EP2384834B1 - Hydraulic die cushion with a hydraulic cylinder - Google Patents
Hydraulic die cushion with a hydraulic cylinder Download PDFInfo
- 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
- Authority
- 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.)
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- 230000033001 locomotion Effects 0.000 claims description 37
- 230000033228 biological regulation Effects 0.000 claims description 4
- 239000002184 metal Substances 0.000 description 20
- 230000001105 regulatory effect Effects 0.000 description 15
- 239000012530 fluid Substances 0.000 description 10
- 238000007667 floating Methods 0.000 description 8
- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 230000001133 acceleration Effects 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 238000000465 moulding Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 230000037303 wrinkles Effects 0.000 description 1
Images
Classifications
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- 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.
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- 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)
- Actuator (AREA)
- Press Drives And Press Lines (AREA)
Description
Die Erfindung betrifft ein hydraulisches Ziehkissen einer Ziehpresse mit einem hydraulischen Zylinder. Beim Ziehvorgang klemmt die Ziehpresse ein Blech zwischen einem Oberwerkzeug und einem Unterwerkzeug ein. Durch eine Relativbewegung zwischen Oberwerkzeug und Unterwerkzeug wird das Blech über ein unteres Formteil gezogen und zwischen zwei Formteilen gepresst. Die für das Ziehen notwendige Blechhaltekraft wird durch das Ziehkissen bereitgestellt.The invention relates to a hydraulic drawing cushion of a drawing press with a hydraulic cylinder. During the drawing process, the drawing press clamps a sheet between an upper tool and a lower tool. By a relative movement between the upper tool and 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.
Ein Ziehkissen für eine Ziehpresse wird zum Beispiel in der
Die nachveröffentlichte
Aus
In
Ausgehend hiervon ist es eine Aufgabe der Erfindung, einen kompakten ein hydraulisches Ziehkissen mit einem hydraulischen Zylinder für zu schaffen, mit dem sowohl die Position der Kolbenstange als auch die von der Kolbenstange ausgeübte Kraft gesteuert oder geregelt werden kann.Based on this, it is an object of the invention to provide a compact hydraulic a hydraulic cushion with a hydraulic cylinder for, with both the position of the piston rod and the force exerted by the piston rod force can be controlled or regulated.
Diese Aufgabe wird durch ein hydraulisches Ziehkissen mit den Merkmalen des Patentanspruches 1 erreicht. Der Hydraulikzylinder des Ziehkissens weist ein Zylindergehäuse mit mehreren Arbeitskammern auf. Im Zylindergehäuse ist eine Kolbenstange verschiebbar gelagert, die an einer Stirnseite aus dem Zylindergehäuse herausragt. An dem äußeren freien Ende der Kolbenstange ist eine Schwebeplatte befestigt, auf der ein Blechhaltering sitzt. Der Blechhaltering übt während des Ziehvorgangs die notwendige Ziehkraft auf das umzuformende Blechteil aus.This object is achieved by a hydraulic die cushion with the features of claim 1. The hydraulic cylinder of the die cushion has a cylinder housing with a plurality of working chambers. In the cylinder housing, a piston rod is slidably mounted, which protrudes on an end side of the cylinder housing. At the outer free end of the piston rod, 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.
Der Hydraulikzylinder verfügt über drei hydraulisch getrennte Arbeitskammern. Die erste und zweite Arbeitskammer grenzen jeweils an eine erste bzw. zweite Kolbenfläche an. Vorzugsweise sind die beiden Arbeitskammern durch einen Ringkolben voneinander getrennt. Die erste und zweite Arbeitskammer weisen lediglich ein geringes Volumen auf und dienen dazu, die Kolbenstange und damit die Schwebeplatte des Unterwerkzeugs in eine gewünschte Position zu bringen. Insbesondere wird durch die hydraulische Beaufschlagung der ersten und zweiten Arbeitskammer die Bewegung und/oder die Lage der Kolbenstange gesteuert oder geregelt. Wegen der kleinen ersten und zweiten Kolbenflächen ist hierfür lediglich ein geringes Fluidvolumen notwendig.The hydraulic cylinder has three hydraulically separated working chambers. The first and second working chamber each adjacent to a first and second piston surface. Preferably, 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. In particular, 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.
Im Zylindergehäuse ist vorzugsweise an der inneren Stirnfläche der Kolbenstange eine dritte Kolbenfläche vorgesehen, die deutlich größer ist als die erste Kolbenfläche und die zweite Kolbenfläche. Beispielsweise kann die dritte Kolbenfläche um einen Faktor 3 bis 10 größer sein als die beiden anderen Kolbenflächen. Die dritte Kolbenfläche grenzt an eine dritte Arbeitskammer an, über die eine von der Kolbenstange auf den Blechhaltering übertragene Blechhaltekraft eingestellt wird. Hierfür wird der hydraulische Druck in der dritten Arbeitskammer auf einen vorgegebenen Drucksollwert gesteuert oder geregelt.In the cylinder housing, 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. For example, 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. For this purpose, the hydraulic pressure in the third working chamber is controlled or regulated to a predetermined pressure setpoint.
Über die hydraulischen Arbeitskammern kann sowohl die Lage und/oder die Bewegung der Kolbenstange, als auch die Blechhaltekraft sehr genau eingestellt werden, weil das Hydraulikmedium im Gegensatz zu gasförmigen Medien inkompressibel ist. Dabei sind die Lage- bzw. Bewegungsregelung der Kolbenstange und die Regelung der Blechhaltekraft unterschiedlichen Arbeitskammern zugeordnet. Die Kolbenfläche bzw. das Kammervolumen der drei Arbeitskammern ist daher an die der Arbeitskammer zugeordnete Funktion angepasst. Dabei wird ein kompakter Aufbau des Hydraulikzylinders mit geringem Durchmesser erreicht. Ein wirtschaftlicher Betrieb des Ziehkissens ist sichergestellt.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.
Vorzugsweise ist der die Kolbenstange aufnehmende Zylinderinnenraum des Zylindergehäuses in zwei koaxial zueinander angeordnete zylindrische Abschnitte aufgeteilt, die über eine ringförmige Stufe ineinander übergehen. Der erste zylindrische Abschnitt des Innenraums weist einen größeren Durchmesser auf als der sich anschließende zweite zylindrische Abschnitt. Vorzugsweise ist im oberen zylindrischen Abschnitt der Ringkolben angeordnet, der diesen oberen zylindrischen Abschnitt in die erste und zweite Arbeitskammer trennt. Im unteren zylindrischen Abschnitt kann die Stirnfläche der Kolbenstange die dritte Arbeitskammer begrenzen. Bei einem solchen Aufbau kann die Kolbenstange als kompaktes zylindrisches Bauteil sehr einfach hergestellt werden. Gleichermaßen lassen sich die beiden zylindrischen Abschnitte durch koaxiale Bohrungen mit wenig Aufwand in das Zylindergehäuse einbringen. Da alle Arbeitskammern mit dem gleichen Hydraulikmedium arbeiten, können auch geringe Leckageströme zwischen den Arbeitskammern toleriert werden, die sich beispielsweise bei längerem Betrieb durch einen gewissen Verschleiß der Kolbendichtungen einstellen können.Preferably, 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. Preferably, in the upper cylindrical portion of the annular piston is arranged, which separates this upper cylindrical portion in the first and second working chamber. In the lower cylindrical portion, the end face of the piston rod can limit the third working chamber. With such a construction, the piston rod as a compact cylindrical member can be manufactured very easily. Similarly, 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.
Die dritte Arbeitskammer ist vorzugsweise mit einem Nachsaugventil hydraulisch verbunden, das insbesondere parallel zu einer Druckregeleinrichtung angeordnet ist. Über das Nachsaugventil wird bei einer Volumenvergrößerung der dritten Arbeitskammer während der Aufwärtsbewegung der Kolbenstange Hydraulikmedium mit einem geringen Nachsaugbetriebsdruck von beispielsweise etwa 5 bis 15 bar zugeführt, um die Bewegung der Kolbenstange nicht zu behindern. Das Nachsaugventil sperrt bei einer Druckerhörung in der dritten Arbeitskammer bzw. bei einer Volumenverringerung der dritten Arbeitskammer, so dass dann automatisch die dazu parallel geschaltete Druckregeleinrichtung wirksam ist. Bei sperrendem Nachsaugventil steigt der Druck in der dritten Arbeitskammer deutlich über den Nachsaugbetriebsdruck an.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 Nachsaugbetriebsdruck, 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 Nachsaugbetriebsdruck.
Eine mit dem erfindungsgemäßen Hydraulikzylinder ausgestattete Ziehpresse kann sehr wirtschaftlich arbeiten, weil für die Bewegung der Kolbenstange lediglich geringe hydraulische Volumenänderungen in der ersten und zweiten Arbeitskammer notwendig sind. Über die deutlich größere dritte Kolbenfläche werden die notwendigen großen Blechhaltekräfte zur Verfügung gestellt. Der hierfür erforderliche Druck in der dritten Arbeitskammer wird automatisch durch die Einfahrbewegung der Kolbenstange erzeugt. Die Schwebeplatte der Ziehpresse kann durch mehrere der erfindungsgemäßen hydraulischen Zylinder gehalten werden. Die Lage und/oder die Bewegung der Kolbenstangen und/oder der hydraulische Druck in den dritten Arbeitskammern können in den verschiedenen Hydraulikzylindern unabhängig voneinander geregelt oder gesteuert werden.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 Blechhaltekräfte 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.
Vorteilhafte Ausführungen der Erfindung ergeben sich aus den abhängigen Patentansprüchen sowie der Beschreibung. Die Beschreibung beschränkt sich auf wesentliche Merkmale der Erfindung sowie sonstiger Gegebenheiten. Die Zeichnung ist ergänzend heranzuziehen. Es zeigen:
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Figur 1 eine schematische Darstellung einer Ziehpresse mit hydraulischem Ziehkissen, -
Figur 2 eine schematische Darstellung eines Hydraulikzylinders des Ziehkissens mit einem vereinfacht dargestellten Hydraulikkreis, -
Figur 3 ein Ausführungsbeispiel für einen an die dritte Arbeitskammer des Hydraulikzylinders angeschlossenen Hydraulikkreis in Form eines Blockschaltbilds, -
Figur 4 ein abgewandeltes Ausführungsbeispiel des an die dritte Arbeitskammer des Hydraulikzylinders angeschlossenen Hydraulikkreis in Form eines Blockschaltbilds, -
Figur 5 ein weiteres Ausführungsbeispiel des an den Hydraulikzylinder des Ziehkissens angeschlossenen Hydraulikkreises mit einem abgewandelten Druckregelventil in Form eines Blockschaltbilds und -
Figur 6 das abgewandelte Druckregelventil ausFigur 5 in Form eines Blockschaltbilds.
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FIG. 1 a schematic representation of a drawing press with hydraulic drawing cushion, -
FIG. 2 a schematic representation of a hydraulic cylinder of the die cushion with a hydraulic circuit shown simplified, -
FIG. 3 an exemplary embodiment of a hydraulic circuit connected to the third working chamber of the hydraulic cylinder in the form of a block diagram, -
FIG. 4 a modified embodiment of the connected to the third working chamber of the hydraulic cylinder hydraulic circuit in the form of a block diagram, -
FIG. 5 a further embodiment of the connected to the hydraulic cylinder of the die cushion hydraulic circuit with a modified pressure control valve in the form of a block diagram and -
FIG. 6 the modified pressure control valveFIG. 5 in the form of a block diagram.
In
In Arbeitsrichtung A mit Abstand gegenüber dem Oberwerkzeug 14 ist das das Unterwerkzeug 15 auf einem Pressentisch 16 des Pressengestells 11 vorgesehen.In the working direction A at a distance from the
Unterhalb des Pressentischs 16 weist die Ziehpresse 10 ein hydraulisches Ziehkissen 20 auf. Dieses umfasst eine Schwebeplatte 21, die in Arbeitsrichtung A verlagerbar an einer Zylinderanordnung 22 aus einem oder mehreren Hydraulikzylindern 23 gelagert ist. Auf der der Zylinderanordnung 22 entgegengesetzten Seite der Schwebeplatte 21 ist diese über Druckstangen 24 mit einem Blechhaltering 25 verbunden. Der Blechhaltering 25 kann demnach zusammen mit den Druckstangen 24 und der Schwebeplatte 21 durch die Beaufschlagung der Zylinderanordnung 22 bewegt werden. Jeder Hydraulikzylinder 22 der Zylinderanordnung 23 ist über eine erste Hydraulikleitung 26, eine zweite Hydraulikleitung 27 und eine dritte Hydraulikleitung 28 mit einem Hydraulikkreis 29 verbunden, so dass Hydraulikmedium zum Hydraulikzylinder 22 zugeführt und vom Hydraulikzylinder 22 abgeführt werden kann.Below the press table 16, the
Einer der Hydraulikzylinder 23 des Ziehkissens 20 sowie eine stark vereinfachte schematische Darstellung des angeschlossenen Hydraulikkreises 29 sind in
Der Zylinderinnenraum 31 weist im Anschluss an die Durchgangsöffnung 32 einen ersten zylindrischen Abschnitt 40 mit einem ersten Durchmesser D1 auf. An den ersten zylindrischen Abschnitt 40 schließt sich ein zweiter zylindrischer Abschnitt 41 mit einem zweiten Durchmesser D2 an. Der zweite Durchmesser D2 ist kleiner als der erste Durchmesser D1. Beim bevorzugten Ausführungsbeispiel entspricht der zweite Durchmesser D2 dem Durchmesser der Durchgangsöffnung 32. Vorzugsweise hat die Kolbenstange 33 zumindest in den der Durchgangsöffnung 32 sowie dem zweiten zylindrischen Abschnitt 41 zugeordneten Axialabschnitten einen Durchmesser, der abgesehen von dem notwendigen Spiel dem zweiten Durchmesser D2 entspricht.The
Die beiden zylindrischen Abschnitte 40, 41 sind über eine Ringstufe 42 miteinander verbunden. Beide zylindrischen Abschnitte 40, 41 sind koaxial zur Längsachse der Kolbenstange 33 angeordnet. Anschließend an die Ringstufe 42 ist eine zweite Dichtungsanordnung 43 in der Innenwand des zweiten zylindrischen Abschnitts 41 vorgesehen, die fluiddicht an der Kolbenstange 33 anliegt.The two
Im ersten zylindrischen Abschnitt 40 ist ein Ringkolben 45 an der Kolbenstange 33 befestigt. Der Ringkolben 45 weist eine dichtend an der Innenwand des ersten zylindrischen Abschnitts 40 anliegende Kolbendichtung 46 auf, wodurch der erste zylindrische Abschnitt 40 fluidisch in eine erste Arbeitskammer 47 und eine zweite Arbeitskammer 48 unterteilt ist. Durch das Verschieben des Ringkolbens 45 können sich die Volumina der beiden Arbeitskammern 47, 48 ändern, wobei die Summe dieser Volumina konstant bleibt.In the first
Der Ringkolben 45 weist angrenzend an die erste Arbeitskammer 47 eine erste Kolbenfläche 49 und angrenzend an die zweite Arbeitskammer 48 eine zweite Kolbenfläche 50 auf. Die erste und die zweite Kolbenfläche 49, 50 sind gleich groß.The
Im zweiten zylindrischen Abschnitt 41 ist eine dritte Arbeitskammer 53 vorgesehen. Die am im Zylindergehäuse 30 befindlichen Ende der Kolbenstange 33 vorgesehene Stirnfläche bildet eine dritte Kolbenfläche 54, die an die dritte Arbeitskammer 53 angrenzt. Der Flächeninhalt der dritten Kolbenfläche 54 ist größer als der Flächeninhalt der ersten und zweiten Kolbenfläche 49, 50. Beim Ausführungsbeispiel ist die dritte Kolbenfläche 54 drei- bis zehn- und vorzugsweise fünfmal so groß wie die erste Kolbenfläche 49 oder die zweite Kolbenfläche 50. Die in Radialrichtung gemessenen Dicke d des Ringkolbens 45 entspricht der Differenz der beiden Durchmesser D1, D2 entspricht.In the second
An den Hydraulikkreis 29 ist die erste Arbeitskammer 47 über die erste Hydraulikleitung 26, die zweite Arbeitskammer 48 über die zweite Hydraulikleitung 27 und die dritte Arbeitskammer 53 über die dritte Hydraulikleitung 28 angeschlossen. Mit der ersten und zweiten Arbeitskammer 47, 48 ist ein erster Hydraulikteilkreis 55 und mit der dritten Arbeitskammer 53 ein zweiter Hydraulikteilkreis 56 hydraulisch verbunden. Die beiden Hydraulikteilkreise 55, 56 sind bei dem hier beschriebenen Ausführungsbeispiel fluidisch vollständig voneinander getrennt.To the
Der erste Hydraulikteilkreis 55 weist einen Vorratsbehälter 57 auf, aus dem eine Motor-Pumpen-Einheit 58 Hydraulikflüssigkeit ansaugt und über eine Druckleitung 59 bereitstellt. An die Druckleitung 59 ist ein Druckspeicher 60 angeschlossen, so dass in der Druckleitung 59 stets eine ausreichende Menge von unter Druck stehendem Hydraulikmedium zur Verfügung steht. Über ein an die Druckleitung 59 angeschlossenes elektrisch ansteuerbares Steuerventil 61 kann die Druckleitung 59 wahlweise mit der ersten Hydraulikleitung 26 oder mit der zweiten Hydraulikleitung 27 verbunden werden. Entsprechend kann eine vom Steuerventil 61 zum Vorratsbehälter 57 geführte Rücklaufleitung 62 über das Steuerventil 61 wahlweise mit der ersten oder der zweiten Hydraulikleitung 26 bzw. 27 hydraulisch verbunden werden. Die zweite Hydraulikleitung 27 ist außerdem über ein Drucksteuerventil 63 mit dem Vorratsbehälter 57 verbunden. Wenn der Druck in der zweiten Arbeitskammer 48 und damit in der zweiten Hydraulikleitung 27 einen vorgegebenen Schwellenwert übersteigt, öffnet das Drucksteuerventil 63, so das Hydraulikmedium aus der zweiten Arbeitskammer 48 in den Vorratsbehälter 57 gefördert werden kann.The first
Das Steuerventil 61 ist beim Ausführungsbeispiel als 4/3-Wegeventil ausgestaltet. Es kann auch durch andere Anordnungen ersetzt werden, wie etwa durch 2-Wege-Einbauventile.The
In einer ersten Schaltstellung I ist die erste Arbeitskammer 47 über die erste Hydraulikleitung 26 mit der Druckleitung 59 verbunden, während die zweite Arbeitskammer 48 über die zweite Hydraulikleitung 27 mit der Rücklaufleitung 62 verbunden ist. In einer zweiten Schaltstellung II sperrt das Steuerventil 61 die Druckleitung 59 sowie eine Abzweigverbindung 27a zur zweiten Hydraulikleitung 27 ab und verbindet die erste Hydraulikleitung 26 mit der Rücklaufleitung 62. Die dritte Schaltstellung III stellt eine hydraulische Verbindung der ersten Arbeitskammer 47 mit der Rücklaufleitung 62 und der zweiten Arbeitskammer 48 mit der Druckleitung 59 her.In a first switching position I, the first working
Der zweite Hydraulikteilkreis 56 enthält ein an die dritte Hydraulikleitung 28 angeschlossenes Hydraulikreservoir 65, das als Niederdruckspeicher ausgeführt werden kann. Über das Hydraulikreservoir 65 wird Hydraulikmedium unter geringem Druck von etwa 5 bis 15 bar bereitgestellt. Das Hydraulikreservoir 65 ist über ein Nachsaugventil 66 mit der dritten Hydraulikleitung 28 fluidisch verbunden. Das Nachsaugventil 66 erlaubt im Nachsaugbetrieb eine Fluidströmung vom Hydraulikreservoir 65 in die dritte Arbeitskammer 53. In umgekehrte Richtung sperrt das Nachsaugventil 66 im Druckregelbetrieb. Parallel zum Nachsaugventil ist mit der dritten Hydraulikleitung 28 eine elektrisch ansteuerbare Druckregeleinrichtung 67 verbunden, über die der in der dritten Hydraulikleitung 28 und damit in der dritten Arbeitskammer 53 herrschende Druck im Druckregelbetrieb gesteuert oder geregelt werden kann. Die Druckregeleinrichtung 67 kann die dritte Hydraulikleitung 28 für eine Rücklaufleitung 68 mit einem Vorratsbehälter 69 verbinden. Zur Ansteuerung der Druckregeleinrichtung 67 sowie des Steuerventils 61 und der Motorpumpeneinheit 58 dient eine Steuereinrichtung 70.The second
In Abwandlung zu dem in
Über den ersten Hydraulikteilkreis 55 wird die Lage und/oder die Bewegung, beispielsweise die Position und/oder die Geschwindigkeit und/oder die Beschleunigung der Kolbenstange 33 gesteuert oder geregelt. In der ersten Schaltstellung I ist die erste Arbeitskammer 47 mit der Druckleitung 59 verbunden, während die zweite Arbeitskammer 48 drucklos mit dem Vorratsbehälter 57 verbunden ist. Aufgrund der Druckdifferenz auf beiden Seiten des Ringkolbens 45 wird auf die Kolbenstange 33 eine Kraft ausgeübt, die die Kolbenstange 33 des Zylinders 23 zum Einfahren veranlasst. Um die Einfahrbewegung der Kolbenstange 33 zu ermöglichen, wird die dritte Arbeitskammer 53 mittels der ansteuerbaren Druckregeleinrichtung 67 mit dem Vorratsbehälter 69 verbunden, so dass Hydraulikmedium aus der dritten Arbeitskammer 53 heraus bewegt werden kann.The position and / or the movement, for example the position and / or the speed and / or the acceleration of the
Eine die Kolbenstange 33 ausfahrende Bewegung wird in der dritten Schaltstellung III des Steuerventils 61 bewirkt. Der höhere Druck in der zweiten Arbeitskammer 48 gegenüber der ersten Arbeitskammer 47 übt auf den Ringkolben 45 und damit die Kolbenstange 33 eine in Richtung des Ausfahrens der Kolbenstange 33 gerichtete Kraft aus. Durch die dabei stattfindende Volumenvergrößerung der dritten Arbeitskammer 53 wird über die dritte Hydraulikleitung 28 und das Nachsaugventil 66 Hydraulikmedium aus dem Hydraulikreservoir 65 nachgesaugt, um die Bewegung der Kolbenstange 33 nicht zu blockieren (Nachsaugbetrieb). Aufgrund der geringen ersten und zweiten Kolbenfläche 49, 50 sind auch die zur Bewegung der Kolbenstange 33 notwendigen Volumenströme in die erste Arbeitskammer 47 und aus der zweiten Arbeitskammer 48 bzw. umgekehrt sehr gering. Die Lage- bzw. Bewegungssteuerung der Kolbenstange 33 kann somit sehr wirtschaftlich erfolgen. Über das Steuerventil 61 und den ersten Hydraulikteilkreis 55 können beispielsweise Vorbeschleunigungen des Blechhalterings 25 erzeugt werden, um die Relativgeschwindigkeit zwischen Oberwerkzeug 15 und Blechhaltering 25 vor dem Aufeinandertreffen zu reduzieren. Auch eine Auswurfbewegung des geformten Blechteils wird über diesen ersten Hydraulikteilkreis 55 und die ersten beiden Arbeitskammern 47, 48 durchgeführt.A movement extending the
Während des Ziehvorgangs muss das umzuformende Blechteil B zwischen dem Blechhaltering 25 und dem Oberwerkzeug 14 mit einer vorgegebenen Blechhaltekraft eingespannt werden. In diesem eingespannten Zustand wird das Blechteil B durch eine fortgesetzte Bewegung des Stößels 12 zum Unterwerkzeug 15 hin über die Form des Unterwerkzeugs 15 gezogen und gleichzeitig durch die im Wesentlichen komplementäre Form des Oberwerkzeugs 14 umgeformt. Die Blechhaltekraft muss dabei eingehalten werden, um die Qualität des Umformteils sicher zu stellen. Bei einer zu großen Blechhaltekraft kann das Blech einreisen. Andererseits können sich während des Umformens Falten im Blech bilden, wenn die Blechhaltekraft zu gering ist.During the drawing process, the sheet metal part B to be formed has to be clamped between the sheet
Die Einstellung der gewünschten und erforderlichen Blechhaltekraft erfolgt durch den zweiten Hydraulikteilkreis 56 und die dritte Arbeitskammer 53 des Hydraulikzylinders 23. Zunächst werden die Zylinder 23 der Zylinderanordnung 22 in ihre Ausgangslage gebracht. Dies erfolgt durch Verschieben des Ringkolbens 45 durch Zu- oder Abfuhr von Hydraulikmedium in bzw. aus der ersten und zweiten Arbeitskammer 47, 48. Das Ziekissen 20 arbeitet in der Lageund/oder Bewegungsregelung. Kurz bevor das Oberwerkzeug 14 mit dem auf dem Blechhaltering 25 befindlichen Blechteil B zur Anlage kommt, kann eine Einwärtsbewegung der Kolbenstangen 33 hervorgerufen werden, um die Relativgeschwindigkeit zwischen Stößel 12 und Blechhaltering 25 zu reduzieren.The setting of the desired and required sheet holding force is performed by the second
Sobald das Oberwerkzeug 14 auf dem Blechteil B aufliegt, schaltet das hydraulische Ziehkissen 20 auf eine Regelung oder Steuerung der Blechhaltekraft um. Hierfür wird das Steuerventil 61 in seine zweite Schaltstellung II gebracht, in der die erste Arbeitskammer 47 mit der Rücklaufleitung 62 verbunden und somit drucklos ist. Die Abzweigverbindung 27a von der zweiten Hydraulikleitung 27 zum Steuerventil 61 wird gesperrt, so dass die zweite Arbeitskammer 48 über das Druckregelventil 63 mit dem Vorratsbehälter 57 verbunden ist. Der Pressenantrieb 13 versucht das Oberwerkzeug 14 weiter in Arbeitsrichtung A zum Unterwerkzeug 15 hin zu bewegen. Dabei steigt der Druck in der zweiten und dritten Arbeitskammer 48, 53 an. Aufgrund dieses Druckanstiegs öffnet das Druckregelventil 63, so dass Hydraulikmedium aus der zweiten Arbeitskammer 48 in den Vorrastbehälter 57 abfliesen kann. Die Blechhaltekraft wird mit Hilfe der Druckregeleinrichtung 67 im zweiten Hydraulikteilkreis 56 eingestellt. Die Druckregeleinrichtung 67 wird über die Steuereinrichtung 70 so angesteuert, dass sich ein gewünschter Druck in der dritten Arbeitskammer 53 einstellt, was zur Einstellung der gewünschten Blechhaltekraft führt. Auf diese Weise bleibt die Blechhaltekraft auch bei einer fortgesetzten Einfahrbewegung der Kolbenstange 33 konstant. Das bedeutet, dass während des Umformens des Blechteils B zwischen Oberwerkzeug 14 und Unterwerkzeug 15 stets die gewünschte Blechhaltekraft vom Blechhaltering 25 ausgeübt wird.As soon as the
In Abwandlung hierzu kann in der zweiten Schaltstellung II die erste Hydraulikleitung 26 bzw. die erste Arbeitskammer 47 abgesperrt sein. Bei dieser Ausgestaltung wird der Druck in der zweiten Arbeitskammer 48 durch das Druckregelventil 63 geregelt. An die erste Arbeitskammer muss dann noch eine Nachsaugleitung angeschlossen werden, um eine Kolbenstangenbewegung zu ermöglichen.In a modification to this, the first
Ist der Umformvorgang abgeschlossen, kann das Oberwerkzeug 14 wieder vom Unterwerkzeug 15 weggefahren werden. Das Ziekissen 20 bzw. der Hydraulikzylinder 23 wird dann nicht mehr zur Einstellung der gewünschten Blechhaltekraft geregelt, sondern wird wieder in eine Lage- oder Positionsregelung betrieben. Das erste Steuerventil 61 schaltet entweder zur Durchführung einer Rückzugbewegung der Kolbenstange 33 in die erste Schaltstellung I oder zur Durchführung einer Auswurfbewegung in seine dritte Schaltstellung III um, in der die Kolbenstange 33 ausgefahren und Hydraulikmedium in die dritte Arbeitskammer 53 nachgesaugt wird. Für eine ausreichende Nachsaugbewegung ist lediglich ein geringer Nachsaugdruck im Bereich von 5 bis 15 bar im zweiten Hydraulikteilkreis 56 notwendig. Im Unterschied dazu stellt der Druckspeicher 60 im ersten Hydraulikteilkreis 55 zur Bewegung der Kolbenstange 33 einen Druck im Bereich von etwa 200 bar bereit, um ausreichend schnelle Kolbenstangenbewegungen durchführen zu können.Once the forming process has been completed, the
In den
Der zweite Hydraulikteilkreis 56 kann zur Bevorratung des Hydraulikreservoirs 65 eine eigene Motor-Pumpen-Einheit 72 aufweisen. Die Druckregeleinrichtung 67 ist beim Ausführungsbeispiel nach
Das Nachsaugventil 66 ist vorzugsweise durch ein druckgesteuertes Sicherheitsventil 74 realisiert. Über einen Eingang 81 steht der Nachsaugdruck des Hydraulikreservoirs 65 am Stößel 75 des Sicherheitsventils 74 an. Ein Ausgang 76 des Sicherheitsventils 74 ist mit der dritten Hydraulikleitung 28 verbunden. Der am Ausgang 76 anstehende Hydraulikdruck wird über eine Steuerleitung 77 einer Steuerkammer 78 zugeführt, die von einer Steuerfläche 79 eines mit dem Stößel 75 verbundenen Kolbens 80 begrenzt wird. Die Steuerfläche 79 ist deutlich größer als die dem Eingang 81 zugeordnete Stirnfläche des Stößels 75. Ist der Druck in der Steuerleitung 77 und damit am Ausgang 75 ausreichend groß, wird der Stößel durch den Druck in der Steuerkammer 78 in eine Schließstellung verschoben, wodurch der Eingang 81 vom Ausgang 76 des Sicherheitsventils 74 getrennt ist. Sinkt der Druck in der Steuerleitung 77 ab, so gibt der Stößel 75 eine Verbindung zwischen Eingang 81 und Ausgang 76 frei, so dass unter Druck stehendes Hydraulikmedium vom Reservoir 65 über den Eingang 81 und den Ausgang 76 in die dritte Hydraulikleitung 28 fliesen kann. Steigt der Druck daraufhin am Ausgang 76 und damit in der Steuerleitung 77 ausreichend stark an, schließt das Sicherheitsventil 74 erneut. Auf diese Weise wird das Ansaugen von Hydraulikflüssigkeit bei einer Ausfahrbewegung der Kolbenstange 33 in die dritte Arbeitskammer realisiert. Während der Druckregelung ist der hydraulische Druck in der dritten Arbeitskammer 53 ausreichend groß, um das Sicherheitsventil 74 in der Schließstellung zu halten. Hydraulikflüssigkeit kann aus der zweiten Hydraulikleitung 28 dann lediglich über die Druckregeleinrichtung 77 und beispielsgemäß das 2/2-Wegeventil 73 abfliesen.The
In
Bei hergestellter Verbindung zwischen Motor-Pumpen-Einheit 72 und der Versorgungsleitung 83 kann das Hydraulikreservoir 65 mit unter Druck stehendem Hydraulikmedium bevorratet werden. Aus der dritten Arbeitskammer 53 kann über die dritte Hydraulikleitung 28 kein Hydraulikmedium abfliesen, da die Verbindung zur Rücklaufleitung 68 abgesperrt ist und das Sicherheitsventil 74 keinen Hydraulikrückstrom zulässt. In der anderen Schaltstellung ist die Verbindung der Motor-Pumpen-Einheit 72 mit den Hydraulikreservoir 65 und dem Sicherheitsventil 74 unterbunden und Hydraulikmedium kann zur Druckreduzierung in der dritten Arbeitskammer 53 über die dritte Hydraulikleitung 28, die Ablaufleitung 68 und die Pumpe der Motor-Pumpen-Einheit 72 in den Vorratsbehälter 69 zurückfliesen. Dabei treibt das zurückströmende Hydraulikmedium die Pumpe an. Der als Elektromotor ausgebildete Motor kann dadurch im Generatorbetrieb Strom erzeugen und beispielsweise in einer Batterie speichern. Auf diese Weise wird die Energieeffizienz des Ziehkissens 20 bzw. der Ziehpresse 10 weiter verbessert.When established connection between the motor-
In Abwandlung zu der in
Sofern die Zylinderanordnung 22 des Ziehkissens 20 mehrere Hydraulikzylinder 23 aufweist, können diese unabhängig voneinander angesteuert werden. Auf diese Weise besteht die Möglichkeit, an verschiedenen Stellen des Blechhalterings 25 unterschiedliche Positionen und/oder Bewegung und/oder Blechhaltekräfte einzustellen. Dies kann bei komplexen Umformprozessen, zum Beispiel bei Karosserieteilen in der Automobilindustrie erforderlich sein.If the
In
Optional kann parallel zum Druckbegrenzungsventil 89 ein zusätzliches Wegeventil 92 geschaltet sein, das von der Steuereinrichtung 70 angesteuert wird. Dieses Wegeventil 92 ist beim bevorzugten Ausführungsbeispiel nach
Die Erfindung betrifft einen Hydraulikzylinder 23 für ein hydraulisches Ziehkissen 20 einer Ziehpresse 10. Der Hydraulikzylinder 23 weist eine erste Arbeitskammer 47, eine zweite Arbeitskammer 48 und eine dritte Arbeitskammer 53. Ein Ringkolben 45 mit einer ersten Kolbenfläche 49 und einer zweiten Kolbenfläche 50 trennt die erste Arbeitskammer 47 von der zweiten Arbeitskammer 48. Die erste und die zweite Kolbenfläche 49, 50 sind gleich groß. Eine im Zylindergehäuse 30 angeordnete Stirnfläche der Kolbenstange 33 bildet eine dritte Kolbenfläche 54, die größer ist als die erste und die zweite Kolbenfläche. Die dritte Kolbenfläche 54 begrenzt die dritte Arbeitskammer 53 des Hydraulikzylinders 23. Die erste und die zweite Arbeitskammer 47, 48 sind zur Steuerung oder Regelung der Lage und/oder der Bewegung der Kolbenstange 33 vorgesehen. Die dritte Arbeitskammer 53 dient zur Steuerung oder Regelung der über die Kolbenstange 33 an der Ziehpresse 10 eingestellte Blechhaltekraft. Die Blechhaltekraft wird durch die Steuerung oder Regelung des Hydraulikdrucks in der dritten Arbeitskammer 53 eingestellt. Dadurch ergibt sich ein kompakter Hydraulikzylinder 23 mit zwei Arbeitskammern 47, 48 zur Lage- und/oder Bewegungsregelung der Kolbenstange 33 und mit einer druckgeregelten weiteren Arbeitskammer 53 zur Einstellung einer Blechhaltekraft. Alle Funktionen des Ziehkissens 20 sind daher in einem Hydraulikzylinder 23 vereint und durch die Trennung in unterschiedliche Arbeitskammern 47, 48 bzw. 53 einfach und wirtschaftlich realisierbar.The
- 1010
- Ziehpressedrawing press
- 1111
- Pressengestellpress frame
- 1212
- Stößeltappet
- 1313
- Pressenantriebpress drive
- 1414
- Oberwerkzeugupper tool
- 1515
- Unterwerkzeuglower tool
- 1616
- Pressentischpress table
- 2020
- hydraulisches Ziekissenhydraulic cushions
- 2121
- Schwebeplattefloating plate
- 2222
- Zylinderanordnungcylinder arrangement
- 2323
- Hydraulikzylinderhydraulic cylinders
- 2424
- Druckstangenpush rods
- 2525
- BlechhalteringSheet holding ring
- 2626
- erste Hydraulikleitungfirst hydraulic line
- 2727
- zweite Hydraulikleitungsecond hydraulic line
- 27a27a
- Abzweigverbindungbranch connection
- 2828
- dritte Hydraulikleitungthird hydraulic line
- 2929
- Hydraulikkreishydraulic circuit
- 3030
- Zylindergehäusecylinder housing
- 3131
- ZylinderinnenraumCylinder interior
- 3232
- zylindrische Durchgangsöffnungcylindrical passage opening
- 3333
- Kolbenstangepiston rod
- 3434
- äußeres freies Ende v. 33outer free end v. 33
- 3535
- erste Dichtungsanordnungfirst seal arrangement
- 4040
- erster zylindrischer Abschnitt v. 31first cylindrical section v. 31
- 4141
- zweiter zylindrischer Abschnitt v. 31second cylindrical section v. 31
- 4242
- Ringstufeannular step
- 4343
- zweite Dichtungsanordnungsecond seal arrangement
- 4545
- Ringkolbenannular piston
- 4646
- Kolbendichtungpiston seal
- 4747
- erste Arbeitskammerfirst working chamber
- 4848
- zweite Arbeitskammersecond working chamber
- 4949
- erste Kolbenflächefirst piston surface
- 5050
- zweite Kolbenflächesecond piston surface
- 5353
- dritte Arbeitskammerthird working chamber
- 5454
- dritte Kolbenflächethird piston area
- 5555
- erster Hydraulikteilkreisfirst hydraulic circuit
- 5656
- zweiter Hydraulikteilkreissecond hydraulic subcircuit
- 5757
- Vorratsbehälterreservoir
- 5858
- Motor-Pumpen-Einheit v. 55Motor-pump unit v. 55
- 5959
- Druckleitungpressure line
- 6060
- Druckspeicheraccumulator
- 6161
- Steuerventilcontrol valve
- 6262
- RücklaufleitungReturn line
- 6363
- DruckregelventilPressure control valve
- 6464
- DruckregeleinrichtungPressure control device
- 6565
- Hydraulikreservoirhydraulic reservoir
- 6666
- Nachsaugventilcavitation valve
- 6767
- DruckregeleinrichtungPressure control device
- 6868
- RücklaufleitungReturn line
- 6969
- Vorratsbehälterreservoir
- 7070
- Steuereinrichtungcontrol device
- 7272
- Motor-Pumpen-Einheit v. 56Motor-pump unit v. 56
- 7373
- 2/2-Wegeventil2/2 way valve
- 7474
- Sicherheitsventilsafety valve
- 7575
- Stößeltappet
- 7676
- Ausgangoutput
- 7777
- Steuerleitungcontrol line
- 7878
- Steuerkammercontrol chamber
- 7979
- Steuerflächecontrol surface
- 8080
- Kolbenpiston
- 8181
- Eingangentrance
- 8282
- 4/2-Wegeventil4/2-way valve
- 8383
- Versorgungsleitungsupply line
- 8585
- Verbindungsleitungconnecting line
- 8686
- Cartridgeventilcartridge valve
- 8787
- Eingang v. 86Entrance v. 86
- 8888
- Ausgang v. 86Output v. 86
- 8989
- DruckbegnezungsventilDruckbegnezungsventil
- 9090
- Steuereingang v. 89Control input v. 89
- 9191
- Steuereingang v. 86Control input v. 86
- 9292
- Wegeventilway valve
- AA
- Arbeitsrichtungworking direction
- BB
- Blechteilsheet metal part
- D1D1
- erster Durchmesserfirst diameter
- D2D2
- zweiter Durchmessersecond diameter
- dd
- Dicke v. 45Thickness v. 45
- II
- erste Schaltstellung v. 61first switching position v. 61
- IIII
- zweite Schaltstellung v. 61second switching position v. 61
- IIIIII
- dritte Schaltstellung v. 61third switching position v. 61
Claims (9)
- Hydraulic die cushion (20) of a drawing press (10), with a hydraulic cylinder (23) having a cylinder housing (30) in which multiple hydraulic working chambers (47, 48, 53) are provided,
wherein the cylinder (23) has a piston rod (33) which serves for connection to a blank holder ring (25) of the drawing press (10),
wherein the cylinder (23) has a first piston face (49) adjoining a first working chamber (47) and a second piston face (50) adjoining a second working chamber (48), wherein the first piston face (49) and the second piston face (50) are substantially the same size, and wherein the cylinder (23) has a third piston face (54) which is larger than the first and second piston faces (49, 50) and which adjoins a third working chamber (53),
with a first hydraulic part circuit (55),
with a second hydraulic part circuit (56) which is hydraulically connected to the third working chamber (53),
wherein the two hydraulic circuits (55, 56) are completely isolated from each other fluidically,
characterized in that the first hydraulic part circuit (55) is hydraulically connected to the first and second working chambers (47, 48),
wherein the first hydraulic part circuit (55) controls or regulates the position and/or the movement of the piston rod (33), and wherein the blank holding force is set by the control or regulation of the hydraulic pressure in the third working chamber (53) by the second hydraulic part circuit (56). - Hydraulic die cushion (20) according to claim 1, characterized in that the third piston face (54) is larger by a factor in the range from 3 to 10 than the first and second piston faces (49, 50).
- Hydraulic die cushion (20) according to claim 1, characterized in that an end face of the piston rod (33) forms the third piston face (54).
- Hydraulic die cushion (20) according to claim 1, characterized in that a ring piston (45) is arranged between the first working chamber (47) and the second working chamber (45) and surrounds the piston rod (33) in the manner of a ring.
- Hydraulic die cushion (20) according to claim 1, characterized in that the cylinder casing (30) delimits a cylinder interior (31) with a first cylindrical portion (40) having a first diameter (D1) and with a second cylindrical portion (31) having a second diameter (D2).
- Hydraulic die cushion (20) according to claim 5, characterized in that the first and second working chambers (47, 48) are arranged in the first cylindrical portion (40) and the third working chamber (53) is arranged in the second cylindrical portion (41).
- Hydraulic die cushion (20) according to claim 1, characterized in that the third working chamber (53) is hydraulically connected to an electrically controllable pressure regulation device (67).
- Hydraulic die cushion (20) according to claim 1, characterized in that the third working chamber (53) is hydraulically connected to a feeder valve (66).
- Hydraulic die cushion (20) according to claim 1, characterized in that the feeder valve (66) is hydraulically connected to a hydraulic reservoir (65) which provides a pressure in the range from 5 bar to 15 bar.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201010019324 DE102010019324B4 (en) | 2010-05-03 | 2010-05-03 | Hydraulic drawing cushion |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2384834A2 EP2384834A2 (en) | 2011-11-09 |
EP2384834A3 EP2384834A3 (en) | 2015-10-21 |
EP2384834B1 true EP2384834B1 (en) | 2018-03-07 |
Family
ID=44510671
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11164657.6A Active EP2384834B1 (en) | 2010-05-03 | 2011-05-03 | Hydraulic die cushion with a hydraulic cylinder |
Country Status (5)
Country | Link |
---|---|
US (1) | US9038431B2 (en) |
EP (1) | EP2384834B1 (en) |
CN (1) | CN102407257B (en) |
DE (1) | DE102010019324B4 (en) |
ES (1) | ES2666722T3 (en) |
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CN201407231Y (en) * | 2009-06-05 | 2010-02-17 | 中国原子能科学研究院 | Hydraulic cylinder structure |
CN101655112B (en) * | 2009-08-21 | 2011-11-16 | 东莞市安德丰电池有限公司 | Series cylinder |
DE102009058407A1 (en) * | 2009-12-15 | 2011-06-16 | Robert Bosch Gmbh | Hydraulic press drive |
-
2010
- 2010-05-03 DE DE201010019324 patent/DE102010019324B4/en not_active Expired - Fee Related
-
2011
- 2011-04-29 US US13/068,054 patent/US9038431B2/en active Active
- 2011-05-03 EP EP11164657.6A patent/EP2384834B1/en active Active
- 2011-05-03 CN CN201110289571.8A patent/CN102407257B/en active Active
- 2011-05-03 ES ES11164657.6T patent/ES2666722T3/en active Active
Non-Patent Citations (1)
Title |
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None * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102019001211A1 (en) * | 2019-02-19 | 2020-08-20 | Hydac International Gmbh | Hydraulic control device |
DE102019001211B4 (en) * | 2019-02-19 | 2021-02-11 | Hydac International Gmbh | Hydraulic control device |
DE102021002179B3 (en) | 2021-04-24 | 2022-09-29 | Hydac International Gmbh | Device for converting volume flows and hydraulic presses with such a device |
Also Published As
Publication number | Publication date |
---|---|
ES2666722T3 (en) | 2018-05-07 |
DE102010019324A1 (en) | 2011-11-03 |
CN102407257A (en) | 2012-04-11 |
EP2384834A3 (en) | 2015-10-21 |
US9038431B2 (en) | 2015-05-26 |
CN102407257B (en) | 2015-02-11 |
EP2384834A2 (en) | 2011-11-09 |
DE102010019324B4 (en) | 2015-05-07 |
US20110265544A1 (en) | 2011-11-03 |
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