JP2003294109A - Differential limiting device - Google Patents
Differential limiting deviceInfo
- Publication number
- JP2003294109A JP2003294109A JP2002212124A JP2002212124A JP2003294109A JP 2003294109 A JP2003294109 A JP 2003294109A JP 2002212124 A JP2002212124 A JP 2002212124A JP 2002212124 A JP2002212124 A JP 2002212124A JP 2003294109 A JP2003294109 A JP 2003294109A
- Authority
- JP
- Japan
- Prior art keywords
- differential
- differential limiting
- limiting device
- pinion gear
- case
- 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.)
- Granted
Links
- 230000000670 limiting effect Effects 0.000 title claims abstract description 123
- 230000002093 peripheral effect Effects 0.000 claims description 9
- 230000002829 reductive effect Effects 0.000 description 11
- 239000000463 material Substances 0.000 description 8
- 230000002787 reinforcement Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000010410 layer Substances 0.000 description 2
- 102100023033 Cyclic AMP-dependent transcription factor ATF-2 Human genes 0.000 description 1
- 101100321670 Fagopyrum esculentum FA18 gene Proteins 0.000 description 1
- 101000974934 Homo sapiens Cyclic AMP-dependent transcription factor ATF-2 Proteins 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000009699 differential effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000002356 single layer Substances 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
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- Retarders (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、デフケースの回転
軸に直交して配設されるピニオン軸と該ピニオン軸に軸
支されたピニオンギヤと該ピニオンギヤの両側に傘歯噛
合して差動配分された駆動力を取り出す左右一対のサイ
ドギヤとを備える差動装置の前記デフケースとサイドギ
ヤとの間にて差動制限力を発生させるように構成された
差動制限装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pinion shaft which is arranged orthogonal to the rotation axis of a differential case, a pinion gear which is axially supported by the pinion shaft, and differentially distributed by bevel gear meshing on both sides of the pinion gear. The present invention relates to a differential limiting device configured to generate a differential limiting force between the side gear and the differential case of a differential device including a pair of left and right side gears for extracting the driving force.
【０００２】[0002]
【従来の技術】この種の、デフケースの回転軸に直交し
て配設されるピニオン軸と該ピニオン軸に軸支されたピ
ニオンギヤと該ピニオンギヤの両側に傘歯噛合して差動
配分された駆動力を取り出す左右一対のサイドギヤとを
備える差動装置の前記デフケースとサイドギヤとの間に
て差動制限力を発生させるように構成された差動制限装
置は、格別な制御手段を設けずとも、機械的な機構のみ
で容易に差動制限力を得ることができることから広く採
用されている。図８に示したものは、特公昭４６−８２
０７号公報に開示された差動制限装置で、デフケース１
１０（左右のデフケース１１１、１１２からなる）の回
転駆動力を、デフケース１１０の回転軸に直交して固定
されたピニオン軸１１３に軸支されたピニオンギヤ１１
４と、これの左右両側から傘歯噛合する左右のサイドギ
ヤ１１５、１１６から構成される差動歯車によって、前
記左右のサイドギヤ１１５、１１６にトルク配分して伝
達するものであり、前記ピニオンギヤ１１４と左右のサ
イドギヤ１１５、１１６との間の噛合反力によって互い
に離反するサイドギヤ１１５、１１６がその背面に介設
されたプレッシャプレート１１７、１１８およびテーパ
リング１１９、１２０（それぞれデフケース１１１、１
１２と回転を共にする）に圧接して差動制限力を得るよ
うに構成されるとともに、前記テーパリング１１９、１
２０間に介設されたばね１２１によって牽引されて差動
制限のためのイニシャルトルクを発生するように構成さ
れたものである。2. Description of the Related Art A pinion shaft, which is arranged orthogonally to the rotary shaft of a differential case, a pinion gear which is pivotally supported by the pinion shaft, and a drive which is differentially distributed by meshing with bevel teeth on both sides of the pinion gear. The differential limiting device configured to generate the differential limiting force between the differential case and the side gears of the differential device including the pair of left and right side gears for extracting the force, without providing a special control means, It is widely adopted because it is possible to easily obtain the differential limiting force only by a mechanical mechanism. What is shown in FIG. 8 is the Japanese Examined Patent Publication No. 46-82.
In the differential limiting device disclosed in Japanese Patent Publication No. 07, the differential case 1
A pinion gear 11 axially supported by a pinion shaft 113 fixed at right angles to the rotational axis of the differential case 110 is a rotational driving force of 10 (consisting of the left and right differential cases 111 and 112).
4 and the left and right side gears 115 and 116 which engage with bevel teeth from the left and right sides of the gear 4 to distribute the torque to the left and right side gears 115 and 116 for transmission. Side gears 115 and 116, which are separated from each other by a meshing reaction force with the side gears 115 and 116, and pressure plates 117 and 118 and taper rings 119 and 120 (respectively, the differential cases 111 and 1).
12 to rotate together) to obtain a differential limiting force, and the taper rings 119, 1
It is configured to be pulled by a spring 121 interposed between 20 and to generate an initial torque for limiting the differential.
【０００３】このような構成の差動制限装置によって、
通常の直進走行時にはエンジンからの駆動力によりデフ
ケース１１０からの所定の駆動力を受けてピニオンギヤ
１１４と噛合する左右の各サイドギヤ１１５、１１６に
均等にその駆動力が伝達される。その際、左右の駆動輪
の走行抵抗がほぼ同じであり、ピニオンギヤ１１４は静
止状態にて噛合反力にて各サイドギヤ１１５、１１６を
離反させ、プレッシャプレート１１７、１１８およびテ
ーパリング１１９、１２０を介してデフケース１１０と
の間を一体化させて、強固な駆動力が得られる。また、
走行中の軽度のスリップ時には、ばね１２１によって発
生したイニシャルトルクにより適度の差動制限力が得ら
れ、さらに、車両が泥濘地等の悪路に遭遇して片輪空転
等により過剰な差動作用が発生しようとした場合にも、
ばね１２１による予圧がピニオンギヤ１１４とサイドギ
ヤ１１５、１１６との間に噛合反力を効果的に生じさせ
て、サイドギヤ１１５と１１６とを離反させてデフケー
ス１１１、１１２それぞれとの内壁面との間に差動制限
力を発生させて、低速車輪側にも駆動力が伝達され、悪
路での脱出性能を向上させることができる。With the differential limiting device having such a structure,
During normal straight running, a predetermined driving force from the differential case 110 is received by the driving force from the engine, and the driving force is evenly transmitted to the left and right side gears 115 and 116 meshing with the pinion gear 114. At that time, the running resistances of the left and right drive wheels are substantially the same, and the pinion gear 114 disengages the side gears 115 and 116 from each other by the meshing reaction force in a stationary state, and the side plates 115 and 118 and the taper rings 119 and 120 are interposed therebetween. A strong driving force can be obtained by integrating with the differential case 110. Also,
At the time of a slight slip during traveling, an appropriate differential limiting force is obtained by the initial torque generated by the spring 121. Further, the vehicle encounters a bad road such as a muddy road and one wheel slips excessively, resulting in excessive differential action. If you try to
The preload by the spring 121 effectively causes a meshing reaction force between the pinion gear 114 and the side gears 115 and 116, causing the side gears 115 and 116 to separate from each other, and causing a difference between the inner surfaces of the differential cases 111 and 112. By generating the dynamic limiting force, the driving force is also transmitted to the low speed wheel side, and the escape performance on a rough road can be improved.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、このよ
うな従来の差動制限装置においては、差動制限部材であ
る比較的大径の部品であるプレッシャプレート１１７、
１１８およびテーパリング１１９、１２０等をデフケー
ス１１０内に組み付ける必要があることから、デフケー
ス１１０を軸方向で左右に２分割して左デフケース１１
１と右デフケース１１２とし、差動歯車や差動制限部材
を組み付け収容した後に、左右のデフケース１１１、１
１２を締結ボルト１２２によって締結一体化していた。
そのため、左右のデフケース１１１、１１２における接
合フランジ面に高い加工精度が要求される上に締結ボル
ト等の余分な部品が必要とされ、さらには、デフケース
１１０左右のベアリング取付面やデフケース駆動ギヤ取
付面の精度を確保するため、デフケース１１１、１１２
を仮組みした上での該部加工が必要である等、コストア
ップや作業効率の低下を招いていた。However, in such a conventional differential limiting device, the pressure plate 117, which is a relatively large-diameter component that is a differential limiting member,
Since it is necessary to assemble 118, taper rings 119, 120, etc. in the diff case 110, the diff case 110 is divided into left and right parts in the axial direction, and the left diff case 11
1 and the right diff case 112, after the differential gear and the differential limiting member are assembled and housed, the left and right diff cases 111, 1
12 was fastened and integrated by fastening bolts 122.
Therefore, the joining flange surfaces of the left and right differential cases 111 and 112 require high processing accuracy, and extra parts such as fastening bolts are required. Furthermore, the left and right bearing mounting surfaces of the differential case 110 and the differential case drive gear mounting surface are also required. In order to ensure the accuracy of the differential case 111, 112
Since it is necessary to temporarily assemble the above parts, the cost is increased and the work efficiency is decreased.
【０００５】そこで本発明では、前記従来の差動制限装
置の諸課題を解決して、比較的小さな孔にて差動制限部
材の組付けを可能にして、一体型のデフケースの採用を
容易にした、低コストな差動制限装置を提供することを
目的とする。Therefore, in the present invention, various problems of the conventional differential limiting device are solved, the differential limiting member can be assembled with a relatively small hole, and the integral diff case is easily adopted. Another object of the present invention is to provide a low-cost differential limiting device.
【０００６】[0006]
【課題を解決するための手段】そこで本発明は、デフケ
ースの回転軸に直交して配設されるピニオン軸と該ピニ
オン軸に軸支されたピニオンギヤと該ピニオンギヤの両
側に傘歯噛合して差動配分された駆動力を取り出す左右
一対のサイドギヤとを備える差動装置の前記デフケース
とサイドギヤとの間にて差動制限力を発生させるように
構成された差動制限装置において、前記デフケースを周
面に孔を穿設した一体構造に構成するとともに、前記孔
を、少なくともピニオンギヤおよび差動制限部材が通過
可能な形状に構成したことを特徴とする。また本発明
は、前記差動制限部材が、サイドギヤとデフケースとの
間の円錐面に介設されたことを特徴とする。また本発明
は、前記少なくとも一方のサイドギヤにおける円錐面
を、少なくともピニオンギヤ投影面に対応して切り欠い
たことを特徴とする。また本発明は、前記少なくとも一
方のサイドギヤにおける円錐面を、ピニオンギヤの少な
くとも最小歯数の歯形に対応して切り欠いたことを特徴
とする。また本発明は、前記差動制限部材として、デフ
ケースと一体に回転するテーパリングを配設し、該少な
くとも一方のテーパリングにおける円錐面を、少なくと
もピニオンギヤ投影面に対応して切り欠いたことを特徴
とする。また本発明は、前記テーパリングを円周上で複
数個に分割するとともに、これらの分割部にデフケース
に係止される回止め片を起立形成したことを特徴とす
る。また本発明は、前記差動制限部材として、サイドギ
ヤと一体に回転する内側テーパリングを配設し、該少な
くとも一方のテーパリングにおける円錐面を、少なくと
もピニオンギヤ投影面に対応して切り欠いたことを特徴
とする。また本発明は、前記差動制限部材として、サイ
ドギヤ背面とデフケース内側面との間に多板クラッチを
配設して構成したことを特徴とする。また本発明は、前
記差動制限部材として、前記ピニオン軸との周方向相対
移動にて軸動する一対のプレッシャリングを介して前記
多板クラッチが配設されたことを特徴とする。また本発
明は、前記差動制限部材を、周方向に分割して組み付け
ることを可能に構成したことを特徴とするもので、２分
割型デフケースの諸欠点を解消した上で、比較的小さい
孔を通じて差動制限部材を組み付けることが可能で、低
コストである。SUMMARY OF THE INVENTION Therefore, according to the present invention, a pinion shaft disposed orthogonally to a rotation axis of a differential case, a pinion gear axially supported by the pinion shaft, and both sides of the pinion gear are meshed with bevel gears to be engaged. In a differential limiting device configured to generate a differential limiting force between the differential case and the side gears of a differential device including a pair of left and right side gears that take out the driving force distributed dynamically, the differential case is surrounded by the differential limiting device. It is characterized in that it is configured as an integral structure in which a hole is formed in the surface, and that the hole is formed in a shape through which at least the pinion gear and the differential limiting member can pass. Further, the present invention is characterized in that the differential limiting member is provided on a conical surface between the side gear and the differential case. Further, the present invention is characterized in that the conical surface of at least one of the side gears is cut out in correspondence with at least the pinion gear projection surface. Further, the present invention is characterized in that the conical surface of at least one of the side gears is cut out in correspondence with at least the tooth profile of the pinion gear having the minimum number of teeth. Further, according to the present invention, as the differential limiting member, a tapered ring that rotates integrally with the differential case is provided, and a conical surface of at least one of the tapered rings is cut out at least corresponding to a projection surface of the pinion gear. And Further, the present invention is characterized in that the taper ring is divided into a plurality of pieces on the circumference, and a detent piece to be engaged with the differential case is formed upright on these divided portions. Further, according to the present invention, as the differential limiting member, an inner taper ring that rotates integrally with a side gear is provided, and a conical surface of at least one of the taper rings is cut out corresponding to at least a pinion gear projection surface. Characterize. Further, the present invention is characterized in that, as the differential limiting member, a multi-plate clutch is arranged between the rear surface of the side gear and the inner side surface of the differential case. Further, the present invention is characterized in that, as the differential limiting member, the multi-plate clutch is arranged via a pair of pressure rings that are axially moved by relative movement with the pinion shaft in a circumferential direction. Further, the present invention is characterized in that the differential limiting member can be assembled by being divided in the circumferential direction, and various drawbacks of the two-part differential case are solved and a relatively small hole is formed. It is possible to assemble the differential limiting member through, and the cost is low.
【０００７】[0007]
【実施の形態】以下、本発明の差動制限装置の実施の形
態を図面に基づいて詳細に説明する。図１〜図３（Ａ）
（Ｂ）は本発明の差動制限装置の第１実施の形態を示
し、図１は差動制限部材を組み付けるための孔の部分を
含む１層テーパリング型の差動制限装置の外面図、図２
は同、全体断面図、図３（Ａ）（Ｂ）は差動制限部材で
あるテーパリングの斜視図および側断面図である。本発
明の差動制限装置は、図１に示すように、デフケース１
の回転軸Ｌに直交して配設されるピニオン軸２（図２参
照）と該ピニオン軸２に軸支されたピニオンギヤ３と該
ピニオンギヤ３の両側に傘歯噛合して差動配分された駆
動力を取り出す左右一対のサイドギヤ４、５とを備える
差動装置の前記デフケース１とサイドギヤ４、５との間
にて差動制限力を発生させるように構成された差動制限
装置において、前記デフケース１を周面に孔８を穿設し
た一体構造に構成するとともに、前記孔８を、少なくと
もピニオンギヤ３および差動制限部材７（サイドギヤ
４、５も差動制限部材を構成する。）が通過可能な形状
に構成したことを特徴とする。好適には、図示の例のよ
うに、ピニオンギヤ３が通過可能な短辺８Ｓと差動制限
部材７が通過可能な長辺８Ｌとで孔８が構成される。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of a differential limiting device of the present invention will be described below in detail with reference to the drawings. 1 to 3 (A)
FIG. 1B shows a first embodiment of a differential limiting device of the present invention, and FIG. 1 is an external view of a single-layer taper ring type limiting device including a hole portion for assembling a differential limiting member. Figure 2
3A and 3B are an overall sectional view, and FIGS. 3A and 3B are a perspective view and a side sectional view of a taper ring that is a differential limiting member. The differential limiting device of the present invention, as shown in FIG.
Of the pinion shaft 2 (see FIG. 2) arranged orthogonal to the rotation axis L of the pinion gear, the pinion gear 3 pivotally supported by the pinion shaft 2, and the differentially distributed drive on both sides of the pinion gear 3 by engaging with bevel teeth. A differential limiting device configured to generate a differential limiting force between the differential case 1 and the side gears 4, 5 of a differential device including a pair of left and right side gears 4 and 5 for extracting force. 1 is configured as an integrated structure in which holes 8 are formed on the peripheral surface, and at least the pinion gear 3 and the differential limiting member 7 (side gears 4 and 5 also configure differential limiting members) can pass through the hole 8. It is characterized by having a different shape. Preferably, as in the illustrated example, the hole 8 is constituted by the short side 8S through which the pinion gear 3 can pass and the long side 8L through which the differential limiting member 7 can pass.
【０００８】以下に詳述すると、本実施の形態のもの
は、低コストの１層テーパリング型の差動制限装置に適
用された例で、図２に示すように、一体構造のデフケー
ス１と該デフケース１の内部に収容される差動歯車から
なる差動装置および差動制限部材から構成される。前記
デフケース１の回転軸Ｌに直交してピニオン軸２が配設
され、該ピニオン軸２に軸支されたピニオンギヤ３と、
該ピニオンギヤ３の両側に傘歯噛合して差動配分された
駆動力を取り出す左右一対のサイドギヤ４、５とから差
動装置が構成される。そして、デフケース１の外周面の
前記ピニオン軸２の配設位置を回避した位置に図１に示
したような孔８が穿設される。該孔８は一体構造のデフ
ケース１でも、サイドギヤ４、５等を含む差動制限部材
（本実施の形態ではテーパリング６、７）を外部から挿
入して組み付けることを可能にするために穿設され、デ
フケース１が軸支されるキャリヤ内での潤滑油の循環
や、冷却機能を有し、さらには軽量化にも寄与するもの
である。More specifically, the present embodiment is an example applied to a low-cost one-layer taper ring type differential limiting device, and as shown in FIG. The differential case 1 includes a differential gear including a differential gear accommodated inside and a differential limiting member. A pinion shaft 2 is disposed orthogonal to the rotation axis L of the differential case 1, and a pinion gear 3 pivotally supported by the pinion shaft 2 is provided.
A differential device is composed of a pair of left and right side gears 4 and 5 that engage with bevel teeth on both sides of the pinion gear 3 and take out the differentially distributed driving force. Then, a hole 8 as shown in FIG. 1 is formed at a position avoiding the position where the pinion shaft 2 is disposed on the outer peripheral surface of the differential case 1. The hole 8 is formed even in the differential case 1 having an integral structure so that the differential limiting member (the taper rings 6 and 7 in this embodiment) including the side gears 4 and 5 can be inserted from the outside and assembled. In addition, the lubricating oil has a function of circulating and cooling in the carrier in which the differential case 1 is axially supported, and also contributes to weight reduction.
【０００９】本実施の形態における差動制限部材は、図
３（Ａ）（Ｂ）に示す（右サイドギヤ５側についてのみ
例示するが、左サイドギヤ４側も同様である）ように、
サイドギヤ５とデフケース１との間の円錐面に介設され
るお碗形状のテーパリング７から構成される。テーパリ
ング７のディスク状部に形成された円周上複数の係止片
７Ｂが、前記デフケース１の内側面の対応部位に形成さ
れた係止溝１Ｂに係止されてデフケース１と回転を共に
する。テーパリング７の円錐面７Ａが前記サイドギヤ５
とデフケース１との間に位置して、ピニオンギヤ３とサ
イドギヤ５、６との間の噛合反力に基づいてサイドギヤ
５、６の軸方向の離反によって、サイドギヤ５の背面と
の間に差動制限力を発生するように構成されている。As shown in FIGS. 3A and 3B, the differential limiting member in the present embodiment (only the right side gear 5 side is illustrated, the left side gear 4 side is also the same).
It is composed of a bowl-shaped taper ring 7 provided on a conical surface between the side gear 5 and the differential case 1. A plurality of circumferential locking pieces 7B formed on the disk-shaped portion of the taper ring 7 are locked in locking grooves 1B formed at corresponding portions on the inner side surface of the differential case 1 to rotate together with the differential case 1. To do. The conical surface 7A of the taper ring 7 is the side gear 5
Between the side gear 5 and the differential case 1, and the side gears 5 and 6 are disengaged in the axial direction based on the meshing reaction force between the pinion gear 3 and the side gears 5 and 6. It is configured to generate force.
【００１０】デフケース１の周面に穿設された前記孔８
は、図１に例示するように、少なくともピニオンギヤ３
が通過可能な短辺８Ｓ（ピニオンギヤ３の外径より僅か
大きい）と差動制限部材であるテーパリング７が通過可
能な長辺８Ｌ（テーパリング７の外径より僅か大きい）
とから構成される。そして、少なくとも一方のテーパリ
ング７の円錐面７Ａを、少なくともピニオンギヤ３投影
面に対応して切り欠いて（円弧状の）切欠き７Ｃを設け
た（図示の例では直径対向位置に一対を設けた）。さら
に、同様に、前記少なくとも一方のサイドギヤ５におけ
る円錐面を、少なくともピニオンギヤ投影面に対応して
切り欠いて（円弧状の）切欠き５Ｃを設けた（図示の例
では直径対向位置に一対を設けた）ものである。サイド
ギヤやテーパリングの摺動面が犠牲になって（小さくな
る）もよければ、これらの円弧状の切欠きに代えて、全
周を切り欠いてもよい。この場合は、サイドギヤ５およ
びテーパリング７の切欠き縁は、前記図１における孔８
の長辺に沿う縁部と重なる。そしてこの場合は、ピニオ
ンギヤ３のサイドギヤ５およびテーパリング７への噛合
組付け時の位置合せが不要となる。The hole 8 formed in the peripheral surface of the differential case 1
Is at least the pinion gear 3 as illustrated in FIG.
A short side 8S (slightly larger than the outer diameter of the pinion gear 3) and a long side 8L (slightly larger than the outer diameter of the taper ring 7) through which the taper ring 7, which is a differential limiting member, can pass.
Composed of and. Then, at least one conical surface 7A of the taper ring 7 is provided with a notch (arcuate) notch 7C corresponding to at least the projection surface of the pinion gear 3 (in the illustrated example, a pair is provided at a diametrically opposed position). ). Further, similarly, the conical surface of at least one of the side gears 5 is provided with a notch (arc-shaped) notch 5C corresponding to at least the projection surface of the pinion gear (in the illustrated example, a pair is provided at a diametrically opposed position). It is a thing. If the sliding surfaces of the side gears and the taper ring may be sacrificed (become smaller), the arcuate notches may be replaced with notches on the entire circumference. In this case, the notched edges of the side gear 5 and the taper ring 7 are the holes 8 in FIG.
Overlaps the edge along the long side of. In this case, it is not necessary to align the pinion gear 3 with the side gear 5 and the taper ring 7 during meshing.
【００１１】一対のテーパリング６、７およびサイドギ
ヤ４、５の一方のみに切欠きが設けられた場合は、ピニ
オンギヤ３をやや傾斜させて、切欠きが設けられていな
い他方側に組み付けてから、切欠きが設けられた一方側
の切欠きに整合させることでピニオンギヤ３を一対のテ
ーパリング６、７およびサイドギヤ４、５に組み付ける
ことができる。これらの組付形態は後述する内側テーパ
リング９、１０へのピニオンギヤ３の組付けについても
同様である。なお、他の部品との関係でデフケース１の
外径寸法が規制される場合に、ピニオン軸孔部の周囲の
デフケース１の内周側に補強のための肉盛り補強部が形
成されるが、テーパリング６および７を軸方向に組み付
ける際に、円弧状の切欠き（後述の図３（Ａ）（Ｂ）に
切欠き７Ｃの例が明示）の存在によって、前記肉盛り補
強部と干渉せずにクリアすることができる。When the notch is provided in only one of the pair of taper rings 6 and 7 and the side gears 4 and 5, after the pinion gear 3 is slightly inclined and assembled on the other side where the notch is not provided, The pinion gear 3 can be assembled to the pair of taper rings 6 and 7 and the side gears 4 and 5 by aligning with the notch on one side provided with the notch. These assembling forms are the same for assembling the pinion gear 3 to the inner taper rings 9 and 10 described later. When the outer diameter of the differential case 1 is restricted in relation to other parts, a buildup reinforcement portion for reinforcement is formed on the inner peripheral side of the differential case 1 around the pinion shaft hole. When the taper rings 6 and 7 are assembled in the axial direction, the presence of an arcuate cutout (an example of the cutout 7C is clearly shown in FIGS. 3A and 3B described later) causes interference with the build-up reinforcement portion. Can be cleared without.
【００１２】以上のように構成したので、デフケース１
の周面におけるピニオン軸２の配設位置を回避した位置
に穿設された前記孔８を通じて、差動制限部材であるテ
ーパリング６、７および左右のサイドギヤ４、５を挿入
の後、軸方向へ組み付ける。次いで、前記サイドギヤ
４、５およびテーパリング６、７における円弧状の各切
欠き４Ｃ、５Ｃおよび６Ｃ、７Ｃを揃えて図１の状態に
して形成されたピニオンギヤ投影面に対応する部分にピ
ニオンギヤ３を噛合挿入する。その後、ピニオンギヤ３
を噛合させたままでサイドギヤ６、７を円周方向に回動
させ、孔８を回避したピニオン軸２の正規の配設位置ま
でピニオンギヤ３を移動させた後、ピニオン軸２をデフ
ケース１の外側から挿入して組付けを完了する。ピニオ
ン軸２には抜止めピン１５が回転軸方向に挿入係止され
る。With the above construction, the differential case 1
After inserting the taper rings 6 and 7 and the left and right side gears 4 and 5 which are the differential limiting members through the holes 8 formed at positions avoiding the position where the pinion shaft 2 is disposed on the peripheral surface of the Attach to Next, the pinion gear 3 is formed in a portion corresponding to the pinion gear projection plane formed by aligning the arcuate notches 4C, 5C and 6C, 7C in the side gears 4, 5 and the taper rings 6, 7 in the state of FIG. Insert mesh. After that, pinion gear 3
While the side gears 6 and 7 are rotated in the circumferential direction while the gears are engaged, the pinion gear 3 is moved to the regular disposition position of the pinion shaft 2 that avoids the hole 8, and then the pinion shaft 2 is moved from the outside of the differential case 1. Insert and complete assembly. A retaining pin 15 is inserted and locked to the pinion shaft 2 in the rotation axis direction.
【００１３】図３（Ｃ）〜（Ｅ）に示した例は、テーパ
リング７を円周上で複数個に分割する（例えば図３
（Ｄ）の２分割あるいは図３（Ｅ）の４分割）ととも
に、これらの分割部にデフケースに係止される回止め片
を起立形成したことを特徴とする。図３（Ｄ）の例で
は、差動制限部材であるテーパリング７を円周上で２分
割して７−１、７−２とし、分割部に、デフケース１の
差動制限面に軸方向に刻設した係止溝１Ｃ、１Ｃに係止
される鍔状の回止め片７Ｄ、７Ｄを曲折して起立形成し
たものである。図３（Ｅ）の例はテーパリングを４分割
したものである。このようなテーパリング７の分割構成
により、図３（Ｃ）に示すように、ピニオンギヤ３の背
面の受座となる肉盛り部１Ｄを形成した場合でも、該肉
盛り部１Ｄと干渉することなくテーパリング７−１、７
−２を組み付けることが可能となる。また、デフケース
１に穿設される孔８についても、前記図１の例のものの
ように、短辺８Ｓと長辺８Ｌからなる長方形の他、短辺
８Ｓとして、ピニオンギヤ３の外径をクリアできる８Ｓ
２と、テーパリング７のための差動制限面を確保して中
心よりでサイドギヤ４、５の歯部よりやや大きめの軸方
向長さをクリアできる短辺８Ｓ１（Ｓ２＞Ｓ１）とから
形成される形状とすることもできる。この場合、孔面積
がさらに小さくなり、駆動トルクを大きくできる。テー
パリング７を分割形成したことにより、孔８における長
辺８Ｌについても、サイドギヤ４、５の外径がクリアで
きればよくさらに短い長さで済む。また、テーパリング
の円周上の１か所のみを切り欠いて、組付け時に弾性的
に縮径させて組み付けるように構成することもできる。
なお、テーパリング６、７が省略されてサイドギヤ背面
とデフケース内面における円錐面とが直接に摺接して差
動制限力を発生させる形式の場合は、サイドギヤ自身が
差動制限部材を構成する。In the example shown in FIGS. 3C to 3E, the taper ring 7 is divided into a plurality of pieces on the circumference (for example, FIG.
In addition to the two divisions of (D) or the four divisions of FIG. 3 (E), a detent piece to be engaged with the differential case is formed upright on these divisions. In the example of FIG. 3D, the taper ring 7 which is the differential limiting member is divided into two on the circumference into 7-1 and 7-2, and the split portion has an axial direction on the differential limiting surface of the differential case 1. The collar-shaped detent pieces 7D, 7D that are engaged with the engaging grooves 1C, 1C formed in the above are bent and formed upright. In the example of FIG. 3 (E), the taper ring is divided into four. With such a divided structure of the taper ring 7, as shown in FIG. 3C, even when the build-up portion 1D that serves as a seat on the rear surface of the pinion gear 3 is formed, it does not interfere with the build-up portion 1D. Taper rings 7-1, 7
-2 can be assembled. As for the hole 8 formed in the differential case 1, the outer diameter of the pinion gear 3 can be cleared as a short side 8S in addition to the rectangular shape having the short side 8S and the long side 8L as in the example of FIG. 8S
2 and a short side 8S1 (S2> S1) that can secure a differential limiting surface for the taper ring 7 and clear an axial length slightly larger than the tooth portion of the side gears 4 and 5 from the center. It can also be formed into a shape. In this case, the hole area is further reduced, and the driving torque can be increased. By forming the tapered ring 7 in a divided manner, it is sufficient that the long side 8L of the hole 8 also has a shorter outer diameter than that of the side gears 4 and 5. It is also possible to cut out only one place on the circumference of the taper ring and elastically reduce the diameter at the time of assembling.
In the case of the type in which the taper rings 6 and 7 are omitted and the rear surface of the side gear and the conical surface on the inner surface of the differential case are in direct sliding contact to generate the differential limiting force, the side gear itself constitutes the differential limiting member.
【００１４】図４は本発明の差動制限装置の第２実施の
形態を示す平面および要部断面図である。本実施の形態
のものは、図４（Ａ）に示すように、前記少なくとも一
方のサイドギヤ５における円錐面を、ピニオンギヤ３の
少なくとも最小歯数（１個）の歯形に対応して切り欠い
た（５Ｃ）ことを特徴とする。図示の例では左右一対の
サイドギヤの両方に切欠きが設けられる。図４（Ｂ）の
例では、歯数２個の歯形に対応して切欠き（サイドギヤ
５について切欠き５Ｃ、５Ｃが形成）が設けられる。な
お、拡大図である図４（Ｃ）および断面図である図４
（Ｄ）に明示するように、サイドギヤ５の円錐面に形成
される切欠き５Ｃは、サイドギヤ５における歯底５Ｄよ
りは浅い位置に留められ、円錐面の強度および該円錐面
をバックとした歯間ひいては歯自体の強度を確保できる
ように構成される。FIG. 4 is a plan view and a sectional view of an essential part showing a second embodiment of the differential limiting device of the present invention. In the present embodiment, as shown in FIG. 4 (A), the conical surface of at least one of the side gears 5 is cut out in correspondence with at least the minimum tooth number (one) tooth profile of the pinion gear 3 ( 5C). In the illustrated example, notches are provided in both the pair of left and right side gears. In the example of FIG. 4B, notches (notches 5C and 5C are formed in the side gear 5) are provided corresponding to the tooth profile having two teeth. 4C which is an enlarged view and FIG. 4 which is a cross-sectional view.
As clearly shown in (D), the notch 5C formed on the conical surface of the side gear 5 is retained at a position shallower than the tooth bottom 5D of the side gear 5, and the strength of the conical surface and the tooth with the conical surface as the back are provided. It is constructed so that the strength of the teeth and the teeth themselves can be secured.
【００１５】図５は本発明の差動制限装置の第３実施の
形態を示す全体断面図で、前記第１実施の形態のもの
に、差動制限部材として、サイドギヤ４、５と一体に回
転する内側テーパリング９、１０を配設し、これら内側
テーパリング９、１０における少なくとも一方（図示の
例では両方）の内側テーパリングの円錐面を、前記第１
実施の形態のものと同様に、少なくともピニオンギヤ３
の投影面に対応して切り欠いたことを特徴とする。これ
らの内側テーパリング９、１０における各ディスク状部
には、前記図３（Ａ）（Ｂ）に示したものと同様に、円
周上複数の係止片９Ｂ、１０Ｂが形成され、前記サイド
ギヤ４、５の対応部位に形成された係止溝に係止されて
サイドギヤ４、５と回転を共にする。したがって、デフ
ケース１と回転を共にする前記テーパリング６、７の円
錐面の内側と、内側テーパリング９、１０の円錐面の外
側との間が摺動回転して、差動制限力が生じるように構
成される。このような構成によって、テーパリング６、
７および内側テーパリング９、１０のみを耐磨耗性の素
材等にて構成することで、サイドギヤ４、５およびデフ
ケース１は低磨耗性材質で済み、素材の選択の自由度が
向上する。FIG. 5 is an overall cross-sectional view showing a third embodiment of the differential limiting device of the present invention. The differential limiting device of the first embodiment rotates integrally with the side gears 4 and 5 as a differential limiting member. Inner taperings 9 and 10 are provided, and the conical surface of at least one (both in the illustrated example) of the inner taperings 9 and 10 is defined as the first conical surface.
As with the embodiment, at least the pinion gear 3
It is characterized by being cut out corresponding to the projection plane of. A plurality of locking pieces 9B and 10B are formed on the circumference of each of the disc-shaped portions of the inner taper rings 9 and 10 in the same manner as those shown in FIGS. The side gears 4 and 5 rotate together with the side gears 4 and 5 by being locked in the locking grooves formed in the corresponding portions of 4 and 5. Therefore, the inner side of the conical surface of the taper rings 6 and 7 that rotates together with the differential case 1 and the outer side of the conical surface of the inner taper rings 9 and 10 are slidably rotated to generate a differential limiting force. Is composed of. With such a configuration, the taper ring 6,
By configuring only 7 and the inner taper rings 9 and 10 with a wear resistant material or the like, the side gears 4 and 5 and the differential case 1 are made of a low wear material, and the degree of freedom in selection of materials is improved.
【００１６】図６は本発明の差動制限装置の第４実施の
形態を示す全体断面図で、前記差動制限部材として、サ
イドギヤ４、５の背面とデフケース１の内側面との間に
多板クラッチ１１、１２を配設して構成したことを特徴
とする。このような構成によって、ピニオンギヤ３と左
右のサイドギヤ４、５との間の噛合反力によって発生す
るスラスト力により前記多板クラッチ１１、１２が摺動
締結されて差動制限力が発生する。本実施の形態では、
デフケース１の外周上に穿設された孔８の長辺の寸法
は、多板クラッチ１１、１２を構成するリング状の内外
プレートの外径がクリアできればよい。FIG. 6 is an overall sectional view showing a fourth embodiment of the differential limiting device of the present invention. As the differential limiting member, a large number of differential limiting members are provided between the rear surfaces of the side gears 4 and 5 and the inner side surface of the differential case 1. It is characterized in that the plate clutches 11 and 12 are arranged. With such a configuration, the multiple disc clutches 11 and 12 are slidably engaged by the thrust force generated by the meshing reaction force between the pinion gear 3 and the left and right side gears 4 and 5, and the differential limiting force is generated. In this embodiment,
The dimension of the long side of the hole 8 formed on the outer periphery of the differential case 1 may be such that the outer diameters of the ring-shaped inner and outer plates forming the multi-plate clutches 11 and 12 can be cleared.
【００１７】図７は本発明の差動制限装置の第５実施の
形態を示す全体断面図で、前記差動制限部材として、図
７（Ａ）に示すように、前記ピニオン軸２との周方向相
対移動にて軸動する一対のプレッシャリング１３、１４
を介して多板クラッチ１１、１２が配設されたことを特
徴とする。多板クラッチ１１、１２におけるインナプレ
ート群はサイドギヤ４、５における外周のラグに係合
し、アウタプレート群は前記プレッシャリング１３、１
４とともにデフケース１の内周面のラグ溝１Ａに係合し
てデフケース１と回転を共にする。プレッシャリング１
３、１４とデフケース１の内側面の間に前記多板クラッ
チ１１、１２が配設され、これらの多板クラッチ１１、
１２には、ピニオンギヤ３と左右のサイドギヤ４、５と
の間の噛合反力に加えて、図７（Ｂ）に示すように、デ
フケース１すなわちプレッシャリング１３、１４におけ
るカム溝１３Ｃ、１４Ｃとピニオン軸２との間の駆動回
転時の相対移動に基づいて発生するカム作用によるスラ
スト力により差動制限力を発生させることができる。本
実施の形態におけるデフケース１の外周上に穿設された
孔８の長辺の寸法は、多板クラッチ１１、１２を構成す
るリング状の内外プレートの外径あるいはプレッシャリ
ング１３、１４の外径のいずれか大きいほうをクリアで
きればよい。本実施の形態でも、プレッシャリング１
３、１４を周方向に分割して組み付けることを可能にす
れば、孔８の長辺の長さを小さくできる。FIG. 7 is an overall sectional view showing a fifth embodiment of a differential limiting device of the present invention. As the differential limiting member, as shown in FIG. 7 (A), the circumference of the pinion shaft 2 is shown. A pair of pressure rings 13 and 14 that axially move by relative movement
The multi-plate clutches 11 and 12 are arranged through the. The inner plate group of the multi-plate clutches 11 and 12 engages with the outer peripheral lugs of the side gears 4 and 5, and the outer plate group of the pressure plates 13 and 1 is the outer plate group.
4, and engages with the lug groove 1A on the inner peripheral surface of the differential case 1 to rotate together with the differential case 1. Pressure ring 1
The multi-plate clutches 11 and 12 are disposed between the inner surface of the differential case 1 and the multi-plate clutches 3 and 14, respectively.
In addition to the meshing reaction force between the pinion gear 3 and the left and right side gears 4 and 5, as shown in FIG. 7 (B), the differential case 1 includes the cam grooves 13C and 14C in the pressure rings 13 and 14 and the pinion. The differential limiting force can be generated by the thrust force due to the cam action that is generated based on the relative movement of the shaft 2 during the driving rotation. The dimension of the long side of the hole 8 formed on the outer periphery of the differential case 1 in the present embodiment is determined by the outer diameter of the ring-shaped inner and outer plates constituting the multi-plate clutch 11, 12 or the outer diameter of the pressure rings 13, 14. It is only necessary to clear whichever is larger. Also in this embodiment, the pressure ring 1
If the parts 3 and 14 can be divided and assembled in the circumferential direction, the length of the long side of the hole 8 can be reduced.
【００１８】以上、本発明の実施の形態を説明してきた
が、本発明の趣旨の範囲内で、一体型デフケースの形
状、形式、ピニオン軸の形状、配置、本数、デフケース
への挿入形態、サイドギヤの形状、形式、テーパリング
の形状およびそのデフケースへの係止形態、内側テーパ
リングの形状およびそのサイドギヤへの係止形態、多板
クラッチの形状、形式およびそのデフケースおよびサイ
ドギヤへの配設形態、プレッシャリングの形状、形式お
よびそのサイドギヤおよびデフケースへの配設形態なら
びにピニオン軸との間のカム形状、孔の形状（短辺側の
形状をピニオンギヤ外形と略一致させてもよい。）、サ
イドギヤおよびテーパリング（内側テーパリングも）に
おける切欠きの形状（図４の歯形に対応した切欠き形状
はテーパリングにも採用できる）、数（組付効率上はピ
ニオンギヤの数に対応した数の対を形成することを好適
とするが、少なくとも最小数の切欠きとして該切欠きを
利用して、１つのピニオンギヤの組付け後に、サイドギ
ヤとピニオンギヤを相対回転させて前記組み付けたピニ
オンギヤを奥側に移動させた上で、前面に戻った切欠き
部を利用して次のピニオンギヤを組み付けることも可能
である。さらには、切欠きの数を多数としたり、全周に
わたり切欠きが形成されることも本発明の範疇であ
る）、差動制限部材としてのテーパリングおよびプレッ
シャリングの分割形態等については適宜採用できる。The embodiments of the present invention have been described above. However, within the scope of the present invention, the shape and type of the integrated diff case, the shape and arrangement of the pinion shaft, the arrangement, the number, the insertion form into the diff case, and the side gears. Shape, form, shape of taper ring and its locking form to the differential case, shape of inner taper ring and its locking form to the side gear, shape and type of multi-plate clutch and its disposition to the diff case and side gear, The shape and type of the pressure ring, the arrangement of the pressure ring on the side gear and the differential case, the cam shape between the pressure ring and the pinion shaft, the shape of the hole (the shape on the short side may be substantially the same as the outer shape of the pinion gear), the side gear, and the side gear. Notch shape in the taper ring (also inside taper ring) (The notch shape corresponding to the tooth profile in Fig. 4 is also applicable to the taper ring. However, it is preferable to form a number of pairs corresponding to the number of pinion gears in terms of assembling efficiency, but at least the minimum number of notches is used as the pair of pinion gears. After attachment, it is also possible to rotate the side gear and the pinion gear relative to each other to move the assembled pinion gear to the inner side, and then to assemble the next pinion gear by utilizing the notch part returned to the front surface. It is also within the scope of the present invention that the number of notches is large, or that notches are formed over the entire circumference), the taper ring and the pressure ring as a differential limiting member, and the like can be appropriately adopted.
【００１９】[0019]
【発明の効果】以上詳細に説明したように、本発明によ
れば、デフケースの回転軸に直交して配設されるピニオ
ン軸と該ピニオン軸に軸支されたピニオンギヤと該ピニ
オンギヤの両側に傘歯噛合して差動配分された駆動力を
取り出す左右一対のサイドギヤとを備える差動装置の前
記デフケースとサイドギヤとの間にて差動制限力を発生
させるように構成された差動制限装置において、前記デ
フケースを周面に孔を穿設した一体構造に構成するとと
もに、前記孔を、少なくともピニオンギヤおよび差動制
限部材が通過可能な形状に構成したことにより、必要最
小限の大きさの孔の穿設によってデフケースの強度を確
保しつつ、差動制限部材の組付けを可能にした一体型デ
フケースを採用することが可能になって、従来の分割型
デフケースのような接合フランジ面の加工や精度に煩わ
されることもなく、部品が削減でき、キャリヤ等への軸
組み時の仮組み精度も向上させることができる。As described in detail above, according to the present invention, a pinion shaft disposed orthogonally to the rotating shaft of the differential case, a pinion gear pivotally supported by the pinion shaft, and an umbrella on both sides of the pinion gear. A differential limiting device configured to generate a differential limiting force between the differential case and a side gear of a differential device including a pair of left and right side gears that meshes with each other to take out a differentially distributed driving force. , The differential case is formed as an integral structure with holes formed in the peripheral surface, and the hole is formed in a shape through which at least the pinion gear and the differential limiting member can pass, so that It is possible to adopt an integral diff case that allows the differential limiting member to be assembled while securing the strength of the diff case by drilling, and Without being bothered to processing and accuracy of the bonded flange surface, parts can be reduced, it is possible to improve the temporary assembling accuracy during axial assembly of the carrier or the like.
【００２０】また、前記差動制限部材が、サイドギヤと
デフケースとの間の円錐面に介設された場合は、比較的
小径のサイドギヤをクリアできればよい孔の大きさを小
さくでき、孔の大きさの設定の自由度すなわち設計の自
由度が向上する。さらに、前記少なくとも一方のサイド
ギヤにおける円錐面を、少なくともピニオンギヤ投影面
に対応して切り欠いた場合は、左右のサイドギヤ間の距
離を小さくしてコンパクトでありながら比較的大きなサ
イズのピニオンギヤの噛合組付けを可能としながら、差
動制限部材とサイドギヤとの間の円錐摩擦面の面積を可
及的に大きく採ることができる。Further, when the differential limiting member is provided on the conical surface between the side gear and the differential case, it suffices if the side gear having a relatively small diameter can be cleared. The degree of freedom in setting, that is, the degree of freedom in design is improved. Further, when the conical surface of at least one of the side gears is cut out at least corresponding to the projection plane of the pinion gear, the distance between the left and right side gears is reduced to be compact, but the meshing assembly of the pinion gear of a relatively large size It is possible to make the area of the conical friction surface between the differential limiting member and the side gear as large as possible.
【００２１】また、前記少なくとも一方のサイドギヤに
おける円錐面を、ピニオンギヤの少なくとも最小歯数の
歯形に対応して切り欠いた場合は、円錐面における切欠
き面積を必要最小限として強度低下を防止し、歯自体の
耐久性を低下させることも抑止できる。さらにまた、前
記差動制限部材として、デフケースと一体に回転するテ
ーパリングを配設し、該少なくとも一方のテーパリング
における円錐面を、少なくともピニオンギヤ投影面に対
応して切り欠いた場合は、デフケースの材質を選ぶこと
なく材質の選定の自由度が向上する上に、前述同様に、
ピニオンギヤ投影面に対応して切り欠いたサイドギヤと
組み合わせて、左右のサイドギヤ間の距離を小さくして
コンパクトでありながら比較的大きなサイズのピニオン
ギヤの噛合組付けを可能としながら、差動制限部材とサ
イドギヤとの間の円錐摩擦面の面積を可及的に大きく採
ることができる。また、前記テーパリングを円周上で複
数個に分割するとともに、これらの分割部にデフケース
に係止される回止め片を起立形成した場合は、デフケー
スの内径を小さくしたり、デフケース内周にピニオンギ
ヤ背面の受座となる肉盛り部を形成しても、これらに干
渉することなくテーパリングを組み付けられ、回止め片
の配設のためのサイドギヤ背面にスペースを要すること
もなくコンパクトかつ簡素となる。しかも、比較的小さ
な孔の形成にて済むことから、駆動トルクを大きく採れ
て強度および耐久性が向上する。When the conical surface of at least one of the side gears is cut out in correspondence with the tooth profile of the pinion gear having at least the minimum number of teeth, the notch area of the conical surface is reduced to a necessary minimum to prevent the strength from decreasing. It is also possible to prevent the durability of the teeth themselves from being reduced. Furthermore, when a taper ring that rotates integrally with the differential case is provided as the differential limiting member, and the conical surface of at least one of the taper rings is cut out at least corresponding to the pinion gear projection plane, the In addition to improving the flexibility of material selection without selecting the material,
In combination with a side gear cut out corresponding to the projection surface of the pinion gear, the distance between the left and right side gears is reduced to enable compact and relatively large size pinion gear meshing and assembly, while at the same time limiting the differential gear and side gear. The area of the conical friction surface between and can be taken as large as possible. Further, when the taper ring is divided into a plurality of parts on the circumference and the detent pieces to be engaged with the differential case are formed upright in these divided parts, the inner diameter of the differential case can be reduced or the inner circumference of the differential case can be reduced. Even if the padding part that forms the seat on the back of the pinion gear is formed, the taper ring can be assembled without interfering with these, and there is no need for space on the back of the side gear for disposition of the detent piece, making it compact and simple. Become. Moreover, since relatively small holes can be formed, a large driving torque can be obtained and strength and durability are improved.
【００２２】さらに、前記差動制限部材として、サイド
ギヤと一体に回転する内側テーパリングを配設し、該少
なくとも一方のテーパリングにおける円錐面を、少なく
ともピニオンギヤ投影面に対応して切り欠いた場合は、
前述同様に、ピニオンギヤ投影面に対応して切り欠いた
サイドギヤおよびテーパリングと組み合わせて、左右の
サイドギヤ間の距離を小さくしてコンパクトでありなが
ら比較的大きなサイズのピニオンギヤの噛合組付けを可
能としながら、差動制限部材とサイドギヤとの間の円錐
摩擦面の面積を可及的に大きく採ることができる他、テ
ーパリングおよび内側テーパリングのみを耐磨耗性の素
材等にて構成することで、サイドギヤおよびデフケース
は低磨耗性材質で済み、素材の選択の自由度がさらに向
上する。さらにまた、前記差動制限部材として、サイド
ギヤ背面とデフケース内側面との間に多板クラッチを配
設して構成した場合は、円錐面加工が不要な単純な構成
の平板状のクラッチ部材の配設により構成された差動制
限装置にも一体型デフケースが採用できる。Further, when the inner taper ring which rotates integrally with the side gear is provided as the differential limiting member, and the conical surface of at least one of the taper rings is cut out at least corresponding to the projection surface of the pinion gear, ,
In the same manner as described above, by combining with a side gear and a taper ring that are cut out corresponding to the projection surface of the pinion gear, the distance between the left and right side gears is reduced to enable compact yet relatively large size pinion gears to be engaged. , The area of the conical friction surface between the differential limiting member and the side gear can be made as large as possible, and by configuring only the taper ring and the inner taper ring with a wear resistant material, The side gears and differential case are made of low-wear materials, further increasing the freedom of material selection. Furthermore, when a multi-plate clutch is arranged between the rear surface of the side gear and the inner side surface of the differential case as the differential limiting member, the arrangement of the flat plate-shaped clutch member which does not require conical surface processing is arranged. An integral diff case can also be adopted for the differential limiting device configured by the construction.
【００２３】また、前記差動制限部材として、前記ピニ
オン軸との周方向相対移動にて軸動する一対のプレッシ
ャリングを介して前記多板クラッチが配設された場合
は、前述同様に、円錐面加工が不要な単純な構成の平板
状のクラッチ部材の配設により構成された差動制限装置
にも一体型デフケースが採用できる上に、ピニオンギヤ
とサイドギヤとの間の噛合反力に加えて、プレッシャリ
ングとピニオン軸との間のカム作用によるスラスト力に
より大きな差動制限力を発生させることができる。さら
に、前記差動制限部材を、周方向に分割して組み付ける
ことを可能に構成した場合は、孔における長辺の長さを
さらに小さくできて、孔の大きさの設定自由度が向上す
る。かくして、本発明によれば、比較的小さな孔にて差
動制限部材の組付けを可能にして、一体型のデフケース
の採用を容易にした、低コストな差動制限装置が提供さ
れる。Further, when the multi-disc clutch is arranged as the differential limiting member via a pair of pressure rings that are axially moved by relative movement in the circumferential direction with respect to the pinion shaft, as in the case described above, In addition to the integral differential case that can also be used in a differential limiting device that is configured by arranging a flat plate-shaped clutch member that does not require surface processing, in addition to the meshing reaction force between the pinion gear and the side gear, A large differential limiting force can be generated by the thrust force due to the cam action between the pressure ring and the pinion shaft. Furthermore, when the differential limiting member is constructed so as to be assembled in a divided manner in the circumferential direction, the length of the long side of the hole can be further reduced, and the degree of freedom in setting the size of the hole is improved. Thus, according to the present invention, there is provided a low-cost differential limiting device which enables the differential limiting member to be assembled with a relatively small hole and facilitates the adoption of the integral differential case.
【図１】本発明の差動制限装置の第１実施の形態を示
し、差動制限部材を組み付けるための孔の部分を含む１
層テーパリング型の差動制限装置の外面図である。FIG. 1 shows a first embodiment of a differential limiting device of the present invention, which includes a hole portion for assembling a differential limiting member.
FIG. 3 is an external view of a layer tapering type limited slip differential device.
【図２】同、全体断面図である。FIG. 2 is an overall sectional view of the same.
【図３】同、図３（Ａ）（Ｂ）は差動制限部材であるテ
ーパリングの斜視図および側断面図、図３（Ｃ）〜
（Ｅ）は差動制限部材であるテーパリングを円周上で複
数個に分割した例を示す断面図である。3 (A) and 3 (B) are a perspective view and a side sectional view of a taper ring which is a differential limiting member, and FIGS.
(E) is a sectional view showing an example in which a taper ring which is a differential limiting member is divided into a plurality of pieces on the circumference.
【図４】本発明の差動制限装置の第２実施の形態を示す
平面および要部断面図である。4A and 4B are a plan view and a cross-sectional view of an essential part showing a second embodiment of a differential limiting device of the present invention.
【図５】本発明の差動制限装置の第３実施の形態を示す
全体断面図である。FIG. 5 is an overall sectional view showing a third embodiment of a differential limiting device of the present invention.
【図６】本発明の差動制限装置の第４実施の形態を示す
全体断面図である。FIG. 6 is an overall sectional view showing a fourth embodiment of a differential limiting device of the present invention.
【図７】本発明の差動制限装置の第５実施の形態を示す
全体断面図である。FIG. 7 is an overall sectional view showing a fifth embodiment of a limited slip differential device of the present invention.
【図８】従来の差動制限装置の全体断面図である。FIG. 8 is an overall sectional view of a conventional limited slip differential device.
１ デフケース １Ａ ラグ溝 １Ｂ 係止溝 ２ ピニオン軸 ３ ピニオンギヤ ４ 左サイドギヤ ４Ｃ 切欠き ５ 右サイドギヤ ５Ｃ 切欠き ６ 左テーパリング（差動制限部材） ６Ｃ 切欠き ７ 右テーパリング（差動制限部材） ７Ａ 円錐面 ７Ｂ 係止片 ７Ｃ 切欠き ８ 孔 ８Ｓ 短辺 ８Ｌ 長辺 ９ 左内側テーパリング（差動制限部材） １０ 右内側テーパリング（差動制限部材） １１ 左多板クラッチ（差動制限部材） １２ 右多板クラッチ（差動制限部材） １３ 左プレッシャリング（差動制限部材） １４ 右プレッシャリング（差動制限部材） Ｌ デフケース回転軸 1 differential case 1A lug groove 1B locking groove 2 pinion shaft 3 pinion gear 4 Left side gear 4C cutout 5 Right side gear 5C cutout 6 Left taper ring (differential limiting member) 6C cutout 7 Right taper ring (differential limiting member) 7A conical surface 7B locking piece 7C cutout 8 holes 8S short side 8L long side 9 Left inner taper ring (differential limiting member) 10 Right inner taper ring (differential limiting member) 11 Left multi-plate clutch (differential limiting member) 12 Right multi-plate clutch (differential limiting member) 13 Left pressure ring (differential limiting member) 14 Right pressure ring (differential limiting member) L differential case rotating shaft
フロントページの続き Ｆターム(参考） 3J027 FA17 FA18 FA19 FB12 HB07 HB16 HC07 HC22 HC23 HD01 HD04 HF06 HG03 HG04 Continued front page F term (reference) 3J027 FA17 FA18 FA19 FB12 HB07 HB16 HC07 HC22 HC23 HD01 HD04 HF06 HG03 HG04
Claims (10)
るピニオン軸と該ピニオン軸に軸支されたピニオンギヤ
と該ピニオンギヤの両側に傘歯噛合して差動配分された
駆動力を取り出す左右一対のサイドギヤとを備える差動
装置の前記デフケースとサイドギヤとの間にて差動制限
力を発生させるように構成された差動制限装置におい
て、前記デフケースを周面に孔を穿設した一体構造に構
成するとともに、前記孔を、少なくともピニオンギヤお
よび差動制限部材が通過可能な形状に構成したことを特
徴とする差動制限装置。1. A left and right pinion shaft that is disposed orthogonally to the rotational axis of the differential case, a pinion gear that is axially supported by the pinion shaft, and bevel gears on both sides of the pinion gear that take out the driving force differentially distributed. In a differential limiting device configured to generate a differential limiting force between the differential case and the side gear of a differential device including a pair of side gears, an integral structure in which the differential case is provided with a hole in a peripheral surface thereof. And the hole is formed in a shape that allows at least the pinion gear and the differential limiting member to pass therethrough.
ケースとの間の円錐面に介設されたことを特徴とする請
求項１に記載の差動制限装置。2. The differential limiting device according to claim 1, wherein the differential limiting member is provided on a conical surface between the side gear and the differential case.
る円錐面を、少なくともピニオンギヤ投影面に対応して
切り欠いたことを特徴とする請求項１または２に記載の
差動制限装置。3. The differential limiting device according to claim 1, wherein the conical surface of at least one of the side gears is cut out at least corresponding to the projection surface of the pinion gear.
る円錐面を、ピニオンギヤの少なくとも最小歯数の歯形
に対応して切り欠いたことを特徴とする請求項３に記載
の差動制限装置。4. The differential limiting device according to claim 3, wherein the conical surface of at least one of the side gears is notched corresponding to at least the tooth profile of the pinion gear having the minimum number of teeth.
一体に回転するテーパリングを配設し、該少なくとも一
方のテーパリングにおける円錐面を、少なくともピニオ
ンギヤ投影面に対応して切り欠いたことを特徴とする請
求項１ないし４のいずれかに記載の差動制限装置。5. A taper ring that rotates integrally with a differential case is provided as the differential limiting member, and a conical surface of at least one taper ring is cut out corresponding to at least a pinion gear projection surface. The differential limiting device according to any one of claims 1 to 4.
割するとともに、これらの分割部にデフケースに係止さ
れる回止め片を起立形成したことを特徴とする請求項５
に記載の差動制限装置。6. The taper ring is divided into a plurality of pieces on the circumference, and a detent piece to be engaged with a differential case is formed upright on these divided portions.
The differential limiting device according to 1.
一体に回転する内側テーパリングを配設し、該少なくと
も一方のテーパリングにおける円錐面を、少なくともピ
ニオンギヤ投影面に対応して切り欠いたことを特徴とす
る請求項１から６のいずれかに記載の差動制限装置。7. An inner taper ring that rotates integrally with a side gear is provided as the differential limiting member, and a conical surface of at least one of the taper rings is cut out in correspondence with at least a pinion gear projection surface. 7. The differential limiting device according to claim 1, wherein the limiting device is a differential limiting device.
面とデフケース内側面との間に多板クラッチを配設して
構成したことを特徴とする請求項１に記載の差動制限装
置。8. The differential limiting device according to claim 1, wherein as the differential limiting member, a multi-plate clutch is arranged between the rear surface of the side gear and the inner side surface of the differential case.
軸との周方向相対移動にて軸動する一対のプレッシャリ
ングを介して前記多板クラッチが配設されたことを特徴
とする請求項８に記載の差動制限装置。9. The multi-disc clutch is arranged as the differential limiting member via a pair of pressure rings that axially move by relative movement in the circumferential direction with respect to the pinion shaft. The differential limiting device according to 1.
て組み付けることを可能に構成したことを特徴とする請
求項１ないし９のいずれかに記載の差動制限装置。10. The differential limiting device according to claim 1, wherein the differential limiting member is configured such that it can be assembled while being divided in the circumferential direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002212124A JP4316196B2 (en) | 2001-07-24 | 2002-07-22 | Differential limiter |
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001-222516 | 2001-07-24 | ||
| JP2001222516 | 2001-07-24 | ||
| JP2002026299 | 2002-02-04 | ||
| JP2002-26299 | 2002-02-04 | ||
| JP2002212124A JP4316196B2 (en) | 2001-07-24 | 2002-07-22 | Differential limiter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003294109A true JP2003294109A (en) | 2003-10-15 |
| JP4316196B2 JP4316196B2 (en) | 2009-08-19 |
Family
ID=29255036
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002212124A Expired - Fee Related JP4316196B2 (en) | 2001-07-24 | 2002-07-22 | Differential limiter |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4316196B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008121738A (en) * | 2006-11-09 | 2008-05-29 | Ｇｋｎ ドライブライン トルクテクノロジー株式会社 | Flange structure to which rotation driving force transmitting member is fixed |
| US7604562B2 (en) | 2005-08-31 | 2009-10-20 | Engineering Center Steyr Gmbh & Co. Kg | Drive axle for a light vehicle |
| US7827882B2 (en) | 2004-01-30 | 2010-11-09 | Toyota Jidosha Kabushiki Kaisha | Differential gear unit |
| JP2011075109A (en) * | 2011-01-17 | 2011-04-14 | Jtekt Corp | Hybrid differential device for vehicle |
| DE102011055101A1 (en) | 2010-11-08 | 2012-05-10 | GKN Driveline Japan Ltd. | differential device |
| WO2020184428A1 (en) * | 2019-03-08 | 2020-09-17 | 武蔵精密工業株式会社 | Differential device |
-
2002
- 2002-07-22 JP JP2002212124A patent/JP4316196B2/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7827882B2 (en) | 2004-01-30 | 2010-11-09 | Toyota Jidosha Kabushiki Kaisha | Differential gear unit |
| US7604562B2 (en) | 2005-08-31 | 2009-10-20 | Engineering Center Steyr Gmbh & Co. Kg | Drive axle for a light vehicle |
| JP2008121738A (en) * | 2006-11-09 | 2008-05-29 | Ｇｋｎ ドライブライン トルクテクノロジー株式会社 | Flange structure to which rotation driving force transmitting member is fixed |
| DE102011055101A1 (en) | 2010-11-08 | 2012-05-10 | GKN Driveline Japan Ltd. | differential device |
| JP2012102772A (en) * | 2010-11-08 | 2012-05-31 | Gkn Driveline Japan Ltd | Differential apparatus |
| US9188213B2 (en) | 2010-11-08 | 2015-11-17 | GKN Driveline Japan Ltd. | Differential apparatus |
| DE102011055101B4 (en) * | 2010-11-08 | 2018-02-22 | GKN Driveline Japan Ltd. | differential device |
| JP2011075109A (en) * | 2011-01-17 | 2011-04-14 | Jtekt Corp | Hybrid differential device for vehicle |
| WO2020184428A1 (en) * | 2019-03-08 | 2020-09-17 | 武蔵精密工業株式会社 | Differential device |
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| Publication number | Publication date |
|---|---|
| JP4316196B2 (en) | 2009-08-19 |
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