JP2010017744A - Holding structure of angular bearing for hollow motor - Google Patents
Holding structure of angular bearing for hollow motor Download PDFInfo
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- JP2010017744A JP2010017744A JP2008181281A JP2008181281A JP2010017744A JP 2010017744 A JP2010017744 A JP 2010017744A JP 2008181281 A JP2008181281 A JP 2008181281A JP 2008181281 A JP2008181281 A JP 2008181281A JP 2010017744 A JP2010017744 A JP 2010017744A
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- angular bearing
- angular
- motor
- bearing
- restraining member
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Resistance Welding (AREA)
Abstract
Description
本発明は、モ―タの回転軸に中空貫通孔を形成し、該モ―タによって駆動され該モ―タの前記中空貫通孔内に引き込まれる部位を有する加圧軸を備え、前記回転軸がアンギュラベアリングによって回転自在に支持された、溶接ガンにおけるアンギュラベアリングの抑え構造に関するものである。 The present invention includes a pressurizing shaft that has a hollow through hole formed in a rotating shaft of a motor and has a portion that is driven by the motor and is drawn into the hollow through hole of the motor. The present invention relates to a structure for restraining an angular bearing in a welding gun, which is rotatably supported by an angular bearing.
従来、モ―タの回転軸に中空貫通孔を形成し、該モ―タによって駆動され該モ―タの前記中空貫通孔内に引き込まれる部位を有する加圧軸を備えた溶接ガンであって、前記回転軸がその前方部位に配置されたアンギュラベアリングで回転自在に支持され、前記加圧軸が軸受で前後進自在に支持され、前記アンギュラベアリングの外輪が、モ―タの前端面にねじ止めされたアンギュラベアリング抑え部材でモ―タの軸線方向に抑えられたアンギュラベアリングの抑え構造がある（例えば特許文献１参照）。 2. Description of the Related Art Conventionally, there is provided a welding gun having a pressure shaft that has a hollow through hole formed in a rotating shaft of a motor and has a portion that is driven by the motor and is drawn into the hollow through hole of the motor. The rotary shaft is rotatably supported by an angular bearing disposed at the front portion thereof, the pressure shaft is supported by the bearing so as to be able to move forward and backward, and the outer ring of the angular bearing is screwed onto the front end surface of the motor. There is a structure for restraining an angular bearing that is restrained in the axial direction of the motor by a stopped angular bearing restraining member (see, for example, Patent Document 1).
ところで、上記従来例の中空モ―タ用アンギュラベアリングの抑え構造では、仮に，アンギュラベアリング抑え部材がアンギュラベアリングの外輪に当接していなくて両者間に隙間があるような場合には、加圧軸の加圧や開動作時に加圧軸がその軸方向にがた付いたり傾いたりして、加圧軸の軸受は加圧軸を正確に支持できずに損傷することがあり、また、アンギュラベアリング抑え部材をアンギュラベアリングの外輪に強く押し込むような場合には、アンギュラベアリング抑え部材によってアンギュラベアリングの外輪を変形させボ―ルをつぶして回転軸の回転の動きを固くするか、ねじの締付力でアンギュラベアリング抑え部材の座板側が変形して傾き、該アンギュラベアリング抑え部材と抑え部材のねじ止め取付面との間に隙間が生じ、アンギュラベアリング抑え部材が不安定に傾くようになり、アンギュラベアリング抑え部材の座板に一体的に固定された加圧軸の軸受は、やはり加圧軸を正確に支持できず、加圧軸をこじったり、加圧軸の中心がずれたりするおそれがある。 By the way, in the conventional structure for holding the angular bearing for a hollow motor, if the angular bearing holding member is not in contact with the outer ring of the angular bearing and there is a gap between them, the pressure shaft The pressurization shaft may rattle or tilt in the axial direction during the pressurization or opening operation, and the bearing of the pressurization shaft may not be able to support the pressurization shaft correctly and may be damaged. When the restraining member is pushed strongly into the outer ring of the angular bearing, the outer ring of the angular bearing is deformed by the angular bearing restraining member and the ball is crushed to stabilize the rotational movement of the rotating shaft, or the screw tightening force As a result, the seat plate side of the angular bearing restraining member is deformed and tilted, and a gap is formed between the angular bearing restraining member and the screw mounting surface of the restraining member. Since the angular bearing restraining member becomes unstable and tilted, the bearing of the pressure shaft that is integrally fixed to the seat plate of the angular bearing restraining member still cannot accurately support the pressure shaft, and does not squeeze the pressure shaft. Or the center of the pressure shaft may be displaced.
本発明は、従来の技術の有するこのような問題点に鑑みてなされたものであり、その目的とするところは、アンギュラベアリング抑え部材が常にアンギュラベアリングの外輪に当接してアンギュラベアリングの移動を抑制し、かつアンギュラベアリング抑え部材の傾くのも防止されて適正な予圧をアンギュラベアリングにかけることができるので、アンギュラベアリングは無理なく正確に作動され、しかも加圧軸もスム―ズに動作される中空モ―タ用アンギュラベアリングの抑え構造を提供しようとするものである。 The present invention has been made in view of such problems of the prior art, and the object of the present invention is to suppress the angular bearing movement by the angular bearing restraining member always contacting the outer ring of the angular bearing. In addition, since the angular bearing restraining member can be prevented from tilting and an appropriate preload can be applied to the angular bearing, the angular bearing can be operated without difficulty and the pressure shaft can be operated smoothly. An attempt is made to provide a holding structure for angular bearings for motors.
上記目的を達成するために、本発明における中空モ―タ用アンギュラベアリングの抑え構造は、モ―タの回転軸に中空貫通孔を形成し、該モ―タによって駆動され該モ―タの前記中空貫通孔内に引き込まれる部位を有する加圧軸を備えた溶接ガンであって、前記回転軸がその前方部位に配置されたアンギュラベアリングで回転自在に支持され、前記加圧軸が軸受で前後進自在に支持され、前記アンギュラベアリングの外輪が、モ―タの前端面にねじ止めされたアンギュラベアリング抑え部材でモ―タの軸線方向に抑えられたアンギュラベアリングの抑え構造において、前記アンギュラベアリング抑え部材にばね機能を持たせると共にアンギュラベアリング抑え部材と加圧軸の軸受とを一体に形成したことを特徴とするものである。 In order to achieve the above object, the hollow motor angular bearing holding structure according to the present invention is formed by forming a hollow through hole in the rotating shaft of the motor and driven by the motor. A welding gun having a pressure shaft having a portion that is pulled into a hollow through-hole, wherein the rotary shaft is rotatably supported by an angular bearing disposed at a front portion thereof, and the pressure shaft is front and rear by a bearing. In the angular bearing restraining structure in which the outer ring of the angular bearing is supported in a freely movable manner and is restrained in the axial direction of the motor by an angular bearing restraining member screwed to the front end surface of the motor. The member is provided with a spring function, and the angular bearing restraining member and the bearing of the pressure shaft are integrally formed.
また、前記アンギュラベアリング抑え部材の外周に放射状の切り込みを形成して該アンギュラベアリング抑え部材にばね機能を持たせたことを特徴とするものである。 Further, a radial cut is formed on the outer periphery of the angular bearing restraining member so that the angular bearing restraining member has a spring function.
また、前記アンギュラベアリング抑え部材の先端側とアンギュラベアリングの外輪側との間に板ばねを介在させてアンギュラベアリング抑え部材にばね機能を持たせたことを特徴とするものである。 Further, the angular bearing restraining member is provided with a spring function by interposing a leaf spring between the distal end side of the angular bearing restraining member and the outer ring side of the angular bearing.
本発明によれば、モ―タの回転軸に中空貫通孔を形成し、該モ―タによって駆動され該モ―タの前記中空貫通孔内に引き込まれる部位を有する加圧軸を備えた溶接ガンであって、前記回転軸がその前方部位に配置されたアンギュラベアリングで回転自在に支持され、前記加圧軸が軸受で前後進自在に支持され、前記アンギュラベアリングの外輪が、モ―タの前端面にねじ止めされたアンギュラベアリング抑え部材でモ―タの軸線方向に抑えられたアンギュラベアリングの抑え構造において、前記アンギュラベアリング抑え部材にばね機能を持たせるようにすると共にアンギュラベアリング抑え部材と加圧軸の軸受とを一体に形成したので、アンギュラベアリング抑え部材が常にアンギュラベアリングの外輪に当接してアンギュラベアリングの移動を抑制し、かつアンギュラベアリング抑え部材の傾くのも防止されて適正な予圧をアンギュラベアリングにかけることができることから、アンギュラベアリングは無理なく正確に作動され、しかも加圧装置全体の長さを短く維持しながら加圧軸もスム―ズに動作される中空モ―タ用アンギュラベアリングの抑え構造となる。 According to the present invention, a welding is provided with a pressure shaft that has a hollow through hole formed in the rotating shaft of the motor and has a portion driven by the motor and drawn into the hollow through hole of the motor. A gun, wherein the rotary shaft is rotatably supported by an angular bearing disposed at a front portion thereof, the pressure shaft is supported by a bearing so as to be movable forward and backward, and an outer ring of the angular bearing is connected to a motor. In the angular bearing restraining structure restrained in the axial direction of the motor by the angular bearing restraining member screwed to the front end surface, the angular bearing restraining member is provided with a spring function and is added to the angular bearing restraining member. Since the bearing of the pressure shaft is integrally formed, the angular bearing restraining member always contacts the outer ring of the angular bearing and The angular bearing can be operated accurately and reasonably, and the overall length of the pressurizing device can be shortened. It becomes a restraining structure of the angular bearing for the hollow motor where the pressure shaft is smoothly operated while maintaining it.
また、前記アンギュラベアリング抑え部材の外周に放射状の切り込みを形成して該アンギュラベアリング抑え部材にばね機能を持たせた場合には、アンギュラベアリングに対するアンギュラベアリング抑え部材のばね動作も有効に作用し得るものとなる。 Further, when a radial cut is formed on the outer periphery of the angular bearing restraining member so that the angular bearing restraining member has a spring function, the spring operation of the angular bearing restraining member with respect to the angular bearing can also act effectively. It becomes.
また、前記アンギュラベアリング抑え部材の先端側とアンギュラベアリングの外輪側との間に板ばねを介在させてアンギュラベアリング抑え部材にばね機能を持たせた場合にも、アンギュラベアリングに対するアンギュラベアリング抑え部材のばね動作も有効に作用し得るものとなる。 In addition, even when a leaf spring is interposed between the tip end side of the angular bearing restraining member and the outer ring side of the angular bearing, and the angular bearing restraining member has a spring function, the spring of the angular bearing restraining member with respect to the angular bearing The operation can also work effectively.
モ―タの回転軸に中空貫通孔を形成し、該モ―タによって駆動され該モ―タの前記中空貫通孔内に引き込まれる部位を有する加圧軸を備えた溶接ガンであって、前記回転軸がその前方部位に配置されたアンギュラベアリングで回転自在に支持され、前記加圧軸が軸受で前後進自在に支持され、前記アンギュラベアリングの外輪が、モ―タの前端面にねじ止めされたアンギュラベアリング抑え部材でモ―タの軸線方向に抑えられたアンギュラベアリングの抑え構造において、前記アンギュラベアリング抑え部材にばね機能を持たせると共にアンギュラベアリング抑え部材と加圧軸の軸受とを一体に形成した中空モ―タ用アンギュラベアリングの抑え構造。 A welding gun comprising a pressurizing shaft having a hollow through hole formed in a rotating shaft of a motor and having a portion driven by the motor and drawn into the hollow through hole of the motor, The rotating shaft is rotatably supported by an angular bearing disposed in the front part thereof, the pressure shaft is supported by the bearing so as to be able to move forward and backward, and the outer ring of the angular bearing is screwed to the front end surface of the motor. In the angular bearing restraining structure that is restrained in the motor axial direction by the angular bearing restraining member, the angular bearing restraining member has a spring function and the angular bearing restraining member and the pressure shaft bearing are integrally formed. Structure for angular bearings for hollow motors.
図１乃至図３を参照してこの発明の実施例について説明をする。
図において、１はサ―ボモ―タであり、該サ―ボモ―タ１は、その外殻２に固定された固定子巻線３とその内周に配置された回転子磁極４及び該回転子磁極４が固定された回転軸５とからなり、該回転軸５には中空貫通孔６が形成されており、該回転軸５は軸受７ａ，７ｂによってサ―ボモ―タ１の前記外殻２の前方部位および後方部位に軸支されている。そして、前記軸受７ａはアンギュラベアリングに構成されている。
An embodiment of the present invention will be described with reference to FIGS.
In the figure, reference numeral 1 denotes a servo motor. The servo motor 1 includes a stator winding 3 fixed to an outer shell 2 thereof, a rotor magnetic pole 4 arranged on the inner periphery thereof, and the rotation The rotating shaft 5 is formed with a hollow through hole 6 which is fixed to the outer shell of the servo motor 1 by bearings 7a and 7b. 2 is supported by the front part and the rear part. The bearing 7a is an angular bearing.
前記回転軸５の後部外周に中空ブレ―キ本体８が取り付けられている。 A hollow brake body 8 is attached to the outer periphery of the rear portion of the rotary shaft 5.
また、モ―タ１の回転軸５の後方端部位にはねじ軸固定部材９が例えばねじ込み１０の手段によって固着されている。 A screw shaft fixing member 9 is fixed to the rear end portion of the rotating shaft 5 of the motor 1 by means of, for example, a screw 10.
前記ねじ軸固定部材９にはボ―ルねじ軸１１がクサビ等の固定手段１２で固定されている。そして、前記ボ―ルねじ軸１１は後述する加圧軸に設けた孔内に向けて延びている。 A ball screw shaft 11 is fixed to the screw shaft fixing member 9 by fixing means 12 such as a wedge. The ball screw shaft 11 extends into a hole provided in a pressure shaft described later.
１３は加圧軸であり、該加圧軸１３の軸線方向中心部には前記ボ―ルねじ軸１１を収納する孔１４が形成されており、該加圧軸１３の後部側には、前記ボ―ルねじ軸１１のねじと間接的にボ―ルを介して噛み合うねじを備えたボ―ルナット１５が螺合部で螺着によって固定されて略同径状に設けられている。そしてボ―ルナット１５は少なくとも前記中空ブレ―キ本体８の直下近傍まで引き込まれるようになっている。また、該加圧軸１３の前部はサ―ボモ―タ１から延出可能とされ、その前端部には、Ｃ型ガンにおいてはワ―クを加圧溶接する電極（図示せず）が、Ｘ型ガンにおいてはガンア―ムと接続する接続部材（図示せず）が、接続されるようになっている。なお、前記ボ―ルねじ軸１１を通常のねじ軸とした場合にボ―ルナット１５を通常のナットとして両者を噛み合わせてもよく、また前記加圧軸１３とナット１５とは螺着手段により一体化することなく一体成形によって構成してもよい。 Reference numeral 13 denotes a pressure shaft, and a hole 14 for accommodating the ball screw shaft 11 is formed at the axial center of the pressure shaft 13. A ball nut 15 provided with a screw that meshes with the screw of the ball screw shaft 11 indirectly via the ball is fixed by screwing at a screwing portion and is provided with substantially the same diameter. The ball nut 15 is pulled into at least the vicinity immediately below the hollow brake body 8. Further, the front portion of the pressure shaft 13 can be extended from the servo motor 1, and an electrode (not shown) for pressure welding the workpiece in the C-type gun is provided at the front end portion. In the X-type gun, a connection member (not shown) connected to the gun arm is connected. When the ball screw shaft 11 is a normal screw shaft, the ball nut 15 may be a normal nut and the two may be engaged with each other. The pressure shaft 13 and the nut 15 may be screwed together. You may comprise by integral molding, without integrating.
また、加圧軸１３の外径は前記中空状の回転軸５の中空貫通孔６の内径より小さくなっており、該加圧軸１３の軸心に関して直角方向の断面の両側には切欠き面が形成されていてＣガンに使用する際の該加圧軸１３の回り止め機構としている。 Further, the outer diameter of the pressure shaft 13 is smaller than the inner diameter of the hollow through hole 6 of the hollow rotary shaft 5, and a notch surface is formed on both sides of the cross section perpendicular to the axial center of the pressure shaft 13. Is used as a detent mechanism for the pressure shaft 13 when used for the C gun.
１６はサ―ボモ―タ１の前壁１７の前端面にねじ１８によって固定されたアンギュラベアリング抑え部材であり、該アンギュラベアリング抑え部材１６は前記アンギュラベアリング７ａの外輪に向けて円筒状の抑え部１９を備え、該抑え部１９の外周にはその全周にわたって放射状の切り込み２０が形成されており、また、切り込み２０とアンギュラベアリング７ａとの間の抑え部材１９の外周の複数箇所（図２では６箇所）にスリット２１，２１…が形成されて該抑え部材１９を分割体に構成しており、前記切り込み２０によりアンギュラベアリング抑え部材１６にばね機能を持たせるようになっている。 Reference numeral 16 denotes an angular bearing restraining member fixed to the front end surface of the front wall 17 of the servo motor 1 with a screw 18, and the angular bearing restraining member 16 is a cylindrical restraining portion facing the outer ring of the angular bearing 7a. 19, a radial cut 20 is formed on the outer periphery of the holding portion 19, and the outer periphery of the holding member 19 between the cut 20 and the angular bearing 7 a (in FIG. 2). Slits 21, 21,... Are formed at six locations to constitute the restraining member 19 in a divided body, and the angular bearing restraining member 16 is provided with a spring function by the cut 20.
また、前記アンギュラベアリング抑え部材１６には前記抑え部１９と反対側に延びる軸受２２が一体に形成されて（図１参照）ストロ―ク長い加圧軸１３の軸受として、或は抑え部１９と同方向に延びる軸受２２が一体に形成されて（図３参照）ストロ―ク短い加圧軸１３に対する軸受となっている。 Further, the angular bearing restraining member 16 is integrally formed with a bearing 22 extending on the opposite side to the restraining portion 19 (see FIG. 1) as a bearing for the long pressure shaft 13 or with the restraining portion 19. A bearing 22 extending in the same direction is integrally formed (see FIG. 3), and serves as a bearing for the pressure shaft 13 having a short stroke.
以上のような構成において、図１或は図３の状態では加圧軸１３がサ―ボモ―タ１の回転軸５内に最も引き込まれた状態にある。この状態から加圧軸１３をサ―ボモ―タ１内から延出させて加圧動作を行わせるには、サ―ボモ―タ１の固定子巻線３に例えば三相電流を供給すると、回転子磁極４が励磁され回転軸５が回転し、該回転軸５に固定されたねじ軸固定部材９を介してボ―ルネジ軸１１が回転を行い、該ボ―ルねじ軸１１の回転に伴ってボ―ルナット１５はボ―ルねじ軸１１に沿って移動するので、ボ―ルナット１５と一体化された加圧軸１３は軸受２２によりガイドされながら回転軸５の内周面内を移動し、加圧軸１３はサ―ボモ―タ１外に順次延出され、加圧装置全体の長さを短く維持しながらサ―ボモ―タ１からの延出量が増大されて加圧動作を行う。 In the configuration as described above, in the state of FIG. 1 or FIG. 3, the pressure shaft 13 is in the most retracted state within the rotating shaft 5 of the servo motor 1. In order to perform the pressurizing operation by extending the pressurizing shaft 13 from the servo motor 1 from this state, for example, by supplying a three-phase current to the stator winding 3 of the servo motor 1, The rotor magnetic pole 4 is excited to rotate the rotating shaft 5, and the ball screw shaft 11 rotates through the screw shaft fixing member 9 fixed to the rotating shaft 5, so that the ball screw shaft 11 rotates. Accordingly, since the ball nut 15 moves along the ball screw shaft 11, the pressure shaft 13 integrated with the ball nut 15 moves within the inner peripheral surface of the rotating shaft 5 while being guided by the bearing 22. The pressurizing shaft 13 is sequentially extended to the outside of the servomotor 1, and the amount of extension from the servomotor 1 is increased while maintaining the entire length of the pressurizing device to be pressurized. I do.
そして、加圧軸１３の前後進に伴ってアンギュラベアリング７ａには回転軸５の軸線方向に圧力が発生し、それによってアンギュラベアリング７ａの外輪にはアンギュラベアリング抑え部材１６に向け或は反対側に向けて移動しようとする力が働くが、該アンギュラベアリング抑え部材１６にはばね機能を持たせてあるので、アンギュラベアリング抑え部材１６の抑え部１９は常時，アンギュラベアリング７ａの外輪に当接した状態にある。 As the pressure shaft 13 moves back and forth, pressure is generated in the angular bearing 7a in the axial direction of the rotary shaft 5, whereby the outer ring of the angular bearing 7a faces the angular bearing restraining member 16 or on the opposite side. The angular bearing restraining member 16 has a spring function, but the restraining portion 19 of the angular bearing restraining member 16 is always in contact with the outer ring of the angular bearing 7a. It is in.
したがって、アンギュラベアリング７ａの外輪が加圧軸１３の開放動作時にアンギュラベアリング抑え部材１６の抑え部１９から離れようとする力が働いた場合には、抑え部１９の追従により、加圧軸１３の動作時に加圧軸１３がその軸方向にがた付いたり傾いたりして加圧軸１３の軸受２２は加圧軸１３を正確に支持できずに損傷するようなことはなく、また、アンギュラベアリング７ａの外輪が加圧軸１３の加圧動作時にアンギュラベアリング抑え部材１６の抑え部１９を押圧するような力が働いた場合には、アンギュラベアリング抑え部材１６の抑え部１９におけるばね機能によって前記押圧力は吸収されて、アンギュラベアリング７ａの外輪を変形させボ―ルをつぶして回転軸５の回転の動きを固くするとか、アンギュラベアリング抑え部材１６の座板側が変形して傾くというようなことがなく、さらにアンギュラベアリング抑え部材１６の座板に一体に固定された加圧軸１３の軸受２２は、加圧軸１３を正確に支持し、加圧軸１３をこじったり、加圧軸１３の中心がずれたりすることもない。 Therefore, when a force is exerted on the outer ring of the angular bearing 7 a to move away from the restraining portion 19 of the angular bearing restraining member 16 during the opening operation of the pressing shaft 13, During operation, the pressure shaft 13 rattles or tilts in the axial direction, and the bearing 22 of the pressure shaft 13 does not support the pressure shaft 13 accurately and is not damaged. When a force that presses the restraining portion 19 of the angular bearing restraining member 16 during the pressurizing operation of the pressurizing shaft 13 is exerted on the outer ring 7a, the pushing function is achieved by the spring function of the restraining portion 19 of the angular bearing restraining member 16. When the pressure is absorbed, the outer ring of the angular bearing 7a is deformed and the ball is crushed to harden the rotational movement of the rotating shaft 5, or the angular bearing The bearing plate side of the pressure member 13 is not deformed and tilted, and the bearing 22 of the pressure shaft 13 integrally fixed to the seat plate of the angular bearing restraining member 16 accurately supports the pressure shaft 13. In addition, the pressing shaft 13 is not twisted and the center of the pressing shaft 13 is not shifted.
前記実施例１においては、アンギュラベアリング抑え部材１６にばね機能を持たせる具体例としてアンギュラベアリング抑え部材１６の抑え部１９の外周に放射状の切り込み２０を形成したものであったが、この実施例２においては、図４に示すようにアンギュラベアリング抑え部材１６にばね機能を持たせるのに、アンギュラベアリング抑え部材１６の抑え部１９の先端側とアンギュラベアリング７ａの外輪側との間に板ばね２３を介在させたものである。また、アンギュラベアリング抑え部材１６と一体に形成された加圧軸の軸受２２は、該アンギュラベアリング抑え部材１６の抑え部１９と反対側および同方向に延びている。そしてその余の構成は前記実施例１と実質的に同一であるのでその説明を省略する。 In the first embodiment, as a specific example in which the angular bearing restraining member 16 has a spring function, the radial notches 20 are formed on the outer periphery of the restraining portion 19 of the angular bearing restraining member 16. In FIG. 4, in order to give the angular bearing restraining member 16 a spring function, a leaf spring 23 is provided between the distal end side of the restraining portion 19 of the angular bearing restraining member 16 and the outer ring side of the angular bearing 7a. Intervened. Further, the pressure shaft bearing 22 formed integrally with the angular bearing restraining member 16 extends in the opposite direction and in the same direction as the restraining portion 19 of the angular bearing restraining member 16. Since the remaining configuration is substantially the same as that of the first embodiment, the description thereof is omitted.
このように、アンギュラベアリング抑え部材１６の先端側とアンギュラベアリング７ａの外輪側との間に板ばね２３を介在させた場合にも、アンギュラベアリング抑え部材１６の抑え部１９は板ばね２３を介して常時，アンギュラベアリング７ａの外輪に当接した状態にあり、アンギュラベアリング７ａの外輪がアンギュラベアリング抑え部材１６の抑え部１９から離れようとしても、板ばね２３の追従により、加圧軸１３の動作時に加圧軸１３がその軸方向にがた付いたり傾いたりして加圧軸１３の軸受２２は加圧軸１３を正確に支持できずに損傷するようなことはなく、また、アンギュラベアリング７ａの外輪がアンギュラベアリング抑え部材１６の抑え部１９を板ばね２３を介して押圧するようなときには、板ばね２３がアンギュラベアリング抑え部材１６の抑え部１９におけるばね機能を発揮し前記押圧力は吸収して、アンギュラベアリング７ａの外輪を変形させボ―ルをつぶして回転軸５の回転の動きを固くするとか、アンギュラベアリング抑え部材１６の座板側が変形して傾くというようなことがなく、さらにアンギュラベアリング抑え部材１６の座板に一体に固定された加圧軸１３の軸受２２は、加圧軸１３を正確に支持し、加圧軸１３をこじったり、加圧軸１３の中心がずれたりすることもない。 As described above, even when the leaf spring 23 is interposed between the distal end side of the angular bearing restraining member 16 and the outer ring side of the angular bearing 7 a, the restraining portion 19 of the angular bearing restraining member 16 is interposed via the leaf spring 23. Even if the outer ring of the angular bearing 7a is always in contact with the outer ring of the angular bearing 7a, and the outer ring of the angular bearing 7a tries to move away from the holding portion 19 of the angular bearing holding member 16, the follow-up of the leaf spring 23 causes the pressing shaft 13 to operate. The pressure shaft 13 does not rattle or tilt in the axial direction so that the bearing 22 of the pressure shaft 13 cannot support the pressure shaft 13 accurately and is not damaged, and the angular bearing 7a is not damaged. When the outer ring presses the restraining portion 19 of the angular bearing restraining member 16 via the leaf spring 23, the leaf spring 23 is A spring function is exerted in the restraining portion 19 of the ring restraining member 16 to absorb the pressing force, and the outer ring of the angular bearing 7a is deformed to crush the ball, thereby making the rotational movement of the rotating shaft 5 hard, or the angular bearing. The bearing plate 22 of the pressure shaft 13 that is integrally fixed to the seat plate of the angular bearing restraining member 16 supports the pressure shaft 13 accurately without the seat plate side of the restraining member 16 being deformed and tilted. In addition, the pressing shaft 13 is not twisted and the center of the pressing shaft 13 is not shifted.
１ モ―タ
５ 回転軸
６ 中空貫通孔
７ａ アンギュラベアリング
１３ 加圧軸
１６ アンギュラベアリング抑え部材
１８ ねじ
２０ 切り込み
２２ 軸受
２３ 板ばね
DESCRIPTION OF SYMBOLS 1 Motor 5 Rotating shaft 6 Hollow through-hole 7a Angular bearing 13 Pressurizing shaft 16 Angular bearing holding member 18 Screw 20 Notch 22 Bearing 23 Leaf spring
Claims (3)
2. The angular contact for a hollow motor according to claim 1, wherein a plate spring is interposed between the tip end side of the angular bearing restraining member and the outer ring side of the angular bearing so that the angular bearing restraining member has a spring function. Bearing holding structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008181281A JP2010017744A (en) | 2008-07-11 | 2008-07-11 | Holding structure of angular bearing for hollow motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008181281A JP2010017744A (en) | 2008-07-11 | 2008-07-11 | Holding structure of angular bearing for hollow motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2010017744A true JP2010017744A (en) | 2010-01-28 |
Family
ID=41703129
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2008181281A Pending JP2010017744A (en) | 2008-07-11 | 2008-07-11 | Holding structure of angular bearing for hollow motor |
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| Country | Link |
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| JP (1) | JP2010017744A (en) |
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| WO2011136013A1 (en) * | 2010-04-30 | 2011-11-03 | 本田技研工業株式会社 | Welding gun |
| CN102275036A (en) * | 2010-06-08 | 2011-12-14 | 小原株式会社 | Electric resistance welding device |
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| JP2003199369A (en) * | 2001-12-27 | 2003-07-11 | Canon Inc | Vibration wave drive unit |
| JP2004279859A (en) * | 2003-03-18 | 2004-10-07 | Canon Inc | Deflecting scanner |
| JP2008155234A (en) * | 2006-12-22 | 2008-07-10 | Obara Corp | Driving unit of welding equipment |
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| JPS60149525U (en) * | 1984-03-16 | 1985-10-04 | 株式会社安川電機 | Bearing support device for rotating electrical machines |
| JPH078911A (en) * | 1993-06-23 | 1995-01-13 | Canon Inc | Vibrator and ultrasonic motor |
| JP2003199369A (en) * | 2001-12-27 | 2003-07-11 | Canon Inc | Vibration wave drive unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2011136013A1 (en) * | 2010-04-30 | 2011-11-03 | 本田技研工業株式会社 | Welding gun |
| JP5588505B2 (en) * | 2010-04-30 | 2014-09-10 | 本田技研工業株式会社 | Welding gun |
| US9156106B2 (en) | 2010-04-30 | 2015-10-13 | Honda Motor Co., Ltd. | Welding gun |
| CN102275036A (en) * | 2010-06-08 | 2011-12-14 | 小原株式会社 | Electric resistance welding device |
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