WO1997002132A1 - Dispositif de cylindre a charge et vitesse elevee et procede de commande - Google Patents
Dispositif de cylindre a charge et vitesse elevee et procede de commande Download PDFInfo
- Publication number
- WO1997002132A1 WO1997002132A1 PCT/JP1996/001790 JP9601790W WO9702132A1 WO 1997002132 A1 WO1997002132 A1 WO 1997002132A1 JP 9601790 W JP9601790 W JP 9601790W WO 9702132 A1 WO9702132 A1 WO 9702132A1
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- cylinder
- piston
- child
- parent
- speed
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
- B30B1/323—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure using low pressure long stroke opening and closing means, and high pressure short stroke cylinder means
-
- 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
- B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7055—Linear output members having more than two chambers
- F15B2211/7056—Tandem cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press
Definitions
- the present invention relates to a high-speed, high-load cylinder device used for a drive source of a press, a machine tool, or the like, and a control method thereof.
- a high-speed cylinder a with a small pressure receiving area and a pressurized cylinder b with a large pressure receiving area are arranged vertically on the same central axis, and both cylinders a and pistons c and d are connected to each other by a piston rod e, and the upper end of the piston rod e projects upward from the high-speed cylinder a to the high-speed cylinder a.
- It employs a so-called double-ended double-cylinder structure.
- hydraulic pressure can be supplied to the high-speed cylinder a through the external piping and valves (not shown) to operate the pistons c and d at high speed, and then hydraulic pressure is supplied to the pressurized cylinder b It is designed to be able to cope with high loads by obtaining a large pressing force.
- the latter cylinder device has, in addition to the basic configuration almost the same as the former, a sequence in which the piston d of the pressurized cylinder b is opened and closed by the pilot pressure.
- Valve f is provided The sequence valve f is turned on and off to switch from high-speed operation to high-pressure operation. This allows for high-speed and high-load operation without the need for external piping and valves. You can do it.
- the former cylinder device cannot provide a large release force, so if it is used as a driving source such as a press, even if the die bites during the press work, it will not be caught by the die. There is a problem that the upper mold cannot be separated from the lower mold immediately after it cannot be released. Further, in the latter cylinder device, since the sequence valve f is installed in the piston d of the pressurized cylinder b, the maintainability of the sequence valve f is poor.
- the high-speed cylinder a has a double-sided cylinder structure. There is a problem that the height etc. becomes large and the press etc. becomes large.
- the piston rod on the high-speed cylinder a side is the same as the piston rod on the pressure cylinder b side, ie, both piston rods.
- the high-speed cylinder a uses an unnecessarily large piston rod e, which is uneconomical.
- the present invention has been made in order to improve the conventional disadvantages, and can be easily separated from the bite of the mold, the press and the like can be reduced in size, and an economical high-speed and high-load cylinder device and its control can be provided. It is intended to provide a method. Disclosure of the invention
- a first aspect of the high-speed / high-load cylinder device according to the present invention is as follows.
- a child cylinder with a small pressure receiving area and a parent cylinder with a large pressure receiving area are arranged vertically on the same central axis, and the pistons in the child cylinder and those in the parent cylinder are replaced with the screws of the parent cylinder.
- the cylinders are connected to each other by piston rods of smaller diameter cylinders than the piston rods, supply pressurized oil to the upper and lower chambers of the parent cylinder, and make a difference in the pressure receiving area between the two chambers.
- the piston is lowered at a high speed, and pressurized oil is supplied only to the upper chamber of the parent cylinder to compress and lower the piston, and the upper and lower chambers of the parent cylinder and the child cylinder are also cooled.
- pressurized oil is supplied to the lower chamber of the child cylinder and the lower chamber of the parent cylinder to raise the piston at a low speed.
- pressurized oil is supplied only to the lower chamber of the child cylinder to raise the piston at high speed.
- Another aspect of the high-speed, high-load cylinder device is that a child cylinder having a small pressure receiving area and a parent cylinder having a large pressure receiving area are arranged vertically on the same central axis, and the piston in the child cylinder is provided. And the piston in the parent cylinder are connected to each other by the piston rod of the child cylinder, which is smaller in diameter than that of the parent cylinder.
- the pressure oil is supplied to the lower chamber to lower the piston at high speed due to the pressure receiving area difference between the two chambers, and the oil is supplied to the upper chamber of the child cylinder and the upper chamber of the parent cylinder to apply the piston.
- the supply of pressurized oil to the upper and lower chambers of the parent cylinder and the upper and lower chambers of the child cylinder is stopped to pressurize and hold the toner.
- the piston is supplied at high speed by supplying pressurized oil only to the chamber.
- a first aspect of the method for controlling a high-speed, high-load cylinder device according to the present invention includes the above-mentioned device,
- the piston is lowered at high speed, then pressurized and lowered at high speed.
- the piston is lowered at high speed, then pressurized and lowered, fired and held, then raised at low speed, and then raised at high speed.
- the piston is depressurized, then depressurized and held, and then slowly decelerated.
- the slide can be moved up and down with a short change in position.
- safety for workers is also improved.
- a fourth aspect of the method for controlling a high-speed and high-load cylinder device according to the present invention is the above-mentioned device
- the piston is lowered at high speed, then pressurized and lowered, then pressurized and held, then pressurized and lowered, then further pressurized and held, then raised at low speed, and then raised at high speed. It is what was done.
- Figure 1 is an explanatory diagram of an example of a conventional high-speed, high-load cylinder device.
- FIG. 2 is an explanatory diagram of another example of a conventional high-speed, high-load cylinder device.
- FIG. 3 is a configuration diagram of one embodiment of a high-speed and high-load cylinder device according to the present invention.
- FIG. 4 is a detailed view of the switching valve portion of the embodiment.
- FIG. 5 is a configuration diagram of another embodiment of a high-speed, high-load cylinder device according to the present invention.
- FIG. 6 is a detailed view of the switching valve portion of the other embodiment.
- FIG. 7 is a curve diagram showing the relationship between the slide position and time according to the first example of the method for controlling a high-speed, high-load cylinder device according to the present invention.
- FIG. 8 is a curve diagram showing a relationship between a slide position and time according to a second example of the control method of the high-speed / high-load cylinder device according to the present invention.
- FIG. 9 is a curve diagram showing a relationship between a slide position and time according to a third example of the control method of the high-speed / high-load cylinder device according to the present invention.
- FIG. 10 is a curve diagram illustrating a relationship between a slide position and time according to a fourth example of the control method for the high-speed / high-load cylinder device according to the present invention.
- 1 is the cylinder body, which has a small pressure receiving area. It consists of a child cylinder 2 and a parent cylinder 3 with a large pressure receiving area. The child cylinder 2 and the parent cylinder 3 are provided on the same central axis in two upper and lower stages. The inner diameter of the child cylinder 2 is D2, and the inner diameter of the parent cylinder 3 is Dl. The pistons 2a and 3a are accommodated in these cylinders 2 and 3, respectively.
- reference numeral 4 denotes a hydraulic source composed of a variable flow pump, and the discharge pressure of the hydraulic source 4 is controlled by the servo valve 5 via the first and second conduits 6, 7 respectively.
- the lower chamber 2d of the cylinder 2 and the upper chamber 3c of the parent cylinder 3 are supplied.
- the first and second pipes 6 and 7 are branched on the way, and the branch pipes 6 a and 7 a are respectively connected via a pressure switching valve 8 and a differential circuit switching valve 9.
- each of the valves 8 and 9 includes a logic valve 8a, 9a and a pilot switching valve 8b, which controls ON and OFF of the logic valve 8a, 9a. 9 b.
- the upper chamber 2c of the secondary cylinder 2 is in communication with the atmosphere via the breather 10.
- the cylinder body 1 When this high-speed, high-load cylinder device is used as the drive source for the press, the cylinder body 1 is installed in the press crown, and the piston rod 3b of the parent cylinder 3 is mounted. Connect a slide (not shown) to the end.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c and the lower chamber 3d of the parent cylinder 3, respectively, and the hydraulic oil of the lower chamber 2d of the child cylinder 2 is supplied to the tank 1
- the piston 3b is lowered at high speed due to the difference between the pressure receiving area A1 of the upper chamber 3c and the pressure receiving area A2 of the lower chamber 3d.
- the logic valve of the pressure switching valve 8 is held while the servo valve 5 is maintained at the descending position 5a. 8a is turned on, and the logic valve 9a of the differential circuit switching valve 9 is turned off.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the lower chamber 2 d of the child cylinder 2 and the lower chamber 3 d of the parent cylinder 3, and the oil is supplied to the upper chamber 3 c of the parent cylinder 3.
- Is discharged to tank 11, and pistons 2b and 3b start to rise.
- the pressure oil supplied to the lower chamber 3 d of the parent cylinder 3 and the lower oil 2 d of the child cylinder 2 Since the supplied pressure oil generates a large lifting force, the upper mold can be easily separated from the lower mold even if biting occurs.
- the logic valve 8a of the pressure switching valve 8 is turned off while the servo valve 5 is held at the ascending position 5b, and the differential circuit switching valve 9 is switched off.
- the logic valve 9a By turning on the logic valve 9a, the entire discharge pressure of the hydraulic pressure source 4 is supplied to the lower chamber 2d of the child cylinder 2, and at the same time, the oil of the upper chamber 3c of the parent cylinder 3 is discharged. Since the fluid flows into the lower chamber 3d of the parent cylinder 3 via the differential circuit switching valve 9, the slide can be raised to the top dead center at high speed.
- FIG. 5 and 6 show another embodiment of the high-speed and high-load cylinder device according to the present invention, which will be described below.
- the structure of the child cylinder 2 and the parent cylinder 3 is the same as that of the above embodiment, but a second pressure switching valve 13 comprising an electromagnetic valve is provided in the middle of the second pipe 7.
- a pipe 7b branched from the second pipe 7 is connected to the ink tank 11 via a pre-fill valve 14 which is turned on and off by a solenoid valve 15. ing.
- the specific circuit is as shown in FIG.
- the logic valve 8a of the first pressure switching valve 8 and the second pressure switching valve 13 are turned off, and the logic valve 9 of the differential switching valve 9 is turned off.
- the servo valve 5 is switched from the neutral position 5c to the descending position 5a.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3 and the lower chamber 3 d of the parent cylinder 3, and the pre-fill valve 1 is provided to the upper chamber 2 c of the child cylinder 2.
- the oil in tank 11 is sucked in through 4 and the pressure oil flows out from lower chamber 2 d to tank 11, so that pressure is received between upper chamber 3 c and lower chamber 3 d of parent cylinder 3.
- the slide is lowered at high speed by the difference in area.
- the logic valve 8a of the first pressure switching valve 8 and the second pressure switching valve 13 are turned on, and the logic valve 9a and the prefill valve 14 of the differential pressure circuit switching valve 9 are turned off.
- the servo valve 5 is switched to the ascending position 5b while holding the pressure, pressure oil is supplied to the lower chamber 2d of the child cylinder 2 and the lower chamber 3d of the parent cylinder 3, and the child oil is supplied to the lower chamber 3d.
- Pressure oil flows out from the upper chamber 2c of the cylinder 2 and the upper chamber 3c of the parent cylinder 3 to the tank 11 to generate a large lifting force. You can easily leave.
- the lower pressure of the child cylinder 2 is reduced.
- the pressurized oil is supplied to the chamber 2 d and the pressurized oil flows out from the upper chamber 2 c to the tank 11, and the oil in the upper chamber 3 c of the parent cylinder 3 is supplied through the differential circuit switching valve 9. Since it flows into the lower chamber 3d of the cylinder 3, the slide can be raised to the top dead center at a high speed.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c and the lower chamber 3d of the parent cylinder 3, respectively, and the pressure oil of the lower chamber 2d of the child cylinder 2 is supplied to the tank 1 Because of the difference between the pressure receiving area A 1 of the upper chamber 3 c and the pressure receiving area A 2 of the lower chamber 3 d, the slide connected to the piston 3 b as shown by 0 in FIG. Can be lowered at high speed.
- the pressurizing switching valve 8 is turned on while the servo valve 5 is held at the descending position 5a, and Turn off the differential circuit switching valve 9.
- the entire discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c of the parent cylinder 3 and the lower chamber 2d of the child cylinder 2 and the lower chamber 3d of the parent cylinder 3.
- the pressure oil flows out to the tank 11, so that the slide is further lowered to the bottom dead center while decelerating as shown by p in FIG. 7, and a large pressing force is obtained at this time.
- the servo valve 5 and the first and second pressurization switching valves 8 and 13 are required.
- the differential circuit switching valve 9 and the prefill valve 14 may be controlled as shown in Table 1 below.
- the slide is pressed down during processing, or the work is held in a pressurized state, or the work is lifted slightly at low speed. In some cases, the pressure is released, and the slide position change curve at this time is as shown in FIG. 8, for example.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c and the lower chamber 3d of the parent cylinder 3, respectively, and the hydraulic oil of the lower chamber 2d of the child cylinder 2 is supplied to the tank.
- the slide connected to piston 3b is caused by the difference between the pressure receiving area A1 of the upper chamber 3 of the parent cylinder 3 and the pressure receiving area A2 of the lower chamber 3d, as shown in Fig. 8. It is lowered at high speed as shown by 0 in FIG. If the slide descends to the required position and the pressure is required, the pressure switching valve 8 is turned on while the servo valve 5 is kept at the descending position 5a, and the differential Turn circuit switching valve 9 off.
- the entire discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c of the parent cylinder 3, and the lower chamber 2d of the child cylinder 2 and the lower chamber 3 of the parent cylinder 3 Since the pressurized oil of d flows out to the tank 11, the slide is further lowered to the bottom dead center while decelerating, as shown by p in FIG. 8, and a large pressing force is obtained at this time.
- the servo valve 5 is once returned to the neutral position 5c with the pressure switching valve 8 turned on and the differential circuit switching valve 9 turned off. Then, the slide is stopped at that position as shown by q in FIG. 8, so that the work can be pressed and held. Then, when the servo valve 5 is switched to the ascending position 5b while the pressure switching valve 8 is turned on and the differential circuit switching valve 9 is turned off, the discharge pressure of the hydraulic power source 4 is changed to the child cylinder. 2 lower room 2d and below parent cylinder 3 Since it is supplied to the chamber 3d at the same time, the slide starts to rise at a low speed as shown in r of Fig. 8, whereby the pressure on the work is gradually released, so-called pressure relief is performed. .
- the servo valve 5 is switched from the neutral position 5c to the descending position 5a, the pressure switching valve 8 is turned on, and the differential circuit is switched. Turn valve 9 off.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c of the parent cylinder 3 and the pressure of the lower chamber 3d of the parent cylinder 3 and the lower chamber 2d of the child cylinder 2 are increased.
- the slide is lowered at a low speed as indicated by 0 in FIG.
- the servo valve 5 When the workpiece is pressurized and held by lowering the slide to the predetermined position, the servo valve 5 is set to the neutral position 5 c with the pressure switching valve 8 turned on and the differential circuit switching valve 9 turned off. Switch to
- the slide can be moved up and down with a short change in position, so work efficiency can be improved, especially in work such as coining, and work can be done with a small change in position, improving safety for workers. .
- the servo valve 5 and the first and second pressurization switching valves 8 and 13 are required.
- the differential circuit switching valve 9 and the prefill valve 14 may be controlled as shown in Table 3 below.
- the discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3 and the lower chamber 3d of the parent cylinder 3, respectively, and the hydraulic oil of the lower chamber 2d of the child cylinder 2 is supplied to the tank 1 As it flows out to 1, the slide connected to the buston 3b is driven at a high speed as shown by 0 in Fig. 10 due to the difference between the pressure receiving area A1 of the upper chamber 3c and the pressure receiving area A2 of the lower chamber 3d. To be lowered.
- the pressurizing switching valve 8 is turned on while the servo valve 5 is maintained at the descending position 5a. To turn off the differential circuit switching valve 9.
- the entire discharge pressure of the hydraulic pressure source 4 is supplied to the upper chamber 3c of the parent cylinder 3, and the lower chamber 2d of the child cylinder 2 and the lower chamber 3d of the parent cylinder 3.
- the pressurized oil flows out to the tank 11, so that the slide is decelerated and lowered while pressurizing the work as shown by p in FIG.
- the servo valve 5 is switched to the neutral position 5c with the pressure switching valve 8 turned on and the differential circuit switching valve 9 turned off. Then, the slide is stopped at that position as shown by q in FIG. 10, so that the work can be held under pressure.
- the servo valve 5 When the workpiece is pressurized and held by the slide that has reached the bottom dead center, the servo valve 5 is set to the neutral position with the pressure switching valve 8 turned on and the differential circuit switching valve 9 turned off. Switch to 5c. Then, the slide is stopped at that position as shown by s in FIG. 10, so that the work can be held under pressure.
- the servo valve 5 When performing so-called depressurization from a state in which the work is being held under pressure, the servo valve 5 is raised while the pressure switching valve 8 is turned on and the differential circuit switching valve 9 is turned off. Switch to 5b.
- the discharge pressure of the hydraulic pressure source 4 is simultaneously supplied to the lower chamber 2 of the child cylinder 2 and the lower chamber 3d of the parent cylinder 3, and the oil in the upper chamber 3c of the parent cylinder 3 is discharged. Since it flows into tank 11, the slide starts rising at a low speed as shown by t in Fig. 10, and the pressure of the work is gradually released to release the pressure.
- the total discharge pressure of the hydraulic power source 4 is reduced.
- the oil is supplied to the lower chamber 2 of the child cylinder 2 and at the same time, the oil in the upper chamber 3c of the parent cylinder 3 flows into the lower chamber 3d of the parent cylinder 3 through the differential circuit switching valve 9, so that the C is quickly raised to the top dead center as shown by u in FIG.
- the servo valve 5 in order to obtain the slide position change curve shown in FIG. 10 in the circuit of another embodiment shown in FIG. 5, the servo valve 5, the first and second pressure switching valves 8, 13
- the differential circuit switching valve 9 and the prefill valve 14 may be controlled as shown in Table 4 below.
- the high-speed high-load cylinder device of the present invention is used as a slide drive source for a press.
- the present invention provides a child cylinder piston rod connecting a child cylinder piston and a parent cylinder biston, with the parent cylinder piston rod.
- the pressure receiving areas of the upper and lower chambers of the parent cylinder are made different, and this difference in pressure receiving area enables high-speed operation, and at the time of high load, the parent cylinder has a large pressure receiving area.
- the use of a one-sided cylinder as the child cylinder allows the overall length of the cylinder body to be shortened, which allows the high-speed and high-load cylinder according to the present invention to be used as a drive source for presses and the like. In this case, the overall height of the press can be reduced, so that the size of the press can be reduced and rigidity can be improved. Furthermore, by reducing the diameter of the piston rod on the secondary cylinder side, the weight and cost of the secondary cylinder side can be reduced.
- the high-speed / high-load cylinder device is controlled so as to descend at a high speed, descend at a high pressure and rise at a high speed.
- a slide position change curve suitable for blanking, bending, or coining can be obtained.
- the mold can be formed without a surge load as compared with the conventional molding using a mechanical press, so that the mold is less worn or damaged and the mold is reduced. The life is improved.
- the number of steps is smaller than that of the conventional one in which these processes are performed in separate steps, so that the number of steps required for molding can be reduced.
- the number of steps can be reduced as compared with the case of molding by a conventional mechanical press, and thus productivity is improved.
- the number of molds used can be reduced due to the reduction in the number of processes, so that the cost of molds can be reduced.
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/981,744 US6003429A (en) | 1995-07-06 | 1996-06-27 | High speed and high-load cylinder device and method for controlling the same |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7/170740 | 1995-07-06 | ||
JP17074095A JP3807632B2 (ja) | 1995-01-25 | 1995-07-06 | 油圧プレスのシリンダ装置及びその制御方法 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997002132A1 true WO1997002132A1 (fr) | 1997-01-23 |
Family
ID=15910512
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1996/001790 WO1997002132A1 (fr) | 1995-07-06 | 1996-06-27 | Dispositif de cylindre a charge et vitesse elevee et procede de commande |
Country Status (5)
Country | Link |
---|---|
US (1) | US6003429A (ja) |
KR (1) | KR100265310B1 (ja) |
CN (1) | CN1192714A (ja) |
TW (1) | TW297800B (ja) |
WO (1) | WO1997002132A1 (ja) |
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WO1997004951A1 (fr) * | 1995-07-25 | 1997-02-13 | Komatsu Ltd. | Circuit de securite a haute vitesse pour presse hydraulique |
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- 1996-06-27 KR KR1019970709911A patent/KR100265310B1/ko not_active IP Right Cessation
- 1996-06-27 CN CN96196129A patent/CN1192714A/zh active Pending
- 1996-06-27 WO PCT/JP1996/001790 patent/WO1997002132A1/ja active IP Right Grant
- 1996-06-27 US US08/981,744 patent/US6003429A/en not_active Expired - Fee Related
- 1996-06-27 TW TW085107759A patent/TW297800B/zh active
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0867271A2 (en) * | 1997-03-26 | 1998-09-30 | Aida Engineering Co., Ltd. | Hydraulic press for forming metal plates |
EP0867271A3 (en) * | 1997-03-26 | 2000-03-15 | Aida Engineering Co., Ltd. | Hydraulic press for forming metal plates |
US6128987A (en) * | 1997-03-26 | 2000-10-10 | Aida Engineering Co., Ltd. | Hydraulic press for forming metal plates |
CN105109079A (zh) * | 2015-08-21 | 2015-12-02 | 浙江大学舟山海洋研究中心 | 一种超高速大行程大吨位冲床液压系统及其工作方法 |
Also Published As
Publication number | Publication date |
---|---|
KR100265310B1 (ko) | 2000-09-15 |
KR19990028590A (ko) | 1999-04-15 |
TW297800B (ja) | 1997-02-11 |
CN1192714A (zh) | 1998-09-09 |
US6003429A (en) | 1999-12-21 |
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