JPS6350127B2 - - Google Patents
Info
- Publication number
- JPS6350127B2 JPS6350127B2 JP16413282A JP16413282A JPS6350127B2 JP S6350127 B2 JPS6350127 B2 JP S6350127B2 JP 16413282 A JP16413282 A JP 16413282A JP 16413282 A JP16413282 A JP 16413282A JP S6350127 B2 JPS6350127 B2 JP S6350127B2
- Authority
- JP
- Japan
- Prior art keywords
- transmission shaft
- crank
- cutter
- drive shaft
- axis
- 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
- 230000005540 biological transmission Effects 0.000 claims description 26
- 238000005520 cutting process Methods 0.000 description 20
- 238000003754 machining Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23F—MAKING GEARS OR TOOTHED RACKS
- B23F5/00—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made
- B23F5/12—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by planing or slotting
- B23F5/16—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by planing or slotting the tool having a shape similar to that of a spur wheel or part thereof
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Processing (AREA)
Description
【発明の詳細な説明】
本発明は、加工能率の向上と工具寿命の増大と
を企図したカツタスピンドルの高速早戻り装置に
関し、特にギヤシエーバに応用して好適なもので
ある。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a high-speed quick return device for a cutter spindle intended to improve machining efficiency and extend tool life, and is particularly suitable for application to a gear shifter.
ギヤシエーバは内歯歯車や段付き歯車、山歯歯
車或いはラツク等のようにホブで加工ができない
場合に不可欠の工作機械であり、加工能率の点で
ホブ盤よりも優れている反面、カツタの寿命がか
なり短い欠点を有している。従来、最も一般的な
ギヤシエーバはピニオンカツタをその軸心と平行
な方向に往復動させる手段として駆動軸の回転運
動を往復直線運動に変換するピストンクランク機
構を採用している。このピストンクランク機構に
おける駆動軸の回転角とピニオンカツタの移動速
度との関係を表す第１図に示すように、ピニオン
カツタの移動速度は正弦曲線で表されることが判
る。この場合、駆動軸の回転角が０度から180度
までの範囲が切削領域であり、平均切削速度V1
にほぼ相当する30度から150度までの範囲が実際
の切削工程Ｃとなる。このため、駆動軸の回転角
が180度から360度までの範囲が戻り行程Ｒである
けれども、この戻り工程Ｒを含めて加工し関与し
ない無駄な時間は駆動軸の一回転当り67％にも及
ぶ。又、ピニオンカツタの寿命は最大切削速度
V2に大きく左右されることが判明しており、一
般にこの最大切削速度V2が低いほどピニオンカ
ツタの寿命を延ばすことが可能である。 A gear sheaver is an indispensable machine tool for processing internal gears, stepped gears, angle gears, rack gears, etc. that cannot be machined with a hob, and while it is superior to a hobbing machine in terms of processing efficiency, it has a shorter lifespan than a hobbing machine. has a rather short drawback. Conventionally, the most common gear shifter employs a piston crank mechanism that converts rotational motion of a drive shaft into reciprocating linear motion as a means for reciprocating a pinion cutter in a direction parallel to its axis. As shown in FIG. 1, which shows the relationship between the rotation angle of the drive shaft and the moving speed of the pinion cutter in this piston crank mechanism, it can be seen that the moving speed of the pinion cutter is represented by a sine curve. In this case, the range of the rotation angle of the drive shaft from 0 degrees to 180 degrees is the cutting area, and the average cutting speed is V 1
The actual cutting process C ranges from 30 degrees to 150 degrees, which is approximately equivalent to . Therefore, although the return stroke R is the range in which the rotation angle of the drive shaft is from 180 degrees to 360 degrees, the wasted time that is not involved in machining, including this return process R, is 67% per rotation of the drive shaft. Extends. Also, the life of the pinion cutter depends on the maximum cutting speed.
It has been found that the cutting speed greatly depends on V 2 , and in general, the lower the maximum cutting speed V 2 is, the longer the life of the pinion cutter can be.
このような観点から、ピニオンカツタの速度曲
線の理想的なものとして例えば第２図に示すよう
なものであることが望ましい。つまり、ピニオン
カツタの最大切削速度V2をその平均切削速度V1
に近付け、戻り行程Ｒの占める割合を少なくする
と共に切削工程Ｃの割合を多くするのである。 From this point of view, it is desirable that the pinion cutter has an ideal speed curve as shown in FIG. 2, for example. In other words, the maximum cutting speed V 2 of the pinion cutter is the average cutting speed V 1
, the ratio of the return stroke R is reduced, and the ratio of the cutting process C is increased.
本発明者らは、第３図ａに示すように第一のク
ランク１とこれに対して一定量ｄだけ偏心した第
二のクランク２とをスライダ３を介して連結し、
この第二のクランク２とカツタスピンドル４とを
リンク５を介して連結したクランクスライダ機構
及び第３図ｂに示すように、カツタスピンドル４
とリンク５との枢着部分を通るこのカツタスピン
ドル４の往復動方向と平行な直線がクランク６の
軸心と一定量ｅだけずれた偏心クランクピストン
機構とを組み合わせることによつて、前述した第
２図に示すような速度曲線に近い速度曲線を有す
るカツタスピンドルを得られることを見い出し
た。 The present inventors connected a first crank 1 and a second crank 2 eccentric by a certain amount d with respect to the first crank 1 via a slider 3, as shown in FIG.
As shown in FIG. 3b, a crank slider mechanism in which the second crank 2 and the cutter spindle 4 are connected via a link 5, and a cutter spindle 4 as shown in FIG.
By combining an eccentric crank piston mechanism in which a straight line parallel to the reciprocating direction of the cutter spindle 4 passing through the pivot point between the shaft and the link 5 is offset by a certain amount e from the axis of the crank 6, the above-mentioned It has been found that it is possible to obtain a katsuta spindle having a speed curve close to the speed curve shown in Figure 2.
つまり、本発明はスピンドルヘツドに取り付け
られると共に駆動源に連結された駆動軸と、この
駆動軸に対して一定量偏心した状態で前記スピン
ドルヘツドに回転自在に取り付けられた伝達軸
と、この伝達軸及び前記駆動軸のいずれか一方に
形成されるクランクに突設されたスライダと、こ
のスライダと対向するように前記伝達軸及び前記
駆動軸のいずれか他方に形成され且つ当該スライ
ダが摺動自在に係合する溝を径方向に刻設したカ
ム板と、軸心が前記伝達軸の軸心と直角でこの伝
達軸の軸心と交差しないピニオンカツタを具え且
つこのピニオンカツタの軸心と平行な方向に往復
動自在に前記スピンドルヘツドに取り付けられた
カツタスピンドルと、このカツタスピンドルにリ
ンクを介して連結されると共に前記伝達軸に形成
された第二のクランクとからなる構成によつて、
加工能率の向上と工具寿命の増大とを企図したギ
ヤシエーバ用のカツタスピンドル早戻り装置を提
供することを目的とする。 In other words, the present invention provides a drive shaft that is attached to a spindle head and connected to a drive source, a transmission shaft that is rotatably attached to the spindle head with a certain amount of eccentricity with respect to the drive shaft, and this transmission shaft. and a slider protruding from a crank formed on one of the drive shafts, and a slider formed on the other of the transmission shaft and the drive shaft so as to face the slider, and the slider is slidable. A cam plate having an engaging groove carved in the radial direction, and a pinion cutter whose axis is perpendicular to the axis of the transmission shaft and does not intersect with the axis of the transmission shaft, and which is parallel to the axis of the pinion cutter. With a structure consisting of a cutter spindle attached to the spindle head so as to be able to reciprocate in the direction, and a second crank connected to the cutter spindle via a link and formed on the transmission shaft,
The object of the present invention is to provide a quick return device for a cutter spindle for a gear shifter, which is intended to improve machining efficiency and extend tool life.
以下、本発明によるカツタスピンドル早戻り装
置の一実施例について第４図〜第６図を参照しな
がら詳細に説明する。本実施例の断面構造を表す
第４図及びその機構原理を表す第５図ａに示すよ
うに、スピンドルヘツド１１に回転自在に取り付
けられた駆動軸１２の一端部にはベルト１３を介
して図示しないモータの回転軸１４に連結される
変速用プーリ１５が一体的に固定されており、こ
の駆動軸１２の他端部には第５図ａ中の矢視Ｂ部
を拡大した第５図ｂに示すように、スライダ１６
を突設した円板形のクランク１７が一体的に設け
られている。一端部がこの駆動軸１２の他端部と
対向するように当該駆動軸１２に対して一定量ｄ
だけ偏心した伝達軸１８はスピンドルヘツド１１
に回転自在に取り付けられ、この伝達軸１８の一
端部にはスライダ１６が摺動自在に係合する溝１
９を径方向に刻設したカム板２０がクランク１７
と対向するように一体的に設けられている。な
お、本実施例ではクランク１７を駆動軸１２に形
成すると共にカム板２０を伝達軸１８に形成した
が、これらを逆に設けるようにしてもよく、これ
らクランク１７及びカム板２０等で第３図ａに示
したクランクスライダ機構が構成されている。一
方、伝達軸１８の他端部には円板形のクランク２
１が一体的に設けられており、ピニオンカツタ２
２が取り付けられたカツタスピンドル２３は伝達
軸１８の軸心と直角な方向に往復動自在にスピン
ドルヘツド１１と一体の図示しない部材に取り付
けられているが、ピニオンカツタ２３の軸心は伝
達軸１８の軸心と交差しない（交わらない）よう
に一定量ｅだけずれた状態に位置決めされてい
る。前記クランク２１とカツタスピンドル２３と
はリンク２４を介して連結され、これらクランク
２１及びリンク２４等で偏心クランクピストン機
構が構成されている。 Hereinafter, an embodiment of the cutter spindle quick return device according to the present invention will be described in detail with reference to FIGS. 4 to 6. As shown in FIG. 4 showing the cross-sectional structure of this embodiment and FIG. A speed change pulley 15 connected to the rotating shaft 14 of the motor is integrally fixed to the other end of the drive shaft 12, as shown in FIG. 5b, which is an enlarged view of arrow B in FIG. Slider 16 as shown in
A disc-shaped crank 17 with a protruding shape is integrally provided. A certain amount d is applied to the drive shaft 12 so that one end faces the other end of the drive shaft 12.
The transmission shaft 18, which is eccentric by
A groove 1 is rotatably attached to the transmission shaft 18, and one end of the transmission shaft 18 has a groove 1 in which the slider 16 is slidably engaged.
A cam plate 20 with 9 carved in the radial direction is connected to the crank 17.
It is integrally provided so as to face the. In this embodiment, the crank 17 is formed on the drive shaft 12, and the cam plate 20 is formed on the transmission shaft 18, but these may be provided in reverse, and the crank 17, cam plate 20, etc. The crank slider mechanism shown in Figure a is constructed. On the other hand, a disc-shaped crank 2 is attached to the other end of the transmission shaft 18.
1 is integrally provided, and a pinion cutter 2
The cutter spindle 23 to which the pinion cutter 2 is attached is attached to a member (not shown) that is integrated with the spindle head 11 so as to be able to reciprocate in a direction perpendicular to the axis of the transmission shaft 18. It is positioned so as to be shifted by a certain amount e so as not to intersect (do not intersect) with the axis of. The crank 21 and the cutter spindle 23 are connected via a link 24, and the crank 21, link 24, etc. constitute an eccentric crank piston mechanism.
従つて、定速回転しているモータからベルト１
３を介して変速プーリ１５へ回転が伝えられると
駆動軸１２は定速回転するが、この駆動軸１２に
対して伝達軸１８は一定量ｄ偏心しているため、
スライダ１６から溝１９を介して伝わる回転力が
不均一となり、伝達軸１８は不等速回転を始め
る。この不等速回転はクランク２１に伝えられる
が、伝達軸１８の軸心とピニオンカツタ２２の軸
心との一定量のずれｅの効果が加わり、カツタス
ピンドル２３は例えば第６図に示すような速度曲
線を描くこととなる。 Therefore, from the motor rotating at a constant speed, the belt 1
When rotation is transmitted to the speed change pulley 15 through the transmission pulley 15, the drive shaft 12 rotates at a constant speed, but since the transmission shaft 18 is eccentric by a certain amount d with respect to the drive shaft 12,
The rotational force transmitted from the slider 16 through the groove 19 becomes non-uniform, and the transmission shaft 18 begins to rotate at non-uniform speeds. This non-uniform rotation is transmitted to the crank 21, but due to the effect of a certain amount of deviation e between the axis of the transmission shaft 18 and the axis of the pinion cutter 22, the cutter spindle 23 is rotated as shown in FIG. 6, for example. A speed curve will be drawn.
この速度曲線を変化させる因子は、クランク２
１の腕の長さｒ、リンク２４の長さｌ、ピニオン
カツタ２２の軸心と伝達軸１８の軸心とのずれの
量ｅ、駆動軸１２の軸心からスライダ１６の中心
までの距離ｔ、駆動軸１２と伝達軸１８との偏心
量ｄ、カツタスピンドル２３の往復動方向に対す
る駆動軸１２と伝達軸１８との偏心方向の傾き角
α及びカム板２０に刻設された溝１９の方向とク
ランク２１に刻設された溝２５の方向とのなす角
βである。第６図のものは、
ｒ＝15mm
ｌ＝250mm
ｅ＝ 0mm
ｒ＝50mm
ｄ＝15mm
α＝ 0゜
β＝90゜
に設定し、毎分1000ストロークの速度でピニオン
カツタ２２を往復動させるようにしたものであ
る。 The factor that changes this speed curve is the crank 2
1, the length r of the link 24, the amount of deviation e between the axis of the pinion cutter 22 and the axis of the transmission shaft 18, and the distance t from the axis of the drive shaft 12 to the center of the slider 16. , the amount of eccentricity d between the drive shaft 12 and the transmission shaft 18, the tilt angle α of the eccentric direction of the drive shaft 12 and the transmission shaft 18 with respect to the reciprocating direction of the cutter spindle 23, and the direction of the groove 19 carved in the cam plate 20. and the direction of the groove 25 carved in the crank 21. The one in Figure 6 is set to r = 15 mm l = 250 mm e = 0 mm r = 50 mm d = 15 mm α = 0° β = 90°, and the pinion cutter 22 is reciprocated at a speed of 1000 strokes per minute. This is what I did.
このように、上述した因子を適宜設定すること
で第６図に示すような速度曲線を任意に得ること
が可能であり、本発明では速度曲線を左右する因
子が上述の如く７つもあるため、目的に応じた最
適の特性に設計することが容易である。例えば、
工具寿命の増大を主目的とする場合には最高切削
速度V2をできるだけ小さくするように各因子を
設定し、又、切削能率の向上を主目的とする場合
には最高戻り速度V3を機械の強度が許す範囲で
最大となるように各因子を設定する。なお、第６
図に示したものでは毎分1000ストロークで最高切
削速度V2を従来のものより３割強小さくするこ
とができ、又、最高戻り速度V3を従来のものの
倍にすることができ、工具寿命の増大と非切削時
間の短縮化とを同時に達成可能となつた。 In this way, by appropriately setting the above-mentioned factors, it is possible to arbitrarily obtain a speed curve as shown in FIG. It is easy to design the optimum characteristics according to the purpose. for example,
If the main purpose is to increase tool life, set each factor to make the maximum cutting speed V 2 as small as possible, and if the main purpose is to improve cutting efficiency, set the maximum return speed V 3 to the machine. Each factor is set so that it is maximized within the allowable range. In addition, the 6th
In the model shown in the figure, the maximum cutting speed V 2 can be reduced by over 30% compared to the conventional model at 1000 strokes per minute, and the maximum return speed V 3 can be doubled compared to the conventional model, resulting in a long tool life. It has become possible to simultaneously increase the amount of cutting and shorten the non-cutting time.
このように本発明のカツタスピンドル早戻り装
置によると、クランクスライダ機構と偏心クラン
クピストン機構とを有機的に組み合わせたので、
戻り工程割合の短縮化に伴う切削工程割合の増大
及び最高戻り速度の上昇及び最高切削速度の低減
を同時に達成でき、従つて工具寿命の増大と切削
能率の上昇とを企図し得る。 As described above, according to the Katsuta spindle quick return device of the present invention, since the crank slider mechanism and the eccentric crank piston mechanism are organically combined,
As the return process rate is shortened, the cutting process rate can be increased, the maximum return speed can be increased, and the maximum cutting speed can be reduced at the same time. Therefore, it is possible to increase tool life and cutting efficiency.
第１図は従来のカツタスピンドルの移動速度と
駆動軸の回転角との関係を表すグラフ、第２図は
ギヤシエーバにおける理想的なカツタスピンドル
の移動速度と駆動軸の回転角との関係を表すグラ
フ、第３図ａはクランクスライダ機構の概念を表
す機構原理図、第３図ｂは偏心クランクピストン
機構の概念を表す機構原理図、第４図は本発明に
よるカツタスピンドル早戻り装置をギヤシエーバ
に応用した一実施例の主要部の構造を表す断面
図、第５図ａはその駆動系の外観を表す斜視図、
第５図ｂは第５図ａ中の矢視Ｂ部の拡大分解した
状態を表す斜視図、第６図は本実施例によるカツ
タスピンドルの移動速度と駆動軸の回転角との関
係を表すグラフである。又、図中の符号で
１１はスピンドルヘツド、１２は駆動軸、１６
はスライダ、１７，２１はクランク、１８は伝達
軸、１９，２５は溝、２０はカム板、２２はピニ
オンカツタ、２３はカツタスピンドル、２４はリ
ンクであり、Ｃは切削工程、ｄは偏心量、ｅは軸
心のずれの量、ｌはリンク２４の長さ、ｒはクラ
ンク２１の腕の長さ、Ｒは戻り工程、ｒはスライ
ダの偏心量、V1は平均切削速度、V2は最大切削
速度、V3は最大戻り速度、α，βは傾き角であ
る。
Figure 1 is a graph showing the relationship between the moving speed of a conventional cutter spindle and the rotation angle of the drive shaft, and Figure 2 is a graph showing the relationship between the ideal cutter spindle moving speed and the rotation angle of the drive shaft in a gear shifter. , Fig. 3a is a mechanism principle diagram showing the concept of a crank slider mechanism, Fig. 3b is a mechanism principle diagram showing the concept of an eccentric crank piston mechanism, and Fig. 4 is an application of the cutter spindle quick return device according to the present invention to a gear shifter. FIG. 5a is a perspective view showing the appearance of the drive system;
Fig. 5b is a perspective view showing an enlarged and exploded state of the part shown by arrow B in Fig. 5a, and Fig. 6 is a graph showing the relationship between the moving speed of the cutter spindle and the rotation angle of the drive shaft according to this embodiment. It is. Also, in the figures, 11 is a spindle head, 12 is a drive shaft, and 16 is a spindle head.
is the slider, 17 and 21 are the cranks, 18 is the transmission shaft, 19 and 25 are the grooves, 20 is the cam plate, 22 is the pinion cutter, 23 is the cutter spindle, 24 is the link, C is the cutting process, and d is the eccentricity , e is the amount of deviation of the axis, l is the length of the link 24, r is the length of the arm of the crank 21, R is the return process, r is the amount of eccentricity of the slider, V 1 is the average cutting speed, V 2 is the The maximum cutting speed, V 3 is the maximum return speed, and α and β are the tilt angles.
Claims (1)
動源に連結された駆動軸と、この駆動軸に対して
一定量偏心した状態で前記スピンドルヘツドに回
転自在に取り付けられた伝達軸と、この伝達軸及
び前記駆動軸のいずれか一方に形成されるクラン
クに突設されたスライダと、このスライダと対向
するように前記伝達軸及び前記駆動軸のいずれか
他方に形成され且つ当該スライダが摺動自在に係
合する溝を径方向に刻設したカム板と、軸心が前
記伝達軸の軸心と直角でこの伝達軸の軸心と交差
しないピニオンカツタを具え且つこのピニオンカ
ツタの軸心と平行な方向に往復動自在に前記スピ
ンドルヘツドに取り付けられたカツタスピンドル
と、このカツタスピンドルにリンクを介して連結
されると共に前記伝達軸に形成された第二のクラ
ンクとからなるカツタスピンドル早戻り装置。1. A drive shaft attached to a spindle head and connected to a drive source, a transmission shaft rotatably attached to the spindle head with a certain amount of eccentricity with respect to the drive shaft, and this transmission shaft and the drive shaft. a slider protruding from a crank formed on one of the two; and a groove formed on the other of the transmission shaft and the drive shaft so as to face the slider, and in which the slider engages slidably. a cam plate carved in the radial direction, and a pinion cutter whose axis is perpendicular to the axis of the transmission shaft and does not intersect with the axis of the transmission shaft, and reciprocating in a direction parallel to the axis of the pinion cutter. A cutter spindle quick return device comprising a cutter spindle freely attached to the spindle head, and a second crank connected to the cutter spindle via a link and formed on the transmission shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16413282A JPS5953120A (en) | 1982-09-22 | 1982-09-22 | Quick returning device of cutter spindle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16413282A JPS5953120A (en) | 1982-09-22 | 1982-09-22 | Quick returning device of cutter spindle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5953120A JPS5953120A (en) | 1984-03-27 |
| JPS6350127B2 true JPS6350127B2 (en) | 1988-10-06 |
Family
ID=15787350
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16413282A Granted JPS5953120A (en) | 1982-09-22 | 1982-09-22 | Quick returning device of cutter spindle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5953120A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5709619B2 (en) * | 2011-04-07 | 2015-04-30 | 三菱重工業株式会社 | Gear shaper |
| CN102528518B (en) * | 2012-02-03 | 2013-10-02 | 宜昌市致远新技术有限公司 | Gear shaping machine main motion control device |
| JP5693685B2 (en) | 2013-09-06 | 2015-04-01 | 三菱重工業株式会社 | Gear processing machine |
| CN113229746B (en) * | 2021-05-10 | 2022-04-15 | 江苏美的清洁电器股份有限公司 | A ground brush assembly and dust catcher for dust catcher |
| CN113229743B (en) * | 2021-05-10 | 2022-08-19 | 江苏美的清洁电器股份有限公司 | A ground brush assembly and dust catcher for dust catcher |
-
1982
- 1982-09-22 JP JP16413282A patent/JPS5953120A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5953120A (en) | 1984-03-27 |
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