JPH0577888B2 - - Google Patents
Info
- Publication number
- JPH0577888B2 JPH0577888B2 JP59146097A JP14609784A JPH0577888B2 JP H0577888 B2 JPH0577888 B2 JP H0577888B2 JP 59146097 A JP59146097 A JP 59146097A JP 14609784 A JP14609784 A JP 14609784A JP H0577888 B2 JPH0577888 B2 JP H0577888B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- spring
- piston
- flexible shaft
- flange
- 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.)
- Expired - Lifetime
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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
-
- 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
- F16D3/64—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 comprising elastic elements arranged between substantially-radial walls of both coupling parts
- F16D3/66—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 comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being metallic, e.g. in the form of coils
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Springs (AREA)
- Braking Arrangements (AREA)
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は大きな制動力を備えたたわみ軸継手
に関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial Field of Application) This invention relates to a flexible shaft coupling with a large braking force.
（従来の技術）
比隔的大きな制動力（振動減衰力）を持つたた
わみ軸継手としてゴム式たわみ軸継手がある。と
ころで、最近さらに大きな制動力を備えたたわみ
軸継手が要求されている。たとえば、最近の舶用
デイーゼルエンジンは燃料節約のため、気筒数を
少なくし、ストロークを大きくしたため、大きな
ねじり振動が生じやすい。(Prior Art) A rubber-type flexible shaft joint is a flexible shaft joint that has a relatively large damping force (vibration damping force). Incidentally, recently there has been a demand for flexible shaft joints with even greater braking force. For example, recent marine diesel engines have fewer cylinders and larger strokes to save fuel, which tends to cause large torsional vibrations.
（発明が解決しようとする問題点）
しかし、従来の上記ゴム式たわみ軸継手ではこ
のような大きなねじり振動を十分に減衰すること
ができず、緩衝作用も小さかつた。また、従来の
ゴム式たわみ軸継手は外径が大きく、広い取付面
積を要するという問題もあつた。(Problems to be Solved by the Invention) However, the conventional rubber type flexible shaft joint described above cannot sufficiently damp such large torsional vibrations, and its buffering effect is also small. Furthermore, conventional rubber flexible shaft joints have a large outer diameter and require a large installation area.
そこで、この発明は大きな制動力および緩衝作
用を備えるとともに、比隔的小型のたわみ軸継手
を提供しようとするものである。 SUMMARY OF THE INVENTION Therefore, the present invention aims to provide a flexible shaft joint that has a large braking force and a damping effect, and is relatively small in size.
（発明の構成）
この発明のたわみ軸継手は、それぞれ伝動軸が
取り付けられ、かつ一端にフランジを有する一対
のハブ、前記フランジに円周方向に間隔をおきピ
ンを介してピン回りに回転自在に取り付けられた
支持体、および支持体の円周方向に向かう二つの
面にそれぞれ固定されたばね受座を備えている。
前記ハブはフランジが向かい合い、かつ支持体が
円周方向に交互に並ぶようにして配置され、隣り
合う支持体のばね受座間にコイルばねが挿入され
ている。そして、相対する前記ばね受座の一方に
接続されたシリンダおよび他方のばね受座に取り
付けられたピストンからなる油圧ダンパがコイル
ばねの内側に設けている。前記シリンダは内側の
シリンダにピストンが挿入された２重シリンダよ
りなつている。そして、内側のシリンダと外側の
シリンダとを連絡する流路に、オリフイスが設け
られている。(Structure of the Invention) The flexible shaft joint of the present invention includes a pair of hubs each having a transmission shaft attached thereto and a flange at one end, and a hub having a flange spaced apart from the flange in the circumferential direction and rotatable around the pin via a pin. It includes an attached support and spring seats fixed respectively to two circumferential surfaces of the support.
The hub is arranged such that the flanges face each other and the supports are arranged alternately in the circumferential direction, and a coil spring is inserted between the spring seats of adjacent supports. A hydraulic damper comprising a cylinder connected to one of the opposing spring seats and a piston attached to the other spring seat is provided inside the coil spring. The cylinder consists of a double cylinder with a piston inserted into the inner cylinder. An orifice is provided in the flow path that communicates the inner cylinder and the outer cylinder.
また、本発明のもう一つのたわみ軸継手では、
上記のように構成された軸継手において、相対す
る前記ばね受座の少なくとも一方に自在継手を介
して前記油圧ダンパが接続されている。 Moreover, in another flexible shaft joint of the present invention,
In the shaft joint configured as described above, the hydraulic damper is connected to at least one of the opposing spring seats via a universal joint.
（作用）
上記のように構成されたたわみ軸継手におい
て、トルクは一方のハブから他方のハブへピン、
支持体、ばね受座、およびコイルばねを介して伝
達される。(Function) In the flexible shaft joint configured as described above, torque is transferred from one hub to the other hub by the pin,
It is transmitted through the support, the spring seat, and the coil spring.
前記ハブのフランジに対し支持体がピン周りを
回転すること、およびハブ、支持体、ピン、ピス
トン、シリンダなどの相互間の隙間により許容さ
れる範囲内でこれら部材が相対変位することによ
つて、軸心の狂いは吸収される。自在継手を備え
た軸継手では、軸心の狂い応じてばね受座に対し
油圧ダンパが傾くので、より大きな軸心の狂いを
調節することができる。 By rotation of the support body around the pin with respect to the flange of the hub, and relative displacement of these members within the range permitted by the mutual clearance between the hub, the support body, the pin, the piston, the cylinder, etc. , the deviation of the axis is absorbed. In a shaft joint equipped with a universal joint, the hydraulic damper tilts with respect to the spring seat according to the misalignment of the shaft center, so it is possible to adjust for larger misalignments of the shaft center.
伝動系のねじり振動は油圧ダンパによつて減衰
される。また、伝動系の衝撃はコイルばねの弾性
変形および油圧ダンパのダツシユポツト作用によ
つて緩和される。 Torsional vibrations in the transmission system are damped by a hydraulic damper. Further, the impact on the transmission system is alleviated by the elastic deformation of the coil spring and the dart pot action of the hydraulic damper.
（実施例）
第１図および第２図はこの発明の実施例を示し
ている。(Embodiment) FIGS. 1 and 2 show an embodiment of the present invention.
これら図面に示すように、たわみ軸継手は一対
のハブ１，５を備えている。各ハブ１，５の一端
にはフランジ２，６が設けられており、伝動軸
（図示しない）を取り付けるためのキー溝３が切
られている。 As shown in these drawings, the flexible shaft joint includes a pair of hubs 1 and 5. A flange 2, 6 is provided at one end of each hub 1, 5, and a keyway 3 is cut therein for attaching a transmission shaft (not shown).
前記フランジ２，６には円周方向に間隔をおい
てたわみ軸継手の軸線方向に突出するようにして
ピン７，９がナツト８，１０により固定されてい
る。このピン７，９を介してフランジ２，６に複
数の支持体１３，１７がピン７，９軸周りに回転
自在に取り付けられている。この実施例では各フ
ランジ２、６にそれぞれ四つの支持体１３，１７
が取り付けられている。なお、ピン７，９と支持
体１３，１７との摺動面にはピン７，９に切られ
た環状溝１４，１８を介して潤滑用のグリースが
供給される。 Pins 7 and 9 are fixed to the flanges 2 and 6 by nuts 8 and 10 at intervals in the circumferential direction and project in the axial direction of the flexible joint. A plurality of supports 13 and 17 are attached to the flanges 2 and 6 via the pins 7 and 9 so as to be rotatable around the axes of the pins 7 and 9. In this embodiment, each flange 2, 6 has four supports 13, 17, respectively.
is installed. Note that lubricating grease is supplied to the sliding surfaces of the pins 7, 9 and the supports 13, 17 through annular grooves 14, 18 cut in the pins 7, 9.
支持体１３，１７は円周方向に向かう二つの面
が設けられており、ここにばね受座２１，２５が
ボルト２２，２６により固定されている。 The supports 13, 17 are provided with two surfaces facing in the circumferential direction, to which spring seats 21, 25 are fixed by bolts 22, 26.
前記ハブ１，５はフランジ２，６が向かい合
い、かつ支持体１３，１７が円周方向に交互に並
ぶようにして配置される。そして、隣り合う支持
体１３，１７のばね受座２１，２５間にコイルば
ね２９が挿入される。 The hubs 1 and 5 are arranged such that the flanges 2 and 6 face each other and the supports 13 and 17 are arranged alternately in the circumferential direction. Then, the coil spring 29 is inserted between the spring seats 21 and 25 of the adjacent supports 13 and 17.
第３図は上記隣り合う支持体１３，１７間の構
造を詳細に示している。 FIG. 3 shows the structure between the adjacent supports 13 and 17 in detail.
相対する前記ばね受座２１，２５の一方に玉型
自在継手３１を介して二重シリンダ４２が接続さ
れている。玉型自在継手３１は第４図に示すよう
にばね受座２１、に固着された軸受台３２にピン
３３が支持されており、このピン３３に球体３４
が回転自在に取り付けられている。この球体３４
に球面座３５が摺動自在にはめ合つている。球面
座３５は保持金具３６を介してシリンダ−ヘツド
４６に連結されている。 A double cylinder 42 is connected to one of the opposing spring seats 21 and 25 via a globe-shaped universal joint 31. As shown in FIG. 4, the ball-shaped universal joint 31 has a pin 33 supported by a bearing stand 32 fixed to the spring seat 21, and a ball 34 attached to the pin 33.
is rotatably attached. This sphere 34
A spherical seat 35 is slidably fitted therein. The spherical seat 35 is connected to a cylinder head 46 via a retainer 36.
シリンダ−ヘツド４６からは他方のばね受座２
５に向かつて内シリンダ４３と外シリンダ４４と
からなる二重シリンダ４２が延びている。二重シ
リンダ４２の先端はカバー４８で閉じられてい
る。カバー４８には内シリンダ４３と外シリンダ
４４とを連結する連通孔４９が設けられており、
この連通孔４９の途中にオリフイス５１が設けら
れている。 From the cylinder head 46, the other spring seat 2
5, a double cylinder 42 consisting of an inner cylinder 43 and an outer cylinder 44 extends. The tip of the double cylinder 42 is closed with a cover 48. The cover 48 is provided with a communication hole 49 that connects the inner cylinder 43 and the outer cylinder 44.
An orifice 51 is provided in the middle of this communication hole 49.
他方のばね受座２５は上記二重シリンダ４２に
向かつて突出する円筒状のガイド部２７を備えて
いる。このガイド部材２７に上記二重シリンダ４
２が摺動自在にはめ合つている。また、ばね受座
２５と前記支持体１７との間に支持部５４が挟ま
れており、ばね受座２５にボルト５５により固定
されている。この支持板５４に前記カバー４８を
摺動自在に貫通するピストンロツド５８がナツト
５６により固着されている。ピストンロツド５８
の先端に内シリンダ４３にはめ合うピストン５９
が取り付けられている。カバー４８およびピスト
ン５９にはそれぞれシール用のＯリング５２，６
０がはめられている。 The other spring seat 25 is provided with a cylindrical guide portion 27 that projects toward the double cylinder 42 . This guide member 27 is connected to the double cylinder 4.
2 are slidably fitted together. Further, a support portion 54 is sandwiched between the spring seat 25 and the support body 17, and is fixed to the spring seat 25 with a bolt 55. A piston rod 58 that slidably passes through the cover 48 is fixed to the support plate 54 by a nut 56. piston rod 58
A piston 59 that fits into the inner cylinder 43 at the tip of the
is installed. O-rings 52 and 6 for sealing are attached to the cover 48 and the piston 59, respectively.
0 is inserted.
上記二重シリンダ４２には作動油が封入されて
おり、二重シリンダ４２とピストン５９とにより
油圧ダンパ４１が構成されている。 The double cylinder 42 is filled with hydraulic oil, and the double cylinder 42 and the piston 59 constitute a hydraulic damper 41.
上記のように構成されたたわみ軸継手におい
て、トルクは一方のハブ１からピン７、支持体１
３およびばね受座２１を介してコイルばね２９お
よび油圧ダンパ４１に伝達される。コイルばね２
９はトルクの大きさに応じて圧縮され、同時に油
圧ダンパ４１にも力が作用してピストン５９が内
シリンダ４３に押し込まれる。そして、トルクは
ばね力およびピストン抵抗力として他方のばね受
座２５、支持体１７およびピン９を介してハブ５
に伝達される。このとき、コイルばね２９の圧縮
およびピストン５９の変位によつて、ハブ１，５
は互いに円周方向に相対的に変位する。しかし、
支持体１３，１７のピン７，９周りの回転および
玉型自在継手３１の運動によつて、無理な力が加
わることなく外シリンダ４４はガイド部材２７に
案内される。 In the flexible shaft joint configured as described above, torque is transmitted from one hub 1 to the pin 7 to the support 1.
3 and the spring seat 21 to the coil spring 29 and the hydraulic damper 41. coil spring 2
9 is compressed according to the magnitude of the torque, and at the same time, force acts on the hydraulic damper 41, pushing the piston 59 into the inner cylinder 43. Then, the torque is transmitted to the hub 5 via the other spring seat 25, the support 17 and the pin 9 as spring force and piston resistance force.
is transmitted to. At this time, due to the compression of the coil spring 29 and the displacement of the piston 59, the hubs 1 and 5
are circumferentially displaced relative to each other. but,
Due to the rotation of the supports 13, 17 around the pins 7, 9 and the movement of the ball-shaped universal joint 31, the outer cylinder 44 is guided to the guide member 27 without applying undue force.
軸心の狂いは玉型自在継手３１の球体３４と球
面座３５とが軸心の狂いに応じて相互に摺動して
調節される。 The misalignment of the axis is adjusted by the spherical body 34 of the ball-shaped universal joint 31 and the spherical seat 35 sliding against each other according to the misalignment of the axis.
伝動系のねじり振動は油圧ダンパ４１によつて
減衰される。また、伝動系の衝撃はコイルばね２
９の弾性変形および油圧ダンパ４１のダツシユポ
ツト作用によつて緩和される。なお、油圧ダンパ
４１の復元作用はコイルばね２９によつて行なわ
れる。 Torsional vibrations of the transmission system are damped by the hydraulic damper 41. In addition, the shock in the transmission system is handled by the coil spring 2.
9 and the dumppot action of the hydraulic damper 41. Note that the restoring action of the hydraulic damper 41 is performed by the coil spring 29.
この発明は上記実施例に限られるものではな
い。たとえば、調節すべき軸心の狂いが小さい場
合には、玉型自在継手３１を省略してもよく、逆
に大きい場合には玉型自在継手３１を両側のばね
受座のそれぞれに連結してもよい。また、玉型自
在継手３１は他の形式のもの、たとえばこま形自
在継手を用いてもよい。 This invention is not limited to the above embodiments. For example, if the misalignment of the shaft center to be adjusted is small, the globe-shaped universal joint 31 may be omitted; if it is large, the globe-shaped universal joint 31 may be connected to each of the spring seats on both sides. Good too. Further, the globe-shaped universal joint 31 may be of another type, such as a top-shaped universal joint.
（発明の効果）
この発明のたわみ軸継手では前述のように相対
する前記ばね受座２１，２５の一方にシリンダ４
２を接続し、他方にピストン５９を取り付けて油
圧ダンパ４１を構成している。したがつて、従来
のゴム式たわみ軸継手に比べ大きな制動力を有す
る。なお、オリフイスの径により制動力つまり伝
達系ねじり振動の減衰率を調節することができ
る。(Effects of the Invention) In the flexible shaft joint of the present invention, as described above, the cylinder 4 is attached to one of the opposing spring seats 21 and 25.
2 are connected to each other, and a piston 59 is attached to the other end to form a hydraulic damper 41. Therefore, it has greater braking force than conventional rubber flexible shaft joints. Note that the damping force, that is, the damping rate of the torsional vibration of the transmission system can be adjusted by adjusting the diameter of the orifice.
また、油圧ダンパ４１はばね受座２１，２５の
間かつコイルばね２９の内側に設けられているの
で、大きな制動力および緩衝作用を有するたわみ
軸継手をコンパクトに設計することができる。 Further, since the hydraulic damper 41 is provided between the spring seats 21 and 25 and inside the coil spring 29, it is possible to design a flexible shaft joint having a large damping force and a buffering effect in a compact manner.
さらに、自在継手を備えた軸継手では、軸心の
狂い応じてばね受座に対し油圧ダンパが傾くの
で、より大きな軸心の狂いを調節することができ
る。 Furthermore, in a shaft joint equipped with a universal joint, the hydraulic damper tilts with respect to the spring seat according to the misalignment of the shaft center, so that a larger misalignment of the shaft center can be adjusted.
第１図はこの発明の一実施例を示すもので、た
わみ軸継手の断面図、第２図は第１図の−線
に沿う断面図、第３図は油圧ダンパの詳細を示す
断面図、および第４図は第３図の−線に沿う
断面図である。
１，５…ハブ、２，６…ハブフランジ、７，９
…ピン、１３，１７…支持体、２１，２５…ばね
受座、２９…コイルばね、３１…玉型自在継手、
４１…油圧ダンパ、４２…二重シリンダ、５１…
オリフイス、５９…ピストン。
FIG. 1 shows an embodiment of the present invention, in which a sectional view of a flexible shaft joint, FIG. 2 a sectional view taken along the line - in FIG. 1, and FIG. 3 a sectional view showing details of a hydraulic damper. and FIG. 4 is a sectional view taken along the - line in FIG. 3. 1, 5...Hub, 2, 6...Hub flange, 7, 9
... Pin, 13, 17... Support body, 21, 25... Spring seat, 29... Coil spring, 31... Globe-shaped universal joint,
41...Hydraulic damper, 42...Double cylinder, 51...
Orifice, 59...piston.
Claims (1)
フランジを有する一対のハブ、各フランジに円周
方向に間隔をおきピンを介してピン回りに回転自
在に取り付けられた支持体、および支持体の円周
方向に向かう二つの面にそれぞれ固定されたばね
受座を備えており、前記ハブはフランジが向かい
合い、かつ支持体が円周方向に交互に並ぶように
して配置され、隣り合う支持体のばね受座間にコ
イルばねが挿入されたたわみ軸継手において、相
対する前記ばね受座の一方に接続されたシリンダ
および他方のばね受座に取り付けられたピストン
からなる油圧ダンパがコイルばねの内側に設けら
れており、前記シリンダが内側のシリンダにピス
トンが挿入された２重シリンダよりなり、内側の
シリンダと外側のシリンダとを連絡する流路にオ
リフイスが設けられていることを特徴とするたわ
み軸継手。 ２ それぞれ伝動軸が取り付けられ、かつ一端に
フランジを有する一対のハブ、各フランジに円周
方向に間隔をおきピンを介してピン回りに回転自
在に取り付けられた支持体、および支持体の円周
方向に向かう二つの面にそれぞれ固定されたばね
受座を備えており、前記ハブはフランジが向かい
合い、かつ支持体が円周方向に交互に並ぶように
して配置され、隣り合う支持体のばね受座間にコ
イルばねが挿入されたたわみ軸継手において、相
対する前記ばね受座の一方に接続されたシリンダ
および他方のばね受座に取り付けられたピストン
からなる油圧ダンパがコイルばねの内側に設けら
れており、前記シリンダが内側のシリンダにピス
トンが挿入された２重シリンダよりなり、内側の
シリンダと外側のシリンダとを連絡する流路にオ
リフイスが設けられていること、ならびに相対す
る前記ばね受座の少なくとも一方に自在継手を介
して前記油圧ダンパが接続されていることを特徴
とするたわみ軸継手。[Scope of Claims] 1. A pair of hubs each having a transmission shaft attached thereto and having a flange at one end; a support mounted to each flange at intervals in the circumferential direction and rotatable around the pin via a pin; and a spring seat fixed to each of the two circumferential surfaces of the support, and the hub is arranged such that the flanges face each other and the supports are arranged alternately in the circumferential direction, In a flexible shaft joint in which a coil spring is inserted between spring seats of a support body, a hydraulic damper consisting of a cylinder connected to one of the opposing spring seats and a piston attached to the other spring seat is used to prevent the coil spring from moving. The cylinder is provided on the inside, and the cylinder is made up of a double cylinder in which a piston is inserted into the inside cylinder, and an orifice is provided in the flow path that communicates the inside cylinder and the outside cylinder. Flexible shaft coupling. 2. A pair of hubs each having a transmission shaft attached and a flange at one end, a support body attached to each flange at intervals in the circumferential direction and rotatable around the pin via a pin, and a circumference of the support body. The hub is provided with spring seats fixed to two surfaces facing the direction, and the flanges of the hub face each other, and the supports are arranged alternately in the circumferential direction, and the spring seats of adjacent supports are In a flexible shaft joint in which a coil spring is inserted, a hydraulic damper consisting of a cylinder connected to one of the opposing spring seats and a piston attached to the other spring seat is provided inside the coil spring. , the cylinder is composed of a double cylinder in which a piston is inserted into the inner cylinder, and an orifice is provided in a flow path communicating the inner cylinder and the outer cylinder, and at least one of the opposing spring seats is provided. A flexible shaft joint, characterized in that the hydraulic damper is connected to one end via a universal joint.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14609784A JPS6124825A (en) | 1984-07-16 | 1984-07-16 | Flexible shaft coupling |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14609784A JPS6124825A (en) | 1984-07-16 | 1984-07-16 | Flexible shaft coupling |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6124825A JPS6124825A (en) | 1986-02-03 |
| JPH0577888B2 true JPH0577888B2 (en) | 1993-10-27 |
Family
ID=15400068
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14609784A Granted JPS6124825A (en) | 1984-07-16 | 1984-07-16 | Flexible shaft coupling |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6124825A (en) |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6018853B2 (en) * | 1976-12-31 | 1985-05-13 | 川崎重工業株式会社 | shaft coupling |
| JPS596424A (en) * | 1982-06-30 | 1984-01-13 | Fuji Electric Co Ltd | Control method of exciting current in magnetic bearing |
-
1984
- 1984-07-16 JP JP14609784A patent/JPS6124825A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6124825A (en) | 1986-02-03 |
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