JP2018132174A - Differential case assembling body - Google Patents

Differential case assembling body Download PDF

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JP2018132174A
JP2018132174A JP2017028259A JP2017028259A JP2018132174A JP 2018132174 A JP2018132174 A JP 2018132174A JP 2017028259 A JP2017028259 A JP 2017028259A JP 2017028259 A JP2017028259 A JP 2017028259A JP 2018132174 A JP2018132174 A JP 2018132174A
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differential case
rotation center
center line
bolts
gear
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JP6711298B2 (en
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高徳 額田
Takanori Nukada
高徳 額田
健利 城戸
Taketoshi Kido
健利 城戸
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Toyota Motor Corp
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Abstract

PROBLEM TO BE SOLVED: To properly prevent the loosening of the rotation of a bolt, in a differential case assembling body in which a ring gear is attached to a differential case with a plurality of the bolts.SOLUTION: Since intervals D3 of a plurality of bolts 16 are set unequal around a rotation center line S so that the intervals of the bolts 16 at a boundary portion between column parts 24, 26 and window parts 32, 34 become small, the fastening rigidity of the boundary portion becomes high. In other words, when torque is transmitted on the basis of fastening forces of the bolts 16 between a ring gear 18 and a differential case 14, the shearing torque of each bolt 16 in the boundary portion in which the intervals D3 are small is reduced. Therefore, even if face pressure between head parts and seat faces of the bolts 16 in the boundary portion is unequal, the generation of the loosening of the rotation of the bolts 16 caused by the generation of a slide between the head parts and the seat faces can be suppressed.SELECTED DRAWING: Figure 4

Description

本発明は、複数の締結部材を介してリングギヤがデフケースに一体的に取り付けられたデフケース組立体に関するものである。   The present invention relates to a differential case assembly in which a ring gear is integrally attached to a differential case via a plurality of fastening members.

(a) 中空形状を成しているとともに、回転中心線を挟んで反対側に一対の柱部が設けられており、その回転中心線まわりにおいて一対の柱部の間にそれぞれ窓部が設けられているデフケースと、(b) 前記デフケースの外周部に一体に設けられた円環形状のギヤ取付部と、(c) 前記回転中心線と平行な方向において前記ギヤ取付部に重ね合わされるように、その回転中心線と同心に前記デフケースの外周部に配置され、その回転中心線まわりに設けられる複数の締結部材を介して前記ギヤ取付部に一体的に取り付けられたリングギヤと、を有するデフケース組立体が知られている。特許文献１の図１１〜図１６に記載の装置はその一例である。   (a) It has a hollow shape, and a pair of pillars are provided on the opposite side across the rotation center line, and a window is provided between the pair of pillars around the rotation center line. A differential case, (b) an annular gear mounting portion integrally provided on the outer periphery of the differential case, and (c) superimposed on the gear mounting portion in a direction parallel to the rotation center line. And a ring gear that is disposed concentrically with the rotation center line on the outer peripheral portion of the differential case and is integrally attached to the gear mounting portion via a plurality of fastening members provided around the rotation center line. A solid is known. The apparatus described in FIGS. 11 to 16 of Patent Document 1 is an example.

また、特許文献２には、リングギヤのギヤ部から内周側へ突き出すように設けられた取付板部の内周側に、デフケースのギヤ取付部に設けられた段差部をインロウ嵌合（締り嵌め）するとともに、ギヤ部の内周面とギヤ取付部の外周縁部とをスプライン嵌合することにより、ギヤ取付部とリングギヤとの径方向および周方向の相対変位を抑制して、締結部材であるボルトの回転緩みを防止する技術が提案されている。   Further, in Patent Document 2, a step portion provided in the gear mounting portion of the differential case is in-row fitted (tightened) on the inner peripheral side of the mounting plate portion provided so as to protrude from the gear portion of the ring gear to the inner peripheral side. ) And spline-fitting the inner peripheral surface of the gear portion and the outer peripheral edge portion of the gear mounting portion, thereby suppressing radial and circumferential relative displacement between the gear mounting portion and the ring gear. A technique for preventing rotational loosening of a bolt has been proposed.

特開平８−３２００５９号公報JP-A-8-320059 特開２０１０−２１０００４号公報JP 2010-210004 A

しかしながら、このようなデフケース組立体においても締結部材の回転緩みが発生する場合があり、未だ改善の余地があった。すなわち、デフケースの回転中心線まわりにおいて柱部が設けられた部分と窓部が設けられた部分とでは、ギヤ取付部の剛性が異なるため、リングギヤの噛合荷重の反力による変形の程度が相違し、窓部が設けられた部分では剛性が低くて変形量が大きくなる。このため、窓部と柱部との境界部分では、周方向において変形量に勾配（変化）が生じ、締結部材の押圧面の接触（面圧）が不均一になり、その押圧面で滑りが生じて締結部材の回転緩みが発生し易くなる。   However, even in such a differential case assembly, rotation of the fastening member may occur, and there is still room for improvement. That is, since the rigidity of the gear mounting portion differs between the portion where the column portion is provided around the rotation center line of the differential case and the portion where the window portion is provided, the degree of deformation due to the reaction force of the meshing load of the ring gear is different. In the portion where the window portion is provided, the rigidity is low and the deformation amount is large. For this reason, at the boundary portion between the window portion and the column portion, a gradient (change) occurs in the deformation amount in the circumferential direction, the contact (surface pressure) of the pressing surface of the fastening member becomes uneven, and slippage occurs on the pressing surface. This is likely to cause loosening of the fastening member.

例えば図６に示すデフケース組立体１０において、リングギヤ１８がはすば歯車の場合、そのリングギヤ１８の噛合側（図６における上方側）では、噛合荷重の反力によってスラスト荷重Ｆが発生し、ギヤ取付部である外向きフランジ６０が回転中心線Ｓと平行な方向（図６では左方向）へ撓み変形する。その場合に、窓部３２、３４が設けられた部分（図の上下方向部分）は剛性が低く、柱部２４、２６が設けられた部分（図の紙面の表裏方向部分）に比較して撓み変形量δが大きくなる。このため、窓部３２、３４と柱部２４、２６との境界部分では、周方向において撓み変形量δに勾配（変化）が生じ、締結部材であるボルト１６（図３等参照）の押圧面（具体的にはボルト頭部と座面）の接触（面圧）が不均一になり、その押圧面で滑りが生じてボルト１６の回転緩みが発生する可能性がある。   For example, in the differential case assembly 10 shown in FIG. 6, when the ring gear 18 is a helical gear, a thrust load F is generated on the meshing side (the upper side in FIG. 6) of the ring gear 18 due to the reaction force of the meshing load. The outward flange 60, which is the mounting portion, is bent and deformed in a direction parallel to the rotation center line S (left direction in FIG. 6). In that case, the portion provided with the windows 32 and 34 (the vertical direction portion in the figure) has low rigidity, and is bent in comparison with the portion provided with the column portions 24 and 26 (the front and back direction portions in the drawing). The deformation amount δ increases. For this reason, in the boundary part of the window parts 32 and 34 and the pillar parts 24 and 26, the bending deformation amount (delta) produces a gradient (change) in the circumferential direction, and the press surface of the volt | bolt 16 (refer FIG. 3 etc.) which is a fastening member. There is a possibility that the contact (surface pressure) of the bolt head (specifically, the bolt head and the seating surface) becomes non-uniform, slippage occurs on the pressing surface, and rotational looseness of the bolt 16 occurs.

これに対し、締結部材の数を増やせば各締結部材の間隔が狭くなって分担トルクが低減されるため、窓部と柱部との境界部分でも、面圧の不均一に拘らず締結部材の回転緩みを抑制できるが、部品点数が増えてコストが高くなったり重量が増加したりする問題がある。   On the other hand, if the number of fastening members is increased, the interval between the fastening members becomes narrow and the shared torque is reduced. Therefore, even at the boundary portion between the window portion and the column portion, the fastening member is not affected by unevenness in surface pressure. Although rotation looseness can be suppressed, there is a problem that the number of parts increases, resulting in an increase in cost and an increase in weight.

本発明は以上の事情を背景として為されたもので、その目的とするところは、複数の締結部材を介してリングギヤがデフケースに取り付けられたデフケース組立体において、締結部材の回転緩みが一層適切に防止されるようにすることにある。   The present invention has been made in the background of the above circumstances, and the object of the present invention is to more appropriately prevent the loosening of the fastening member in the differential case assembly in which the ring gear is attached to the differential case via a plurality of fastening members. It is to be prevented.

かかる目的を達成するために、本発明は、(a) 中空形状を成しているとともに、回転中心線を挟んで反対側に一対の柱部が設けられており、その回転中心線まわりにおいて一対の柱部の間にそれぞれ窓部が設けられているデフケースと、(b) 前記デフケースの外周部に一体に設けられた円環形状のギヤ取付部と、(c) 前記回転中心線と平行な方向において前記ギヤ取付部に重ね合わされるように、その回転中心線と同心に前記デフケースの外周部に配置され、その回転中心線まわりに設けられる複数の締結部材を介して前記ギヤ取付部に一体的に取り付けられたリングギヤと、を有するデフケース組立体において、(d) 前記柱部と前記窓部との境界部分における前記締結部材の間隔が小さくなるように、前記回転中心線まわりにおいて前記複数の締結部材の間隔が不等分間隔とされていることを特徴とする。   In order to achieve such an object, the present invention provides (a) a hollow shape, and a pair of pillars provided on the opposite side across the rotation center line. A differential case provided with a window portion between each of the pillar portions, (b) an annular gear mounting portion integrally provided on the outer peripheral portion of the differential case, and (c) parallel to the rotation center line. Is arranged on the outer peripheral part of the differential case concentrically with the rotation center line so as to be superimposed on the gear attachment part in the direction, and is integrated with the gear attachment part via a plurality of fastening members provided around the rotation center line. A differential gear assembly having a ring gear attached thereto, and (d) the plurality of the plurality of fastening members around the rotation center line so that an interval between the fastening members at a boundary portion between the pillar portion and the window portion is reduced. Tighten It is characterized in that the interval between the binding members is an unequal interval.

このようなデフケース組立体においては、柱部と窓部との境界部分における締結部材の間隔が小さくなるように、回転中心線まわりにおいて複数の締結部材の間隔が不等分間隔とされているため、その境界部分における締結強度が高くなる。言い換えれば、リングギヤとデフケースとの間で締結部材の締結力に基づいてトルク伝達が行なわれる際に、境界部分の各締結部材の分担トルクが低減される。このため、境界部分における締結部材の押圧面の面圧が不均一であっても、滑りが生じて締結部材の回転緩みが発生することが抑制される。また、境界部分以外の締結部材の間隔は比較的大きいため、単純に締結部材の数を増やすだけの場合に比較して、締結部材の数を少なく維持して部品点数の増加や重量増加を抑制しつつ、境界部分の締結部材の回転緩みを適切に抑制できる。   In such a differential case assembly, the intervals between the plurality of fastening members are not evenly spaced around the rotation center line so that the interval between the fastening members at the boundary portion between the column portion and the window portion is reduced. The fastening strength at the boundary portion becomes high. In other words, when torque is transmitted between the ring gear and the differential case based on the fastening force of the fastening member, the shared torque of each fastening member at the boundary portion is reduced. For this reason, even if the surface pressure of the pressing surface of the fastening member at the boundary portion is not uniform, the occurrence of slippage and the occurrence of rotational loosening of the fastening member are suppressed. In addition, since the interval between the fastening members other than the boundary portion is relatively large, the number of fastening members is kept small and the increase in the number of parts and the weight increase are suppressed as compared with the case where the number of fastening members is simply increased. However, the rotational looseness of the fastening member at the boundary portion can be appropriately suppressed.

本発明の一実施例であるデフケース組立体を備えたディファレンシャル装置の断面図で、図４におけるIV−IV矢視断面に相当する断面図である。It is sectional drawing of the differential apparatus provided with the differential case assembly which is one Example of this invention, and is sectional drawing equivalent to the IV-IV arrow cross section in FIG. 図１のデフケース組立体を単独で示した斜視図である。It is the perspective view which showed the differential case assembly of FIG. 1 independently. 図２のデフケース組立体の断面図で、図１に対応する図である。FIG. 3 is a cross-sectional view of the differential case assembly of FIG. 2, corresponding to FIG. 1. 図２のデフケース組立体の正面図である。FIG. 3 is a front view of the differential case assembly of FIG. 2. 図２のデフケース組立体のボルト締結部分の拡大断面図で、図４におけるＶ−Ｖ矢視部分の断面図である。FIG. 5 is an enlarged cross-sectional view of a bolt fastening portion of the differential case assembly of FIG. 2, and is a cross-sectional view taken along the line VV in FIG. 4. 図２のデフケースの窓部側が噛合い位置（図の上方位置）の場合に、噛合荷重の反力によって生じる撓み変形を説明する図で、図４におけるVI−VI矢視部分の断面図である。FIG. 5 is a diagram for explaining bending deformation caused by a reaction force of a meshing load when the window side of the differential case in FIG. 2 is a meshing position (upward position in the figure), and is a cross-sectional view taken along the line VI-VI in FIG. .

本発明は、例えば車両用駆動装置の左右輪、或いは前後輪に動力を分配するディファレンシャル装置のデフケース組立体に好適に適用されるが、車両用駆動装置以外のディファレンシャル装置にも適用され得る。デフケースは、例えば鋳鉄等の鋳物によって一体に構成されるが、必要に応じて複数の部材で構成してボルトや溶接等により一体的に結合しても良い。リングギヤとしてはすば歯車が用いられる場合に本発明は好適に適用されるが、ハイポイドギヤやまがりばかさ歯車など、噛合荷重の反力でスラスト荷重が発生する他の歯車が用いられても、目的とする作用効果が得られる。基本的にスラスト荷重が発生しない平歯車をリングギヤとして用いる場合にも、締結部材が不等分間隔で設けられる本発明のデフケース組立体を採用することができる。   The present invention is preferably applied to, for example, a differential case assembly of a differential device that distributes power to the left and right wheels or front and rear wheels of a vehicle drive device, but can also be applied to a differential device other than the vehicle drive device. The differential case is integrally formed of, for example, cast iron or the like, but may be formed of a plurality of members as necessary and integrally connected by bolts, welding, or the like. The present invention is preferably applied when a helical gear is used as the ring gear. However, even if other gears such as hypoid gears and spiral bevel gears that generate a thrust load due to the reaction force of the meshing load are used, The following effects can be obtained. Even when a spur gear that basically does not generate a thrust load is used as a ring gear, the differential case assembly of the present invention in which the fastening members are provided at unequal intervals can be employed.

複数の締結部材は、例えば一定の径寸法の同一規格のボルトが好適に用いられるが、径寸法が異なる複数種類のボルトを組み合わせて用いて締結することも可能である。締結部材としてボルトを用いる場合、例えばギヤ取付部およびリングギヤの何れか一方に雌ねじが設けられるとともに、他方にボルト挿通穴が設けられ、他方の部材のボルト挿通穴を挿通させられたボルトが一方の部材の雌ねじに螺合されることによって両者が一体的に締結されるが、ギヤ取付部およびリングギヤの両方にボルト挿通穴を設け、両者を貫通するようにボルトを挿通させて、先端部にナットを螺合して締結することも可能である。ギヤ取付部およびリングギヤの何れか一方にボルトを溶接等で固設し、他方に設けられたボルト挿通穴内を挿通させて先端部にナットを螺合するようにしても良いなど、種々の態様が可能である。   For example, bolts having the same diameter and the same standard are preferably used as the plurality of fastening members. However, a plurality of types of bolts having different diameters can be combined and fastened. When using a bolt as a fastening member, for example, either one of the gear mounting portion and the ring gear is provided with a female screw, the other is provided with a bolt insertion hole, and the bolt inserted through the bolt insertion hole of the other member is one of the bolts. Both are integrally fastened by being screwed to the female screw of the member. Bolt insertion holes are provided in both the gear mounting portion and the ring gear, and bolts are inserted so as to penetrate both, and nuts are provided at the tip portion. It is also possible to fasten and fasten. There are various modes such as fixing a bolt to one of the gear mounting portion and the ring gear by welding or the like, and inserting a nut into the tip portion by inserting the bolt insertion hole provided on the other. Is possible.

リングギヤは、例えばギヤ部と該ギヤ部の内周面から内周側へ突き出す円環形状の取付板部とを備えて構成され、その取付板部がギヤ取付部に重ね合わされて複数の締結部材により一体的に固設される。その場合に、例えば引用文献２に記載のように、リングギヤの取付板部の内周側に、デフケースのギヤ取付部に設けられた外向き段差部をインロウ嵌合したり、ギヤ部の内周面とギヤ取付部の外周縁部とをスプライン嵌合したりすることもできる。ギヤ部の内周面にデフケースのギヤ取付部の外周縁部をインロウ嵌合したり、ギヤ取付部に設けられた外向き段差部と取付板部の内周縁部とをスプライン嵌合したりすることも可能である。また、スプライン嵌合を締り嵌めで行なうことでインロウ嵌合を省略することもできる。なお、本発明の実施に際しては、インロウ嵌合およびスプライン嵌合を何れも省略することができる。   The ring gear is configured to include, for example, a gear portion and an annular mounting plate portion protruding from the inner peripheral surface of the gear portion toward the inner peripheral side, and the mounting plate portion is overlapped with the gear mounting portion to form a plurality of fastening members. Are integrally fixed. In that case, for example, as described in the cited document 2, an outwardly stepped portion provided in the gear mounting portion of the differential case is fitted inward on the inner peripheral side of the ring gear mounting plate portion, or the inner periphery of the gear portion is It is also possible to perform spline fitting between the surface and the outer peripheral edge of the gear mounting portion. The outer peripheral edge of the gear mounting portion of the differential case is in-row fitted to the inner peripheral surface of the gear portion, or the outward stepped portion provided on the gear mounting portion and the inner peripheral edge of the mounting plate portion are spline-fitted. It is also possible. Further, by performing spline fitting by interference fitting, in-row fitting can be omitted. In implementing the present invention, both in-row fitting and spline fitting can be omitted.

複数の締結部材の不等分間隔は、少なくとも柱部と窓部との境界部分における締結部材の間隔が他の部分よりも小さくなるように定められる。具体的には、例えば回転中心線まわりにおいて柱部と窓部との境界線を跨いで隣接する締結部材の間隔が、該境界線を跨がずに隣接する締結部材の間隔よりも小さくされるが、境界線上に締結部材が設けられる場合でも、その締結部材に隣接する締結部材との間隔が他よりも小さければ良い。複数の境界部分における締結部材の間隔は同じであっても良いが、互いに相違していても良く、少なくとも境界線を跨がずに隣接する締結部材の間隔よりも小さければ良い。   The unequal interval between the plurality of fastening members is determined so that the interval between the fastening members at least at the boundary portion between the column portion and the window portion is smaller than the other portions. Specifically, for example, the interval between the adjacent fastening members straddling the boundary line between the column portion and the window portion around the rotation center line is made smaller than the interval between the adjacent fastening members without straddling the boundary line. However, even when the fastening member is provided on the boundary line, it is only necessary that the interval between the fastening member adjacent to the fastening member is smaller than the others. The intervals between the fastening members at the plurality of boundary portions may be the same, but may be different from each other, as long as they are at least smaller than the interval between the adjacent fastening members without straddling the boundary line.

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

図１は、本発明の一実施例であるデフケース組立体１０を備えているディファレンシャル装置１２の断面図で、図４におけるIV−IV矢視断面に相当する部分の断面図である。図２は、デフケース組立体１０を単独で示した斜視図で、図３はデフケース組立体１０の断面図で、図１に対応する図である。また、図４はデフケース組立体１０の正面図、すなわち図３における右方向から見た図である。   FIG. 1 is a cross-sectional view of a differential device 12 including a differential case assembly 10 according to an embodiment of the present invention, and is a cross-sectional view of a portion corresponding to a cross section taken along line IV-IV in FIG. 2 is a perspective view showing the differential case assembly 10 alone, and FIG. 3 is a cross-sectional view of the differential case assembly 10 and corresponding to FIG. 4 is a front view of the differential case assembly 10, that is, a view seen from the right direction in FIG.

デフケース組立体１０は、デフケース１４の外周側に複数（実施例では８本）のボルト１６を用いてリングギヤ１８を一体的に取り付けたものである。デフケース１４は、共通の回転中心線Ｓ上に設けられた両端部の一対のジャーナル２０、２２と、そのジャーナル２０、２２を連結する一対の柱部２４、２６とを備えており、全体として中空形状を成しているとともに、一対のジャーナル２０、２２を介してベアリング２８、３０により図示しないトランスアクスルケース等に回転中心線Ｓまわりに回転可能に支持される。一対の柱部２４、２６は、中間部分が回転中心線Ｓから離間するように外周側へ膨出する湾曲形状を成しているとともに、回転中心線Ｓを挟んで反対側に対称的に設けられており、回転中心線Ｓまわりにおいて一対の柱部２４、２６の間にそれぞれ窓部３２、３４が設けられている。窓部３２、３４は、デフケース１４の内部に傘歯車式の差動機構４０を挿入して組み付けたり、そのための切削加工等を行なったりするための開口部である。柱部２４、２６は、本実施例では回転中心線Ｓを挟んで対称形状を成すように設けられているが、非対称形状であっても良い。窓部３２、３４についても、本実施例では回転中心線Ｓを挟んで対称形状を成すように設けられているが、非対称形状であっても良い。   In the differential case assembly 10, a ring gear 18 is integrally attached to the outer peripheral side of the differential case 14 using a plurality of (eight in the embodiment) bolts 16. The differential case 14 includes a pair of journals 20 and 22 at both ends provided on a common rotation center line S, and a pair of pillars 24 and 26 that connect the journals 20 and 22, and is hollow as a whole. It has a shape and is supported by a bearing 28, 30 via a pair of journals 20, 22 so as to be rotatable around a rotation center line S by a transaxle case (not shown). The pair of column portions 24 and 26 have a curved shape that bulges to the outer peripheral side so that the intermediate portion is separated from the rotation center line S, and is provided symmetrically on the opposite side across the rotation center line S. The window portions 32 and 34 are provided between the pair of column portions 24 and 26 around the rotation center line S, respectively. The window portions 32 and 34 are openings for inserting and assembling a bevel gear type differential mechanism 40 into the differential case 14 and performing cutting processing for the assembly. In the present embodiment, the column portions 24 and 26 are provided so as to have a symmetrical shape with the rotation center line S therebetween, but may be asymmetrical. The windows 32 and 34 are also provided so as to have a symmetrical shape with the rotation center line S interposed therebetween in the present embodiment, but may be asymmetrical.

差動機構４０は、一対のピニオン４２、４４、および一対のサイドギヤ４６、４８から成り、一対のピニオン４２、４４は単一のピニオンピン５０に回転自在に支持されている。ピニオンピン５０は、デフケース１４の一対の柱部２４、２６に跨がって配設され、回転中心線Ｓに対して直交する姿勢で支持されており、デフケース１４と一体的に回転中心線Ｓまわりに回転させられる。柱部２４、２６には、それぞれピニオンピン５０が挿通させられる取付穴２４ａ、２６ａが設けられており、止めピン５２によってピニオンピン５０が一方の柱部２４に固定されている。サイドギヤ４６、４８は、それぞれ回転中心線Ｓまわりに回転自在にデフケース１４によって支持されているとともに、スプライン嵌合により一対の回転軸５４、５６に動力伝達可能に連結される。これにより、リングギヤ１８と一対の回転軸５４、５６との間で差動回転可能に動力伝達が行なわれる。このようなディファレンシャル装置１２は、例えばエンジン等の原動機から自動変速機等を介してリングギヤ１８に伝達された動力を、一対の回転軸５４、５６を介して左右の駆動輪に分配する車両用駆動装置のディファレンシャル装置として好適に用いられる。なお、図示は省略するが、一対のピニオン４２、４４、および一対のサイドギヤ４６、４８の回転支持部には、それぞれ必要に応じて軸受等が設けられる。   The differential mechanism 40 includes a pair of pinions 42 and 44 and a pair of side gears 46 and 48, and the pair of pinions 42 and 44 is rotatably supported by a single pinion pin 50. The pinion pin 50 is disposed so as to straddle the pair of column portions 24 and 26 of the differential case 14 and is supported in a posture orthogonal to the rotation center line S. The rotation center line S is integrated with the differential case 14. Rotated around. Mounting holes 24 a and 26 a through which the pinion pins 50 are inserted are respectively provided in the column portions 24 and 26, and the pinion pins 50 are fixed to one column portion 24 by a stop pin 52. The side gears 46 and 48 are supported by the differential case 14 so as to be rotatable about the rotation center line S, respectively, and are connected to the pair of rotating shafts 54 and 56 by spline fitting so that power can be transmitted. Thereby, power transmission is performed between the ring gear 18 and the pair of rotating shafts 54 and 56 so as to be differentially rotatable. Such a differential device 12 is a vehicle drive that distributes power transmitted to a ring gear 18 from a prime mover such as an engine via an automatic transmission or the like to left and right drive wheels via a pair of rotating shafts 54 and 56. It is suitably used as a differential device for the device. In addition, although illustration is abbreviate | omitted, the rotation support part of a pair of pinions 42 and 44 and a pair of side gears 46 and 48 is each provided with a bearing etc. as needed.

上記デフケース組立体１０のデフケース１４は、例えば鋳鉄等の鋳物によって一体に構成される。デフケース１４の外周部には、外周側へ突き出すように円環形状の板状の外向きフランジ６０が一体に設けられている。この外向きフランジ６０はギヤ取付部に相当し、回転中心線Ｓと平行な方向において前記窓部３２、３４に隣接する位置、具体的には一方のジャーナル２０側に隣接する位置に、回転中心線Ｓに対して直交する姿勢で設けられている。前記一対の柱部２４、２６の一端部、すなわちジャーナル２０側の端部は、外向きフランジ６０に一体に連結されている。一方、前記リングギヤ１８は、はすば歯車が設けられた円筒形状のギヤ部６２と、そのギヤ部６２の内周面（裏面）から内周側へ突き出す円環形状の取付板部６４とを備えて構成されており、回転中心線Ｓと平行な方向において取付板部６４が外向きフランジ６０に重ね合わされ、且つ回転中心線Ｓと同心に配置されて、回転中心線Ｓまわりに設けられる複数のボルト１６を介して外向きフランジ６０に一体的に取り付けられている。複数のボルト１６は締結部材に相当し、本実施例では径寸法が等しい同一規格のボルト１６が用いられている。   The differential case 14 of the differential case assembly 10 is integrally formed of a casting such as cast iron. An annular plate-like outward flange 60 is integrally provided on the outer peripheral portion of the differential case 14 so as to protrude toward the outer peripheral side. The outward flange 60 corresponds to a gear mounting portion, and in the direction parallel to the rotation center line S, the rotation center is located at a position adjacent to the window portions 32 and 34, specifically, at a position adjacent to one journal 20 side. It is provided in a posture orthogonal to the line S. One end portion of the pair of column portions 24 and 26, that is, the end portion on the journal 20 side, is integrally connected to the outward flange 60. On the other hand, the ring gear 18 includes a cylindrical gear portion 62 provided with a helical gear, and an annular mounting plate portion 64 protruding from the inner peripheral surface (back surface) of the gear portion 62 to the inner peripheral side. A plurality of mounting plate portions 64 are overlapped with the outward flange 60 in a direction parallel to the rotation center line S, are arranged concentrically with the rotation center line S, and are provided around the rotation center line S. Are integrally attached to the outward flange 60 via bolts 16. The plurality of bolts 16 correspond to fastening members, and in the present embodiment, bolts 16 of the same standard having the same diameter are used.

図５は、ボルト締結部分の拡大断面図で、図４におけるＶ−Ｖ矢視部分の断面図である。図５から明らかなように、リングギヤ１８の取付板部６４には雌ねじ６６が設けられ、外向きフランジ６０にはボルト挿通穴６８が設けられており、ボルト１６のねじ部がボルト挿通穴６８を挿通させられてリングギヤ１８の雌ねじ６６に螺合される。雌ねじ６６およびボルト挿通穴６８は回転中心線Ｓと平行で、回転中心線Ｓと平行な方向にボルト１６がねじ込まれる。ボルト１６と雌ねじ６６との締結力により、ボルト１６の頭部１６ａが外向きフランジ６０に設けられた座面６０ａに押圧され、取付板部６４と頭部１６ａとの間で外向きフランジ６０が挟圧された状態で、その外向きフランジ６０に対してリングギヤ１６が一体的に固設される。この場合、頭部１６ａと座面６０ａとの間の摩擦によってボルト１６の回転緩みが防止され、締結状態が維持される。必要に応じて頭部１６ａと座面６０ａとの間に座金を配置することもできる。   FIG. 5 is an enlarged cross-sectional view of the bolt fastening portion, and is a cross-sectional view taken along the line VV in FIG. As is apparent from FIG. 5, the mounting plate portion 64 of the ring gear 18 is provided with a female screw 66, the outward flange 60 is provided with a bolt insertion hole 68, and the screw portion of the bolt 16 has a bolt insertion hole 68. It is inserted and screwed into the female screw 66 of the ring gear 18. The female screw 66 and the bolt insertion hole 68 are parallel to the rotation center line S, and the bolt 16 is screwed in a direction parallel to the rotation center line S. The head 16a of the bolt 16 is pressed against the seat surface 60a provided on the outward flange 60 by the fastening force between the bolt 16 and the female screw 66, and the outward flange 60 is interposed between the mounting plate portion 64 and the head 16a. The ring gear 16 is integrally fixed to the outward flange 60 in a state of being clamped. In this case, the bolt 16 is prevented from loosening due to friction between the head portion 16a and the seat surface 60a, and the fastening state is maintained. A washer may be disposed between the head 16a and the seating surface 60a as necessary.

外向きフランジ６０の外径寸法はギヤ部６２の内周面６２ａの内径寸法よりも僅かに大きく、外向きフランジ６０の外周縁部はギヤ部６２の内側にインロウ嵌合されている。これにより、外向きフランジ６０とリングギヤ１８との径方向（図５における上下方向）の相対変位が抑制され、その相対変位による頭部１６ａの滑りでボルト１６の回転緩みが発生することが抑制される。すなわち、リングギヤ１８には噛合荷重の反力で径方向（図５における下向き）の荷重が作用し、外向きフランジ６０に対してリングギヤ１８が図５の下方側へ相対変位する力が発生するが、外向きフランジ６０がギヤ部６２の内側にインロウ嵌合されることによって相対変位が抑制され、その相対変位に起因するボルト１６の回転緩みが抑制される。インロウ嵌合を許容するように、ボルト挿通穴６８とボルト１６の軸部との間には所定の遊びが設けられているとともに、リングギヤ１８の取付板部６４の内周端部６４ａとデフケース１４との間にも所定の隙間が設けられている。   The outer diameter dimension of the outward flange 60 is slightly larger than the inner diameter dimension of the inner peripheral surface 62 a of the gear portion 62, and the outer peripheral edge portion of the outward flange 60 is in-row fitted inside the gear portion 62. Thereby, the relative displacement in the radial direction (vertical direction in FIG. 5) between the outward flange 60 and the ring gear 18 is suppressed, and the occurrence of rotational loosening of the bolt 16 due to the slip of the head 16a due to the relative displacement is suppressed. The In other words, a radial load (downward in FIG. 5) acts on the ring gear 18 due to the reaction force of the meshing load, and a force is generated that causes the ring gear 18 to be relatively displaced downward in FIG. When the outward flange 60 is fitted inward to the gear portion 62, the relative displacement is suppressed, and the loosening of the bolt 16 due to the relative displacement is suppressed. A predetermined play is provided between the bolt insertion hole 68 and the shaft portion of the bolt 16 so as to allow in-row fitting, and the inner peripheral end portion 64 a of the mounting plate portion 64 of the ring gear 18 and the differential case 14. A predetermined gap is also provided between the two.

一方、ギヤ部６２にはすば歯車が設けられたリングギヤ１８においては、噛合荷重の反力でスラスト荷重Ｆが発生する。このため、例えば図６に示すように、リングギヤ１８の噛合側（図６における上方側）では、スラスト荷重Ｆにより外向きフランジ６０が回転中心線Ｓと平行な方向（図６では左方向）へ撓み変形する。本実施例では、外向きフランジ６０の外周縁部がギヤ部６２の内側にインロウ嵌合されているため、図６に示す外向きフランジ６０の撓み変形時においても、その変形に倣ってリングギヤ１８が変形させられるだけで、径方向へ相対変位する可能性が小さい。これに対し、例えば特許文献２に記載のように、取付板部６４の内周端部６４ａの内側に外向きフランジ６０の段差部をインロウ嵌合した場合には、図６のように外向きフランジ６０が撓み変形させられると、その外向きフランジ６０に対して相対的にリングギヤ１８を外周側へ押し出す方向の力が発生するため、その径方向の相対変位によってボルト１６の回転緩みが発生する可能性がある。図６は、理解を容易にするため、撓み変形を極端に拡大して示した図である。   On the other hand, in the ring gear 18 in which the gear portion 62 is provided with a helical gear, a thrust load F is generated by the reaction force of the meshing load. For this reason, for example, as shown in FIG. 6, on the meshing side (upper side in FIG. 6) of the ring gear 18, the outward flange 60 is parallel to the rotation center line S by the thrust load F (leftward in FIG. 6). Deforms and deforms. In the present embodiment, since the outer peripheral edge of the outward flange 60 is in-row fitted inside the gear portion 62, the ring gear 18 follows the deformation even when the outward flange 60 shown in FIG. The possibility of relative displacement in the radial direction is small simply by deforming the. On the other hand, for example, as described in Patent Document 2, when the stepped portion of the outward flange 60 is in-fitted inside the inner peripheral end portion 64a of the mounting plate portion 64, the outward direction as shown in FIG. When the flange 60 is bent and deformed, a force in the direction of pushing the ring gear 18 toward the outer peripheral side relative to the outward flange 60 is generated, so that the bolt 16 is loosened due to the relative displacement in the radial direction. there is a possibility. FIG. 6 is an extremely enlarged view showing the bending deformation for easy understanding.

また、本実施例のデフケース組立体１０の場合、柱部２４、２６の有無によって外向きフランジ６０の剛性、すなわち図６に示す撓み変形に対する剛性が、回転中心線Ｓまわりにおいて変化している。すなわち、窓部３２、３４が設けられた部分は、柱部２４、２６が設けられた部分に比較して剛性が低くなり、図６に示す撓み変形量δが、柱部２４、２６が設けられた部分に比較して窓部３２、３４が設けられた部分では大きくなる。このため、窓部３２、３４と柱部２４、２６との境界線Ｌｂ（図４参照）の近傍部分では、周方向において撓み変形量δに勾配（変化）が生じ、ボルト１６の頭部１６ａと座面６０ａとの接触（面圧）が不均一になり、それ等の間で滑りが生じてボルト１６の回転緩みが発生し易くなる。図６は、デフケース１４の窓部３４側が噛合い位置（図の上方位置）の場合に、噛合荷重の反力によって生じる撓み変形を説明する図で、図４におけるVI−VI矢視部分の断面図である。   Further, in the case of the differential case assembly 10 of this embodiment, the rigidity of the outward flange 60, that is, the rigidity against the bending deformation shown in FIG. That is, the portion where the window portions 32 and 34 are provided is less rigid than the portion where the column portions 24 and 26 are provided, and the bending deformation amount δ shown in FIG. Compared with the provided part, it becomes large in the part in which the window parts 32 and 34 were provided. Therefore, in the vicinity of the boundary line Lb (see FIG. 4) between the window portions 32 and 34 and the column portions 24 and 26, a gradient (change) occurs in the bending deformation amount δ in the circumferential direction, and the head 16a of the bolt 16 And the seating surface 60a are non-uniform in contact (surface pressure), and slip occurs between them, and the bolt 16 is liable to loosen. FIG. 6 is a view for explaining the bending deformation caused by the reaction force of the meshing load when the window portion 34 side of the differential case 14 is in the meshing position (the upper position in the figure). FIG.

これに対し、本実施例では、図４に示すように、柱部２４、２６と窓部３２、３４との境界部分、すなわち境界線Ｌｂの近傍部分（４箇所）におけるボルト１６の間隔Ｄ３が、境界線Ｌｂを含まない他の部分のボルト１６の間隔Ｄ１、Ｄ２よりも小さくなるように、回転中心線Ｓまわりにおける複数のボルト１６の間隔が不等分間隔とされている。具体的には、回転中心線Ｓまわりにおいて境界線Ｌｂを跨いで隣接する２本のボルト１６の間隔Ｄ３は、境界線Ｌｂを跨がずに隣接する２本のボルト１６の間隔Ｄ１またはＤ２よりも小さい。間隔Ｄ１は、柱部２４、２６が設けられた部分に位置する一対ずつのボルト１６の間隔で、間隔Ｄ２は、窓部３２、３４が設けられた部分に位置する一対ずつのボルト１６の間隔であり、何れも境界部分の間隔Ｄ３よりも大きい。   On the other hand, in this embodiment, as shown in FIG. 4, the distance D3 between the bolts 16 at the boundary portions between the column portions 24 and 26 and the window portions 32 and 34, that is, the vicinity portions (four locations) of the boundary line Lb. The intervals between the plurality of bolts 16 around the rotation center line S are unequal intervals so as to be smaller than the intervals D1 and D2 between the bolts 16 in other portions not including the boundary line Lb. Specifically, the interval D3 between the two bolts 16 that are adjacent to each other across the boundary line Lb around the rotation center line S is greater than the interval D1 or D2 between the two adjacent bolts 16 that do not extend across the boundary line Lb. Is also small. The interval D1 is the interval between the pair of bolts 16 located in the portion where the pillar portions 24 and 26 are provided, and the interval D2 is the interval between the pair of bolts 16 located in the portion where the window portions 32 and 34 are provided. These are both larger than the distance D3 between the boundary portions.

このような本実施例のデフケース組立体１０においては、柱部２４、２６と窓部３２、３４との境界部分におけるボルト１６の間隔Ｄ３が小さくなるように、回転中心線Ｓまわりにおいて複数のボルト１６の間隔が不等分間隔とされているため、その境界部分における締結強度が高くなる。言い換えれば、リングギヤ１８とデフケース１４との間でボルト１６の締結力に基づいてトルク伝達が行なわれる際に、間隔Ｄ３が小さい境界部分の各ボルト１６の分担トルクが低減される。このため、境界部分におけるボルト１６の頭部１６ａと座面６０ａとの間の面圧が不均一であっても、それ等の間で滑りが生じてボルト１６の回転緩みが発生することが抑制される。   In such a differential case assembly 10 of the present embodiment, a plurality of bolts around the rotation center line S so that the distance D3 of the bolts 16 at the boundary portions between the column portions 24 and 26 and the window portions 32 and 34 is reduced. Since the interval of 16 is an unequal interval, the fastening strength at the boundary portion is increased. In other words, when torque transmission is performed between the ring gear 18 and the differential case 14 based on the fastening force of the bolt 16, the shared torque of each bolt 16 at the boundary portion where the distance D3 is small is reduced. For this reason, even if the surface pressure between the head portion 16a of the bolt 16 and the seating surface 60a at the boundary portion is not uniform, it is possible to prevent slippage between them and the bolt 16 from rotating and loosening. Is done.

また、境界線Ｌｂを跨がない部分のボルト１６の間隔Ｄ１、Ｄ２は比較的大きいため、単純にボルト１６の数を増やすだけの場合に比較して、ボルト１６の数を少なく維持して部品点数の増加や重量増加を抑制しつつ、境界部分のボルト１６の回転緩みを適切に抑制できる。   In addition, since the distances D1 and D2 between the bolts 16 that do not straddle the boundary line Lb are relatively large, the number of bolts 16 is kept small compared to the case where the number of bolts 16 is simply increased. While suppressing an increase in the number of points and an increase in weight, it is possible to appropriately suppress the loose rotation of the bolt 16 at the boundary portion.

また、本実施例では外向きフランジ６０の外周縁部がギヤ部６２の内周面６２ａの内側にインロウ嵌合されているため、外向きフランジ６０とリングギヤ１８との径方向の相対変位が抑制され、その相対変位による頭部１６ａの滑りでボルト１６の回転緩みが発生することが抑制される。特に、図６に示すような外向きフランジ６０の撓み変形時においても、その変形に倣ってリングギヤ１８が変形させられるだけで、径方向へ相対変位する可能性が少なく、ボルト１６の回転緩みが適切に抑制される。   Further, in this embodiment, the outer peripheral edge of the outward flange 60 is in-row fitted inside the inner peripheral surface 62a of the gear portion 62, so that the radial relative displacement between the outward flange 60 and the ring gear 18 is suppressed. Thus, the loosening of the rotation of the bolt 16 due to the slip of the head 16a due to the relative displacement is suppressed. In particular, even when the outward flange 60 is bent and deformed as shown in FIG. 6, the ring gear 18 is only deformed following the deformation, so that there is little possibility of relative displacement in the radial direction, and the bolt 16 is loosened. Appropriately suppressed.

なお、上記実施例では柱部２４、２６、および窓部３２、３４の領域にそれぞれ２本ずつボルト１６が設けられているが、境界部分の間隔Ｄ３よりも相互の間隔が大きくなることを条件として、例えば回転中心線Ｓまわりの角度範囲が大きい窓部３２、３４の領域にボルト１６を３本ずつ設けることもできる。ボルト１６の本数は、リングギヤ１８の大きさ等に応じて適宜定められる。   In the above embodiment, two bolts 16 are provided in each of the regions of the pillar portions 24 and 26 and the window portions 32 and 34, provided that the mutual interval is larger than the interval D3 of the boundary portion. As an example, three bolts 16 may be provided in the region of the windows 32 and 34 having a large angular range around the rotation center line S. The number of the bolts 16 is appropriately determined according to the size of the ring gear 18 and the like.

また、図６ではスラスト荷重Ｆにより外向きフランジ６０が柱部２４、２６と反対方向（図の左方向）へ撓み変形させられる場合について説明したが、逆方向すなわち柱部２４、２６側へ外向きフランジ６０が撓み変形させられる場合にも、本発明は同様に適用され得る。   FIG. 6 illustrates the case where the outward flange 60 is bent and deformed in the direction opposite to the column parts 24 and 26 (the left direction in the figure) by the thrust load F. The present invention can be similarly applied when the directional flange 60 is bent and deformed.

以上、本発明の実施例を図面に基づいて詳細に説明したが、これはあくまでも一実施形態であり、本発明は当業者の知識に基づいて種々の変更，改良を加えた態様で実施することができる。   As mentioned above, although the Example of this invention was described in detail based on drawing, this is an embodiment to the last, and this invention implements in the aspect which added various change and improvement based on the knowledge of those skilled in the art. Can do.

１０：デフケース組立体 １４：デフケース １６：ボルト（締結部材） １８：リングギヤ ２４、２６：柱部 ３２、３４：窓部 ６０：外向きフランジ（ギヤ取付部） Ｓ：回転中心線 Ｌｂ：境界線 Ｄ３：境界部分のボルトの間隔   10: Differential case assembly 14: Differential case 16: Bolt (fastening member) 18: Ring gear 24, 26: Column portion 32, 34: Window portion 60: Outward flange (gear mounting portion) S: Center of rotation Lb: Boundary line D3 : Boundary bolt distance

Claims (1)

中空形状を成しているとともに、回転中心線を挟んで反対側に一対の柱部が設けられており、該回転中心線まわりにおいて該一対の柱部の間にそれぞれ窓部が設けられているデフケースと、
前記デフケースの外周部に一体に設けられた円環形状のギヤ取付部と、
前記回転中心線と平行な方向において前記ギヤ取付部に重ね合わされるように、該回転中心線と同心に前記デフケースの外周部に配置され、該回転中心線まわりに設けられる複数の締結部材を介して前記ギヤ取付部に一体的に取り付けられたリングギヤと、
を有するデフケース組立体において、
前記柱部と前記窓部との境界部分における前記締結部材の間隔が小さくなるように、前記回転中心線まわりにおいて前記複数の締結部材の間隔が不等分間隔とされている
ことを特徴とするデフケース組立体。 It has a hollow shape, and a pair of pillars are provided on the opposite side across the rotation center line, and a window is provided between the pair of pillars around the rotation center line. Differential case,
An annular gear mounting portion integrally provided on the outer peripheral portion of the differential case;
Via a plurality of fastening members disposed on the outer periphery of the differential case concentrically with the rotation center line so as to be superimposed on the gear mounting portion in a direction parallel to the rotation center line. A ring gear integrally attached to the gear attachment portion,
A differential case assembly having
The intervals between the plurality of fastening members are unequal intervals around the rotation center line so that the interval between the fastening members at the boundary portion between the column portion and the window portion is reduced. Differential case assembly.
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Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102019218193A1 (en) 2018-11-27 2020-05-28 Musashi Seimitsu Industry Co., Ltd. DIFFERENTIAL DEVICE

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JP2010265924A (en) * 2009-05-12 2010-11-25 Toyota Motor Corp Differential device
JP2015081630A (en) * 2013-10-22 2015-04-27 スズキ株式会社 Differential device
JP2017036780A (en) * 2015-08-07 2017-02-16 トヨタ自動車株式会社 Differential device for vehicle

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Publication number Priority date Publication date Assignee Title
JP2010265924A (en) * 2009-05-12 2010-11-25 Toyota Motor Corp Differential device
JP2015081630A (en) * 2013-10-22 2015-04-27 スズキ株式会社 Differential device
JP2017036780A (en) * 2015-08-07 2017-02-16 トヨタ自動車株式会社 Differential device for vehicle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019218193A1 (en) 2018-11-27 2020-05-28 Musashi Seimitsu Industry Co., Ltd. DIFFERENTIAL DEVICE
US10883587B2 (en) 2018-11-27 2021-01-05 Musashi Seimitsu Industry Co., Ltd. Differential device

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