EP2384834B1 - Coussin de serre-flan hydraulique avec un vérin hydraulique - Google Patents

Coussin de serre-flan hydraulique avec un vérin hydraulique Download PDF

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Publication number
EP2384834B1
EP2384834B1 EP11164657.6A EP11164657A EP2384834B1 EP 2384834 B1 EP2384834 B1 EP 2384834B1 EP 11164657 A EP11164657 A EP 11164657A EP 2384834 B1 EP2384834 B1 EP 2384834B1
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EP
European Patent Office
Prior art keywords
hydraulic
working chamber
piston
cylinder
die cushion
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.)
Active
Application number
EP11164657.6A
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German (de)
English (en)
Other versions
EP2384834A2 (fr
EP2384834A3 (fr
Inventor
Michael Micklisch
Markus Dr. Müller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
L Schuler GmbH
Original Assignee
L Schuler GmbH
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Filing date
Publication date
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Publication of EP2384834A2 publication Critical patent/EP2384834A2/fr
Publication of EP2384834A3 publication Critical patent/EP2384834A3/fr
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Publication of EP2384834B1 publication Critical patent/EP2384834B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • B21D24/14—Devices controlling or operating blank holders independently, or in conjunction with dies pneumatically or hydraulically
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/02—Die-cushions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • 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
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control
    • 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
    • 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
    • F15B2211/76—Control of force or torque of the 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/765—Control of position or angle of the 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
    • F15B2211/70—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 invention relates to a hydraulic drawing cushion of a drawing press with a hydraulic cylinder.
  • the drawing press clamps a sheet between an upper tool and a lower tool.
  • the sheet is pulled over a lower molding and pressed between two moldings.
  • the sheet holding force required for drawing is provided by the die cushion.
  • the die cushion has a cylinder comprising three working chambers. Two of the working chambers operate pneumatically, while the third working chamber is designed as a hydraulic working chamber.
  • the hydraulic working chamber serves to lock the die cushion in the lower end position and to control the upward movement of the piston rod.
  • the two pneumatic working chambers are separated by a differential piston. During the upward movement of the piston rod, the two pneumatic working chambers are connected to each other, so that the surface difference of the differential piston is effective and moves the piston for ejecting the molded sheet metal part upwards. This movement can be controlled by the oppositely acting hydraulic pressure in the hydraulic working chamber.
  • FR 867 309 A discloses a hydraulic press having a hydraulic cylinder for moving a press ram.
  • three working chambers are provided to each one of the working chamber assigned piston surface of a piston to pressurize.
  • Two of the working chambers are separated by an annular piston and have the same size piston surfaces.
  • the further working chamber is located above the piston and is formed by the end face of the piston rod.
  • the post-published EP 2 335 840 A2 describes a press ram with a hydraulic cylinder having three working chambers. Two of the working chambers are connected to a rapid traction drive, while the third working chamber is connected to a counter-holding drive. About this counter drive the press ram is raised. Via the rapid traction drive, the press ram is accelerated downwards to dampen the impact of the upper tool.
  • Out DE 196 39 222 A1 is a device for pre-acceleration of a die cushion for sheet metal forming in presses known.
  • the die cushion includes a travel control cylinder with a working chamber and an adjustable stop and die cushion cylinder, each with a working chamber. This structure requires a lot of construction.
  • EP 0 074 421 A1 describes a hydraulic die cushion according to the preamble of claim 1.
  • a die cushion cylinder has a piston rod to which a piston and a die cushion piston and an annular piston are attached. Adjacent to the piston, a working chamber is provided, which serves for downward acceleration of the piston rod. During this downward movement of the piston rod, the annular piston is displaced so that the volume between the die cushion piston and the annular piston changes only then, when the annular piston rests against the end wall of the die cushion cylinder. Means for controlling the plate holding force are not provided.
  • JP 63036931 A is described a hydro-pneumatic die cushion with a hydraulic cylinder.
  • This hydraulic cylinder is associated with two pistons and three working chambers.
  • the third piston surface adjacent to the third working chamber is not larger than the other piston surfaces, as provided by the invention.
  • the sheet holding force is affected in this die cushion by the compressible air in the air chamber 1a and therefore can not be set exactly. Means for controlling or regulating the sheet holding force are therefore not available.
  • the hydraulic cylinder of the die cushion has a cylinder housing with a plurality of working chambers.
  • a piston rod is slidably mounted, which protrudes on an end side of the cylinder housing.
  • a floating plate is fixed, on which a sheet holding ring sits. The sheet metal holding ring exerts the necessary pulling force on the sheet metal part to be formed during the drawing process.
  • the hydraulic cylinder has three hydraulically separated working chambers.
  • the first and second working chamber each adjacent to a first and second piston surface.
  • the two working chambers are separated by an annular piston.
  • the first and second working chamber have only a small volume and serve to bring the piston rod and thus the floating plate of the lower tool in a desired position.
  • the movement and / or the position of the piston rod is controlled or regulated by the hydraulic loading of the first and second working chambers. Because of the small first and second piston surfaces only a small volume of fluid is necessary for this purpose.
  • a third piston surface is preferably provided on the inner end face of the piston rod, which is significantly larger than the first piston surface and the second piston surface.
  • the third piston area may be larger by a factor of 3 to 10 than the other two piston areas.
  • the third piston surface adjoins a third working chamber, via which a sheet-metal holding force transmitted by the piston rod to the sheet-metal holding ring is set.
  • the hydraulic pressure in the third working chamber is controlled or regulated to a predetermined pressure setpoint.
  • Both the position and / or the movement of the piston rod, as well as the sheet-holding force can be adjusted very accurately via the hydraulic working chambers, because the hydraulic medium is incompressible in contrast to gaseous media.
  • the position or movement control of the piston rod and the regulation of the plate holding force are assigned to different working chambers.
  • the piston area or chamber volume of the three working chambers is therefore adapted to the function associated with the working chamber. In this case, a compact construction of the hydraulic cylinder is achieved with a small diameter. An economical operation of the Drawing cushion is ensured.
  • the piston rod receiving cylinder interior of the cylinder housing is divided into two coaxial with each other arranged cylindrical sections, which merge into one another via an annular step.
  • the first cylindrical portion of the interior has a larger diameter than the subsequent second cylindrical portion.
  • in the upper cylindrical portion of the annular piston is arranged, which separates this upper cylindrical portion in the first and second working chamber.
  • the end face of the piston rod can limit the third working chamber.
  • the piston rod as a compact cylindrical member can be manufactured very easily.
  • the two cylindrical sections can be introduced by coaxial bores with little effort in the cylinder housing. Since all working chambers work with the same hydraulic medium, even small leakage flows between the working chambers can be tolerated, which can be adjusted for example during prolonged operation by a certain wear of the piston seals.
  • the third working chamber is preferably hydraulically connected to a Nachsaugventil, which is arranged in particular parallel to a pressure control device.
  • About the suction valve is supplied with an increase in volume of the third working chamber during the upward movement of the piston rod hydraulic medium with a low Nachsaug sesstik, for example, about 5 to 15 bar, so as not to hinder the movement of the piston rod.
  • the suction valve locks at a pressure pickup in the third working chamber or at a reduction in volume of the third working chamber, so that then automatically connected in parallel pressure control device is effective. at locking suction valve, the pressure in the third working chamber rises significantly above the Nachsaug Stahlstik.
  • a drawing press equipped with the hydraulic cylinder according to the invention can operate very economically, because only slight hydraulic volume changes in the first and second working chamber are necessary for the movement of the piston rod. About the much larger third piston surface, the necessary large Blechhalte rule be provided. The required pressure in the third working chamber is automatically generated by the retraction movement of the piston rod.
  • the floating plate of the drawing press can be held by a plurality of hydraulic cylinders according to the invention. The position and / or the movement of the piston rods and / or the hydraulic pressure in the third working chambers can be controlled or controlled independently of each other in the various hydraulic cylinders.
  • FIG. 1 a drawing press with a press frame 11 is shown in a schematic side view.
  • a plunger 12 is slidably mounted in a working direction A and in particular in the vertical direction.
  • a press drive 13 serves to move the plunger 12 in the working direction A.
  • the plunger 12, the upper tool 14 is arranged.
  • the lower tool 15 is provided on a press table 16 of the press frame 11.
  • the drawing press 10 has a hydraulic die cushion 20.
  • This comprises a floating plate 21, which is mounted in the working direction A displaceable on a cylinder assembly 22 of one or more hydraulic cylinders 23.
  • the blank holder ring 25 can therefore together with the push rods 24 and the floating plate 21 by the application the cylinder assembly 22 are moved.
  • Each hydraulic cylinder 22 of the cylinder assembly 23 is connected via a first hydraulic line 26, a second hydraulic line 27 and a third hydraulic line 28 to a hydraulic circuit 29, so that hydraulic medium can be supplied to the hydraulic cylinder 22 and discharged from the hydraulic cylinder 22.
  • the hydraulic cylinder 23 has a cylinder housing 30 which delimits a cylinder interior 31.
  • the cylinder interior 31 has a cylindrical passage opening 32, through which a piston rod 33 displaceably mounted in the cylinder housing 30 protrudes with its outer free end 34 out of the cylinder housing 30.
  • the floating plate 21 is attached.
  • a first sealing arrangement is provided for the fluidic sealing of the cylinder interior 31.
  • the passage opening 32 also serves to guide the movement of the piston rod 33 in the working direction A.
  • the cylinder interior 31 has, subsequent to the passage opening 32, a first cylindrical section 40 with a first diameter D1.
  • the first cylindrical portion 40 is adjoined by a second cylindrical portion 41 having a second diameter D2.
  • the second diameter D2 is smaller than the first diameter D1.
  • the second diameter D2 corresponds to the diameter of the through-opening 32.
  • the piston rod 33 at least in the axial openings assigned to the passage opening 32 and the second cylindrical portion 41 has one Diameter, which apart from the necessary clearance corresponds to the second diameter D2.
  • the two cylindrical sections 40, 41 are connected to each other via an annular step 42. Both cylindrical sections 40, 41 are arranged coaxially to the longitudinal axis of the piston rod 33. Subsequent to the annular step 42, a second sealing arrangement 43 is provided in the inner wall of the second cylindrical section 41, which rests against the piston rod 33 in a fluid-tight manner.
  • annular piston 45 In the first cylindrical portion 40, an annular piston 45 is fixed to the piston rod 33.
  • the annular piston 45 has a piston seal 46 which bears sealingly against the inner wall of the first cylindrical section 40, as a result of which the first cylindrical section 40 is subdivided fluidically into a first working chamber 47 and a second working chamber 48.
  • the volumes of the two working chambers 47, 48 may change, the sum of these volumes remaining constant.
  • the annular piston 45 has, adjacent to the first working chamber 47, a first piston surface 49 and, adjacent to the second working chamber 48, a second piston surface 50.
  • the first and second piston surfaces 49, 50 are the same size.
  • a third working chamber 53 is provided in the second cylindrical portion 41.
  • the end face of the piston rod 33 located in the cylinder housing 30 forms a third piston surface 54, which adjoins the third working chamber 53.
  • the area of the third piston surface 54 is greater than the surface area of the first and second piston surfaces 49, 50.
  • the third piston surface 54 is three to ten and preferably five times as large as the first piston surface 49 or the second piston surface 50.
  • the thickness d measured in the radial direction of the annular piston 45 corresponds to the difference between the two diameters D1, D2 corresponds.
  • first working chamber 47 via the first hydraulic line 26
  • second working chamber 48 via the second hydraulic line 27 and the third working chamber 53 via the third hydraulic line 28 is connected.
  • first and second working chamber 47, 48 a first hydraulic circuit 55 and the third working chamber 53
  • second hydraulic circuit 56 is hydraulically connected.
  • the two hydraulic subcircuits 55, 56 are fluidically completely separated from each other in the embodiment described here.
  • the first hydraulic circuit 55 has a reservoir 57, from which a motor-pump unit 58 sucks in hydraulic fluid and provides via a pressure line 59.
  • a pressure accumulator 60 is connected, so that in the pressure line 59 is always a sufficient amount of pressurized hydraulic fluid is available.
  • the pressure line 59 Via a connected to the pressure line 59 electrically controllable control valve 61, the pressure line 59 can be selectively connected to the first hydraulic line 26 or the second hydraulic line 27. Accordingly, a guided from the control valve 61 to the reservoir 57 return line 62 via the control valve 61 selectively connected to the first or the second hydraulic line 26 and 27 hydraulically.
  • the second hydraulic line 27 is also connected via a pressure control valve 63 to the reservoir 57. When the pressure in the second working chamber 48 and thus in the second hydraulic line 27 exceeds a predetermined threshold, the pressure control valve 63 opens, so Hydraulic medium from the second working chamber 48 can be promoted in the reservoir 57.
  • the control valve 61 is configured in the embodiment as a 4/3-way valve. It can also be replaced by other arrangements, such as 2-way cartridge valves.
  • first switching position I the first working chamber 47 is connected via the first hydraulic line 26 to the pressure line 59, while the second working chamber 48 is connected via the second hydraulic line 27 to the return line 62.
  • second switching position II the control valve 61 blocks the pressure line 59 and a branch connection 27a to the second hydraulic line 27 and connects the first hydraulic line 26 to the return line 62.
  • the third switching position III provides a hydraulic connection of the first working chamber 47 with the return line 62 and the second working chamber 48 with the pressure line 59 ago.
  • the second hydraulic circuit 56 includes a hydraulic reservoir 65 connected to the third hydraulic line 28, which can be designed as a low-pressure accumulator. Via the hydraulic reservoir 65 hydraulic medium is provided under low pressure of about 5 to 15 bar.
  • the hydraulic reservoir 65 is fluidly connected to the third hydraulic line 28 via a suction valve 66.
  • the Nachsaugventil 66 allows in Nachsaug congress a fluid flow from the hydraulic reservoir 65 into the third working chamber 53. In the reverse direction, the Nachsaugventil 66 locks in pressure control operation.
  • Parallel to the suction valve is connected to the third hydraulic line 28, an electrically controllable pressure control device 67, via which in the third hydraulic line 28 and thus in the third Working chamber 53 prevailing pressure in pressure control mode can be controlled or regulated.
  • the pressure regulating device 67 may connect the third hydraulic line 28 for a return line 68 with a reservoir 69.
  • For controlling the pressure control device 67 and the control valve 61 and the motor pump unit 58 is a control device 70th
  • the position and / or the movement, for example the position and / or the speed and / or the acceleration of the piston rod 33 are controlled or regulated via the first hydraulic subcircuit 55.
  • the first working chamber 47 is connected to the pressure line 59, while the second working chamber 48 is connected without pressure to the reservoir 57. Due to the pressure difference on both sides of the annular piston 45, a force is exerted on the piston rod 33, which causes the piston rod 33 of the cylinder 23 to retract.
  • the third working chamber 53 is connected by means of the controllable pressure control device 67 to the reservoir 69, so that hydraulic medium from the third working chamber 53 can be moved out.
  • a movement extending the piston rod 33 is effected in the third switching position III of the control valve 61.
  • the higher pressure in the second working chamber 48 relative to the first working chamber 47 exerts on the annular piston 45 and thus the piston rod 33 in the direction of extension of the piston rod 33 directed force.
  • By the thereby occurring increase in volume of the third working chamber 53 is sucked via the third hydraulic line 28 and the Nachsaugventil 66 hydraulic medium from the hydraulic reservoir 65 so as not to block the movement of the piston rod 33 (Nachsaug réelle). Because of the small first and second piston surfaces 49, 50, the volume flows necessary for moving the piston rod 33 into the first working chamber 47 and out of the second working chamber 48 or vice versa are also very low.
  • the position or movement control of the piston rod 33 can thus be very economical.
  • pre-accelerations of the sheet-metal holding ring 25 can be generated via the control valve 61 and the first hydraulic-circuit 55 in order to reduce the relative speed between the upper-tool 15 and the sheet-metal holding ring 25 prior to the collision.
  • An ejection movement of the shaped sheet metal part is also carried out via this first hydraulic circuit 55 and the first two working chambers 47, 48.
  • the sheet metal part B to be formed has to be clamped between the sheet metal holding ring 25 and the upper tool 14 with a predetermined sheet holding force.
  • the sheet metal part B is pulled by a continued movement of the plunger 12 to the lower tool 15 over the shape of the lower tool 15 and simultaneously formed by the substantially complementary shape of the upper tool 14.
  • the sheet holding force must be adhered to in order to ensure the quality of the forming. If the sheet holding force is too large, the sheet can enter. On the other hand, wrinkles may form in the sheet during forming when the sheet holding force is too low.
  • the setting of the desired and required sheet holding force is performed by the second hydraulic circuit 56 and the third working chamber 53 of the hydraulic cylinder 23.
  • the cylinder 23 of the cylinder assembly 22 are brought into their initial position. This is done by moving the annular piston 45 by supplying or removing hydraulic medium into or out of the first and second working chambers 47, 48.
  • the drawing pad 20 operates in position and / or motion control. Shortly before the upper tool 14 comes to rest with the sheet metal part B located on the sheet metal holding ring 25, an inward movement of the piston rods 33 can be brought about in order to reduce the relative speed between the ram 12 and the sheet metal holding ring 25.
  • the hydraulic die cushion 20 switches to a regulation or control of the sheet holding force.
  • the control valve 61 is brought into its second switching position II, in which the first working chamber 47 connected to the return line 62 and thus is depressurized.
  • the branch connection 27a from the second hydraulic line 27 to the control valve 61 is blocked, so that the second working chamber 48 is connected to the reservoir 57 via the pressure regulating valve 63.
  • the press drive 13 tries to move the upper tool 14 further in the working direction A to the lower tool 15.
  • the pressure in the second and third working chamber 48, 53 increases. Due to this pressure increase opens the pressure control valve 63, so that hydraulic medium from the second working chamber 48 can drain into the Vorrast matterser 57.
  • the sheet holding force is adjusted by means of the pressure control device 67 in the second hydraulic circuit 56.
  • the pressure control device 67 is controlled via the control device 70 so that a desired pressure in the third working chamber 53 sets, which leads to the setting of the desired sheet holding force. In this way, the Blechhaltekraft remains even with a continued retraction of the piston rod 33 constant. This means that during the forming of the sheet metal part B between the upper tool 14 and lower tool 15 always the desired sheet holding force is exerted by the sheet metal holding ring 25.
  • the first hydraulic line 26 and the first working chamber 47 can be shut off in the second switching position II.
  • the pressure in the second working chamber 48 is regulated by the pressure regulating valve 63. Then a Nachsaugtechnisch must be connected to the first working chamber to allow a piston rod movement.
  • the upper tool 14 can be moved away again from the lower tool 15.
  • the Ziekissen 20 and the hydraulic cylinder 23 is then no longer regulated to set the desired sheet holding force, but is operated again in a position or position control.
  • the first control valve 61 switches either to carry out a retraction movement of the piston rod 33 in the first switching position I or to carry out an ejection movement in its third switching position III, in which the piston rod 33 is extended and hydraulic medium is sucked into the third working chamber 53.
  • a sufficient Nachsaugiolo only a low suction pressure in the range of 5 to 15 bar in the second hydraulic circuit 56 is necessary.
  • the pressure accumulator 60 in the first hydraulic circuit 55 for movement of the piston rod 33 a pressure in the range of about 200 bar ready to perform sufficiently fast piston rod movements can.
  • the second hydraulic subcircuit 56 can have its own motor-pump unit 72 for storing the hydraulic reservoir 65.
  • the pressure control device 67 is in the embodiment according to FIG. 3 formed by a 2/2-way valve 73, which can be electrically switched by the controller 70. If the pressure in the third hydraulic line 28 and thus in the third working chamber 53 increases to a variably predefinable threshold value, the 2/2-way valve 73 is briefly opened in order to discharge hydraulic medium to the reservoir 69 and lower the pressure again.
  • the threshold corresponds to the pressure to be set sheet holding force in pressure control mode.
  • the suction valve 66 is preferably realized by a pressure-controlled safety valve 74. Via an input 81, the suction pressure of the hydraulic reservoir 65 is applied to the plunger 75 of the safety valve 74. An output 76 of the safety valve 74 is connected to the third hydraulic line 28. The hydraulic pressure at the outlet 76 is supplied via a control line 77 to a control chamber 78 which is delimited by a control surface 79 of a piston 80 connected to the plunger 75. If the pressure in the control line 77 and thus at the output 75 is sufficiently large, the plunger is displaced by the pressure in the control chamber 78 in a closed position, whereby the input 81 is separated from the output 76 of the safety valve 74.
  • the plunger 75 provides a connection between the input 81 and the output 76 free, so that pressurized hydraulic fluid from the reservoir 65 via the input 81 and the output 76 in the third hydraulic line 28 can tile. If the pressure then increases sufficiently at the output 76 and thus in the control line 77, the safety valve 74 closes again. In this way, the suction of hydraulic fluid is realized in an extension movement of the piston rod 33 in the third working chamber. During pressure control, the hydraulic pressure in the third working chamber 53 is sufficiently great to maintain the safety valve 74 in the closed position. Hydraulic fluid can then only flow off the second hydraulic line 28 via the pressure control device 77 and, according to the example, the 2/2-way valve 73.
  • FIG. 4 a modified embodiment of the second hydraulic circuit 56 is shown, in which an energy recovery by a generator operation of the motor-pump unit 72 is provided.
  • a 4/2-way valve 82 can be used as a pressure control device 67.
  • the motor-pump unit 72 sits in the return line 68.
  • the return line 68 branches at the 4/2-way valve 82 and is connected to two terminals.
  • a supply line 83 is led to the input 81 of the safety valve 74 and simultaneously to the hydraulic reservoir 65, while the other terminal is connected to the third hydraulic line 28.
  • the supply line 83 is connected to the motor-pump unit 72, whereas the connection to the third hydraulic line 28 is shut off.
  • the connection between the supply line 83 and the motor-pump unit 72 is interrupted while the motor-pump unit is connected to the third hydraulic line 28.
  • the hydraulic reservoir 65 can be stored with pressurized hydraulic medium. From the third working chamber 53, no hydraulic medium can flow off via the third hydraulic line 28, since the connection to the return line 68 is shut off and the safety valve 74 does not allow any hydraulic return flow. In the other switching position, the connection of the motor-pump unit 72 with the hydraulic reservoir 65 and the safety valve 74 is inhibited and hydraulic medium can be used to reduce the pressure in the third working chamber 53 via the third hydraulic line 28, the drain line 68 and the pump of the motor pump. Tile unit 72 back into the reservoir 69. The backflowing hydraulic medium drives the pump.
  • the motor designed as an electric motor can thereby generate electricity in the generator mode and store for example in a battery. In this way, the energy efficiency of the die cushion 20 and the drawing press 10 is further improved.
  • a connecting line with a regulating valve between the third hydraulic line 28 and the reservoir 69 may be present in parallel with the pressure regulating device 67, as shown in FIG. 3 is shown.
  • the fluid flow from the third working chamber 53 can then be controlled independently of the motor-pump unit.
  • the cylinder arrangement 22 of the die cushion 20 has a plurality of hydraulic cylinders 23, these can be controlled independently of one another. In this way it is possible to adjust 25 different positions and / or movement and / or Blechhalte concept at different points of the sheet metal retaining ring. This can be complex Forming processes, for example, be required for body parts in the automotive industry.
  • FIG. 5 a modified embodiment of the first hydraulic circuit 55 is illustrated.
  • the hydraulic cylinder and the second hydraulic circuit 56 correspond to the embodiment according to FIG. 2 .
  • a pressure regulating device 64 is provided, which is inserted into a connecting line 85 between the first hydraulic line 26 and the second hydraulic line 27.
  • the pressure control device 64 is actuated via the control device 70.
  • a detailed illustration of the pressure control device 63 is shown in FIG FIG. 6 to see.
  • a main valve, such as cartridge valve 86 is interposed, with its input 87 to the second hydraulic line 27 and its output 88 is connected to the first hydraulic line 26.
  • a pressure limiting valve 89 is connected on the input side to the second hydraulic line 27 and on the output side to the reservoir 57.
  • the control input 90 of the pressure relief valve 89 is fluidly shorted to its input side.
  • the input side of the pressure relief valve 89 is further connected to a control input 91 of the cartridge valve 86. If the pressure in the second working chamber 48 rises due to a retraction movement of the piston rod 33 via the switching threshold of the pressure limiting valve 89, the cartridge valve 86 is opened via the control input 91 and the connection in the connecting line 85 is released. As a result, the hydraulic fluid is diverted from the second working chamber 48 via the connecting line 85 into the first working chamber 47. A supply of hydraulic fluid is not required here.
  • the control valve 61 is located in a modified second switching position II, in which all Lines are shut off by the control valve 61 (see FIG. 5 ).
  • an additional directional valve 92 may be connected, which is controlled by the control device 70.
  • This directional control valve 92 is in the preferred embodiment after FIG. 6 designed as a 4/2-way valve.
  • the directional control valve could alternatively be designed as a 2/2-way valve. In its rest position locks the directional control valve 92, while it short-circuits the pressure limiting valve 89 between its input and output in its activated switching position. Such a fluidic short circuit leads to the reduction of the pressure at the control input 91 of the cartridge valve 86 and establishes the fluidic connection of the two working chambers 47, 48 via the connection line 85 then opened.
  • the control signal for activating the directional control valve 92 and thus for establishing the hydraulic connection between the two working chambers 47, 48 takes place by means of a triggering event.
  • a triggering event By way of example, the triggering of a pressure gradient threshold value in the second working chamber 48 can be used as a triggering event.
  • one or more position values of the press ram can also represent a triggering event.
  • the hydraulic cylinder 23 has a first working chamber 47, a second working chamber 48 and a third working chamber 53.
  • An annular piston 45 with a first piston surface 49 and a second piston surface 50 separates the first Working chamber 47 from the second working chamber 48.
  • the first and the second piston surface 49, 50 are the same size.
  • An end face of the piston rod 33 arranged in the cylinder housing 30 forms a third piston surface 54, which is larger than the first and the second piston surfaces.
  • the third piston surface 54 bounds the third working chamber 53 of the hydraulic cylinder 23.
  • the first and the second working chamber 47, 48 are provided for controlling the position and / or the movement of the piston rod 33.
  • the third working chamber 53 serves to control or regulate the set on the piston rod 33 on the drawing press 10 Blechhaltekraft.
  • the sheet holding force is set by the control of the hydraulic pressure in the third working chamber 53.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Press Drives And Press Lines (AREA)
  • Actuator (AREA)

Claims (9)

  1. Coussin de serre-flan (20) hydraulique d'une presse d'emboutissage (10), comprenant un vérin hydraulique (23) qui présente un corps de cylindre (30) dans lequel sont prévues plusieurs chambres de travail (47, 48, 53) hydrauliques,
    le vérin (23) présentant une tige de piston (33) qui est destinée à la liaison avec une bague de maintien de tôle (25) de la presse d'emboutissage (10),
    le vérin (23) présentant une première surface de piston (49), adjacente à une première chambre de travail (47), et une deuxième surface de piston (50) adjacente à une deuxième chambre de travail (48), la première surface de piston (49) et la deuxième surface de piston (50) ayant sensiblement les mêmes dimensions, et le vérin (23) présentant une troisième surface de piston (54) qui est plus grande que les première et deuxième surfaces de piston (49, 50) et qui est adjacente à une troisième chambre de travail (53),
    comprenant un premier circuit hydraulique partiel (55), comprenant un deuxième circuit hydraulique partiel (56) qui est relié sur le plan hydraulique à la troisième chambre de travail (53),
    les deux circuits hydrauliques partiels (55, 56) étant séparés complètement l'un de l'autre sur le plan fluidique ;
    caractérisé en ce que le premier circuit hydraulique partiel (55) est relié sur le plan hydraulique aux première et deuxième chambres de travail (47, 48),
    le premier circuit hydraulique partiel (55) ayant pour effet de commander ou régler la position et/ou le mouvement de la tige de piston (33), et la force de maintien de la tôle étant réglée par le deuxième circuit hydraulique partiel (56), par commande ou régulation de la pression hydraulique dans la troisième chambre de travail (53).
  2. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce que la troisième surface de piston (54) est plus grande d'un facteur compris dans la plage de 3 à 10 que les première et deuxième surfaces de piston (49, 50).
  3. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce qu'une face frontale de la tige de piston (33) constitue la troisième surface de piston (54).
  4. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce qu'il est prévu entre la première chambre de travail (47) et la deuxième chambre de travail (48), un piston annulaire (45) qui entoure la tige de piston (33) sous forme d'anneau.
  5. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce que le corps de cylindre (30) délimite un volume interne de cylindre (31), avec une première partie cylindrique (40), présentant un premier diamètre (D1), et avec une deuxième partie cylindrique (41) présentant un deuxième diamètre (D2).
  6. Coussin de serre-flan (20) hydraulique selon la revendication 5, caractérisé en ce que les première et deuxième chambres de travail (47, 48) sont disposées dans la première partie cylindrique (40), et la troisième chambre de travail (53) est disposée dans la deuxième partie cylindrique (41).
  7. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce que la troisième chambre de travail (53) est reliée sur le plan hydraulique à un dispositif de régulation de pression (67) pouvant être activé par voie électrique.
  8. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce que la troisième chambre de travail (53) est reliée sur le plan hydraulique à une soupape de réaspiration (66).
  9. Coussin de serre-flan (20) hydraulique selon la revendication 1, caractérisé en ce que la soupape de réaspiration (66) est reliée sur le plan hydraulique à un réservoir hydraulique (65) qui fournit une pression dans la plage comprise entre 5 bars et 35 bars.
EP11164657.6A 2010-05-03 2011-05-03 Coussin de serre-flan hydraulique avec un vérin hydraulique Active EP2384834B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010019324 DE102010019324B4 (de) 2010-05-03 2010-05-03 Hydraulisches Ziehkissen

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EP2384834A2 EP2384834A2 (fr) 2011-11-09
EP2384834A3 EP2384834A3 (fr) 2015-10-21
EP2384834B1 true EP2384834B1 (fr) 2018-03-07

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US (1) US9038431B2 (fr)
EP (1) EP2384834B1 (fr)
CN (1) CN102407257B (fr)
DE (1) DE102010019324B4 (fr)
ES (1) ES2666722T3 (fr)

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DE102021002179B3 (de) 2021-04-24 2022-09-29 Hydac International Gmbh Vorrichtung zum Umwandeln von Volumenströmen und hydraulische Pressen mit einer solchen Vorrichtung

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CN103586321B (zh) * 2013-10-16 2015-05-13 西安交通大学 一种增压式电动伺服拉深垫
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Also Published As

Publication number Publication date
ES2666722T3 (es) 2018-05-07
EP2384834A2 (fr) 2011-11-09
DE102010019324A1 (de) 2011-11-03
DE102010019324B4 (de) 2015-05-07
CN102407257B (zh) 2015-02-11
CN102407257A (zh) 2012-04-11
EP2384834A3 (fr) 2015-10-21
US9038431B2 (en) 2015-05-26
US20110265544A1 (en) 2011-11-03

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