JPH09119506A - Differential gear - Google Patents
Differential gearInfo
- Publication number
- JPH09119506A JPH09119506A JP29924695A JP29924695A JPH09119506A JP H09119506 A JPH09119506 A JP H09119506A JP 29924695 A JP29924695 A JP 29924695A JP 29924695 A JP29924695 A JP 29924695A JP H09119506 A JPH09119506 A JP H09119506A
- Authority
- JP
- Japan
- Prior art keywords
- output shaft
- transmission
- shaft
- central axis
- torque
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、４輪駆動車のセ
ンタ・デファレンシャルなどに用いられる差動装置に関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential gear used for a center differential of a four-wheel drive vehicle.
【０００２】[0002]
【従来の技術】従来、４輪駆動車においては、エンジン
の駆動力がトランスミッションを介してセンタ・デファ
レンシャルに伝達され、この駆動力が第１出力軸（出力
用回転体）を介して前輪に伝達される一方、第２出力軸
（出力用回転体）を介して後輪に伝達される。そして、
走行中に路面抵抗などの条件により前輪と後輪とに差動
が発生した場合、センタ・デファレンシャルに設けた差
動装置により第１出力軸および第２出力軸へのトルク配
分を最適化している。2. Description of the Related Art Conventionally, in a four-wheel drive vehicle, a driving force of an engine is transmitted to a center differential via a transmission, and this driving force is transmitted to a front wheel via a first output shaft (rotating body for output). On the other hand, it is transmitted to the rear wheels via the second output shaft (rotating body for output). And
When a difference occurs between the front wheels and the rear wheels due to conditions such as road resistance during traveling, the torque distribution to the first output shaft and the second output shaft is optimized by the differential device provided in the center differential. .
【０００３】この差動装置の一例が『ファミリア新型車
の紹介・１９８９年２月発行［マツダ株式会社］』に記
載されている。この文献に記載された差動装置は、１組
の遊星歯車機構を使用し、そのリングギヤを入力部材と
するとともに、キャリヤを前輪側の出力部材とし、か
つ、サンギヤを後輪側の出力部材としたものである。し
たがって、前輪側と後輪側とに対するトルクの分配率
は、遊星歯車機構の回転中心からキャリヤにおける荷重
の作用点の半径（ピニオンに対する荷重の作用点の半径
位置）とサンギヤの半径とに基づいて決まる値に固定さ
れている。そこで、トルク分配率の変更を行うための構
成を特別に設けている。つまり、キャリヤとサンギヤと
の間にビスカスカップリングを配置し、これら両者の間
で差動回転数に応じた粘性流体の粘性抵抗力によってキ
ャリヤとサンギヤとの間、すなわち前輪側と後輪側とで
トルクの伝達を行わせ、遊星歯車機構をいわゆるバイパ
スする形で前後輪の間でトルクが伝達され、これにより
遊星歯車機構によるトルク分配率を実質的に補正するよ
うにしている。An example of this differential device is described in "Introduction of new model of Familia, issued in February 1989 [Mazda Motor Corporation]". The differential device described in this document uses a set of planetary gear mechanisms, and uses the ring gear as an input member, the carrier as a front wheel side output member, and the sun gear as a rear wheel side output member. It was done. Therefore, the torque distribution ratio between the front wheel side and the rear wheel side is based on the radius of the point of action of the load on the carrier from the rotation center of the planetary gear mechanism (the radial position of the point of action of the load on the pinion) and the radius of the sun gear. It is fixed at a fixed value. Therefore, a special configuration for changing the torque distribution ratio is provided. In other words, a viscous coupling is arranged between the carrier and the sun gear, and the viscous resistance force of the viscous fluid corresponding to the differential rotation speed between the carrier and the sun gear, that is, between the front wheel side and the rear wheel side. Torque is transmitted between the front and rear wheels in a form of so-called bypassing the planetary gear mechanism, whereby the torque distribution ratio by the planetary gear mechanism is substantially corrected.
【０００４】[0004]
【発明が解決しようとする課題】上述のように従来の差
動装置は、その構成上、トルク分配率が固定されたもの
であり、これに対してせん断抵抗力や摩擦力によって差
動制限を行うことにより、所定の二部材の間でトルク伝
達を生じさせ、これによりトルクの分配率を変更するよ
うにしている。そのため差動装置の機構上決まるトルク
分配率以外の分配率に設定するには、不可避的に滑りや
せん断抵抗力が生じることになり、このために伝達する
べき動力の一部が熱エネルギとなって消費されてしま
う。また、差動制限を行なう機構の温度上昇やそれに伴
う耐久性の低下、さらには動力の損失などの不都合を生
じる。As described above, the conventional differential device has a fixed torque distribution ratio because of its structure. On the other hand, the differential limit is limited by the shear resistance force or the friction force. By doing so, torque transmission is caused between the predetermined two members, and thereby the torque distribution ratio is changed. Therefore, in order to set a distribution ratio other than the torque distribution ratio determined by the mechanism of the differential gear, slip and shear resistance forces will inevitably occur, and for this reason, part of the power to be transmitted becomes thermal energy. Will be consumed. Further, there arises inconveniences such as an increase in the temperature of the mechanism for limiting the differential, a decrease in durability accompanying it, and a loss of power.
【０００５】この発明は上記事情を背景としてなされた
ものであり、差動を行なう機構自体でトルク分配率の変
更を行なうことのでき、かつ、機構自体の発熱、滑りや
せん断抵抗力の発生を防止できる差動装置を提供するこ
とを目的とするものである。The present invention has been made in view of the above circumstances, and the torque distribution ratio can be changed by the mechanism that performs the differential operation, and the mechanism itself can generate heat, slip, and shear resistance. An object of the present invention is to provide a differential device that can be prevented.
【０００６】そしてこの目的は、対向配置した出力用回
転体の間に、入力用回転体で保持された自転および公転
可能な伝動用回転体を挟持させ、出力用回転体に対する
伝動用回転体のトルク伝達位置を変化できるように構成
することにより達成される。[0006] For this purpose, the rotating body for rotation which can be rotated and revolved and which is held by the rotating body for input is sandwiched between the rotating bodies for outputting which are opposed to each other, and the rotating body for transmitting the rotating body for transmitting the rotating body for output is arranged. This is achieved by making the torque transmission position variable.
【０００７】[0007]
【課題を解決するための手段およびその作用】上記の目
的を達成するために、請求項１に記載した発明は、互い
に対向し、かつ、同一中心軸線上に回転可能に配置され
た一対の出力用回転体と、これら一対の出力用回転体の
互いに対向する伝動面の周辺部分の間に配置され、外周
面を前記各伝動面にトルク伝達可能に接触させた自転可
能な伝動用回転体と、前記伝動用回転体を、前記中心軸
線を中心に公転させる入力部材と、を備えていることを
特徴とする。In order to achieve the above-mentioned object, the invention described in claim 1 is a pair of outputs arranged to face each other and rotatably arranged on the same central axis. A rotary body for rotation, and a rotary body for rotation which is arranged between the peripheral portions of the transmission surfaces of the pair of output rotary bodies which face each other, and whose outer peripheral surface is in contact with each of the transmission surfaces in a torque-transmittable manner. And an input member for revolving the transmission rotary body about the central axis.
【０００８】したがって、請求項１に記載した発明で
は、回転される入力部材のトルクが伝動用回転体、各伝
動面を介して一対の出力用回転体に各々伝達されるか
ら、一対の出力用回転体に対するトルクの分配率は、中
心軸線を中心とする伝動用回転体の外周面と各伝動面と
の接触半径に基づいて決まる。このため、差動を行なう
機構自体で一対の出力用回転体に伝達されるトルクの分
配率を変えることができる。Therefore, in the invention described in claim 1, since the torque of the rotated input member is transmitted to the pair of output rotary bodies through the transmission rotary body and the respective transmission surfaces, the pair of output rotary bodies is transmitted. The torque distribution ratio to the rotating body is determined based on the contact radius between the outer peripheral surface of the transmission rotating body centered on the central axis and each transmission surface. Therefore, the distribution ratio of the torque transmitted to the pair of output rotary members can be changed by the mechanism that performs the differential.
【０００９】また、請求項２に記載した発明は、請求項
１のこの伝動用回転体を、その自転中心軸線が前記中心
軸線を通る平面内で傾動するよう駆動する駆動機構が設
けられていることを特徴とする。According to a second aspect of the present invention, there is provided a drive mechanism for driving the transmission rotary body of the first aspect so that the rotation center axis of the transmission rotation body tilts in a plane passing through the center axis. It is characterized by
【００１０】したがって、請求項２に記載した発明で
は、請求項１と同様の作用がある他、駆動機構を駆動さ
せて伝動用回転体を傾動させれば、伝動用回転体の外周
面と各伝動面との接触半径を変更され、一対の出力用回
転体に伝達されるトルクの分配率を変えることができ
る。Therefore, according to the invention described in claim 2, in addition to the same operation as in claim 1, if the drive mechanism is driven to tilt the transmission rotary body, the outer peripheral surface of the transmission rotary body and the respective outer peripheral surfaces of the transmission rotary body are reduced. The distribution radius of the torque transmitted to the pair of output rotary members can be changed by changing the contact radius with the transmission surface.
【００１１】請求項３に記載した発明は、請求項１の一
対の出力用回転体の回転状態に基づいて前記駆動機構を
作動させるフィードバック機構が設けられていることを
特徴とする。According to a third aspect of the present invention, there is provided a feedback mechanism for operating the drive mechanism based on the rotating states of the pair of output rotary members according to the first aspect.
【００１２】したがって、請求項３に記載した発明で
は、請求項１と同様の作用がある他、フィードバック機
構が第１出力軸と第２出力軸との回転状態を検出し、検
出結果に基づいて駆動機構が作動して伝動用回転体が傾
動し、伝動用回転体と各伝動面との接触半径比が変更さ
れる。Therefore, in the invention described in claim 3, in addition to the same operation as in claim 1, the feedback mechanism detects the rotation state of the first output shaft and the second output shaft, and based on the detection result. The drive mechanism operates to tilt the transmission rotary body, and the contact radius ratio between the transmission rotary body and each transmission surface is changed.
【００１３】[0013]
【００１４】[0014]
【第１実施例】つぎに、この発明を図面に基づいて具体
的に説明する。図１は４輪駆動車のセンタ・デファレン
シャルのハウジング１１の内部に設けられた差動装置Ａ
の一例を示す断面図、図２は図１の差動装置ＡをII−II
線に沿って分割した状態の右側面図である。ハウジング
１１は中心軸線Ｚを中心とする一対の筒部１１Ｂ，１１
Ｃを有し、一対の筒部１１Ｂ，１１Ｃにはそれぞれ中心
軸線Ｚを中心とする軸穴１１Ａ，１１Ｄが設けられてい
る。軸穴１１Ａには軸受１２Ａが固定され、軸穴１１Ｄ
には軸受１２Ｂが固定されている。[First Embodiment] The present invention will be described in detail with reference to the drawings. FIG. 1 shows a differential device A provided inside a housing 11 of a center differential of a four-wheel drive vehicle.
FIG. 2 is a sectional view showing an example of the differential device A of FIG.
It is a right side view of the state divided along the line. The housing 11 has a pair of cylindrical portions 11B and 11 centered on the central axis Z.
The pair of cylindrical portions 11B and 11C has a shaft hole 11A and 11D centered on the central axis Z, respectively. The bearing 12A is fixed to the shaft hole 11A, and the shaft hole 11D
A bearing 12B is fixed to.
【００１５】中心軸線Ｚを中心として回転される円筒状
のデフケース（入力部材）１は中心軸線Ｚと直交する平
面（図示せず）を境として二つに分割された半割り体２
と半割り体３とから構成され、互いの突き合せ面２４，
２６を突き合せた状態において、円周方向に沿って複数
本のボルト６で締め付け固定されている。A cylindrical differential case (input member) 1 rotated about a central axis Z is divided into two halves with a plane (not shown) orthogonal to the central axis Z as a boundary.
And a half-divided body 3, and abutment surfaces 24 of each other,
In the state in which 26 is abutted, it is fastened and fixed by a plurality of bolts 6 along the circumferential direction.
【００１６】半割り体２は第１筒部２Ａと、第１筒部２
Ａの一端側内周に沿って設けられた第１内向き部２Ｂ
と、第１内向き部２Ｂの内周端から筒部１１Ｂ側へ向け
て設けられた第２筒部２Ｃと、第２筒部２Ｃの一端内周
に沿って設けられた第２内向き部２Ｄとを有する。第２
筒部２Ｃは軸穴１１Ａ内に回転自在に挿入され、第２内
向き部２Ｄの外端面が軸受１２の端面に当接されてい
る。半割り体３は第１筒部３Ａと、第１筒部３Ａの一端
側内周に沿って設けられた第１内向き部３Ｂと、第１内
向き部３Ｂの内周端から筒部１１Ｃ側へ向けて設けられ
た第２筒部３Ｃと、第２筒部３Ｃの一端内周に沿って設
けられた第２内向き部３Ｄとを有している。なお、半割
り体２の第１筒部２Ａの外周にはギヤ４が設けられてお
り、図示しないトランスミッションに接続されたギヤ５
をギヤ４に噛み合わせてある。The half-split body 2 includes a first tubular portion 2A and a first tubular portion 2
A first inward portion 2B provided along the inner circumference of one end side of A
And a second tubular portion 2C provided from the inner peripheral end of the first inwardly facing portion 2B toward the tubular portion 11B side, and a second inwardly facing portion provided along one end inner periphery of the second tubular portion 2C. 2D and. Second
The cylindrical portion 2C is rotatably inserted into the shaft hole 11A, and the outer end surface of the second inward portion 2D is in contact with the end surface of the bearing 12. The half-split body 3 includes a first tubular portion 3A, a first inward facing portion 3B provided along an inner circumference of one end of the first tubular portion 3A, and a tubular portion 11C from an inner circumferential end of the first inward facing portion 3B. It has the 2nd cylinder part 3C provided toward the side, and the 2nd inward part 3D provided along one end inner circumference of the 2nd cylinder part 3C. A gear 4 is provided on the outer circumference of the first tubular portion 2A of the half-split body 2, and a gear 5 connected to a transmission (not shown).
Is meshed with the gear 4.
【００１７】第２内向き部２Ｄ，３Ｄには、各々中心軸
線Ｚを中心とする軸穴７，８が設けられており、軸穴
７，８には中心軸線Ｚを中心とする一対の出力用回転
体、つまり第１出力軸９と第２出力軸１０とが各々回転
自在に挿入されている。第１出力軸９は軸受１２Ａによ
り支持されている一方、第２出力軸１０は軸受１２Ｂに
より支持されている。The second inward portions 2D and 3D are respectively provided with shaft holes 7 and 8 centered on the central axis Z, and the shaft holes 7 and 8 are provided with a pair of outputs centered on the central axis Z. The rotating body, that is, the first output shaft 9 and the second output shaft 10 are rotatably inserted. The first output shaft 9 is supported by a bearing 12A, while the second output shaft 10 is supported by a bearing 12B.
【００１８】第１出力軸９と第２出力軸１０との対向部
には、所定間隔をおいて第１ディスク１２および第２デ
ィスク１３が各々設けられている。この第１ディスク１
２と第２ディスク１３とはほぼ同一外径に設定した円盤
状をなしており、互いの対向面には円周方向に沿って伝
動面１４と伝動面１５とが各々設けられている。伝動面
１４と伝動面１５は中心軸線Ｚ方向における断面形状が
円弧状に形成されており、この伝動面１４，１５を形成
する円弧はいずれも図２に示す自転中心軸線Ｂを中心と
した形状である。また、伝動面１４，１５は、その曲
率、内径、外径が共に同一に設定されている。A first disk 12 and a second disk 13 are provided at predetermined intervals at opposing portions of the first output shaft 9 and the second output shaft 10. This first disc 1
The second disk 13 and the second disk 13 have a disk shape having substantially the same outer diameter, and a transmission surface 14 and a transmission surface 15 are provided on the surfaces facing each other along the circumferential direction. The transmission surface 14 and the transmission surface 15 are formed to have an arcuate cross-sectional shape in the central axis Z direction, and the arcs forming the transmission surfaces 14 and 15 are both shaped around the rotation center axis B shown in FIG. Is. Further, the transmission surfaces 14 and 15 have the same curvature, inner diameter, and outer diameter.
【００１９】また、半割り体２の第１内向き部２Ｂの内
端面１６と第１ディスク１２との間、および半割り体３
の第１内向き部３Ｂとの間には、各々環状のスペーサ１
８，１９を介在させてあり、デフケース１に対する第１
ディスク１２および第２ディスク１３の中心軸線Ｚ方向
の位置決めを大まかに行っている。Further, between the inner end surface 16 of the first inward facing portion 2B of the half-split body 2 and the first disk 12, and the half-split body 3.
Of the annular spacers 1 between the first inward facing portions 3B of the
8 and 19 are interposed, and the first with respect to the differential case 1
The positioning of the disk 12 and the second disk 13 in the direction of the central axis Z is roughly performed.
【００２０】一方、半割り体２の第２筒部２Ｃと第１出
力軸９との間にはポンプ２０が設けられている。このポ
ンプ２０はデフケース１と第１出力軸９との円周方向の
相対移動量に基づいて、第１出力軸９と第２出力軸との
回転数差を間接的に検出するためのものである。半割り
体２の第２筒部２Ｃの外周面には円周方向に沿って環状
溝２１が設けられており、環状溝２１は第２内向き部２
Ｄの内部に設けられた油路２２によりポンプ２０に接続
されている。ハウジング１１の筒部１１Ｂには軸穴１１
Ａに開口した油路２３が設けられており、この油路２３
が環状溝２１に接続されている。なお、第２筒部２Ｃの
外周面には環状溝２１の両側にシールリング８０を装着
して環状溝２１のシール性を保っている。On the other hand, a pump 20 is provided between the second cylinder portion 2C of the half body 2 and the first output shaft 9. The pump 20 is for indirectly detecting the rotational speed difference between the first output shaft 9 and the second output shaft based on the relative movement amount of the differential case 1 and the first output shaft 9 in the circumferential direction. is there. An annular groove 21 is provided along the circumferential direction on the outer peripheral surface of the second tubular portion 2C of the half body 2, and the annular groove 21 is the second inward facing portion 2
It is connected to the pump 20 by an oil passage 22 provided inside D. The shaft hole 11 is formed in the cylindrical portion 11B of the housing 11.
An oil passage 23 opened to A is provided.
Are connected to the annular groove 21. Note that seal rings 80 are attached to both sides of the annular groove 21 on the outer peripheral surface of the second tubular portion 2C to maintain the sealing property of the annular groove 21.
【００２１】また、半割り体２にはポンプ２０から突き
合せ面２４に到達する油路２５が設けられており、この
油路２５は図２に示す駆動機構Ｃに接続されている。こ
の駆動機構Ｃは入力軸２９Ａ，２９Ｂを、その中心軸線
Ｂを中心として回転させるためのものである。駆動機構
Ｃは突き合せ面２４と突き合せ面２６とに跨がって設け
られているが、図２の実施例では一方の入力軸２９Ａお
よびこれに対応する駆動機構Ｃのみが示されている。前
記自転中心軸線Ｂは中心軸線Ｚと平行な平面（図示せ
ず）内において、中心軸線Ｚに対して直交して配置され
ている。Further, the half body 2 is provided with an oil passage 25 reaching the abutment surface 24 from the pump 20, and this oil passage 25 is connected to the drive mechanism C shown in FIG. The drive mechanism C is for rotating the input shafts 29A and 29B about the central axis B thereof. The drive mechanism C is provided so as to straddle the abutting surface 24 and the abutting surface 26, but only one input shaft 29A and the corresponding drive mechanism C are shown in the embodiment of FIG. . The rotation center axis B is arranged orthogonal to the center axis Z in a plane (not shown) parallel to the center axis Z.
【００２２】突き合せ面２４，２６に跨がって設けられ
た保持穴２７とシリンダ室２８とは共に中心軸線Ｂを中
心として設けられている。デフケース１内に配置された
入力軸２９Ａは長手方向の両端に断面円形の軸部３０，
３１を有し、軸部３０が保持穴２７内に回転自在に挿入
されている一方、軸部３１は軸穴３２を介してシリンダ
室２８内に回転自在に挿入されている。軸部３０，３１
には各々その中と部位に鍔部３０Ａ，３１Ａが設けられ
ており、鍔部３０Ａ，３１Ａをデフケース１内に対向し
て設けた規制面２Ｂ，２Ｃに当接させ、中心軸線Ｚ方向
における入力軸２９の位置決めを行っている。The holding hole 27 and the cylinder chamber 28, which are provided so as to straddle the abutting surfaces 24, 26, are both provided about the central axis B. The input shaft 29A arranged in the differential case 1 has a shaft portion 30 having a circular cross section at both ends in the longitudinal direction.
The shaft portion 30 is rotatably inserted into the holding hole 27 while the shaft portion 31 is rotatably inserted into the cylinder chamber 28 through the shaft hole 32. Shafts 30, 31
Are provided with flange portions 30A and 31A respectively in and inside thereof, and the flange portions 30A and 31A are brought into contact with the restricting surfaces 2B and 2C provided in the differential case 1 so as to face each other, and input in the central axis Z direction. The shaft 29 is being positioned.
【００２３】軸部３１におけるシリンダ室２８側には、
図３に示すように円周方向の異なる位置にピン３３，３
４が対向して設けられている。また、軸部３１の外周に
は円筒状のドラム３５が相対回転自在に装着されてい
る。このドラム３５は図４に示すように径方向に沿って
分割構成した分割体３６，３７を組み合わせたもので、
その外周面には長手方向に沿って案内溝３８が設けられ
ている。On the cylinder chamber 28 side of the shaft portion 31,
As shown in FIG. 3, the pins 33, 3 are provided at different positions in the circumferential direction.
4 are provided facing each other. Further, a cylindrical drum 35 is mounted on the outer periphery of the shaft portion 31 so as to be relatively rotatable. As shown in FIG. 4, this drum 35 is a combination of divided bodies 36 and 37 which are divided along the radial direction.
A guide groove 38 is provided on the outer peripheral surface along the longitudinal direction.
【００２４】また、ドラム３５の内周面には円周方向の
対向位置から互いに逆方向に１８０度旋回した螺旋溝３
９，４０が設けられており、螺旋溝３９，４０にピン３
３，３４が移動自在に挿入されている。さらに、シリン
ダ室２８の内周面には円周方向の対称位置にピン４１が
設けられており、ピン４１が案内溝３８内へと移動自在
に挿入されている。Further, on the inner peripheral surface of the drum 35, the spiral groove 3 which is turned 180 degrees in the opposite direction from the circumferentially opposed position is formed.
9 and 40 are provided, and the pin 3 is provided in the spiral grooves 39 and 40.
3, 34 are movably inserted. Further, pins 41 are provided on the inner peripheral surface of the cylinder chamber 28 at symmetrical positions in the circumferential direction, and the pins 41 are movably inserted into the guide grooves 38.
【００２５】さらにまた、シリンダ室２８はドラム３５
を隔てて圧力室４２とばね収納室４３とに区分されてお
り、圧力室４２は油路２５に接続されている。ドラム３
５において圧力室４２に面する位置にはシールリング４
４が装着されている。一方、圧力室４３内にはドラム３
５を圧力室４２側へ押圧する圧縮ばね４５が設けられて
いる。なお、シリンダ室２８の内周面においてピン４１
と圧力室４２との間には、リリーフ穴４６が設けられて
いる。したがって、ドラム３５はシリンダ室２８内を中
心軸線Ｂに沿って正逆方向へ移動でき、その結果、案内
溝３９，４０によってピン３３，３４が押されて入力軸
２９Ａが回転することになる。Furthermore, the cylinder chamber 28 has a drum 35.
Are separated from each other by a pressure chamber 42 and a spring accommodating chamber 43, and the pressure chamber 42 is connected to the oil passage 25. Drum 3
5, a seal ring 4 is provided at a position facing the pressure chamber 42.
4 is installed. On the other hand, in the pressure chamber 43, the drum 3
A compression spring 45 that presses 5 toward the pressure chamber 42 is provided. In addition, the pin 41 is provided on the inner peripheral surface of the cylinder chamber 28.
A relief hole 46 is provided between the pressure chamber 42 and the pressure chamber 42. Therefore, the drum 35 can move in the cylinder chamber 28 in the forward and reverse directions along the central axis B, and as a result, the pins 33 and 34 are pushed by the guide grooves 39 and 40 and the input shaft 29A rotates.
【００２６】前記入力軸２９Ａは軸部３０と軸部３１と
を枠体４６で接続してあり、枠体４６は自転中心軸線Ｂ
と平行な一対の構成板４６Ａと、中心軸線Ｂと直交する
一対の構成板４６Ｂとを備えている。また、一対の構成
板４６Ａ同士の対向面には支軸４７の両端が接続され、
支軸４７に対して伝動用回転体、つまり円盤形状の摩擦
ローラ４８が回転自在に取り付けられている。摩擦ロー
ラ４８の外周面は伝達溝１４，１５に対して高圧で当接
している。The input shaft 29A connects the shaft portion 30 and the shaft portion 31 with a frame body 46, and the frame body 46 has a rotation center axis B.
And a pair of constituent plates 46A parallel to the central axis B and a pair of constituent plates 46B orthogonal to the central axis B. Further, both ends of the support shaft 47 are connected to the facing surfaces of the pair of constituent plates 46A,
A transmission rotating body, that is, a disk-shaped friction roller 48 is rotatably attached to the support shaft 47. The outer peripheral surface of the friction roller 48 is in high pressure contact with the transmission grooves 14 and 15.
【００２７】そして、支軸の自転中心軸線Ｔの延長上に
中心軸線Ｚが位置している。したがって、入力軸２９Ａ
が回転されると摩擦ローラ４８は自転中心軸線Ｔが中心
軸線Ｚを通る平面内で、図１の二点鎖線Ｘ，Ｙで示すよ
うに傾動される。さらに、上記入力軸２９Ｂの構成は入
力軸２９Ａと対称であり、入力軸２９Ｂにも駆動機構Ｃ
と同様の駆動機構が設けられていることは勿論である。The center axis Z is located on the extension of the rotation center axis T of the support shaft. Therefore, the input shaft 29A
When is rotated, the friction roller 48 is tilted as shown by the chain double-dashed lines X and Y in FIG. 1 in the plane where the rotation center axis T passes through the center axis Z. Further, the configuration of the input shaft 29B is symmetrical to that of the input shaft 29A, and the drive mechanism C is also attached to the input shaft 29B.
It goes without saying that a drive mechanism similar to the above is provided.
【００２８】なお、半割り体３の第２内向き部３Ｄと第
２出力軸１０のボス部１０Ａとの間には圧力室５０が設
けられており、圧力室５０は、軸穴８の内周面に装着し
たシールリング７７と、ボス部１０Ａの外周面に装着し
たシールリング７８とにより液密に維持されている。そ
して、第２出力軸１０には圧力室５０に接続する油路１
０Ｂが設けられている。この実施例ではポンプ２０、油
路２２，２３，２５などによりフィードバック機構が構
成されている。A pressure chamber 50 is provided between the second inward portion 3D of the half body 3 and the boss portion 10A of the second output shaft 10. The pressure chamber 50 is located inside the shaft hole 8. Liquid-tightness is maintained by a seal ring 77 mounted on the peripheral surface and a seal ring 78 mounted on the outer peripheral surface of the boss portion 10A. The second output shaft 10 has an oil passage 1 connected to the pressure chamber 50.
0B is provided. In this embodiment, the pump 20, the oil passages 22, 23, 25, etc. constitute a feedback mechanism.
【００２９】つぎに、第１実施例の作用を説明する。ま
ず、図示しないエンジンおよびトランスミッションを介
してギヤ５へ駆動力が伝達され、ギヤ５の回転によりデ
フケース１が回転し、入力軸２９Ａ，２９Ｂおよび摩擦
ローラ４８が中心軸線Ｚの周囲を公転する。その結果、
回転されるデフケース１のトルクが摩擦ローラ４８を介
して第１ディスク１２の伝達面１４および第２ディスク
１３の伝達面１５へ各々伝達され、第１出力軸９および
第２出力軸１０が回転して図示しない前輪および後輪が
回転して車両が走行する。ここで、第１出力軸９および
第２出力軸１０に伝達されるトルクの分配率は、中心軸
線Ｚを中心とする摩擦ローラ４８と各伝動面１４，１５
との接触半径比により決定される。Next, the operation of the first embodiment will be described. First, the driving force is transmitted to the gear 5 via an engine and a transmission (not shown), the rotation of the gear 5 causes the differential case 1 to rotate, and the input shafts 29A and 29B and the friction roller 48 revolve around the central axis Z. as a result,
The torque of the rotated differential case 1 is transmitted to the transmission surface 14 of the first disk 12 and the transmission surface 15 of the second disk 13 via the friction roller 48, and the first output shaft 9 and the second output shaft 10 rotate. The front and rear wheels (not shown) rotate to drive the vehicle. Here, the distribution ratio of the torque transmitted to the first output shaft 9 and the second output shaft 10 is the friction roller 48 centered on the central axis Z and the transmission surfaces 14, 15 respectively.
It is determined by the contact radius ratio with.
【００３０】そして、車両の走行中、第１出力軸９と第
２出力軸１０との回転数が等しければ、デフケース１と
第１出力軸９とが一体的に回転するため、圧力室４２の
圧力と、圧縮ばね４５の弾性力による押圧力とが釣り合
っており、摩擦ローラ４８は図１の実線で示す中立位
置、即ち、中心軸線Ｚとほぼ平行な状態にある。したが
って、中心軸線Ｚを中心とする摩擦ローラ４８と各伝動
面１４，１５との接触半径比は均等であり、第１出力軸
９および第２出力軸１０に伝達されるトルク分配率は等
しい状態にある。When the first output shaft 9 and the second output shaft 10 are equal in rotational speed while the vehicle is traveling, the differential case 1 and the first output shaft 9 rotate integrally, so that the pressure chamber 42 The pressure and the pressing force by the elastic force of the compression spring 45 are balanced, and the friction roller 48 is in a neutral position shown by the solid line in FIG. 1, that is, in a state substantially parallel to the central axis Z. Therefore, the contact radius ratio between the friction roller 48 and the respective transmission surfaces 14 and 15 centering on the central axis Z is equal, and the torque distribution ratios transmitted to the first output shaft 9 and the second output shaft 10 are equal. It is in.
【００３１】一方、例えば前輪の回転数が後輪の回転数
よりも低くなって、第１出力軸９と第２出力軸１０とに
差動が発生した場合、摩擦ローラ４８は軸受４９の周囲
を公転しつつ伝動面１４，１５に対して転がり摩擦の状
態となって自転中心軸線Ｔを中心として自転する。On the other hand, for example, when the rotation speed of the front wheels becomes lower than the rotation speed of the rear wheels and a differential is generated between the first output shaft 9 and the second output shaft 10, the friction roller 48 moves around the bearing 49. While revolving around, it becomes a state of rolling friction with respect to the transmission surfaces 14 and 15, and rotates about the rotation center axis line T.
【００３２】すると、デフケース１の回転よりも第１出
力軸９の回転の方が遅くなってポンプ２０により圧力室
４２の油が吸引されてその圧力が低下するため、ドラム
３５が圧力室４２側へ移動されて案内溝３９，４０およ
びピン３３、３４により入力軸２９Ａが中心軸線Ｂを中
心として回転され、摩擦ローラ４８の外周面が伝動面１
４，１５に当接したまま中心軸線Ｚを中心として半径方
向にすべりながら所定角度傾動して停止する。その結
果、例えば図１の二点鎖線Ｘで示すように伝動面１４と
摩擦ローラ４８との接触半径は、第２伝動面１５と摩擦
ローラ４８との接触半径よりも大きくなるため、第１出
力軸９に伝達されるトルクの方が第２出力軸１０に伝達
されるトルクよりも大きくなる。Then, the rotation of the first output shaft 9 is slower than the rotation of the differential case 1, and the oil in the pressure chamber 42 is sucked by the pump 20 and the pressure thereof is lowered, so that the drum 35 is moved to the pressure chamber 42 side. The input shaft 29A is rotated about the central axis B by the guide grooves 39, 40 and the pins 33, 34, and the outer peripheral surface of the friction roller 48 is moved to the transmission surface 1.
While abutting on 4, 4 and 15, while sliding in the radial direction about the central axis Z, the robot tilts by a predetermined angle and stops. As a result, for example, the contact radius between the transmission surface 14 and the friction roller 48 becomes larger than the contact radius between the second transmission surface 15 and the friction roller 48 as indicated by the chain double-dashed line X in FIG. The torque transmitted to the shaft 9 is larger than the torque transmitted to the second output shaft 10.
【００３３】上記とは逆に後輪の回転数が前輪よりも低
くなった場合は第１出力軸９がデフケース１よりも速く
回転し、ポンプ２０の作動により圧力室４２の圧力が圧
縮ばね４５の付勢力を上回り、ドラム３５がばね収納室
４３側へ移動される。その結果、入力軸２９Ａ，２９Ｂ
が回転されて摩擦ローラ４８が前記とは逆の方向に傾動
される。すると、例えば図１の二点鎖線Ｙで示すよう
に、伝動面１４と摩擦ローラ４８との接触半径は、伝動
面１５と摩擦ローラ４８との接触半径よりも小さくな
り、第２出力軸１０に伝達されるトルクの方が第１出力
軸９に伝達されるトルクよりも大きくなる。On the contrary, when the rotational speed of the rear wheel becomes lower than that of the front wheel, the first output shaft 9 rotates faster than the differential case 1, and the pressure of the pressure chamber 42 is compressed by the operation of the pump 20. And the drum 35 is moved to the spring storage chamber 43 side. As a result, the input shafts 29A, 29B
Is rotated and the friction roller 48 is tilted in the opposite direction to the above. Then, as shown by the chain double-dashed line Y in FIG. 1, the contact radius between the transmission surface 14 and the friction roller 48 becomes smaller than the contact radius between the transmission surface 15 and the friction roller 48, and the second output shaft 10 is The torque transmitted is larger than the torque transmitted to the first output shaft 9.
【００３４】図５は差動装置Ａの原理を示す概念図であ
る。第１出力軸９と第２出力軸１０とが同一回転数の場
合は、入力軸２９Ａは中立位置にあり、摩擦ローラ４８
に対する伝動面１４の接触点Ｐから中心軸線Ｚまでの半
径Ｒ0 は、摩擦ローラ４８に対する伝動面１５の接触点
Ｑから中心軸線Ｚまでの半径Ｒ0 と等しい。この場合
は、入力軸２９ＡのトルクＦは第１出力軸９および第出
力軸１０に対してそれぞれｆ＝Ｆ／２ずつに等分配され
る。FIG. 5 is a conceptual diagram showing the principle of the differential gear A. When the first output shaft 9 and the second output shaft 10 have the same rotation speed, the input shaft 29A is in the neutral position and the friction roller 48
The radius R 0 from the contact point P of the transmission surface 14 to the central axis Z with respect to is equal to the radius R 0 from the contact point Q of the transmission surface 15 to the friction roller 48 to the central axis Z. In this case, the torque F of the input shaft 29A is equally distributed to the first output shaft 9 and the first output shaft 10 at f = F / 2.
【００３５】そして、第１出力軸９と第２出力軸１０と
の差動時、入力軸２９Ａが中立位置から角度θ回転され
ると、接触点ＰはΔＲ拡大して半径Ｒ3 となる一方、接
触点ＱはΔＲ縮小して半径Ｒ4 となる。その結果、摩擦
ローラ４８の半径をｒとした場合、第１出力軸９にはＴ
3 ＝ｆ×Ｒ3 ＝ｆ×（Ｒ0 ＋ΔＲ）＝ｆ×（Ｒ0 ＋ｒ・
ｓｉｎθ）のトルクが加わり、第２出力軸１０側にはＴ
4 ＝ｆ×（Ｒ0 −ｒ・ｓｉｎθ）のトルクが加わること
となる。したがって、入力軸２９Ａ，２９Ｂの回転方向
および回転角度を変化させることにより、第１出力軸９
と第２出力軸１０とに伝達されるトルクの分配率を変え
ることができる。つまり、第１実施例では、摩擦ローラ
４８、第１ディスク１２、第２ディスク１３などの機構
が、第１出力軸９および第２出力軸１０にトルクを伝達
するための機能と、伝達されるトルクの分配率の変更機
能とを兼備しているのである。When the input shaft 29A is rotated by the angle θ from the neutral position during the differential between the first output shaft 9 and the second output shaft 10, the contact point P expands by ΔR and becomes the radius R 3. , The contact point Q is reduced by ΔR to a radius R 4 . As a result, when the radius of the friction roller 48 is r, the first output shaft 9 has T
3 = f × R 3 = f × (R 0 + ΔR) = f × (R 0 + r ·
sin θ) torque is applied to the second output shaft 10 side, and T
A torque of 4 = f × (R 0 −r · sin θ) is applied. Therefore, by changing the rotation direction and the rotation angle of the input shafts 29A and 29B, the first output shaft 9
The distribution ratio of the torque transmitted to the second output shaft 10 can be changed. That is, in the first embodiment, the mechanism such as the friction roller 48, the first disc 12, the second disc 13 and the like are transmitted with the function of transmitting torque to the first output shaft 9 and the second output shaft 10. It also has the function of changing the torque distribution ratio.
【００３６】なお、圧力室４２の圧力が過剰に上昇した
場合、シールリング４４がリリーフ穴４６よりも圧縮ば
ね４５側へ移動した時点で圧力室４２の油をリリーフ穴
４６から吐き出すことにより、圧力室４２内の圧力上昇
を抑制してトルク分配率の変更機能を維持する。When the pressure in the pressure chamber 42 rises excessively, the oil in the pressure chamber 42 is discharged from the relief hole 46 when the seal ring 44 moves to the compression spring 45 side of the relief hole 46, and the pressure is reduced. The function of changing the torque distribution ratio is maintained by suppressing the pressure increase in the chamber 42.
【００３７】このように、第１実施例においては摩擦ロ
ーラ４８を傾動させることにより、伝動面１４に対する
摩擦ローラ４８の接触半径比と、伝動面１５に対する摩
擦ローラ４８の接触半径比とを変更すれば、差動を行な
う機構自体で第１出力軸９と第２出力軸１０とに伝達す
るトルクの分配率を任意に変更できるし、摩擦ローラ４
８と各伝動面１４，１５との当接面には、中心軸線Ｚを
中心とした円周方向の滑りやせん断抵抗力の発生や発熱
がおきにくく、摩擦ローラ４８、第１ディスク１２、第
２ディスク１３などの機構の耐久性が向上されるし、動
力の熱エネルギー化が抑制されて動力損失が防止される
効果がある。As described above, in the first embodiment, by tilting the friction roller 48, the contact radius ratio of the friction roller 48 to the transmission surface 14 and the contact radius ratio of the friction roller 48 to the transmission surface 15 can be changed. For example, the distribution mechanism of the torque that is transmitted to the first output shaft 9 and the second output shaft 10 can be arbitrarily changed by the mechanism that performs the differential operation, and the friction roller 4 can be used.
8 does not easily generate circumferential friction around the central axis Z, shear resistance, or heat generation on the contact surfaces between the friction roller 48, the first disk 12, and the contact surfaces between the transmission surfaces 14 and 15. The durability of the mechanism such as the 2 disk 13 is improved, and the heat energy of the power is suppressed, and the power loss is prevented.
【００３８】また、本実施例で摩擦ローラ４８を傾動し
た際、摩擦ローラ４８の外周面の当接部分の移動軌跡が
伝動面１４，１５の断面形状と一致しているため、摩擦
ローラ４８の傾動動作が円滑に行われ、トルク分配機能
が一層向上される効果がある。さらに、本実施例では、
フィードバック機構が設けられているから、第１出力軸
９と第２出力軸１０との回転状態に基づいて自動的に摩
擦ローラ４８を傾動させることができ、第１出力軸９と
第２出力軸１０との回転状態に変化が発生した場合、そ
の変化に即して自動的にトルク分配率の変更を行なえる
効果もある。Further, when the friction roller 48 is tilted in this embodiment, the movement locus of the abutting portion of the outer peripheral surface of the friction roller 48 coincides with the cross-sectional shape of the transmission surfaces 14 and 15. The tilting operation is smoothly performed, and the torque distribution function is further improved. Further, in this embodiment,
Since the feedback mechanism is provided, the friction roller 48 can be automatically tilted based on the rotation states of the first output shaft 9 and the second output shaft 10, and the first output shaft 9 and the second output shaft 10 can be tilted. When a change occurs in the rotational state with respect to 10, the torque distribution ratio can be automatically changed in accordance with the change.
【００３９】[0039]
【第２実施例】図６は４輪駆動車のセンタ・デファレン
シャルのハウジング５５の内部に設けられた差動装置Ｗ
の一例を示す断面図、図７は図６の差動装置ＷをVII −
VII 線に沿って分割した状態の右側面図であり、図１と
同様の構成部分については同一の符号を用いている。ハ
ウジング５５は中心軸線Ｚを中心とする一対の筒部５５
Ａ，５５Ｂを有し、一対の筒部５５Ａ，５５Ｂにはそれ
ぞれ内周側に内向き部５５Ｃ，５５Ｄを備えている。内
向き部５５Ｃ，５５Ｄには中心軸線Ｚを中心とする軸穴
５８，６１が各々設けられている一方、筒部５５Ｃの内
周面には軸受１２が固定され、筒部５５Ｂの内周面には
軸受１３が固定されている。[Second Embodiment] FIG. 6 shows a differential device W provided inside a center differential housing 55 of a four-wheel drive vehicle.
FIG. 7 is a sectional view showing an example of the differential unit W of FIG.
FIG. 7 is a right side view of a state in which it is divided along line VII, and the same reference numerals are used for the same components as in FIG. 1. The housing 55 has a pair of cylindrical portions 55 centered on the central axis Z.
A and 55B, and the pair of cylindrical portions 55A and 55B are respectively provided with inwardly facing portions 55C and 55D on the inner peripheral side. The inward portions 55C and 55D are provided with shaft holes 58 and 61 centered on the central axis Z, respectively, while the bearing 12 is fixed to the inner peripheral surface of the cylindrical portion 55C and the inner peripheral surface of the cylindrical portion 55B. A bearing 13 is fixed to the.
【００４０】中心軸線Ｚを中心として回転されるデフケ
ース（入力部材）５１は、中心軸線Ｚと直交する平面
（図示せず）を境として二つに分割された半割り体５２
と半割り体５３とから構成されている。The differential case (input member) 51 rotated about the central axis Z is divided into two halves 52 with a plane (not shown) orthogonal to the central axis Z as a boundary.
And a half body 53.
【００４１】半割り体５２は第１筒部５２Ａと、第１筒
部５２Ａの一端側内周に沿って設けられた内向き部５２
Ｂと、内向き部５２Ｂの内周端から軸受１２側へ向けて
設けられた第２筒部５４とを有する。第２筒部５４は筒
部５５Ａ内へと回転自在に挿入され、第２筒部５４の外
端面が軸受１２の端面に当接されている。The half-split body 52 includes a first tubular portion 52A and an inwardly facing portion 52 provided along the inner circumference of one end side of the first tubular portion 52A.
B, and the second tubular portion 54 provided from the inner peripheral end of the inward facing portion 52B toward the bearing 12 side. The second tubular portion 54 is rotatably inserted into the tubular portion 55A, and the outer end surface of the second tubular portion 54 is in contact with the end surface of the bearing 12.
【００４２】半割り体５３は第１筒部５３Ａと、第１筒
部５３Ａの一端側内周に沿って設けられた第１内向き部
５３Ｂと、第１内向き部５３Ｂの内周端から軸受１３側
へ向けて設けられた第２筒部５３Ｃと、第２筒部５３Ｃ
の内周に沿って設けられた第２内向き部５６とを有す
る。第２筒部５３Ｃはハウジンング５５の第１筒部５５
Ｂ内へと回転自在に挿入され、第２内向き部５６の端面
が軸受１２Ｂの端面に当接している。The half-split body 53 includes a first cylindrical portion 53A, a first inward facing portion 53B provided along the inner circumference of one end of the first cylindrical portion 53A, and an inner circumferential end of the first inward facing portion 53B. A second tubular portion 53C provided toward the bearing 13 side, and a second tubular portion 53C
And a second inward facing portion 56 provided along the inner circumference of the. The second tubular portion 53C is the first tubular portion 55 of the housing 55.
It is rotatably inserted into B, and the end face of the second inward portion 56 is in contact with the end face of the bearing 12B.
【００４３】前記第２筒部５４には軸穴５９が設けら
れ、第２内向き部５６には軸穴６０が設けられており、
軸穴５８，５９には第１出力軸９が回転自在に挿入さ
れ、軸穴６０，６１には第２出力軸１０が回転自在に挿
入されている。The second cylindrical portion 54 is provided with a shaft hole 59, and the second inward portion 56 is provided with a shaft hole 60.
The first output shaft 9 is rotatably inserted into the shaft holes 58 and 59, and the second output shaft 10 is rotatably inserted into the shaft holes 60 and 61.
【００４４】ハウジング５５には、軸穴５８に臨む位置
にポンプ６２が設けられているとともに、ポンプ６２に
接続する油路６３及び油路６４が設けられている。油路
６４の一端は筒部５５Ａの内周面まで到達している。ポ
ンプ６２は環状のプレート６５により固定されている。The housing 55 is provided with a pump 62 at a position facing the shaft hole 58, and an oil passage 63 and an oil passage 64 connected to the pump 62. One end of the oil passage 64 reaches the inner peripheral surface of the tubular portion 55A. The pump 62 is fixed by an annular plate 65.
【００４５】一方、内向き部５５Ｄには、軸穴６１に臨
む位置にポンプ６６が設けられているとともに、ポンプ
６６に接続する油路６７及び油路６８が設けられてい
る。油路６８の一端は筒部５５Ｂの内周面に到達してい
る。ポンプ６６は環状のプレート６９により固定されて
いる。なお、油路６８の他の経路にはリリーフバルブ７
０が設けられている。On the other hand, the inward portion 55D is provided with a pump 66 at a position facing the shaft hole 61, and an oil passage 67 and an oil passage 68 connected to the pump 66. One end of the oil passage 68 reaches the inner peripheral surface of the tubular portion 55B. The pump 66 is fixed by an annular plate 69. In addition, the relief valve 7 is provided in the other path of the oil path 68.
0 is provided.
【００４６】前記半割り体５２の第２筒部５４の外周面
には円周方向に沿って環状溝７３が設けられており、環
状溝７３から当接面２４に到達する油路７１が設けられ
ている。環状溝７３は油路６４に接続されている。ま
た、半割り体５３の第２筒部５３Ｃの外周面には環状溝
７４が設けられており、環状溝７４から突き合せ面２６
に到達する油路７２が設けられている。環状溝７４は油
路６８におけるポンプ６６とリリーフバルブ７０との間
に相当する位置へと接続されている。なお、油路７１と
油路７２とは、実際は円周方向の位相が異なる位置に配
置されているが図面では便宜上同一位相として示してい
る。An annular groove 73 is provided along the circumferential direction on the outer peripheral surface of the second tubular portion 54 of the half-split body 52, and an oil passage 71 reaching from the annular groove 73 to the contact surface 24 is provided. Has been. The annular groove 73 is connected to the oil passage 64. Further, an annular groove 74 is provided on the outer peripheral surface of the second tubular portion 53C of the half body 53, and the abutment surface 26 is formed from the annular groove 74.
Is provided with an oil passage 72. The annular groove 74 is connected to the oil passage 68 at a position between the pump 66 and the relief valve 70. Although the oil passage 71 and the oil passage 72 are actually arranged at positions where the phases in the circumferential direction are different, they are shown as the same phase for convenience in the drawings.
【００４７】図７はデフケース１に設けた駆動機構Ｅお
よび入力軸２９Ａ，２９Ｂの構成を示す。図２と同一の
構成部分については同一の符号で示されている。シリン
ダ室２８にはドラム３５の両側に圧力室７４，７５が設
けられており、圧力室７４は油路７１に接続されてい
る。圧力室７５は油路７６を介して油路７２に接続され
ている。ドラム３５の両側にはシールリング４４がそれ
ぞれ設けられている。なお、軸穴６０の内周および第２
出力軸１０のボス部１０Ａにはシールリング７７，７８
が設けられており、圧力室５０を液密に維持している。
第２実施例では、ポンプ６２，６６、油路６３，６４，
６７，７１，７２，６８などによりフィードバック機構
を構成している。FIG. 7 shows the structure of the drive mechanism E and the input shafts 29A and 29B provided on the differential case 1. The same components as those in FIG. 2 are designated by the same reference numerals. The cylinder chamber 28 is provided with pressure chambers 74 and 75 on both sides of the drum 35, and the pressure chamber 74 is connected to the oil passage 71. The pressure chamber 75 is connected to the oil passage 72 via an oil passage 76. Seal rings 44 are provided on both sides of the drum 35, respectively. The inner circumference of the shaft hole 60 and the second
A seal ring 77, 78 is provided on the boss portion 10A of the output shaft 10.
Is provided to maintain the pressure chamber 50 liquid-tight.
In the second embodiment, the pumps 62, 66, the oil passages 63, 64,
A feedback mechanism is composed of 67, 71, 72, 68 and the like.
【００４８】つぎに、第２実施例の作用を説明する。ま
ず、図示しないエンジンおよびトランスミッションを介
してギヤ５へ駆動力が伝達され、ギヤ５の回転によりデ
フケース５１が回転し、入力軸２９および摩擦ローラ４
８が公転する。その結果、デフケース５１の回転トルク
が摩擦ローラ４８を介して第１ディスク１２、第２ディ
スク１３へ伝達され、第１出力軸９および第２出力軸１
０が回転して図示しない前輪および後輪が回転して車両
が走行する。ここで、第１出力軸９および第２出力軸１
０に伝達されるトルクの分配率は、中心軸線Ｚを中心と
する摩擦ローラ４８の外周面と各伝動面１４，１５との
接触半径比により決定される。Next, the operation of the second embodiment will be described. First, the driving force is transmitted to the gear 5 via an engine and a transmission (not shown), and the rotation of the gear 5 causes the differential case 51 to rotate, so that the input shaft 29 and the friction roller 4 are rotated.
8 revolves around. As a result, the rotational torque of the differential case 51 is transmitted to the first disk 12 and the second disk 13 via the friction roller 48, and the first output shaft 9 and the second output shaft 1 are transmitted.
0 rotates and the front wheels and rear wheels (not shown) rotate and the vehicle runs. Here, the first output shaft 9 and the second output shaft 1
The distribution ratio of the torque transmitted to 0 is determined by the contact radius ratio between the outer peripheral surface of the friction roller 48 centering on the central axis Z and the transmission surfaces 14 and 15.
【００４９】走行中、ポンプ６２，６６は第１出力軸
９、第２出力軸１０の回転数を別個に検出しており、第
１出力軸９と第２出力軸１０との回転数が等しい場合
は、圧力室７４と圧力室７５との圧力が等しい状態に維
持される。したがって、摩擦ローラ４８は図５のように
中立位置、即ち、中心軸線Ｚとほぼ平行な状態でトルク
の伝達を行う。したがって、第１出力軸９、第２出力軸
１０に伝達されるトルクの分配率は均等な状態にある。During traveling, the pumps 62 and 66 detect the rotational speeds of the first output shaft 9 and the second output shaft 10 separately, and the rotational speeds of the first output shaft 9 and the second output shaft 10 are equal. In this case, the pressures of the pressure chamber 74 and the pressure chamber 75 are maintained in the same state. Therefore, the friction roller 48 transmits the torque in the neutral position, that is, in a state substantially parallel to the central axis Z as shown in FIG. Therefore, the distribution ratio of the torque transmitted to the first output shaft 9 and the second output shaft 10 is in a uniform state.
【００５０】一方、車両の走行中、第１出力軸９と第２
出力軸１０とに差動が生じた場合、ポンプ６２，６６の
作動圧が不均等となり、圧力室７４と圧力室７５とに圧
力差が生じ、ドラム３５がシリンダ室２８内でいずれか
一方へ移動する。その結果、実施例１と同様の作用によ
り入力軸２９Ａ，２９Ｂが軸部３０，３１を中心として
所定角度回転し、例えば二点鎖線Ｘまたは二点鎖線Ｙの
位置で停止すれば、第１実施例と同様に第１出力軸９と
第２出力軸１０に対する伝達トルクの分配率が変更され
る。On the other hand, while the vehicle is traveling, the first output shaft 9 and the second output shaft 9
When a differential occurs between the output shaft 10 and the pump 62, 66, the operating pressures of the pumps 62 and 66 become uneven, and a pressure difference occurs between the pressure chamber 74 and the pressure chamber 75. Moving. As a result, if the input shafts 29A and 29B rotate about the shaft portions 30 and 31 by a predetermined angle by the same action as in the first embodiment and stop at the position of the chain double-dashed line X or the chain double-dashed line Y, the first embodiment Similar to the example, the distribution ratio of the transmission torque to the first output shaft 9 and the second output shaft 10 is changed.
【００５１】伝達トルクの分配率の変更後は、出力軸
９，１０の回転数が等しくなった時点でポンプ６２，６
６の作動圧が等しくなり、入力軸２９Ａ，２９Ｂが中立
位置へと復帰することとなる。After changing the distribution ratio of the transmission torque, the pumps 62 and 6 are pumped when the rotational speeds of the output shafts 9 and 10 become equal.
The operating pressures of 6 become equal, and the input shafts 29A and 29B return to the neutral position.
【００５２】このように、第２実施例においても第１実
施例と同様の効果を得ることができる。また、油路６８
内の圧力が過剰に高圧となった場合は、リリーフバルブ
７０によりこの圧力を調節することで調整機能を確保す
ることができる。なお、第１実施例および第２実施例は
２輪駆動の前輪または後輪のデファレンシャルに用いる
ことも可能である。As described above, also in the second embodiment, the same effect as in the first embodiment can be obtained. In addition, the oil passage 68
When the internal pressure becomes excessively high, the adjusting function can be ensured by adjusting this pressure by the relief valve 70. The first and second embodiments can also be used for a two-wheel drive front wheel or rear wheel differential.
【００５３】さらにまた、第１実施例および第２実施例
において、各伝動面の断面形状は円弧形状でなく平坦面
でもよい。この場合、出力用回転体が伝動用回転体の傾
動に追従して中心軸線方向に沿って移動する構成として
おき、伝動面と伝動用回転体の外周面との当接圧力が一
定の値に維持することは勿論である。さらにまた、伝動
用回転体は、その外周面形状が円形であれば円盤状以外
の形状であってもよい。Furthermore, in the first and second embodiments, the cross-sectional shape of each transmission surface may be a flat surface instead of an arc shape. In this case, the output rotor is configured to move along the central axis direction following the tilt of the transmission rotor, and the contact pressure between the transmission surface and the outer peripheral surface of the transmission rotor is kept constant. Of course to maintain. Furthermore, the transmission rotating body may have a shape other than a disk shape as long as the outer peripheral surface shape is circular.
【００５４】[0054]
【発明の効果】以上説明したように請求項１の発明によ
れば、回転される入力部材のトルクが伝動用回転体の各
伝動面を介して一対の出力用回転体に各々伝達されるか
ら、一対の出力用回転体に対するトルクの分配率は、中
心軸線を中心とする伝動用回転体の外周面と各伝動面と
の接触半径に基づいて決まる。As described above, according to the invention of claim 1, the torque of the rotated input member is transmitted to each of the pair of output rotary bodies through the respective transmission surfaces of the transmission rotary body. The distribution ratio of torque to the pair of output rotary bodies is determined based on the contact radius between the outer peripheral surface of the transmission rotary body centered on the central axis and each transmission surface.
【００５５】したがって、差動を行なう機構自体でトル
クの分配率を変更できる上、伝動用回転体と各伝動面と
の当接面に発熱や滑りおよびせん断抵抗力が発生しにく
く、伝動用回転体、一対の出力用回転体などの機構の耐
久性が向上される上、動力の熱エネルギー化が抑制され
動力損失が防止される効果がある。Therefore, the torque distribution ratio can be changed by the mechanism for performing the differential, and heat generation, slippage, and shear resistance are less likely to occur on the contact surfaces between the transmission rotating body and each transmission surface, and the transmission rotation can be prevented. The durability of the body and a mechanism such as the pair of output rotary bodies is improved, and further, there is an effect that the heat energy of the power is suppressed and the power loss is prevented.
【００５６】また、請求項２の発明によれば、請求項１
と同様の効果を得られる他、駆動機構を駆動して伝動用
回転体を傾動させ、伝動用回転体の外周面と各伝動面と
の接触半径を変更することにより、一対の出力用回転体
に伝達されるトルクの分配率を任意に変更できる効果が
ある。According to the invention of claim 2, according to claim 1,
In addition to obtaining the same effect as in the above, the drive mechanism is driven to tilt the transmission rotary body, and the contact radius between the outer peripheral surface of the transmission rotary body and each transmission surface is changed to thereby produce a pair of output rotary bodies. The effect is that the distribution ratio of the torque transmitted to the can be arbitrarily changed.
【００５７】さらに、請求項３の発明によれば、請求項
１と同様の効果を得られる他、フィードバック機構が第
１出力軸と第２出力軸との回転状態の変化に即して自動
的に駆動機構が作動して伝動用回転体を傾動させ、トル
クの分配率を変更できる効果がある。Further, according to the invention of claim 3, the same effect as that of claim 1 can be obtained, and the feedback mechanism automatically operates in accordance with the change of the rotational states of the first output shaft and the second output shaft. In addition, there is an effect that the drive mechanism operates to tilt the transmission rotary body and change the torque distribution ratio.
【図１】この発明の第１実施例に係る差動装置を示す正
面断面図である。FIG. 1 is a front sectional view showing a differential device according to a first embodiment of the present invention.
【図２】図１の差動装置をII−II線で分割した状態の右
側面図である。FIG. 2 is a right side view of the differential device shown in FIG. 1 taken along line II-II.
【図３】第１実施例に用いる駆動機構の構成を示す断面
図である。FIG. 3 is a cross-sectional view showing a configuration of a drive mechanism used in the first embodiment.
【図４】第１実施例で用いるドラムの分解斜視図であ
る。FIG. 4 is an exploded perspective view of a drum used in the first embodiment.
【図５】第１実施例に係る差動装置の原理を説明する概
念図である。FIG. 5 is a conceptual diagram illustrating the principle of the differential device according to the first embodiment.
【図６】この発明の第２実施例に係る差動装置を示す正
面断面図である。FIG. 6 is a front sectional view showing a differential device according to a second embodiment of the present invention.
【図７】図６の差動装置をVII −VII 線で分割した状態
の右側面図である。FIG. 7 is a right side view of the differential device shown in FIG. 6 divided along line VII-VII.
１，５１ デフケース（入力部材） ９ 第１出力軸（出力用回転体） １０ 第２出力軸（出力用回転体） １４，１５ 伝動面 ４８ 摩擦ローラ（伝動用回転体） ２０，６２，６６ ポンプ（フィードバック機構） ２２，２５，６３，６４，６７，６８，７１，７２ 油
路（フィードバック機構） Ｃ，Ｅ 駆動機構 Ｚ 中心軸線1,51 Differential case (input member) 9 1st output shaft (rotating body for output) 10 2nd output shaft (rotating body for output) 14,15 Transmission surface 48 Friction roller (rotation body for transmission) 20,62,66 Pump (Feedback mechanism) 22, 25, 63, 64, 67, 68, 71, 72 Oil passage (feedback mechanism) C, E Drive mechanism Z Central axis
Claims (3)
回転可能に配置された一対の出力用回転体と、 これら一対の出力用回転体の互いに対向する伝動面の周
辺部分の間に配置され、外周面を前記各伝動面にトルク
伝達可能に接触させた自転可能な伝動用回転体と、 前記伝動用回転体を、前記中心軸線を中心に公転させる
入力部材とを備えていることを特徴とする差動装置。1. A pair of output rotary members that are arranged to face each other and are rotatable on the same central axis, and a pair of output rotary members that are arranged between peripheral portions of transmission surfaces of the pair of output rotary members that face each other. And a rotation body for rotation which has an outer peripheral surface in contact with each of the transmission surfaces so that torque can be transmitted, and an input member which revolves the rotation body for transmission about the central axis. Characteristic differential device.
が前記中心軸線を通る平面内で傾動するよう駆動する駆
動機構が設けられていることを特徴とする請求項１に記
載の差動装置。2. The differential according to claim 1, further comprising a drive mechanism for driving the transmission rotary body so that the rotation center axis of the transmission rotation body tilts in a plane passing through the center axis. apparatus.
づいて前記駆動機構を作動させるフィードバック機構が
設けられていることを特徴とする請求項１に記載の差動
装置。3. The differential device according to claim 1, further comprising a feedback mechanism that operates the drive mechanism based on a rotation state of the pair of output rotary bodies.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29924695A JPH09119506A (en) | 1995-10-23 | 1995-10-23 | Differential gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29924695A JPH09119506A (en) | 1995-10-23 | 1995-10-23 | Differential gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09119506A true JPH09119506A (en) | 1997-05-06 |
Family
ID=17870050
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP29924695A Pending JPH09119506A (en) | 1995-10-23 | 1995-10-23 | Differential gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09119506A (en) |
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| US6464614B2 (en) * | 1998-09-11 | 2002-10-15 | Torotrak (Development) Limited | Hydraulic supply for infinitely variable transmission |
| US7125361B2 (en) * | 2000-12-13 | 2006-10-24 | Toyota Jidosha Kabushiki Kaisha | Toroidal type continuously variable transmission |
| FR2918433A1 (en) * | 2007-07-05 | 2009-01-09 | Peugeot Citroen Automobiles Sa | Transmission component for e.g. automobile, has hydraulic control system for controlling inclination of pivoting axis of each roller to control distribution of engine torques transmitted to disks |
| WO2010140433A1 (en) * | 2009-06-03 | 2010-12-09 | 日産自動車株式会社 | Two/four-wheel drive mode shift controller for traction-transmitting part time four-wheel drive vehicl and method for controlling the same |
| WO2013109723A1 (en) * | 2012-01-19 | 2013-07-25 | Dana Limited | Tilting ball variator continuously variable transmission torque vectoring device |
| US8986150B2 (en) | 2012-09-07 | 2015-03-24 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| FR3014159A3 (en) * | 2013-12-03 | 2015-06-05 | Renault Sa | "BALL DIFFERENTIAL FOR THE TRANSMISSION OF THE MOTOR TORQUE TO THE DRIVING WHEELS OF A VEHICLE" |
| US9052000B2 (en) | 2012-09-07 | 2015-06-09 | Dana Limited | Ball type CVT/IVT including planetary gear sets |
| US9194472B2 (en) | 2013-03-14 | 2015-11-24 | Dana Limited | Ball type continuously variable transmission |
| US9353842B2 (en) | 2012-09-07 | 2016-05-31 | Dana Limited | Ball type CVT with powersplit paths |
| US9404414B2 (en) | 2013-02-08 | 2016-08-02 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
| US9541179B2 (en) | 2012-02-15 | 2017-01-10 | Dana Limited | Transmission and driveline having a tilting ball variator continuously variable transmission |
| US9551404B2 (en) | 2013-03-14 | 2017-01-24 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variator drive |
| US9556941B2 (en) | 2012-09-06 | 2017-01-31 | Dana Limited | Transmission having a continuously or infinitely variable variator drive |
| US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
| US9599204B2 (en) | 2012-09-07 | 2017-03-21 | Dana Limited | Ball type CVT with output coupled powerpaths |
| US9638296B2 (en) | 2012-09-07 | 2017-05-02 | Dana Limited | Ball type CVT including a direct drive mode |
| US9777815B2 (en) | 2013-06-06 | 2017-10-03 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
| US10030748B2 (en) | 2012-11-17 | 2018-07-24 | Dana Limited | Continuously variable transmission |
| US10030751B2 (en) | 2013-11-18 | 2018-07-24 | Dana Limited | Infinite variable transmission with planetary gear set |
| US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
| US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
-
1995
- 1995-10-23 JP JP29924695A patent/JPH09119506A/en active Pending
Cited By (34)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6464614B2 (en) * | 1998-09-11 | 2002-10-15 | Torotrak (Development) Limited | Hydraulic supply for infinitely variable transmission |
| US7125361B2 (en) * | 2000-12-13 | 2006-10-24 | Toyota Jidosha Kabushiki Kaisha | Toroidal type continuously variable transmission |
| FR2918433A1 (en) * | 2007-07-05 | 2009-01-09 | Peugeot Citroen Automobiles Sa | Transmission component for e.g. automobile, has hydraulic control system for controlling inclination of pivoting axis of each roller to control distribution of engine torques transmitted to disks |
| WO2010140433A1 (en) * | 2009-06-03 | 2010-12-09 | 日産自動車株式会社 | Two/four-wheel drive mode shift controller for traction-transmitting part time four-wheel drive vehicl and method for controlling the same |
| CN102458899A (en) * | 2009-06-03 | 2012-05-16 | 日产自动车株式会社 | Two/four-wheel drive mode shift controller for traction-transmitting part time four-wheel drive vehicl and method for controlling the same |
| JP5131384B2 (en) * | 2009-06-03 | 2013-01-30 | 日産自動車株式会社 | Two-wheel / four-wheel drive switching control device and control method for traction transmission type part-time four-wheel drive vehicle |
| US8483921B2 (en) | 2009-06-03 | 2013-07-09 | Nissan Motor Co., Ltd. | Two/four-wheel drive mode shift controller for traction-transmitting part time four-wheel drive vehicle and method for controlling the same |
| US9347532B2 (en) | 2012-01-19 | 2016-05-24 | Dana Limited | Tilting ball variator continuously variable transmission torque vectoring device |
| WO2013109723A1 (en) * | 2012-01-19 | 2013-07-25 | Dana Limited | Tilting ball variator continuously variable transmission torque vectoring device |
| US9541179B2 (en) | 2012-02-15 | 2017-01-10 | Dana Limited | Transmission and driveline having a tilting ball variator continuously variable transmission |
| US9556941B2 (en) | 2012-09-06 | 2017-01-31 | Dana Limited | Transmission having a continuously or infinitely variable variator drive |
| US8986150B2 (en) | 2012-09-07 | 2015-03-24 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9689477B2 (en) | 2012-09-07 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9353842B2 (en) | 2012-09-07 | 2016-05-31 | Dana Limited | Ball type CVT with powersplit paths |
| US9416858B2 (en) | 2012-09-07 | 2016-08-16 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9052000B2 (en) | 2012-09-07 | 2015-06-09 | Dana Limited | Ball type CVT/IVT including planetary gear sets |
| US10088026B2 (en) | 2012-09-07 | 2018-10-02 | Dana Limited | Ball type CVT with output coupled powerpaths |
| US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
| US9599204B2 (en) | 2012-09-07 | 2017-03-21 | Dana Limited | Ball type CVT with output coupled powerpaths |
| US10006527B2 (en) | 2012-09-07 | 2018-06-26 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9638296B2 (en) | 2012-09-07 | 2017-05-02 | Dana Limited | Ball type CVT including a direct drive mode |
| US10030748B2 (en) | 2012-11-17 | 2018-07-24 | Dana Limited | Continuously variable transmission |
| US9404414B2 (en) | 2013-02-08 | 2016-08-02 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
| US9644530B2 (en) | 2013-02-08 | 2017-05-09 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
| US9551404B2 (en) | 2013-03-14 | 2017-01-24 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variator drive |
| US9689482B2 (en) | 2013-03-14 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission |
| US9933054B2 (en) | 2013-03-14 | 2018-04-03 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variator drive |
| US9638301B2 (en) | 2013-03-14 | 2017-05-02 | Dana Limited | Ball type continuously variable transmission |
| US9194472B2 (en) | 2013-03-14 | 2015-11-24 | Dana Limited | Ball type continuously variable transmission |
| US9777815B2 (en) | 2013-06-06 | 2017-10-03 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
| US10030751B2 (en) | 2013-11-18 | 2018-07-24 | Dana Limited | Infinite variable transmission with planetary gear set |
| US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
| FR3014159A3 (en) * | 2013-12-03 | 2015-06-05 | Renault Sa | "BALL DIFFERENTIAL FOR THE TRANSMISSION OF THE MOTOR TORQUE TO THE DRIVING WHEELS OF A VEHICLE" |
| US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
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