JPH07269579A - Flange hub for connecting rotary shaft - Google Patents

Flange hub for connecting rotary shaft

Info

Publication number
JPH07269579A
JPH07269579A JP6063239A JP6323994A JPH07269579A JP H07269579 A JPH07269579 A JP H07269579A JP 6063239 A JP6063239 A JP 6063239A JP 6323994 A JP6323994 A JP 6323994A JP H07269579 A JPH07269579 A JP H07269579A
Authority
JP
Japan
Prior art keywords
hub body
hub
peripheral surface
flange
outer peripheral
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
Application number
JP6063239A
Other languages
Japanese (ja)
Other versions
JP2694683B2 (en
Inventor
Yasunori Tanizawa
安則 谷澤
Masakuni Nakamura
正久仁 中村
Hidenori Kawamura
秀紀 川村
Miyahiko Koshiba
宮比古 小柴
Takayuki Watanabe
孝行 渡辺
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NAKAMURA JICO KK
NAKAMURA JIKOU KK
Nippon Steel Corp
Original Assignee
NAKAMURA JICO KK
NAKAMURA JIKOU KK
Sumitomo Metal Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NAKAMURA JICO KK, NAKAMURA JIKOU KK, Sumitomo Metal Industries Ltd filed Critical NAKAMURA JICO KK
Priority to JP6063239A priority Critical patent/JP2694683B2/en
Publication of JPH07269579A publication Critical patent/JPH07269579A/en
Application granted granted Critical
Publication of JP2694683B2 publication Critical patent/JP2694683B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

PURPOSE:To provide a flange hub for connecting a rotary shaft in which a pressure contact force to the outer peripheral surface of a rotary shaft is uniformed when the rotary shaft is connected. CONSTITUTION:In a pair of chord planes 6b in the oval hole 6 of a flange hub 14, four slits 15 extending in the axial direction respectively, and cut in the direction orthogonal to the chord planes 6b are formed. The four slits 15 are provided at almost equal intervals in the direction of the chord, and their bottoms are cut to the position to contact to an imaginary extention surface M of the circumferential surface 6a. In this case, the opening widths of the slits 15 at the chord planes 6b are made 3mm to 4mm, and large width parts 15a with a circular pipe form whose diameters are larger than the opening width of the slits 15 at the chord planes 6b are formed at the bottoms of the slits 15.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】本発明は、駆動側の回転軸と従動
側の回転軸とを連結するためのフランジハブに係り、特
にハブ本体外周面が均一圧縮されて弾性変形することに
よりハブ本体内に挿入された回転軸を固定する回転軸連
結用フランジハブに関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flange hub for connecting a rotary shaft on a driving side and a rotary shaft on a driven side, and more particularly, the outer peripheral surface of the hub main body is uniformly compressed and elastically deformed. The present invention relates to a rotary shaft connecting flange hub for fixing a rotary shaft inserted therein.

【0002】[0002]

【従来の技術】図6は油圧固定継手及び油圧固定継手と
共に用いられる従来のフランジハブを示す側面断面図、
図7は図6に示した油圧固定継手及びフランジハブの軸
方向の正面断面図である。
2. Description of the Related Art FIG. 6 is a side sectional view showing a hydraulic fixed joint and a conventional flange hub used together with the hydraulic fixed joint.
FIG. 7 is an axial front sectional view of the hydraulic fixed joint and the flange hub shown in FIG.

【0003】1は油圧固定継手、2は油圧固定継手1に
おいて環状に形成された継手本体、3は継手本体2内に
おいて内周面2aに沿って形成された環状の油圧室であ
る。油圧室3には、図示を省略した油供給手段が接続さ
れており、この油供給手段は、軸連結時に油圧室3に高
圧の作動油を供給し圧力を保持する。
Reference numeral 1 is a hydraulic fixed joint, 2 is a joint main body formed in the hydraulic fixed joint 1 in an annular shape, and 3 is an annular hydraulic chamber formed in the joint main body 2 along an inner peripheral surface 2a. An oil supply means (not shown) is connected to the hydraulic chamber 3, and the oil supply means supplies a high-pressure hydraulic oil to the hydraulic chamber 3 to hold the pressure when the shaft is connected.

【0004】4は回転軸連結用のフランジハブ、5はフ
ランジハブ4において円柱状に形成されたハブ本体、6
はハブ本体5の一端面において開口する小判形孔、7は
ハブ本体5の他端部に固定されたフランジである。小判
形孔6は、回転中心となるハブ本体5の仮想中心線Lか
ら半径R離間した円周面部6a及びそれぞれが平行な一
対の弦平面部6bによって形成されている。
Reference numeral 4 denotes a flange hub for connecting the rotary shaft, 5 denotes a hub body formed in the flange hub 4 in a cylindrical shape, 6
Is an oval hole opened at one end surface of the hub body 5, and 7 is a flange fixed to the other end portion of the hub body 5. The oval hole 6 is formed by a circumferential surface portion 6a separated by a radius R from an imaginary center line L of the hub body 5 which is the center of rotation, and a pair of chordal plane portions 6b parallel to each other.

【0005】油圧固定継手1及びフランジハブ4は、従
動軸10を駆動軸(図示省略)に連結するために用いられ
る。従動軸10は、端部付近に小判形孔6と相似形状で段
面積が僅かに小さい挿入部10aが形成され、挿入部10a
は、軸連結時に小判形孔6に嵌挿する。また、駆動軸の
フランジ(図示省略)は、フランジハブ4のフランジ7と
ボルトやナット等によって締結固定される。
The hydraulic fixed joint 1 and the flange hub 4 are used to connect the driven shaft 10 to a drive shaft (not shown). The driven shaft 10 has an insertion portion 10a formed in a shape similar to the oval hole 6 and having a slightly small step area in the vicinity of the end portion.
Is inserted into the oval hole 6 when the shaft is connected. Further, the flange (not shown) of the drive shaft is fastened and fixed to the flange 7 of the flange hub 4 with bolts, nuts or the like.

【0006】軸連結時には、継手本体2がハブ本体5に
外嵌し、かつ小判形孔6に従動軸10の挿入部10aが嵌挿
して、従動軸10が回転方向においてフランジハブ4に固
定される。この状態で、油供給手段によって油圧室3に
高圧の作動油を充填することにより、継手本体2におけ
る内周面2aと油圧室3との隔壁2bが半径方向に膨出し
て、ハブ本体5外周面に周方向において均一分布する圧
縮応力を作用させる。ここで、ハブ本体5は、例えば、
鋼によって形成され、弾性限度の範囲内で弾性変形可能
である。
When the shafts are connected, the joint body 2 is fitted onto the hub body 5 and the insertion portion 10a of the driven shaft 10 is fitted into the oval hole 6 so that the driven shaft 10 is fixed to the flange hub 4 in the rotational direction. It In this state, by filling the hydraulic chamber 3 with high-pressure hydraulic oil by the oil supply means, the partition wall 2b between the inner peripheral surface 2a of the joint body 2 and the hydraulic chamber 3 bulges in the radial direction, and the outer periphery of the hub body 5 A compressive stress uniformly distributed in the circumferential direction is applied to the surface. Here, the hub body 5 is, for example,
It is made of steel and is elastically deformable within elastic limits.

【0007】外周面に作用する応力によってハブ本体5
が収縮するので、小判形孔6の断面積も収縮して円周面
部6a及び弦平面部6bが従動軸10の挿入部10aに圧接す
る。このことにより、小判形孔6に挿入され回転方向で
固定された挿入部10aが軸方向においても固定され、従
動軸10はフランジハブ4に固定される。
Due to the stress acting on the outer peripheral surface, the hub body 5
Contract, the sectional area of the oval hole 6 also contracts, and the circumferential surface portion 6a and the chordal plane portion 6b are pressed against the insertion portion 10a of the driven shaft 10. As a result, the insertion portion 10a inserted into the oval hole 6 and fixed in the rotational direction is also fixed in the axial direction, and the driven shaft 10 is fixed to the flange hub 4.

【0008】通常、駆動軸がフランジ7に固定された状
態で、上記したように従動軸10がフランジハブ4に固定
される。また、従動軸10を切り離す場合には、油圧室3
の作動油を減圧することにより、隔壁2bが元の形状に
復元するので、従動軸10を小判形孔6から抜き取ること
が可能になる。このように、油圧固定継手1及びフラン
ジハブ4を用いることにより、従動軸10の交換が容易に
なり、例えば、従動軸10と一体の圧延ロールの交換を短
時間で行うことが可能になる。
Normally, the driven shaft 10 is fixed to the flange hub 4 as described above, with the drive shaft fixed to the flange 7. When disconnecting the driven shaft 10, the hydraulic chamber 3
By decompressing the working oil of No. 2, the partition wall 2b is restored to its original shape, so that the driven shaft 10 can be pulled out from the oval hole 6. As described above, by using the hydraulic fixed joint 1 and the flange hub 4, the driven shaft 10 can be easily replaced, and for example, the rolling roll integrated with the driven shaft 10 can be replaced in a short time.

【0009】[0009]

【発明が解決しようとする課題】図8は軸開放時から軸
連結時への従来のフランジハブの変形を示す説明図であ
る。上記したフランジハブ4においては、ハブ本体5と
小判形孔6との間の肉厚が一定になっておらず、ハブ本
体5は、円周面部6aの外側部分で弦平面部6bの外側部
分より肉厚が薄くなっている。このことにより、相対的
に円周面部6a外側の薄肉部分は剛性が小さく、弦平面
部6b外側の厚肉部分は剛性が大きいものになってい
る。
FIG. 8 is an explanatory view showing the deformation of the conventional flange hub from the time of opening the shaft to the time of connecting the shaft. In the flange hub 4 described above, the thickness between the hub body 5 and the oval hole 6 is not constant, and the hub body 5 has an outer portion of the circumferential surface portion 6a and an outer portion of the chordal plane portion 6b. The wall thickness is thinner. As a result, the thin portion outside the circumferential surface portion 6a has a relatively low rigidity, and the thick portion outside the chordal plane portion 6b has a large rigidity.

【0010】ハブ本体5の周方向における剛性分布が一
定でないため、図8に示すように小判形孔6に挿入部10
aが嵌挿していない状態で、継手本体2によってハブ本
体5外周面を均一応力で圧縮した場合、ハブ本体5は、
2点鎖線によって示すように相対的に円周面部6a外側
の薄肉部分での変形量が大きくなり、弦平面部6b外側
の厚肉部分での変形量が小さくなる。このため、軸連結
時における従動軸10の挿入部10aに対する圧接力は、弦
平面部6bで大きくなり、かつ円周面部6a中央付近で小
さくなる。
Since the rigidity distribution in the circumferential direction of the hub body 5 is not constant, the insertion portion 10 is inserted into the oval hole 6 as shown in FIG.
When the outer peripheral surface of the hub body 5 is compressed by the joint body 2 with a uniform stress in the state where a is not inserted, the hub body 5 is
As indicated by the chain double-dashed line, the amount of deformation in the thin portion outside the circumferential surface portion 6a becomes relatively large, and the amount of deformation in the thick portion outside the chordal plane portion 6b becomes small. Therefore, the pressure contact force of the driven shaft 10 with respect to the insertion portion 10a at the time of shaft coupling becomes large at the chordal plane portion 6b and becomes small near the center of the circumferential surface portion 6a.

【0011】軸連結時の圧接力が円周面部6a中央付近
で小さくなることにより、挿入部10aに対して十分な固
定力を発生させようとした場合、ハブ本体5外周面に対
する圧縮応力を大きくしなければならない。圧縮応力を
大きくすることにより、フランジハブ4が金属疲労によ
って劣化しやすくなり寿命が短くなり、また挿入部10a
に偏摩耗を発生させやすくなる。
When an attempt is made to generate a sufficient fixing force for the insertion portion 10a by reducing the pressure contact force at the time of connecting the shafts in the vicinity of the center of the circumferential surface portion 6a, a large compressive stress is applied to the outer peripheral surface of the hub body 5. Must. By increasing the compressive stress, the flange hub 4 is prone to deterioration due to metal fatigue, shortening the service life, and reducing the insertion portion 10a.
Uneven wear is likely to occur.

【0012】本発明の目的は、上記の問題を解決するた
め、軸連結時に回転軸外周面に対する圧接力が均一化さ
れた回転軸連結用フランジハブを提供することにある。
In order to solve the above problems, an object of the present invention is to provide a rotary shaft connecting flange hub in which the pressure contact force to the outer peripheral surface of the rotary shaft is made uniform when the shafts are connected.

【0013】[0013]

【課題を解決するための手段】上記の課題を解決するた
め、本発明の第1の手段は、円柱状のハブ本体と、この
ハブ本体に固定されたフランジと、ハブ本体回転中心か
ら一定半径の円周面部及びそれぞれが平行な一対の弦平
面部によって形成され、前記ハブ本体の少なくとも一端
面で開口した小判形孔とを備え、前記ハブ本体外周面が
均一応力によって加圧され、前記小判形孔に挿入された
回転軸に小判形孔内周面を圧接させる回転軸連結用フラ
ンジハブにおいて、前記弦平面部に、前記円周面部の仮
想延長面の内側に2本乃至5本の軸方向に延在するスリ
ットを形成し、しかも前記スリット底部に、円形パイプ
状の幅広部を設けたことを特徴とする。
In order to solve the above problems, the first means of the present invention is to provide a cylindrical hub body, a flange fixed to the hub body, and a constant radius from the center of rotation of the hub body. And an oval hole which is formed by a pair of parallel chordal planes each of which is parallel to each other, and which is open at least at one end surface of the hub body, the outer peripheral surface of the hub body is pressed by a uniform stress, and the oval shape is formed. A rotary shaft connecting flange hub for press-contacting an inner peripheral surface of an oval hole with a rotary shaft inserted in a shaped hole, wherein two to five shafts are provided on the chordal plane portion inside a virtual extension surface of the circumferential surface portion. A slit extending in the direction is formed, and a circular pipe-shaped wide portion is provided at the bottom of the slit.

【0014】また、第2の手段は、円柱状のハブ本体
と、このハブ本体に固定されたフランジと、ハブ本体回
転中心から一定半径Rの円周面部及びそれぞれが平行な
一対の弦平面部によって形成され、前記ハブ本体の少な
くとも一端面で開口した小判形孔とを備え、前記ハブ本
体外周面が均一応力によって加圧され、前記小判形孔に
挿入された回転軸に小判形孔内周面を圧接させる回転軸
連結用フランジハブにおいて、前記弦平面部中央部に、
軸方向に延在し前記円周面部の延長面を底面とする溝を
形成し、前記溝の開口幅Wを、前記一定半径Rの0.70倍
乃至0.85倍にしたことを特徴とする。
The second means is a cylindrical hub body, a flange fixed to the hub body, a circumferential surface portion having a constant radius R from the center of rotation of the hub body, and a pair of chordal plane portions parallel to each other. And an oval hole formed in at least one end surface of the hub body, the outer peripheral surface of the hub body being pressed by uniform stress, and the inner circumference of the oval hole being inserted into the oval hole. In the rotary shaft connecting flange hub that presses the surfaces, in the central portion of the chordal plane portion,
A groove extending in the axial direction and having an extension surface of the circumferential surface portion as a bottom surface is formed, and an opening width W of the groove is set to 0.70 to 0.85 times the constant radius R.

【0015】また、第3の手段は、円柱状のハブ本体
と、このハブ本体に固定されたフランジと、ハブ本体回
転中心から一定半径の円周面部及びそれぞれが平行な一
対の弦平面部によって形成され、前記ハブ本体の少なく
とも一端面で開口した小判形孔とを備え、前記ハブ本体
外周面が均一応力によって加圧され、前記小判形孔に挿
入された回転軸に小判形孔内周面を圧接させる回転軸連
結用フランジハブにおいて、前記弦平面部中央位置と前
記ハブ本体外周面との間に、軸方向に延在する第1の円
形孔を穿設し、かつ前記弦平面部と前記ハブ本体外周面
との間に、前記第1の円形孔の両側方にそれぞれ配置さ
れ軸方向に延在する一対の第2の円形孔を穿設し、しか
も第1の円形孔の径を前記第2の円形孔より大きくした
ことを特徴とする。
A third means is a cylindrical hub body, a flange fixed to the hub body, a circumferential surface portion having a constant radius from the center of rotation of the hub body, and a pair of chordal plane portions parallel to each other. And an oval hole formed in at least one end surface of the hub body, the outer peripheral surface of the hub body being pressed by a uniform stress, and the oval hole inner peripheral surface of the rotating shaft inserted into the oval hole. In the rotary shaft connecting flange hub that presses against each other, a first circular hole extending in the axial direction is bored between the central position of the chordal plane portion and the outer peripheral surface of the hub body, and A pair of second circular holes, which are arranged on both sides of the first circular hole and extend in the axial direction, are bored between the outer peripheral surface of the hub body and the diameter of the first circular hole. It is characterized in that it is made larger than the second circular hole.

【0016】また、第4の手段は、円柱状のハブ本体
と、このハブ本体に固定されたフランジと、ハブ本体回
転中心から一定半径Rの円周面部及びそれぞれが平行な
一対の弦平面部によって形成され、前記ハブ本体の少な
くとも一端面で開口した小判形孔とを備え、前記ハブ本
体外周面が均一応力によって加圧され、前記小判形孔に
挿入された回転軸に小判形孔内周面を圧接させる回転軸
連結用フランジハブにおいて、前記弦平面部の両端部
に、前記円周面部と連続する曲率半径rの円形溝を形成
し、前記曲率半径rを前記一定半径Rの0.10倍乃至0.14
倍にしたことを特徴とする。
A fourth means is a cylindrical hub body, a flange fixed to the hub body, a circumferential surface portion having a constant radius R from the center of rotation of the hub body, and a pair of chordal plane portions parallel to each other. And an oval hole formed in at least one end surface of the hub body, the outer peripheral surface of the hub body being pressed by uniform stress, and the inner circumference of the oval hole being inserted into the oval hole. In the rotary shaft connecting flange hub that presses the surfaces, circular grooves having a radius of curvature r continuous with the circumferential surface portion are formed at both ends of the chordal plane portion, and the radius of curvature r is 0.10 times the constant radius R. To 0.14
It is characterized by doubling.

【0017】[0017]

【作用】上記の第1の手段によれば、ハブ本体外周面と
弦平面部との間の厚肉部分の剛性が低下してハブ本体に
おける周方向の剛性が均一化し、かつスリット底部での
応力集中が防止される。
According to the above-mentioned first means, the rigidity of the thick portion between the outer peripheral surface of the hub body and the chordal plane portion is reduced to make the rigidity of the hub body uniform in the circumferential direction, and at the slit bottom portion. Stress concentration is prevented.

【0018】また、第2の手段によれば、ハブ本体外周
面と弦平面部との間の厚肉部分の剛性が低下してハブ本
体における周方向の剛性が均一化し、かつ弦平面部の回
転軸外周面に対する接触面積が十分確保される。
Further, according to the second means, the rigidity of the thick portion between the outer peripheral surface of the hub body and the chordal plane portion is reduced, and the rigidity in the circumferential direction of the hub body is made uniform, and the chordal plane portion has a uniform rigidity. A sufficient contact area with the outer peripheral surface of the rotating shaft is secured.

【0019】また、第3の手段によれば、ハブ本体外周
面と弦平面部との間の厚肉部分の剛性が低下してハブ本
体における周方向の剛性が均一化する。
According to the third means, the rigidity of the thick portion between the outer peripheral surface of the hub body and the chordal plane portion is reduced, and the rigidity of the hub body in the circumferential direction is made uniform.

【0020】また、第4の手段によれば、弦平面部と円
周面部とのコーナ部における応力集中が抑制される。
Further, according to the fourth means, stress concentration at the corner portions of the chordal plane portion and the circumferential surface portion is suppressed.

【0021】[0021]

【実施例】以下、本発明の実施例を図面に基づいて説明
する。尚、図1乃至図4において図6及び図7に基づい
て説明した部材に対応する部材については、同一符号を
付して説明を省略する。図1は本発明の回転軸連結用の
フランジハブの第1実施例を示す軸方向正面図である。
フランジハブ14の小判形孔6において一対の弦平面部6
bには、それぞれ軸方向に延在し、かつ弦平面部6bに対
して直交する方向に切り込まれた4本のスリット15が形
成されている。4本のスリット15は、弦方向において略
等間隔に配置され、それぞれの底が円周面部6aの仮想
延長面Mに接する位置まで切り込まれている。この結
果、スリット15は、弦平面部6bの中央に近いものほど
深く切り込まれている。
Embodiments of the present invention will be described below with reference to the drawings. 1 to 4, members corresponding to the members described with reference to FIGS. 6 and 7 are designated by the same reference numerals and the description thereof will be omitted. FIG. 1 is an axial front view showing a first embodiment of a flange hub for connecting a rotary shaft of the present invention.
In the oval hole 6 of the flange hub 14, the pair of chord flat parts 6
Four slits 15 extending in the axial direction and cut in a direction orthogonal to the chordal plane portion 6b are formed in b. The four slits 15 are arranged at substantially equal intervals in the chord direction, and are cut to the position where the bottoms of the four slits 15 contact the virtual extension surface M of the circumferential surface portion 6a. As a result, the slit 15 is cut deeper toward the center of the chordal plane portion 6b.

【0022】ここで、それぞれのスリット15の弦平面部
6bでの開口幅は3mm乃至4mmの範囲内に設定され、ス
リット15の底部には、弦平面部6bでのスリット15の開
口幅より径が大きい円形パイプ状の幅広部15aが形成さ
れている。
Here, the opening width of each slit 15 at the chordal plane portion 6b is set within the range of 3 mm to 4 mm, and the diameter of the slit 15 at the bottom is larger than the opening width of the slit 15 at the chordal plane portion 6b. A wide portion 15a having a large circular pipe shape is formed.

【0023】弦平面部6bにスリット15を形成したこと
により、ハブ本体5外周面と弦平面部6bとの間の厚肉
部分の剛性が低下する。スリット15の本数及び開口幅
は、有限要素法によって厚肉部分での剛性がハブ本体5
外周面と円周面部6aとの間の薄肉部分での剛性と略等
しくなるように算出されたものである。このことによ
り、ハブ本体5における周方向の剛性分布が均一化す
る。また、スリット15の底部に円形断面の幅広部15aを
形成したことにより、スリット15底部での応力集中を防
止できるので、繰返し応力によるスリット15底部の割れ
を防止できる。
By forming the slits 15 in the chordal plane portion 6b, the rigidity of the thick portion between the outer peripheral surface of the hub body 5 and the chordal plane portion 6b is reduced. Regarding the number of slits 15 and the opening width, the rigidity in the thick portion is determined by the finite element method.
The rigidity is calculated so as to be substantially equal to the rigidity in the thin portion between the outer peripheral surface and the peripheral surface portion 6a. As a result, the rigidity distribution in the circumferential direction of the hub body 5 becomes uniform. Further, since the wide portion 15a having a circular cross section is formed at the bottom of the slit 15, stress concentration at the bottom of the slit 15 can be prevented, so that cracking at the bottom of the slit 15 due to repeated stress can be prevented.

【0024】フランジハブ14の小判形孔6に従動軸10の
挿入部10aを嵌挿して、油圧固定継手1によってハブ本
体5外周面に均一応力を加えた場合、半径方向において
ハブ本体5が均等に収縮するので、従動軸10の挿入部10
a外周面に対する円周面部6a及び弦平面部6bの圧接力
が略等しくなる。このことにより、油圧固定継手1の油
圧室3に充填される作動油の圧力を効率的に挿入部10a
に伝えることができ、従来と比較して作動油圧力を低下
させても十分な圧接力で従動軸10を確実に固定でき、さ
らにハブ本体5の金属疲労及び挿入部10aの偏摩耗を抑
制できる。また、有限要素法による解析では、弦平面部
6bに形成するスリット15の本数を2本乃至5本の範囲
で形成すれば、図示の4本のスリット15が形成されたフ
ランジハブ14と同等の性能が得られることが明らかにな
っており、弦平面部6bに形成するスリット15を2本,
3本あるいは5本にすることも可能である。
When the insertion portion 10a of the driven shaft 10 of the oval hole 6 of the flange hub 14 is fitted and uniform stress is applied to the outer peripheral surface of the hub body 5 by the hydraulic fixed joint 1, the hub body 5 is evenly distributed in the radial direction. The driven shaft 10 inserts 10
The pressure contact forces of the circumferential surface portion 6a and the chordal flat surface portion 6b with respect to the outer peripheral surface are substantially equal. As a result, the pressure of the hydraulic oil with which the hydraulic chamber 3 of the hydraulic fixed joint 1 is filled can be efficiently adjusted.
And the driven shaft 10 can be reliably fixed with a sufficient pressure contact force even when the hydraulic oil pressure is reduced as compared with the prior art, and metal fatigue of the hub body 5 and uneven wear of the insertion portion 10a can be suppressed. . Further, in the analysis by the finite element method, if the number of slits 15 formed in the chordal plane portion 6b is formed within a range of 2 to 5, it is equivalent to the flange hub 14 in which the four slits 15 shown are formed. It has been clarified that the performance can be obtained, and two slits 15 are formed in the chordal plane portion 6b,
It is also possible to use three or five.

【0025】図2は本発明の回転軸連結用のフランジハ
ブの第2実施例を示す軸方向正面図である。フランジハ
ブ24の小判形孔6において一対の弦平面部6bには、そ
れぞれ軸方向に延在し、かつ弦方向において開口幅Wの
溝25が形成されている。ここで、溝25は弦平面部6bの
中央位置で開口し、溝25の開口幅Wは、円周面部6aの
半径Rの0.70倍乃至0.85倍に設定されている。また、溝
25の底面部25aは、円周面部6aの延長面によって形成さ
れている。
FIG. 2 is an axial front view showing a second embodiment of the flange hub for connecting the rotating shaft of the present invention. In the oval hole 6 of the flange hub 24, a pair of chord plane portions 6b are formed with grooves 25 each extending in the axial direction and having an opening width W in the chord direction. Here, the groove 25 opens at the central position of the chordal plane portion 6b, and the opening width W of the groove 25 is set to 0.70 to 0.85 times the radius R of the circumferential surface portion 6a. Also, the groove
The bottom surface portion 25a of 25 is formed by an extension surface of the circumferential surface portion 6a.

【0026】弦平面部6bに溝25を形成したことによ
り、ハブ本体5外周面と弦平面部6bとの間の厚肉部分
の剛性が低下する。溝25の形状及び開口幅Wは、有限要
素法によって厚肉部分での剛性がハブ本体5外周面と円
周面部6aとの間の薄肉部分での剛性と略等しくなるよ
うに算出されたものであり、さらに従動軸10の挿入部10
aに対する弦平面部6bの接触面積が十分確保されるよう
にしたものである。このことにより、ハブ本体5におけ
る周方向の剛性分布が均一化し、かつ挿入部10a外周面
に対する小判形孔6の接触面積が十分確保される。
By forming the groove 25 in the chordal plane portion 6b, the rigidity of the thick portion between the outer peripheral surface of the hub body 5 and the chordal plane portion 6b is reduced. The shape and opening width W of the groove 25 are calculated by the finite element method so that the rigidity in the thick portion is substantially equal to the rigidity in the thin portion between the outer peripheral surface of the hub body 5 and the circumferential surface portion 6a. And the insertion part 10 of the driven shaft 10
The contact area of the chordal plane portion 6b with respect to a is sufficiently secured. As a result, the rigidity distribution in the circumferential direction of the hub body 5 is made uniform, and the contact area of the oval hole 6 with the outer peripheral surface of the insertion portion 10a is sufficiently secured.

【0027】フランジハブ24の小判形孔6に従動軸10の
挿入部10aを嵌挿して、油圧固定継手1によってハブ本
体5外周面に均一応力を加えた場合、半径方向において
ハブ本体5が均等に収縮するので、従動軸10の挿入部10
a外周面に対する円周面部6a及び弦平面部6bの圧接力
が略等しくなり、かつ十分な接触面積が確保される。こ
のことにより、油圧固定継手1の油圧室3に充填される
作動油の圧力を効率的に挿入部10aに伝えることがで
き、従来と比較して作動油圧力を低下させても十分な圧
接力で従動軸10を確実に固定でき、さらにハブ本体5の
金属疲労及び挿入部10aの偏摩耗を抑制できる。
When the insertion portion 10a of the driven shaft 10 is fitted into the oval hole 6 of the flange hub 24 and uniform stress is applied to the outer peripheral surface of the hub body 5 by the hydraulic fixed joint 1, the hub body 5 is evenly distributed in the radial direction. The driven shaft 10 inserts 10
The pressure contact forces of the circumferential surface portion 6a and the chordal flat surface portion 6b with respect to the outer peripheral surface are substantially equal, and a sufficient contact area is secured. As a result, the pressure of the hydraulic oil filled in the hydraulic chamber 3 of the hydraulic fixed joint 1 can be efficiently transmitted to the insertion portion 10a, and a sufficient pressure contact force can be obtained even if the hydraulic oil pressure is reduced as compared with the conventional case. Thus, the driven shaft 10 can be securely fixed, and further, metal fatigue of the hub body 5 and uneven wear of the insertion portion 10a can be suppressed.

【0028】図3は本発明の回転軸連結用のフランジハ
ブの第3実施例を示す軸方向正面図である。
FIG. 3 is an axial front view showing a third embodiment of the flange hub for connecting a rotating shaft according to the present invention.

【0029】フランジハブ34のハブ本体5において、一
対の弦平面部6bのそれぞれの中央位置とハブ本体5外
周面との間には、軸方向に延在する円形孔35が穿設さ
れ、さらに、弦平面部6bとハブ本体5外周面との間に
は、円形孔35の両側方にそれぞれ配置され軸方向に延在
する一対の円形孔36が穿設されている。ここで、中央の
円形孔35は、その径が側方の円形孔36より大きくされて
いる。
In the hub body 5 of the flange hub 34, a circular hole 35 extending in the axial direction is bored between the central position of each of the pair of chordal plane portions 6b and the outer peripheral surface of the hub body 5. A pair of circular holes 36, which are arranged on both sides of the circular hole 35 and extend in the axial direction, are formed between the chordal plane portion 6b and the outer peripheral surface of the hub body 5. Here, the central circular hole 35 has a diameter larger than that of the lateral circular holes 36.

【0030】弦平面部6bとハブ本体5外周面との間に
円形孔35,36を穿設したことにより、ハブ本体5外周面
と弦平面部6bとの間の厚肉部分の剛性が低下する。円
形孔35,36の径及び位置は、有限要素法によって厚肉部
分での剛性がハブ本体5外周面と円周面部6aとの間の
薄肉部分での剛性と略等しくなるように算出されたもの
である。このことにより、ハブ本体5における周方向の
剛性分布が均一化する。
By forming the circular holes 35 and 36 between the chord plane portion 6b and the hub body 5 outer peripheral surface, the rigidity of the thick portion between the hub body 5 outer peripheral surface and the chord plane portion 6b is reduced. To do. The diameters and positions of the circular holes 35 and 36 were calculated by the finite element method so that the rigidity in the thick portion was substantially equal to the rigidity in the thin portion between the outer peripheral surface of the hub body 5 and the circumferential surface portion 6a. It is a thing. As a result, the rigidity distribution in the circumferential direction of the hub body 5 becomes uniform.

【0031】フランジハブ34の小判形孔6に従動軸10の
挿入部10aを嵌挿して、油圧固定継手1によってハブ本
体5外周面に均一応力を加えた場合、半径方向において
ハブ本体5が均等に収縮するので、挿入部10a外周面に
対する円周面部6a及び弦平面部6bの圧接力が略等しく
なる。このことにより、油圧固定継手1の油圧室3に充
填される作動油の圧力を効率的に挿入部10aに伝えるこ
とができ、従来と比較して作動油圧力を低下させても十
分な圧接力で従動軸10を確実に固定でき、さらにハブ本
体5の金属疲労及び挿入部10aの偏摩耗を抑制できる。
When the insertion portion 10a of the driven shaft 10 is fitted into the oval hole 6 of the flange hub 34 and uniform stress is applied to the outer peripheral surface of the hub body 5 by the hydraulic fixed joint 1, the hub body 5 is evenly distributed in the radial direction. As a result, the circumferential surface portion 6a and the chordal plane portion 6b have substantially the same pressure contact force with respect to the outer peripheral surface of the insertion portion 10a. As a result, the pressure of the hydraulic oil filled in the hydraulic chamber 3 of the hydraulic fixed joint 1 can be efficiently transmitted to the insertion portion 10a, and a sufficient pressure contact force can be obtained even if the hydraulic oil pressure is reduced as compared with the conventional case. Thus, the driven shaft 10 can be securely fixed, and further, metal fatigue of the hub body 5 and uneven wear of the insertion portion 10a can be suppressed.

【0032】図4は本発明の回転軸連結用のフランジハ
ブの第4実施例を示す軸方向正面図である。
FIG. 4 is an axial front view showing a fourth embodiment of the flange hub for connecting a rotary shaft of the present invention.

【0033】フランジハブ44の小判形孔6において一対
の弦平面部6bの両端部には、それぞれ軸方向に延在
し、かつ円周面部6aと連続する円形溝45が形成されて
いる。円形溝45は、それぞれ図5の説明図に示すように
弦平面部6bの仮想延長面Nと円周面部6aとの交線Pと
において円周面部6aと滑らかに連続する曲率半径rが
一定の曲面によって形成されている。ここで、円形溝45
の曲率半径rは、円周面部6aの半径Rの0.10倍乃至0.1
4倍に設定されている。
In the oval hole 6 of the flange hub 44, circular grooves 45, which extend in the axial direction and are continuous with the circumferential surface portion 6a, are formed at both ends of the pair of chordal plane portions 6b. As shown in the explanatory view of FIG. 5, each of the circular grooves 45 has a constant radius of curvature r that is smoothly continuous with the circumferential surface portion 6a at the intersection line P between the virtual extension surface N of the chordal plane portion 6b and the circumferential surface portion 6a. It is formed by a curved surface. Where the circular groove 45
Has a radius r of 0.10 to 0.1 times the radius R of the circumferential surface portion 6a.
It is set to 4 times.

【0034】弦平面部6bの両端部に溝25を形成したこ
とにより、弦平面部6bと円周面部6aとが滑らかな曲面
によって結ばれ、コーナ部における応力集中が抑制され
る。ここで、円形溝45の曲率半径rを円周面部6aの半
径Rの0.10倍乃至0.14倍に設定したことにより、許容圧
力の範囲内で油圧固定継手1によってハブ本体5外周面
に圧力を加えた場合、コーナ部に集中する応力を無害化
できるレベルまで応力を分散できるので、ハブ本体5が
金属疲労により破損することを抑制できる。
By forming the grooves 25 at both ends of the chordal plane portion 6b, the chordal plane portion 6b and the circumferential surface portion 6a are connected by a smooth curved surface, and stress concentration at the corner portion is suppressed. Here, by setting the radius of curvature r of the circular groove 45 to 0.10 to 0.14 times the radius R of the circumferential surface portion 6a, pressure is applied to the outer peripheral surface of the hub body 5 by the hydraulic fixed joint 1 within the allowable pressure range. In this case, the stress concentrated in the corner portion can be dispersed to such a level that it can be rendered harmless, so that the hub body 5 can be prevented from being damaged by metal fatigue.

【0035】[0035]

【発明の効果】以上説明したように、本発明の第1の手
段によれば、ハブ本体外周面と弦平面部との間の厚肉部
分の剛性が低下してハブ本体における周方向の剛性が均
一化し、かつスリット底部での応力集中が防止されるこ
とにより、フランジハブの小判形孔に回転軸を嵌挿し
て、ハブ本体外周面に均一応力を加えた場合、半径方向
においてハブ本体が均等に収縮するので、回転軸外周面
に対する円周面部及び弦平面部の圧接力が略等しくなり
回転軸を確実に固定できるとともに、ハブ本体の金属疲
労及び回転軸の偏摩耗を抑制でき、さらに繰返し応力に
よるスリット底部の割れも防止できる。
As described above, according to the first means of the present invention, the rigidity of the thick portion between the outer peripheral surface of the hub body and the chordal plane portion is reduced, and the rigidity of the hub body in the circumferential direction is reduced. When the rotating shaft is inserted into the oval hole of the flange hub and uniform stress is applied to the outer peripheral surface of the hub main body, the hub main body moves in the radial direction. Since it contracts evenly, the pressure contact forces of the circumferential surface portion and the chordal plane portion with respect to the outer peripheral surface of the rotating shaft are substantially equal, the rotating shaft can be reliably fixed, and metal fatigue of the hub body and uneven wear of the rotating shaft can be suppressed. It is also possible to prevent cracks at the bottom of the slit due to repeated stress.

【0036】また、第2の手段によれば、ハブ本体外周
面と弦平面部との間の厚肉部分の剛性が低下してハブ本
体における周方向の剛性が均一化し、かつ弦平面部の回
転軸外周面に対する接触面積が十分確保されることによ
り、フランジハブの小判形孔に回転軸を嵌挿して、ハブ
本体外周面に均一応力を加えた場合、半径方向において
ハブ本体が均等に収縮し、かつ十分な接触面積が確保さ
れているので、回転軸外周面に対する円周面部及び弦平
面部の圧接力が略等しくなり回転軸を確実に固定でき、
さらにハブ本体の金属疲労及び回転軸の偏摩耗を抑制で
きる。
According to the second means, the rigidity of the thick portion between the outer peripheral surface of the hub body and the chordal plane portion is reduced to make the rigidity of the hub body in the circumferential direction uniform, and By ensuring a sufficient contact area with the outer peripheral surface of the rotating shaft, if the rotating shaft is inserted into the oval hole of the flange hub and uniform stress is applied to the outer peripheral surface of the hub main body, the hub main body shrinks uniformly in the radial direction. In addition, since the sufficient contact area is secured, the pressure contact force of the circumferential surface portion and the chordal plane portion with respect to the outer peripheral surface of the rotating shaft becomes substantially equal, and the rotating shaft can be securely fixed,
Further, metal fatigue of the hub body and uneven wear of the rotating shaft can be suppressed.

【0037】また、第3の手段によれば、ハブ本体外周
面と弦平面部との間の厚肉部分の剛性が低下してハブ本
体における周方向の剛性が均一化することにより、フラ
ンジハブの小判形孔に回転軸を嵌挿して、ハブ本体外周
面に均一応力を加えた場合、半径方向においてハブ本体
が均等に収縮するので、回転軸外周面に対する円周面部
及び弦平面部の圧接力が略等しくなり、十分な圧接力で
回転軸を確実に固定でき、さらにハブ本体の金属疲労及
び回転軸の偏摩耗を抑制できる。
According to the third means, the rigidity of the thick portion between the outer peripheral surface of the hub body and the chordal plane portion is reduced and the circumferential rigidity of the hub body is made uniform. When the rotating shaft is inserted into the oval hole of and the uniform stress is applied to the outer peripheral surface of the hub body, the hub main body shrinks uniformly in the radial direction. The forces become substantially equal, the rotating shaft can be securely fixed with sufficient pressure contact force, and further metal fatigue of the hub body and uneven wear of the rotating shaft can be suppressed.

【0038】また、第4の手段によれば、弦平面部と円
周面部とのコーナ部における応力集中が抑制され、フラ
ンジハブの許容圧力の範囲内でハブ本体外周面に圧力を
加えた場合、コーナ部に集中する応力を無害化できるレ
ベルまで応力を分散できるので、ハブ本体が金属疲労に
より破損することを抑制できる。
Further, according to the fourth means, stress concentration at the corner portions of the chordal plane portion and the circumferential surface portion is suppressed, and when pressure is applied to the outer peripheral surface of the hub body within the allowable pressure range of the flange hub. Since the stress concentrated on the corners can be dispersed to a level where it can be rendered harmless, it is possible to prevent the hub body from being damaged by metal fatigue.

【図面の簡単な説明】[Brief description of drawings]

【図1】本発明の回転軸連結用のフランジハブの第1実
施例を示す軸方向正面図である。
FIG. 1 is an axial front view showing a first embodiment of a flange hub for connecting a rotating shaft according to the present invention.

【図2】本発明の回転軸連結用のフランジハブの第2実
施例を示す軸方向正面図である。
FIG. 2 is an axial front view showing a second embodiment of the rotary shaft connecting flange hub of the present invention.

【図3】本発明の回転軸連結用のフランジハブの第3実
施例を示す軸方向正面図である。
FIG. 3 is an axial front view showing a third embodiment of the flange hub for connecting the rotating shaft of the present invention.

【図4】本発明の回転軸連結用のフランジハブの第4実
施例を示す軸方向正面図である。
FIG. 4 is an axial front view showing a fourth embodiment of the flange hub for connecting the rotating shaft of the present invention.

【図5】本発明の第4実施例における円形溝の形状の説
明図である。
FIG. 5 is an explanatory diagram of a shape of a circular groove according to a fourth embodiment of the present invention.

【図6】油圧固定継手及び油圧固定継手と共に用いられ
る従来のフランジハブを示す側面断面図である。
FIG. 6 is a side sectional view showing a hydraulic fixed joint and a conventional flange hub used together with the hydraulic fixed joint.

【図7】図6に示した油圧固定継手及びフランジハブの
軸方向の正面断面図である。
7 is an axial front sectional view of the hydraulic fixed joint and the flange hub shown in FIG.

【図8】軸開放時から軸連結時への従来のフランジハブ
の変形を示す説明図である。
FIG. 8 is an explanatory view showing the deformation of the conventional flange hub from the time of opening the shaft to the time of connecting the shaft.

【符号の説明】[Explanation of symbols]

6…小判形孔、 6a…円周面部、 6b…弦平面部、
14,24,34,44…フランジハブ、 15…スリット、 15
a…幅広部、 25…溝、 35…円形孔、 36…円形孔、
45…円形溝、 L…仮想中心線、 R…半径。
6 ... Oval hole, 6a ... Circumferential surface part, 6b ... Chordal plane part,
14, 24, 34, 44 ... Flange hub, 15 ... Slit, 15
a ... Wide part, 25 ... Groove, 35 ... Circular hole, 36 ... Circular hole,
45 ... Circular groove, L ... Virtual center line, R ... Radius.

───────────────────────────────────────────────────── フロントページの続き (72)発明者 川村 秀紀 東京都中央区築地3丁目10番10号 株式会 社中村自工内 (72)発明者 小柴 宮比古 東京都中央区築地3丁目10番10号 株式会 社中村自工内 (72)発明者 渡辺 孝行 東京都中央区築地3丁目10番10号 株式会 社中村自工内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Hideki Kawamura, 3-10-10 Tsukiji, Chuo-ku, Tokyo In-house company Nakamura (72) Inventor, Koshiba Miyabiko 3-10-10, Tsukiji, Chuo-ku, Tokyo No. 10 In-house company of Nakamura (72) Inventor Takayuki Watanabe 3-10-10 Tsukiji, Chuo-ku, Tokyo In-house company of Nakamura

Claims (4)

【特許請求の範囲】[Claims] 【請求項1】 円柱状のハブ本体と、このハブ本体に固
定されたフランジと、ハブ本体回転中心から一定半径の
円周面部及びそれぞれが平行な一対の弦平面部によって
形成され、前記ハブ本体の少なくとも一端面で開口した
小判形孔とを備え、前記ハブ本体外周面が均一応力によ
って加圧され、前記小判形孔に挿入された回転軸に小判
形孔内周面を圧接させる回転軸連結用フランジハブにお
いて、前記弦平面部に、前記円周面部の仮想延長面の内
側に2本乃至5本の軸方向に延在するスリットを形成
し、しかも前記スリット底部に、円形パイプ状の幅広部
を設けたことを特徴とする回転軸連結用フランジハブ。
1. A hub body having a cylindrical shape, a flange fixed to the hub body, a circumferential surface portion having a constant radius from the center of rotation of the hub body, and a pair of chordal plane portions parallel to each other. And an oval hole opened at least at one end surface of the hub body, wherein the outer peripheral surface of the hub body is pressed by a uniform stress, and the inner peripheral surface of the oval hole is pressed against the rotary shaft inserted into the oval hole. In the flange hub for use, in the chordal plane portion, two to five slits extending in the axial direction are formed inside the virtual extension surface of the circumferential surface portion, and at the bottom of the slit, a circular pipe-shaped wide portion is formed. A flange hub for connecting a rotating shaft, which is provided with a portion.
【請求項2】 円柱状のハブ本体と、このハブ本体に固
定されたフランジと、ハブ本体回転中心から一定半径R
の円周面部及びそれぞれが平行な一対の弦平面部によっ
て形成され、前記ハブ本体の少なくとも一端面で開口し
た小判形孔とを備え、前記ハブ本体外周面が均一応力に
よって加圧され、前記小判形孔に挿入された回転軸に小
判形孔内周面を圧接させる回転軸連結用フランジハブに
おいて、前記弦平面部中央部に、軸方向に延在し前記円
周面部の延長面を底面とする溝を形成し、前記溝の開口
幅Wを、前記一定半径Rの0.70倍乃至0.85倍にしたこと
を特徴とする回転軸連結用フランジハブ。
2. A cylindrical hub body, a flange fixed to the hub body, and a constant radius R from the center of rotation of the hub body.
And an oval hole which is formed by a pair of parallel chordal planes each of which is parallel to each other, and which is open at least at one end surface of the hub body, the outer peripheral surface of the hub body is pressed by a uniform stress, and the oval shape is formed. In a rotary shaft connecting flange hub that press-contacts an oval hole inner peripheral surface with a rotary shaft inserted in a shaped hole, in the central portion of the chordal plane portion, an extension surface of the circumferential surface portion that extends in the axial direction is a bottom surface. A flange hub for connecting a rotary shaft, wherein a groove is formed, and an opening width W of the groove is set to 0.70 to 0.85 times the constant radius R.
【請求項3】 円柱状のハブ本体と、このハブ本体に固
定されたフランジと、ハブ本体回転中心から一定半径の
円周面部及びそれぞれが平行な一対の弦平面部によって
形成され、前記ハブ本体の少なくとも一端面で開口した
小判形孔とを備え、前記ハブ本体外周面が均一応力によ
って加圧され、前記小判形孔に挿入された回転軸に小判
形孔内周面を圧接させる回転軸連結用フランジハブにお
いて、前記弦平面部中央位置と前記ハブ本体外周面との
間に、軸方向に延在する第1の円形孔を穿設し、かつ前
記弦平面部と前記ハブ本体外周面との間に、前記第1の
円形孔の両側方にそれぞれ配置され軸方向に延在する一
対の第2の円形孔を穿設し、しかも第1の円形孔の径を
前記第2の円形孔より大きくしたことを特徴とする回転
軸連結用フランジハブ。
3. A hub body having a cylindrical shape, a flange fixed to the hub body, a circumferential surface portion having a constant radius from the center of rotation of the hub body, and a pair of chordal plane portions parallel to each other. An oval hole opening at least at one end surface of the hub body, wherein the outer peripheral surface of the hub body is pressed by uniform stress and the inner peripheral surface of the oval hole is pressed against the rotary shaft inserted into the oval hole. In the flange hub for use, a first circular hole extending in the axial direction is bored between the central position of the chordal plane portion and the outer peripheral surface of the hub body, and the chordal plane portion and the outer peripheral surface of the hub body are formed. A pair of second circular holes, which are arranged on both sides of the first circular hole and extend in the axial direction, are formed between the first circular hole, and the diameter of the first circular hole is equal to that of the second circular hole. Flanges for connecting rotating shafts characterized by a larger size Boo.
【請求項4】 円柱状のハブ本体と、このハブ本体に固
定されたフランジと、ハブ本体回転中心から一定半径R
の円周面部及びそれぞれが平行な一対の弦平面部によっ
て形成され、前記ハブ本体の少なくとも一端面で開口し
た小判形孔とを備え、前記ハブ本体外周面が均一応力に
よって加圧され、前記小判形孔に挿入された回転軸に小
判形孔内周面を圧接させる回転軸連結用フランジハブに
おいて、前記弦平面部の両端部に、前記円周面部と連続
する曲率半径rの円形溝を形成し、前記曲率半径rを前
記一定半径Rの0.10倍乃至0.14倍にしたことを特徴とす
る回転軸連結用フランジハブ。
4. A cylindrical hub body, a flange fixed to the hub body, and a constant radius R from the center of rotation of the hub body.
And an oval hole which is formed by a pair of parallel chordal planes each of which is parallel to each other, and which is open at least at one end surface of the hub body, the outer peripheral surface of the hub body is pressed by a uniform stress, and the oval shape is formed. In a flange hub for connecting a rotary shaft in which an inner peripheral surface of an oval hole is pressed against a rotary shaft inserted in a shaped hole, circular grooves having a radius of curvature r continuous with the peripheral surface portion are formed at both ends of the chordal plane portion. The rotary hub connecting flange hub is characterized in that the radius of curvature r is 0.10 to 0.14 times the constant radius R.
JP6063239A 1994-03-31 1994-03-31 Flange hub for connecting rotating shafts Expired - Lifetime JP2694683B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP6063239A JP2694683B2 (en) 1994-03-31 1994-03-31 Flange hub for connecting rotating shafts

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP6063239A JP2694683B2 (en) 1994-03-31 1994-03-31 Flange hub for connecting rotating shafts

Publications (2)

Publication Number Publication Date
JPH07269579A true JPH07269579A (en) 1995-10-17
JP2694683B2 JP2694683B2 (en) 1997-12-24

Family

ID=13223479

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6063239A Expired - Lifetime JP2694683B2 (en) 1994-03-31 1994-03-31 Flange hub for connecting rotating shafts

Country Status (1)

Country Link
JP (1) JP2694683B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103912590A (en) * 2013-01-05 2014-07-09 北大方正集团有限公司 Transmission device and electronic device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3386779B2 (en) 2000-05-24 2003-03-17 株式会社中村自工 Hydraulic joint

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6414331U (en) * 1987-07-17 1989-01-25
JPS6417365U (en) * 1987-07-16 1989-01-27

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6417365U (en) * 1987-07-16 1989-01-27
JPS6414331U (en) * 1987-07-17 1989-01-25

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103912590A (en) * 2013-01-05 2014-07-09 北大方正集团有限公司 Transmission device and electronic device

Also Published As

Publication number Publication date
JP2694683B2 (en) 1997-12-24

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