JP2010138973A - Vibration restraining device - Google Patents
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- JP2010138973A JP2010138973A JP2008314740A JP2008314740A JP2010138973A JP 2010138973 A JP2010138973 A JP 2010138973A JP 2008314740 A JP2008314740 A JP 2008314740A JP 2008314740 A JP2008314740 A JP 2008314740A JP 2010138973 A JP2010138973 A JP 2010138973A
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- 230000000452 restraining effect Effects 0.000 title abstract 4
- 238000013016 damping Methods 0.000 claims abstract description 129
- 238000003825 pressing Methods 0.000 claims abstract description 95
- 238000004804 winding Methods 0.000 claims description 70
- 230000001629 suppression Effects 0.000 claims description 24
- 230000005484 gravity Effects 0.000 claims description 11
- 239000000463 material Substances 0.000 claims description 5
- 230000008602 contraction Effects 0.000 claims 1
- 230000008878 coupling Effects 0.000 claims 1
- 238000010168 coupling process Methods 0.000 claims 1
- 238000005859 coupling reaction Methods 0.000 claims 1
- 238000009434 installation Methods 0.000 abstract description 5
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 238000005096 rolling process Methods 0.000 abstract 1
- 238000006073 displacement reaction Methods 0.000 description 21
- 238000000034 method Methods 0.000 description 11
- 230000000052 comparative effect Effects 0.000 description 8
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000037303 wrinkles Effects 0.000 description 4
- 230000002238 attenuated effect Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000004069 differentiation Effects 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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- Vibration Prevention Devices (AREA)
- Winding Of Webs (AREA)
- Rolls And Other Rotary Bodies (AREA)
Abstract
Description
本発明は、二軸延伸フィルム、無延伸フィルムなどのシート状物の巻き取りに使用される振動抑制装置に関する。 The present invention relates to a vibration suppressing device used for winding a sheet-like material such as a biaxially stretched film or an unstretched film.
フィルムの巻き取り工程では、ある巻き取り速度でフィルムが巻芯に巻き取られることで巻きロールが形成される。この巻き取り速度に関し、ＰＥＴ製やＰＰ製の樹脂製フィルムは紙製フィルムに比し通気性に乏しいことで生ずる意図しない現象のために巻き取り速度の制約が厳しく、紙製フィルムの場合ほど速度を高めることが難しい。すなわち、巻きロールの巻き取り速度がある値を超えると、巻きロールの軸芯に沿う方向に樹脂フィルムがずれて巻き取られてしまうという巻きずれが顕著となる。巻きずれ、あるいは偏心巻き、フィルム上の皺の発生といった望ましくない現象を防止して安定した巻き取り状態を確保するため、巻きロールの表面を押圧ロールで押えつける方法が広く用いられている。 In the film winding process, the film is wound around the core at a certain winding speed to form a winding roll. Regarding the winding speed, a resin film made of PET or PP has a severe restriction on the winding speed due to an unintended phenomenon caused by poor air permeability compared to a paper film. It is difficult to increase. That is, when the winding speed of the winding roll exceeds a certain value, winding deviation that the resin film is displaced and wound in the direction along the axis of the winding roll becomes significant. In order to prevent undesired phenomena such as winding deviation, eccentric winding, and wrinkles on the film and to ensure a stable winding state, a method of pressing the surface of the winding roll with a pressing roll is widely used.
しかし、フィルムの巻き替え時に発生するフィルム表面の皺、巻取り時に折り重なるフィルムの表面形状の違いに起因する凹凸、巻取り時にフィルム間に空気が混入することで形成された突起などを押圧ロールが乗り越える際、押圧ロールが巻きロール表面からバウンドして振動する。これにより、フィルムの巻き姿が悪化して商品価値を低下させることが問題となっている。特に近年は巻き取り速度が従来に増して高速化しているため、この問題が顕在化し、製品フィルムの歩留まりや品質を低下させる原因となっている。 However, the pressing roll can remove wrinkles on the surface of the film that occur during film rewinding, irregularities that result from differences in the surface shape of the film that folds during winding, and protrusions that are formed when air enters between the films during winding. When getting over, the pressing roll bounces from the surface of the winding roll and vibrates. Thereby, it has been a problem that the rolled form of the film deteriorates and the commercial value is lowered. Particularly in recent years, since the winding speed has been increased more than before, this problem has become apparent, causing a reduction in the yield and quality of product films.
この問題に対処するため、例えば特許文献１に開示される従来のシート状物巻き取り装置では、次のような振動抑制装置によって押圧ロールの振動が抑えられている。すなわち、図１２に示す振動抑制装置１０１は、固定台１０２、押圧ロール軸受けフォルダー１０３、押圧ロール１０４、加圧手段１０５、振動減衰手段１０６および移動レール１１０を備えている。押圧ロール１０４は、連結手段としての押圧ロール軸受けフォルダー１０３内に配された駆動軸１０８が巻芯の軸と平行になるように配置されているとともに、巻きロール１０７を巻芯の軸芯に向かう方向に外部から押圧する。加圧手段１０５は例えばエアーシリンダーで構成されており、加圧方向が押圧ロール１０４の押圧方向と一致するように一端が固定台１０２に取り付けられている。他端は押圧ロール軸受けフォルダー１０３に固定されている。振動減衰手段１０６は例えば油圧ダンパーなどで構成されており、この押圧方向とピストンロッドの運動方向（減衰力印加方向）とが一致するように一端が固定台１０２に取り付けられている。他端は押圧ロール軸受けフォルダー１０３に固定されている。移動レール１１０を介して押圧ロール１０４が固定台１０２に連結されていることで、押圧ロール１０４は移動レール１１０上を振動方向に沿って自由に移動できるようになっている。このように構成された振動抑制装置の力学的モデルを図１３に示す。 In order to cope with this problem, for example, in the conventional sheet-like material winding device disclosed in Patent Document 1, the vibration of the pressing roll is suppressed by the following vibration suppression device. That is, the vibration suppressing device 101 shown in FIG. 12 includes a fixed base 102, a pressing roll bearing folder 103, a pressing roll 104, a pressing means 105, a vibration damping means 106, and a moving rail 110. The pressure roll 104 is arranged so that a drive shaft 108 disposed in a pressure roll bearing folder 103 as a connecting means is parallel to the axis of the winding core, and the winding roll 107 is directed to the axis of the winding core. Press from the outside in the direction. The pressurizing means 105 is composed of, for example, an air cylinder, and one end is attached to the fixed base 102 so that the pressurizing direction coincides with the pressing direction of the pressing roll 104. The other end is fixed to the press roll bearing folder 103. The vibration damping means 106 is constituted by, for example, a hydraulic damper, and one end is attached to the fixed base 102 so that the pressing direction and the movement direction of the piston rod (damping force application direction) coincide with each other. The other end is fixed to the press roll bearing folder 103. Since the pressing roll 104 is connected to the fixed base 102 via the moving rail 110, the pressing roll 104 can freely move on the moving rail 110 along the vibration direction. FIG. 13 shows a mechanical model of the vibration suppression device configured as described above.
こうした振動抑制装置の構成により、次のような各構成要素の機能が生じる。すなわち、押圧ロールが巻きロール表面の突起を乗り越えることによって、押圧ロールは移動レールに沿う直線方向に変位し、この変位を打ち消すように振動する。この振動を受ける加圧手段には押圧ロールの振動方向と同方向の振動が加えられる。他端が固定台に固定された加圧手段には、押圧ロールの直線変位と同じ量の変位が印加される。その際、例えばエアーシリンダーで構成された加圧手段の空気の抵抗（反発力）が、この印加された変位の方向と反対方向にはたらく。この反発力は、加圧手段に加えられた変位を印加前の状態に戻そうとする復元力として作用し、この復元力は押圧ロールに直接印加される。他方、振動減衰手段にも、押圧ロールの振動方向と同方向の振動がピストンロッドなどの外力受容部に加えられる。そのため、他端が固定台に固定された振動減衰手段には、外力受容部にて押圧ロールの直線変位に伴う速度と同じ速度が印加される。その際、この速度に対応する運動エネルギーの一部が流体で成る減衰部の粘性抵抗によって熱エネルギーに変えられ、残りのエネルギーが復元力（減衰力）として外力受容部に加えられる。この減衰力は外力受容部から押圧ロールに直接印加される。こうした一連の構成要素の運動は、次の運動方程式で表現される。 Such a configuration of the vibration suppressing device causes the following functions of the constituent elements. That is, when the pressing roll gets over the protrusion on the surface of the winding roll, the pressing roll is displaced in a linear direction along the moving rail, and vibrates so as to cancel this displacement. A vibration in the same direction as the vibration direction of the pressing roll is applied to the pressurizing means that receives this vibration. The same amount of displacement as the linear displacement of the pressing roll is applied to the pressing means whose other end is fixed to the fixed base. At that time, for example, the air resistance (repulsive force) of the pressurizing means constituted by an air cylinder acts in a direction opposite to the direction of the applied displacement. This repulsive force acts as a restoring force for returning the displacement applied to the pressurizing means to the state before application, and this restoring force is directly applied to the pressing roll. On the other hand, also in the vibration damping means, vibration in the same direction as the vibration direction of the pressing roll is applied to an external force receiving portion such as a piston rod. Therefore, the same speed as the speed accompanying the linear displacement of the pressing roll is applied to the vibration damping means whose other end is fixed to the fixed base at the external force receiving portion. At that time, a part of the kinetic energy corresponding to this velocity is converted into thermal energy by the viscous resistance of the damping part made of fluid, and the remaining energy is applied to the external force receiving part as a restoring force (damping force). This damping force is directly applied to the pressing roll from the external force receiving portion. The motion of such a series of components is expressed by the following equation of motion.
なお、左辺では、Ｍ：押圧ロールの質量、Ｃ：振動減衰手段の粘性減衰係数、Ｋ：加圧手段のばね定数、ｙ、ｙの時間による１回微分、およびｙの時間による２回微分：押圧ロールの振動方向への直線変位、速度、および加速度をそれぞれ表す。右辺では、ａ：突起の高さの２分の１、ω：押圧ロールの角振動数をそれぞれ表す。 On the left side, M: mass of the pressing roll, C: viscosity damping coefficient of the vibration damping means, K: spring constant of the pressurizing means, one-time differentiation with respect to y and y, and two-time differentiation with respect to y: The linear displacement, the speed, and the acceleration in the vibration direction of the pressing roll are respectively represented. On the right side, a: half the height of the protrusion, and ω: the angular frequency of the pressing roll.
上記の２階線型常微分方程式は、Ｍ、Ｃ、Ｋ、ａ、ω間のある条件の下で時間経過とともに振動しながら減衰して収束するような解が得られる。これにより、押圧ロールの振動を抑えることができる。
しかしながら、近年のフィルム成形速度の高速化およびフィルム広幅化の要請に伴って、押圧ロールの振動現象は顕著となっており、上述のような従来の振動抑制方法ではこの振動現象を十分に抑制することが困難になってきている。すなわち上記の構成の振動抑制装置では、発生する振動と同方向の直線変位および変位速度に応じた、加圧手段による反発力と振動減衰手段による減衰力しか発生させることができない。そのため、運転条件によって即座に振動を抑制したい際にこれらの構成だけでは対応できず、複数のばね定数の異なる加圧手段や粘性減衰係数の異なる振動減衰手段を設ける必要がある。各手段の設置箇所での直線変位、変位速度に応じて異なる反発力や減衰力を発生させることで振動が減衰可能となる。すなわち、従来の振動抑制装置では、複数の加圧手段あるいは複数の振動減衰手段を設けることでしかこれらの力の大きさを調整することができない構成となっている。上述の運転条件として例えば生産調整などでライン速度を変更する場合、ライン速度を上げるためにはより大きなばね定数や粘性減衰係数が必要となる。一方、ライン速度を下げる際にはそれほど大きなばね定数や粘性減衰係数は必要とならない。また、運転条件としてフィルムの厚みを増大させる場合、フィルムの剛性が高まることでしわが発生しにくく折れ曲がりにくい。そのため、それほど大きなばね定数や粘性減衰係数は必要とならない。一方、厚みを減少させる場合、フィルムの剛性が低くなることでしわが発生しやすく折れ曲がって表面に凹凸を形成しやすい。そのため、より大きなばね定数や粘性減衰係数が必要となる。 However, with the recent demand for higher film forming speed and wider film, the vibration phenomenon of the pressing roll has become remarkable, and the conventional vibration suppression method as described above sufficiently suppresses this vibration phenomenon. It has become difficult. That is, in the vibration suppressing device having the above-described configuration, only the repulsive force by the pressurizing unit and the damping force by the vibration damping unit can be generated according to the linear displacement and the displacement speed in the same direction as the generated vibration. For this reason, when it is desired to immediately suppress the vibration depending on the operating conditions, it is not possible to cope with these configurations alone, and it is necessary to provide a plurality of pressurizing means having different spring constants and vibration damping means having different viscosity damping coefficients. The vibration can be attenuated by generating a repulsive force or a damping force that varies depending on the linear displacement and the displacement speed at the place where each means is installed. That is, the conventional vibration suppressing device has a configuration in which the magnitude of these forces can be adjusted only by providing a plurality of pressurizing means or a plurality of vibration damping means. When the line speed is changed, for example, by production adjustment as the above operating condition, a larger spring constant or viscosity damping coefficient is required to increase the line speed. On the other hand, when the line speed is lowered, a very large spring constant and viscous damping coefficient are not required. Moreover, when increasing the thickness of the film as an operating condition, wrinkles are unlikely to occur due to the increased rigidity of the film, and it is difficult to bend. Therefore, a very large spring constant and viscous damping coefficient are not necessary. On the other hand, when the thickness is reduced, wrinkles are likely to occur due to the low rigidity of the film, and it is easy to bend and form irregularities on the surface. Therefore, a larger spring constant and a viscous damping coefficient are required.
更に、この加圧手段はフォルダーを介して押圧ロールに両端部でしか連結されていないため、押圧ロールの軸芯に沿った押圧ロール表面の全長が長くなった際に加圧手段はこの一箇所での変動にしか対応できない。すなわち、加圧手段は、押圧ロール表面の全体に亘って均一に加圧することができない。 Furthermore, since this pressurizing means is connected to the press roll only at both ends via the folder, the pressurizing means is located at this one place when the entire length of the press roll surface along the axial center of the press roll becomes long. Can only handle fluctuations in That is, the pressurizing unit cannot pressurize uniformly over the entire surface of the pressing roll.
また、従来の振動抑制装置は、押圧ロールの駆動軸の軸芯と巻きロールの軸芯とが重力方向同位置に配されている。そのため、押圧ロール自体は、巻きロールに自身の重力を印加することができない構成となっている。 In the conventional vibration suppressing device, the axis of the drive shaft of the pressing roll and the axis of the winding roll are arranged at the same position in the gravity direction. Therefore, the pressing roll itself is configured such that its own gravity cannot be applied to the winding roll.
更に、従来の振動抑制装置は、加圧手段の加圧方向、振動減衰手段の減衰力印加方向が押圧ロールの押圧方向と一致するように構成されている。これにより、例えば減衰力を増大させて振動をより抑制したい場合、振動減衰手段のサイズは、この押圧方向に沿う方向に大きくせざるを得ない。そのため、振動減衰手段が連結された台車を含む振動抑制装置は、押圧ロールの押圧方向へ一方向にだけサイズが増大してしまう。 Furthermore, the conventional vibration suppressing device is configured such that the pressing direction of the pressing unit and the damping force applying direction of the vibration damping unit coincide with the pressing direction of the pressing roll. Thereby, for example, when it is desired to suppress the vibration by increasing the damping force, the size of the vibration attenuating means must be increased in the direction along the pressing direction. Therefore, the size of the vibration suppression device including the carriage to which the vibration damping means is connected increases only in one direction in the pressing direction of the pressing roll.
本発明は上記事情に鑑みてなされたものであり、加圧手段や振動減衰手段の反発力や減衰力が調整可能であり、押圧ロールが巻きロールを押圧でき、更に設置スペースを抑えることができる振動抑制装置を提供することを目的とする。 The present invention has been made in view of the above circumstances, the repulsive force and damping force of the pressurizing means and the vibration damping means can be adjusted, the pressing roll can press the winding roll, and the installation space can be further reduced. An object is to provide a vibration suppressing device.
本発明の一態様の振動抑制装置は、シート状物が巻き取られる巻きロールに対向配置され、第２および第３の連結部を有する固定台と、第１の連結部を有する第１の部材と、第１の部材と交差する方向に第１の部材から延び、第４および第５の連結部を有する第２の部材と、を有し、第１の連結部を介して固定台と連結された連結手段であって、第１、第４および第５の連結部のそれぞれの位置が変更可能な連結手段と、第１の連結部と離間して配された駆動軸を有し、駆動軸を介して連結手段の第１の部材と連結された押圧ロールであって、駆動軸の軸芯が巻きロールの軸芯よりも重力方向上側に位置して押圧ロールが巻きロールを押圧可能であり、押圧ロールが駆動軸周りに回転するとともに駆動軸が第１の連結部を支軸として揺動する、押圧ロールと、第１の連結部と離間して配された一端および他端を有し、一端が第４の連結部を介して連結手段の第２の部材と連結されているとともに、他端が第２の連結部を介して固定台の第２の連結部と連結されている加圧手段であって、加圧手段の一端と他端とを結ぶ直線が連結手段の第２の部材と交差する方向にあり、第１の連結部と加圧手段の一端とを結ぶ直線と交差する方向に反発力を発生させて押圧ロールを加圧する加圧手段と、第１の連結部と離間して配された一端および他端を有し、一端が第５の連結部を介して連結手段の第２の部材と連結されているとともに、他端が第３の連結部を介して固定台の第３の連結部と連結されている振動減衰手段であって、振動減衰手段の一端と他端とを結ぶ直線が連結手段の第２の部材と交差する方向にあり、第１の連結部と振動減衰手段の一端とを結ぶ直線と交差する方向に減衰力を発生させて押圧ロールの振動を減衰させる振動減衰手段と、を有する。 The vibration suppressing device according to one aspect of the present invention is arranged to face a winding roll on which a sheet-like material is wound, and includes a fixing base having second and third connecting portions, and a first member having a first connecting portion. And a second member extending from the first member in a direction intersecting with the first member and having fourth and fifth connecting portions, and connected to the fixed base via the first connecting portion. A connecting means that can change the positions of the first, fourth, and fifth connecting portions, and a drive shaft that is spaced apart from the first connecting portion. A pressing roll connected to the first member of the connecting means via a shaft, wherein the axis of the drive shaft is positioned above the axis of the winding roll in the direction of gravity and the pressing roll can press the winding roll. Yes, the pressing roll rotates around the drive shaft and the drive shaft swings with the first connecting portion as a support shaft. The pressing roll has one end and the other end spaced apart from the first connecting portion, and one end is connected to the second member of the connecting means via the fourth connecting portion, and the other end. Is a pressurizing means connected to the second connecting part of the fixed base via the second connecting part, and a straight line connecting one end and the other end of the pressurizing means is connected to the second member of the connecting means. A pressurizing means that presses the pressure roll by generating a repulsive force in a direction intersecting the straight line connecting the first connecting portion and one end of the pressurizing means, and spaced apart from the first connecting portion; And the other end is connected to the second member of the connecting means via the fifth connecting portion, and the other end is connected to the fixing base via the third connecting portion. A vibration attenuating means connected to the third connecting portion, wherein a straight line connecting one end and the other end of the vibration attenuating means is the second portion of the connecting means. And it is in the direction intersecting, has a vibration damping means for damping vibrations of the first to generate a damping force in a direction crossing a line connecting the one end of the connecting portion and the vibration damping means pressing roll, the.
本発明に係る振動抑制装置によれば、固定台と連結される連結手段の第１の連結部の位置、加圧手段と連結される第４の連結部の位置、振動減衰手段と連結される第５の連結部の位置のそれぞれが変更可能である。これにより、複数の加圧手段または複数の振動減衰手段を設けなくても連結部の位置を変えるだけで、この位置に起因する加圧手段または振動減衰手段の第１の連結部周りのモーメントを調整できる。これにより、複数の加圧手段、振動減衰手段を設けずに反発力、減衰力に起因する各モーメントを調節できる。また、加圧手段取り付け位置である連結手段上の第４の連結部の位置が変更可能となっているため、一箇所だけでなく複数箇所で連結手段を介して押圧ロールを加圧できる。これにより、加圧手段は押圧ロール表面の全体に亘って均一に加圧することができる構成となっている。 According to the vibration suppressing device of the present invention, the position of the first connecting portion of the connecting means connected to the fixed base, the position of the fourth connecting portion connected to the pressurizing means, and the vibration damping means are connected. Each position of the fifth connecting portion can be changed. Thus, the moment around the first connecting part of the pressurizing means or the vibration damping means due to this position can be changed by simply changing the position of the connecting part without providing a plurality of pressurizing means or a plurality of vibration attenuating means. Can be adjusted. Thereby, each moment resulting from repulsive force and damping force can be adjusted without providing a plurality of pressurizing means and vibration damping means. Moreover, since the position of the 4th connection part on the connection means which is a pressurization means attachment position can be changed, a press roll can be pressurized via a connection means not only in one place but in multiple places. Thereby, the pressurizing means is configured to be able to pressurize uniformly over the entire surface of the pressing roll.
また、本発明に係る振動抑制装置によれば、押圧ロールの駆動軸の軸芯が巻きロールの軸芯よりも重力方向上側に位置して押圧ロールが巻きロールを押圧可能である。これにより、押圧ロールは巻きロールと重力方向同位置ではなく上側に配されるため、押圧ロールは巻きロールに対して自身の重力を印加できる。 Further, according to the vibration suppressing device of the present invention, the axis of the drive shaft of the pressing roll is positioned above the axis of the winding roll in the gravity direction so that the pressing roll can press the winding roll. Thereby, since a press roll is distribute | arranged not to the winding roll but the same position in the gravity direction, the press roll can apply own gravity with respect to a winding roll.
更に、本発明に係る振動抑制装置によれば、連結手段が第１の連結部を有する第１の部材と、第１の部材と交差する方向に第１の部材から延びる第２の部材と、を有し、第１の連結部を介して固定台と連結されている。更に、加圧手段の一端と他端とを結ぶ直線が連結手段の第２の部材と交差する方向にあるとともに、振動減衰手段の一端と他端とを結ぶ直線が連結手段の第２の部材と交差する方向にある。つまり、加圧手段と振動減衰手段を第２の部材に対して倒立させて配置している。そのため、減衰力を増大させて振動をより抑制したい場合でも、加圧手段および振動減衰手段は、連結手段における第１の部材と第２の部材との間で形成される空間内に配される。よって、従来の連結手段外に加圧手段および振動減衰手段が配される形態に比し、振動抑制装置の設置スペースを抑えることができる。 Furthermore, according to the vibration suppressing device according to the present invention, the first member having the first connecting portion of the connecting means, the second member extending from the first member in the direction intersecting the first member, And is connected to the fixed base via the first connecting portion. Further, the straight line connecting one end and the other end of the pressurizing means is in a direction intersecting the second member of the connecting means, and the straight line connecting one end and the other end of the vibration damping means is the second member of the connecting means. In the direction that intersects In other words, the pressurizing unit and the vibration damping unit are arranged upside down with respect to the second member. Therefore, even when it is desired to suppress the vibration more by increasing the damping force, the pressurizing means and the vibration attenuating means are arranged in the space formed between the first member and the second member in the connecting means. . Therefore, the installation space of the vibration suppressing device can be reduced as compared with the conventional configuration in which the pressurizing means and the vibration damping means are arranged outside the connecting means.
従って、加圧手段や振動減衰手段の反発力や減衰力が調整可能であり、押圧ロールが巻きロールを押圧でき、更に設置スペースを抑えることができる振動抑制装置を提供することができる。 Therefore, it is possible to provide a vibration suppressing device in which the repulsive force and damping force of the pressurizing means and the vibration damping means can be adjusted, the pressing roll can press the winding roll, and the installation space can be reduced.
以下、本発明を実施するための最良の形態について図面を参照して説明する。
（第１の実施形態）
図１に本発明の第１の実施形態に係る振動抑制装置の概念図を示す。図２に図１のＡ箇所の拡大図を示す。図３に図１に表す振動抑制装置の力学モデルを示す。振動抑制装置１は、固定台２と、連結手段３と、押圧ロール４と、加圧手段５と、振動減衰手段６とで構成されている。
The best mode for carrying out the present invention will be described below with reference to the drawings.
(First embodiment)
FIG. 1 is a conceptual diagram of a vibration suppressing device according to the first embodiment of the present invention. FIG. 2 shows an enlarged view of a portion A in FIG. FIG. 3 shows a dynamic model of the vibration suppressing device shown in FIG. The vibration suppressing device 1 includes a fixed base 2, a connecting means 3, a pressing roll 4, a pressing means 5, and a vibration damping means 6.
固定台２は、シート状物が巻き取られる巻きロール７に対向配置されるように構成されているとともに、第２の連結部１０および第３の連結部１１を有する。第２の連結部１０では固定台２と加圧手段５の一端とが連結されている。第３の連結部１１では固定台２と振動減衰手段６の一端とが連結されている。更に、固定台２の内側表面で定められる内側空間内には、連結手段３、押圧ロール４、加圧手段５、および振動減衰手段６が配されている。なお、図１に示す固定台２は略Ｕ字状を呈しているが、これに限定されるものではない。すなわち、連結手段３、押圧ロール４、加圧手段５、および振動減衰手段６による振動抑制効果が維持できるような任意の形態を選択することができる。 The fixed base 2 is configured to be opposed to the winding roll 7 on which the sheet-like material is wound, and has a second connecting portion 10 and a third connecting portion 11. In the second connecting portion 10, the fixed base 2 and one end of the pressurizing means 5 are connected. In the third connecting portion 11, the fixed base 2 and one end of the vibration damping means 6 are connected. Further, in the inner space defined by the inner surface of the fixed base 2, a connecting means 3, a pressing roll 4, a pressing means 5, and a vibration damping means 6 are arranged. In addition, although the fixing stand 2 shown in FIG. 1 is exhibiting substantially U shape, it is not limited to this. That is, it is possible to select any form that can maintain the vibration suppressing effect of the connecting means 3, the pressing roll 4, the pressing means 5, and the vibration damping means 6.
連結手段３は、押圧ロール４の駆動軸８と連結されているとともに第１の連結部９を介して固定台２と連結されている。更に、連結手段３は、第１の連結部９を有する第１の部材１４と、第４および第５の連結部１２、１３を有する第２の部材１５とを有する。第２の部材１５は、第１の部材１４と交差する方向に第１の部材１４から延びている。図１に示す第１の部材１４と第２の部材１５とは直交するように示されているが、この形態に限定されることはなく、第１の部材１４と第２の部材１５とが交差する構成であればよい。このように構成された連結手段３は、押圧ロール４の駆動軸８の軸芯１６の方向と直交する断面形状が略Ｕ字状である。また、連結手段３は第４の連結部１２を介して加圧手段５の一端と連結されているとともに、第５の連結部１３を介して振動減衰手段６の一端と連結されている。なお、第１の連結部９から第５の連結部１３のすべては回転軸を有し、この回転軸周りに自由に回転可能である。 The connecting means 3 is connected to the drive shaft 8 of the pressing roll 4 and is connected to the fixed base 2 via the first connecting portion 9. Further, the connecting means 3 includes a first member 14 having a first connecting portion 9 and a second member 15 having fourth and fifth connecting portions 12 and 13. The second member 15 extends from the first member 14 in a direction intersecting with the first member 14. Although the 1st member 14 and the 2nd member 15 which are shown in FIG. 1 are shown so as to be orthogonal, it is not limited to this form, The 1st member 14 and the 2nd member 15 are Any configuration that intersects may be used. The connecting means 3 configured in this way has a substantially U-shaped cross section perpendicular to the direction of the axis 16 of the drive shaft 8 of the pressing roll 4. The connecting means 3 is connected to one end of the pressurizing means 5 via the fourth connecting portion 12 and is connected to one end of the vibration damping means 6 via the fifth connecting portion 13. Note that all of the first connecting portion 9 to the fifth connecting portion 13 have a rotating shaft and can freely rotate around the rotating shaft.
また、第１、第４および第５の連結部９、１２、１３の各々は、連結手段３に複数個設けられていてもよい（図１および図２参照）。すなわち、これらの連結部９、１２、１３のそれぞれの位置は変更可能となっている。これにより、複数の加圧手段５あるいは複数の振動減衰手段６を設けなくても連結部９、１２、１３の位置を変えるだけで、この位置に起因する加圧手段５または振動減衰手段６の第１の連結部９周りのモーメントを調整できる。つまり、複数の加圧手段５、振動減衰手段６を設けずに反発力、減衰力に起因する各モーメントを調節できる。 Further, a plurality of first, fourth and fifth connecting portions 9, 12, 13 may be provided in the connecting means 3 (see FIGS. 1 and 2). That is, the positions of these connecting portions 9, 12, and 13 can be changed. Thus, even if the plurality of pressurizing means 5 or the plurality of vibration damping means 6 are not provided, the positions of the pressurizing means 5 or the vibration damping means 6 caused by this position can be changed by simply changing the positions of the connecting portions 9, 12, and 13. The moment around the first connecting portion 9 can be adjusted. That is, each moment resulting from the repulsive force and the damping force can be adjusted without providing the plurality of pressurizing means 5 and vibration damping means 6.
更に、加圧手段５取り付け位置である連結手段３上の第４の連結部１２の位置が変更可能となっているため、一箇所だけでなく複数箇所で連結手段３を介して押圧ロール４を加圧できる。これにより、加圧手段５は押圧ロール４表面の全体に亘って均一に加圧することができる構成となっている。 Furthermore, since the position of the 4th connection part 12 on the connection means 3 which is an attachment position of the pressurization means 5 can be changed, the press roll 4 can be moved via the connection means 3 not only at one place but at multiple places. Can be pressurized. Thereby, the pressurization means 5 becomes a structure which can pressurize uniformly over the whole press roll 4 surface.
また、振動減衰手段６取り付け位置である連結手段３上の第５の連結部１３の位置が変更可能となっているため、一箇所だけでなく複数箇所で連結手段３を介して押圧ロール４の振動を減衰できる。これにより、振動減衰手段６は押圧ロール４表面の全体に亘って均一に減衰力を印加することができる構成となっている。 Moreover, since the position of the 5th connection part 13 on the connection means 3 which is a vibration damping means 6 attachment position can be changed, not only one place but the multiple places of the press roll 4 via the connection means 3 is possible. Vibration can be damped. Thereby, the vibration damping means 6 is configured to apply a damping force uniformly over the entire surface of the pressing roll 4.
押圧ロール４は、第１の連結部９と離間して配された駆動軸８を有し、駆動軸８を介して連結手段３の第１の部材１４と連結されている。また、押圧ロール４は駆動軸８周りに回転するとともに駆動軸８は第１の連結部９を支軸として揺動する。更に、図１に示すように、駆動軸８の軸芯１６が巻きロール７の軸芯よりも重力方向上側に位置して押圧ロール４が巻きロール７を押圧可能である。これにより、押圧ロール４は巻きロール７と重力方向同位置ではなく上側に配されるため、押圧ロールは巻きロールに対して自身の重力を印加できる。また、押圧ロール４の巻きロール７への重力印加の大きさを変更したい場合には、図２に示すように、第１の連結部９の位置を連結手段３上で変えることで対応できる。 The pressing roll 4 has a drive shaft 8 that is spaced apart from the first connecting portion 9, and is connected to the first member 14 of the connecting means 3 via the drive shaft 8. Further, the pressing roll 4 rotates around the drive shaft 8 and the drive shaft 8 swings with the first connecting portion 9 as a support shaft. Furthermore, as shown in FIG. 1, the shaft 16 of the drive shaft 8 is positioned above the shaft of the winding roll 7 in the direction of gravity, and the pressing roll 4 can press the winding roll 7. Thereby, since the press roll 4 is distribute | arranged rather than the winding roll 7 and the gravity position same position, a press roll can apply own gravity with respect to a winding roll. Further, when it is desired to change the magnitude of the gravity applied to the winding roll 7 of the pressing roll 4, it can be dealt with by changing the position of the first connecting portion 9 on the connecting means 3, as shown in FIG.
加圧手段５は、第１の連結部９と離間して配された一端および他端を有する。この一端は第４の連結部１２を介して連結手段３の第２の部材１５と連結されているとともに、この他端は第２の連結部１０を介して固定台２の第２の連結部１０と連結されている。更に、加圧手段５の一端と他端とを結ぶ直線は連結手段３の第２の部材１５と交差する方向にある。そして、加圧手段５は、第１の連結部９と加圧手段５のこの一端とを結ぶ直線と交差する方向にその内部に封入された流体により反発力を発生させて押圧ロール４を加圧する。また、加圧手段５の一端と他端とを結ぶ直線の方向は押圧ロール４の振動方向と交差する方向に限らず、第１の連結部９周りにこの一端と第１の連結部９との距離および反発力に起因するモーメントを生じさせる形態であれば、押圧ロール４の振動方向と平行な方向であってもよい。なお、加圧手段５は、固定台２と連結手段３との間に配された少なくとも１つのエアーシリンダーで構成されていることが好ましい。 The pressurizing means 5 has one end and the other end that are spaced apart from the first connecting portion 9. This one end is connected to the second member 15 of the connecting means 3 via the fourth connecting portion 12, and the other end is connected to the second connecting portion of the fixed base 2 via the second connecting portion 10. 10 is connected. Furthermore, a straight line connecting one end and the other end of the pressurizing means 5 is in a direction intersecting with the second member 15 of the connecting means 3. The pressurizing means 5 applies a pressing roll 4 by generating a repulsive force by the fluid enclosed therein in a direction crossing a straight line connecting the first connecting portion 9 and the one end of the pressurizing means 5. Press. Further, the direction of the straight line connecting one end and the other end of the pressurizing means 5 is not limited to the direction intersecting the vibration direction of the pressing roll 4, and the one end and the first connecting portion 9 are arranged around the first connecting portion 9. The direction parallel to the vibration direction of the pressing roll 4 may be used as long as the moment caused by the distance and the repulsive force is generated. The pressurizing means 5 is preferably composed of at least one air cylinder disposed between the fixed base 2 and the connecting means 3.
振動減衰手段６は、第１の連結部９と離間して配された一端および他端を有する。この一端は第５の連結部１３を介して連結手段３の第２の部材１５と連結されているとともに、他端は第３の連結部１１を介して固定台２の第３の連結部１１と連結されている。更に、振動減衰手段６の一端と他端とを結ぶ直線は連結手段３の第２の部材１５と交差する方向にある。そして、振動減衰手段６は、第１の連結部９と振動減衰手段６の一端とを結ぶ直線と交差する方向に減衰力を発生させて押圧ロール４の振動を減衰させる。このように構成された振動減衰手段６は、その内部に封入された流体の粘性抵抗によってこの一端と第１の連結部９との距離および減衰力に起因する第１の連結部９周りのモーメントが加圧手段５によるモーメントを打ち消す方向に作用して押圧ロール４の振動を減衰させる。また、振動減衰手段６の一端と他端とを結ぶ直線の方向は押圧ロール４の振動方向と交差する方向に限らず、押圧ロール４の振動を減衰させる形態であれば、押圧ロール４の振動方向と平行な方向であってもよい。 The vibration damping means 6 has one end and the other end that are spaced apart from the first connecting portion 9. This one end is connected to the second member 15 of the connecting means 3 via the fifth connecting portion 13, and the other end is connected to the third connecting portion 11 of the fixing base 2 via the third connecting portion 11. It is connected with. Further, a straight line connecting one end and the other end of the vibration damping means 6 is in a direction intersecting with the second member 15 of the connecting means 3. Then, the vibration damping means 6 attenuates the vibration of the pressing roll 4 by generating a damping force in a direction intersecting with a straight line connecting the first connecting portion 9 and one end of the vibration damping means 6. The vibration damping means 6 configured as described above has a moment around the first connecting portion 9 caused by the distance between the one end and the first connecting portion 9 and the damping force due to the viscous resistance of the fluid sealed therein. Acts in the direction of canceling out the moment by the pressurizing means 5 and attenuates the vibration of the pressing roll 4. Further, the direction of the straight line connecting one end and the other end of the vibration damping means 6 is not limited to the direction intersecting with the vibration direction of the pressing roll 4. The direction may be parallel to the direction.
本実施形態における振動減衰手段６のこの一端と加圧手段５の上記一端とは、固定台２上の同一平面上では無い位置に配されている。一方、振動減衰手段６のこの他端と加圧手段５の上記他端とは、連結手段３の同一平面上では無い位置に配されている。これにより、振動減衰手段６の一端と他端とを結ぶ直線は、加圧手段５の一端と他端とを結ぶ直線に対してねじれの位置にある。 In the present embodiment, the one end of the vibration damping means 6 and the one end of the pressurizing means 5 are arranged at positions that are not on the same plane on the fixed base 2. On the other hand, the other end of the vibration damping means 6 and the other end of the pressurizing means 5 are arranged at positions that are not on the same plane of the connecting means 3. Thus, the straight line connecting one end and the other end of the vibration damping means 6 is in a twisted position with respect to the straight line connecting the one end and the other end of the pressurizing means 5.
更に、振動減衰手段６の上記一端と第１の連結部９との距離は、加圧手段５の上記一端と第１の連結部９との距離よりも大きい。すなわち、図２に示すように、振動減衰手段６と第１の連結部９との間の距離ｌ4は、第１の連結部９と押圧ロール４の駆動軸８との間の距離ｌ2よりも大きい。なお、振動減衰手段６は、固定台２と連結手段３との間に配された少なくとも１つの油圧ダンパーで構成されているのが好適である。 Further, the distance between the one end of the vibration damping means 6 and the first connecting portion 9 is larger than the distance between the one end of the pressurizing means 5 and the first connecting portion 9. That is, as shown in FIG. 2, the distance l 4 between the vibration damping means 6 and the first connecting portion 9, the distance l 2 between the drive shaft 8 of the first connecting portion 9 and the pressing roll 4 Bigger than. The vibration damping means 6 is preferably composed of at least one hydraulic damper disposed between the fixed base 2 and the connecting means 3.
また、伸縮する際に減衰力を発生させる振動減衰手段６において、第２の部材１５と連結された一端と固定台２と連結された他端とが互いに離れるように伸びる際の粘性減衰係数は、この一端とこの他端とが互いに近づくように縮む際の粘性減衰係数よりも小さいことが好ましい。すなわち、押圧ロール４が巻きロール７から離れる方向に変位する場合には粘性減衰係数が大きくなるように設定することにより振動の振幅を小さく抑制し、反対に、押圧ロール４が巻きロール７に近づく方向に変位する場合には減衰係数が小さくなるように設定されている。圧縮方向の粘性減衰係数に対する伸張方向の粘性減衰係数の比は、０．０１以上０．１未満であることが好適である。これにより、押圧ロール４が極めて短時間で巻きロール７のフィルム表面に変位するようにしておけば、押圧ロール４が巻きロール７に接触する時間がより長くなり、良好な巻き姿を実現することが可能となる。圧縮方向と伸張方向で減衰係数をそれぞれ別個に設定できる振動減衰手段としては、例えば、ＥＮＩＤＩＮＥ社の油圧ダンパーＡＤＡ５００シリーズ、ＡＤＡ７００シリーズなどが用いられる。 In addition, in the vibration damping means 6 that generates a damping force when expanding and contracting, the viscous damping coefficient when the one end connected to the second member 15 and the other end connected to the fixed base 2 extend away from each other is It is preferable that the one end and the other end be smaller than the viscous damping coefficient when contracting so as to approach each other. That is, when the pressing roll 4 is displaced in a direction away from the winding roll 7, the amplitude of vibration is suppressed to be small by setting the viscosity damping coefficient to be large, and conversely, the pressing roll 4 approaches the winding roll 7. In the case of displacement in the direction, the attenuation coefficient is set to be small. The ratio of the viscous damping coefficient in the extension direction to the viscous damping coefficient in the compression direction is preferably 0.01 or more and less than 0.1. Thus, if the pressing roll 4 is displaced to the film surface of the winding roll 7 in a very short time, the time for the pressing roll 4 to contact the winding roll 7 becomes longer and a good winding shape is realized. Is possible. For example, hydraulic dampers ADA500 series and ADA700 series manufactured by ENIDINE are used as the vibration damping means capable of setting damping coefficients separately in the compression direction and the extension direction.
このように構成された振動減衰手段６を有する振動抑制装置１は、連結手段３が第１の連結部９を有する第１の部材１４と、第１の部材１４と交差する方向に第１の部材１４から延びる第２の部材１５とを有する。更に、連結手段３は第１の連結部９を介して固定台２と連結されている。更に、加圧手段５の一端と他端とを結ぶ直線が連結手段３の第２の部材１５と交差する方向にあるとともに、振動減衰手段６の一端と他端とを結ぶ直線が連結手段３の第２の部材１５と交差する方向にある。つまり、加圧手段５と振動減衰手段６を第２の部材１５に対して倒立させて配置している。そのため、減衰力を増大させて振動をより抑制したい場合でも、加圧手段５および振動減衰手段６は、連結手段３における第１の部材１４と第２の部材１５との間で形成される空間内に配される。これにより、振動抑制装置１は、図１中矢印Ｂで示す振動抑制装置１の奥行き方向への長さが抑えられる。よって、従来の連結手段外に加圧手段および振動減衰手段が配される形態に比し、振動抑制装置の設置スペースを抑えることができる。 The vibration suppressing device 1 having the vibration damping means 6 configured as described above includes the first member 14 in which the connecting means 3 has the first connecting portion 9 and the first member 14 in the direction intersecting the first member 14. And a second member 15 extending from the member 14. Further, the connecting means 3 is connected to the fixed base 2 via the first connecting portion 9. Further, a straight line connecting one end and the other end of the pressurizing means 5 is in a direction intersecting the second member 15 of the connecting means 3, and a straight line connecting one end and the other end of the vibration damping means 6 is the connecting means 3. In the direction intersecting with the second member 15. That is, the pressurizing means 5 and the vibration damping means 6 are arranged upside down with respect to the second member 15. Therefore, even when the damping force is increased to further suppress the vibration, the pressurizing means 5 and the vibration attenuating means 6 are spaces formed between the first member 14 and the second member 15 in the connecting means 3. Arranged inside. Thereby, as for the vibration suppression apparatus 1, the length to the depth direction of the vibration suppression apparatus 1 shown by the arrow B in FIG. 1 is suppressed. Therefore, the installation space of the vibration suppressing device can be reduced as compared with the conventional configuration in which the pressurizing means and the vibration damping means are arranged outside the connecting means.
次に、上記のように構成された本実施形態に係る振動抑制装置１の各構成要素の作用を詳述する。押圧ロール４が巻きロール７表面の突起部を乗り越えることによって押圧ロール４には振動が生じ、押圧ロール４は第１の連結部９を中心にθの角度でもって揺動する。この場合、加圧手段５には押圧ロール４の揺動変位（ｌ2θ）によって生じた第２の連結部１０と第４の連結部１２との間の変位（Ｘ1）が印加される。これにより変位（Ｘ1）と加圧手段５のばね定数（Ｋ）に比例する復元力としての反発力（＝Ｋ×Ｘ1）が発生し、この反発力は連結手段３を介して押圧ロール４に印加される。この反発力は連結部間の距離（ｌ2、ｌ3）の比率によってその大きさを変えることもできる。また、振動減衰手段６には押圧ロール４の揺動によって生じた第３の連結部１１と第５の連結部１３との間の変位（Ｘ2＝ｌ4θ）に伴う速度（dＸ2/dt）が印加される。これにより変位速度（dＸ2/dt）と振動減衰手段６の粘性減衰係数（Ｃ）に応じた減衰力（＝Ｃ×dＸ2/dt）が発生し、この減衰力は連結手段３を介して押圧ロール４に印加されることにより振動が抑制される。減衰力は連結部間の距離（ｌ2、ｌ4）の比率によってその大きさを変えることもできる。この場合、上述のように、第１から第５の連結部９から１３をそれぞれ複数箇所設けることで、押圧ロール４の取り付け位置、加圧手段５の取り付け位置および振動減衰手段６の取り付け位置を変更可能することもできる。これらの手段の取り付け位置を変更することで各連結部間の距離（ｌ2、ｌ3、ｌ4）が変えられ、加圧手段５による反発力および振動減衰手段６による減衰力が容易に変更可能となる。例えば、加圧手段５を第１の連結部９からより離れた位置に取り付けることで、加圧手段５のばね定数Ｋを変更することなく、より大きな反発力が得ることができる。
（第２の実施形態）
図４に本発明の第２の実施形態に係る振動抑制装置の概念図を示す。図５に図４のＣ箇所の拡大図を示す。図６に図４に表す振動抑制装置の力学モデルを示す。本実施形態は、第１の実施形態に対して連結手段３の断面形状が略Ｌ字状である点が異なる。更に、第４の連結部１２に連結された加圧手段５の一端と第５の連結部１３に連結された振動減衰手段６の一端とが固定台２の同一平面上に並列に配されている点が異なる。また、第２の連結部１０に連結された加圧手段５の他端と第３の連結部１１に連結された振動減衰手段６の他端とが連結手段３の同一平面上に並列に配されている点が異なっている。以上のような相違点のみが第１の実施形態と異なる本実施形態の構成においては、第１の実施形態と同様の作用効果を奏することができる。
Next, the operation of each component of the vibration suppression device 1 according to this embodiment configured as described above will be described in detail. When the pressing roll 4 gets over the protrusion on the surface of the winding roll 7, the pressing roll 4 is vibrated, and the pressing roll 4 swings around the first connecting portion 9 at an angle θ. In this case, the displacement (X 1 ) between the second connecting portion 10 and the fourth connecting portion 12 caused by the swinging displacement (l 2 θ) of the pressing roll 4 is applied to the pressing means 5. . As a result, a repulsive force (= K × X 1 ) as a restoring force proportional to the displacement (X 1 ) and the spring constant (K) of the pressurizing means 5 is generated. 4 is applied. The magnitude of the repulsive force can be changed by the ratio of the distances (l 2 , l 3 ) between the connecting portions. The speed associated with the displacement between the third connecting portion 11 caused by the swinging of the press roll 4 is a vibration damping means 6 and the fifth connection portion 13 of the (X 2 = l 4 θ) (dX 2 / dt) is applied. As a result, a damping force (= C × dX 2 / dt) corresponding to the displacement speed (dX 2 / dt) and the viscous damping coefficient (C) of the vibration damping means 6 is generated, and this damping force is transmitted via the connecting means 3. Vibration is suppressed by being applied to the pressing roll 4. The magnitude of the damping force can be changed according to the ratio of the distances (l 2 , l 4 ) between the connecting portions. In this case, as described above, by providing a plurality of first to fifth connecting portions 9 to 13 respectively, the attachment position of the pressing roll 4, the attachment position of the pressurizing means 5, and the attachment position of the vibration damping means 6 can be adjusted. It can also be changed. By changing the mounting position of these means, the distances (l 2 , l 3 , l 4 ) between the connecting portions can be changed, and the repulsive force by the pressurizing means 5 and the damping force by the vibration damping means 6 can be easily changed. It becomes possible. For example, a larger repulsive force can be obtained without changing the spring constant K of the pressurizing means 5 by attaching the pressurizing means 5 to a position further away from the first connecting portion 9.
(Second Embodiment)
FIG. 4 is a conceptual diagram of a vibration suppressing device according to the second embodiment of the present invention. FIG. 5 shows an enlarged view of a portion C in FIG. FIG. 6 shows a dynamic model of the vibration suppressing device shown in FIG. This embodiment is different from the first embodiment in that the cross-sectional shape of the connecting means 3 is substantially L-shaped. Further, one end of the pressurizing means 5 connected to the fourth connecting portion 12 and one end of the vibration damping means 6 connected to the fifth connecting portion 13 are arranged in parallel on the same plane of the fixed base 2. Is different. Further, the other end of the pressurizing means 5 connected to the second connecting portion 10 and the other end of the vibration damping means 6 connected to the third connecting portion 11 are arranged in parallel on the same plane of the connecting means 3. Is different. In the configuration of the present embodiment, which is different from the first embodiment only in the differences as described above, the same operational effects as those of the first embodiment can be achieved.
（第１の実施例）
本発明の実施形態を適用した実施例の効果を検証するために、巻取りフィルム上の突起を図７に示すようにモデル化し、図３および図６の力学モデルから運動方程式（数２、数３）を導出し振動減衰性能の評価を行なった。なお、図７に示すＬRは巻きロールの半径、Ｌ1は突起部の距離（巻きロールの弧上長さ）、θ1はＬ1に対する中心角、Ｌ2は巻きロールの円周の半分からＬ1を引いた長さ、θ2はＬ2に対する中心角をそれぞれ示す。また、数２は突起部への乗り上げ時、すなわち強制振動の場合の運動方程式を示し、数３は巻きロールから離れているとき、すなわち自由振動の場合の運動方程式を示す。計算に用いたパラメータは以下の通りである。なお、本発明の範囲は以降に詳述する実施例に限定されるものではない。
(First embodiment)
In order to verify the effect of the example to which the embodiment of the present invention is applied, the protrusion on the winding film is modeled as shown in FIG. 7, and the equation of motion (Equation 2, Equation 2) is calculated from the dynamic model shown in FIGS. 3) was derived and vibration damping performance was evaluated. In FIG. 7, L R is the radius of the winding roll, L 1 is the distance of the protrusion (the length on the arc of the winding roll), θ 1 is the central angle with respect to L 1 , and L 2 is half the circumference of the winding roll. A length obtained by subtracting L 1 from θ 2 indicates a central angle with respect to L 2 . Equation 2 represents the equation of motion when riding on the protrusion, that is, forced vibration, and Equation 3 represents the equation of motion when away from the winding roll, that is, free vibration. The parameters used for the calculation are as follows. Note that the scope of the present invention is not limited to the examples described in detail below.
突起部高さ（２ａ）：１ｍｍ
突起部長さ（Ｌ）：５０ｍｍ
巻取り速度（ν）：６００ｍ／分
ばね定数（Ｋ）：５９５３４Ｎ／ｍ
圧縮時の粘性減衰係数（Ｃ）：１００００Ｎ・ｓ／ｍ
伸張時の粘性減衰係数（Ｃ）：５００Ｎ・ｓ／ｍ
押圧ロールの重量（Ｍ）：４００ｋｇ
連結手段３の連結部間の長さ
ｌ2：０．０８ｍ
ｌ3：０．０７５ｍ
ｌ4：０．２ｍ
Projection height (2a): 1 mm
Projection length (L): 50 mm
Winding speed (ν): 600 m / min Spring constant (K): 59534 N / m
Viscous damping coefficient during compression (C): 10000 N · s / m
Viscous damping coefficient during extension (C): 500 N · s / m
Pressure roll weight (M): 400 kg
Length between connecting portions of connecting means 3 l 2 : 0.08 m
l 3 : 0.075m
l 4 : 0.2m
数２におけるωは突起部形状の角振動数を示し、数４で表される。 In Equation 2, ω represents the angular frequency of the protrusion shape, and is represented by Equation 4.
これらの計算結果を図８に示す。
（第１の比較例）
本発明に係る第１の実施例との比較例として、図１３の力学モデルから運動方程式（数２、数３）を導出し振動減衰性能の評価を行なった。計算に用いたパラメータとしては、圧縮時と伸張時との粘性減衰係数をいずれも同じ値である１００００Ｎ・ｓ／ｍにした以外は、第１の実施例と同様の値を用いた。これらの計算結果を図９に示す。
The calculation results are shown in FIG.
(First comparative example)
As a comparative example with the first embodiment according to the present invention, the equation of motion (Equation 2 and Equation 3) was derived from the dynamic model of FIG. 13 and the vibration damping performance was evaluated. As parameters used for the calculation, the same values as those in the first example were used except that the viscous damping coefficient at the time of compression and at the time of expansion was set to 10000 N · s / m which is the same value. These calculation results are shown in FIG.
図８および図９より明らかな通り、同一の突起の高さおよび突起の長さに対して、本発明の実施例に係るバウンド抑制方法は、比較例のバウンド抑制方法よりも巻きロールに接触している時間が格段に長くなることが判る。
（第２の実施例）
本発明の実施形態を適用した実施例の効果を検証するために、第１の実施例と同様に巻取りフィルム上の突起を図７に示すようにモデル化し、図３および図６の力学モデルから運動方程式（数５、数６）を導出し振動減衰性能の評価を行なった。数５は突起部への乗り上げ時、すなわち強制振動の場合の運動方程式を示し、数６は巻きロールから離れているとき、すなわち自由振動の場合の運動方程式を示す。計算に用いたパラメータは以下の通りである。
As is clear from FIGS. 8 and 9, for the same protrusion height and protrusion length, the bounce suppressing method according to the example of the present invention is more in contact with the winding roll than the bounce suppressing method of the comparative example. It can be seen that the time is significantly longer.
(Second embodiment)
In order to verify the effect of the example to which the embodiment of the present invention is applied, the protrusion on the winding film is modeled as shown in FIG. 7 as in the first example, and the dynamic model of FIGS. Equations of motion (Equations 5 and 6) were derived from the above and vibration damping performance was evaluated. Equation 5 shows the equation of motion when riding on the projection, that is, in the case of forced vibration, and Equation 6 shows the equation of motion when away from the winding roll, that is, in the case of free vibration. The parameters used for the calculation are as follows.
突起部高さ（２ａ）：１ｍｍ
突起部長さ（Ｌ）：５０ｍｍ
巻取り速度（ν）：６００ｍ／分
ばね定数（Ｋ）：５９５３４Ｎ／ｍ
圧縮時の粘性減衰係数（Ｃ）：３００００Ｎ・ｓ／ｍ
伸張時の粘性減衰係数（Ｃ）：１５００Ｎ・ｓ／ｍ
押圧ロールの重量（Ｍ）：４００ｋｇ
Projection height (2a): 1 mm
Projection length (L): 50 mm
Winding speed (ν): 600 m / min Spring constant (K): 59534 N / m
Viscous damping coefficient during compression (C): 30000 N · s / m
Viscous damping coefficient during extension (C): 1500 N · s / m
Pressure roll weight (M): 400 kg
これらの計算結果を図１０に示す。
（第２の比較例）
本発明に係る第１の実施例との比較例として、図１３の力学モデルから運動方程式（数５、数６）を導出し振動減衰性能の評価を行なった。計算に用いたパラメータとしては、圧縮時と伸張時との粘性減衰係数いずれも同じ値である３００００Ｎ・ｓ／ｍにした以外は、第２の実施例と同様の値を用いた。これらの計算結果を図１１に示す。
These calculation results are shown in FIG.
(Second comparative example)
As a comparative example with the first embodiment according to the present invention, the equation of motion (Equations 5 and 6) was derived from the dynamic model of FIG. 13 and the vibration damping performance was evaluated. As parameters used for the calculation, the same values as those in the second example were used except that the viscosity damping coefficient at the time of compression and at the time of expansion was set to 30000 N · s / m, which is the same value. The calculation results are shown in FIG.
図１０および図１１より明らかな通り、同一の突起の高さおよび突起の長さに対して、本発明の実施例に係るバウンド抑制方法は、比較例のバウンド抑制方法よりも巻きロールに接触している時間が格段に長くなることが判る。 As is clear from FIGS. 10 and 11, the bounce suppression method according to the example of the present invention is more in contact with the winding roll than the bounce suppression method of the comparative example with respect to the same protrusion height and protrusion length. It can be seen that the time is significantly longer.
以上説明したように、本発明は、押圧ロールが往復直線運動する形態の振動で減衰する質点としてではなく、押圧ロールの駆動軸に連結された揺動中心周りに押圧ロールが振り子運動する形態の振動で減衰する質点として着目することで上述の課題の解決が図られた。 As described above, the present invention is not a mass point that is attenuated by vibration in a form in which the press roll reciprocates linearly, but in a form in which the press roll makes a pendulum movement around the swing center connected to the drive shaft of the press roll. The above-mentioned problem has been solved by paying attention as a mass point that attenuates due to vibration.
以上のように構成された本実施形態に係る振動抑制装置１によれば、固定台２に連結された押圧ロール４が巻きロール７の表面に沿って動き、その突起を通過する際、押圧ロール４には突起の突出方向に外力が加わる。押圧ロール４は、外力によって駆動軸８が連結手段３の第１の連結部９を支軸として巻きロール７から離間する方向に動く。この外力は、押圧ロール４の駆動軸８に連結された連結手段３の第１の部材１４と、第１の部材１４から延びる第２の部材１５と、を介して加圧手段５に印加される。加圧手段５は、一端が第４の連結部１２を介して連結手段３の第２の部材１５と連結されているとともに、他端が第２の連結部１０を介して固定台２の第２の連結部１０と連結されている。更に、第１の連結部９と加圧手段５の一端とを結ぶ直線と交差する方向に反発力を発生させる。こうした加圧手段５の構成により、この直線距離と反発力との積であるモーメントが第１の連結部９周りに生じることで、押圧ロール４は、駆動軸８が第１の連結部９を支軸として巻きロール７に接近する方向に動く。なお、加圧手段５のみの構成では、このモーメントによって押圧ロール４の振動が発散する方向に向かってしまう。しかし、振動減衰手段６の一端が第５の連結部１３を介して連結手段３の第２の部材１５と連結されているとともに、他端が第３の連結部１１を介して固定台２の第３の連結部１１と連結されている。更に、振動減衰手段６は、第１の連結部９と振動減衰手段６の一端とを結ぶ直線と交差する方向に減衰力を発生させる。こうした振動減衰手段６の構成により、この直線距離と減衰力との積であるモーメントが第１の連結部９周りに生じる。このようにして、振動減衰手段６は加圧手段５によるモーメントを打ち消す方向に第１の連結部９周りのモーメントを発生させる。そのため、押圧ロール４の振動は減衰し、収束する方向に向かう。従って、巻きロール表面の突起などの障害物を乗り越える際の押圧ロールの振動を従来の振動抑制装置に比べ抑えることができる。 According to the vibration suppression device 1 according to the present embodiment configured as described above, when the pressing roll 4 connected to the fixed base 2 moves along the surface of the winding roll 7 and passes through the protrusion, the pressing roll An external force is applied to 4 in the protruding direction of the protrusion. The pressing roll 4 moves in a direction away from the winding roll 7 with the first connecting portion 9 of the connecting means 3 as a support shaft by the external force. This external force is applied to the pressurizing means 5 via the first member 14 of the connecting means 3 connected to the drive shaft 8 of the pressing roll 4 and the second member 15 extending from the first member 14. The The pressurizing means 5 has one end connected to the second member 15 of the connecting means 3 via the fourth connecting portion 12 and the other end connected to the second of the fixing base 2 via the second connecting portion 10. Are connected to two connecting portions 10. Furthermore, a repulsive force is generated in a direction intersecting with a straight line connecting the first connecting portion 9 and one end of the pressurizing means 5. With the configuration of the pressurizing unit 5, a moment that is a product of the linear distance and the repulsive force is generated around the first connecting portion 9, so that the pressing roll 4 causes the drive shaft 8 to move the first connecting portion 9. It moves in the direction approaching the winding roll 7 as a support shaft. In addition, in the structure only of the pressurization means 5, it will go to the direction where the vibration of the press roll 4 diverges by this moment. However, one end of the vibration attenuating means 6 is connected to the second member 15 of the connecting means 3 via the fifth connecting portion 13, and the other end is connected to the fixed base 2 via the third connecting portion 11. It is connected to the third connecting part 11. Further, the vibration damping means 6 generates a damping force in a direction intersecting with a straight line connecting the first connecting portion 9 and one end of the vibration damping means 6. Due to the configuration of the vibration damping means 6, a moment that is the product of the linear distance and the damping force is generated around the first connecting portion 9. In this way, the vibration damping means 6 generates a moment around the first connecting portion 9 in a direction that cancels out the moment generated by the pressurizing means 5. Therefore, the vibration of the pressing roll 4 is attenuated and goes in the direction of convergence. Therefore, the vibration of the pressing roll when getting over obstacles such as protrusions on the surface of the winding roll can be suppressed as compared with the conventional vibration suppressing device.
１ 振動抑制装置
２ 固定台
３ 連結手段
４ 押圧ロール
５ 加圧手段
６ 振動減衰手段
７ 巻きロール
８ 駆動軸
９ 第１の連結部
１０ 第２の連結部
１１ 第３の連結部
１２ 第４の連結部
１３ 第５の連結部
１４ 第１の部材
１５ 第２の部材
１６ 駆動軸の軸芯
DESCRIPTION OF SYMBOLS 1 Vibration suppression apparatus 2 Fixing base 3 Connection means 4 Press roll 5 Pressurization means 6 Vibration damping means 7 Winding roll 8 Drive shaft 9 1st connection part 10 2nd connection part 11 3rd connection part 12 4th connection Part 13 Fifth connecting part 14 First member 15 Second member 16 Axle of drive shaft
Claims (11)
第１の連結部を有する第１の部材と、該第１の部材と交差する方向に該第１の部材から延び、第４および第５の連結部を有する第２の部材と、を有し、該第１の連結部を介して前記固定台と連結された連結手段であって、該第１、第４および第５の連結部のそれぞれの位置が変更可能な連結手段と、
前記第１の連結部と離間して配された駆動軸を有し、該駆動軸を介して前記連結手段の前記第１の部材と連結された押圧ロールであって、該駆動軸の軸芯が前記巻きロールの軸芯よりも重力方向上側に位置して該押圧ロールが前記巻きロールを押圧可能であり、該押圧ロールが該駆動軸周りに回転するとともに該駆動軸が該第１の連結部を支軸として揺動する、押圧ロールと、
前記第１の連結部と離間して配された一端および他端を有し、該一端が前記第４の連結部を介して前記連結手段の前記第２の部材と連結されているとともに、該他端が前記第２の連結部を介して前記固定台の該第２の連結部と連結されている加圧手段であって、該加圧手段の該一端と該他端とを結ぶ直線が前記連結手段の前記第２の部材と交差する方向にあり、該第１の連結部と該加圧手段の該一端とを結ぶ直線と交差する方向に反発力を発生させて前記押圧ロールを加圧する加圧手段と、
前記第１の連結部と離間して配された一端および他端を有し、該一端が前記第５の連結部を介して前記連結手段の前記第２の部材と連結されているとともに、該他端が前記第３の連結部を介して前記固定台の該第３の連結部と連結されている振動減衰手段であって、該振動減衰手段の該一端と該他端とを結ぶ直線が前記連結手段の前記第２の部材と交差する方向にあり、該第１の連結部と該振動減衰手段の該一端とを結ぶ直線と交差する方向に減衰力を発生させて前記押圧ロールの振動を減衰させる振動減衰手段と、
を有する、
振動抑制装置。 A fixed base disposed opposite to a winding roll on which the sheet-like material is wound, and having second and third connecting portions;
A first member having a first connecting portion; and a second member extending from the first member in a direction crossing the first member and having fourth and fifth connecting portions. A connecting means connected to the fixed base via the first connecting portion, the connecting means being capable of changing the positions of the first, fourth and fifth connecting portions;
A pressing roll having a drive shaft arranged apart from the first connecting portion and connected to the first member of the connecting means via the drive shaft, the shaft of the drive shaft Is positioned above the axis of the winding roll in the gravity direction so that the pressing roll can press the winding roll, the pressing roll rotates around the driving shaft, and the driving shaft is connected to the first coupling. A pressing roll that swings around the support shaft,
And having one end and the other end spaced apart from the first connecting portion, the one end being connected to the second member of the connecting means via the fourth connecting portion, and The other end of the pressing means is connected to the second connecting portion of the fixed base via the second connecting portion, and a straight line connecting the one end of the pressing means and the other end is formed. The pressing roll is applied by generating a repulsive force in a direction intersecting the second member of the connecting means and intersecting a straight line connecting the first connecting portion and the one end of the pressing means. Pressurizing means for pressing,
And having one end and the other end spaced apart from the first connecting portion, the one end being connected to the second member of the connecting means via the fifth connecting portion, Vibration damping means having the other end connected to the third connecting portion of the fixed base via the third connecting portion, and a straight line connecting the one end of the vibration damping means and the other end The vibration of the pressing roll by generating a damping force in a direction intersecting the second member of the connecting means and intersecting a straight line connecting the first connecting portion and the one end of the vibration damping means. Vibration damping means for damping
Having
Vibration suppression device.
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| JP2021031241A (en) * | 2019-08-26 | 2021-03-01 | 株式会社日本製鋼所 | Winding machine and film manufacturing system |
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| CN103323163B (en) * | 2013-06-14 | 2015-11-04 | 中国科学院自动化研究所 | A kind of Active Compensation based on force feedback presses down vibrating system |
| CN109279401A (en) * | 2018-11-06 | 2019-01-29 | 苏州极数印花科技有限公司 | A kind of guide rail structure of high-speed multiple channel printing machine delivery system |
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| JPS6023157U (en) * | 1983-07-21 | 1985-02-16 | 株式会社 片岡機械製作所 | Winder contact pressure stabilizer |
| JPS61184139U (en) * | 1985-05-09 | 1986-11-17 | ||
| JPH04292357A (en) * | 1991-03-20 | 1992-10-16 | Mitsubishi Heavy Ind Ltd | Winding device for belt-like substance |
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| CN112429562A (en) * | 2019-08-26 | 2021-03-02 | 株式会社日本制钢所 | Winder and film manufacturing system |
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| CN112429562B (en) * | 2019-08-26 | 2024-05-10 | 株式会社日本制钢所 | Winding machine and film manufacturing system |
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