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WO1991001215A1 - Controleur de charge exterieure de presse - Google Patents

Controleur de charge exterieure de presse Download PDF

Info

Publication number
WO1991001215A1
WO1991001215A1 PCT/JP1990/000914 JP9000914W WO9101215A1 WO 1991001215 A1 WO1991001215 A1 WO 1991001215A1 JP 9000914 W JP9000914 W JP 9000914W WO 9101215 A1 WO9101215 A1 WO 9101215A1
Authority
WO
WIPO (PCT)
Prior art keywords
slide
hydraulic
pressure
hydraulic chamber
load
Prior art date
Application number
PCT/JP1990/000914
Other languages
English (en)
Japanese (ja)
Inventor
Hidemi Moriyama
Original Assignee
Kabushiki Kaisha Komatsu Seisakusho
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kabushiki Kaisha Komatsu Seisakusho filed Critical Kabushiki Kaisha Komatsu Seisakusho
Priority to BR909007524A priority Critical patent/BR9007524A/pt
Priority to KR1019920700031A priority patent/KR920703323A/ko
Publication of WO1991001215A1 publication Critical patent/WO1991001215A1/fr

Links

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

Definitions

  • the present invention relates to a double-acting force dual-calm weight load control device.
  • a double load force control device provided on a dual-force press is equipped with a hydraulic chamber and a high port, which are provided at the points of the peta slide.
  • the hydraulic chamber of the blank holder is connected by a pipeline, and the pressure in the air chamber of the high-pressure blank holder is controlled by an air regulator.
  • the pressure in the hydraulic chamber of the above point and the hydraulic chamber of the hydro blank holder are controlled.
  • the present invention has been made in view of the circumstances described above, and the purpose thereof is to provide a high precision in pressure adjustment. It is another object of the present invention to provide a press water load control device having improved responsiveness.
  • a double-acting two-way press having an inner slide and a fatal slide.
  • a hydraulic cylinder of a hydraulic cylinder provided for each point of the peta slide and an overload protection are provided.
  • Logic valve that has a relief function with respect to the over-opening port and is calculated for each lower position of the inner slide.
  • a servo valve that is controlled in accordance with the generated point generated load, wherein the hydraulic pressure in the hydraulic chamber is variably controlled by the servo valve.
  • a load control device is provided.
  • the point load of the ataside slide is controlled in accordance with the stroke position of the inner slide.
  • the hydraulic chamber provided at the point of the atrium slide and the overload protector were shut off with the mouth lock valve. Since the hydraulic pressure in the hydraulic chamber is directly controlled, the pressure can be adjusted with high accuracy, and the responsiveness is also improved.
  • FIG. 1 is an overall circuit diagram showing a specific example of the present invention
  • FIG. 2 is an explanatory diagram showing the load distribution of the points
  • FIG. 3 is a flowchart showing the operation of the embodiment of the present invention.
  • reference numeral 1 denotes an outer slide provided on a double-acting mechanical press, and a plurality of slides are provided.
  • points 2 are provided at four locations, and a hydraulic cylinder 3 is provided at each of the points 2.
  • the piston 3a housed in each of the hydraulic cylinders 3 is connected to the plunger 3b, and is not shown in the drawing.
  • the driving force is transmitted to the outer slide 1 through the hydraulic pressure in the hydraulic chamber 3c of the plunger 3b and the hydraulic cylinder 3.
  • the hydraulic chamber 3c of the hydraulic chamber 3 is connected to the hydraulic chamber 6a of the outlet port 6 through a pipe 4 and a port valve 5.
  • the above-mentioned mouth lock valve 5 has a valve body 5b which is urged in the closing direction by a compression spring 5a, and the pressure of the pipe line 4 is piped to the spring chamber 5b side.
  • G In addition to being introduced through the conduit 7 and the solenoid valve 8, there is a gap between the spring chamber 5 b and the solenoid valve 8.
  • a relief valve 9 is provided so that the pressure in the spring chamber 5b is drained to the tank 10 during overload.
  • the above-mentioned nozzle protector 6 has a hydraulic chamber 6a and a pneumatic chamber 6b having a larger area than the hydraulic chamber 6a.
  • the pistons 6 d and 6 e connected by a piston rod 6 c to the air pressure chamber 6 b are accommodated respectively.
  • air at a constant pressure is supplied through the air regulator 13 and the air tank 14, and the air pressure causes the air to flow through the pistons 6 d and 6 e.
  • the hydraulic chamber 6a has an internal force ⁇ pressurized.
  • a pressure sensor 15 and a servo valve 16 are connected in the middle of the pipeline 4 connecting the hydraulic chamber 3 c of the hydraulic cylinder 3 and the logic valve 5. It has been done.
  • the pressure sensor 15 detects the pressure in the hydraulic chamber 3 c and outputs the detected value to the control device 17, and the servo valve 16 is controlled by the control device 17. Then, the hydraulic pressure supplied to the hydraulic chamber 3c from the hydraulic pump 18 via the pipeline 19 is controlled.
  • a pre-outlet-pressure switching valve 20 for switching the preload pressure supplied to the hydraulic chamber 3 c into two stages, high pressure and low pressure.
  • the accumulator 23 is connected to the downstream side of the check valve 21 via a solenoid valve 22.
  • reference numeral 25 denotes a hydraulic oil pump for supplying operating pressure to the above-mentioned servo valve 16
  • reference numeral 26 denotes a cooling pump for cooling the hydraulic oil in the tank 10
  • reference numeral 27 Is a limit switch which is installed near the projector 3b to detect the stroke limit of the data slide 1, and 28 is a hammer switch. Use the limit switch to detect the idle zone.
  • reference numeral 30 denotes a balancer for urging the anode slide 1 upward
  • 31 denotes a mold attached to the anode slide 1.
  • the controller 17 is provided with an inner slide in advance.
  • the load patterns R1 to R1 for the torque s are set as set values, and the encoder dinosaur provided in the mouthpiece Stroke detectors such as a linear skyliner attached to the inverter, 3 3 Air pressure in pneumatic chamber 6b and balancer 30 in evening 6, and pulling force r in bottom dead center of slide Which are input respectively
  • the solenoid valve 8 is set to the position 8 b and the inside of the spring chamber 5 c is set.
  • the logic valve 5 is opened and the preload pressure switching valve 20 is switched to the low pressure side.
  • set the set load to the maximum by setting the servo valve 16 to the position 16a, and move the solenoid valve 22 to the position 22b. Disconnect cumulator 23 from line 19.
  • the solenoid valve 8 is set to position 8a, the logic valve 6 is closed, and the preload pressure switching valve 20 is set to high pressure. Switch to the side.
  • the solenoid valve 22 is set to the position 22 a, the accumulator 23 is connected to the pipe line 19, and at the same time, the load is reduced. Set the pressure of the air regulator 13 that supplies air to the pneumatic chamber 6b in the evening 6 to zero.
  • the slide 1 descends to the bottom dead center and is elastically supported by a not-shown die cushion.
  • the periphery of the blank is clamped between the blank holders (not shown) on the lower mold side.
  • the controller 1 7 3 full b over Ji Ya one Bok scan la and follow each port Lee down bets every 2 to Lee de weight to 4 shown in the figure, the mold heavy H-4 forces, et al Po Lee
  • the point generated load-4 is calculated for each point by the following formula.
  • Point generation at each position on the inner slide The load is obtained by correcting the slide stroke S 'from the stroke S of the inner slide and the rotation speed N of the main motor by the following formula. Request.
  • the point load at each position of the inner slide obtained as described above is amplified by the amplifier and sent to the servo valve 16.
  • the hydraulic pressure in the hydraulic chamber 3 c of the hydraulic cylinder 3 is controlled by the servo valve 16, and the hydraulic pressure in the hydraulic chamber 3 c is controlled by the pressure sensor 15. It is detected and fed back to the controller 17.
  • the hydraulic pressure in the hydraulic chamber 3c is drained from the outlet lock valve 5 to the outlet port 6 and the outlet port is drained to the outlet 6. Is prevented, and the pressure sensor 15 detects that the oil pressure in the hydraulic chamber 3c has dropped abnormally. Therefore, the servo valve 16 is turned into the position 16 The pressure is switched to 16b from a, and the oil pressure in the hydraulic chamber 3c is drained to the tank 10.
  • the limit switch for hydro-zone detection is turned off.
  • the limit switch 27 for detecting the stroke limit also causes an abnormality in the hydraulic system, or the die-height adjustment mistake. Warn if there is 16160AV

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

Contrôleur de charge extérieure d'une presse visant à obtenir une précision élevée de la régulation de la pression et à améliorer la sensibilité de fonctionnement. Ledit contrôleur comprend une vanne logique (5) laquelle est connectée entre la chambre hydraulique (3c) d'un cylindre hydraulique (3) disposée au niveau de chaque point (2) d'une coulisse extérieure (1), ainsi qu'un dispositif de protection de surcharge (6), et laquelle a une fonction de libération en cas de surcharge, ainsi qu'une servo-vanne (16) commandée en fonction d'une charge de pointe calculée à chaque position de descente de la coulisse. La pression d'huile à l'intérieur de la chambre hydraulique est commandée de manière variable par la servo-vanne se trouvant dans ledit contrôleur.
PCT/JP1990/000914 1989-07-14 1990-07-13 Controleur de charge exterieure de presse WO1991001215A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
BR909007524A BR9007524A (pt) 1989-07-14 1990-07-13 Dispositivo de controle de carga externa para prensa
KR1019920700031A KR920703323A (ko) 1989-07-14 1990-07-13 프레스의 아웃터 하중 제어장치

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP1180598A JPH0763879B2 (ja) 1989-07-14 1989-07-14 プレスのアウタ荷重制御装置
JP1/180598 1989-07-14

Publications (1)

Publication Number Publication Date
WO1991001215A1 true WO1991001215A1 (fr) 1991-02-07

Family

ID=16086061

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1990/000914 WO1991001215A1 (fr) 1989-07-14 1990-07-13 Controleur de charge exterieure de presse

Country Status (5)

Country Link
EP (1) EP0496882A4 (fr)
JP (1) JPH0763879B2 (fr)
KR (1) KR920703323A (fr)
BR (1) BR9007524A (fr)
WO (1) WO1991001215A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3534326B2 (ja) * 1994-11-29 2004-06-07 株式会社小松製作所 油圧プレスのスライド制御方法
FR2840381B1 (fr) * 2002-06-04 2006-07-07 Linde Ag Systeme d'entrainement hydrostatique, notamment pour un chariot transport
JP2011038615A (ja) * 2009-08-17 2011-02-24 Sumitomo Heavy Industries Techno-Fort Co Ltd 機械プレスにおける湿式クラッチブレーキの冷却油量制御装置
CN103331937A (zh) * 2013-07-04 2013-10-02 天津市天锻压力机有限公司 基于压力反馈的数控液压机泄压系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS623720B2 (fr) * 1984-06-07 1987-01-26 Toyota Motor Co Ltd
JPS6246198U (fr) * 1985-09-02 1987-03-20
JPS62151300A (ja) * 1985-12-26 1987-07-06 Komatsu Ltd プレス機械の過荷重保護装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS623720B2 (fr) * 1984-06-07 1987-01-26 Toyota Motor Co Ltd
JPS6246198U (fr) * 1985-09-02 1987-03-20
JPS62151300A (ja) * 1985-12-26 1987-07-06 Komatsu Ltd プレス機械の過荷重保護装置

Also Published As

Publication number Publication date
EP0496882A1 (fr) 1992-08-05
KR920703323A (ko) 1992-12-17
JPH0763879B2 (ja) 1995-07-12
EP0496882A4 (en) 1992-11-04
JPH0347700A (ja) 1991-02-28
BR9007524A (pt) 1992-06-23

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