JPS6150733B2 - - Google Patents
Info
- Publication number
- JPS6150733B2 JPS6150733B2 JP6245582A JP6245582A JPS6150733B2 JP S6150733 B2 JPS6150733 B2 JP S6150733B2 JP 6245582 A JP6245582 A JP 6245582A JP 6245582 A JP6245582 A JP 6245582A JP S6150733 B2 JPS6150733 B2 JP S6150733B2
- Authority
- JP
- Japan
- Prior art keywords
- band saw
- saw blade
- cutting
- principal
- cutting force
- 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
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
- B23D55/00—Sawing machines or sawing devices working with strap saw blades, characterised only by constructional features of particular parts
- B23D55/08—Sawing machines or sawing devices working with strap saw blades, characterised only by constructional features of particular parts of devices for guiding or feeding strap saw blades
- B23D55/082—Devices for guiding strap saw blades
- B23D55/084—Devices for guiding strap saw blades which automatically detect or correct band saw blade deflection
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sawing (AREA)
Description
本発明は帯鋸盤の切削主分力検出方法に関わ
り、更に詳細には切削主分力を帯鋸刃のひねりト
ルクに起因する帯鋸刃案内体の変位量或いはひね
りトルクを測定して検出する方法に関するもので
ある。
従来の帯鋸盤では切削主分力検出方法として駆
動モータの電流変化を利用していた。この方法は
鋸刃から離れた位置で間接的に検出するものであ
つて、鋸速によつても変り機械的損失も大きく瞬
間的な切削主分力を検出できず平均的な切削主分
力を離れた位置で間接的に検出する不都合があつ
た。
第１図にもとづいてまづ本発明の周囲を説明す
る。
第１図に示したいわゆる横型帯鋸盤１は、材料
台３の上に被切削材５をバイス７によつて固定
し、機台９上のバイスベツト１１の一端に設けた
水平な支軸１３のまわりをスイングシリンダ１５
によつて揺動するハウジング１７がある。第１図
に２点鎖線で示したのはスイングシリンダ１５に
よつてハウジング１７が上昇した状態を示してい
る。ハウジング１７の両袖の基盤１９は上端部分
が溝形鋼などからなる繋ぎ梁２１で連結されて同
じ平面を保つており、基盤１９は第１図に示した
ような平面図で上方が奥に下方が手前に傾斜して
いるのが普通であるが、材料台３に対し垂直に設
けた機械もある。
何れにしても基盤１９に垂直に設けられた複数
の軸２３のまわりを駆動ホイール２５と従動ホイ
ール２７が回転し、両ホイールにかけまわされた
無端環状の帯鋸刃２９は、被切削材５に向つて垂
直に下降しなければ、巾のある帯鋸刃２９で被切
削材５を切削できないから、被切削材５の両側に
ガイドアーム３１を設けその下端に帯鋸刃案内体
３３を設けて帯鋸刃を両案内体の間では被切削材
５言い換えれば材料台３に垂直な姿勢を保つて下
降するようにしてある。
即ち第１図に示したいわゆる横型帯鋸盤１では
帯鋸刃２９はホイールに破線で示した矢印の方向
に移動するから従動ホイール２７と被切削材５と
の間に設けられた帯鋸刃案内体３３で材料台３に
対して垂直な姿勢を保つようにひねり起こされ、
被切削材５を通過して駆動ホイール２５に向う間
に設けられた帯鋸刃案内体３３までの間上記した
垂直の姿勢を保ち続け、その通過後は駆動ホイー
ル２５に帯鋸刃の側面が密着するようにひねりも
どされるのである。
なお図示を省略してあるが従動ホイール２７の
軸２３は、ハウジング１９の裏面で横移動自在な
摺動部材に回転自在に保持されていて帯鋸刃２９
を左右両ホイールと左右両案内体にかけまわして
から横移動させて予め一定のテンシヨンを帯鋸刃
に与えてある。
上記した従来のいわゆる横型帯鋸盤１で被切削
材５を切削するには、ハウジング１７をスイング
シリンダ１５に圧油を送入して揺動上昇させ、被
切削材５をバイス７で固定してから、被切削材５
の被削性によつてスイングシリンダ１５からの流
出量と鋸刃の移動速度を設定してハウジングの自
重によつて切込みを続けるのであり、これらの選
定はすべて帯鋸刃という剛性の低い工具に無理の
かからないような安全範囲で主として作業員の経
験によつて行つていた。
しかしながら第１図に示したように大型の丸材
を切削する場合は、直径部分で最も切削方向の抵
抗（切削主分力）が大きくなるのは明らかで、丸
材の上下端では帯鋸刃の切削能力の大部分を利用
しない切削を行つているのである。
従つて帯鋸刃の切削主分力を時々刻々検出し得
て、流量制御弁の流量を連動的に自動制御すると
か、鋸刃の移動速度を適宜修正できれば帯鋸盤の
効率を向上することができる筈である。
本発明は以上の目的を達成すべく切削主分力を
時々刻々検出する方法を提供するものであり、ま
づ本発明の根拠となつた基本原理及び計算値と実
験結果を示す。
初めに薄帯のねじり理論により薄金属帯のひね
りトルクの式は材料力学（テイモンエンコ箸）か
ら
Mt＝１／３bc3Gθ（１＋１／１２０・Ｅ／Ｇ・ｂ４／
ｃ
・θ２＋１／４・δ０／Ｇ・ｂ２／ｃ２） …(1)
(1)式において
ｂ；帯鋸刃有効巾 mm
ｃ；帯鋸刃厚 mm
Ｇ；横弾性係数 Kg／cm2
Ｅ；縦弾性係数 Kg／cm2
θ；単位長さ当りのひねり角 rad／mm
δ０；縦引張応力
Mt；ひねりトルク
Ｐ；テンシヨン力
(1)式より帯鋸刃が空中を切削している時のひね
りトルクをMt0とすると、
Mt0＝ｂｃ３Ｇθ／３
（１＋Ｅｂ４θ２／１２０Ｇｃ＋ｂ２／４Ｇｃ２・
Ｐ／ｂ×ｃ）…(2)
切削時のひねりトルクをMt1とすると、
Mt1＝ｂｃ３Ｇθ／３
（１＋Ｅｂ４θ２／１２０Ｇｃ＋ｂ２／４Ｇｃ２・
Ｐ＋ｆ／ｂ×ｃ）…(3)
ここで
Ｐ；テンシヨン力（厳密にはテンシヨン力と無負
荷回転抵抗が合算されたもの）
ｆ；切削主分力
(3)−(2)
Mt1−Mt0＝
ｂｃ３Ｇθ／３×ｂ２ｆ／４Ｇｃ３ｂ＝ｂ２ｆθ／
１２
ｂ；帯鋸刃有効巾（常数）
故にひねりトルクの差が検出されれば切削主分
力が検出できることが明白である。
次に帯鋸刃のひねりに要するトルクを前記の(1)
式を使つて計算し、別途実際に左右の両ホイール
間に帯鋸刃をテンシヨンをかけて張りその中央を
静止の状態で帯鋸刃の高さの中央を中心に45度か
ら垂直にまでばね計りを介してひねつて比較して
見たのである。この場合の
ｂ；帯鋸刃有効巾 22mm
ｃ；帯鋸刃厚 0.95mm
Ｇ；横弾性係数
0.84×106Kg／cm2＝8400Kg／mm2
Ｅ；縦弾性係数
2.1×106Kg／cm2＝2100Kg／mm2
θ；単位長さ当りのひねり角
＝０．７８５４（４５度のｒａｄ値）／５７０（駆動
ホイール接点から実測）
＝0.0013779rad／mm
δ０；縦引張応力＝Ｐ／Ａ＝４１４．６１５Kg（実測値
）／０．９５×２２mm2
＝19.8380Kg／mm2
(1)式による
Mt＝１／３bc3Gθ
（１＋１／１２０ Ｅ／Ｇ ｂ４／ｃ２・θ２＋１
／４・δ０／Ｇ・ｂ２／ｃ２）
＝96.5620Kg，mm…計算値
実際にばね計りで測定した値は、
１／２ｂ＝11mmが入つて
Mt＝11×9.5（実測値）
＝104.5Kg／mm2…実測値
上記したように計算値と実測値とは殆んど同じ
である。その10％程の相異は実際のひねりおこし
のための把持具には巾があつて計算の場合の駆動
ホイール接点からの実測値（上記では570）が点
で計算していることが主因と考えられる。
更に実際の帯鋸盤の寸法を使用して切削主分力
を25Kg、50Kg，…………200Kgまで25Kgごとに計
算してみると下記の表のようになる。
計算式は切記した(1)式で
Mt＝１／３bc3Gθ
（１＋１／１２０・Ｅ／Ｇ・ｂ４／ｃ・θ２＋１／
４・δ０／Ｇ・ｂ２／ｃ２）…(1)
Mt；ひねりトルク25，50，……200とする。
Kg，mm
ｂ，ｃ，Ｇ，Ｅ、は前記したと同じ数字を使用
し帯鋸刃をかけまわしてプリテンシヨンは実測値
414.615Kgをかけ、駆動ホイールの帯鋸刃接点か
ら395mmの位置での45度のひねりもどし角度を設
定した。
この場合25Kgの切削主分力を発生するには、
δ０＝４１６．６１５＋２５／０．９５×２２＝21.0
342Kg／mm2
θ＝０．７８５４（４５度のｒａｄ値）／３９５（駆
動ホイールまでの距離）
＝0.00198835rad／mm
となるから(1)式から142.5121Kg、mmが得られる。
The present invention relates to a method of detecting the principal cutting force of a band saw machine, and more particularly to a method of detecting the principal cutting force by measuring the amount of displacement or twisting torque of the band saw blade guide caused by the twisting torque of the band saw blade. It is something. Conventional bandsaw machines use changes in the drive motor's current to detect the principal cutting force. This method indirectly detects the cutting force at a position far from the saw blade, and the mechanical loss varies depending on the saw speed, so the instantaneous principal cutting force cannot be detected, and the average principal cutting force cannot be detected. There was an inconvenience in detecting it indirectly from a remote location. First, the surroundings of the present invention will be explained based on FIG. The so-called horizontal band saw machine 1 shown in FIG. Swing cylinder around 15
There is a housing 17 which is swung by. The two-dot chain line in FIG. 1 shows the state in which the housing 17 is raised by the swing cylinder 15. The upper ends of the bases 19 on both sleeves of the housing 17 are connected by connecting beams 21 made of channel steel or the like to maintain the same plane. Usually, the lower part is inclined toward the front, but there are also machines that are installed perpendicularly to the material table 3. In any case, a driving wheel 25 and a driven wheel 27 rotate around a plurality of shafts 23 provided perpendicularly to the base 19, and an endless annular band saw blade 29, which is wound around both wheels, is directed toward the workpiece 5. Since the wide band saw blade 29 cannot cut the workpiece 5 unless the band saw blade 29 moves vertically down, guide arms 31 are provided on both sides of the workpiece 5, and a band saw blade guide 33 is provided at the lower end of the guide arm 31 to cut the band saw blade. Between the two guide bodies, the material to be cut 5, in other words, descends while maintaining a posture perpendicular to the material table 3. That is, in the so-called horizontal band saw machine 1 shown in FIG. 1, the band saw blade 29 moves in the direction of the arrow shown by the broken line on the wheel, so the band saw blade guide 33 provided between the driven wheel 27 and the workpiece 5 Twist it up so that it stays perpendicular to the material table 3,
The band saw blade continues to maintain the above-described vertical posture until it passes through the workpiece 5 and reaches the band saw blade guide 33 provided between the drive wheels 25 and after passing through, the side surface of the band saw blade comes into close contact with the drive wheel 25. It is twisted back like this. Although not shown, the shaft 23 of the driven wheel 27 is rotatably held by a sliding member that can move laterally on the back side of the housing 19, and the shaft 23 of the driven wheel 27 is rotatably held by a sliding member that can move laterally on the back side of the housing 19.
is passed around both the left and right wheels and the left and right guide bodies, and then moved laterally to apply a certain tension to the band saw blade in advance. In order to cut a workpiece 5 with the conventional so-called horizontal bandsaw machine 1 described above, the housing 17 is swung upward by supplying pressure oil to the swing cylinder 15, and the workpiece 5 is fixed with a vise 7. From, material to be cut 5
The flow rate from the swing cylinder 15 and the moving speed of the saw blade are set according to the machinability of the housing, and the cutting is continued by the weight of the housing.All these selections are impossible for a band saw blade, a tool with low rigidity. This was done mainly based on the experience of the workers within a safe range that would not cause any damage. However, when cutting a large round material as shown in Figure 1, it is clear that the resistance in the cutting direction (principal cutting force) is greatest at the diameter part, and the cutting capacity of the bandsaw blade is greater at the upper and lower ends of the round material. In other words, cutting is performed without using most of the material. Therefore, if the main cutting force of the band saw blade can be detected moment by moment, and the flow rate of the flow control valve can be automatically controlled in conjunction with it, or the moving speed of the saw blade can be adjusted as appropriate, the efficiency of the band saw machine can be improved. It should be. The present invention provides a method for detecting the principal component of cutting force moment by moment in order to achieve the above object, and first, the basic principles, calculated values, and experimental results on which the present invention is based will be shown. First, according to the twisting theory of thin strips, the formula for the twisting torque of a thin metal strip is obtained from the mechanics of materials (Teimonenko chopsticks) as follows: Mt=1/3bc 3 Gθ(1+1/120・E/G・b4 /
c・θ 2 +1/4・δ 0 /G・b 2 /c 2 ) …(1) In equation (1), b: Band saw blade effective width mm c: Band saw blade thickness mm G: Transverse elastic modulus Kg/cm 2 E: Modulus of longitudinal elasticity Kg/cm 2 θ: Twisting angle per unit length rad/mm δ 0 ; Longitudinal tensile stress Mt: Twisting torque P: Tension force According to equation (1), when the band saw blade is cutting in the air If the twisting torque of is Mt 0 , then Mt 0 = bc 3 Gθ/3 (1+Eb 4 θ 2 /120Gc+b 2 /4Gc 2・
P/b×c)…(2) If the twisting torque during cutting is Mt 1 , then Mt 1 = bc 3 Gθ/3 (1+Eb 4 θ 2 /120Gc+b 2 /4Gc 2・
P+f/b×c)…(3) Here, P: Tension force (strictly speaking, the sum of tension force and no-load rotational resistance) f: Principal cutting force (3)−(2) Mt 1 −Mt 0 = bc 3 Gθ/3×b 2 f/4Gc 3 b=b 2 fθ/
12 b; Band saw blade effective width (constant) Therefore, it is clear that the principal component of cutting force can be detected if the difference in twisting torque is detected. Next, calculate the torque required to twist the bandsaw blade as described in (1) above.
Calculate using the formula, and separately actually tension the band saw blade between the left and right wheels, hold the center stationary, and measure the spring from 45 degrees vertically around the center of the height of the band saw blade. I made a twisted comparison. In this case, b: Band saw blade effective width 22mm C: Band saw blade thickness 0.95mm G: Transverse elastic modulus 0.84×10 6 Kg/cm 2 = 8400 Kg/mm 2 E: Longitudinal elastic modulus 2.1×10 6 Kg/cm 2 = 2100 Kg /mm 2 θ; Twisting angle per unit length = 0.7854 (rad value of 45 degrees) / 570 (actually measured from drive wheel contact point) = 0.0013779 rad/mm δ 0 ; Longitudinal tensile stress = P/A = 414. 615Kg (actual measurement)/0.95×22mm 2 =19.8380Kg/mm 2 According to formula (1) Mt=1/3bc 3 Gθ (1+1/120 E/G b 4 /c 2・θ 2 +1
/4・δ 0 /G・b 2 /c 2 ) = 96.5620Kg, mm...Calculated value The value actually measured with a spring scale is: 1/2b = 11mm is included, Mt = 11 × 9.5 (actual value) = 104.5Kg/mm 2 ...Actually measured value As mentioned above, the calculated value and the actually measured value are almost the same. The difference of about 10% is mainly due to the fact that the actual gripping tool for twisting has a width, and the actual measurement value from the drive wheel contact point (570 in the above) is calculated as a point. Conceivable. Furthermore, using the dimensions of the actual bandsaw machine, calculate the principal cutting force in increments of 25Kg from 25Kg to 50Kg to 200Kg, and the results will be as shown in the table below. The calculation formula is the truncated formula (1): Mt=1/3bc 3 Gθ (1+1/120・E/G・b 4 /c・θ 2 +1/
4・δ 0 /G・b 2 /c 2 )...(1) Mt; Twisting torque is 25, 50,...200. Kg, mm b, c, G, E, use the same numbers as above, rotate the band saw blade, and pretension is the actual value.
We applied 414.615Kg and set a twist return angle of 45 degrees at a position of 395mm from the band saw blade contact point of the drive wheel. In this case, to generate a principal cutting force of 25Kg, δ 0 =416.615+25/0.95×22=21.0
342Kg/mm 2 θ = 0.7854 (rad value at 45 degrees) / 395 (distance to drive wheel) = 0.00198835rad/mm Therefore, 142.5121Kg, mm can be obtained from equation (1).
【表】
即ち切削主分力25Kgの変化ごとにひねりトルク
は2.0048Kg，mm変化するのである。
上記した基本原理、計算値、実験にもとづいて
第２図に示した切削主分力検出装置を実施し、第
３図のようなグラフを得た。
第２図の場合、被切削材５と駆動ホイール２５
との間に設けた帯鋸刃案内体３３として軸が平行
して垂下する段違いガイドローラ３５，３７を使
用し帯鋸盤前方側の短軸ガイドローラ３５に対
し、後方側の長軸ガイドローラ３７の先端が切削
主分力に比例したひねりトルクによつて第２図で
右方向に変位する量を差動変圧器型変位計３９へ
（電機マイクロと略称することもある）の触針４
１で検出し、増幅装置４３、図示記録装置４５に
よつてグラフ化するものであり、グラフ化した図
の一例が第３図である。
第３図は被切削材料５としてS45C、200δを使
用し、流量制御弁を目盛３の一定開度に保つて切
削をしたものである。
帯鋸刃に溶接して無端環状に加工してあつて完
全に一様ではなく、環移動の間の機械的抵抗も加
わつてグラフはかなり激しい振幅を示している
が、切削開始前、切削終了後と比較して大きな振
幅の下端が切削主分力を瞬間的に検出しているこ
とが理解されよう。
即ち切削主分力線４７が丸い被切削材料の直径
切削時に最も大きくなる放物線的な曲線を呈する
のである。
第４図に示す第２実施例は、第３図に示した方
法と類似しているが、長軸ガイドローラ３７の軸
に歪検出体４９を固着した切削主分力検出法を示
している。
第５図の第３実施例は第４図と同じような検出
方法を、帯鋸刃案内体３３の長短両方ガイドロー
ラ３５と３７とを支持する天井ブラケツト５１を
比較的薄い材料にして切削主分力によつて歪みや
すくし、この部分に歪検出体４９を固着して間接
的に切削主分力を検出する方法を示している。
第６図の第４実施例は帯鋸刃案内体３３と駆動
ホイール２５との間に帯鋸刃案内体３３とは別個
に長短軸ガイドローラの３５と３７とを設け、そ
の天井ブラケツト５１に比較して剛性の低い繋ぎ
部材５３のひねり歪を歪検出体４９によつて検出
して間接的に切削主分力を検出する方法を示して
いる。
第７図の第５実施例は被切削材５の前後の帯鋸
刃案内体３３とは別に、被切削材のあとの帯鋸刃
案内体３３と駆動ホイール２５との間に帯鋸刃案
内体３３とは独立して帯鋸刃２９の横から弾機５
５を内蔵するローラ接触子５７を帯鋸刃の有効巾
の上端或いは下端に押圧して、ローラ接触子５５
が帯鋸刃２９を押圧する位置でのひねりトルクが
切削主分力増加量に比例することを利用して直接
的に主分力を検出する方法を例示している。
この第５実施例では前記した帯鋸刃２９をホイ
ールにかけまわし、帯鋸刃が空中を移動して空切
削するときのひねりトルクに弾機の押圧力を調整
しておくことによつて第４実施例までの方法より
敏感で直接的な検出が可能である。
第８図の第６実施例は第５実施例と同じ位置に
帯鋸刃２９をまたぐ態様のひねり回動体５９を設
け、帯鋸刃２９と回動軸６１を中にした反対端に
ドグ６３を突設し、帯鋸刃２９をホイールにかけ
まわしてプリテンシヨンを与え空気中を移動した
ときの空切削主分力を補正する弾機６５，６７に
よる付勢力を与えて前記ドグ６３を中立状態に保
ち（第８図の状態）、磁気変位計測器のセンサー
６９をドグ６３の対応位置に設けて第１〜４実施
例に比較してより迅速直接的に切削主分力を検出
する方法を示したものである。なお上記した回動
軸６１と弾機６５，６７の調節自在な端と磁気変
位計測器のセンサー６９を保持するヨーク状のブ
ラケツト７１は第１図に示したガイドアーム３１
などハウジング１７の一部に固定されているのは
当然である。第９図、第１０図は第５図に示した
第３実施例の態様を詳細に示したものである。
かくして本発明の方法は、帯鋸盤における帯鋸
刃の切削主分力の変化を時々刻々且つ時間的おく
れなく、切削主分力による帯鋸刃のひねりトルク
に起因する帯鋸刃支承部材の歪変化量或いは帯鋸
刃に現われるひねりトルクと弾機とのバランスと
からなるひねりトルクの大きさを、帯鋸刃に与え
たプリテンシヨン力を含む空切削時の切削主分力
を差し引いた状態で検出できるのである。[Table] In other words, for every change in the principal cutting force of 25 kg, the twisting torque changes by 2.0048 kg, mm. Based on the basic principles, calculated values, and experiments described above, the principal cutting force detection device shown in FIG. 2 was implemented, and the graph shown in FIG. 3 was obtained. In the case of FIG. 2, the workpiece 5 and the drive wheel 25
As a band saw blade guide 33 provided between the band saw blade guide 33, uneven guide rollers 35 and 37 whose axes are parallel to each other and hang down are used. The amount by which the tip is displaced in the right direction in Fig. 2 due to the twisting torque proportional to the principal cutting force is measured by the stylus 4 of the differential transformer type displacement meter 39 (sometimes abbreviated as electric micro).
1, and graphed by the amplification device 43 and graphic recording device 45, and an example of the graphed diagram is shown in FIG. In FIG. 3, S45C, 200δ was used as the material to be cut 5, and cutting was performed while keeping the flow control valve at a constant opening of scale 3. It is welded to the band saw blade and machined into an endless ring, so it is not completely uniform, and the mechanical resistance during movement of the ring also adds to the graph, which shows quite strong amplitudes, but before cutting starts and after cutting ends. It will be understood that the lower end, which has a large amplitude compared to , instantaneously detects the principal component of cutting force. That is, the cutting principal force line 47 exhibits a parabolic curve that becomes largest when cutting the diameter of a round material to be cut. The second embodiment shown in FIG. 4 is similar to the method shown in FIG. 3, but shows a cutting principal force detection method in which a strain detector 49 is fixed to the shaft of the long-axis guide roller 37. . The third embodiment shown in FIG. 5 uses a detection method similar to that shown in FIG. 4, but uses a relatively thin material for the ceiling bracket 51 that supports both the long and short guide rollers 35 and 37 of the bandsaw blade guide 33, and performs the main cutting task. A method is shown in which the main component of the cutting force is indirectly detected by making the portion easily distorted by force and fixing the strain detection body 49 to this portion. In the fourth embodiment shown in FIG. 6, long and short axis guide rollers 35 and 37 are provided between the band saw blade guide 33 and the drive wheel 25 separately from the band saw blade guide 33, and compared to the ceiling bracket 51. A method is shown in which the torsional strain of the connecting member 53, which has low rigidity, is detected by the strain detector 49 to indirectly detect the principal component of cutting force. In the fifth embodiment shown in FIG. 7, in addition to band saw blade guides 33 before and after the workpiece 5, there is also a band saw blade guide 33 between the band saw blade guide 33 behind the workpiece and the drive wheel 25. independently from the side of the band saw blade 29.
Press the roller contactor 57 with a built-in roller contactor 57 against the upper or lower end of the effective width of the band saw blade.
This example exemplifies a method of directly detecting the principal component force by utilizing the fact that the twisting torque at the position where the band saw blade 29 is pressed is proportional to the amount of increase in the principal component of cutting force. In this fifth embodiment, the band saw blade 29 described above is rotated around a wheel, and the pressing force of the bullet is adjusted to the twisting torque when the band saw blade moves in the air and performs dry cutting. This method allows for more sensitive and direct detection than previous methods. The sixth embodiment shown in FIG. 8 is provided with a twist rotating body 59 that straddles the band saw blade 29 at the same position as the fifth embodiment, and a dog 63 is protruded at the opposite end of the band saw blade 29 and the rotating shaft 61. The dog 63 is maintained in a neutral state by applying pretension by rotating the band saw blade 29 around the wheel and applying a biasing force by bullets 65 and 67 that corrects the main component force for dry cutting when moving in the air ( 8) shows a method of detecting the principal component of cutting force more quickly and directly than in the first to fourth embodiments by installing a sensor 69 of a magnetic displacement measuring device at a corresponding position of the dog 63. It is. The above-mentioned rotating shaft 61, the adjustable ends of the bullets 65 and 67, and the yoke-shaped bracket 71 that holds the sensor 69 of the magnetic displacement measuring device are the guide arm 31 shown in FIG.
It goes without saying that it is fixed to a part of the housing 17. 9 and 10 show details of the third embodiment shown in FIG. 5. FIG. Thus, the method of the present invention detects changes in the principal cutting force of the band saw blade in a band saw machine moment by moment and without any time delay, and changes the amount of strain change in the band saw blade support member due to the twisting torque of the band saw blade due to the principal cutting force. The magnitude of the twisting torque, which is the balance between the twisting torque appearing on the band saw blade and the bullet, can be detected by subtracting the main cutting force during dry cutting, including the pretension force applied to the band saw blade.
第１図はいわゆる横型帯鋸盤の正面図、第２図
は本発明方法の第１実施例説明図、第３図は第２
図の方法による切削主分力グラフ、第４図は第２
実施例説明図、第５図は第３実施例説明図、第６
図は第４実施例説明図、第７図は第５実施例説明
図、第８図は第６実施例説明図である。第９図は
第５図に示した第３実施例の態様を詳細に示した
正面図、第１０図は同上側面図である。
図面の主要部分を表わす符号の説明、１……横
型帯鋸盤、５……被切削材、２５……駆動ホイー
ル、２９……帯鋸刃、３３……帯鋸刃案内体、３
７……長軸ガイドローラ、４７……切削主分力
線、４９……歪検出体、５７……ローラ接触子、
５９……ひねり回転体、６９……磁気変位計測器
のセレンサー。
Fig. 1 is a front view of a so-called horizontal bandsaw machine, Fig. 2 is an explanatory diagram of a first embodiment of the method of the present invention, and Fig. 3 is a diagram of a second embodiment of the method of the present invention.
Cutting principle component force graph according to the method shown in the figure, Figure 4 is the 2nd
Embodiment explanatory diagram, Fig. 5 is the third embodiment explanatory diagram, Fig. 6
FIG. 7 is an explanatory diagram of the fourth embodiment, FIG. 7 is an explanatory diagram of the fifth embodiment, and FIG. 8 is an explanatory diagram of the sixth embodiment. FIG. 9 is a front view showing in detail the aspect of the third embodiment shown in FIG. 5, and FIG. 10 is a side view of the same. Explanation of symbols representing main parts of the drawings: 1...Horizontal band saw machine, 5...Work material, 25...Drive wheel, 29...Band saw blade, 33...Band saw blade guide, 3
7... Long axis guide roller, 47... Cutting principal force line, 49... Strain detector, 57... Roller contactor,
59... Twisting rotating body, 69... Serencer of magnetic displacement measuring device.
Claims (1)
かけまわして循環移動する帯鋸刃の進行途中の材
料切削部の前で帯鋸刃をひねり起し且つ後方でひ
ねりもどして前記切削部範囲だけで材料を切削す
る帯鋸盤の切削主分力検出方法にして、材料切削
部の後方と駆動ホイールとの間で帯鋸刃のひねり
もどしを行うガイドローラのひねりトルクに起因
する帯鋸刃先端の変位量から、切削主分力を検出
することを特徴とする帯鋸盤の切削主分力検出方
法。 ２ 複数の帯鋸刃ホイールに無端環状の帯鋸刃を
かけまわして循環移動する帯鋸刃の進行途中の材
料切削部の前で帯鋸刃をひねり起し且つ後方でひ
ねりもどして前記切削部範囲だけで材料を切削す
る帯鋸盤の切削主分力検出方法にして、材料切削
部の後方と駆動ホイールとの間で帯鋸刃のひねり
もどしを行うガイドローラのひねりトルクに起因
するローラ支承部材の変位量から、切削主分力を
検出することを特徴とする帯鋸盤の切削主分力検
出方法。[Scope of Claims] 1. An endless annular band saw blade is wound around a plurality of band saw blade wheels, and the band saw blade is rotated in front of a material cutting part in the progress of the band saw blade, and twisted back at the rear to perform the above-mentioned operations. This is a method of detecting the principal cutting force of a band saw machine that cuts material only in the cutting area, and the band saw blade is caused by the twisting torque of the guide roller that untwists the band saw blade between the rear of the material cutting part and the drive wheel. A method for detecting the principal cutting force of a band saw machine, which is characterized by detecting the principal cutting force from the amount of displacement of the tip. 2 An endless annular band saw blade is passed around a plurality of band saw blade wheels, and the band saw blade is rotated in front of the material cutting section in the progress of the band saw blade, and the band saw blade is twisted up in front of the material cutting section, and then twisted back at the rear to cut the material only in the area of the cutting section. A method for detecting the principal cutting force of a band saw machine that cuts material is based on the amount of displacement of the roller support member caused by the twisting torque of the guide roller that twists and untwists the band saw blade between the rear of the material cutting section and the drive wheel. A method for detecting principal cutting force for a band saw machine, which is characterized by detecting principal cutting force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6245582A JPS58181518A (en) | 1982-04-16 | 1982-04-16 | Detecting method of cutting main component in band sawing machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6245582A JPS58181518A (en) | 1982-04-16 | 1982-04-16 | Detecting method of cutting main component in band sawing machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58181518A JPS58181518A (en) | 1983-10-24 |
| JPS6150733B2 true JPS6150733B2 (en) | 1986-11-05 |
Family
ID=13200687
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6245582A Granted JPS58181518A (en) | 1982-04-16 | 1982-04-16 | Detecting method of cutting main component in band sawing machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58181518A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02114196U (en) * | 1989-02-23 | 1990-09-12 |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU575658B2 (en) * | 1984-06-25 | 1988-08-04 | Amada Company Limited | Band saw machine |
| CN102672270A (en) * | 2012-04-30 | 2012-09-19 | 苏州赛特尔集团机械有限公司 | Clamping guide mechanism for numerical control cutting machine |
-
1982
- 1982-04-16 JP JP6245582A patent/JPS58181518A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02114196U (en) * | 1989-02-23 | 1990-09-12 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58181518A (en) | 1983-10-24 |
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