meshes with the outer peripheral output gear. There is an advantage that it is directly supported by the support wall via the bearing.

本発明の一実施例の遊星歯車装置を有する車両用動力伝達装置の構成を説明する骨子図である。BRIEF DESCRIPTION OF THE DRAWINGS 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. 図１のII-II矢視図であって、トランスアクスルの支持壁部に装着された第２キャリヤを、一部を切り欠いて示す図である。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 | worn. 図２のIII-III矢視断面を示す図である。It is a figure which shows the III-III arrow cross section of FIG.

以下、本発明の一実施例を図面を参照して詳細に説明する。なお、以下の実施例において図は適宜簡略化或いは変形されており、各部の寸法比および形状等は必ずしも正確に描かれていない。   Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

図１は、本発明の一実施例の車両用動力伝達装置１０の構成を説明する骨子図である。図１において、車両用動力伝達装置１０は、例えばＦＦ（フロントエンジン・フロントドライブ）形式のハイブリッド車両においてエンジン１２と駆動輪１４との間に設けられる。上記車両用動力伝達装置１０は、トランスアクスルケース１６内において、エンジン１２の出力軸（クランク軸）にダンパ装置１８を介して連結された入力軸２０と、その入力軸２０と同心に配置されてダンパ装置１８側から順に設けられた第１モータジェネレータＭＧ１、動力分配用遊星歯車装置２２、減速用遊星歯車装置２４、および第２モータジェネレータＭＧ２とを備えている。上記ダンパ装置１８、入力軸２０、第１モータジェネレータＭＧ１、動力分配用遊星歯車装置２２、減速用遊星歯車装置２４、および第２モータジェネレータＭＧ２に連結されたポンプ駆動軸２５を介して回転駆動されるオイルポンプＯＰは、共通の軸中心線Ｃ上に配置されている。トランスアクスルケース１６は、本発明におけるケースに相当するものであり、例えばアルミニウム合金からダイカスト成形される。また、減速用遊星歯車装置２４は、本発明の遊星歯車装置に相当するものである。   FIG. 1 is a skeleton diagram illustrating the configuration of a vehicle power transmission device 10 according to an embodiment of the present invention. In FIG. 1, 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. It is rotationally driven via a pump drive shaft 25 connected to the damper device 18, the input shaft 20, the first motor generator MG1, the power distribution planetary gear device 22, the reduction planetary gear device 24, and the second motor generator MG2. 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. Further, the reduction planetary gear unit 24 corresponds to the planetary gear unit of the present invention.

動力分配用遊星歯車装置２２は、第１モータジェネレータＭＧ１の第１ロータ支持軸ＲＳ１の軸端にスプタライン嵌合により装着された第１サンギヤＳ１と、動力分配用遊星歯車装置２２および減速用遊星歯車装置２４の外周側に配置された円筒状出力部材２６の動力分配用遊星歯車装置２２側の端部に一体に設けられた第１リングギヤＲ１と、第１サンギヤＳ１の外周側および第１リングギヤＲ１の内周側においてそれら第１サンギヤＳ１および第１リングギヤＲ１にそれぞれ噛み合わされた複数の第１ピニオンＰ１と、入力軸２０に連結され、複数の第１ピニオンＰ１をそれぞれ回転可能且つ軸中心線Ｃ方向まわりの公転可能に支持する第１キャリヤＣＡ１とを有するシングルピニオン型の遊星歯車装置である。この動力分配用遊星歯車装置２２は、エンジン１２からの動力を第１モータジェネレータＭＧ１と円筒状出力部材２６とに機械的に分配する動力分配機構として機能するものであり、円筒状出力部材２６の内周側において減速用遊星歯車装置２４のダンパ装置１８側に隣接して設けられている。   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. A first ring gear R1 integrally provided at an end of the cylindrical output member 26 disposed on the outer peripheral side of the device 24 on the power distribution planetary gear device 22 side, an outer peripheral side of the first sun gear S1, and a first ring gear R1. Are connected to the input shaft 20 and a plurality of first pinions P1 meshed with the first sun gear S1 and the first ring gear R1, respectively. This is a single pinion type planetary gear device having a first carrier CA1 that is supported to revolve around a direction. 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.

動力分配用遊星歯車装置２２により第１モータジェネレータＭＧ１に分配されたエンジン１２の動力は、その第１モータジェネレータＭＧ１を発電機として駆動するために用いられる。また、動力分配用遊星歯車装置２２により円筒状出力部材２６に分配されたエンジン１２の動力は、駆動輪１４を回転駆動するために用いられる。上記円筒状出力部材２６の軸中心線Ｃ方向の中間部には、その軸中心線Ｃ方向において動力分配用遊星歯車装置２２の第１リングギヤＲ１と減速用遊星歯車装置２４の第２リングギヤＲ２との間に位置して外周出力歯として機能する第１ドライブギヤ２８が一体に設けられている。   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. In the middle of the cylindrical output member 26 in the axial center line C direction, 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.

第１モータジェネレータＭＧ１は、エンジン１２により動力分配用遊星歯車装置２２を介して駆動されることで発電機として機能させられ、回生により発生した電気エネルギーを例えばバッテリ等の蓄電装置に充電する。また、第１モータジェネレータＭＧ１は、例えばエンジン始動時には動力分配用遊星歯車装置２２を介してエンジン１２を駆動することで電動機（エンジンスターター）として機能させられる。   The first motor generator MG1 is driven by the engine 12 via the power distribution planetary gear unit 22 to function as a generator, and charges the electric energy generated by the 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.

上記動力分配用遊星歯車装置２２の差動状態は、第１モータジェネレータＭＧ１の回生状態が制御されることにより連続的に変化させられる。そのため、動力分配用遊星歯車装置２２および第１モータジェネレータＭＧ１は、その第１モータジェネレータＭＧ１の運転状態を制御して動力分配用遊星歯車装置２２の差動状態を連続的に変化させることにより円筒状出力部材２６の回転速度を無段階に変化させる電気式変速部を構成している。円筒状出力部材２６に形成された第１ドライブギヤ２８は、その電気式変速部の出力歯車として機能する。   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.

減速用遊星歯車装置２４は、第２モータジェネレータＭＧ２の第２ロータ支持軸ＲＳ２の軸端にスプライン嵌合により装着された第２サンギヤＳ２と、円筒状出力部材２６の減速用遊星歯車装置２４側の端部に一体に設けられた第２リングギヤＲ２と、第２サンギヤＳ２の外周側および第２リングギヤＲ２の内周側においてそれら第２サンギヤＳ２および第２リングギヤＲ２にそれぞれ噛み合わされた複数個（本実施例では４個）の第２ピニオンＰ２と、トランスアクスルケース１６の第１壁部１６ａに回転不能に嵌めつけられ、複数の第２ピニオンＰ２をそれぞれ回転可能に支持する第２キャリヤＣＡ２とを有するシングルピニオン型の遊星歯車装置である。この減速用遊星歯車装置２４は、第２モータジェネレータＭＧ２の回転を減速して第２リングギヤＲ２へ伝達する減速機として機能するものである。なお、第２サンギヤＳ２、第２リングギヤＲ２、第２ピニオンＰ２、および第２キャリヤＣＡ２は、本発明におけるサンギヤ、リングギヤ、ピニオンギヤ、およびキャリヤに相当するものである。   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. It is a single pinion type planetary gear device having 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.

第２モータジェネレータＭＧ２は、単独で或いはエンジン１２と共に駆動輪１４を回転駆動する電動機として機能させられる。また、第２モータジェネレータＭＧ２は、例えば車両の減速走行時等には駆動輪１４により駆動されることで発電機として機能させられ、発電により発生した電気エネルギーを例えばバッテリ等の蓄電装置に充電する。   Second motor generator MG2 is caused to function as an electric motor that rotates drive wheel 14 alone or together with 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. .

円筒状出力部材２６は、軸中心線Ｃ上において相互に隣接して設けられた動力分配用遊星歯車装置２２および減速用遊星歯車装置２４の外周側に配設された円筒状の部材であり、その円筒状出力部材２６の軸中心線Ｃ方向の中間部内側およびエンジン１２側端部の外側にそれぞれ配置された第１軸受３０および第２軸受３２を介して減速用遊星歯車装置２４およびトランスアクスルケース１６により軸中心線Ｃ方向まわりの回転可能に支持されている。上記第１軸受３０は、第１壁部１６ａに固定された減速用遊星歯車装置２４の第２キャリヤＣＡ２の外周側に嵌めつけられている。また、上記第２軸受３２は、動力分配用遊星歯車装置２２の外周側においてトランスアクスルケース１６の内壁面から内周側に延設された第２壁部１６ｂに嵌めつけられている。円筒状出力部材２６の軸中心線Ｃ方向の両端部の内周側には、第１リングギヤＲ１および第２リングギヤＲ２がそれぞれ一体に設けられており、また、円筒状出力部材２６の軸中心線Ｃ方向の中間部の外周側には、第１ドライブギヤ２８およびパーキングロックギヤ３４がそれぞれ一体に設けられている。円筒状出力部材２６は、第１リングギヤＲ１、第２リングギヤＲ２、第１ドライブギヤ２８、およびパーキングロックギヤ３４が一体に設けられた複合ギヤ部材である。   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.

車両用動力伝達装置１０は、さらに、円筒状出力部材２６に連結された減速歯車装置３６と、その減速歯車装置３６から伝達された動力を、左右一対の車軸３８にそれらの回転差を許容しつつ分配する差動歯車装置４０とを備えている。減速歯車装置３６は、円筒状出力部材２６からの出力を減速しつつ差動歯車装置４０へ伝達するものであり、入力軸２０に平行に設けられたカウンタ軸４２に一体に設けられて第１ドライブギヤ２８と噛み合わされた第１ドリブンギヤ４４と、第１ドリブンギヤ４４よりも小径であってカウンタ軸４２に一体に設けられた第２ドライブギヤ４６と、差動歯車装置４０のデフケース４８の外周側に固定されて第２ドライブギヤ４６に噛み合わされた大径リングギヤ５０とを有して構成されている。   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. A first driven gear 44 meshed with the drive gear 28, a second drive gear 46 having a smaller diameter than the first driven gear 44 and provided integrally with the counter shaft 42, and the outer peripheral side of the differential case 48 of the differential gear device 40 And a large-diameter ring gear 50 that is fixed to the second drive gear 46 and meshed with the second drive gear 46.

減速用遊星歯車装置２４において、第２キャリヤＣＡ２は、第２モータジェネレータＭＧ２側の端部がトランスアクスルケース１６の第１壁部 (支持壁) １６ａに貫通して形成された後述の嵌合穴１６ｃ内に相対回転不能な状態に嵌め入れられるとともに、第１モータジェネレータＭＧ１側の端部は、第１壁部 (支持壁) １６ａから軸中心線Ｃ方向に平行な方向へ突設された支持アーム部１６ｄの先端に固定されて支持されるとともに、第３軸受５２を介して円筒状出力部材２６を回転可能に支持している。図２は、第２キャリヤＣＡ２の装着状態を説明する図１のII-II矢視図であって、第１軸受３０、第２サンギヤＳ２、第２ロータ支持軸ＲＳ２、ポンプ駆動軸２５を除去し、専ら、キャリヤＣＡ２、第２ピニオンＰ２、およびトランスアクスル１６の第１壁部１６ａの一部を示している。図３は、図２のIII-III矢視断面を示す図である。以下、図２および図３を参照して第２キャリヤＣＡ２の支持構造を詳細に説明する。   In the reduction planetary gear unit 24, the second carrier CA2 has a fitting hole, which will be described later, formed by penetrating the first wall portion (support wall) 16a of the transaxle case 16 at the end on the second motor generator MG2 side. The end portion on the first motor generator MG1 side is fitted in the non-rotatable state in 16c, and a support projecting from the first wall portion (support wall) 16a in a direction parallel to the axial center line C direction is provided. 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. 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. Hereinafter, the support structure of the second carrier CA2 will be described in detail with reference to FIG. 2 and FIG.

第２キャリヤＣＡ２は、第２ピニオンＰ２を回転可能に支持するキャリヤピン５４の両端部をそれぞれ支持するキャリヤ本体５６とキャリヤカバー５８とを備え、それらキャリヤ本体５６とキャリヤカバー５８とは、溶接、或いは焼結合金による型成形などにより、相互に一体的に構成されている。   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.

上記キャリヤ本体５６は、第２モータジェネレータＭＧ２側へ突き出し、第２ロータ軸ＲＳ２の一端部を支持する第３軸受５２が内周側に嵌めつけられた円筒状のボス部５６ａと、そのボス部５６ａの第２ピニオンＰ２側の端部から径方向外側へ延設され、周方向に複数本(本実施例では４本)配設されたキャリヤピン５４の第２モータジェネレータＭＧ２側の端部をそれぞれ支持する円板状のプレート部５６ｂと、プレート部５６ｂの外周部から径方向外側に突き出すように平坦なスプライン歯状に形成され、軸中心線Ｃ方向に対して対称に位置する各７個の２群の係合歯５６ｃと、プレート部５６ｂにおいてそれら２群の係合歯５６ｃの間に位置するように形成された一対の切欠き部５６ｄと、周方向において一対の切欠き部５６ｄの間に位置するようにプレート部５６ｂから突設されてキャリヤカバー５８に到達する連結部５６ｅとを有している。   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. Of the two groups of engagement teeth 56c, 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. Between It is projected from the plate portion 56b so as to location and a connecting portion 56e to reach the carrier cover 58.

キャリヤカバー５８は、キャリヤ本体５６のプレート部５６ｂから突設された連結部の先端に一体的に固定され、キャリヤピン５４の第１モータジェネレータＭＧ１側の端部をそれぞれ支持する円板状のプレート部５８ｂと、そのプレート部５８ｂのうちキャリヤ本体５６の切欠き部５６ｄに対応する位置に貫通して形成された締結穴５８ｃと、その締結穴５８ｃの第１モータジェネレータＭＧ１側に開口する開口縁部に形成された所定深さの座ぐり穴５８ｄとを有している。   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. Portion 58b, a fastening hole 58c formed through the plate portion 58b at a position corresponding to the cutout portion 56d of the carrier body 56, and an opening edge of the fastening hole 58c that opens to the first motor generator MG1 side And a counterbore 58d of a predetermined depth formed in the portion.

トランスアクスルケース１６の第１壁部 (支持壁) １６ａには、それを貫通して形成された嵌合穴１６ｃの外周縁から外周側へ突き出す係合溝１６ｅが形成されている。この係合溝１６ｅは、キャリヤ本体５６のプレート部５６ｂの外周にに形成された各７個の２群の係合歯５６ｃを嵌め入れ可能となるように、それら係合歯５６ｃと同様の外形状であってそれら係合歯５６ｃの厚み寸法と同様の深さ形成されている。それらの係合溝１６ｅに、キャリヤ本体５６のプレート部５６ｂの外周に形成された各７個の２群の係合歯５６ｃが嵌め入れられることで、第２キャリヤＣＡ２が相対回転不能に、第１壁部 (支持壁) １６ａに且つ軸中心線Ｃ方向と同心に位置決めされた状態で嵌めつけられるようになっている。 An engagement groove 16e is formed on the first wall portion (support wall) 16a of the transaxle case 16 so as to protrude from the outer peripheral edge of the fitting hole 16c formed therethrough to the outer peripheral side. 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. One wall portion (support wall) 16a is fitted in a state of being positioned concentrically with the axial center line C direction.

上記第１壁部 (支持壁) １６ａから突設された軸中心線Ｃ方向に平行な方向へ突設された支持アーム部１６ｄは、キャリヤ本体５６のプレート部５６ｂに形成された切欠き部５６ｄを通過してキャリヤカバー５８まで到達している。支持アーム部１６ｄのキャリヤカバー５８に当接する先端面６０には、雌ねじ穴６２が形成されており、その雌ねじ穴６２内に、キャリヤカバー５８のプレート部５８ｂに形成された締結穴５８ｃを通した締結ボルト６４が螺合されることで、第２キャリヤＣＡ２が支持されている。第２キャリヤＣＡ２は、位置固定のトランスアクスルケース１６の第１壁部 (支持壁) １６ａにより、支持アーム部１６ｄの先端面６０に当接するキャリヤカバー５８の裏面で支持されている。締結ボルト６４は、雄ねじが形成された軸部６４ａと軸部６４ａよりも大径且つ座ぐり穴５８ｄの深さよりも短い寸法の頭部６４ｂとから構成されている。   A support arm portion 16d that projects from the first wall portion (support wall) 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 by the first wall portion (support wall) 16a of the position-fixed transaxle case 16 on the back surface of the carrier cover 58 that comes into contact with the front end surface 60 of the support arm portion 16d. 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.

円筒状出力部材２６は、位置固定の第２キャリヤＣＡ２のキャリヤカバー５８の外周に嵌め着けられた第１軸受３０と、トランスアクスルケース１６の第２壁部１６ｂに嵌め着けられた第２軸受３２とを介して回転可能に支持されており、その第１軸受３０の外側に、外周出力歯車として機能する第１ドライブギヤ２８を備えている。そして、図３に詳しく示すように、軸中心線Ｃ方向において、キャリヤカバー５８の裏面である第２キャリヤＣＡ２の支持位置ＳＰと、第１軸受３０の位置ＢＰとが、第１ドライブギヤ２８の歯幅Ｗ内に位置させられている。好適には、第１ドライブギヤ２８と第１ドリブンギヤ４４との噛合い幅内に位置させられている。これにより、第２キャリヤＣＡ２の支持位置ＳＰすなわち固定位置から、第１ドリブンギヤ４４からのラジアル荷重を受ける第１ドライブギヤ２８までのアーム長が可及的に短縮されている。   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. As shown in detail in FIG. 3, 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. Preferably, 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.

上述のように、本実施例の減速用遊星歯車装置２４の第２キャリヤＣＡ２によれば、その第２キャリヤＣＡ２が第１壁部(支持壁)１６ａに固定される固定位置すなわち支持位置ＳＰが、軸中心線Ｃ方向において第１ドライブギヤ（外周出力歯車）２８の歯幅Ｗ内に位置していることから、円筒状出力部材２６の第１ドライブギヤ（外周出力歯車）２８と噛み合う第１ドリブンギヤ（動力伝達歯車）４４からの反力すなわちラジアル荷重が、その第１ドライブギヤ２８の歯幅Ｗ内に第１壁部 (支持壁) １６ａによる支持位置ＳＰが位置している、第２キャリヤＣＡ２により支持されるので、その第２キャリヤＣＡ２の傾きが抑制される。また、その第２キャリヤＣＡ２の傾きに起因して第２ピニオン（ピニオンギヤ）Ｐ２の荷重分布が不均等となり、振動や騒音が発生することが、好適に解消される。   As described above, according to the second carrier CA2 of the reduction planetary gear unit 24 of the present embodiment, the fixed position at which the second carrier CA2 is fixed to the first wall portion (support wall) 16a, that is, the support position SP. Since it is located within the tooth width W of the first drive gear (outer peripheral output gear) 28 in the direction of the axial center line C, the first meshing with the first drive gear (outer peripheral output gear) 28 of the cylindrical output member 26 is performed. 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 (support wall) 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.

また、本実施例によれば、第２キャリヤＣＡ２は、第２ピニオン（ピニオンギヤ）Ｐ２を回転可能に支持するキャリヤピン（支持ピン）５４と、そのキャリヤピン５４の一端部が嵌め着けられ、第１壁部(支持壁)１６ａに相対回転不能に嵌合されたキャリヤ本体５６と、そのキャリヤ本体５６から突設された連結部５６ｅに一体的に連結され、キャリヤピン５４の他端部が嵌め着けられたキャリヤカバー５８とを備えたものであり、第１壁部(支持壁)１６ａは、軸中心線Ｃ方向に平行な方向に突き出してキャリヤカバー５８に当接する支持アーム部１６ｄを備え、キャリヤカバー５８は、固定具(締結ボルト６４)により支持アーム部１６ｄに固定されている。このため、円筒状出力部材２６の第１ドライブギヤ（外周出力歯車）２８と噛み合う第１ドリブンギヤ（動力伝達歯車）４４からの反力すなわちラジアル荷重が、その第１ドライブギヤ２８の歯幅Ｗ内に位置している、キャリヤカバー５８の裏面に当接する支持アーム部１６ｄの先端面６０により支持されるので、第２キャリヤＣＡ２の傾きが抑制される。また、その第２キャリヤＣＡ２の傾きに起因して第２ピニオン（ピニオンギヤ）Ｐ２の荷重分布が不均等となり、振動や騒音が発生することが、好適に解消される。   Further, according to the present embodiment, 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). Therefore, 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. Is supported by the front end surface 60 of the support arm portion 16d that is in contact with the back surface of the carrier cover 58, 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.

また、本実施例によれば、上記固定具は、雄ねじが形成された軸部６４ａとその軸部６４ａよりも大径の頭部６４ｂとを備えてその軸部６４ａが支持アーム部１６ｄに螺合される締結ボルト６４であり、キャリヤカバー５８は、その締結ボルト６４の軸部６４ａを貫通させる締結穴５８ｃと、その締結穴５８ｃのキャリヤ本体５６とは反対側の開口部にその締結穴５８ｃよりも大径に形成されて締結ボルト６４の頭部６４ｂを埋没させる座ぐり穴５８ｄとを備えたものである。このため、第１壁部 (支持壁) １６ａから突き出す支持アーム部１６ｄの先端面６０に螺合してキャリヤカバー５８を締結するための締結ボルト６４が用いられているが、その締結ボルト６４の頭部６４ｂはキャリヤカバー５８に形成された座ぐり穴５８ｄ内に位置しているので、軸方向寸法が増大しない利点がある。 Further, according to the present embodiment, 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. For this reason, a fastening bolt 64 for screwing the carrier cover 58 into the front end surface 60 of the support arm portion 16d protruding from the first wall portion (support wall) 16a 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.

また、本実施例によれば、キャリヤ本体５６の外周部には、軸中心線Ｃ方向に対して対称部位に外周側へ突き出すようにフランジ状にそれぞれ形成された複数個の係合歯５６ｃが形成され、第１壁部 (支持壁) １６ａには、それら複数個の係合歯５６ｃを有するキャリヤ本体５６のプレート部５６ｂの外周形状と同様の形状を有し、そのキャリヤ本体５６を相対回転不能に嵌め入れる係合溝 １６ｅが嵌合穴１６ｃの外周に形成されている。このように、嵌合穴１６ｃおよび係合溝１６ｅに相対回転不能に嵌め入れられるキャリヤ本体５６の外周部には、軸中心線Ｃ方向に対して対称部位にそれぞれ形成された複数個の係合歯５６ｃが形成されているため、各係合歯５６ｃが受ける反力の合力は相殺されて小さなものとなるので、キャリヤ本体５６の振動等が一層抑制される。 Further, according to the present embodiment, 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 (support wall) 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. As described above, 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.

また、本実施例によれば、キャリヤ本体５６は、キャリヤカバー５８とは反対側へ突き出すボス部５６ａを備え、そのボス部５６ａの内周面には、第２サンギヤＳ２が装着される第２ロータ支持軸(回転軸)ＲＳ２の外周面に嵌合してそれを回転可能に支持するための第３軸受５２が、嵌め着けられている。このため、第２サンギヤＳ２が装着される第２ロータ支持軸(回転軸)ＲＳ２を支持する第３軸受５２がキャリヤ本体５６の内周面に嵌め着けられているので、減速用遊星歯車装置(遊星歯車装置)２４の軸方向寸法が一層短縮される。 Further, according to the present embodiment, 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.

また、本実施例によれば、キャリヤカバー５８の外周面には、円筒状出力部材２６の内周面のうち第１ドライブギヤ（外周出力歯車）２８に対応する部位に嵌合してそれを回転可能に支持するための第１軸受３０が嵌め着けられている。このように、円筒状出力部材２６の内周面のうち第１ドライブギヤ（外周出力歯車）２８に対応する部位に嵌合してそれを回転可能に支持するための第１軸受３０がキャリヤカバー５８の外周面に嵌め着けられているので、減速用遊星歯車装置(遊星歯車装置)２４の軸方向寸法が一層短縮される。また、円筒状出力部材２６の第１ドライブギヤ（外周出力歯車）２８と噛み合う第１ドリブンギヤ（動力伝達歯車）４４からの反力すなわちラジアル荷重が、その第１ドライブギヤ２８の歯幅Ｗ内に位置している、第２キャリヤＣＡ２を支持する支持アーム部１６ｄの先端部によりその第１軸受３０を介して直接的に支持される利点がある。 According to the present embodiment, 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. As described above, 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. Further, 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. There is an advantage that it is directly supported via the first bearing 30 by the tip end portion of the support arm portion 16d that supports the second carrier CA2.

以上、本発明の一実施例を図面を参照して詳細に説明したが、本発明はこの実施例に限定されるものではなく、別の態様でも実施され得る。   As mentioned above, although one Example of this invention was described in detail with reference to drawings, this invention is not limited to this Example, It can implement in another aspect.

例えば、前述の減速用遊星歯車装置２４の第２キャリヤＣＡ２は、４本のキャリヤピン５４に回転可能に支持された４個の第２ピニオンＰ２を備え、２本の締結ボルト６４によって第１壁部(支持壁)１６ａに支持され、キャリヤ本体５６は２本の連結部５６ｅを介して相互に連結されていたが、第２ピニオンＰ２の個数、締結ボルト６４の本数、連結部５６ｅの本数はいずれの一例であり、それらの個数或いは本数は変更され得るものである。   For example, 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. However, 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.

また、前述の実施例において、係合歯５６ｃおよびそれを嵌め入れる係合溝１６ｅの数は、軸中心線Ｃ方向に対して対称の部位に７個ずつ形成されていたが、必ずしも７個でなくてもよく、たとえば２個乃至８個程度のいずれでであってもよい。 Further, in the above-described embodiment, 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. For example, it may be any of about 2 to 8.

また、前述の実施例において、円筒状出力部材２６は、キャリヤカバー３８の外周面と円筒状出力部材２６の軸中心線Ｃ方向の中間位置の内周面との間に嵌め入れられた第１軸受３０と、動力分配用遊星歯車装置２２側の外周面に嵌め着けられた第２軸受３２とによって回転可能に支持されていたが、第１軸受３０は、円筒状出力部材２６の減速用遊星歯車装置２４側の外周面と第１壁部１６ａとの間に設けられてもよい。   In the above-described embodiment, 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. Although 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.

なお、上述したのはあくまでも一実施形態であり、その他一々例示はしないが、本発明は、その主旨を逸脱しない範囲で当業者の知識に基づいて種々変更、改良を加えた態様で実施することができる。   It should be noted that the above description is merely an embodiment, and other examples are not illustrated. However, the present invention is implemented in variously modified and improved modes based on the knowledge of those skilled in the art without departing from the gist of the present invention. Can do.

１０：車両用動力伝達装置
１６：トランスアクスルケース（ケース）
１６ａ：第１壁部（支持壁）
１６ｃ：嵌合穴
１６ｄ：支持アーム部
１６ｅ：係合溝
２４：減速用遊星歯車装置（遊星歯車装置）
２６：円筒状出力部材
２８：第１ドライブギヤ（外周出力歯）
３０：第１軸受
４４：第１ドリブンギヤ（動力伝達歯車）
５２：第３軸受
５４：キャリヤピン（支持ピン）
５６：キャリヤ本体
５６ａ：ボス部
５６ｂ：プレート部
５６ｃ：係合歯
５６ｅ：連結部
５８：キャリヤカバー
５８ｃ：締結穴
５８ｄ：座ぐり穴
６０：先端面
６４：締結ボルト (固定具)
６４ａ：軸部
６４ｂ：頭部
Ｃ：軸中心線
ＣＡ２：第２キャリヤ（キャリヤ）
ＭＧ１：第１モータジェネレータ
ＲＳ１：第１ロータ軸
ＭＧ２：第２モータジェネレータ
ＲＳ２：第２ロータ軸
Ｐ２：第２ピニオン（ピニオンギヤ）
Ｒ２：第２リングギヤ（リングギヤ）
Ｓ２：第２サンギヤ（サンギヤ）
10: 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)

Claims (5)

サンギヤおよびリングギヤにそれぞれ噛み合わされたピニオンギヤを回転可能に支持するキャリヤと、該リングギヤが内周面に形成され且つ後段の動力伝達歯車と噛み合う外周出力歯が外周面に形成された円筒状出力部材とを軸中心線まわりに同心に備え、位置固定の支持壁に前記キャリヤが相対回転不能に支持された車両用動力伝達装置の遊星歯車装置であって、
前記キャリヤの前記支持壁との固定位置が、軸中心線方向において前記外周出力歯車の歯幅内に位置しており、
前記キャリヤは、前記ピニオンギヤを回転可能に支持する支持ピンと
、該支持ピンの一端部が嵌め着けられ、前記支持壁に相対回転不能に嵌合されたキャリヤ本体と、該キャリヤ本体から突設された連結部に一体的に連結され、前記支持ピンの他端部が嵌め着けられたキャリヤカバーとを備えたものであり、
前記支持壁は、前記軸中心線に平行な方向に突き出して前記キャリヤカバーに当接する支持アーム部を備え、
前記キャリヤカバーは、固定具により該支持アーム部に固定されていることを特徴とする車両用動力伝達装置の遊星歯車装置。 A carrier that rotatably supports the pinion gear meshed with the sun gear and the ring gear, and a cylindrical output member with the ring gear formed on the inner circumferential surface and outer circumferential output teeth that mesh with the power transmission gear of the subsequent stage, Is a planetary gear unit of a power transmission device for a vehicle in which the carrier is supported on a support wall fixed in position so as not to be relatively rotatable.
A fixing position of the carrier with the support wall is located within a tooth width of the outer peripheral output gear in the axial center line direction;
The carrier includes a support pin that rotatably supports the pinion gear, a carrier body that is fitted with one end of the support pin and is non-rotatably fitted to the support wall, and protrudes from the carrier body. A carrier cover that is integrally connected to the connecting portion and to which the other end of the support pin is fitted;
The support wall includes a support arm portion that protrudes in a direction parallel to the axial center line and contacts the carrier cover,
The planetary gear device for a vehicle power transmission device, wherein the carrier cover is fixed to the support arm portion by a fixture. 前記固定具は、雄ねじが形成された軸部と該軸部よりも大径の頭部とを備えて該軸部が前記支持アーム部に螺合される締結ボルトであり、
前記キャリヤカバーは、該締結ボルトの軸部を貫通させる貫通穴と、該貫通穴の前記キャリヤ本体とは反対側の開口部に該貫通穴よりも大径に形成されて前記締結ボルトの頭部を埋没させる座ぐり穴とを備えたものであるこを特徴とする請求項１の車両用動力伝達装置の遊星歯車装置。 The fixture is a fastening bolt that 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 to 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 portion on the opposite side of the through hole from the carrier body, and has a larger diameter than the through hole. The planetary gear device for a power transmission device for a vehicle according to claim 1, further comprising a counterbore for embedding the shaft. 前記キャリヤ本体の外周部には、前記軸中心線に対して対称部位において外周側へフランジ状に突き出すようにそれぞれ形成された複数個の係合歯が形成され、
前記支持壁には、該複数個の係合歯を有する前記キャリヤ本体の外周形状と同様の形状を有し、該キャリヤ本体を相対回転不能に嵌め入れる嵌合穴が、形成されていることを特徴とする請求項１または２の車両用動力伝達装置の遊星歯車装置。 A plurality of engaging teeth are formed on the outer peripheral portion of the carrier body so as to protrude in a flange shape toward the outer peripheral side at a portion symmetrical 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 has a fitting hole into which the carrier body is fitted so as not to be relatively rotatable. The planetary gear unit for a vehicle power transmission device according to claim 1 or 2 . 前記キャリヤ本体には、前記キャリヤカバーとは反対側へ突き出すボス部が形成されており、
該ボス部の内周面には、前記サンギヤが装着される回転軸の外周面に嵌合してそれを回転可能に支持するための第３軸受が、嵌め着けられていることを特徴とする請求項１乃至３のいずれか１の車両用動力伝達装置の遊星歯車装置。 The carrier body is formed with a boss portion protruding to the opposite side of the carrier cover,
A third bearing is fitted on the inner peripheral surface of the boss portion so as to fit and rotatably support the outer peripheral surface of the rotary shaft on which the sun gear is mounted. A planetary gear device for a vehicle power transmission device according to any one of claims 1 to 3 . 前記キャリヤカバーの外周面には、前記円筒状出力部材の内周面のうち前記外周出力歯に対応する部位に嵌合してそれを回転可能に支持するための第１軸受が嵌め着けられていることを特徴とする請求項１乃至４のいずれか１の車両用動力伝達装置の遊星歯車装置。 On the outer peripheral surface of the carrier cover, a first bearing for fitting in a portion corresponding to the outer peripheral output tooth of the inner peripheral surface of the cylindrical output member and rotatably supporting it is fitted. The planetary gear device for a vehicle power transmission device according to any one of claims 1 to 4 .
JP2013523731A 2011-07-11 2011-07-11 Planetary gear device for vehicle power transmission device Expired - Fee Related JP5626467B2 (en)

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JP6286460B2 (en) * 2016-02-18 2018-02-28 本田技研工業株式会社 Planetary gear mechanism and transmission
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JPH01122542U (en) * 1988-02-16 1989-08-21
JP2004116737A (en) * 2002-09-27 2004-04-15 Toyota Motor Corp Planetary gear device and power train
JP2009092123A (en) * 2007-10-05 2009-04-30 Toyota Motor Corp Transmission and power transmission device

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DE102004006723A1 (en) * 2004-02-11 2005-09-01 Zf Friedrichshafen Ag planetary gear
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JP2009092123A (en) * 2007-10-05 2009-04-30 Toyota Motor Corp Transmission and power transmission device

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