JPS59230672A - Differential type amplitude expanding mechanism - Google Patents
Differential type amplitude expanding mechanismInfo
- Publication number
- JPS59230672A JPS59230672A JP10621183A JP10621183A JPS59230672A JP S59230672 A JPS59230672 A JP S59230672A JP 10621183 A JP10621183 A JP 10621183A JP 10621183 A JP10621183 A JP 10621183A JP S59230672 A JPS59230672 A JP S59230672A
- Authority
- JP
- Japan
- Prior art keywords
- coupling member
- coupling
- movable
- displacement
- movable member
- 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
Links
Landscapes
- Impact Printers (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】 本発明は差動型振幅拡大機構に関する。[Detailed description of the invention] The present invention relates to a differential amplitude expansion mechanism.
従来、駆動源が発生する機械的変位を二つのレバーによ
り拡大して伝達し、この二つのレバーが差動的に伝達す
る偶力を可動部材に作用させて、振幅を拡大した変位を
得るための差動型振幅拡大機構がある。Conventionally, the mechanical displacement generated by the drive source is magnified and transmitted by two levers, and the couple differentially transmitted by these two levers is applied to the movable member to obtain displacement with expanded amplitude. There is a differential amplitude expansion mechanism.
第１図は従来の差動型振幅拡大機構を示す側面図である
。同図において、一端を金属の取付部材１に固定した圧
電体２が駆動源である。圧電体２の電極（図示省略）に
駆動電圧を印加したときに圧電体２が伸びて寸法の歪（
朱じ、この寸法歪が金属の第１および第３の結合部材３
および５を介して金属の第１および第２の可動部材７お
よび８に伝達され、それぞれ破線矢印ＡおよびＢで示す
向きの機械的変位を与える。第１および第２の可動部材
７および８の下端はそれぞれ、第１および第３の結合部
材３および５から所定間隔をおいた箇所で、金属の第２
および第４の結合部材４および６ｔ−介して取付部材１
に接続して−いる。破線矢印ＡおよびＢの向きの機械的
変位がそれぞれ第↓および第２の可動部材７および８に
伝達されると、これに応じて第２および第４の結合部材
４および６が屈曲し、第１および第２の可動部材７およ
び８に回転モーメンｌ−生じて、第１および第２の可動
部材７および８の上端部にはそれぞれ破線矢印Ｃおよび
Ｄで示す向きの拡大された変位を生ずる。第１および第
２の可動部材７および８の上端部には、それぞれ金属板
の第５および第６の結合部材９および１０の一方の端部
が固着しておシ、第５および第６の結合部材９および１
０の他方の端部は金属の第３の可動部材１１に接続して
いる。FIG. 1 is a side view showing a conventional differential amplitude expansion mechanism. In the figure, a piezoelectric body 2 whose one end is fixed to a metal mounting member 1 is a driving source. When a driving voltage is applied to the electrodes (not shown) of the piezoelectric body 2, the piezoelectric body 2 expands, resulting in dimensional distortion (
This dimensional distortion is caused by the metal first and third joining members 3.
and 5 to the metal first and second movable members 7 and 8, giving mechanical displacements in the directions indicated by dashed arrows A and B, respectively. The lower ends of the first and second movable members 7 and 8 are connected to a metal second movable member at a predetermined distance from the first and third coupling members 3 and 5, respectively.
and fourth coupling members 4 and 6t - via mounting member 1
It is connected to. When mechanical displacements in the directions of dashed arrows A and B are transmitted to the ↓ and second movable members 7 and 8, respectively, the second and fourth coupling members 4 and 6 are bent in response, and the second and fourth coupling members 4 and 6 are bent. A rotational moment l- is generated in the first and second movable members 7 and 8, resulting in an enlarged displacement in the direction indicated by dashed arrows C and D at the upper ends of the first and second movable members 7 and 8, respectively. . One ends of fifth and sixth coupling members 9 and 10 made of metal plates are fixed to the upper ends of the first and second movable members 7 and 8, respectively. Connecting members 9 and 1
0 is connected to a third movable member 11 made of metal.
第３の可動部材１１には、第５および第６の結合部材９
および１０を介してそれぞれ破線矢印ＣおよびＤの向き
の変位が伝達される。この二つの変位は互いに逆向きで
あるから、第３の可動部材１１は差動的な二つの変位を
与える偶力を受けて、その先端部に破線矢印Ｅで示す向
きの拡大された変位を生ずる。The third movable member 11 includes fifth and sixth coupling members 9.
and 10, displacements in the directions of dashed arrows C and D are transmitted, respectively. Since these two displacements are in opposite directions, the third movable member 11 receives a couple of differential displacements and causes an enlarged displacement in the direction indicated by the dashed arrow E at its tip end. arise.
第２図は従来の差動型振幅拡大機構を示す部分側面図で
あり、動作時に第５および第６の結合部材９および１０
に作用する力の向きを例示する。FIG. 2 is a partial side view showing a conventional differential amplitude amplification mechanism, in which the fifth and sixth coupling members 9 and 10 are connected during operation.
The direction of the force acting on is exemplified.
圧電体２が伸びて第１の可動部材７に破線矢印ＡＯ向き
の変位が伝達されたときに、第１の可動部材７は第２の
結合部材４の中央部を通る軸Ｐを中心軸としそのまわり
に回転運動する。これに伴なって、第１の可動部材７と
第５の結合部材９との接合箇所には、破線矢印Ｆで示す
向きの、すなわちその接合箇所と軸Ｐとを結ぶ線分に直
交する向きの力が作用する。この力は、破線矢印Ｃで示
す向きに作用して第５の結合部材９を板面に沿りた向き
に引張るとともに、破線矢印Ｇで示すごとく第５の結合
部材９の板面に直角に作用して第５の結合部材９の板面
に曲げを生じさせる。同様に、第２の可動部材８に破線
矢印Ｂの向きの変位が伝達され、第２の可動部材８が第
４の結合部材６の中央部を通る軸Ｑ′ｆｔ、中心軸とし
そのまわシに回転運動して、第２の可動部材８と第６の
結合部材１０との接合箇所には、破線矢印Ｈで示すごと
くその接合箇所と軸Ｑとを結ぶ線分に直交する向きの力
が作用する。この力は、破線矢印りで示すごとく第６の
結合部材１０を板面に沿って押すとともに、破線矢印Ｊ
で示すごとく第６の結合部材１０の板面に直角に作用し
て曲げを生じさせる。When the piezoelectric body 2 extends and a displacement in the direction of the broken line arrow AO is transmitted to the first movable member 7, the first movable member 7 has an axis P passing through the center of the second coupling member 4 as its central axis. rotate around it. Along with this, the joint between the first movable member 7 and the fifth coupling member 9 is arranged in the direction indicated by the dashed arrow F, that is, in the direction perpendicular to the line segment connecting the joint and the axis P. The force of is applied. This force acts in the direction shown by the dashed arrow C and pulls the fifth coupling member 9 along the plate surface, and also at right angles to the plate surface of the fifth coupling member 9 as indicated by the broken arrow G. This causes the plate surface of the fifth coupling member 9 to bend. Similarly, the displacement in the direction of the dashed arrow B is transmitted to the second movable member 8, and the second movable member 8 moves to the axis Q'ft passing through the center of the fourth coupling member 6, and rotates around the axis Q'ft. As a result, a force is applied to the joint between the second movable member 8 and the sixth coupling member 10 in a direction perpendicular to the line segment connecting the joint and the axis Q, as shown by the dashed arrow H. act. This force pushes the sixth coupling member 10 along the plate surface as shown by the broken line arrow J.
As shown in , it acts perpendicularly to the plate surface of the sixth coupling member 10 to cause bending.
このように、従来の差動型振幅拡大機構では、動作時に
第５および第６の結合部材９および１０にそれぞれ引張
応力および圧縮応力金生ずるとともに、曲げ応力を生ず
る。このため、特に繰返し動作回数が多い機器、例えば
ドツトインパクト方式プリンタの印字ヘッドに適用する
と、第５および第６の結合部材９および１０に繰返し作
用する応力の大きさが疲労限度を超えて、第５および第
６の結合部材９および１０に折損を生じ易いという欠点
がある。In this manner, the conventional differential amplitude amplification mechanism generates tensile stress and compressive stress, as well as bending stress, in the fifth and sixth coupling members 9 and 10, respectively, during operation. For this reason, especially when applied to a device that operates repeatedly many times, such as the print head of a dot impact printer, the magnitude of the stress that repeatedly acts on the fifth and sixth connecting members 9 and 10 may exceed the fatigue limit. There is a disadvantage that the fifth and sixth coupling members 9 and 10 are easily broken.
本発明の目的は、上述の欠点を除去し偶力を伝達する板
状の結合部材に作用する曲げ応力を従来よシも軽減して
折損を生じないようにした差動型振幅拡大機構を提供す
ることにある。An object of the present invention is to provide a differential amplitude amplification mechanism that eliminates the above-mentioned drawbacks and reduces the bending stress acting on the plate-shaped coupling member that transmits the force couple more than ever before, thereby preventing breakage. It's about doing.
本発明の機構は、所定箇所が取付部材に固定されておシ
所定の向きの変位を発生するための駆動部材と、
前記駆動部材の第１の所定箇所に一端が接続された第１
の結合部材と前記取付部材の第１の所定箇所に一端が接
続された第２の結合部材とのそれぞれの他端に接続して
お夛、前記第１の結合部材を介して伝達される前記変位
に応じて前記第２の結合部材を通る中心軸の回シに回転
し第１の角変位を生ずる第１の可動部材と、
前記駆動部材の第２の所定箇所に一端が接続された第３
の結合部材と前記取付部材の第２の所定箇所に一端が接
続された第４の結合部材とのそれぞれの他端に接続して
おり、前記第３の結合部材を介して伝達される前記変位
に応じて前記第４の結合部材を通る中心軸の回９に回転
し第２０角変位を生ずる第２の可動部材と、
一端が前記第１の可動部材の所定箇所に接合しておシ前
記第１の角変位を伝達するための板状の第５の結合部材
と一端が前記第２の可動部材の所定箇所に接合しており
前記第２の角変位を伝達するための板状の第６の結合部
材とを有し、前記第５および第６の結合部材の少くとも
いずれか一方の結合部材は、該結合部材の前記接合箇所
と前記第１および第２の可動部材のうち該結合部材が接
合している可動部材の前記回転の前記中心軸とを結ぶ線
分に対し、該結合部材の板面が実質的に直角をなすよう
配設された差動型変位伝達部材と、前記第５おｌび第６
の結合部材のそれぞれの他端に接続しておりこの両者を
介して伝達される前記第１および第２の角変位に応じて
第３の角変位を生じ円弧運動を発生する第３の可動部材
とを備えている。The mechanism of the present invention includes: a drive member whose predetermined portion is fixed to a mounting member for generating displacement in a predetermined direction; and a first drive member whose one end is connected to the first predetermined portion of the drive member.
and a second coupling member, one end of which is connected to the first predetermined location of the mounting member, respectively, so that the a first movable member that rotates about its central axis passing through the second coupling member in response to the displacement to produce a first angular displacement; and a first movable member that has one end connected to a second predetermined location of the drive member. 3
and a fourth coupling member, one end of which is connected to a second predetermined location of the mounting member, and the displacement transmitted via the third coupling member. a second movable member that rotates at a rotation angle of 9 with respect to a central axis passing through the fourth coupling member to produce a 20th angular displacement in response to the movement of the second movable member; a fifth plate-shaped coupling member for transmitting the first angular displacement; and a fifth plate-shaped coupling member, one end of which is joined to a predetermined location of the second movable member, for transmitting the second angular displacement. 6 coupling members, and at least one of the fifth and sixth coupling members connects the joint portion of the coupling member with the coupling member of the first and second movable members. a differential displacement transmission member disposed such that a plate surface of the coupling member is substantially perpendicular to a line segment connecting the central axis of rotation of a movable member to which the member is joined; 5th and 6th
a third movable member connected to each other end of the coupling member and generating a third angular displacement and circular arc motion in response to the first and second angular displacements transmitted through the two; It is equipped with
次に図面を参照して本発明の詳細な説明する。Next, the present invention will be described in detail with reference to the drawings.
第３図（ａｌおよび（ｂ）はそれぞれ本発明の詳細な説
明するための部分斜視図および特性図である。同図ｔａ
＋において、第１の可動部材７と第５の結合部材９との
接合箇所Ｊ１に作用する破線矢印Ｆの向きの力の大きさ
をｆとし、この力を第５の結合部材９の板面に対しそれ
ぞれ平行および直角な向きの、すなわち破線矢印Ｃおよ
びＧの向きの二つの分力に分解し、それぞれの分力の大
きさｆ、ｆｔおよびｆ２とする。破線矢印Ｆおよび０間
の角度０を用いて表わせば明らかに、ｆ１＝ｆＣＯ１θ
およびｆ２−ｆ＊θが成立つ。第５の結合部材９の板厚
’６ｔとし、板幅をＷとする。また第５の結合部材９と
第３の可動部材１１との接合箇所Ｊ２と接合箇所Ｊ１と
の間の長さヲ皿とする。接合点Ｊ１に破線矢印の向きに
ｆの力が作用したとき、接合箇所Ｊ１および５２間の第
５の結合部材９には、ｆｌの力に応じた引張応力とｆ２
の力に応じた曲げ応力とを生ずる。この引張応力の大き
さをσ１ とすれば、σ１＝ｆｉ／ｗｔが成立つ。また
曲げ応力は板面上で最大となりその大きさｔ０２とすれ
ば、σ２ ” ｆ ２ Ｘ ｊ Ｑ ／ ４ Ｉ、ただ
しｌは断面二次モーメントで工＝Ｖｌ ｔ／１２である
から、σ２＝ｆ２Ｘ３ Ｑ ／−ｔ２でおる。従って第
５の結合部材９に生ずる最大の応力全σとすれば、
’ ” ’ ｉ ＋’ ２ ＝ （’ ｉ／”ｔ ）
＋（ｆ２ Ｘ３１／ｗｔ”）＝ （ｆ ／ｗｔ ） （
ＣＯ３θ＋（３ｆｉ／１）Ｘ４θ） ・−・・−（１）
が成立つ。3(a) and 3(b) are a partial perspective view and a characteristic diagram, respectively, for explaining the present invention in detail.
+, the magnitude of the force in the direction of the broken arrow F acting on the joint J1 between the first movable member 7 and the fifth coupling member 9 is f, and this force is applied to the plate surface of the fifth coupling member 9. The force is divided into two component forces parallel to and perpendicular to, that is, in the directions of dashed arrows C and G, and the magnitudes of the respective component forces are f, ft, and f2. If expressed using the dashed arrow F and the angle 0 between 0, it is clear that f1=fCO1θ
and f2-f*θ hold true. The plate thickness of the fifth coupling member 9 is '6t, and the plate width is W. Further, the length between the joint J2 and J1 between the fifth coupling member 9 and the third movable member 11 is set as a plate. When a force f acts on the joint J1 in the direction of the dashed arrow, the fifth connecting member 9 between the joint J1 and 52 has a tensile stress corresponding to the force fl and a tensile stress f2.
A bending stress corresponding to the force is generated. If the magnitude of this tensile stress is σ1, then σ1=fi/wt holds true. Also, the bending stress is maximum on the plate surface and its magnitude is t02, then σ2 '' f 2 Q/-t2. Therefore, if the maximum total stress generated in the fifth connecting member 9 is σ, '''' i +' 2 = ('i/'t )
+(f2 X31/wt”)=(f/wt) (
CO3θ+(3fi/1)X4θ) ・−・・−(1)
holds true.
第３図（ｂｌは、上記の式（１）に−設計例の数値を代
入した場合の角度θと応力σとの関係を示す。本設計例
では、ｆ＝２Ｋｆ、１＝１０簡、ｗ＝２ｍｔｔ＝０．３
ｍｍでアシ、これを式（１）に代入すると、σ＝３．３
３Ｘ（ｃｏｓｏ＋６６．６Ｘｓ＋ｔｎθ）、ただしσの
単位はに４７，１、なる関係式が得られる。この関係式
を図示したのが第３図（ｂ）であり、ｆｆｉ＞ｔである
ため、角度θが増大すると曲げ応力σ２が急激に増大し
、これに伴なって応力σが急激に増大することが判る。Figure 3 (bl shows the relationship between the angle θ and the stress σ when the numerical values of the design example are substituted into the above equation (1). In this design example, f = 2Kf, 1 = 10, w =2mtt=0.3
If we substitute this into equation (1), we get σ=3.3.
3X(coso+66.6Xs+tnθ), where the unit of σ is 47.1, is obtained. This relational expression is illustrated in FIG. 3(b), and since ffi>t, as the angle θ increases, the bending stress σ2 increases rapidly, and along with this, the stress σ increases rapidly. I understand that.
本設計例において、第５の結合部材９の材料として疲労
限度が４０Ｋｆ／ＥＪ程度の鋼を使用する場合には、角
度θがダ以下になるよう設計して折損破壊を防がねばな
らない。勿論、破壊を生じないような角度θの上限値は
上記の各数値や使用材料の選定の仕方によって異なって
くるが、通常の設計では旦〉ｔであるため、角度θの増
大に伴なって曲げ応力σ２が急激に増大するのを避けら
れない場合が多い。本発明の機構では、角度０を実質的
に０°となるよう構成することにより、偶力伝達用の結
°合部材に過大な曲げ応力が生じないようにして、折損
破壊を防止する。In this design example, when steel with a fatigue limit of about 40 Kf/EJ is used as the material for the fifth coupling member 9, it is necessary to design the angle θ to be less than or equal to da to prevent breakage. Of course, the upper limit of the angle θ that does not cause damage will vary depending on the above values and how the materials used are selected, but in normal design it is 1〉t, so as the angle θ increases, In many cases, it is unavoidable that the bending stress σ2 increases rapidly. In the mechanism of the present invention, by configuring the angle 0 to be substantially 0°, excessive bending stress is not generated in the couple transmission coupling member, thereby preventing breakage and breakage.
第４図は本発明の第１の実施例を示す側面図である。同
図の機構では、第５の結合部材１９の板面が、破線矢印
Ｆで示す向きすなわち第１の可動部材１７および第５の
結合部材１９の接合箇所と第１の可動部材１７の回転の
中心軸とを結ぶ線分に直交する向きに対し平行に々るよ
う構成されてお９、且つ第６の結合部材２０の板面が、
破線矢印Ｈで示す向きすなわち第２の可動部材１８およ
び第６の結合部材２０の接合箇所と第２の可動部材１８
の回転の中心軸とを結ぶ線分に直交する向きに対し平行
になるよう構成されている。従って第１および第２の可
動部材１７および１８にそれぞれ破線矢印人およびＢの
向きの変位が伝達され、これを拡大した変位が第５およ
び第６の結合部材１９および２０を介して第３の可動部
材２１に伝達されるときに、第３図（ａｌおよび（ｂｌ
において角度θが０°の場合に相当する動作全行うから
、第５および第６の結合部材１９および２０には過大な
曲げ応力を生じない。これによシ、印字ヘッドのように
繰返し動作回数が多い機器に適用しても折損波１１ｔ−
生ずることがなく、耐用期間を従来よシも著しく長くす
ることができる。FIG. 4 is a side view showing the first embodiment of the present invention. In the mechanism shown in the figure, the plate surface of the fifth coupling member 19 is oriented in the direction shown by the broken line arrow F, that is, the joint location of the first movable member 17 and the fifth coupling member 19 and the rotation of the first movable member 17. The plate surface of the sixth coupling member 20 is configured to extend parallel to a direction perpendicular to a line segment connecting the central axis, and the plate surface of the sixth coupling member 20 is
The direction indicated by the dashed arrow H, that is, the joint location of the second movable member 18 and the sixth coupling member 20 and the second movable member 18
It is configured to be parallel to the direction perpendicular to the line segment connecting the central axis of rotation. Therefore, displacements in the directions of dashed arrows 1 and B are transmitted to the first and second movable members 17 and 18, respectively, and a displacement that is expanded is transmitted to the third movable members 17 and 18 via the fifth and sixth coupling members 19 and 20. When transmitted to the movable member 21, FIG.
Since all operations corresponding to the case where the angle θ is 0° are performed in , excessive bending stress is not generated in the fifth and sixth coupling members 19 and 20. As a result, even when applied to equipment that operates repeatedly many times, such as a print head, the broken wave 11t-
This does not occur, and the service life can be significantly extended compared to the conventional method.
第５図は本発明の第２の実施例を示す側面図である。本
実施例の機構は、第１の実施例と同様に第３図（ａｌお
よび（ｂ）において角度０がσの場合に相当する動作を
行うよう構成されているが、第３の可動部材３１で得ら
れる変位の向きが第１の実施例の場合と異なる。すなわ
ち、第１および第２の可動部材２７および２８の形状を
変更して、破線矢印ＡおよびＢで示す向きの変位が伝達
され、これが第５および第６の結合部材２９およびａｏ
’４介して第３の可動部材３１に伝達されたときに、破
線矢印Ｅで示すごとく破線矢印ＡおよびＢの向きに対し
平行な向きの変位が得られるよう構成しである。第１の
実施例では、第４図に示したごとく、圧電体２から伝達
される変位の向きと、第３の可動部材２１に伝達される
変位の向きとは、互いに直交してお９、この二つの変位
の向きの間の角度は、第１および第２の可動部材を適宜
変更することにより、所望の大きさに選定することがで
きる。その際にも、第３図（ａｌおよび（ｂｌにおいて
角、度θがＯｏの場合に相当する動作を行うよう構成で
き、従って第１の実施例と同様に、偶力伝達用の結合部
材に過大な曲げ応力を生じないようにして折損破壊を防
止できる。FIG. 5 is a side view showing a second embodiment of the invention. Similar to the first embodiment, the mechanism of this embodiment is configured to perform an operation corresponding to the case where the angle 0 is σ in FIGS. The direction of the displacement obtained is different from that in the first embodiment.In other words, the shapes of the first and second movable members 27 and 28 are changed to transmit the displacement in the directions indicated by broken line arrows A and B. , this is the fifth and sixth coupling member 29 and ao
When transmitted to the third movable member 31 via '4, displacement in a direction parallel to the directions of broken line arrows A and B, as shown by broken line arrow E, is obtained. In the first embodiment, as shown in FIG. 4, the direction of the displacement transmitted from the piezoelectric body 2 and the direction of the displacement transmitted to the third movable member 21 are orthogonal to each other. The angle between these two directions of displacement can be selected to a desired size by appropriately changing the first and second movable members. In that case, it can be configured to perform the operation corresponding to the case where the angle and degree θ are Oo in FIG. Breakage and breakage can be prevented by not generating excessive bending stress.
なお、第１および第２の実施例ではいずれも、第５およ
び第６の結合部材の両者とも角度θが０゜となるよう構
成しているが、作用する力や板厚。In both the first and second embodiments, the angle θ of both the fifth and sixth coupling members is 0°; however, the applied force and plate thickness may vary.
板幅、板長がすべて両者で相等しいとは限らないから、
両者のうちのいずれか一方は角度θを実質的にσにしな
くても疲労限度を超える曲げ応力を生じない場合がある
。このような場合には、両者のうちの他の一方だけにつ
いて角度θが実質的に０°となるよう構成すれば、所期
の効果が得られる。Since the board width and board length are not necessarily equal for both,
Either one of the two may not produce bending stress exceeding the fatigue limit even if the angle θ is not substantially σ. In such a case, the desired effect can be obtained by configuring only the other one of them so that the angle θ is substantially 0°.
以上の説明によシ明らかなごとく、本発明には偶力伝達
用の板状結合部材に作用する曲げ応力を従来よりも軽減
して折損破壊を生じないようにした差動型振幅拡大機構
を実現できるという効果がらり、特に繰返し動作回数が
多い機器に適用してその効果が著しい。As is clear from the above explanation, the present invention includes a differential amplitude amplification mechanism that reduces the bending stress acting on the plate-like coupling member for couple transmission more than the conventional one and prevents breakage. This is particularly effective when applied to equipment that requires a large number of repeated operations.
第１図および第２図はそれぞれ従来の差動型振幅拡大機
構を示す側面図および部分側面図、第３図（ａ）および
（ｂｌはそれぞれ本発明の詳細な説明するための部分斜
視図および特性図、第４図および第５図はいずれも本発
明の実施例を示す側面図である。
１・・・・・・取付部材、２・・・・・・圧電体、３・
・・・・・第１の結合部材、４・・・・・・第２の結合
部材、５・・・・・・第３の結合部材、６・・・・・・
第４の結合部材、７，１７．２７・・・・・・第１の可
動部材、８，１８．２８・・・・・・第２の可動部材、
９，１９．２９−・・・・・第５の結合部材、１０，２
０．３０・−・・・・第６の結合部材、１１，２１，３
１・・・・・・第３の可動部材。
く、ご〕ノ
８１図
筈Ｚ図FIGS. 1 and 2 are a side view and a partial side view showing a conventional differential amplitude amplification mechanism, respectively, and FIGS. The characteristic diagram, FIG. 4, and FIG. 5 are all side views showing embodiments of the present invention. 1... Attachment member, 2... Piezoelectric body, 3.
...First coupling member, 4...Second coupling member, 5...Third coupling member, 6...
Fourth coupling member, 7, 17.27... First movable member, 8, 18.28... Second movable member,
9,19.29--Fifth coupling member, 10,2
0.30 --- Sixth coupling member, 11, 21, 3
1...Third movable member. ku,go]no 81 diagram Z diagram
Claims (1)
を発生するだめの駆動部材と、前記駆動部材の第１の所
定箇所に一端が接続された第１の結合部材と前記取付部
材の第１の所定箇所に一端が接続された第２の結合部材
とのそれぞれの他端に接続しておシ、前記第１の結合部
材を介して伝達される前記変位に応じて前記第２の結合
部材を通る沖心軸の回りに回転し第１の角変位を生ずる
第１の可動部材と、 前記駆動部材の第２の所定箇所に一端が接続された第３
の結合部材と前記取付部材の第２の所定箇所に一端が接
続された第４の結合部材とのそれぞれの他端に接続して
おシ、前記第３の結合部材を介して伝達される前記変位
に応じて前記第４の結合部材を通る中心軸の回シに回転
し第２の角変位を生ずる第２の可動部材と、 一端が前記第１の可動部材の所定箇所に接合しておシ前
記第１の角変位を伝達するための板状の第５の結合部材
と一端が前記第２の可動部材の所定箇所に接合しており
前記第２の角変位を伝達するための板状の第６の結合部
材とを有し、前記第５および第６の結合部材の少くとも
いずれか一方の結合部材は、該結合部材の前記接合箇所
と前記第１および第２の可動部材のうち該結合部材が接
合している可動部材の前記回転の前記中心軸とを結ぶ線
分に対し、該結合部材の板面が実質的に直角をなすよう
配設された差動型変位伝達部材と、前記第５および第６
の結合部材のそれぞれの他端に接続しておシこの両者を
介して伝達される前記第１および第２の角変位に応じて
第３の角変位を生じ円弧運動を発生する第３の可動部材
とを備えたことを特徴とする差動型振幅拡大機構。[Scope of Claims] A drive member whose predetermined portion is fixed to a mounting member and generates displacement in a predetermined direction, and a first coupling member whose one end is connected to the first predetermined portion of the drive member. and a second coupling member, one end of which is connected to the first predetermined location of the mounting member, and the second coupling member has one end connected to the first predetermined location of the mounting member, and is responsive to the displacement transmitted via the first coupling member. a first movable member that rotates around an offshore axis that passes through the second coupling member and causes a first angular displacement; and a third movable member that has one end connected to a second predetermined location of the drive member.
and a fourth coupling member, one end of which is connected to the second predetermined location of the mounting member, are connected to the other ends of the fourth coupling member, and the a second movable member that rotates about its central axis passing through the fourth coupling member in response to the displacement to produce a second angular displacement; and one end of the second movable member is joined to a predetermined location of the first movable member. a plate-shaped fifth coupling member for transmitting the first angular displacement; and a plate-shaped fifth coupling member having one end joined to a predetermined location of the second movable member and transmitting the second angular displacement. a sixth coupling member, at least one of the fifth and sixth coupling members is connected to the joint portion of the coupling member and the first and second movable members. A differential displacement transmission member disposed such that a plate surface of the coupling member is substantially perpendicular to a line connecting the central axis of rotation of a movable member to which the coupling member is connected; , the fifth and sixth
a third movable member that is connected to the other end of each of the coupling members and generates a third angular displacement in response to the first and second angular displacements transmitted through both the cylinders and generates an arcuate motion; A differential amplitude amplification mechanism characterized by comprising a member.
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10621183A JPS59230672A (en) | 1983-06-14 | 1983-06-14 | Differential type amplitude expanding mechanism |
| CA000447850A CA1218561A (en) | 1983-02-25 | 1984-02-20 | Differential lever actuator including differentially force-transmitting members which are not liable to break |
| US06/582,667 US4518887A (en) | 1983-02-25 | 1984-02-23 | Differential lever actuator including differentially force-transmitting members which are not liable to break |
| BR8400913A BR8400913A (en) | 1983-02-25 | 1984-02-24 | DIFFERENTIAL LEVER DRIVER INCLUDING DIFFERENTIAL ELEMENTS OF POWER TRANSMITTERS NOT SUBJECT TO BREAKING |
| DE8484101948T DE3482664D1 (en) | 1983-02-25 | 1984-02-24 | DIFFERENTIAL DRIVE FOR ONE LEVER. |
| AU25036/84A AU559869B2 (en) | 1983-02-25 | 1984-02-24 | Differential lever actuator |
| EP84101948A EP0117547B1 (en) | 1983-02-25 | 1984-02-24 | Differential lever actuator |
| KR8400963A KR890003340B1 (en) | 1983-02-25 | 1984-02-25 | Differential lever actuator including differentially force-transmitting members which are not liable |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10621183A JPS59230672A (en) | 1983-06-14 | 1983-06-14 | Differential type amplitude expanding mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59230672A true JPS59230672A (en) | 1984-12-25 |
| JPH0419944B2 JPH0419944B2 (en) | 1992-03-31 |
Family
ID=14427815
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10621183A Granted JPS59230672A (en) | 1983-02-25 | 1983-06-14 | Differential type amplitude expanding mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59230672A (en) |
-
1983
- 1983-06-14 JP JP10621183A patent/JPS59230672A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0419944B2 (en) | 1992-03-31 |
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