JPH0347700A - Outer load controller for press - Google Patents
Outer load controller for pressInfo
- Publication number
- JPH0347700A JPH0347700A JP1180598A JP18059889A JPH0347700A JP H0347700 A JPH0347700 A JP H0347700A JP 1180598 A JP1180598 A JP 1180598A JP 18059889 A JP18059889 A JP 18059889A JP H0347700 A JPH0347700 A JP H0347700A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- slide
- point
- pressure
- hydraulic chambers
- 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
- 230000001012 protector Effects 0.000 claims abstract description 12
- 230000001105 regulatory effect Effects 0.000 claims 1
- 230000004043 responsiveness Effects 0.000 abstract description 6
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 7
- 238000000465 moulding Methods 0.000 description 4
- 230000036316 preload Effects 0.000 description 4
- 238000001514 detection method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/22—Control arrangements for fluid-driven presses controlling the degree of pressure applied by the ram during the pressing stroke
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/28—Arrangements for preventing distortion of, or damage to, presses or parts thereof
- B30B15/281—Arrangements for preventing distortion of, or damage to, presses or parts thereof overload limiting devices
- B30B15/284—Arrangements for preventing distortion of, or damage to, presses or parts thereof overload limiting devices releasing fluid from a fluid chamber subjected to overload pressure
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Presses (AREA)
- Press Drives And Press Lines (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は複動メカニカルプレスのアウタ荷重制御装置
に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an outer load control device for a double-acting mechanical press.
従来複動メカニカルプレスに設けられたアウタ荷重制御
装置は、アウタスライドのポンインに設けられた油圧室
とハイドロブランクホルダの油圧室を管路で結ぶと共に
、ハイドロブランクホルダのエア室の圧力をエアレギュ
レータにより制御することにより、上記ポイントの油圧
室とハイドロブランクホルダの油圧室の圧力を制御する
ようになっている。The outer load control device installed in conventional double-acting mechanical presses connects the hydraulic chamber installed in the pop-in of the outer slide and the hydraulic chamber of the hydro blank holder with a conduit, and controls the pressure in the air chamber of the hydro blank holder using an air regulator. The pressure in the hydraulic chambers at the points mentioned above and the hydraulic chambers of the hydro blank holder is controlled by controlling the hydraulic pressure chambers.
しかし上記従来のアウタ荷重制御装置では、エアレギュ
レータによりハイドロブランクホルダのエア室の圧力を
制御する構成のため、精度及び応答性が低いと共に、特
に圧力変更時エアの温度が変化するため制御が不安定と
なる不具合があった。However, the conventional outer load control device described above has a configuration in which the pressure in the air chamber of the hydro blank holder is controlled by an air regulator, so the accuracy and responsiveness are low, and the control is unstable especially when the pressure is changed because the air temperature changes. There was a problem with stability.
またハイドロブランクホルダを介してアウタ荷重を間接
的に制御しているため、さらに精度及び応答性も悪くな
るなどの不具合もあった。Furthermore, since the outer load is indirectly controlled via the hydro blank holder, there are also problems such as further deterioration of accuracy and responsiveness.
この発明は上記不具合を改善する目的でなされたもので
、精度及び応答性を向上したプレスのアウタ荷重制御装
置を提供するようとするものである。This invention has been made for the purpose of improving the above-mentioned problems, and it is an object of the present invention to provide a press outer load control device with improved accuracy and responsiveness.
〔課題を解決するための手段及び作用〕この発明は上記
目的を達成するために、インナスライドとアウタスライ
ドを備えた複動メカニカルプレスにおいて、上記アウタ
スライドの各ポイント毎に設けられた油圧シリンダの油
圧室とオーバロードプロテクタの間を、オーバロードに
対してリリーフ機能を有するロジック弁を介して接続す
ると共に、上記油圧室内の油圧を、インナスライドの下
降位置毎に算出したポイント発生荷重に応じて制御され
るサーボ弁により可変制御することにより、油圧室の油
圧を直接制御できるようにして精度及び応答性を向上さ
せたプレスのアウタ荷重制御装置を提供するものである
。[Means and operations for solving the problem] In order to achieve the above object, the present invention provides a double-acting mechanical press equipped with an inner slide and an outer slide, in which a hydraulic cylinder is provided at each point of the outer slide. The hydraulic chamber and the overload protector are connected through a logic valve that has a relief function against overload, and the hydraulic pressure in the hydraulic chamber is adjusted according to the point generated load calculated for each lowered position of the inner slide. The present invention provides a press outer load control device that can directly control the hydraulic pressure in a hydraulic chamber through variable control using a controlled servo valve, thereby improving accuracy and responsiveness.
この発明の一実施例を図面を参照して詳述すると、図に
おいて１は複動メカニカルプレスに設けられたアウタス
ライドで、複数個所、例えば４個所にポイント２が設け
られており、これらポイント２に油圧シリンダ３が設け
られている。One embodiment of the present invention will be described in detail with reference to the drawings. In the drawing, reference numeral 1 denotes an outer slide provided on a double-acting mechanical press, and points 2 are provided at a plurality of locations, for example, four locations. A hydraulic cylinder 3 is provided at.
上記油圧シリンダ３内に収容されたピストン３ａはプラ
ンジャ３ｂと連結されていて、図示しないアウタスライ
ド駆動機構からの駆動力はプランジャ３ｂ及び油圧シリ
ンダ３の油圧室３ｃ内の油圧を介してアウタスライド１
へ伝達されるようになっている。The piston 3a housed in the hydraulic cylinder 3 is connected to a plunger 3b, and the driving force from an outer slide drive mechanism (not shown) is transmitted to the outer slide 1 through the plunger 3b and the hydraulic pressure in the hydraulic chamber 3c of the hydraulic cylinder 3.
It is now transmitted to
また上記油圧室３の油圧室３ｃは管路４及びロジック弁
５を介してオーバロードプロテクタ６の油圧室６ａと接
続されている。Further, the hydraulic chamber 3c of the hydraulic chamber 3 is connected to the hydraulic chamber 6a of the overload protector 6 via a conduit 4 and a logic valve 5.
上記ロジック弁５は圧縮ばね５ａで閉方向に付勢された
弁体５ｂを有していて、ばね室５ｂ側には管路４の圧力
がパイロット管路７及び電磁弁８を介して導入されてい
ると共に、ばね室５ｂと電磁弁８の間にはオーバロード
リリーフ弁９が設けられていて、オーバロード時ばね室
５ｂ内の圧力をタンク１０ヘドレンするようになってい
る。The logic valve 5 has a valve body 5b biased in the closing direction by a compression spring 5a, and the pressure of the pipe line 4 is introduced into the spring chamber 5b side via the pilot pipe line 7 and the electromagnetic valve 8. In addition, an overload relief valve 9 is provided between the spring chamber 5b and the electromagnetic valve 8, and drains the pressure inside the spring chamber 5b to the tank 10 in the event of an overload.
上記オーバロードプロテクタ６は油圧室６ａと、これよ
り面積の大きい空圧室６ｂを有していて、これら油圧室
６ａと空圧室６ｂにピストン杆６Ｃにより連結されたピ
ストン６ｄ、６ｅがそれぞれ収容されており、空圧室６
ｂにはエア源１２よりエアレギュレータ１３及びエアタ
ンク１４を介して一定圧のエアか供給され、このエア圧
によりピストン６ｄ、６ｅを介して油圧室６ａ内が加圧
されている。The overload protector 6 has a hydraulic chamber 6a and a pneumatic chamber 6b having a larger area. Pistons 6d and 6e connected to the hydraulic chamber 6a and the pneumatic chamber 6b by a piston rod 6C are housed, respectively. and pneumatic chamber 6
Air at a constant pressure is supplied from an air source 12 through an air regulator 13 and an air tank 14 to b, and this air pressure pressurizes the inside of the hydraulic chamber 6a through pistons 6d and 6e.
一方油圧シリンダ３の油圧室３ｃとロジック弁５の間を
接続する管路４の途中には、圧力センサ１５及びサーボ
弁１６が接続されているｇ圧力センサ１５は油圧室３ｃ
内の圧力を検出して制御装置１７へ出力すると共に、サ
ーボ弁１６は上記制御装置１７により制御されて、油圧
ポンプ１８より管路１９を介して上記油圧室３ｃへ供給
される油圧を制御するようになっている。On the other hand, a pressure sensor 15 and a servo valve 16 are connected in the middle of the pipe line 4 connecting between the hydraulic chamber 3c of the hydraulic cylinder 3 and the logic valve 5.
The servo valve 16 is controlled by the control device 17 to control the hydraulic pressure supplied from the hydraulic pump 18 to the hydraulic chamber 3c via the pipe line 19. It looks like this.
上記油圧ポンプ１８の吐出側には油圧室３ｃへ供給する
プリロード圧を高圧、低圧の２段階に切換えるプリロー
ド圧切換え弁２ｏが、またチエツク弁２１の下流側に電
磁弁２２を介してアキュムレータ２３が接続されている
。On the discharge side of the hydraulic pump 18, there is a preload pressure switching valve 2o for switching the preload pressure supplied to the hydraulic chamber 3c into two stages, high pressure and low pressure. It is connected.
なお図中２５は上記サーボ弁１６へ作動圧を供給する作
動油ポンプ、２６はタンクｌｏ内の作動油を冷却する冷
却ポンプ、２７はプランジャ３ｂの近傍に設置されて、
アウタスライド１のストロークリミットを検出するリミ
ットスイッチ２８はハイドロゾーンを検出するリミット
スイッチである。In the figure, 25 is a hydraulic oil pump that supplies operating pressure to the servo valve 16, 26 is a cooling pump that cools the hydraulic oil in the tank LO, and 27 is installed near the plunger 3b.
The limit switch 28 that detects the stroke limit of the outer slide 1 is a limit switch that detects the hydro zone.
また第２図において３０はアウタスライド１を上方へ付
勢するバランサ、３１はアウタスライド１に取付けられ
た金型を示す。Further, in FIG. 2, reference numeral 30 indicates a balancer that urges the outer slide 1 upward, and reference numeral 31 indicates a mold attached to the outer slide 1.
次に第３図に示すフローチャートを混えて作用を説明す
ると、制御装置１７には予めインナスライドのストロー
クＳに対する荷重パターンＲ１〜Ｒ４が設定値として設
定されており、またロータリカムに設けたエンコーダや
インナスライドに取付けたりニヤスケールなどのストロ
ーク検出器３３よりインナスライドのストロークが、さ
らにオーバロードプロテクタ６の空圧室６ｂ及びバラン
サ３０のエア圧や、スライド下死点におけるバランサ引
上げ力ｒなどがそれぞれ入力されている。Next, to explain the operation with reference to the flowchart shown in FIG. The stroke of the inner slide is input from a stroke detector 33 attached to the slide or a near scale, as well as the air pressure of the air pressure chamber 6b of the overload protector 6 and the balancer 30, the balancer pulling force r at the bottom dead center of the slide, etc. has been done.
いまオーバロードプロテクタ６を使用して従来と同様な
成形を行う場合は、電磁弁８をポジション８ｂにしてば
ね室５ｃ内の圧力をドレンさせることによりロジック弁
５を開放し、プリロード圧切換え弁２０は低圧側へ切換
える。If you want to use the overload protector 6 to perform molding similar to the conventional method, open the logic valve 5 by setting the solenoid valve 8 to position 8b to drain the pressure in the spring chamber 5c, and then open the preload pressure switching valve 20. switch to the low pressure side.
そしてサーボ弁１６をポジション１６ａにして設定荷重
を最大に設定すると共に、電磁弁２２をポジション２２
ｂにしてアキュムレータ２３を管路１９より切離す。Then, the servo valve 16 is set to position 16a to set the set load to the maximum, and the solenoid valve 22 is set to position 22.
The accumulator 23 is separated from the conduit 19 in step b.
この状態で成形することにより、アウタ荷重を最大とし
てアウタスライド１を追込むことができるようになる。By molding in this state, the outer load can be maximized and the outer slide 1 can be pushed in.
次にアウタ荷重を可変にして成形を行う場合は、電磁弁
８をポジション８ａにしてロジック弁６を閉にし、プリ
ロード圧切換え弁２ｏは高圧側へ切換える。Next, when molding is performed with variable outer load, the solenoid valve 8 is set to position 8a, the logic valve 6 is closed, and the preload pressure switching valve 2o is switched to the high pressure side.
また電磁弁２２をポジション２２ａにして管路１９ｔ、
ｌ：７キユムレータ２３を接続すると共に、オーバロー
ドプロテクタ６の空圧室６ｂへエアを供給するエアレギ
ュレータ１３、を圧力０に設定する。In addition, the solenoid valve 22 is set to the position 22a, and the pipe line 19t,
1:7 cumulator 23 is connected, and the air regulator 13, which supplies air to the pneumatic chamber 6b of the overload protector 6, is set to zero pressure.
そしてこの状態から成形を開始すると、まずアウタスラ
イド１が下死点まで下降して、図示しないダイクツショ
ンに弾性支持された下型側のブランクホルダ（ともに図
示せず）の間でブランクの周辺部を挟着する。When molding is started from this state, the outer slide 1 first descends to the bottom dead center, and the peripheral part of the blank is moved between blank holders (both not shown) on the lower die side that are elastically supported by a duct (not shown). to pinch.
一方制御装置１７は第３図に示すフローチャートに従っ
て各ポイント２毎のスライド重量Ｗ、〜４、金型重量ｗ
、〜４がらポイント発生荷重Ｆ、〜４を各ポイント毎に
次式により算出する。On the other hand, the control device 17 controls the slide weight W for each point 2, ~4, the mold weight w, according to the flowchart shown in FIG.
, ~4 The point generated load F, ~4 is calculated for each point using the following equation.
ＦＩ〜４−Ｒ１−４＋ Ｗ＋〜４−Ｗｌ−４そし
てインナスライドの各位置におけるポイント発生荷重を
、インナスライドのストロークＳやメーンモータの回転
数ＮよりスライドストロークＳ′を次式で補正した値よ
り求める。FI~4-R1-4+ W+~4-Wl-4 And the point generated load at each position of the inner slide is the value obtained by correcting the slide stroke S' using the following formula from the stroke S of the inner slide and the rotation speed N of the main motor. Seek more.
Ｓ’ −８−ｋＮ なおｋは比例常数上記のよ
うにして求められたインナスライドの各位置におけるポ
イント荷重は、増幅器により増幅されてサーボ弁１６へ
送られ、サーボ弁１６により油圧シリンダ３の油圧室３
ｃ内の油圧が制御されると共に、油圧室３ｃ内の油圧は
圧力センサ１５により検出されて制御装置１７ヘフイー
ドバツクされる。S' -8-kN Note that k is a proportional constant.The point load at each position of the inner slide determined as above is amplified by an amplifier and sent to the servo valve 16, which adjusts the hydraulic pressure of the hydraulic cylinder 3. Room 3
The hydraulic pressure in the hydraulic chamber 3c is controlled, and the hydraulic pressure in the hydraulic chamber 3c is detected by the pressure sensor 15 and fed back to the control device 17.
また上記動作中アウタスライド１にオーバロードが発生
すると、オーバロードリリーフ弁９がリリーフするため
ロジック弁５が開放する。Further, when an overload occurs on the outer slide 1 during the above operation, the overload relief valve 9 provides relief, and the logic valve 5 opens.
これによって油圧室３ｃ内の油圧がロジック弁５よりオ
ーバロードプロテクタ６ヘドレインされてオーバロード
が回避されると共に、圧力センサ１５が油圧室３ｃ内の
油圧が異常に低下したのを検出するため、サーボ弁１６
がポジション１６ａより１６ｂへ切換えられ、油圧室３
ｃ内の油圧がタンク１ｏヘトレンされる。As a result, the hydraulic pressure in the hydraulic chamber 3c is drained from the logic valve 5 to the overload protector 6 to avoid overload, and the pressure sensor 15 detects an abnormal decrease in the hydraulic pressure in the hydraulic chamber 3c, so the servo valve 16
is switched from position 16a to 16b, and the hydraulic chamber 3
The oil pressure in the tank 1o is transferred to the tank 1o.
さらにダイハイド調整にミスなどがあった場合は運転中
にハイドロゾーン検出用リミットスイッチ２８がこれを
検出して警報を出すと共に、ストロークリミット検出用
のリミットスイッチ２７も油圧システムに異常が発生し
たり、ダイハイド調整ミスがあった場合に警報を出すよ
うになっている。Furthermore, if there is a mistake in the die-hydro adjustment, the hydro zone detection limit switch 28 will detect this during operation and issue an alarm, and the stroke limit detection limit switch 27 will also detect an error in the hydraulic system. It is designed to issue an alarm if there is a mistake in die-hide adjustment.
この発明は以上詳述したように、インナスライドのスト
ローク位置に応じてアウタスライドのポイント荷重を制
御するようにしたもので、アウタスライドのポイントに
設けられた油圧室とオーバロードプロテクタの間をロジ
ック弁で遮断した状態で上記油圧室の油圧を直接制御す
るようにしたことから、精度の高い圧力調整が可能にな
ると共に、応答性も向上する。As described in detail above, this invention controls the point load of the outer slide according to the stroke position of the inner slide, and uses logic between the hydraulic chamber provided at the point of the outer slide and the overload protector. Since the hydraulic pressure in the hydraulic chamber is directly controlled in a state where it is shut off by a valve, highly accurate pressure adjustment is possible and responsiveness is also improved.
図面はこの発明の一実施例を示し、第１図は回路図、第
２図はポイントの荷重分布を示す説明図、第３図は作用
を示すフローチャートである。
１はアウタスライド、２はポイント、３は油圧シリンダ
、３ｃは油圧室、５はロジック弁、６はオーバロードプ
ロテクタ、１３はエアレギュレータ、１６はサーボ弁、
３０はバランサ。The drawings show an embodiment of the present invention, and FIG. 1 is a circuit diagram, FIG. 2 is an explanatory diagram showing load distribution at points, and FIG. 3 is a flow chart showing the operation. 1 is an outer slide, 2 is a point, 3 is a hydraulic cylinder, 3c is a hydraulic chamber, 5 is a logic valve, 6 is an overload protector, 13 is an air regulator, 16 is a servo valve,
30 is a balancer.
Claims (3)
メカニカルプレスにおいて、上記アウタスライド１の各
ポイント２毎に設けられた油圧シリンダ３の油圧室３ｃ
とオーバロードプロテクタ６の間を、オーバロードに対
してリリーフ機能を有するロジック弁５を介して接続す
ると共に、上記油圧室３ｃ内の油圧を、インナスライド
の下降位置毎に算出したポイント発生荷重に応じて制御
されるサーボ弁１６により可変制御してなるプレスのア
ウタ荷重制御装置。(1) In a double-acting mechanical press equipped with an inner slide and an outer slide 1, the hydraulic chamber 3c of the hydraulic cylinder 3 is provided at each point 2 of the outer slide 1.
and the overload protector 6 are connected via a logic valve 5 having a relief function against overload, and the hydraulic pressure in the hydraulic chamber 3c is adjusted to the point generated load calculated for each lowering position of the inner slide. A press outer load control device that is variably controlled by a servo valve 16 that is controlled accordingly.
プロテクタ６を調圧するエアレギュレータ１３を０に設
定してなる請求項１記載のアウタ荷重制御装置。(2) The outer load control device according to claim 1, wherein the air regulator 13 for regulating the pressure of the overload protector 6 is set to 0 when the hydraulic pressure of the hydraulic chamber 3c is variably controlled.
、バランサ３０の付勢力、金型重量分布及びスライド荷
重分布により補正して制御してなる請求項１記載のアウ
タ荷重制御装置。(3) The outer load control device according to claim 1, wherein the hydraulic pressure supplied to the hydraulic chambers 3c at each point 2 is corrected and controlled based on the biasing force of the balancer 30, the mold weight distribution, and the slide load distribution.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1180598A JPH0763879B2 (en) | 1989-07-14 | 1989-07-14 | Outer load control device for press |
| PCT/JP1990/000914 WO1991001215A1 (en) | 1989-07-14 | 1990-07-13 | Outer load controller of press |
| BR909007524A BR9007524A (en) | 1989-07-14 | 1990-07-13 | EXTERNAL LOAD CONTROL DEVICE FOR PRESS |
| EP19900910945 EP0496882A4 (en) | 1989-07-14 | 1990-07-13 | Outer load controller of press |
| KR1019920700031A KR920703323A (en) | 1989-07-14 | 1990-07-13 | Outer load control device of press |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1180598A JPH0763879B2 (en) | 1989-07-14 | 1989-07-14 | Outer load control device for press |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0347700A true JPH0347700A (en) | 1991-02-28 |
| JPH0763879B2 JPH0763879B2 (en) | 1995-07-12 |
Family
ID=16086061
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1180598A Expired - Fee Related JPH0763879B2 (en) | 1989-07-14 | 1989-07-14 | Outer load control device for press |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0496882A4 (en) |
| JP (1) | JPH0763879B2 (en) |
| KR (1) | KR920703323A (en) |
| BR (1) | BR9007524A (en) |
| WO (1) | WO1991001215A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996016795A1 (en) * | 1994-11-29 | 1996-06-06 | Komatsu Ltd. | Slide control method of hydraulic press |
| JP2011038615A (en) * | 2009-08-17 | 2011-02-24 | Sumitomo Heavy Industries Techno-Fort Co Ltd | Cooling oil quantity control device of wet type clutch brake in mechanical press |
| CN103331937A (en) * | 2013-07-04 | 2013-10-02 | 天津市天锻压力机有限公司 | Numerical control hydraulic machine decompression system based on pressure feedback |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2840381B1 (en) * | 2002-06-04 | 2006-07-07 | Linde Ag | HYDROSTATIC DRIVE SYSTEM, IN PARTICULAR FOR A TRANSPORT TROLLEY |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60261698A (en) * | 1984-06-07 | 1985-12-24 | Toyota Motor Corp | Method and device for controlling outer load of press |
| JPS6246198U (en) * | 1985-09-02 | 1987-03-20 | ||
| JPS62151300A (en) * | 1985-12-26 | 1987-07-06 | Komatsu Ltd | Over load protecting device for press machine |
-
1989
- 1989-07-14 JP JP1180598A patent/JPH0763879B2/en not_active Expired - Fee Related
-
1990
- 1990-07-13 KR KR1019920700031A patent/KR920703323A/en not_active Application Discontinuation
- 1990-07-13 WO PCT/JP1990/000914 patent/WO1991001215A1/en not_active Application Discontinuation
- 1990-07-13 BR BR909007524A patent/BR9007524A/en unknown
- 1990-07-13 EP EP19900910945 patent/EP0496882A4/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996016795A1 (en) * | 1994-11-29 | 1996-06-06 | Komatsu Ltd. | Slide control method of hydraulic press |
| US5673615A (en) * | 1994-11-29 | 1997-10-07 | Komatsu Ltd. | Slide control method in a hydraulic press |
| JP2011038615A (en) * | 2009-08-17 | 2011-02-24 | Sumitomo Heavy Industries Techno-Fort Co Ltd | Cooling oil quantity control device of wet type clutch brake in mechanical press |
| CN103331937A (en) * | 2013-07-04 | 2013-10-02 | 天津市天锻压力机有限公司 | Numerical control hydraulic machine decompression system based on pressure feedback |
Also Published As
| Publication number | Publication date |
|---|---|
| KR920703323A (en) | 1992-12-17 |
| EP0496882A4 (en) | 1992-11-04 |
| JPH0763879B2 (en) | 1995-07-12 |
| EP0496882A1 (en) | 1992-08-05 |
| BR9007524A (en) | 1992-06-23 |
| WO1991001215A1 (en) | 1991-02-07 |
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