JP2003049863A - Shaft coupling for vehicle - Google Patents
Shaft coupling for vehicleInfo
- Publication number
- JP2003049863A JP2003049863A JP2001238635A JP2001238635A JP2003049863A JP 2003049863 A JP2003049863 A JP 2003049863A JP 2001238635 A JP2001238635 A JP 2001238635A JP 2001238635 A JP2001238635 A JP 2001238635A JP 2003049863 A JP2003049863 A JP 2003049863A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- annular plate
- hole
- arm portion
- insertion hole
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/78—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings
- F16D3/79—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings the disc or ring being metallic
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、車両のプロペラシ
ャフト部分等に用いられる軸継手に関し、とりわけ、軸
方向の挙動変位を弾性的に吸収する機能を備えた軸継手
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shaft coupling used for a propeller shaft portion of a vehicle, and more particularly to a shaft coupling having a function of elastically absorbing behavioral displacement in the axial direction.
【０００２】[0002]
【従来の技術】車両のプロペラシャフト部分に用いられ
る軸継手として、例えば、実開昭６３-１７８６３２号
公報に記載されたもののようにゴム弾性体を用いたもの
が知られている。2. Description of the Related Art As a shaft coupling used for a propeller shaft portion of a vehicle, there is known a shaft coupling using a rubber elastic body such as that described in Japanese Utility Model Laid-Open No. 63-178632.
【０００３】この軸継手は、図８及び図９に示すよう
に、ゴム弾性体から成るほぼ円環状の本体部１に周方向
等間隔に複数のブッシュ２が設けられ、隣接するブッシ
ュ２，２相互が剛性の高い補強線材８によって連結され
ている。第１軸３と第２軸４の各端部には、複数の分岐
アーム（結合部）５ａ，６ａを有するヨーク５，６が夫
々取付けられ、この両ヨーク５，６の分岐アーム５ａ，
６ａが軸継手のブッシュ２に円周方向で交互にボルト１
２（締結手段）によって結合されている。そして、第１
軸３の先端部は軸継手の本体部１を貫通して突出し、第
２軸４にゴムブッシュ７を介してセンタリングされてい
る。As shown in FIGS. 8 and 9, this shaft coupling has a plurality of bushes 2 provided at equal intervals in the circumferential direction on a substantially annular main body 1 made of a rubber elastic body, and adjacent bushes 2, 2 The reinforcing wire rods 8 having high rigidity are connected to each other. At each end of the first shaft 3 and the second shaft 4, yokes 5 and 6 having a plurality of branch arms (coupling portions) 5a and 6a are respectively attached, and the branch arms 5a and 5a of the two yokes 5 and 6, respectively.
6a is bolt 1 alternately in the bush 2 of the shaft coupling in the circumferential direction.
2 (fastening means). And the first
The tip of the shaft 3 penetrates the main body 1 of the shaft coupling and projects, and is centered on the second shaft 4 via a rubber bush 7.
【０００４】この軸継手は、隣接するブッシュ２が補強
線材８によって結合されているため、両軸３，４間の軸
方向の相対変位は弾性的に許容し、回転方向の動力は補
強線材８の張力によって剛的に伝達することができる。In this shaft joint, since the adjacent bushes 2 are connected by the reinforcing wire rod 8, the axial relative displacement between the shafts 3 and 4 is elastically permitted, and the power in the rotational direction is reinforced. It can be transmitted rigidly by the tension.
【０００５】しかし、この軸継手にあっては、部品点数
が多くなるばかりか、装置全体が大型化し易い等の問題
がある。そこで、近年、これに代わる軸継手として金属
プレート等を用いたものも開発されている（例えば、実
開昭６０−１８９６２０号公報参照）。However, in this shaft joint, there are problems that not only the number of parts is increased, but also the entire device is easily enlarged. Therefore, in recent years, there has been developed an alternative shaft coupling using a metal plate or the like (see, for example, Japanese Utility Model Laid-Open No. 60-189620).
【０００６】この軸継手は、図１０に示すように、金属
製の環状プレート９に円周方向に等間隔位置にボルト
（締結手段）を挿通する複数の挿通孔１０…が設けら
れ、これらの挿通孔１０…に、第１軸側の結合部と第２
軸側の結合部（図示は省略してあるが、図８及び図９の
分岐アーム５ａ，６ａに相当）が円周方向で交互になる
ように結合されている。そして、環状プレート９は、剛
性の高い金属によって一定の肉厚で形成されていると共
に、一定の径方向幅Ｗの円環状に形成されている。な
お、同図中１１は、ボルト締結時に用いられるワッシャ
である。As shown in FIG. 10, this shaft coupling is provided with a plurality of through holes 10 ... Through which bolts (fastening means) are inserted in circumferentially equidistant positions in a metal annular plate 9, and these are formed. In the insertion hole 10 ...
The shaft side coupling portions (not shown, but corresponding to the branch arms 5a and 6a in FIGS. 8 and 9) are coupled so as to alternate in the circumferential direction. The annular plate 9 is formed of a metal having a high rigidity to have a constant wall thickness, and is also formed in an annular shape having a constant radial width W. In addition, 11 in the figure is a washer used when fastening the bolt.
【０００７】したがって、今、環状プレート９上の隣接
する挿通孔１０，１０間の円周方向の領域を連結アーム
部９ａと呼ぶとすると、各連結アーム部９ａは、軸方向
の挙動変位入力に対して曲げ方向に弾性変形することに
よりその挙動変位を吸収することができ、回動方向（捩
り方向）の入力に対しては変形を生じることなくトルク
を剛的に伝達することができる。また、この軸継手の場
合、第１軸と第２軸は剛性の高いの環状プレート９を介
してセンタリングされるため、特別なセンタリング機構
を設ける必要もない。Therefore, if the area in the circumferential direction between the adjacent through holes 10, 10 on the annular plate 9 is called a connecting arm portion 9a, each connecting arm portion 9a is used for inputting the behavioral displacement in the axial direction. On the other hand, by elastically deforming in the bending direction, the behavioral displacement can be absorbed, and the torque can be rigidly transmitted to the input in the rotation direction (twisting direction) without deformation. Further, in the case of this shaft coupling, since the first shaft and the second shaft are centered via the annular plate 9 having high rigidity, it is not necessary to provide a special centering mechanism.
【０００８】[0008]
【発明が解決しようとする課題】しかしながら、この後
者の従来の軸継手にあっては、挙動変位の吸収性能を高
めるために、環状プレート９の肉厚を薄くしたり、ある
いは連結アーム部９ａの長さを長くして該各連結アーム
部９ａの軸方向剛性を低減する必要があるが、前記環状
プレート９全体の肉厚を薄くするのには限界があり、ま
た、連結アーム部９ａの長さを長くしようとすると環状
プレート９の外径が大きくなって、軸継手全体の大型化
を招く。However, in this latter conventional shaft coupling, the wall thickness of the annular plate 9 is made thin or the connecting arm portion 9a is made thicker in order to enhance the behavior displacement absorption performance. Although it is necessary to increase the length to reduce the axial rigidity of each connecting arm portion 9a, there is a limit to reducing the wall thickness of the annular plate 9 as a whole, and the length of the connecting arm portion 9a is limited. If the length is increased, the outer diameter of the annular plate 9 becomes large, and the overall size of the shaft coupling is increased.
【０００９】つまり、環状プレート９は、変位吸収のた
めに軸方向に変位したとき、締結手段との相対変位や環
状プレート９，９同士の相対変位によってボルト挿通孔
１０の周域部分に摩耗を生じるが、環状プレート全体の
肉厚を薄くしていくと、板厚に対しての摩耗量が多くな
ることから耐久性の低下を招き易くなり、したがって、
環状プレート９全体の厚みはある程度以上には薄くする
ことができない。また、連結アーム部９ａは、その長さ
を単純に長くしようとすると、環状プレート９の外径が
大きくなり、それに伴って軸継手全体が大型化してしま
う。That is, when the annular plate 9 is displaced in the axial direction to absorb the displacement, the peripheral area of the bolt insertion hole 10 is abraded due to the relative displacement between the fastening means and the relative displacement between the annular plates 9 and 9. Although it occurs, if the thickness of the entire annular plate is reduced, the amount of wear with respect to the plate thickness increases, and thus the durability is likely to decrease.
The total thickness of the annular plate 9 cannot be made thinner than a certain degree. Further, if the length of the connecting arm portion 9a is simply increased, the outer diameter of the annular plate 9 is increased, and accordingly, the entire shaft coupling is increased in size.
【００１０】そこで本発明は、耐久性の低下や装置の大
型化を招くことなく、軸方向の挙動変位の吸収性能を高
めることのできる車両用軸継手を提供しようとするもの
である。Therefore, the present invention is intended to provide a shaft coupling for a vehicle capable of enhancing the absorption performance of the behavioral displacement in the axial direction without lowering the durability and increasing the size of the apparatus.
【００１１】[0011]
【課題を解決するための手段】請求項１に記載の発明
は、第１軸と第２軸の突合せ部に回動方向の剛性の大き
い環状プレートを配置し、前記第１軸と第２軸の各端部
に円周方向に間隔をおいて設けられた結合部を、第１軸
側のものと第２軸側のものが円周方向で交互になるよう
に、前記環状プレートに締結手段を介して結合し、前記
環状プレートの円周方向へ所定間隔をもって穿設された
前記締結手段が挿通する各挿通孔間の部位を連結アーム
部とし、該各連結アームの弾性変形により、軸方向の挙
動変位を吸収するようにした車両用軸継手において、前
記連結アーム部に肉抜き孔を形成すると共に、前記連結
アーム部を、隣接する前記両挿通孔の中心を結ぶ環状プ
レートと同心円の円弧曲線の仮想線よりも径方向外側に
位置される外側アーム部と、同仮想線よりも径方向内側
に位置される内側アーム部とに設定し、該内側アーム部
の前記挿通孔の中心と環状プレートの中心を結ぶ線上に
切欠孔を形成し、前記肉抜き孔と切欠孔との間に、環状
プレートのほぼ径方向に沿った一対の連結部位を形成し
たことを特徴としている。According to a first aspect of the present invention, an annular plate having a great rigidity in a rotating direction is arranged at a butting portion of the first shaft and the second shaft, and the first shaft and the second shaft are arranged. Fastening means to the annular plate so that the first shaft side ones and the second shaft side ones are alternately arranged in the circumferential direction at the respective end parts of the Connecting portions through the insertion holes through which the fastening means formed at predetermined intervals in the circumferential direction of the annular plate are connected to form a connecting arm portion, and the elastic deformation of each connecting arm causes an axial direction. In a vehicle shaft joint adapted to absorb the behavioral displacement of the above, a lightening hole is formed in the connecting arm portion, and the connecting arm portion is concentric with an annular plate connecting the centers of the two adjacent through holes. An outer arm located radially outside the imaginary line of the curve And an inner arm portion located radially inward of the imaginary line, and a notch hole is formed on a line connecting the center of the insertion hole of the inner arm portion and the center of the annular plate, and the meat A feature of the present invention is that a pair of connecting portions extending substantially in the radial direction of the annular plate is formed between the cutout hole and the cutout hole.
【００１２】したがって、この発明によれば、連結アー
ム部に肉抜き孔を形成したため、環状プレートの厚さを
薄くしたり、径を増大させることなく、連結アーム部の
軸方向剛性を下げることができる。また、連結アーム部
を、仮想線に対して径方向外側と内側の外側アーム部と
内側アーム部に設定したため、隣接する挿通孔間に作用
する引張力や押付力が一方のアーム部にモーメントとし
て作用しても、そのアーム部の変形は他方のアーム部に
よって抑えられる。Therefore, according to the present invention, since the lightening hole is formed in the connecting arm portion, the axial rigidity of the connecting arm portion can be reduced without reducing the thickness of the annular plate or increasing the diameter thereof. it can. Further, since the connecting arm portion is set to the outer arm portion and the inner arm portion on the radially outer side and the inner side with respect to the imaginary line, the tensile force or the pressing force acting between the adjacent insertion holes acts as a moment on one arm portion. Even if it works, the deformation of the arm portion is suppressed by the other arm portion.
【００１３】しかも、挿通孔と環状プレートの中心側と
の間に切欠部を形成したため、前記挿通孔の内側アーム
部側の剛性が小さくなって、かかる内側アーム部の挿通
孔近傍に作用する軸方向変位時の集中応力を挿通孔の両
側方向に分散させることが可能になる。In addition, since the notch is formed between the insertion hole and the center side of the annular plate, the rigidity of the insertion hole on the inner arm side is reduced, and the shaft acting near the insertion hole of the inner arm is formed. It is possible to disperse the concentrated stress at the time of directional displacement in both directions of the insertion hole.
【００１４】請求項２に記載の発明は、前記連結部位の
前記肉抜き孔と切欠孔との間の幅を、前記挿通孔側より
も環状プレートの中心側の方を小さく設定したことを特
徴としている。According to a second aspect of the present invention, the width between the lightening hole and the notch hole of the connecting portion is set smaller on the center side of the annular plate than on the insertion hole side. I am trying.
【００１５】したがって、この発明によれば、連結部位
の剛性を内側（環状プレートの中心側）と外側（挿通孔
側）で変化させ、外側より内側の方の剛性を小さくした
ことから、軸方向の変位時に該内側の撓み変形が大きく
なり、連結部位に作用する集中応力をさらに分散させる
ことができる。Therefore, according to the present invention, the rigidity of the connecting portion is changed between the inner side (center side of the annular plate) and the outer side (insertion hole side), and the inner side rigidity is made smaller than the outer side. At the time of displacement, the flexural deformation of the inside increases, and the concentrated stress acting on the connecting portion can be further dispersed.
【００１６】請求項３に記載の発明は、前記仮想線上の
前記挿通孔と肉抜き孔との間に、小孔を穿設したことを
特徴としている。The invention according to claim 3 is characterized in that a small hole is provided between the insertion hole and the lightening hole on the imaginary line.
【００１７】したがって、この発明によれば、隣接する
挿通孔間の仮想線上に位置する部位が、小孔によって、
細長い内外側部位に分離されてトルク伝達経路が小孔を
迂回する形になって長さが長くなり、この部位の強度が
小さくなる。このため、回転方向の捩りトルク作用する
とかかる内外側部位が容易に撓み変形して、前記捩りト
ルクにより挿通孔の周囲に作用する集中応力を分散させ
ることができる。Therefore, according to the present invention, the portion located on the imaginary line between the adjacent insertion holes is formed by the small holes.
The torque transmission path is divided into elongated inner and outer portions, and the torque transmission path bypasses the small hole, so that the length becomes longer and the strength of this portion becomes smaller. Therefore, when a torsional torque acts in the rotational direction, the inner and outer portions are easily flexibly deformed, and the concentrated stress acting around the insertion hole due to the torsional torque can be dispersed.
【００１８】また、前記内外側部位によって軸方向のト
ルクに対しても分散させることができる。Further, the inner and outer portions can disperse the torque in the axial direction.
【００１９】[0019]
【発明の実施の形態】以下、本発明にかかる車両用軸継
手の各実施形態を図面に基づいて詳述する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of a vehicle shaft coupling according to the present invention will be described in detail below with reference to the drawings.
【００２０】図１及び図２は、本発明の第１の実施形態
の軸継手が適用された車両のプロペラシャフト部分の断
面を示し、図中２０は第１軸である変速機側の出力軸、
２１は第２軸であるプロペラシャフトのシャフト本体で
ある。1 and 2 are cross-sectional views of a propeller shaft portion of a vehicle to which a shaft coupling according to a first embodiment of the present invention is applied. In the drawings, 20 is a first shaft, which is an output shaft on the transmission side. ,
Reference numeral 21 is a shaft body of a propeller shaft which is a second shaft.
【００２１】前記出力軸２０側は、その端部に鍛造製の
ヨーク２２が結合され、シャフト本体２１側は、その端
部にプレス成形されたヨーク２３が溶接固定されてい
る。これらのヨーク２２，２３は、いずれも三叉状に等
間隔に分岐した分岐アーム２２ａ，２３ａを有し、これ
らの各分岐アーム２２ａ，２３ａの先端が結合部とされ
ている。そして、両ヨーク２２，２３の間には重合した
二枚の金属製の環状プレート２４，２４が配置され、両
ヨーク２２，２３がこれらの環状プレート２４，２４を
介して連結されている。本発明にかかる軸継手はヨーク
２２，２３と、この環状プレート２４，２４を主だった
部品として構成されている。A forged yoke 22 is coupled to the end of the output shaft 20 side, and a press-formed yoke 23 is welded and fixed to the end of the shaft body 21 side. Each of these yokes 22 and 23 has branch arms 22a and 23a branched at equal intervals in a three-pronged manner, and the tip ends of these branch arms 22a and 23a serve as coupling portions. Then, between the two yokes 22 and 23, two metal annular plates 24 and 24 that are polymerized are arranged, and the two yokes 22 and 23 are connected via these annular plates 24 and 24. The shaft coupling according to the present invention is composed of the yokes 22 and 23 and the annular plates 24 and 24 as main components.
【００２２】前記各環状プレート２４は、図１に示すよ
うに、その外周縁が円形状に形成されていると共に、中
央に比較的小さな円形孔３１が形成されて、環状プレー
ト２４の外周縁と円形孔３１の内周縁との間が比較的幅
のある円環部に形成されている。また、外周部側に６つ
のボルト挿通孔２５が同心円上に等間隔位置に穿設され
ており、前記出力軸２０側とシャフト本体２１側の各分
岐アーム２２ａ，２３ａが、図２に示すように円周方向
で交互になるように両環状プレート２４，２４のボルト
挿通孔２５、２５部分で締結手段であるボルト２６及び
ナット２７によって締結されている。この各ボルト２６
とナット２７の締結にあたっては、両環状プレート２
４，２４の外面側に夫々ワッシャ２８，２８が重合配置
され、この一対のワッシャ２８，２８で両環状プレート
２４，２４を直接挟み込む形になっている。As shown in FIG. 1, each of the annular plates 24 has a circular outer peripheral edge, and a relatively small circular hole 31 is formed in the center of the annular plate 24 so that the outer peripheral edge of the annular plate 24 is A relatively wide annular portion is formed between the inner peripheral edge of the circular hole 31 and the inner peripheral edge. Further, six bolt insertion holes 25 are concentrically formed on the outer peripheral side at equidistant positions, and the branch arms 22a and 23a on the output shaft 20 side and the shaft body 21 side are respectively arranged as shown in FIG. Further, bolts 26 and nuts 27, which are fastening means, are fastened at the bolt insertion holes 25, 25 of both annular plates 24, 24 so as to alternate in the circumferential direction. These bolts 26
When tightening the nut 27 and the nut 27, both annular plates 2
Washers 28, 28 are superposed on the outer surface sides of 4, 24, respectively, and both annular plates 24, 24 are directly sandwiched by the pair of washers 28, 28.
【００２３】また、前記各環状プレート２４は、図１に
示すように、前記隣接するボルト挿通孔２５，２５間に
連結アーム部２９が形成されていると共に、この連結ア
ーム部２９に肉抜き孔３０が形成されている。Further, as shown in FIG. 1, each of the annular plates 24 has a connecting arm portion 29 formed between the adjacent bolt insertion holes 25, 25, and a lightening hole is formed in the connecting arm portion 29. 30 is formed.
【００２４】この肉抜き孔３０は、外周側の矩形部３０
ａと内周側の三角形部３０ｂでほぼ扇状に形成され、そ
の矩形部３０ａが隣接するボルト挿通孔２５、２５の中
心Ｘ、Ｘを環状プレート２４と同心円の円弧曲線で結ぶ
仮想線ｐを通る位置に形成されている。そして、連結ア
ーム部２９が、仮想線ｐよりも径方向外側に位置される
外側アーム部２９ａと、同仮想線ｐよりも径方向内側に
位置される内側アーム部２９ｂとに分離設定されてい
る。また、肉抜き孔３０の矩形部３０ａの円周方向の両
端部や三角形部３０ｂの内側端部は、円弧状の丸みが設
けられ、応力集中の緩和とそれによる耐久性の向上が図
られている。The lightening hole 30 has a rectangular portion 30 on the outer peripheral side.
a and a triangular portion 30b on the inner peripheral side are formed in a substantially fan shape, and the rectangular portion 30a passes through a virtual line p that connects the centers X of the bolt insertion holes 25, 25 adjacent to each other and the circular plate 24 with a circular arc curve of a concentric circle. Is formed in position. Then, the connecting arm portion 29 is separately set into an outer arm portion 29a located radially outside the imaginary line p and an inner arm portion 29b located radially inside the imaginary line p. . In addition, both ends of the rectangular portion 30a of the lightening hole 30 in the circumferential direction and inner ends of the triangular portion 30b are provided with arcuate roundness, so that stress concentration is alleviated and durability thereof is improved. There is.
【００２５】したがって、内外側アーム部２９ａ，２９
ｂは、その各径方向幅の中心ｑ1，ｑ2が仮想線ｐの径方
向外側と内側を通ることから、これらの各長さは仮想線
ｐよりも長く設定されている。Therefore, the inner and outer arm portions 29a, 29
In b, the centers q 1 and q 2 of the radial widths thereof are set to be longer than the virtual line p because the centers q 1 and q 2 of the radial widths pass through the outer side and the inner side of the virtual line p in the radial direction.
【００２６】また、前記内側アーム部２９ｂの前記ボル
ト挿通孔２５の中心Ｘと前記円形孔３１の中心Ｙを結ぶ
半径方向線Ｓ上に６つの切欠孔３２が形成されている。
この各切欠孔３２は、前記半径方向線Ｓを中心としたほ
ぼ二等辺三角形状に形成され、その両辺と前記肉抜き孔
３０の三角形部３０ｂの両辺との間に、左右一対の連結
部位３３，３３が形成されている。Further, six notch holes 32 are formed on a radial line S connecting the center X of the bolt insertion hole 25 of the inner arm portion 29b and the center Y of the circular hole 31.
Each of the notch holes 32 is formed in a substantially isosceles triangle shape centering on the radial line S, and a pair of left and right connecting portions 33 is provided between both sides of the notch hole 32 and both sides of the triangular portion 30 b of the lightening hole 30. , 33 are formed.
【００２７】この各連結部位３３は、半径方向線Ｓを中
心に左右対称形状に細長く形成され、その幅はボルト挿
通孔２５側の幅Ｗ１よりも円形孔３１側の幅Ｗ２の方が
漸次小さく設定されている。Each of the connecting portions 33 is formed in a long and narrow shape symmetrical with respect to the radial line S, and its width is gradually smaller on the circular hole 31 side than on the bolt insertion hole 25 side. It is set.
【００２８】なお、前記肉抜き孔３０や切欠孔３２は、
環状プレート２４にボルト挿通孔２５等をプレス成形す
る際に同時に打ち抜かれて形成されている。したがっ
て、この環状プレート２４は、一度のプレス作業によっ
て製造を完了することができ、特別な後加工が必要でな
いため、低コストでの製造が可能である。The lightening hole 30 and the cutout hole 32 are
It is formed by punching at the same time when the bolt insertion hole 25 and the like are press-formed in the annular plate 24. Therefore, the annular plate 24 can be manufactured at a low cost because the manufacturing can be completed by one pressing operation and no special post-processing is required.
【００２９】したがって、この軸継手によれば、肉抜き
孔３０を設けることにより連結アーム部２９全体の径方
向幅を狭め、かつ、内外側アーム部２９ａ，２９ｂの各
長さを長く設定してあるため、これらの相乗効果によっ
て連結アーム部２９の軸方向剛性を充分に低減し、軸方
向の挙動変位の吸収性能を十分に高めることができる。Therefore, according to this shaft coupling, by providing the lightening hole 30, the radial width of the entire connecting arm portion 29 is narrowed, and each length of the inner and outer arm portions 29a, 29b is set to be long. Therefore, due to these synergistic effects, the rigidity in the axial direction of the connecting arm portion 29 can be sufficiently reduced, and the absorption performance of the behavioral displacement in the axial direction can be sufficiently enhanced.
【００３０】また、環状プレート２４を必要以上に薄肉
にしたり、径を大きくする必要がないため、挿通孔２５
周域の摩耗の増大による耐久性の低下や、軸継手全体の
大型化を招くこともない。Further, since it is not necessary to make the annular plate 24 thinner than necessary or to increase its diameter, the insertion hole 25
There is no decrease in durability due to increased wear in the peripheral region and no increase in size of the entire shaft coupling.
【００３１】さらに、この軸継手は、環状プレート２４
の各連結アーム部２９が、仮想線ｐの径方向外側を通る
外側アーム部２９ａと内側を通る内側アーム部２９ｂと
に分離設定されているため、隣接するボルト挿通孔２
５，２５間に作用する引張力や押付力に起因したモーメ
ントにより、連結アーム部２９に座屈が生じる不具合も
生じない。Further, the shaft coupling is composed of an annular plate 24.
Since each of the connecting arm portions 29 is set as an outer arm portion 29a that passes radially outside the imaginary line p and an inner arm portion 29b that passes inside, the adjacent bolt insertion holes 2
The moment caused by the pulling force or the pressing force acting between the No. 5 and No. 25 does not cause the problem that the connecting arm portion 29 is buckled.
【００３２】即ち、図６の比較例のように、連結アーム
部２９は、その径方向幅を挿通孔２５周域の径方向幅よ
りも狭めて仮想線ｐの径方向外側若しくは内側に形成す
れば、軸方向剛性を低く設定することができるが、この
ように連結アーム部２９を仮想線ｐの径方向外側と内側
のいずれかに偏寄させると、隣接する挿通孔２５，２５
に作用する回転駆動力による引張力Ｆ1や押付力Ｆ2が各
連結アーム部２９にモーメントとして作用する。例え
ば、同図の例のようにの各連結アーム部２９を仮想線ｐ
の径方向外側に形成した場合には、引張力Ｆ1は連結ア
ーム部２９の略中間位置を基点に挿通孔２５，２５相互
を離反させるようにモーメントＭ1生じさせ、押付力Ｆ2
は逆に連結アーム部２９の略中間位置を基点に挿通孔２
５，２５相互を近接させるようにモーメントＭ2を生じ
させる。そして、このときの引張力Ｆ1によるモーメン
トＭ1は、連結アーム部２９の略中間位置の径方向外側
部に図７に示すような口開きを起こすような座屈ａを生
じさせ、押付力Ｆ2によるモーメントＭ2は逆に径方向内
側部に同様の座屈ｂを生じさせる。That is, as in the comparative example of FIG. 6, the connecting arm portion 29 is formed on the outer side or the inner side of the imaginary line p in the radial direction with the radial width thereof narrower than the radial width of the peripheral region of the insertion hole 25. For example, the rigidity in the axial direction can be set low, but if the connecting arm portion 29 is biased to either the outer side or the inner side of the imaginary line p in the radial direction in this way, the adjacent insertion holes 25, 25
The pulling force F 1 and the pressing force F 2 due to the rotational driving force that acts on each coupling arm portion 29 act as a moment. For example, as shown in the example of FIG.
When the formed radially outwardly pulling force F 1 is caused moment M 1 so as to separate the insertion hole 25 to each other starting from the substantially intermediate position of the connecting arm portion 29, the pressing force F 2
On the contrary, the insertion hole 2 with the substantially middle position of the connecting arm 29 as the base point
A moment M 2 is generated so as to bring 5, 25 close to each other. Then, the moment M 1 by tension F 1 at this time, cause buckling a that causes the bore opening, such as shown in FIG. 7 in the radially outer portion of the substantially intermediate position of the connecting arm portion 29, the pressing force moment M 2 by F 2 causes a similar buckling b radially inner portion reversed.
【００３３】しかし、この実施形態においては、連結ア
ーム部２９が仮想線ｐ内外の外側アーム部２９ａと内側
アーム部２９ｂとに分離設定されているため、一方のア
ーム部２９ａ（２９ｂ）に比較例のようなモーメントが
作用しても、そのモーメントによる一方のアーム部２９
ａ（２９ｂ）の変形を他方のアーム部２９ｂ（２９ａ）
で抑えることができ、このことから比較例のような座屈
の発生は確実に阻止することができる。したがって、座
屈部分が形状復帰する際に生じる反転音や、環状プレー
ト２４，２４間での異物の噛み込み等は未然に防止する
ことができる。However, in this embodiment, since the connecting arm portion 29 is set separately for the outer arm portion 29a inside and outside the virtual line p and the inner arm portion 29b, one arm portion 29a (29b) is a comparative example. Even if a moment such as
a (29b) is a modification of the other arm portion 29b (29a)
Therefore, the occurrence of buckling as in the comparative example can be surely prevented. Therefore, it is possible to prevent reversal noise that occurs when the buckling portion returns to its original shape, and foreign matter from being caught between the annular plates 24.
【００３４】しかも、ボルト挿通孔２５と円形孔３１と
の間に切欠部３２を形成したため、前記ボルト挿通孔２
５の内側アーム部２９ｂ側の剛性が小さくなって、環状
プレート２４に作用する軸方向の変位時における内側ア
ーム部２９ｂのボルト挿通孔２５近傍に作用する集中応
力をボルト挿通孔２５の両側方向に分散させることが可
能になる。Moreover, since the notch 32 is formed between the bolt insertion hole 25 and the circular hole 31, the bolt insertion hole 2 is formed.
5, the rigidity of the inner arm portion 29b side becomes smaller, and the concentrated stress acting in the vicinity of the bolt insertion hole 25 of the inner arm portion 29b at the time of axial displacement acting on the annular plate 24 is applied to both sides of the bolt insertion hole 25. It becomes possible to disperse.
【００３５】また、各連結部位３３が、半径方向線Ｓを
中心に左右対称形状に細長く形成され、その幅はボルト
挿通孔２５側の幅Ｗ１よりも円形孔３１側の幅Ｗ２の方
が漸次小さく設定されて、連結部位３３の剛性をボルト
挿通孔２５側より円形孔３１の方の剛性を小さくしたこ
とから、軸方向の変位時に該円形孔３１側の撓み変形が
大きくなり、ボルト挿通孔２５付近から連結部位３３に
作用する集中応力をさらに分散させることができる。Further, each connecting portion 33 is formed in a slender shape symmetrically with respect to the radial line S, and the width thereof is gradually smaller in the width W2 of the circular hole 31 side than in the width W1 of the bolt insertion hole 25 side. Since the rigidity of the connecting portion 33 is set to be smaller in the circular hole 31 than in the bolt insertion hole 25 side, the flexural deformation of the circular hole 31 side becomes large at the time of axial displacement, and the bolt insertion hole 25 side becomes larger. The concentrated stress acting on the connecting portion 33 from around 25 can be further dispersed.
【００３６】すなわち、かかる応力の分布を示す図３に
基づいて具体的に説明すれば、環状プレート２４に軸方
向のトルクが作用すると、まず、そのトルクがボルト挿
通孔２５の周囲の切欠孔３２側近傍（丸Ａ箇所）に大き
く掛かるが、切欠孔３２の存在によって前記内側アーム
部２９ｂの剛性が小さくなっていることから、この付近
が容易に撓み変形して、図３のａ、ｂの指示箇所で示す
ように応力が切欠孔３２の頂部３２ａからボルト挿通孔
２５の肉抜き孔３０方向の両側に及び肉抜き孔３０の三
角形部３０ｂの内側頂部付近に分離移動して分散され
る。Specifically, referring to FIG. 3 showing the distribution of such stress, when axial torque acts on the annular plate 24, first, the torque is applied to the notch hole 32 around the bolt insertion hole 25. Although it largely hangs near the side (circle A), since the rigidity of the inner arm portion 29b is reduced due to the presence of the notch hole 32, the inner arm portion 29b is easily flexed and deformed, and the vicinity of the side of FIG. As indicated by the pointed portion, the stress is separated and moved from the top portion 32a of the cutout hole 32 to both sides of the bolt insertion hole 25 in the direction of the lightening hole 30 and near the inner top portion of the triangular portion 30b of the lightening hole 30 to be dispersed.
【００３７】また、連結部位３３側では、幅の細い円形
孔３１側の付近（図３のｃ箇所）が容易に撓み変形して
前記応力を吸収することから、ボルト挿通孔２５付近に
掛かる応力集中をさらに幅広く分散させることが可能に
なる。On the side of the connecting portion 33, the vicinity of the side of the narrow circular hole 31 (location c in FIG. 3) is easily bent and deformed to absorb the stress, so that the stress applied to the vicinity of the bolt insertion hole 25 is reduced. It is possible to spread the concentration more widely.
【００３８】なお、各連結アーム部２９に肉抜き孔３０
を設けたことによる環状プレート２４の回動方向の剛性
低下は、環状プレート２４の重合枚数を適宜増加するこ
とによって補うことができる。It should be noted that each connecting arm portion 29 has a lightening hole 30.
The decrease in rigidity in the rotating direction of the annular plate 24 due to the provision of the above can be compensated by appropriately increasing the number of overlapping annular plates 24.
【００３９】図４は本発明の第２の実施形態を示し、こ
の実施形態の軸継手は、肉抜き孔４０の形状を変更する
と共に、該肉抜き孔４０とボルト挿通孔２５との間に、
小孔４１をそれぞれ穿設したものである。FIG. 4 shows a second embodiment of the present invention. In the shaft coupling of this embodiment, the shape of the lightening hole 40 is changed, and between the lightening hole 40 and the bolt insertion hole 25. ,
The small holes 41 are formed respectively.
【００４０】すなわち、前記各肉抜き孔４０は、それぞ
れほぼ菱形状に形成され、外側の三角部位４０ａと内側
の三角部位４０ｂとを合わせた形状に形成され、外側三
角部位４０ａの頂点４０ｃ付近に前記仮想線ｐが位置し
ていると共に、内側三角部位４０ｂの下部頂点４０ｄが
比較的曲率の小さな円弧状に形成されている。That is, each of the lightening holes 40 is formed in a substantially rhombic shape, and is formed in a shape in which the outer triangular portion 40a and the inner triangular portion 40b are combined, and the outer triangular portion 40a is formed near the apex 40c. The imaginary line p is located, and the lower apex 40d of the inner triangular portion 40b is formed in an arc shape having a relatively small curvature.
【００４１】一方、前記小孔４１は、前記仮想線ｐ上に
全部で１２個設けられ、それぞれが隣接する外側三角部
位４０ａの１辺の傾斜角度に沿ったほぼ長円形状に形成
されており、したがって、連結アーム２９の外側アーム
部２９ａと内側アーム部２９ｂが小孔４１を挟んで配置
されることから、内外側アーム部２９ａ、２９ｂの小孔
４１回りの内外側部位の見かけ上の長さが長くなってい
る。その他、切欠孔３２や連結部位３３，３３の構成な
どは第１の実施形態と同様である。On the other hand, a total of 12 small holes 41 are provided on the imaginary line p, and each small hole 41 is formed in a substantially elliptical shape along the inclination angle of one side of the adjacent outer triangular portion 40a. Therefore, since the outer arm portion 29a and the inner arm portion 29b of the connecting arm 29 are arranged so as to sandwich the small hole 41, the apparent length of the inner and outer portions of the inner and outer arm portions 29a, 29b around the small hole 41 is increased. Is getting longer. Other than that, the configurations of the cutout holes 32 and the connection portions 33, 33 are similar to those of the first embodiment.
【００４２】したがって、この実施形態の軸継手におい
ては、基本的には第１の実施形態と同様の作用効果を得
ることができるが、さらに、各小孔４１の存在によっ
て、隣接するボルト挿通孔２５間の仮想線ｐ上に位置す
る連結アーム部２９の外側アーム部２９ａと内側アーム
部２９ｂの小孔４１回りの細長い内外側部位に分離設定
されて、トルク伝達経路（図４の矢印方向）が各小孔４
１を迂回する形になって長さが長くなる。したがって、
この内外側部位の強度が小さくなり、容易に撓み変形す
ることから、かかる部位に作用する回転方向の捩りトル
クを効果的に吸収できる。このため、図５の指示箇所
ｄ、ｅに示すように、前記捩りトルクによりボルト挿通
孔２５の周囲に作用する集中応力を各肉抜き孔４０の各
頂部４０ｃ、４０ｄ付近や各小孔４１の周囲内外部位に
分散させることができる。Therefore, in the shaft coupling of this embodiment, basically, the same operational effect as that of the first embodiment can be obtained, but the existence of each small hole 41 further causes the adjacent bolt insertion holes. The outer side arm portion 29a and the inner side arm portion 29b of the connecting arm portion 29 located on the imaginary line p between 25 are separately set to be elongated inner and outer portions around the small hole 41, and the torque transmission path (direction of arrow in FIG. 4) Each small hole 4
The length becomes longer by detouring 1. Therefore,
Since the strength of the inner and outer portions is reduced and the inner and outer portions are easily bent and deformed, it is possible to effectively absorb the torsion torque in the rotational direction that acts on the portion. Therefore, as indicated by the indicated points d and e in FIG. 5, the concentrated stress acting on the periphery of the bolt insertion hole 25 due to the twisting torque is generated in the vicinity of the tops 40c and 40d of the lightening holes 40 and in the small holes 41. It can be dispersed in the inner or outer position.
【００４３】また、前記内外側部位の容易な撓み変形に
よって軸方向のトルクに対しても分散させることができ
る。Further, it is possible to disperse the torque in the axial direction by the easy bending deformation of the inner and outer portions.
【００４４】[0044]
【発明の効果】以上のように請求項１に記載の発明は、
連結アーム部に肉抜き孔を形成したために、環状プレー
トの厚さを薄くしたり、径を増大させることなく、連結
アーム部の軸方向剛性を下げることができる。また、連
結アーム部を、仮想線に対して径方向外側と内側の外側
アーム部と内側アーム部に設定したため、隣接する挿通
孔間に作用する引張力や押付力が一方のアーム部にモー
メントとして作用しても、そのアーム部の変形は他方の
アーム部によって抑えられる。As described above, the invention described in claim 1 is
Since the lightening hole is formed in the connecting arm portion, the axial rigidity of the connecting arm portion can be reduced without reducing the thickness of the annular plate or increasing the diameter. Further, since the connecting arm portion is set to the outer arm portion and the inner arm portion on the radially outer side and the inner side with respect to the imaginary line, the tensile force or the pressing force acting between the adjacent insertion holes acts as a moment on one arm portion. Even if it works, the deformation of the arm portion is suppressed by the other arm portion.
【００４５】特に、挿通孔と環状プレートの中心側との
間に切欠部を形成したため、前記挿通孔の内側アーム部
側の剛性が小さくなって、軸方向変位時に内側アーム部
の挿通孔近傍に作用する集中応力を挿通孔の両側方向に
分散させることが可能になる。In particular, since the notch is formed between the insertion hole and the center side of the annular plate, the rigidity of the insertion hole on the side of the inner arm portion is reduced, and when the axial displacement is made, the inner arm portion is close to the insertion hole. It becomes possible to disperse the concentrated stress acting on both sides of the insertion hole.
【００４６】この結果、環状プレートの特に挿通孔周辺
部に経時的な亀裂や破損などの発生が確実に防止され
て、環状プレートの耐久性の向上が図れる。As a result, it is possible to reliably prevent the occurrence of cracks or damages with time, especially in the peripheral portion of the insertion hole of the annular plate, and to improve the durability of the annular plate.
【００４７】請求項２に記載の発明によれば、連結部位
の剛性を内側（環状プレートの中心側）と外側（挿通孔
側）で変化させ、外側より内側の方の剛性を小さくした
ことから、軸方向の変位時に該内側の撓み変形が大きく
なり、前記挿通孔周辺に作用する集中応力をさらに分散
させることができる。According to the second aspect of the present invention, the rigidity of the connecting portion is changed between the inner side (center side of the annular plate) and the outer side (insertion hole side), so that the inner side rigidity is made smaller than the outer side rigidity. The flexural deformation on the inner side becomes large when displaced in the axial direction, and the concentrated stress acting on the periphery of the insertion hole can be further dispersed.
【００４８】請求項３に記載の発明によれば、小孔の存
在によって、隣接する挿通孔間の仮想線上に位置する部
位が細長い内外側部位に分離されて、これらの長さが長
くなり、この部位の強度が小さくなることから、かかる
内外側部位に作用する回転方向の捩りトルクを効果的に
吸収することができる。このため、前記捩りトルクによ
り挿通孔の周囲に作用する集中応力を分散させることが
できる。According to the third aspect of the present invention, due to the existence of the small holes, the portions located on the imaginary line between the adjacent insertion holes are separated into the elongated inner and outer portions, and the length thereof is increased. Since the strength of this portion is reduced, it is possible to effectively absorb the torsional torque in the rotational direction that acts on the inner and outer portions. Therefore, it is possible to disperse the concentrated stress acting around the insertion hole by the torsion torque.
【００４９】また、前記内外側部位によって軸方向のト
ルクに対しても分散させることができる。したがって、
環状プレートの耐久性を一層向上させることが可能にな
る。Further, it is possible to disperse the axial torque by the inner and outer portions. Therefore,
It is possible to further improve the durability of the annular plate.
【図１】本発明の第１の実施形態を示す環状プレートの
正面図。FIG. 1 is a front view of an annular plate showing a first embodiment of the present invention.
【図２】同実施形態を示す軸継手の断面図。FIG. 2 is a sectional view of a shaft coupling showing the same embodiment.
【図３】本実施形態における環状プレートに作用する軸
方向の応力分布図。FIG. 3 is a stress distribution diagram in the axial direction which acts on the annular plate in the present embodiment.
【図４】本発明の第２の実施形態を示す環状プレートの
正面図。FIG. 4 is a front view of an annular plate showing a second embodiment of the present invention.
【図５】本実施形態における環状プレートに作用する軸
方向の応力分布図。FIG. 5 is an axial stress distribution diagram that acts on the annular plate in the present embodiment.
【図６】本発明の比較例を示す環状プレートの正面図。FIG. 6 is a front view of an annular plate showing a comparative example of the present invention.
【図７】同比較例を示す図６のａ，ｂ部分の側面図。FIG. 7 is a side view of portions a and b of FIG. 6 showing the comparative example.
【図８】従来の技術を示す断面図。FIG. 8 is a sectional view showing a conventional technique.
【図９】同技術を示すＣ矢視図。FIG. 9 is a view on arrow C showing the same technique.
【図１０】別の従来の技術を示す環状プレートの平面
図。FIG. 10 is a plan view of an annular plate showing another conventional technique.
２０…出力軸（第１軸） ２１…シャフト本体（第２軸） ２２ａ，２３ａ…分岐アーム（結合部） ２４…環状プレート ２５…挿通孔 ２６…ボルト（締結手段） ２７…ナット（締結手段） ２９…連結アーム部 ２９ａ…外側アーム部 ２９ｂ…内側アーム部 ３０・４０…肉抜き孔 ３２…切欠孔 ３３…連結部位 ４１…小孔 ｐ…仮想線 20 ... Output shaft (1st shaft) 21 ... Shaft body (second axis) 22a, 23a ... Branch arm (joint part) 24 ... Annular plate 25 ... Insertion hole 26 ... Bolt (fastening means) 27 ... Nut (fastening means) 29 ... Connection arm part 29a ... Outer arm part 29b ... Inner arm 30/40 ... Lightening hole 32 ... Notch hole 33 ... Connection part 41 ... Small hole p ... virtual line
Claims (3)
剛性の大きい環状プレートを配置し、前記第１軸と第２
軸の各端部に円周方向に間隔をおいて設けられた結合部
を、第１軸側のものと第２軸側のものが円周方向で交互
になるように、前記環状プレートに締結手段を介して結
合し、前記環状プレートの円周方向へ所定間隔をもって
穿設された前記締結手段が挿通する各挿通孔間の部位を
連結アーム部とし、該各連結アームの弾性変形により、
軸方向の挙動変位を吸収するようにした車両用軸継手に
おいて、 前記連結アーム部に肉抜き孔を形成すると共に、前記連
結アーム部を、隣接する前記両挿通孔の中心を結ぶ環状
プレートと同心円の円弧曲線の仮想線よりも径方向外側
に位置される外側アーム部と、同仮想線よりも径方向内
側に位置される内側アーム部とに設定し、該内側アーム
部の前記挿通孔の中心と環状プレートの中心を結ぶ線上
に切欠孔を形成し、前記肉抜き孔と切欠孔との間に、環
状プレートのほぼ径方向に沿った一対の連結部位を形成
したことを特徴とする車両用軸継手。1. An annular plate having a high rigidity in a rotation direction is arranged at a butting portion of the first shaft and the second shaft, and the first shaft and the second shaft are arranged.
Fastening the coupling parts provided at each end of the shaft at intervals in the circumferential direction to the annular plate so that the one on the first shaft side and the one on the second shaft side alternate in the circumferential direction. Connecting through means, a portion between each insertion hole through which the fastening means formed at a predetermined interval in the circumferential direction of the annular plate is inserted is a connecting arm portion, and by elastic deformation of each connecting arm,
In a vehicle shaft coupling adapted to absorb behavioral displacement in the axial direction, a hollow hole is formed in the connecting arm portion, and the connecting arm portion is concentric with an annular plate connecting the centers of the two adjacent through holes. The outer arm portion located radially outside the imaginary line of the circular arc curve and the inner arm portion located radially inward of the imaginary line are set to the center of the insertion hole of the inner arm portion. And a notch hole are formed on a line connecting the centers of the annular plate, and a pair of connecting portions extending substantially in the radial direction of the annular plate is formed between the lightening hole and the notch hole. Shaft coupling.
の間の幅を、前記挿通孔側よりも環状プレートの中心側
の方を小さく設定したことを特徴とする請求項１に記載
の車両用軸継手。2. The width between the lightening hole and the notch hole of the connecting portion is set smaller on the center side of the annular plate than on the insertion hole side. Vehicle shaft coupling.
の間に、小孔を穿設したことを特徴とする請求項２に記
載の車両用軸継手。3. The shaft coupling for a vehicle according to claim 2, wherein a small hole is formed between the insertion hole and the lightening hole on the imaginary line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001238635A JP4008215B2 (en) | 2001-08-07 | 2001-08-07 | Vehicle shaft coupling |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001238635A JP4008215B2 (en) | 2001-08-07 | 2001-08-07 | Vehicle shaft coupling |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003049863A true JP2003049863A (en) | 2003-02-21 |
| JP4008215B2 JP4008215B2 (en) | 2007-11-14 |
Family
ID=19069515
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001238635A Expired - Fee Related JP4008215B2 (en) | 2001-08-07 | 2001-08-07 | Vehicle shaft coupling |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4008215B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2019143745A (en) * | 2018-02-22 | 2019-08-29 | 日本電産シンポ株式会社 | Flexible outer tooth gear and wave gear device having the same |
| WO2020050078A1 (en) * | 2018-09-07 | 2020-03-12 | 日立オートモティブシステムズ株式会社 | Joint for power transmission shaft |
-
2001
- 2001-08-07 JP JP2001238635A patent/JP4008215B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2019143745A (en) * | 2018-02-22 | 2019-08-29 | 日本電産シンポ株式会社 | Flexible outer tooth gear and wave gear device having the same |
| WO2020050078A1 (en) * | 2018-09-07 | 2020-03-12 | 日立オートモティブシステムズ株式会社 | Joint for power transmission shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4008215B2 (en) | 2007-11-14 |
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