JPS63300840A - Clamp cylinder - Google Patents
Clamp cylinderInfo
- Publication number
- JPS63300840A JPS63300840A JP62136385A JP13638587A JPS63300840A JP S63300840 A JPS63300840 A JP S63300840A JP 62136385 A JP62136385 A JP 62136385A JP 13638587 A JP13638587 A JP 13638587A JP S63300840 A JPS63300840 A JP S63300840A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- piston
- cylinder
- diameter
- small diameter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000008878 coupling Effects 0.000 abstract description 7
- 238000010168 coupling process Methods 0.000 abstract description 7
- 238000005859 coupling reaction Methods 0.000 abstract description 7
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 241000755729 Clivia Species 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000012790 confirmation Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q16/00—Equipment for precise positioning of tool or work into particular locations not otherwise provided for
- B23Q16/02—Indexing equipment
- B23Q16/08—Indexing equipment having means for clamping the relatively movable parts together in the indexed position
- B23Q16/10—Rotary indexing
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Machine Tool Positioning Apparatuses (AREA)
- Actuator (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は機械類の割出しクランプする部材に使用される
好適なりランプシリンダに関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a lamp cylinder suitable for use in indexing and clamping members of machinery.
従来技術
工作機械例えば旋盤などのタレント刃物台のタレットは
加工に対応して必要工具が割出される。In the turret of a talent tool rest of a conventional machine tool such as a lathe, the necessary tools are determined in accordance with the machining process.
この割出しのときにタレットは刃物台本体から油圧によ
って浮き上がらせられてカーピックカップリングの噛合
いを外して旋回され、割出し位置でタレットが引き込ま
れて再びカービックカップリングを噛合わせ刃物台本体
にクランプされる。この作動にはピストンシリンダ機構
が用いられる。During this indexing, the turret is lifted up from the tool post body by hydraulic pressure, disengages the car pick coupling, and rotates. At the indexing position, the turret is retracted and engages the car pick coupling again, causing the turret to engage. Clamped to the main body. A piston cylinder mechanism is used for this operation.
発明が解決しようとする問題点
強力な切削、若しくは大形工具を用いることが多くなり
タレットのクランプ力はこれに対応して強くする必要が
あり、大径のシリンダ、ピストンにより大きな力を得て
いた。このようにシリンダが大径となると容積が大きく
なりタレットの往復移動の時間が長くなって作業効率を
悪くしていた。Problems to be solved by the invention As powerful cutting or large tools are often used, the clamping force of the turret needs to be correspondingly strong. Ta. As described above, when the diameter of the cylinder becomes large, the volume becomes large, and the time required for the reciprocating movement of the turret becomes long, which deteriorates work efficiency.
問題点を解決するための手段
中央を大径部4aとしその両側を小径部とした段付シリ
ンダ4と、該段付シリンダ4の大径部4a及び両側の小
径部4bI、4b1にそれぞれ嵌装するとともにクラン
プ体を取付けるピストンロッド3を有する段付ピストン
5と、該段付ピストン5で両側に分けられた前記大径部
の室4a1,4a2を連通させる流路20.21を開閉
する弁部材17.47と、前期段付シリンダ4のクラン
プ作用方向の大径部の室4a+ と小径部の室4b、と
をクランプ方向のピストン移動の終端近(から連通させ
る流路5Cと、該連通される大径部の室4a、の反対側
の大径部の室4a!の排出流路26を絞るクンシラン絞
り弁19とを含んでなるものである。Means for Solving the Problems A stepped cylinder 4 with a large diameter section 4a at the center and small diameter sections on both sides, and fittings into the large diameter section 4a and small diameter sections 4bI and 4b1 on both sides of the stepped cylinder 4, respectively. and a valve member that opens and closes a flow path 20.21 that communicates the stepped piston 5 having the piston rod 3 to which the clamp body is attached, and the large diameter chambers 4a1 and 4a2 divided on both sides by the stepped piston 5. 17.47, and a flow path 5C that connects the large diameter chamber 4a+ and the small diameter chamber 4b of the stepped cylinder 4 in the clamping direction near the end of the piston movement in the clamping direction. It includes a clivia throttle valve 19 that throttles the discharge passage 26 of the large diameter chamber 4a on the opposite side of the large diameter chamber 4a!.
実施例
以下本発明の実施例を図面にもとづき説明するや旋盤の
タレット刃物台を例として説明する。Embodiments Hereinafter, embodiments of the present invention will be described based on the drawings, and a turret tool rest of a lathe will be explained as an example.
刃物台1にタレット2が旋回軸3によって旋回軸方向移
動可能に水平に軸承されている。クランプ用段付シリン
ダ4の中央の大径部4a、その両側の同径の小径部にそ
れぞれ嵌装される大径部51、その両側に小径部5bx
5btを有するピストン5が旋回軸3と同心一体に形成
されており、前側小径部5b+ にはピストンの右行移
動終端近傍でシリンダの大径部の室4a1 と小径部の
室4b、とを連通ずる切欠き5Cが外周軸方向に削設さ
れている。旋回軸3にはタレットの割出し角度に対応し
て円周に切欠きを削設した割出し円板6゜タレット旋回
用歯車7及び後端に割出し角度検出器8.ドック9とが
設けられている。またタレット2の背面には同心にカー
ピックカップリング1Oaが取付けられており、刃物台
1側の対向く面に相手側のカーピックカップリング10
bが同心に固着されている。さらに割出し円板6と直角
方向の位置決め用のシリンダ11に嵌装したピストン1
2のピストンロッド端が位置決めノツチ13となってい
て円板6の切欠きに嵌入され粗位置が決められる。タレ
ット旋回用歯車7は中間歯車14を介して油圧モータ1
5で旋回され、トング9は近接スイッチ16とでカーピ
ックカップリング10a、10bのクランプを確認する
。A turret 2 is horizontally supported on a tool rest 1 by a pivot shaft 3 so as to be movable in the direction of the pivot shaft. The large diameter part 4a at the center of the stepped cylinder 4 for clamping, the large diameter parts 51 fitted into the small diameter parts of the same diameter on both sides thereof, and the small diameter parts 5bx on both sides thereof.
A piston 5 having a diameter of 5 bt is formed concentrically with the pivot shaft 3, and a front small diameter portion 5b+ connects a large diameter portion chamber 4a1 and a small diameter portion chamber 4b of the cylinder near the end of rightward movement of the piston. A communicating notch 5C is cut in the direction of the outer circumferential axis. The rotation shaft 3 is equipped with an indexing disc 6° with a notch cut on its circumference corresponding to the indexing angle of the turret, a gear 7 for rotating the turret, and an indexing angle detector 8 at the rear end. A dock 9 is provided. In addition, a car pick coupling 1Oa is installed concentrically on the back of the turret 2, and a car pick coupling 10a on the opposite side of the turret 1 side is mounted on the opposite side of the turret 1.
b are fixed concentrically. Furthermore, the piston 1 is fitted into a cylinder 11 for positioning in a direction perpendicular to the index disk 6.
The end of the piston rod 2 is a positioning notch 13, which is inserted into a notch in the disc 6 to determine the rough position. The turret rotation gear 7 is connected to the hydraulic motor 1 via an intermediate gear 14.
5, the tongs 9 confirm the clamping of the car pick couplings 10a, 10b with the proximity switch 16.
クランプ用段付シリンダ4の大径部4aはピストン5の
大径部5aによって前側大径部の室4al、後側大径部
の室4a、に分けられ、この両室はパイロットチェック
弁17を介して油路20,21で連通されている。そし
てパイロ7トチエツク弁17のバイロフト圧が後述シリ
ンダ4の後側小径部の室4b8からとられている。また
クランプ用シリンダの前側小径部の室4b、は流路22
によってシリンダ11の後室11aに連通され後室11
aの油路23が2位置切換電磁弁41を介し逆止弁42
を介して圧力側または排出側に接続されている。またク
ランプ用段付シリンダの後側小径部の室4bxは油路2
4によって2位置切換電磁弁41.逆止弁42を介して
圧力側または排出側に接続されている。そして前側小径
部の室4b+の油路22とシリンダ11の油路23との
間をクランキング用の逆止弁1Bを介挿した油路25に
よって連通されピストン12によって油路22が閉じら
れたときの側路となっている。また後側の大径部の室4
8xの油路21がクランプ時のクフシ四ンのための温度
補償形の流量絞り弁19を介して油路26で排出側に接
続されている。またシリンダ11の前室11bが油路2
7によって流路24に接続されている。The large diameter portion 4a of the stepped cylinder 4 for clamping is divided by the large diameter portion 5a of the piston 5 into a front large diameter chamber 4al and a rear large diameter chamber 4a, and both chambers are connected to a pilot check valve 17. The oil passages 20 and 21 communicate with each other. The biloft pressure of the pyro-7 check valve 17 is taken from a chamber 4b8 in the rear small diameter portion of the cylinder 4, which will be described later. In addition, the chamber 4b in the small diameter portion on the front side of the clamp cylinder has a flow path 22.
The rear chamber 11 is communicated with the rear chamber 11a of the cylinder 11 by
The oil passage 23 of a is connected to the check valve 42 via the 2-position switching solenoid valve 41.
connected to the pressure side or discharge side via. Also, the chamber 4bx in the small diameter part on the rear side of the stepped cylinder for clamping is the oil passage 2.
4 by two-position switching solenoid valve 41. It is connected to the pressure side or the discharge side via a check valve 42. The oil passage 22 of the chamber 4b+ in the front small diameter portion and the oil passage 23 of the cylinder 11 are communicated by an oil passage 25 in which a check valve 1B for cranking is inserted, and the oil passage 22 is closed by the piston 12. It has become a side road. Also, chamber 4 of the large diameter part on the rear side
An 8x oil passage 21 is connected to the discharge side by an oil passage 26 via a temperature-compensated flow rate restricting valve 19 for use when clamping. Also, the front chamber 11b of the cylinder 11 is connected to the oil passage 2.
7 to the flow path 24.
油圧モータ15の油路28.29は3位置切換電磁弁4
3.逆止弁42を介して圧力側に、また温度補償形の流
量絞り弁44.逆止弁42を介して排出側に接続されて
いる。そして流量絞り弁44に対するバイパス回路30
が温度補償形流量絞り弁45と旋回速度高低切換弁46
とで形成され高速旋回、低速旋回を可能としている。The oil passages 28 and 29 of the hydraulic motor 15 are connected to the 3-position switching solenoid valve 4.
3. On the pressure side via a check valve 42 and a temperature compensated flow restrictor 44 . It is connected to the discharge side via a check valve 42. and a bypass circuit 30 for the flow restrictor valve 44.
are the temperature compensated flow rate restrictor 45 and the swing speed high/low switching valve 46.
This enables high-speed and low-speed turning.
作用
クランプ状態にあったタレフト2が割出し指令されたと
する。タレット2をアンクランプするため切換電磁弁4
1が■位置に切換えられ、圧油は油路24よりクランプ
シリンダ4の後側小径部の室4bzに送られるとともに
位置決め用シリンダ11の前室11bに送られる。これ
によってノツチ13が外されピストン5が第1図で左行
される。Assume that the talleft 2, which is in the active clamp state, is commanded to index. Switching solenoid valve 4 for unclamping the turret 2
1 is switched to the ■ position, and pressure oil is sent from the oil passage 24 to the chamber 4bz of the rear small diameter portion of the clamp cylinder 4 and also to the front chamber 11b of the positioning cylinder 11. As a result, the notch 13 is removed and the piston 5 is moved to the left in FIG.
後側小径部の室4bgへの油圧がパイロット圧としてパ
イロットチェック弁17を開きピストンの左行により前
側大径部の室4a+ の油は押し出されて後側大径部の
室48tに送り込まれ、前側小径部の室4bt の油は
油路22.25より逆止弁18を開いて油路23より逆
止弁42を経て排出され(第2図)、カーピックカップ
リング10 a rlobの噛合いが外される。The oil pressure in the chamber 4bg of the rear small diameter section opens the pilot check valve 17 as pilot pressure, and the leftward movement of the piston pushes out the oil in the chamber 4a+ of the front large diameter section and sends it into the chamber 48t of the rear large diameter section. The oil in the chamber 4bt of the front small diameter portion opens the check valve 18 from the oil passage 22, 25, and is discharged from the oil passage 23 through the check valve 42 (Fig. 2), and the oil is discharged from the oil passage 23 through the check valve 42 (Fig. is removed.
次いで切換電磁弁43が■の中立位置から近回りする方
向の■ (または■)位置にそし、て切換電磁弁46が
1位置に切換えられ圧油が流路28より油圧モータ15
に送られ中間歯車14.歯車7を介して旋回軸3ととも
にタレフト2が高速旋回され角度検出器80割出信号で
切換電磁弁43は■位置とされる。この間高低切換弁4
6が■位置にされ油圧モータ15の戻り油が流量絞り弁
44を通過することによりタレフト2は減速される。Next, the switching solenoid valve 43 is switched from the neutral position (■) to the ■ (or ■) position, which is a shortcut direction, and the switching solenoid valve 46 is switched to the 1 position, and the pressure oil is transferred from the flow path 28 to the hydraulic motor 15.
intermediate gear 14. The tower shaft 2 is rotated at high speed together with the rotation shaft 3 via the gear 7, and the switching solenoid valve 43 is set to the position (2) by the index signal from the angle detector 80. During this time, the height switching valve 4
6 is set to the ■ position, and the return oil of the hydraulic motor 15 passes through the flow rate restricting valve 44, whereby the taleft 2 is decelerated.
切換電磁弁41が1位置に切換えられ、圧油は流路23
よりシリンダ11の後室11aに送られピストン12を
前進させてノツチ13を割出し板6に嵌入させ、さらに
油路22より前側小径部の室4b+ に送り込まれる。The switching solenoid valve 41 is switched to the 1 position, and the pressure oil flows through the flow path 23.
The oil is sent to the rear chamber 11a of the cylinder 11, moves the piston 12 forward to fit the notch 13 into the indexing plate 6, and is further sent through the oil passage 22 into the chamber 4b+ of the small diameter portion on the front side.
ピストン5が右行され(第3図)後側小径部の室4b、
の油は油路24より排出され後側大径部の室4agの油
は油路21よりバイロフトチェック弁17を経て前側大
径部の室4a、に送り込まれる。ピストン5の右行の終
端手前で切欠き5cにより前側小径部の室4b、に送ら
れた油は前側大径部の室4a、にも送られパイロットチ
ェック弁17を閉じる。このため後側大径部の室4al
の油は油路26.クランプクンシラン用の流量絞り19
を経て排出されクランプ時のクツシラン作用が行われる
(第4図)。When the piston 5 moves to the right (Fig. 3), the chamber 4b of the small diameter part on the rear side,
The oil in the chamber 4ag of the rear large diameter section is discharged from the oil passage 24, and the oil in the chamber 4ag of the rear large diameter section is sent from the oil passage 21 through the biloft check valve 17 to the chamber 4a of the front large diameter section. The oil sent to the front small-diameter chamber 4b by the notch 5c before the end of the rightward movement of the piston 5 is also sent to the front large-diameter chamber 4a, and closes the pilot check valve 17. Therefore, the chamber 4al of the rear large diameter part
The oil is in oil line 26. Flow restrictor 19 for Clamp Clivia
It is discharged through the process and is subjected to the action of kutsushiran during clamping (Fig. 4).
そしてカービックカップリング10a、10bは前側大
径部の室4a、と前側小径部の室4b。The curvic couplings 10a and 10b have a chamber 4a at the front large diameter section and a chamber 4b at the front small diameter section.
との広い面積に作用する油圧力により強い力で噛合わさ
れクランプされる。近接スイッチ16からはクランプ確
認信号が出力される切換電磁弁43は■位置となる。They are engaged and clamped with strong force by hydraulic pressure acting on a wide area. The switching solenoid valve 43, to which the clamp confirmation signal is output from the proximity switch 16, is in the ■ position.
実施例第2
第5図においてパイロットチェック弁17に代えてオン
かオフかを引換える切換電磁弁47となしたもので、こ
の場合は前側大径部の室4a、 と後側大径部の室4a
、とを連通させる必要のあるときパイロットチェック弁
17が開く同じときに指令により開路される。この作用
は前記と同じである。なお切換弁47は他の同等の作用
を有するものなら使用可能であり限定されない。Embodiment 2 In Fig. 5, the pilot check valve 17 is replaced with a switching solenoid valve 47 that switches between on and off. Room 4a
, and at the same time that the pilot check valve 17 opens when it is necessary to establish communication between the two, the circuit is opened by a command. This effect is the same as described above. Note that the switching valve 47 is not limited and can be used as long as it has the same function.
効果 以上詳述したように本発明はタレフト等を旋回。effect As detailed above, the present invention rotates the taleft and the like.
割出クランプする油圧シリンダ、ピストンを大径部の両
側に小径部を有する段付となしたので、小径部に圧油を
送って急速移動をさせることができる。またクランプの
ときのように大きな力を必要とする側の大径部、小径部
をクランプ時点で連通させるようになしたので、シリン
ダの全面積に圧油を作用させて大きな力をうろことがで
き、圧油ポンプの能力を変更することなく急速移動と強
力クランプを容易に得ることができる効果を有する。Since the hydraulic cylinder and piston for indexing and clamping are stepped with small diameter parts on both sides of the large diameter part, pressure oil can be sent to the small diameter part for rapid movement. In addition, the large-diameter part and small-diameter part on the side that requires a large force, such as when clamping, are communicated at the time of clamping, so that pressure oil can be applied to the entire area of the cylinder and large forces cannot be applied. This has the effect of making it possible to easily obtain rapid movement and strong clamping without changing the capacity of the pressure oil pump.
第1図は本発明のクランプシリンダをタレント刃物台に
組合わせた説明図、第2図はアンクランプ開始時のシリ
ンダの状態を示す図、第3図はクランプ開始時のシリン
ダの状態を示す図、第4図はクランプ時のシリンダの状
態図、第5図はシリンダ大径部の室のオン、オフ弁の他
の実施例を示す説明図である。
2・・タレフト 3・・旋回軸
4・・クランプシリンダ
4a+、48g ・・大径部の室
4b1.4bg ・・小径部の室 5・・ピストン5
a・・大径部 sb、、5b、 ・・小径部17・・
バイロフトチェック弁
18・・逆止弁 19・・絞り弁
47・・切換電磁弁
第5′rl!JFig. 1 is an explanatory diagram of the clamp cylinder of the present invention combined with a talent tool post, Fig. 2 is a diagram showing the state of the cylinder at the start of unclamping, and Fig. 3 is a diagram showing the state of the cylinder at the start of clamping. 4 is a state diagram of the cylinder during clamping, and FIG. 5 is an explanatory diagram showing another embodiment of the on/off valve for the chamber in the large diameter portion of the cylinder. 2...Talleft 3...Swivel shaft 4...Clamp cylinder 4a+, 48g...Large diameter chamber 4b1.4bg...Small diameter chamber 5...Piston 5
a...Large diameter part sb,,5b,...Small diameter part 17...
Viloft check valve 18... Check valve 19... Throttle valve 47... Switching solenoid valve No. 5'rl! J
Claims (5)
リンダと、該段付シリンダの大径部及び両側の小径部に
それぞれ嵌装するとともにクランプ体を取付けるピスト
ンロッドを有する段付ピストンと、該段付ピストンで両
側に分けられた前記大径部の室を連通させる流路を開閉
する弁部材と、前記段付シリンダのクランプ作用方向の
大径部の室と小径部の室とをクランプ方向のピストン移
動の終端近くから連通させる流路と、該連通される大径
部の室の反対側の大径部の室の排出流路を絞るクッショ
ン絞り弁とを含んでなり小径部の室に圧油が送られ急速
送り、小径部の室と大径部の室との面積によってクラン
プすることを特徴とするクランプシリンダ。(1) A stepped cylinder having a large diameter part in the center and small diameter parts on both sides, and a stepped cylinder having a piston rod that fits into the large diameter part and the small diameter parts on both sides of the stepped cylinder and has a clamp body attached thereto. a piston, a valve member that opens and closes a flow path that communicates the large-diameter chamber divided into both sides by the stepped piston, and a large-diameter chamber and a small-diameter chamber in the clamp action direction of the stepped cylinder; and a cushion throttle valve that throttles the discharge flow path of the large-diameter chamber on the opposite side of the large-diameter chamber that communicates with the small-diameter chamber from near the end of piston movement in the clamping direction. A clamp cylinder characterized in that pressurized oil is sent rapidly to a chamber in the section, and clamping is performed by the area of a chamber in a small diameter section and a chamber in a large diameter section.
範囲第1項記載のクランプシリンダ。(2) The clamp cylinder according to claim 1, wherein the valve member is a pilot check valve.
請求の範囲第1項記載のクランプシリンダ。(3) The clamp cylinder according to claim 1, wherein the valve member is a solenoid valve that selects opening and closing.
囲第1項、第2項、第3項何れか1項に記載のクランプ
シリンダ。(4) The clamp cylinder according to any one of claims 1, 2, and 3, wherein the small diameter portions of the stepped cylinders have the same diameter.
切欠き溝である特許請求の範囲第1項乃至第4項の何れ
か1項に記載のクランプシリンダ。(5) The clamp cylinder according to any one of claims 1 to 4, wherein the flow path to be communicated is a notch groove formed in the small diameter portion of the piston.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62136385A JPS63300840A (en) | 1987-05-30 | 1987-05-30 | Clamp cylinder |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP62136385A JPS63300840A (en) | 1987-05-30 | 1987-05-30 | Clamp cylinder |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS63300840A true JPS63300840A (en) | 1988-12-08 |
JPH0526627B2 JPH0526627B2 (en) | 1993-04-16 |
Family
ID=15173917
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP62136385A Granted JPS63300840A (en) | 1987-05-30 | 1987-05-30 | Clamp cylinder |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS63300840A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05177509A (en) * | 1991-08-12 | 1993-07-20 | Daikin Ind Ltd | Position dividing device |
JPH06173908A (en) * | 1992-12-01 | 1994-06-21 | Smc Corp | Cylinder device |
JP2007536477A (en) * | 2004-05-07 | 2007-12-13 | ドクトル インジエニエール ハー ツエー エフ ポルシエ アクチエンゲゼルシヤフト | Hydraulic linear drive, especially hydraulic variable speed transmission actuator |
JP2014055659A (en) * | 2012-09-14 | 2014-03-27 | Sugino Machine Ltd | Non-pulsation pump |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5852302U (en) * | 1981-10-03 | 1983-04-09 | 株式会社大隈鐵工所 | rapid clamping device |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5852302B2 (en) * | 1979-01-18 | 1983-11-21 | 豊化学工業株式会社 | Electrode plate for alkaline storage battery |
-
1987
- 1987-05-30 JP JP62136385A patent/JPS63300840A/en active Granted
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5852302U (en) * | 1981-10-03 | 1983-04-09 | 株式会社大隈鐵工所 | rapid clamping device |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05177509A (en) * | 1991-08-12 | 1993-07-20 | Daikin Ind Ltd | Position dividing device |
JPH06173908A (en) * | 1992-12-01 | 1994-06-21 | Smc Corp | Cylinder device |
JP2007536477A (en) * | 2004-05-07 | 2007-12-13 | ドクトル インジエニエール ハー ツエー エフ ポルシエ アクチエンゲゼルシヤフト | Hydraulic linear drive, especially hydraulic variable speed transmission actuator |
JP4757257B2 (en) * | 2004-05-07 | 2011-08-24 | ドクター エンジニール ハー ツェー エフ ポルシェ アクチエンゲゼルシャフト | Hydraulic linear drive, especially hydraulic variable speed transmission actuator |
JP2014055659A (en) * | 2012-09-14 | 2014-03-27 | Sugino Machine Ltd | Non-pulsation pump |
Also Published As
Publication number | Publication date |
---|---|
JPH0526627B2 (en) | 1993-04-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US4065988A (en) | Unitary work changer for a machining center | |
EP0888840B1 (en) | A cutting-off method of an automatic lathe and an automatic lathe | |
JPS63300840A (en) | Clamp cylinder | |
US2389746A (en) | Lathe and method of making the same | |
US4013176A (en) | Unitary work changer for a machining center | |
US2114284A (en) | Machine tool and control therefor | |
JPH03228506A (en) | Composite machining device incorporating tool bed which can exchange stationary and rotary tools | |
JPH0364271B2 (en) | ||
US4738171A (en) | Multiple-spindle lathe | |
JP2000107916A (en) | Four-jaw type automatic chucking device for machine tool | |
US4070935A (en) | Chucking device for a machine tool | |
JPH0632263Y2 (en) | Hydraulic pressure supply / discharge device with switchable pressure for hydraulic clamp | |
JP3438478B2 (en) | Spindle drive | |
JPH0627327Y2 (en) | Air motor shock absorber | |
WO2022269744A1 (en) | Nc table with chuck | |
US4209180A (en) | Self-centering work holding and positioning fixture for machine tools | |
JPH0524432Y2 (en) | ||
CN219275560U (en) | Multi-grinding wheel trimming device suitable for compound grinding machine and compound grinding machine | |
US3081103A (en) | Chuck especially for lathes | |
KR100326358B1 (en) | Turret for computerized numerically controlled machine | |
RU2215912C2 (en) | Hydraulic drive | |
JPH0426972B2 (en) | ||
SU1366299A1 (en) | Multispindle lathe | |
JP2765852B2 (en) | Hydraulic index motor | |
JPS63156644A (en) | Hydraulic indexing device |