JPH04127423U - Yoke for universal joint - Google Patents
Yoke for universal jointInfo
- Publication number
- JPH04127423U JPH04127423U JP4285991U JP4285991U JPH04127423U JP H04127423 U JPH04127423 U JP H04127423U JP 4285991 U JP4285991 U JP 4285991U JP 4285991 U JP4285991 U JP 4285991U JP H04127423 U JPH04127423 U JP H04127423U
- Authority
- JP
- Japan
- Prior art keywords
- yoke
- universal joint
- support arm
- mounting board
- 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.)
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Abstract
(57)【要約】
【目的】剛性を保持しつつ、軽量化を図る。
【構成】自在継手用ヨークは、金属板をプレス成形する
事で造る。取付基板部２９の両側には、同方向に向けて
１対の支持腕部３０、３０を折り曲げ形成している。各
支持腕部３０、３０の先端には、十字軸枢支用の円孔２
６、２６を形成している。又、取付基板部２９の幅方向
中央部から支持腕部３０、３０の基部に亙って、透孔２
８を形成している。
(57) [Summary] [Purpose] To reduce weight while maintaining rigidity. [Structure] The yoke for the universal joint is made by press-forming a metal plate. A pair of support arms 30, 30 are formed on both sides of the mounting board section 29 by bending them in the same direction. At the tip of each support arm 30, 30, there is a circular hole 2 for supporting the cross axis.
6 and 26 are formed. In addition, the through hole 2 extends from the center part in the width direction of the mounting board part 29 to the base of the support arm parts 30, 30.
8 is formed.
Description
【０００１】0001
この考案に係る自在継手用ヨークは、例えば自動車のステアリング装置用の自 在継手を構成する。 The yoke for a universal joint according to this invention can be used, for example, in an automobile steering system. Configure existing joints.
【０００２】0002
自動車用の操舵装置は、ステアリングホイールの動きをステアリングシャフト を介してステアリングギヤに伝達し、操舵車輪（一般的には前輪）に舵角を付与 する様に構成されている。 An automobile steering system uses a steering shaft to control the movement of the steering wheel. The signal is transmitted to the steering gear via the It is configured to do so.
【０００３】 この様な操舵装置は、一般的には機械式の伝達機構により構成されている為、 そのままでは、悪路走行等によって操舵車輪に加わった振動が、ステアリングギ ヤやステアリングシャフトを介してステアリングホイールに迄伝達されてしまう 。0003 This kind of steering device is generally composed of a mechanical transmission mechanism, so If left as is, vibrations applied to the steering wheels due to driving on rough roads, etc., will cause damage to the steering gear. It is transmitted to the steering wheel via the steering shaft and steering shaft. .
【０００４】 この様に、悪路走行等に伴なう振動が、ステアリングホイールに迄伝達された 場合、運転者に不快感を与える為、例えば特開昭６１−１９７８２０号公報に開 示されている様に、ステアリングシャフトの端部に弾性自在継手を設ける事でこ の振動を吸収し、操舵車輪の振動がそのままステアリングホイールに迄伝わらな い様にしている。0004 In this way, vibrations caused by driving on rough roads are transmitted to the steering wheel. For example, in order to cause discomfort to the driver, the This can be achieved by providing an elastic universal joint at the end of the steering shaft as shown. absorbs the vibrations of the steering wheel and prevents the vibration of the steering wheel from being transmitted directly to the steering wheel. I'm doing it like that.
【０００５】 図８〜９は、前記公報に記載されたステアリングシャフト用弾性自在継手を示 している。フランジ１が、ステアリングギヤに通じる軸２の端部に固定されてい る。又、３は、ゴム等の弾性材製のカップリング部材で、弾性継手は、このカッ プリング部材３の弾性により、振動を吸収する様に構成されている。又、４は、 このカップリング部材３を介して前記フランジ１と対向したヨークで、このヨー ク４とステアリングシャフト５（使用状態を示す図１０参照）の端部とを、十字 軸６（図１０）を介して結合自在としている。[0005] Figures 8 and 9 show the elastic universal joint for a steering shaft described in the above publication. are doing. A flange 1 is fixed to the end of the shaft 2 leading to the steering gear. Ru. 3 is a coupling member made of an elastic material such as rubber, and the elastic joint is a coupling member made of an elastic material such as rubber. The elasticity of the pulling member 3 is configured to absorb vibrations. Also, 4 is A yoke facing the flange 1 via the coupling member 3. 4 and the end of the steering shaft 5 (see Figure 10 showing the state of use). They can be freely connected via a shaft 6 (FIG. 10).
【０００６】 前記フランジ１と前記カップリング部材３とは、直径方向反対位置２箇所で、 第一の結合手段によって結合されている。この第一の結合手段は、第一のボルト ７、７、第一のナット８、８及び、直径方向反対位置２箇所に円弧状の第一の切 り欠き２４、２４を有する欠円状に形成された第一の抑え板９により構成される 。即ち、フランジ１の両端部２箇所位置に形成した通孔１０、１０を挿通した第 一のボルト７、７は、カップリング部材３に互いに等間隔に形成された４個の通 孔１１、１２の内、直径方向反対位置に存在する１対の通孔１１、１１を貫通し 、上記第一の抑え板９の両端部に形成した通孔１３、１３を貫通してから、その 先端部に第一のナット８、８を螺合し、緊締している。[0006] The flange 1 and the coupling member 3 are arranged at two diametrically opposite positions, They are coupled by first coupling means. This first coupling means includes a first bolt 7, 7, the first nut 8, 8, and the first arc-shaped cut at two diametrically opposite positions. Consisting of a first restraining plate 9 formed in an occluded circular shape having notches 24, 24. . That is, the holes 10, 10 formed at two positions on both ends of the flange 1 are inserted through the holes 10, 10. One bolt 7, 7 has four holes formed in the coupling member 3 at equal intervals. Among the holes 11 and 12, a pair of through holes 11 and 11 that are located at opposite positions in the diametrical direction are penetrated. , after passing through the through holes 13, 13 formed at both ends of the first restraining plate 9, First nuts 8, 8 are screwed onto the tip and tightened.
【０００７】 一方、前記ヨーク４と前記カップリング部材３とは、やはり直径方向反対位置 ２箇所で、第二の結合手段によって結合されている。この第二の結合手段は、第 二のボルト１４、１４、第二のナット１５、１５及び、前記第一の抑え板９と同 様の欠円状に形成された第二の抑え板１６により構成される。即ち、ヨーク４基 端の両端部２箇所位置に形成した通孔１８を挿通した第二のボルト１４、１４は 、カップリング部材３に形成された上記４個の通孔１１、１２の内、残りの通孔 １２、１２を貫通し、上記第二の抑え板１６の両端部に形成した通孔１７、１７ を貫通してから、その先端部に第二のナット１５、１５を螺合し、緊締している 。[0007] On the other hand, the yoke 4 and the coupling member 3 are also located at opposite positions in the diametrical direction. They are joined at two points by second joining means. This second coupling means The second bolts 14, 14, the second nuts 15, 15, and the same as the first restraining plate 9. It is constituted by a second restraining plate 16 formed in the shape of a broken circle. That is, 4 yokes The second bolts 14, 14 are inserted through through holes 18 formed at two positions on both ends. , the remaining through holes among the four through holes 11 and 12 formed in the coupling member 3. 12, 12, and through holes 17, 17 formed at both ends of the second restraining plate 16. After passing through, the second nuts 15, 15 are screwed onto the tip and tightened. .
【０００８】 この結果、軸２の端部に固定したフランジ１とヨーク４とは、図９に示す様に 、弾性材製のカップリング部材３を介して結合された状態となる。この様に構成 される弾性継手は、図１０に示す様に、前記ヨーク４と他のヨーク３２とを、十 字軸６を介して、互いに変位を自在に結合する事により、弾性自在継手とする。 そして、前記軸２を、別の自在継手１９と連結ロッド２０等とを介して、ステア リングギヤ（図示せず）の入力軸に結合している。[0008] As a result, the flange 1 and yoke 4 fixed to the end of the shaft 2 are arranged as shown in FIG. , they are connected via a coupling member 3 made of an elastic material. Configure like this The elastic joint, as shown in FIG. By connecting them to each other through the shaft 6 so that they can be displaced freely, an elastic universal joint is formed. Then, the shaft 2 is connected to the steering wheel via another universal joint 19, a connecting rod 20, etc. It is coupled to the input shaft of a ring gear (not shown).
【０００９】 弾性自在継手をステアリング装置に、上述の様に組み込んだ状態で、図示しな いステアリングホイールを操作する事によりステアリングシャフト５を回動させ 、十字軸６を介してヨーク４を捩り方向に回転させると、この回転がカップリン グ部材３を介してフランジ１に伝わり、このフランジ１を固定した軸２が、捩り 方向に回転する。そしてこの回転が、自在継手１９、連結ロッド２０を介してス テアリングギヤに伝達され、前記操舵輪への舵角付与が行なわれる。[0009] With the elastic universal joint installed in the steering device as described above, The steering shaft 5 is rotated by operating the steering wheel. , when the yoke 4 is rotated in the torsional direction via the cross shaft 6, this rotation is caused by the coupling. The torque is transmitted to the flange 1 through the connecting member 3, and the shaft 2 to which the flange 1 is fixed is torsionally Rotate in the direction. This rotation then moves through the universal joint 19 and the connecting rod 20. The signal is transmitted to the steering gear, and a steering angle is applied to the steered wheels.
【００１０】 カップリング部材３は、ゴム等の弾性材により造られている為、操舵車輪から 軸２に振動が伝わった場合には、カップリング部材３が回転方向及び軸方向に弾 性変形してこの振動を吸収し、ステアリングシャフト５に接続されるヨーク４が 振動する事を防止する。0010 Since the coupling member 3 is made of an elastic material such as rubber, it When vibration is transmitted to the shaft 2, the coupling member 3 becomes elastic in the rotational direction and the axial direction. The yoke 4, which is connected to the steering shaft 5, deforms and absorbs this vibration. Prevent vibration.
【００１１】 尚、前記第一のボルト７、７が挿通された第一のスリーブ２１、２１は、第二 の抑え板１６に形成された第二の切り欠き２２、２２に、第二のボルト１４、１ ４が挿通された第二のスリーブ２３、２３は、第一の抑え板９に形成された第一 の切り欠き２４、２４に、それぞれ係合している。そして、前記フランジ１とヨ ーク４との捩り方向に亙る変位は、各スリーブ２１、２３が各切り欠き２２、２ ４の内側で移動出来る範囲内でのみ、可能である。この為、前記カップリング部 材３の弾性変形量が過大となり、このカップリング部材３が破損する様な事はな い。[0011] Note that the first sleeves 21, 21 into which the first bolts 7, 7 are inserted are The second bolts 14, 1 are inserted into the second notches 22, 22 formed in the restraining plate 16. 4 is inserted into the second sleeves 23, 23, which are inserted into the first retaining plate 9. are engaged with the notches 24, 24, respectively. Then, the flange 1 and Displacement in the torsional direction with respect to the arc 4 is caused by the displacement of each sleeve 21, 23 with each notch 22, 2. This is possible only within the range of movement within 4. For this reason, the coupling part This prevents the coupling member 3 from being damaged due to excessive elastic deformation of the member 3. stomach.
【００１２】0012
ところが、上述の様に構成され作用する、従来のステアリングシャフト用弾性 自在継手に組み込まれたヨーク４の場合、その基板部外形がカップリング部材３ の丸形形状に沿った形状を有する為に重量が嵩み、このヨーク４を組み込んで構 成された弾性自在継手等の重量が徒に嵩んでしまう。 However, the conventional elastic steering shaft that is configured and operates as described above In the case of the yoke 4 incorporated in the universal joint, the outer shape of the base plate is the same as that of the coupling member 3. Since it has a shape that follows the round shape of The weight of the elastic universal joint, etc. thus constructed increases unnecessarily.
【００１３】 本考案の自在継手用ヨークは、上述の様な不都合を解消するものである。[0013] The yoke for a universal joint of the present invention eliminates the above-mentioned disadvantages.
【００１４】[0014]
【課題を解決する為の手段】 本考案の自在継手用ヨークは、金属厚板を折り曲げ形成して成り、取付基板部 と、この取付基板部の両端から同方向にほぼ直角に折れ曲がった支持腕部と、両 支持腕部の先端部に形成された、互いに同心の１対の円孔とから成る自在継手用 ヨークに於いて、前記取付基板部の幅方向中央部から前記両支持腕部の基部に亙 る透孔を形成した事を特徴としている。[Means to solve the problem] The yoke for the universal joint of this invention is made by bending a thick metal plate, and the mounting board part , support arms bent from both ends of the mounting board in the same direction at almost right angles, and both ends of the mounting board. For universal joints consisting of a pair of mutually concentric circular holes formed at the tip of the support arm. In the yoke, from the center in the width direction of the mounting board section to the bases of both the support arms. It is characterized by the formation of through holes.
【００１５】[0015]
上述の様に構成される本考案の自在継手用ヨークの場合、透孔を形成した分、 実用強度を低下させる事なく、軽量化を図れる。 In the case of the yoke for a universal joint of the present invention configured as described above, since the through hole is formed, Weight reduction can be achieved without reducing practical strength.
【００１６】[0016]
図１〜４は本考案の第一実施例を示している。本考案の自在継手用ヨークを造 る場合、先ず、鋼板等の十分な剛性を有する金属厚板を打ち抜き形成する事で、 図４に示す様な素材２５を造る。この素材２５は、全体を略菱形状に形成すると 共に、その両端部に十字軸６（図１０）支持用の円孔２６を、中央両側部にボル ト挿通用の円孔２７、２７を、それぞれ形成している。更に、中央部分には、前 記各孔２６、２７をよけて、透孔２８を形成している。 1 to 4 show a first embodiment of the invention. The yoke for the universal joint of this invention was created. In the case of A material 25 as shown in FIG. 4 is made. This material 25 is formed into a substantially diamond shape as a whole. Both have circular holes 26 for supporting the cross shaft 6 (Fig. 10) at both ends, and bolts at both sides of the center. Circular holes 27, 27 for insertion are formed, respectively. Furthermore, the central part has a A through hole 28 is formed apart from the holes 26 and 27.
【００１７】 上述の様な素材２５は、図１〜３に示す様に、中間部２箇所位置を同じ方向に ほぼ直角に折り曲げる事で、両側端部にボルト挿通用の円孔２７、２７を有する 取付基板部２９と、この取付基板部２９の両端から同方向にほぼ直角に折れ曲が り、それぞれの先端部に円孔２６、２６を有する支持腕部３０、３０とから成る 、本考案の自在継手用ヨークとする。[0017] The above-mentioned material 25 has two middle parts in the same direction as shown in Figures 1 to 3. By bending it almost at right angles, it has circular holes 27, 27 for bolt insertion at both ends. The mounting board part 29 is bent from both ends of the mounting board part 29 in the same direction at almost right angles. and support arms 30, 30 having circular holes 26, 26 at their respective tips. , the yoke for a universal joint of the present invention.
【００１８】 この様に、前記素材２５の２箇所位置を折り曲げる事で、本考案の自在継手用 ヨークとした状態に於いて、前記各支持腕部３０、３０先端の円孔２６、２６は 、互いに同心となる。又、前記取付基板部２９の幅方向中央部から前記両支持腕 部３０、３０の基部に亙って透孔２８が存在する状態となる。[0018] In this way, by bending the material 25 at two positions, the universal joint of the present invention can be bent. In the yoke state, the circular holes 26, 26 at the tips of each of the support arms 30, 30 are , become concentric with each other. Further, both the support arms are connected from the widthwise central portion of the mounting board portion 29. The through hole 28 is present over the base portions of the portions 30, 30.
【００１９】 上述の様に構成される本考案の自在継手用ヨークの場合、透孔２８を形成した 分、実用強度を低下させる事なく、軽量化を図れる。[0019] In the case of the universal joint yoke of the present invention configured as described above, the through hole 28 is formed. Therefore, weight reduction can be achieved without reducing practical strength.
【００２０】 尚、本考案の自在継手用ヨークを造る為の素材２５の形状は、図４に示す様な ものに限定されず、他にも、図５に示す様な形状等、他の形状とする事も出来る 。[0020] The shape of the material 25 for making the yoke for the universal joint of the present invention is as shown in Fig. 4. The shape is not limited to this, and other shapes such as the shape shown in Figure 5 can also be used. .
【００２１】 次に、本考案の自在継手用ヨークと従来型の自在継手用ヨークとの強度を比較 した試算値に就いて説明する。尚、本考案の自在継手用ヨークとして、前記図４ に示す様な形状の素材２５から造られたものを使用し、従来型の自在継手用ヨー クとして、図７に示す様な形状の素材３１から造られたものを使用した。[0021] Next, we compared the strength of the yoke for universal joints of this invention and the conventional yoke for universal joints. The estimated values will be explained below. In addition, as a yoke for a universal joint of the present invention, the above-mentioned FIG. The conventional universal joint yaw is made from material 25 with the shape shown in the figure. A material 31 made of a material 31 having a shape as shown in FIG. 7 was used as the material.
【００２２】 試算の前提として、ステアリング用ジョイントの降伏トルクは、一般に２０kg f・m 以上とされているので、ヨークの十字軸６の支持用円孔２６に作用する曲げ モーメントＭを２０×１０3 kgf・mmとし、ヨークの支持腕部３０、３０の幅（板 厚中央部同士の間隔）Ｌを３５mmとした。従って、各支持腕部３０、３０先端の 円孔２６、２６の中央に作用する力Ｆは、Ｆ＝Ｍ／Ｌ≒５７０kgf となる。As a premise of the trial calculation, since the yield torque of the steering joint is generally 20 kg f·m or more, the bending moment M acting on the support circular hole 26 of the cross shaft 6 of the yoke is set to 20×10 3 . kgf·mm, and the width L of the supporting arm portions 30, 30 of the yoke (the distance between the center portions of the plate thickness) was 35 mm. Therefore, the force F acting on the center of the circular holes 26, 26 at the tips of each support arm 30, 30 is F=M/L≈570 kgf.
【００２３】 この前提の下で、前記図７に示した従来型のヨークの最大曲げ応力σ1 を求め ると、次式で求められる。尚、この曲げ応力σ1 を求めた点は、前記支持腕部３ ０の基部で、前記円孔２６の中心からｌ（２３mm）だけ離れた位置である。Under this premise, the maximum bending stress σ 1 of the conventional yoke shown in FIG. 7 is determined by the following equation. The point at which this bending stress σ 1 was determined is at the base of the support arm 30 and a distance l (23 mm) from the center of the circular hole 26 .
【００２４】 Ｍ＝Ｆ・ｌ＝σ1 ・ｚ1 M=F・l=σ 1・z 1
【００２５】 但し、ｚ1 は支持腕部３０の断面係数で、ｚ1 ＝ｂ・ｈ2 ／６で表わされる。 又、ｂは支持腕３０の厚さで、６mmと仮定する。更に、ｈは当該部分に於ける支 持腕部３０の幅寸法で、２３mmと仮定する。これらにより前記最大曲げ応力σ1 を求めると、σ1 ≒２４．８kgf/mm2 となる。However, z 1 is the section modulus of the support arm portion 30 and is expressed as z 1 =b·h 2 /6. Further, b is the thickness of the support arm 30, which is assumed to be 6 mm. Further, h is the width dimension of the support arm portion 30 at the relevant portion, which is assumed to be 23 mm. When the maximum bending stress σ 1 is determined from these, σ 1 ≈24.8 kgf/mm 2 .
【００２６】 一方、図４に示す様な本考案の自在継手用ヨークに於いては、ジョイント曲げ 角度が特に大きく（例えば３５度以上）ならない限り、同図に示す様に、支持腕 部３０を構成する部分を、基部に向かう程幅寸法が大きくなる様に構成出来る。 何となれば、弾性自在継手を構成するヨークの場合、取付基板部２９にボルトの 頭やナットを設け、これらと他のヨークとの干渉を避ける必要上、前記支持腕部 ３０を（弾性自在継手でない）一般的なヨークの場合よりも長くしている為と、 支持腕部３０の断面が円弧状でなく平坦であり、取付基板部２９近くの支持腕部 ３０の内側縁が軸心より離れており、相手ヨークと干渉しにくい為とである。[0026] On the other hand, in the universal joint yoke of the present invention as shown in Fig. 4, joint bending Unless the angle is particularly large (e.g. 35 degrees or more), the support arm should be The portions constituting the portion 30 can be configured such that the width increases toward the base. In the case of a yoke that constitutes an elastic universal joint, the bolts are attached to the mounting board part 29. Due to the need to provide a head and nut and avoid interference between these and other yokes, the support arm portion 30 is longer than that of a general yoke (not an elastic universal joint), The cross section of the support arm portion 30 is not arcuate but flat, and the support arm portion near the mounting board portion 29 This is because the inner edge of 30 is further away from the axis and is less likely to interfere with the mating yoke.
【００２７】 そこで、図４に示した本考案の自在継手用ヨークの支持腕部３０の、円孔２６ の中心からの距離ｌが２０mmである点に加わる最大曲げ応力σ2 と、前記円孔２ ６の中心からの距離ｌが３０mmである点に加わる最大曲げ応力σ3 とは、次式に より求められる。Therefore, the maximum bending stress σ 2 applied to the support arm 30 of the yoke for a universal joint of the present invention shown in FIG. 4 at a point where the distance l from the center of the circular hole 26 is 20 mm, and The maximum bending stress σ 3 applied at a point where the distance l from the center of 2 6 is 30 mm is determined by the following equation.
【００２８】 Ｍ＝５７０×２０（３０）＝σ2 （σ3 ）・ｚ2 （ｚ3 ）M=570×20(30)=σ 2 (σ 3 )・z 2 (z 3 )
【００２９】 但し、ｚ2 （ｚ3 ）は支持腕部３０の断面係数で、ｚ2 （ｚ3 ）＝ｂ（ｈ0 3− ｈi 3）／６ｈ0 で表わされる。尚、ｈ0 は、当該部分に於ける支持腕部３０の幅 （外寸）、ｈi は同じく透孔２８の幅（内寸）である。However, z 2 (z 3 ) is the section modulus of the support arm portion 30, and is expressed as z 2 (z 3 )=b(h 0 3 −h i 3 )/6h 0 . Note that h 0 is the width (outer dimension) of the support arm portion 30 at the relevant portion, and h i is the width (inner dimension) of the through hole 28 .
【００３０】 この式から、前記従来形状と同等以上の最大曲げ応力（≒２５kgf/mm2 ）を得 る為に要する、支持腕部３０の幅寸法ｔを求める。尚、板厚ｂは、従来と同じ６ mmとする。この結果、円孔２６の中心からの距離ｌが２０mmである点（ｈ0 ＝３ ０mm) では、前記幅寸法ｔが３．１５mm以上あれば、前記円孔２６の中心からの 距離ｌが３０mmである点（ｈ0 ＝４０mm）では、前記幅寸法ｔが３．４mm以上あ れば、それぞれの点に於ける最大曲げ応力σ2 、σ3 が２５kgf/mm2 となる事が 解る。From this equation, the width t of the support arm 30 required to obtain a maximum bending stress (≈25 kgf/mm 2 ) equal to or higher than that of the conventional shape is determined. The plate thickness b is 6 mm, which is the same as before. As a result, at a point where the distance l from the center of the circular hole 26 is 20 mm (h 0 = 30 mm), if the width t is 3.15 mm or more, the distance l from the center of the circular hole 26 is 30 mm. It can be seen that at a certain point (h 0 =40 mm), if the width dimension t is 3.4 mm or more, the maximum bending stresses σ 2 and σ 3 at each point will be 25 kgf/mm 2 .
【００３１】 そして、この様な計算結果から求められた、図４に示す様な形状を有する本考 案の自在継手用ヨークの重量は約８０ｇとなり、図７に示した従来形状のヨーク の重量約１４０ｇに比べて、４０％強の重量軽減を図れる事が解る。[0031] The proposed model, which has the shape shown in Figure 4, was obtained from these calculation results. The weight of the proposed universal joint yoke is approximately 80g, which is compared to the conventional shaped yoke shown in Figure 7. It can be seen that the weight can be reduced by over 40% compared to the weight of about 140g.
【００３２】 又、各支持腕部３０、３０の捩り剛性も、従来品に比べて向上する。即ち、支 持腕部３０、３０の曲げ剛性は各支持腕部３０、３０の断面二次モーメントＩに 比例するが、この断面二次モーメントＩは、従来品の場合にはＩ＝ｂｈ3/１２で 、本考案品の場合にはＩ＝ｂ（ｈ0 3−ｈi 3）／１２で、それぞれ表わされる。そ して、前述の条件により、従来のヨークの支持腕部の基部近くの点で、これら断 面二次モーメントＩを求めると、従来品の場合には６．０８×１０3 (mm4) と、 本考案品の場合には前記幅寸法ｔ＝６mmとして、１０．６×１０3 (mm4) となり 、本考案品の場合には、各支持腕部３０、３０の捩り剛性も向上する事が解る。[0032]Furthermore, the torsional rigidity of each support arm portion 30, 30 is also improved compared to conventional products. That is, the bending rigidity of the support arms 30, 30 is proportional to the moment of inertia I of each support arm 30, 30, and in the case of the conventional product, the moment of inertia I is I=bh 3 /12. In the case of the product of the present invention, I=b(h 0 3 −h i 3 )/12, respectively. Based on the above-mentioned conditions, the moment of inertia I of the area at a point near the base of the support arm of the conventional yoke is found to be 6.08×10 3 (mm 4 ). In the case of the invented product, assuming the aforementioned width dimension t = 6 mm, it becomes 10.6 x 10 3 (mm 4 ), and it can be seen that in the case of the invented product, the torsional rigidity of each support arm portion 30, 30 is also improved. .
【００３３】 例えば、本考案者の行なった実験によると、図７に示す様な従来形状のヨーク の場合、各支持腕部３０、３０に加えられたトルクと捩れ角との関係が、図６に 破線で示す様に変化したのに対して、本考案品の場合には、同図に実線で示す様 に変化した。この図６の記載からも、本考案の自在継手用ヨークが、十分な強度 と剛性とを有する事が解る。[0033] For example, according to experiments conducted by the present inventor, a conventionally shaped yoke as shown in Fig. In this case, the relationship between the torque applied to each support arm 30 and the torsion angle is shown in FIG. In contrast, in the case of the invented product, the change was as shown by the solid line in the same figure. It changed to From the description in Fig. 6, it can be seen that the yoke for the universal joint of the present invention has sufficient strength. It can be seen that the material has the following properties:
【００３４】[0034]
本考案の自在継手用ヨークは、以上に述べた通り、十分な強度を保持しつつ軽 量化を図れる為、自在継手を組み込んだ装置の軽量化を図れる。 As stated above, the yoke for universal joints of this invention is lightweight while maintaining sufficient strength. Since it can be quantified, it is possible to reduce the weight of devices incorporating universal joints.
【図１】本考案の自在継手用ヨークの第一実施例を示す
斜視図。FIG. 1 is a perspective view showing a first embodiment of a yoke for a universal joint of the present invention.
【図２】同平面図。FIG. 2 is a plan view of the same.
【図３】図２のＡ−Ａ断面図。FIG. 3 is a sectional view taken along line AA in FIG. 2;
【図４】同展開図。[Fig. 4] Developed view of the same.
【図５】第二実施例を示す展開図。FIG. 5 is a developed view showing a second embodiment.
【図６】本考案品と従来品との強度を比較した線図。FIG. 6 is a diagram comparing the strength of the product of the present invention and the conventional product.
【図７】従来の自在継手用ヨークの展開図。FIG. 7 is a developed view of a conventional yoke for a universal joint.
【図８】弾性自在継手の分解斜視図。FIG. 8 is an exploded perspective view of the elastic universal joint.
【図９】同じく組み立てた状態を示す斜視図。FIG. 9 is a perspective view showing the same assembled state.
【図１０】同じく使用状態を示す側面図。FIG. 10 is a side view showing the state of use.
１ フランジ ２ 軸 ３ カップリング部材 ４ ヨーク ５ ステアリングシャフト ６ 十字軸 ７ 第一のボルト ８ 第一のナット ９ 第一の抑え板 １０ 通孔 １１ 通孔 １２ 通孔 １３ 通孔 １４ 第二のボルト １５ 第二のナット １６ 第二の抑え板 １７ 通孔 １８ 通孔 １９ 自在継手 ２０ 連結ロッド ２１ 第一のスリーブ ２２ 第二の切り欠き ２３ 第二のスリーブ ２４ 第一の切り欠き ２５ 素材 ２６ 円孔 ２７ 円孔 ２８ 透孔 ２９ 取付基板部 ３０ 支持腕部 ３１ 素材 ３２ ヨーク 1 flange 2 axes 3 Coupling member 4 York 5 Steering shaft 6 Cross axis 7 First bolt 8 First nut 9 First restraining plate 10 Through hole 11 Through hole 12 Through hole 13 Through hole 14 Second bolt 15 Second nut 16 Second holding plate 17 Through hole 18 Through hole 19 Universal joint 20 Connecting rod 21 First sleeve 22 Second notch 23 Second sleeve 24 First notch 25 Material 26 Circular hole 27 Circular hole 28 Through hole 29 Mounting board part 30 Support arm 31 Material 32 York
Claims (1)
基板部と、この取付基板部の両端から同方向にほぼ直角
に折れ曲がった支持腕部と、両支持腕部の先端部に形成
された、互いに同心の１対の円孔とから成る自在継手用
ヨークに於いて、前記取付基板部の幅方向中央部から前
記両支持腕部の基部に亙る透孔を形成した事を特徴とす
る自在継手用ヨーク。Claim 1: It is formed by bending a thick metal plate, and includes a mounting board, support arms bent from both ends of the mounting board at substantially right angles in the same direction, and tips of both support arms. Further, in the yoke for a universal joint comprising a pair of circular holes concentric with each other, a through hole is formed extending from the widthwise center of the mounting board part to the bases of both the support arms. Yoke for universal joints.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991042859U JP2578809Y2 (en) | 1991-05-14 | 1991-05-14 | Yoke for universal joint |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991042859U JP2578809Y2 (en) | 1991-05-14 | 1991-05-14 | Yoke for universal joint |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04127423U true JPH04127423U (en) | 1992-11-19 |
| JP2578809Y2 JP2578809Y2 (en) | 1998-08-20 |
Family
ID=31923280
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1991042859U Expired - Lifetime JP2578809Y2 (en) | 1991-05-14 | 1991-05-14 | Yoke for universal joint |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2578809Y2 (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6382891A (en) * | 1986-09-26 | 1988-04-13 | 木村 攻二 | Manufacture of front fork for bicycle consisting of carbon fiber composite body |
| JPH01250620A (en) * | 1987-12-07 | 1989-10-05 | Dana Corp | Universal joint and yoke made of ferrous metal thereof |
| JPH02292520A (en) * | 1990-04-20 | 1990-12-04 | Fuji Kiko Co Ltd | Universal joint |
-
1991
- 1991-05-14 JP JP1991042859U patent/JP2578809Y2/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6382891A (en) * | 1986-09-26 | 1988-04-13 | 木村 攻二 | Manufacture of front fork for bicycle consisting of carbon fiber composite body |
| JPH01250620A (en) * | 1987-12-07 | 1989-10-05 | Dana Corp | Universal joint and yoke made of ferrous metal thereof |
| JPH02292520A (en) * | 1990-04-20 | 1990-12-04 | Fuji Kiko Co Ltd | Universal joint |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2578809Y2 (en) | 1998-08-20 |
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| EXPY | Cancellation because of completion of term |