JP3397609B2 - Vibration type driving device - Google Patents
Vibration type driving deviceInfo
- Publication number
- JP3397609B2 JP3397609B2 JP34856996A JP34856996A JP3397609B2 JP 3397609 B2 JP3397609 B2 JP 3397609B2 JP 34856996 A JP34856996 A JP 34856996A JP 34856996 A JP34856996 A JP 34856996A JP 3397609 B2 JP3397609 B2 JP 3397609B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- output shaft
- rolling
- pressure
- vibration type
- 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 - Fee Related
Links
Landscapes
- General Electrical Machinery Utilizing Piezoelectricity, Electrostriction Or Magnetostriction (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、振動体に移動体を
加圧接触させて駆動力を得る振動型駆動装置に関するも
のである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration type driving device for obtaining a driving force by bringing a moving body into pressure contact with a vibrating body.
【０００２】[0002]
【従来の技術】振動型駆動装置（振動型モータ）は、電
気−機械エネルギ変換素子を接合した弾性部材からなる
振動体に移動体を加圧接触させ、上記変換素子に交流電
圧を印加して振動体に進行性振動波を発生させることに
より、移動体を摩擦駆動するものである。2. Description of the Related Art A vibration type driving device (vibration type motor) applies a moving body to a vibrating body composed of an elastic member having an electro-mechanical energy conversion element bonded thereto under pressure, and applies an AC voltage to the conversion element. The moving body is frictionally driven by generating a progressive vibration wave in the vibrating body.
【０００３】図７には、従来の振動型モータを示してい
る。ベース１０１に固定されたリング状のステータ（振
動体）１０２、弾性体１２１の下面に、コネクタ１１０
およびフレキシブル基板１１１を通じて通電される電気
−機械エネルギ変換素子１２２を接合し、弾性体１２１
の上面に摩擦部材１２３を接着して構成されている。ロ
ータ（移動体）１０３の上面にはゴム板１０７を介して
加圧ばね１０６の外周部が取り付けられており、加圧ば
ね１０６の内周部は出力軸１０４に焼嵌めされたディス
ク１０５に取り付けられている。FIG. 7 shows a conventional vibration type motor. On the lower surface of the ring-shaped stator (vibration body) 102 and elastic body 121 fixed to the base 101, the connector 110
The electro-mechanical energy conversion element 122 that is energized through the flexible substrate 111 is joined to the elastic body 121.
The friction member 123 is bonded to the upper surface of the. The outer peripheral portion of the pressure spring 106 is attached to the upper surface of the rotor (moving body) 103 via the rubber plate 107, and the inner peripheral portion of the pressure spring 106 is attached to the disk 105 shrink-fitted to the output shaft 104. Has been.
【０００４】出力軸１０４は、ベース１０１に固定され
た外輪と、出力軸１０４の外周に嵌合した内輪とを有す
る一対のころがり軸受１８１，１８２によって回転自在
に支持される。ディスク１０５はころがり軸受１８２の
内輪に当接している。一方、ころがり軸受１８１の内輪
は、ロータ１０３をステータ１０２に適切な力で加圧接
触させるための加圧ばね１０６の変位量分だけ、ディス
ク１０５ところがり軸受１８２の内輪とともに出力軸１
０４をステータ１０２側へ押し込んだ状態で、出力軸１
０４の溝に装着したスナップリング１０９と係合してい
る。The output shaft 104 is rotatably supported by a pair of rolling bearings 181 and 182 having an outer ring fixed to the base 101 and an inner ring fitted to the outer periphery of the output shaft 104. The disk 105 is in contact with the inner ring of the rolling bearing 182. On the other hand, the inner ring of the rolling bearing 181 is, together with the inner ring of the disc 105 and the rolling bearing 182, the output shaft 1 by an amount of displacement of the pressure spring 106 for bringing the rotor 103 into pressure contact with the stator 102 with an appropriate force.
04 is pushed toward the stator 102 side, and the output shaft 1
It is engaged with the snap ring 109 mounted in the groove 04.
【０００５】これにより、図６に示すように、軸受１８
２では、ディスク１０５によって内輪に加圧バネ１０６
の加圧力と同方向の予圧がかけられて軸受１８２内の径
方向がたが排除される。一方、軸受１８１では、スナッ
プリング１０９によって内輪に加圧バネ１０６の加圧力
と反対方向の予圧力がかけられて軸受１８２内の径方向
がたが排除される。こうして、各軸受１８１，１８２の
径方向がたがなくなることにより、出力軸１０４の径方
向のぶれも抑えられる。As a result, as shown in FIG. 6, the bearing 18
In 2, the disk 105 presses the inner surface of the pressure spring 106.
A preload is applied in the same direction as the pressure force of the bearing 182 to eliminate the radial play in the bearing 182. On the other hand, in the bearing 181, the snap ring 109 applies a preload to the inner ring in a direction opposite to the pressure of the pressure spring 106, so that the radial play in the bearing 182 is eliminated. In this way, the radial deviation of the bearings 181 and 182 is eliminated, so that radial deviation of the output shaft 104 is also suppressed.
【０００６】ここで、加圧ばねの加圧反力をＦ、軸受１
８１の予圧力をＰ１、軸受１８２の予圧力をＰ２とする
と、これらの３つの力には、
Ｆ＝Ｐ１−Ｐ２
という関係が成立する。[0006] Here, the pressure reaction force of the pressure spring is F, and the bearing 1
Assuming that the preload of 81 is P1 and the preload of the bearing 182 is P2, the relationship of F = P1-P2 is established among these three forces.
【０００７】このことから分かるように、軸受１８１は
加圧反力と軸受１８２の予圧力の和を予圧力として受け
るため、その予圧力は軸受１８２の予圧力に比較して極
端に大きくなる。As can be seen from the above, the bearing 181 receives the sum of the pressure reaction force and the preload of the bearing 182 as the preload, so that the preload becomes extremely larger than the preload of the bearing 182.
【０００８】[0008]
【発明が解決しようとする課題】通常、軸受の疲れ寿命
は、軸受荷重の３乗に反比例する。このため大きな予圧
力を受ける軸受１８１の疲れ寿命は軸受１８２に比べて
極端に短い。さらに、振動型モータは低速度での使用が
多く、軸受の転動体と軌道面との間に油膜が形成されに
くいため、軸受の転動体荷重を通常よりも小さくとる必
要がある。Generally, the fatigue life of a bearing is inversely proportional to the cube of the bearing load. Therefore, the fatigue life of the bearing 181 that receives a large preload is extremely shorter than that of the bearing 182. Further, since the vibration type motor is often used at a low speed and an oil film is not easily formed between the rolling element of the bearing and the raceway surface, it is necessary to make the rolling element load of the bearing smaller than usual.
【０００９】モータが発生し得るトルクは、ステータと
ロータ間の最大摩擦力に依存する。この摩擦力はロー
タ、ステータ間の摩擦係数と、加圧力によって決定され
るから、最大トルクを大きくする場合には、加圧力を増
すことが有効である。The torque that can be generated by the motor depends on the maximum frictional force between the stator and the rotor. Since this frictional force is determined by the friction coefficient between the rotor and the stator and the pressing force, it is effective to increase the pressing force when increasing the maximum torque.
【００１０】しかしながら従来のモータでは、加圧力を
すべて軸受１８１が負担するため、軸受寿命を短くせず
に加圧力を増すにはさらに定格荷重の大きい軸受を使用
しなければならず、軸受が大きくなり、しかも高価とな
る。However, in the conventional motor, since the bearing 181 bears all the pressure force, in order to increase the pressure force without shortening the life of the bearing, it is necessary to use a bearing having a larger rated load, and the bearing is large. And is expensive.
【００１１】そこで、本願発明は、軸受寿命ひいては駆
動装置としての寿命を延ばすとともに、定格荷重の小さ
な軸受を使用して安価で省スペースを図れる振動型駆動
装置を提供することを目的としている。Therefore, an object of the present invention is to provide a vibration type drive device which extends the life of the bearing and thus the life of the drive device, and uses a bearing having a small rated load, which is inexpensive and saves space.
【００１２】[0012]
【課題を解決するための手段】第１の発明は、請求項１
に記載のように、振動が励起される振動体と、この振動
体に接触して駆動される振動体と、この移動体と出力軸
とを連結するとともに、前記移動体と前記振動体とを加
圧接触させる加圧部材と、前記出力軸を回転自在に支持
する複数の軸受部材と、前記加圧部材による加圧反力を
前記出力軸を介して前記複数の軸受部材に配分するため
のバネ力を備えた部材を有することを特徴とする振動型
駆動装置とするものである。第２の発明は、請求項２に
記載のように、上記第１の発明で、前記加圧反力を、前
記複数の軸受部材の内部予圧力として用いることを特徴
とする。 The first aspect of the present invention is the first aspect of the present invention.
As described in (1), the vibrating body in which vibration is excited, the vibrating body driven by contacting the vibrating body, the moving body and the output shaft are connected, and the moving body and the vibrating body are connected to each other. A pressure member to be brought into pressure contact, a plurality of bearing members that rotatably support the output shaft, and a pressure reaction force generated by the pressure member to be distributed to the plurality of bearing members via the output shaft.
The Rukoto to have a member with a spring force is to the vibration type driving apparatus according to claim. The second invention is in claim 2.
As described, in the first invention, the pressurizing reaction force, before
Characterized by being used as an internal preload for multiple bearing members
And
【００１３】すなわち、複数の軸受部材に同一方向の与
圧力がかかるように構成して加圧部材による加圧反力を
複数の軸受部材に負担させるだけでなく、バネ力を備え
た部材により前記複数の軸受部材に対して加圧反力が適
切な割合で配分するように調整することが可能となり、
前記複数の軸受部材の軸受部材の寿命を略等しくするこ
とができ、振動型駆動装置の長寿命化を実現できるよう
にしている。That is, a plurality of bearing members are applied in the same direction.
It is configured to apply pressure so that the pressure reaction force from the pressure member
Equipped with a spring force as well as bearing on multiple bearing members
Appropriate pressure reaction force against the multiple bearing members
It becomes possible to adjust so that it will be distributed at a painful rate,
The life of the bearing members of the plurality of bearing members is made approximately equal.
This makes it possible to achieve a longer service life of the vibration type drive device.
【００１４】第３の発明は、請求項３に記載のように、
振動が励起される振動体と、この振動体に接触して駆動
される振動体と、この移動体と出力軸とを連結するとと
もに、前記移動体と前記振動体とを加圧接触させる加圧
部材と、前記出力軸を回転自在に支持する複数の軸受部
材とを有し、前記加圧反力を、前記複数の軸受部材に対
し、これら各軸受部材の定格荷重の比に応じて分担させ
ることを特徴とする振動型駆動装置とするものである。
第４の発明は、請求項４に記載のように、上記第１から
第３のいずれかの発明で、前記複数の軸受部材が、ころ
がり軸受であることを特徴とする。 第５の発明は、請求
項５に記載のように、上記第４の発明で、前記加圧反力
を、前記複数のころがり軸受に対し、これら各ころがり
軸受の軌動面と転動体との接触面圧が等しくなるように
分担させることを特徴とする。 第３、第５の発明では、
各軸受部材がほぼ等しい寿命となるような条件にするこ
とができ、振動型駆動装置の長寿命化を図ることができ
る。According to a third aspect of the present invention, as described in claim 3,
The vibrating body where the vibration is excited and the vibrating body come into contact and drive
When the vibration body and the moving body and the output shaft are connected,
In addition, pressurization for pressing the moving body and the vibrating body into contact with each other.
Member and a plurality of bearings for rotatably supporting the output shaft
And a timber, said pressurizing reaction force, said the plurality of bearing members, is shared according to the ratio of the rated load of the bearing members
A vibration type drive device characterized by the above .
According to a fourth aspect of the present invention, as described in claim 4,
In any one of the third invention, the plurality of bearing members are rollers.
It is characterized by being a roller bearing. The fifth invention is a request
As described in Item 5, in the fourth invention, the pressure reaction force is applied.
For each of these rolling bearings.
Ensure that the contact surface pressure between the rolling surface of the bearing and the rolling element is equal
It is characterized by sharing. In the third and fifth inventions,
Conditions can be set so that the bearing members have almost the same life, and the life of the vibration type drive device can be extended.
It
【００１５】第６の発明は、請求項６に記載のように、
上記第４又は第５の発明で、前記複数のころがり軸受の
各内輪と前記出力軸とが、前記出力軸への前記加圧反力
の作用方向に一体的に移動可能に結合していることを特
徴とする。 第７の発明は、請求項７に記載のように、上
記第４から第６のいずれかの発明で、前記複数のころが
り軸受が、前記加圧手段を挟んで前記出力軸の軸方向両
側に配置されていることを特徴とする。 According to a sixth aspect of the present invention, as described in claim 6,
In the fourth or fifth aspect of the invention, each inner ring of the plurality of rolling bearings and the output shaft are integrally movably coupled in a direction in which the pressure reaction force acts on the output shaft. Special
To collect. According to a seventh aspect of the invention, as described in claim 7,
From serial fourth sixth any one of the said plurality of rolling bearings, characterized in that disposed on both axial sides of the output shaft across the pressurizing means.
【００１６】第８の発明は、請求項８に記載のように、
上記第１又は第２の発明で、前記複数の軸受部材が複数
のころがり軸受であり、前記複数のころがり軸受のうち
所定のころがり軸受の内輪と前記出力軸とが前記出力軸
への前記加圧反力の作用方向に一体的に移動可能に結合
しており、前記所定のころがり軸受の内輪と他のころが
り軸受の内輪との間に前記バネ力を備えた部材が配設さ
れていることを特徴とする。 第９の発明は、請求項９に
記載のように、上記第８の発明で、前記バネ力を備えた
部材のバネの変位を、前記各ころがり軸受に、前記加圧
反力をこれら各ころがり軸受の定格荷重の比に応じて分
担させるよう設定したことを特徴とする。 第１０の発明
は、請求項１０に記載のように、上記第８の発明で、前
記バネ力を備えた部材のバネの変位を、前記各ころがり
軸受の軌動面と転動体との接触面圧が等しくなるよう設
定したことを特徴とする。 An eighth invention is, as described in claim 8,
In the first or second invention, the plurality of bearing members are plural.
Of a rolling bearing, integrally movably coupled with the inner ring of a predetermined rolling bearing and the output shaft in the direction of action of the pressurizing reaction force to the output shaft of the plurality of rolling bearings
Member of arranged with the spring force between the to and inner ring of the inner ring and the other rolling bearing of the predetermined rolling bearing
It is characterized by being. A ninth invention is based on claim 9.
As described above, in the eighth invention, the spring force is provided.
The displacement of the spring member, said each rolling bearing, the pressure reaction force, characterized in that set so as to be shared according to the ratio of the rated load of the rolling bearings. 10th invention
According to the tenth aspect of the present invention,
The displacement of the spring of the member having the spring force is set so that the contact surface pressure between the rolling surface of each rolling bearing and the rolling element becomes equal .
【００１７】第１１の発明は、請求項１１に記載のよう
に、上記第４又は第５の発明で、前記複数のころがり軸
受の転動体が、前記出力軸の外周に形成された軌動溝部
を転動することを特徴とする。 An eleventh invention is as described in claim 11.
, In the invention of the fourth or fifth rolling elements of said plurality of rolling bearings, characterized in that rolling軌動groove formed on the outer periphery of the output shaft.
【００１８】[0018]
（第１実施形態）図１には、本願発明の第１実施形態で
ある振動型駆動装置を示している。ベース１に固定され
たリング状の金属製ステータ（振動体）２は、弾性体２
１の下面に、コネクタ１０およびフレキシブル基板１１
を通じて通電される電気−機械エネルギ変換素子２２を
接合し、弾性体２１の上面に摩擦部材２３を接着して構
成されている。ロータ（移動体）３の上面にはゴム板７
を介して加圧ばね６の外周部が取り付けられており、加
圧ばね６の内周部は出力軸４に焼嵌めされたディスク５
に取り付けられている。(First Embodiment) FIG. 1 shows a vibration type driving apparatus according to a first embodiment of the present invention. The ring-shaped metal stator (vibrating body) 2 fixed to the base 1 is made of an elastic body 2.
On the lower surface of 1, the connector 10 and the flexible substrate 11
The electro-mechanical energy conversion element 22 that is energized through is joined, and the friction member 23 is bonded to the upper surface of the elastic body 21. A rubber plate 7 is provided on the upper surface of the rotor (moving body) 3.
The outer peripheral portion of the pressure spring 6 is attached through the inner peripheral portion of the pressure spring 6, and the inner peripheral portion of the pressure spring 6 is shrink-fitted onto the output shaft 4.
Is attached to.
【００１９】出力軸４は、ベース１に固定された外輪
と、出力軸４の外周に嵌合した内輪とを有する一対の深
溝玉軸受（ころがり軸受）８１，８２によって回転自在
に支持される。The output shaft 4 is rotatably supported by a pair of deep groove ball bearings (rolling bearings) 81, 82 having an outer ring fixed to the base 1 and an inner ring fitted to the outer periphery of the output shaft 4.
【００２０】各軸受８１，８２の内輪は、ロータ３をス
テータ２に適切な力で加圧接触させるための加圧ばね６
の変位量分だけ、ディスク５と出力軸４とをステータ２
側へ押し込んだ状態で、出力軸４における各軸受８１，
８２の下側に形成された溝に装着されたスナップリング
９と係合している。これにより、加圧ばね６から出力軸
４への加圧反力の作用方向に対して、出力軸４と各軸受
８１，８２の内輪とが一体的に移動可能となる。なお、
ディスク５は軸受８２の内輪および外輪から離れてい
る。The inner rings of the bearings 81 and 82 are pressure springs 6 for pressing the rotor 3 against the stator 2 with appropriate force.
The disk 5 and the output shaft 4 by the amount of displacement of the stator 2
The bearings 81 on the output shaft 4 while being pushed to the side,
It engages with a snap ring 9 mounted in a groove formed on the underside of 82. As a result, the output shaft 4 and the inner rings of the bearings 81 and 82 can move integrally with each other in the acting direction of the pressure reaction force from the pressure spring 6 to the output shaft 4. In addition,
The disk 5 is separated from the inner ring and the outer ring of the bearing 82.
【００２１】また、軸受８２の内輪とこれに係合するス
ナップリング９との間には、ウェーブワッシャ１２が介
在している。このウェーブワッシャ１２の変形量は、上
記加圧反力を軸受８１と軸受８２の定格荷重の比に比例
配分した場合の反力成分が軸受８２の内輪に作用する変
形量に設定されている。A wave washer 12 is interposed between the inner ring of the bearing 82 and the snap ring 9 engaging with the inner ring. The amount of deformation of the wave washer 12 is set to the amount of deformation of the reaction force component acting on the inner ring of the bearing 82 when the pressure reaction force is proportionally distributed to the ratio of the rated loads of the bearing 81 and the bearing 82.
【００２２】このように各軸受８１，８２の内輪に出力
軸４およびスナップリング９を介して加圧反力を作用さ
せることにより、それぞれが負担する反力成分が軸受８
１，８２内の予圧力として用いられることになる。こう
して、各軸受８１，８２の径方向がたがなくなることに
より、出力軸４の径方向のぶれも抑えられる。As described above, by applying a pressure reaction force to the inner races of the bearings 81 and 82 via the output shaft 4 and the snap ring 9, the reaction force component respectively bears the bearing component 8.
It will be used as a preload within 1,82. In this way, the radial deviation of the bearings 81 and 82 is eliminated, so that radial deviation of the output shaft 4 is also suppressed.
【００２３】ここで、各軸受８１，８２の予圧力の関係
について図５を用いて詳しく説明する。図５は、各軸受
８１，８２を模式的に示しており、ロータ３、ステータ
２、加圧ばね６は省略してある。Here, the relationship between the preloads of the bearings 81 and 82 will be described in detail with reference to FIG. FIG. 5 schematically shows the bearings 81 and 82, and the rotor 3, the stator 2 and the pressure spring 6 are omitted.
【００２４】加圧反力Ｆは、出力軸４に対し上向きの力
として作用しており、この加圧反力Ｆは２つの軸受８
１，８２によって負担され、各軸受８１，８２の予圧力
はそれぞれＰ１、Ｐ２となっている。The pressure reaction force F acts on the output shaft 4 as an upward force, and the pressure reaction force F is applied to the two bearings 8.
1, 82, and the preloads of the bearings 81 and 82 are P1 and P2, respectively.
【００２５】ここで、予圧力Ｐ２は、加圧時の各軸受８
１，８２の内輪の軸方向の移動量の差と外輪の相対位置
と出力軸４に施した２つのスナップリング９，９の間隔
で決まるウェーブワッシャ１２の変形量に対するバネ力
に等しい。Here, the preload P2 is the bearing 8 at the time of pressurization.
It is equal to the spring force with respect to the deformation amount of the wave washer 12 which is determined by the difference in the amount of axial movement of the inner ring 1, 82, the relative position of the outer ring, and the distance between the two snap rings 9, 9 provided on the output shaft 4.
【００２６】各軸受８１，８２の予圧力Ｐ１，Ｐ２の方
向が等しく、加圧反力Ｆと同じ方向であるので、軸受８
１の予圧力Ｐ１は加圧反力の大きさから軸受８２の予圧
力Ｐ２を差し引いた値となる。結果として、加圧反力Ｆ
を２つの軸受８１，８２に予圧力として分散させること
ができる。Since the preloads P1 and P2 of the bearings 81 and 82 are in the same direction and are in the same direction as the pressure reaction force F, the bearing 8
The preload P1 of 1 is a value obtained by subtracting the preload P2 of the bearing 82 from the magnitude of the pressure reaction force. As a result, the pressure reaction force F
Can be distributed as a preload on the two bearings 81, 82.
【００２７】ところで、玉軸受の疲れ寿命は、次式で表
わされることが経験的に知られている。By the way, it is empirically known that the fatigue life of a ball bearing is expressed by the following equation.
【００２８】Ｌ∝（Ｃ／Ｐ）3
ただし、Ｌ；寿命、Ｃ；軸受の基本動定格荷重、Ｐ；軸
受荷重
複数の軸受を用いる場合、最短の軸受寿命が、駆動装置
の寿命となるため、各軸受がほぼ等しい寿命となるよう
な条件にすることで、駆動装置の長寿命化が図れる。こ
のためには、上の式から各軸受８１，８２の定格荷重Ｃ
と軸受荷重Ｐの比が等しくなるように加圧反力Ｆを各軸
受８１，８２の定格荷重の比に比例配分して各軸受荷重
（予圧力）とすればよい。L∝ (C / P) 3 However, L: life, C: basic dynamic load rating of bearing, P: bearing load When using a plurality of bearings, the shortest bearing life is the life of the drive unit. By making the conditions such that the bearings have substantially the same life, the life of the drive device can be extended. For this purpose, the rated load C of each bearing 81, 82 is calculated from the above equation.
The pressure reaction force F may be proportionally distributed to the ratio of the rated loads of the bearings 81 and 82 so that the ratio of the bearing load P and the bearing load P becomes equal to each bearing load (preload).
【００２９】本実施形態では、加圧反力Ｆを比例配分し
た軸受荷重を発生させるためのウェーブワッシャ１２の
変形量を与えるようにスナップリング９間の間隔および
軸受外輪の位置を定めればよい。In the present embodiment, the spacing between the snap rings 9 and the position of the bearing outer ring may be determined so as to give the deformation amount of the wave washer 12 for generating the bearing load in which the pressure reaction force F is proportionally distributed. .
【００３０】また、軸受が静止しているときやきわめて
低速回転している場合に、軸受の軌道面と転動体の接触
面圧が大きいと軌道面や転動体に永久変形を生じ、使用
できなくなるおそれがある。If the contact surface pressure between the bearing raceway and the rolling elements is large when the bearing is stationary or rotating at an extremely low speed, the raceway and rolling elements are permanently deformed and cannot be used. There is a risk.
【００３１】このため、軸受の基本静低格荷重Ｃ0 と軸
受への静荷重Ｐ0 の比
ｆ＝Ｃ0 ／Ｐ0
で表わされる安全係数ｆを等しくするうように、加圧反
力を各軸受の定格荷重の比に比例配分して各軸受荷重と
すればよい。Therefore, the pressurizing reaction force is set so that the safety factor f represented by the ratio f = C 0 / P 0 between the basic static load rating C 0 of the bearing and the static load P 0 on the bearing becomes equal. Each bearing load may be proportionally distributed to the ratio of the rated load of each bearing.
【００３２】また厳密には、軌道面と転動体の接触面圧
は軸受荷重に対して比例関係にはないから、軌道面と転
動体の接触面圧が各軸受で等しくなるように軸受荷重を
配分してもよい。Strictly speaking, since the contact surface pressure between the raceway surface and the rolling element is not in proportion to the bearing load, the bearing load is set so that the contact surface pressure between the raceway surface and the rolling element is equal in each bearing. May be distributed.
【００３３】（第２実施形態）図２は、本発明の第２実
施形態である振動型駆動装置を示している。ベース１に
固定されたリング状の金属製ステータ（振動体）２は、
弾性体２１の下面に、コネクタ１０およびフレキシブル
基板１１を通じて通電される電気−機械エネルギ変換素
子２２を接合し、弾性体２１の上面に摩擦部材２３を接
着して構成されている。ロータ（移動体）３の上面には
ゴム板７を介して加圧ばね６の外周部が取り付けられて
おり、加圧ばね６の内周部は出力軸４に焼嵌めされたデ
ィスク５に取り付けられている。(Second Embodiment) FIG. 2 shows a vibration type driving apparatus according to a second embodiment of the present invention. The ring-shaped metal stator (vibration body) 2 fixed to the base 1 is
An electro-mechanical energy conversion element 22 energized through the connector 10 and the flexible substrate 11 is joined to the lower surface of the elastic body 21, and a friction member 23 is bonded to the upper surface of the elastic body 21. The outer peripheral portion of the pressure spring 6 is attached to the upper surface of the rotor (moving body) 3 via the rubber plate 7, and the inner peripheral portion of the pressure spring 6 is attached to the disk 5 shrink-fitted to the output shaft 4. Has been.
【００３４】出力軸４は、ベース１における加圧ばね６
およびディスク５を挟んだ位置に固定された外輪と、出
力軸４の外周に嵌合した内輪とを有する一対の深溝玉軸
受（ころがり軸受）８１，８２によって回転自在に支持
される。The output shaft 4 includes a pressure spring 6 on the base 1.
And, it is rotatably supported by a pair of deep groove ball bearings (rolling bearings) 81, 82 having an outer ring fixed at a position sandwiching the disk 5 and an inner ring fitted to the outer periphery of the output shaft 4.
【００３５】軸受８１の内輪は、ロータ３をステータ２
に適切な力で加圧接触させるための加圧ばね６の変位量
分だけ、ディスク５と出力軸４とをステータ２側へ押し
込んだ状態で、出力軸４における軸受８１の下側に形成
された溝に装着されたスナップリング９と係合してい
る。また、軸受８２の内輪は、ウェーブワッシャ１２を
挟んでディスク５の上面に当接している。これにより、
加圧ばね６から出力軸４への加圧反力の作用方向に対し
て、出力軸４と各軸受８１，８２の内輪とが一体的に移
動可能となる。The inner ring of the bearing 81 connects the rotor 3 to the stator 2
Is formed below the bearing 81 on the output shaft 4 in a state where the disk 5 and the output shaft 4 are pushed toward the stator 2 by an amount of displacement of the pressure spring 6 for making pressure contact with an appropriate force. Engaged with a snap ring 9 mounted in the groove. Further, the inner ring of the bearing 82 is in contact with the upper surface of the disk 5 with the wave washer 12 interposed therebetween. This allows
The output shaft 4 and the inner rings of the bearings 81 and 82 can move integrally with each other in the acting direction of the pressure reaction force from the pressure spring 6 to the output shaft 4.
【００３６】ウェーブワッシャ１２の変形量は、上記加
圧反力を軸受８１と軸受８２の定格荷重の比に比例配分
した場合の反力成分が軸受８２の内輪に作用する変形量
に設定されている。The amount of deformation of the wave washer 12 is set to the amount of deformation of the reaction force component acting on the inner ring of the bearing 82 when the pressure reaction force is proportionally distributed to the ratio of the rated loads of the bearing 81 and the bearing 82. There is.
【００３７】本実施形態においても、２つの軸受８１，
８２に、加圧反力を定格荷重の比に比例配分した同方向
の予圧力を与えることによって、加圧反力を軸受８１，
８２が均等に負担することになり、駆動装置の長寿命化
が実現できる。Also in this embodiment, the two bearings 81,
By applying a preload in the same direction in which the pressure reaction force is proportionally distributed to the ratio of the rated load to 82, the pressure reaction force is applied to the bearings 81,
Since 82 is evenly burdened, the life of the drive device can be extended.
【００３８】また、２つの軸受８１，８２を加圧ばね６
およびディスク５（つまりはロータ３、ステータ２）を
挟む位置に設けたことによって、軸受間距離を大きくで
き、出力軸４のラジアル荷重に対する剛性を大きくでき
る。Further, the two bearings 81 and 82 are attached to the pressure spring 6
Further, by providing the disk 5 (that is, the rotor 3 and the stator 2) so as to sandwich it, the distance between the bearings can be increased, and the rigidity of the output shaft 4 against the radial load can be increased.
【００３９】（第３実施形態）図３には、本発明の第３
実施形態である振動型駆動装置を示している。ベース１
に固定されたリング状の金属製ステータ（振動体）２
は、弾性体２１の下面に、コネクタ１０およびフレキシ
ブル基板１１を通じて通電される電気−機械エネルギ変
換素子２２を接合し、弾性体２１の上面に摩擦部材２３
を接着して構成されている。ロータ（移動体）３の上面
にはゴム板７を介して加圧ばね６の外周部が取り付けら
れており、加圧ばね６の内周部は出力軸４に焼嵌めされ
たディスク５に取り付けられている。(Third Embodiment) FIG. 3 shows the third embodiment of the present invention.
1 illustrates a vibration type drive device according to an embodiment. Base 1
Ring-shaped metal stator (vibrating body) fixed to the
Joins the electro-mechanical energy conversion element 22 energized through the connector 10 and the flexible substrate 11 to the lower surface of the elastic body 21, and the friction member 23 on the upper surface of the elastic body 21.
It is configured by bonding. The outer peripheral portion of the pressure spring 6 is attached to the upper surface of the rotor (moving body) 3 via the rubber plate 7, and the inner peripheral portion of the pressure spring 6 is attached to the disk 5 shrink-fitted to the output shaft 4. Has been.
【００４０】出力軸４は、ベース１に固定された外輪
と、出力軸４の外周に嵌合した内輪とを有する一対の深
溝玉軸受（ころがり軸受）８１，８２によって回転自在
に支持される。The output shaft 4 is rotatably supported by a pair of deep groove ball bearings (rolling bearings) 81 and 82 having an outer ring fixed to the base 1 and an inner ring fitted to the outer periphery of the output shaft 4.
【００４１】軸受８１の内輪は、ロータ３をステータ２
に適切な力で加圧接触させるための加圧ばね６の変位量
分だけ、ディスク５と出力軸４とをステータ２側へ押し
込んだ状態で、出力軸４の外周に接着されている。ま
た、軸受８１の内輪と軸受８２の内輪との間には、圧縮
コイルばね３２が所定量圧縮された状態で挟持されてい
る。圧縮コイルばね１２の圧縮量は、上記加圧反力を軸
受８１と軸受８２の定格荷重の比に比例配分した場合の
反力成分が軸受８２の内輪に作用する変形量に設定され
ている。The inner ring of the bearing 81 includes the rotor 3 and the stator 2
The disk 5 and the output shaft 4 are bonded to the outer circumference of the output shaft 4 in a state of being pushed toward the stator 2 by an amount of displacement of the pressure spring 6 for making pressure contact with an appropriate force. Further, the compression coil spring 32 is sandwiched between the inner ring of the bearing 81 and the inner ring of the bearing 82 in a state of being compressed by a predetermined amount. The compression amount of the compression coil spring 12 is set to the amount of deformation in which the reaction force component acts on the inner ring of the bearing 82 when the pressure reaction force is proportionally distributed to the ratio of the rated loads of the bearing 81 and the bearing 82.
【００４２】本実施形態においても、２つの軸受８１，
８２に、加圧反力を定格荷重の比に比例配分した同方向
の予圧力を与えることによって、加圧反力を軸受８１，
８２が均等に負担することになり、駆動装置の長寿命化
が実現できる。Also in this embodiment, the two bearings 81,
By applying a preload in the same direction in which the pressure reaction force is proportionally distributed to the ratio of the rated load to 82, the pressure reaction force is applied to the bearings 81,
Since 82 is evenly burdened, the life of the drive device can be extended.
【００４３】また、本実施形態では、圧縮ばね３２の両
端を軸受内輪で支持し、一方の軸受内輪は出力軸４と接
着しているため、出力軸４にスナップリングをはめる溝
などを加工することなく、安価に長寿命化が可能とな
る。Further, in this embodiment, both ends of the compression spring 32 are supported by the bearing inner ring, and one bearing inner ring is adhered to the output shaft 4, so that a groove or the like for fitting a snap ring is formed on the output shaft 4. Without increasing the cost, it is possible to extend the life at low cost.
【００４４】（第４実施形態）図４は、本願発明の第４
実施形態である振動型駆動装置を示している。ベース１
に固定されたリング状の金属製ステータ（振動体）２
は、弾性体２１の下面に、コネクタ１０およびフレキシ
ブル基板１１を通じて通電される電気−機械エネルギ変
換素子２２を接合し、弾性体２１の上面に摩擦部材２３
を接着して構成されている。ロータ（移動体）４３は、
加圧ばね部４３ａおよびディスク部４３ｂを一体に有し
ている。そして、ロータ４３のディスク部４３ｂは、出
力軸４４をベース１の下方から挿入した上で適当な加圧
力が得られる変位分押し込んだ状態で出力軸４４に接着
されている。(Fourth Embodiment) FIG. 4 shows a fourth embodiment of the present invention.
1 illustrates a vibration type drive device according to an embodiment. Base 1
Ring-shaped metal stator (vibrating body) fixed to the
Joins the electro-mechanical energy conversion element 22 energized through the connector 10 and the flexible substrate 11 to the lower surface of the elastic body 21, and the friction member 23 on the upper surface of the elastic body 21.
It is configured by bonding. The rotor (moving body) 43 is
The pressure spring portion 43a and the disc portion 43b are integrally provided. The disc portion 43b of the rotor 43 is adhered to the output shaft 44 in a state where the output shaft 44 is inserted from below the base 1 and is pushed in by a displacement for obtaining an appropriate pressing force.
【００４５】出力軸４４は、出力軸４４の外周に形成さ
れた軌動溝４４ａ内を転動する転動体を有する出力軸４
４と一体の一対の軸受（ころがり軸受）８１，８２によ
って回転自在に支持される。軸受８１の外輪はベース１
に固定され、軸受８２の外輪は圧縮ばね４２を介してベ
ース１に保持されている。軸受８２の外輪は、ベース１
に対して圧縮ばね４２により押し下げられている。The output shaft 44 has a rolling element that rolls in a track groove 44a formed on the outer periphery of the output shaft 44.
It is rotatably supported by a pair of bearings (rolling bearings) 81 and 82 integrated with the bearing 4. Outer ring of bearing 81 is base 1
The outer ring of the bearing 82 is held by the base 1 via the compression spring 42. The outer ring of the bearing 82 is the base 1
Is pressed down by the compression spring 42.
【００４６】圧縮ばね４２の圧縮量は、加圧ばね部４５
ａの加圧反力を軸受８１と軸受８２の定格荷重の比に比
例配分した場合の反力成分が軸受８２の内輪に作用する
変形量に設定されている。The compression amount of the compression spring 42 depends on the pressure spring portion 45.
The reaction force component when the pressure reaction force of a is proportionally distributed to the ratio of the rated loads of the bearing 81 and the bearing 82 is set to the deformation amount that acts on the inner ring of the bearing 82.
【００４７】本実施形態においても、２つの軸受８１，
８２に、加圧反力を定格荷重の比に比例配分した同方向
の予圧力を与えることによって、加圧反力を軸受８１，
８２が均等に負担することになり、駆動装置の長寿命化
が実現できる。Also in this embodiment, the two bearings 81,
By applying a preload in the same direction in which the pressure reaction force is proportionally distributed to the ratio of the rated load to 82, the pressure reaction force is applied to the bearings 81,
Since 82 is evenly burdened, the life of the drive device can be extended.
【００４８】また、本実施形態では、部品点数が少な
く、さらに軸受内輪を有する軸受と出力軸との嵌合がた
による出力軸の振れ回りも少ないため、安価で、組立性
の良い、長寿命な駆動装置とすることができる。Further, in this embodiment, the number of parts is small and the whirling of the output shaft due to the fitting between the bearing having the bearing inner ring and the output shaft is small, so that the cost is low, the assemblability is good, and the life is long. Drive device.
【００４９】[0049]
【発明の効果】以上説明したように、本願発明によれ
ば、複数の軸受部材に同一方向の与圧力がかかるように
構成して加圧部材による加圧反力を複数の軸受部材に負
担させるだけでなく、バネ力を備えた部材により前記複
数の軸受部材に対して加圧反力が適切な割合で配分する
ように調整することが可能となり、前記複数の軸受部材
の軸受部材の寿命を略等しくすることができ、振動型駆
動装置の長寿命化を実現できる。As described above, according to the present invention, it is possible to apply a pressing force in the same direction to a plurality of bearing members.
The pressure reaction force generated by the pressure member is applied to multiple bearing members.
In addition to supporting it, a member with spring force
Appropriate proportion of pressure reaction force to several bearing members
It is possible to adjust so that the plurality of bearing members
The life of the bearing members can be made substantially equal, and the life of the vibration type drive device can be extended.
【００５０】また、各軸受部材の負担分配を各軸受部材
の定格荷重の比に比例配分したり、軸受軌道面と転動体
との接触面圧を等しくするように配分したりすれば、さ
らなる軸受部材および振動型駆動装置の長寿命化を図る
ことができる。[0050] In addition, or prorating to the ratio of the rated load bearing distribution of the bearing members <br/> of the bearing members, by allocation or to equalize the contact pressure between the bearing raceways and rolling elements If so, the life of the bearing member and the vibration type drive device can be further extended.
【図１】本発明の第１実施形態である振動型駆動装置の
断面図である。FIG. 1 is a cross-sectional view of a vibration-type drive device according to a first embodiment of the present invention.
【図２】本発明の第２実施形態である振動型駆動装置の
断面図である。FIG. 2 is a cross-sectional view of a vibration type driving device according to a second embodiment of the present invention.
【図３】本発明の第３実施形態である振動型駆動装置の
断面図である。FIG. 3 is a cross-sectional view of a vibration type drive device according to a third embodiment of the present invention.
【図４】本発明の第３実施形態である振動型駆動装置の
断面図である。FIG. 4 is a cross-sectional view of a vibration type drive device according to a third embodiment of the present invention.
【図５】上記第１実施形態の軸受部の模式図である。FIG. 5 is a schematic view of a bearing portion of the first embodiment.
【図６】従来の振動型駆動装置の軸受部の模式図であ
る。FIG. 6 is a schematic view of a bearing portion of a conventional vibration type drive device.
【図７】従来の振動型駆動装置の断面図である。FIG. 7 is a cross-sectional view of a conventional vibration type driving device.
１ ベース ２ ステータ ３，４３ ロータ ４，４４ 出力軸 ５ ディスク ６ 加圧ばね ７ ゴム ８１，８２ 軸受 ９ スナップリング １０ コネクタ １１ フレキシブル基板 １２ ウェーブワッシャ ３２ 圧縮コイルばね ４２ 圧縮ばね 1 base 2 stator 3,43 rotor 4,44 Output shaft 5 discs 6 Pressure spring 7 rubber 81,82 bearings 9 snap ring 10 connectors 11 Flexible substrate 12 Wave washers 32 compression coil spring 42 Compression spring
フロントページの続き (56)参考文献 特開 平７−143766（ＪＰ，Ａ) 特開 平６−121561（ＪＰ，Ａ) 特開 昭62−178178（ＪＰ，Ａ) 米国特許3531070（ＵＳ，Ａ) 米国特許3666219（ＵＳ，Ａ) 米国特許4531700（ＵＳ，Ａ) 米国特許5600196（ＵＳ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) H02N 2/00 Continuation of the front page (56) Reference JP-A-7-143766 (JP, A) JP-A-6-121561 (JP, A) JP-A-62-178178 (JP, A) US Patent 3531070 (US, A) US Patent 3666219 (US, A) US Patent 4531700 (US, A) US Patent 5600196 (US, A) (58) Fields investigated (Int.Cl. 7 , DB name) H02N 2/00
Claims (11)
に接触して駆動される振動体と、この移動体と出力軸と
を連結するとともに、前記移動体と前記振動体とを加圧
接触させる加圧部材と、前記出力軸を回転自在に支持す
る複数の軸受部材と、前記加圧部材による加圧反力を前
記出力軸を介して前記複数の軸受部材に配分するための
バネ力を備えた部材を有することを特徴とする振動型駆
動装置。1. A vibrating body in which vibration is excited, a vibrating body driven in contact with the vibrating body, the moving body and an output shaft are connected, and the moving body and the vibrating body are added. A pressure member to be brought into pressure contact with each other, a plurality of bearing members that rotatably support the output shaft, and a pressure reaction force generated by the pressure member to be distributed to the plurality of bearing members via the output shaft .
Vibration type driving apparatus according to claim Rukoto to have a member with a spring force.
内部予圧力として用いることを特徴とする請求項１に記
載の振動型駆動装置。2. The vibration type drive device according to claim 1, wherein the pressure reaction force is used as an internal preload of the plurality of bearing members.
に接触して駆動される振動体と、この移動体と出力軸と
を連結するとともに、前記移動体と前記振動体とを加圧
接触させる加圧部材と、前記出力軸を回転自在に支持す
る複数の軸受部材とを有し、前記加圧反力を、前記複数
の軸受部材に対し、これら各軸受部材の定格荷重の比に
応じて分担させることを特徴とする振動型駆動装置。3. A vibrating body in which vibration is excited, and this vibrating body.
Vibrating body that is driven by contact with the moving body, the moving body and the output shaft
And pressurize the moving body and the vibrating body.
A pressure member to be brought into contact with the output shaft is rotatably supported.
And a plurality of bearing members according to claim 1, wherein the pressure reaction force is shared by the plurality of bearing members according to the ratio of the rated loads of these bearing members.
あることを特徴とする請求項１から３のいずれかに記載
の振動型駆動装置。4. The vibration type drive device according to claim 1, wherein the plurality of bearing members are rolling bearings.
受に対し、これら各ころがり軸受の軌動面と転動体との
接触面圧が等しくなるように分担させることを特徴とす
る請求項４に記載の振動型駆動装置。5. The pressure reaction force is shared by the plurality of rolling bearings so that the contact surface pressures of the rolling surfaces of the respective rolling bearings and the rolling elements become equal to each other. The vibration type drive device according to item 4.
出力軸とが、前記出力軸への前記加圧反力の作用方向に
一体的に移動可能に結合していることを特徴とする請求
項４又は５に記載の振動型駆動装置。6. The inner races of the plurality of rolling bearings and the output shaft are integrally movably coupled in a direction in which the pressure reaction force acts on the output shaft. The vibration type drive device according to Item 4 or 5.
段を挟んで前記出力軸の軸方向両側に配置されているこ
とを特徴とする請求項４から６のいずれかに記載の振動
型駆動装置。7. The vibration type drive according to claim 4, wherein the plurality of rolling bearings are arranged on both sides of the output shaft in the axial direction with the pressurizing means interposed therebetween. apparatus.
受であり、前記複数のころがり軸受のうち所定のころが
り軸受の内輪と前記出力軸とが前記出力軸への前記加圧
反力の作用方向に一体的に移動可能に結合しており、前
記所定のころがり軸受の内輪と他のころがり軸受の内輪
との間に前記バネ力を備えた部材が配設されていること
を特徴とする請求項１又は２に記載の振動型駆動装置。 8. The plurality of bearing members are a plurality of rolling shafts.
A receiving are bound to be movable integrally with the direction of action of the pressurizing reaction force between the inner ring of a given rolling bearings of the plurality of rolling bearings and the output shaft to said output shaft, said predetermined vibratory driving device according to claim 1 or 2 member having the spring force between the inner ring of the rolling bearing of the other of the rolling bearing inner ring is characterized in that it is arranged.
を、前記各ころがり軸受に、前記加圧反力をこれら各こ
ろがり軸受の定格荷重の比に応じて分担させるよう設定
したことを特徴とする請求項８に記載の振動型駆動装
置。9. The displacement of the spring of the member having the spring force is set so that the rolling bearings share the pressure reaction force in accordance with the ratio of the rated loads of the rolling bearings. The vibration type drive device according to claim 8.
を、前記各ころがり軸受の軌動面と転動体との接触面圧
が等しくなるよう設定したことを特徴とする請求項８に
記載の振動型駆動装置。10. The displacement of the spring of the member having the spring force is set so that the contact surface pressure between the rolling surface of each rolling bearing and the rolling element is equal. Vibration type drive device.
前記出力軸の外周に形成された軌動溝部を転動すること
を特徴とする請求項４又は５に記載の振動型駆動装置。11. The rolling element of the plurality of rolling bearings comprises:
The vibration type drive device according to claim 4 or 5, wherein a rolling groove portion formed on the outer periphery of the output shaft rolls.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34856996A JP3397609B2 (en) | 1996-12-26 | 1996-12-26 | Vibration type driving device |
| US08/997,814 US6107723A (en) | 1996-12-26 | 1997-12-24 | Vibrating type driving device |
| CNB971208557A CN1166049C (en) | 1996-12-26 | 1997-12-26 | Vibrating type driving device |
| CNB031453325A CN1262359C (en) | 1996-12-26 | 1997-12-26 | Vibrating driver |
| KR1019970073887A KR100341720B1 (en) | 1996-12-26 | 1997-12-26 | Vibration Drive |
| US09/266,854 US6225730B1 (en) | 1996-12-26 | 1999-03-12 | Vibrating type driving device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34856996A JP3397609B2 (en) | 1996-12-26 | 1996-12-26 | Vibration type driving device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10191667A JPH10191667A (en) | 1998-07-21 |
| JP3397609B2 true JP3397609B2 (en) | 2003-04-21 |
Family
ID=18397906
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP34856996A Expired - Fee Related JP3397609B2 (en) | 1996-12-26 | 1996-12-26 | Vibration type driving device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3397609B2 (en) |
-
1996
- 1996-12-26 JP JP34856996A patent/JP3397609B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH10191667A (en) | 1998-07-21 |
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