JP2008501920A - Planetary differential transmission - Google Patents

Planetary differential transmission Download PDF

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JP2008501920A
JP2008501920A JP2007526547A JP2007526547A JP2008501920A JP 2008501920 A JP2008501920 A JP 2008501920A JP 2007526547 A JP2007526547 A JP 2007526547A JP 2007526547 A JP2007526547 A JP 2007526547A JP 2008501920 A JP2008501920 A JP 2008501920A
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gear
planetary
planetary gear
ring gear
differential transmission
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セドグウィック ジェフリー
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リカード ユーケイ リミテッド
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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
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • 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
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • 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
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • 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
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K7/0007—Disposition of motor in, or adjacent to, traction wheel the motor being electric
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring gears
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/02004—Gearboxes; Mounting gearing therein the gears being positioned relative to one another by rolling members or by specially adapted surfaces on the gears, e.g. by a rolling surface with the diameter of the pitch circle
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • F16H63/3416—Parking lock mechanisms or brakes in the transmission
    • F16H63/3425—Parking lock mechanisms or brakes in the transmission characterised by pawls or wheels

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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)
  • Arrangement And Driving Of Transmission Devices (AREA)

Abstract

単一速度の遊星差動伝動装置は、入力シャフト１２を二つの出力シャフト１６，２３に接続するとともに実質的に等しいトルクに分配するものである。この装置は、出力シャフト１６，２３に相対的な変速を与える差動ギヤとしての機能を持つ一体の環状部／サンギヤ１７，１８を有する、二つの遊星ギヤ列を具えるものである。
【選択図】図１A single speed planetary differential transmission connects the input shaft 12 to the two output shafts 16, 23 and distributes it to a substantially equal torque. This device comprises two planetary gear trains having integral annular / sun gears 17, 18 that function as differential gears that provide relative speed changes to output shafts 16, 23.
[Selection] Figure 1

Description

本発明は、二つの駆動車輪を有する車両、とりわけ電気駆動車両に用いるのに特に適した遊星差動伝動装置に関するものである。   The present invention relates to a planetary differential transmission device which is particularly suitable for use in a vehicle having two drive wheels, in particular an electrically driven vehicle.

二つの駆動車輪と一つの駆動力源を有する車両は、一つの駆動シャフトをそれぞれの駆動車輪に結合されたハーフシャフトに分割する手段が必要である。また、例えばコーナリング時には、それら駆動車輪間のそれぞれの回転を調整するための差動ギヤも必要である。さらには、特に前輪駆動車両においては、トルクステアを回避するために、それら駆動車輪間で駆動トルクを均等に分配する必要がある。   A vehicle having two driving wheels and one driving force source requires means for dividing one driving shaft into half shafts coupled to the respective driving wheels. Further, for example, at the time of cornering, a differential gear for adjusting each rotation between the driving wheels is also necessary. Further, particularly in front wheel drive vehicles, it is necessary to evenly distribute the drive torque among these drive wheels in order to avoid torque steer.

通常、ベベルギヤのような最終駆動減速ギヤは、従来のベベルギヤ式差動装置に組み込まれており、この装置は特に小型というわけではない。   Usually, a final drive reduction gear such as a bevel gear is incorporated in a conventional bevel gear type differential, and this device is not particularly small.

電動機のトルク特性により、走行速度をモータ速度に正比例させることができるので、電気自動車は、通常は単一速度の減速ギヤのみしか必要としない。コンパクトに収納するためには、ハーフシャフトを、電動機の電機子の軸方向に沿って延在させて駆動車輪に結合する、同軸配置とするのが好ましい。   Because the running speed can be directly proportional to the motor speed due to the torque characteristics of the electric motor, an electric vehicle usually only requires a single speed reduction gear. In order to store in a compact manner, the half shaft preferably has a coaxial arrangement that extends along the axial direction of the armature of the motor and is coupled to the drive wheel.

本発明に従う、単一速度の遊星差動伝動装置は、ハウジングと、ハウジング内に回転軸を有する回転可能な環状の入力部材と、前記軸上にあり、回転可能な対向した二つの出力部材であって、そのうちの一方が前記入力部材により駆動されるように構成された出力部材と、前記入力部材の周囲に設けられた遊星ギヤ列と、を具え、前記入力部材はサンギヤを具え、インナ遊星ギヤが前記サンギヤと噛み合った状態で設けられており、前記入力部材と関連して出力部材とともに高速回転するインナ遊星ギヤキャリアが設けられており、インナリングギヤがその内側を前記インナ遊星ギヤに噛み合わせ、その外側を前記ハウジングの軸上を回転可能なアウタ遊星ギヤに噛み合わせた状態で設けられており、アウタリングギヤが前記アウタ遊星ギヤと噛み合うとともに、前記出力部材のうちの他方の部材に接続された状態で設けられていることを特徴するものである。   According to the present invention, a single-speed planetary differential transmission device includes a housing, a rotatable annular input member having a rotation shaft in the housing, and two opposed output members that are rotatable on the shaft. An output member configured to be driven by the input member, and a planetary gear train provided around the input member, the input member including a sun gear, and an inner planetary gear. An inner planetary gear carrier that rotates at a high speed together with the output member is provided in association with the input member, and an inner ring gear meshes with the inner planetary gear on the inside. The outer planetary gear is provided with its outer side meshed with an outer planetary gear rotatable on the shaft of the housing, and the outer ring gear is provided with the outer planetary gear. Meshes with, is to being provided in a state of being connected to the other member of said output member.

この配置は、軸方向距離が短く、遊星ギヤ列の要素が、駆動車輪間に実質的に等しいトルクを分配すると同時に、それぞれの出力部材の相対的な回転を調整する差動ギヤとして機能する単一速度の伝動装置を提供するものである。   This arrangement has a short axial distance and the elements of the planetary gear train function as a differential gear that regulates the relative rotation of each output member while at the same time distributing substantially equal torque between the drive wheels. A one-speed transmission is provided.

さらには、サンギヤと、インナ遊星ギヤと、インナリングギヤとを実質的に同一平面内に配置するのが好ましい。また、インナリングギヤと、アウタ遊星ギヤと、アウタリングギヤとを実質的に同一平面内に配置するのが好ましい。好適な実施例では、サンギヤと、遊星ギヤと、リングギヤとを全て実質的に同一の平面内に配置している。この配置の特に有利な点は、出力部材の内端同士を互いに極めて接近させ得ることで、これにより、ハーフシャフトの長さを最大にすることができるとともに、車両のサスペンションが作動している際の、ハーフシャフトの揺動（アーティキュレーション）を最小とすることができる。   Furthermore, it is preferable that the sun gear, the inner planetary gear, and the inner ring gear are arranged in substantially the same plane. Further, it is preferable that the inner ring gear, the outer planetary gear, and the outer ring gear are arranged in substantially the same plane. In the preferred embodiment, the sun gear, the planetary gear, and the ring gear are all disposed in substantially the same plane. The particular advantage of this arrangement is that the inner ends of the output members can be very close to each other, thereby maximizing the length of the half shaft and when the vehicle suspension is in operation. Thus, the swing (articulation) of the half shaft can be minimized.

好適な実施例では、四つのインナ遊星ギヤと、四つのアウタ遊星ギヤとを設けている。   In the preferred embodiment, four inner planetary gears and four outer planetary gears are provided.

本装置は、伝動装置を固定するため、およびパークロック機能を提供するために、ハウジングに対して遊星ギヤ列の要素を制止させる係合可能なロック爪をさらに具えることができる。この爪を、例えばアウタリングギヤに係合させることもできる。   The device can further include an engageable locking pawl that restrains the elements of the planetary gear train relative to the housing to secure the transmission and to provide a park lock function. The claw can be engaged with, for example, an outer ring gear.

好適な実施例では、サンギヤは３３歯を有し、インナ遊星ギヤは２６歯を有し、インナリングギヤはその内側に８７歯およびその外側に１０３歯を有し、アウタ遊星ギヤは１９歯を有し、アウタリングギヤは１４１歯を有している。この装置は７．２４対１の総減速比を有することになる。   In the preferred embodiment, the sun gear has 33 teeth, the inner planetary gear has 26 teeth, the inner ring gear has 87 teeth on the inside and 103 teeth on the outside, and the outer planetary gear has 19 teeth. The outer ring gear has 141 teeth. This device will have a total reduction ratio of 7.24 to 1.

インナリングギヤは、インナ遊星ギヤ列の環状部およびアウタ遊星ギヤ列のサンギヤを具えていることは理解されよう。このインナリングギヤは、差動ギヤとしての作用を奏するために、インナ遊星ギヤ列およびアウタ遊星ギヤ列の互いの要素間で浮動する。   It will be appreciated that the inner ring gear comprises an annular portion of the inner planetary gear train and a sun gear of the outer planetary gear train. This inner ring gear floats between the elements of the inner planetary gear train and the outer planetary gear train in order to act as a differential gear.

実質的にトルクを等しく分配するために、ギヤ比を注意深く選択する必要があるが、これは、必要とする最終的な駆動減速および、遊星ギヤ要素の一連の寸法制限を考慮した上で、伝動装置を熟知した技術者が計算により求め得るものである。   In order to distribute the torque substantially equally, the gear ratio must be carefully selected, which takes into account the final drive reduction required and the set of dimensional limitations of the planetary gear elements. It can be obtained by calculation by an engineer familiar with the apparatus.

好適な実施例において、本発明にかかる伝動装置の軸方向距離は、従来の最終駆動／差動ユニットの５０％近くに短縮され、部品数は約３０％が削減されている。小型車両においては、ステアリングおよびサスペンションの部品のためのスペースを最大化することができるので、軸方向距離を短縮することは有益である。   In the preferred embodiment, the axial distance of the transmission according to the present invention is reduced to nearly 50% of the conventional final drive / differential unit and the number of parts is reduced by about 30%. In small vehicles, it is beneficial to reduce the axial distance as space for steering and suspension components can be maximized.

さらに、本発明は、例えば、両出力シャフト間の速度比を固定もしくは制御する、差動固定機能もしくは差動制限機能を取り入れることもできる。これは、出力部材同士が直接隣接しており、かつ同一の回転軸上にあるので、比較的容易に達成することができる。   Furthermore, the present invention can incorporate a differential fixing function or a differential limiting function that fixes or controls the speed ratio between the two output shafts, for example. This can be achieved relatively easily because the output members are directly adjacent and on the same axis of rotation.

本発明のさらなる特徴は、本発明の一例として図示した好適な実施例の詳細な説明から理解することができ、ここに、図１は、本発明にかかる伝動装置を示した概略図、図２は、図１の実施例の概略図の実際を示した軸方向の断面図である。   Further features of the present invention can be understood from the detailed description of the preferred embodiment illustrated as an example of the present invention, wherein FIG. 1 is a schematic diagram showing a transmission according to the present invention, FIG. FIG. 2 is an axial sectional view showing the actual schematic diagram of the embodiment of FIG. 1.

図１に示すように、伝動装置は、中空の電機子（図示せず）を有する電動機１１上に回転の主軸１０を具えている。電機子は、伝動装置の、中空の入力シャフト１２に直接接続されており、その入力シャフトは、図に示すように、全ての主要なギヤ部品が実質的に同一の平面内に配置された二段遊星伝動装置のサンギヤ１３を具えている。   As shown in FIG. 1, the transmission includes a rotating main shaft 10 on an electric motor 11 having a hollow armature (not shown). The armature is directly connected to the hollow input shaft 12 of the transmission, which, as shown, has two main gear parts arranged in substantially the same plane. A sun gear 13 of a stage planetary transmission is provided.

複数の（典型的に四つの）インナ遊星ギヤ１４は、サンギヤと噛み合った状態でその周りを回り、一般の遊星ギヤキャリア１５によって軸支されている。このキャリア１５は、車両の駆動車輪に接続するために、入力シャフト１２およびモータ１１に沿って延在する駆動シャフト１６に結合されている。   A plurality (typically four) of the inner planetary gears 14 rotate around the sun gear while being engaged with the sun gear, and are supported by a general planetary gear carrier 15. The carrier 15 is coupled to an input shaft 12 and a drive shaft 16 that extends along the motor 11 for connection to drive wheels of the vehicle.

遊星ギヤ１４の周りには、直径方向内側にインナ遊星ギヤ１４と噛み合うギヤ歯を持つインナリングギヤ（環状部）１７が設けられている。さらに、このインナリングギヤは、直径方向外側にギヤ歯を有し、このようにして、アウタ遊星ギヤ列のサンギヤ１８は構成されている。   Around the planetary gear 14, an inner ring gear (annular portion) 17 having gear teeth that mesh with the inner planetary gear 14 is provided on the inner side in the diameter direction. Further, this inner ring gear has gear teeth on the outer side in the diameter direction, and thus the sun gear 18 of the outer planetary gear train is configured.

複数の（典型的に四つの）アウタ遊星ギヤ１９は、上記アウタサンギヤ１８と噛み合った状態でその周りを回り、伝動装置ケーシング２１に固定されたスピゴット２０にそれぞれ軸支されている。   A plurality of (typically four) outer planetary gears 19 rotate around the outer sun gear 18 while meshing with the outer sun gear 18, and are respectively supported by spigots 20 fixed to the transmission casing 21.

アウタリングギヤ（環状部）２２は、アウタ遊星ギヤ１９と噛み合うとともに、車両の第二の駆動車輪と接続するために、もう一方の駆動シャフト２３に接続されている。   The outer ring gear (annular portion) 22 meshes with the outer planetary gear 19 and is connected to the other drive shaft 23 in order to connect to the second drive wheel of the vehicle.

使用時には、電動機１１からの駆動トルクは、入力シャフト１２を介してサンギヤ１３に伝動される。インナリングギヤ１７による反動トルクは、インナ遊星ギヤを回転させ、キャリア１５および駆動シャフト１６を作動させる。   In use, the drive torque from the electric motor 11 is transmitted to the sun gear 13 via the input shaft 12. The reaction torque generated by the inner ring gear 17 rotates the inner planetary gear and operates the carrier 15 and the drive shaft 16.

アウタサンギヤ１８も（インナリングギヤ１７とともに）回転し、アウタ遊星ギヤ１９を介してアウタリングギヤ２２にトルクを伝達する。これらアウタ遊星ギヤは、伝動装置ケーシング２１によって構成される固定キャリアとしての機能を効果的に果たしており、これにより、アウタリングギヤ２２は回転し、そして駆動シャフト２３を作動させる。   The outer sun gear 18 also rotates (together with the inner ring gear 17) and transmits torque to the outer ring gear 22 via the outer planetary gear 19. These outer planetary gears effectively function as a fixed carrier constituted by the transmission casing 21, whereby the outer ring gear 22 rotates and the drive shaft 23 is operated.

駆動シャフト間における速度バランスは、路面と接触する車輪によって制御されることは理解されよう。インナリングギヤ１７／アウタサンギヤ１８は、差動ギヤであるから、それぞれの駆動シャフトを（例えば車両のコーナリング時に）相対的に回転させる。   It will be appreciated that the speed balance between the drive shafts is controlled by the wheels in contact with the road surface. Since the inner ring gear 17 / outer sun gear 18 are differential gears, the drive shafts are relatively rotated (for example, during cornering of the vehicle).

電動機からの駆動トルクは、二つの遊星ギヤ列間で分配され、トルクバランスは、選択された回転比によって決定される。車両の駆動車輪が実質的に同一軸上ある場合は、トルクを等しく分配するのが好ましいが、例えば、駆動シャフトが全輪駆動車両の異なる軸に接続されている場合、または自動車以外の特殊な用途に用いる場合は、異なるトルク分配を選択することができる。   The drive torque from the motor is distributed between the two planetary gear trains, and the torque balance is determined by the selected rotation ratio. If the drive wheels of the vehicle are substantially on the same axis, it is preferable to distribute the torque equally, but for example if the drive shaft is connected to a different axis of an all-wheel drive vehicle or a special vehicle other than an automobile. Different torque distributions can be selected for use in applications.

図１に、要求に応じてアウタリングギヤ２２を伝動装置ケーシング２１に係合して固定することのできるパークロック爪２４を示す。アウタリングギヤの回転を妨げることで、伝動装置の作動を固定でき、このようにすれば、車両に車輪ブレーキを与えることができることは理解されよう。   FIG. 1 shows a park lock claw 24 capable of engaging and fixing the outer ring gear 22 to the transmission casing 21 as required. It will be appreciated that by preventing the outer ring gear from rotating, the operation of the transmission can be fixed, and in this way a wheel brake can be applied to the vehicle.

本装置は、差動ギヤ１７／１８の外的な制御に対する変更に適している。その差動ギヤ１７／１８を外的に制御することによって、駆動シャフト１６，２３間のトルク分配を調整することができることは理解されよう。差動ギヤ１７／１８を制動するための手段は、ブレーキバンド、クラッチまたは粘性カップリングが適している。   This device is suitable for changes to the external control of the differential gear 17/18. It will be appreciated that the torque distribution between the drive shafts 16, 23 can be adjusted by externally controlling the differential gear 17/18. Suitable means for braking the differential gear 17/18 are brake bands, clutches or viscous couplings.

駆動シャフト１６，２３の内端同士を互いに直接接近させて配置することにより、従来の差動ギヤ装置の駆動シャフトの内端間と比べて、車両のサスペンションが作動している際の、伝動装置の駆動シャフトの揺動（アーティキュレーション）を最小にすることができる。この配置は、車両の軌跡が比較的狭い、小型の前輪駆動車両に特に有用である。さらには、駆動軸端同士を接近させて配置することにより、駆動シャフト同士を固定する、または駆動シャフト同士の相対的な回転を制限するカップリングを比較的容易に装備させることができる。このようにして、この装置は、特定の車両には重要となる差動固定機能または差動制限機能を具えることができる。   By arranging the inner ends of the drive shafts 16 and 23 to be in direct proximity to each other, the transmission device when the suspension of the vehicle is operating as compared with between the inner ends of the drive shafts of the conventional differential gear device. Swaying (articulation) of the drive shaft can be minimized. This arrangement is particularly useful for small front wheel drive vehicles where the vehicle trajectory is relatively narrow. Furthermore, by arranging the drive shaft ends close to each other, a coupling that fixes the drive shafts or restricts relative rotation of the drive shafts can be relatively easily equipped. In this way, the device can have a differential locking function or a differential limiting function that is important for a particular vehicle.

図１に概略的に示した実施例では、差動ギヤ１７／１８を外的に制御することなく、実質的に等しいトルクに分配するために、各ギヤは以下に示す数の歯を有している。
インナサンギヤ１３ ‐ ３３歯
インナ遊星ギヤ１４ ‐ ２６歯
インナリングギヤ１７ ‐８７歯
アウタサンギヤ１８ ‐ １０３歯
アウタ遊星ギヤ１９ ‐１９歯
アウタリングギヤ２２ ‐１４１歯 In the embodiment schematically shown in FIG. 1, in order to distribute the differential gears 17/18 to a substantially equal torque without external control, each gear has the following number of teeth: ing.
Inner sun gear 13-33 teeth Inner planetary gear 14-26 teeth Inner ring gear 17-87 teeth Outer sun gear 18-103 teeth Outer planetary gear 19-19 teeth Outer ring gear 22-141 teeth

従って、これら個々の比による総減速比は、７．２４対１である。   Therefore, the total reduction ratio by these individual ratios is 7.24 to 1.

前輪駆動車両用の実際的な伝動装置を図２に示しており、伝動装置ケーシング１１、ベアリング、シャフトシールおよび他の従来の部品をより詳細に説明している。必要に応じて部品には図１に対応した参照符号を付したが、パークロック装置は図示していない。   A practical transmission for a front-wheel drive vehicle is shown in FIG. 2 and describes the transmission casing 11, bearings, shaft seals and other conventional parts in more detail. Parts are denoted by reference numerals corresponding to FIG. 1 as necessary, but the park lock device is not shown.

伝動装置ケーシング２１は、図示したように、電動機のケーシング３０に直接ボルト留めされている。   As shown in the figure, the transmission device casing 21 is directly bolted to the casing 30 of the electric motor.

本発明にかかる伝動装置を示した概略図である。It is the schematic which showed the transmission concerning this invention. 図１の実施例の概略図の実際を示した軸方向の断面図である。It is sectional drawing of the axial direction which showed the actual schematic of the Example of FIG.

Claims (8)

ハウジング（２１）と、ハウジング内に回転軸（１０）を有する回転可能な環状の入力部材（１２）と、前記軸上（１０）にあり、回転可能な対向した二つの出力部材であって、そのうちの一方が前記入力部材（１２）により駆動されるよう構成された出力部材（１６，２３）と、前記入力部材（１２）の周囲に設けられた遊星ギヤ列と、を具え、
前記入力部材（１２）は、サンギヤ（１３）を具え、
インナ遊星ギヤ（１４）が前記サンギヤと噛み合った状態で設けられており、
前記入力部材（１２）と関連して、出力部材（１６）とともに高速回転するインナ遊星ギヤキャリア（１５）が設けられており、
インナリングギヤがその内側を前記インナ遊星ギヤ（１４）に噛み合わせ、その外側を前記ハウジング内の軸（２０）上を回転可能なアウタ遊星ギヤ（１９）に噛み合わせた状態で設けられており、
アウタリングギヤが前記アウタ遊星ギヤ（１９）と噛み合うとともに、前記出力部材のうちの他方の部材（２３）に接続された状態で設けられていることを特徴する、遊星差動伝動装置。 A housing (21), a rotatable annular input member (12) having a rotating shaft (10) in the housing, and two opposed opposing output members on the shaft (10); One of them comprising an output member (16, 23) configured to be driven by the input member (12), and a planetary gear train provided around the input member (12),
The input member (12) comprises a sun gear (13),
An inner planetary gear (14) is provided in mesh with the sun gear;
In connection with the input member (12), an inner planetary gear carrier (15) rotating at a high speed with the output member (16) is provided,
An inner ring gear is provided in a state where its inner side meshes with the inner planetary gear (14) and its outer side meshes with an outer planetary gear (19) rotatable on the shaft (20) in the housing,
An outer ring gear meshes with the outer planetary gear (19) and is provided in a state of being connected to the other member (23) of the output members. 前記サンギヤ（１３）と、インナ遊星ギヤ（１４）と、インナリングギヤ（１７）とは、実質的に同一平面内に配置されたことを特徴とする、請求項１記載の遊星差動伝動装置。   The planetary differential transmission device according to claim 1, characterized in that the sun gear (13), the inner planetary gear (14) and the inner ring gear (17) are arranged substantially in the same plane. インナリングギヤ（１７）と、アウタ遊星ギヤ（１９）と、アウタリングギヤ（２２）とは、実質的に同一平面内に配置されたことを特徴とする、請求項１もしくは２に記載の遊星差動伝動装置。   The planetary differential according to claim 1 or 2, characterized in that the inner ring gear (17), the outer planetary gear (19) and the outer ring gear (22) are arranged in substantially the same plane. Transmission device. サンギヤ（１３）と、遊星ギヤ（１４，１９）と、リングギヤ（１７，２２）とは、全て実質的に同一平面内に配置されたことを特徴とする、請求項２もしくは３に記載の遊星差動伝動装置。   The planet according to claim 2 or 3, characterized in that the sun gear (13), the planetary gear (14, 19) and the ring gear (17, 22) are all arranged substantially in the same plane. Differential transmission. 四つのインナ遊星ギヤ（１４）と、四つのアウタ遊星ギヤ（１９）とが設けられていることを特徴とする、請求項１〜４の何れか一項に記載の遊星差動伝動装置。   The planetary differential transmission device according to any one of claims 1 to 4, wherein four inner planetary gears (14) and four outer planetary gears (19) are provided. 前記遊星差動伝動装置は、遊星差動伝動装置を固定するため、およびパークロック機能を提供するために、ハウジング（２１）に対して遊星ギヤ列の要素を制止させる係合可能なロック爪（２４）をさらに具えることを特徴とする、請求項１〜５の何れか一項に記載の遊星差動伝動装置。   The planetary differential transmission includes an engageable lock pawl (which locks the planetary gear train element against the housing (21) in order to fix the planetary differential transmission and to provide a park lock function. 24) The planetary differential transmission device according to any one of claims 1 to 5, further comprising: 24). 前記ロック爪（２４）は、アウタリングギヤ（２２）に係合することを特徴とする、請求項６に記載の遊星差動伝動装置。   The planetary differential transmission according to claim 6, wherein the lock claw (24) is engaged with the outer ring gear (22). サンギヤ（１３）は３３歯を有し、インナ遊星ギヤ（１４）は２６歯を有し、インナリングギヤ（１７）はその内側に８７歯およびその外側に１０３歯を有し、アウタ遊星ギヤ（１９）は１９歯を有し、アウタリングギヤ（２２）は１４１歯を有することを特徴とする、請求項１〜７の何れか一項に記載の遊星差動伝動装置。   The sun gear (13) has 33 teeth, the inner planetary gear (14) has 26 teeth, the inner ring gear (17) has 87 teeth inside and 103 teeth outside, and the outer planetary gear (19 ) Has 19 teeth and the outer ring gear (22) has 141 teeth, the planetary differential transmission device according to any one of claims 1 to 7.
JP2007526547A 2004-06-08 2005-06-08 Planetary differential transmission Pending JP2008501920A (en)

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GBGB0412736.1A GB0412736D0 (en) 2004-06-08 2004-06-08 An electrically driven single speed differential transmission
PCT/GB2005/002286 WO2005120877A1 (en) 2004-06-08 2005-06-08 Epicyclic differential transmission

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113892002A (en) * 2019-04-23 2022-01-04 采埃孚股份公司 Transmission and vehicle with transmission

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007050205A1 (en) * 2007-10-20 2009-04-23 Schaeffler Kg Differential gear with lightweight support parts and visco-coupling
US20090107741A1 (en) * 2007-10-25 2009-04-30 Textron Inc. Limited Slip Differential For Electric Vehicle
DE102009026704A1 (en) 2009-06-04 2010-12-09 Zf Friedrichshafen Ag Lubricating device for a planetary gear
DE102009026703A1 (en) * 2009-06-04 2010-12-09 Zf Friedrichshafen Ag Wheelset arrangement of a planetary gear
US8366581B2 (en) * 2010-06-09 2013-02-05 GM Global Technology Operations LLC Multi-speed transmission having stacked planetary gear sets
US8769819B2 (en) 2011-10-14 2014-07-08 Gm Global Technology Operations, Llc. Methods of fabricating combination gear for stacked planetary gearset
CN102996781A (en) * 2012-12-27 2013-03-27 宁波广天赛克思液压有限公司 Planet carrier with combination structure
CN104989803A (en) * 2015-08-03 2015-10-21 许奉成 Differential planetary reducer
WO2017063621A1 (en) * 2015-10-13 2017-04-20 Schaeffler Technologies AG & Co. KG Transmission device and electric drive unit comprising a transmission device
DE102017212781A1 (en) 2017-07-25 2019-01-31 Magna powertrain gmbh & co kg transaxles
DE102018213504B3 (en) 2018-08-10 2020-01-16 Magna powertrain gmbh & co kg Transfer case for a motor vehicle
DE102018216251B3 (en) * 2018-09-24 2019-10-10 Engineering Center Steyr Gmbh & Co Kg DRIVE TRAVEL ARRANGEMENT WITH A DECOUPLING UNIT FOR UNPACKING A DRIVE SHAFT FROM A SHAFT
US10982745B2 (en) * 2019-01-15 2021-04-20 GM Global Technology Operations LLC Planetary differential drive system
DE102019203920A1 (en) * 2019-03-22 2020-09-24 Zf Friedrichshafen Ag Wheel head gear for a wheel head of a motor vehicle drive axle and wheel head
CN110173553A (en) * 2019-06-10 2019-08-27 杨巍 Differential mechanism, hub-type differential mechanism and the motor cycle combination with hub-type differential mechanism
DE102019216507A1 (en) * 2019-10-25 2021-04-29 Zf Friedrichshafen Ag Transmission, drivetrain and vehicle with gearbox
DE102019216508A1 (en) * 2019-10-25 2021-04-29 Zf Friedrichshafen Ag Transmission, drivetrain and vehicle with gearbox
DE102021200527A1 (en) 2021-01-21 2022-07-21 Zf Friedrichshafen Ag Drive train for a motor vehicle and motor vehicle with at least one such drive train
DE102021200524A1 (en) 2021-01-21 2022-07-21 Zf Friedrichshafen Ag Drive train for a hybrid vehicle and hybrid vehicle with at least one such drive train
DE102021203412B4 (en) 2021-04-07 2023-08-10 Zf Friedrichshafen Ag Rolling differential gear with step planet, as well as drive train and vehicle with such a gear
DE102021208557A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021208553A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021208559A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021208556A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021208550A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021208555A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021208554A1 (en) 2021-08-06 2023-02-09 Zf Friedrichshafen Ag Transmission and drive train for a vehicle
DE102021133004A1 (en) 2021-12-14 2023-06-15 Schaeffler Technologies AG & Co. KG Parking lock arrangement for a planetary gear and planetary gear with such a parking lock arrangement
DE102022202378A1 (en) * 2022-03-10 2023-09-14 Zf Friedrichshafen Ag Transmission for a vehicle and drive train with such a transmission
DE102022211901A1 (en) 2022-11-10 2024-05-16 Zf Friedrichshafen Ag Transmission for a drive train of a motor vehicle and drive train with such a transmission
DE102022213256B4 (en) 2022-12-08 2024-06-27 Zf Friedrichshafen Ag Transmission for a vehicle and drive train with such a transmission
DE102022213921A1 (en) 2022-12-19 2024-06-20 Zf Friedrichshafen Ag Transmission for a vehicle and drive train with such a transmission

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9117520D0 (en) * 1991-08-14 1991-10-02 Lotus Car Differential unit
JP3538958B2 (en) * 1995-04-19 2004-06-14 アイシン・エィ・ダブリュ株式会社 Drive for electric vehicles
US5718300A (en) * 1995-05-15 1998-02-17 New Venture Gear, Inc. Electric vehicle final drive
US5919109A (en) * 1996-10-16 1999-07-06 Linde Aktiengesellschaft Drive axle with planetary gear
EP1377473B1 (en) * 2001-03-14 2008-07-02 Magna Powertrain USA, Inc. Drive axle for hybrid vehicle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113892002A (en) * 2019-04-23 2022-01-04 采埃孚股份公司 Transmission and vehicle with transmission

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