EP2629901A1 - Ziehpresse mit dynamisch optimierter blechhaltung - Google Patents
Ziehpresse mit dynamisch optimierter blechhaltungInfo
- Publication number
- EP2629901A1 EP2629901A1 EP11770114.4A EP11770114A EP2629901A1 EP 2629901 A1 EP2629901 A1 EP 2629901A1 EP 11770114 A EP11770114 A EP 11770114A EP 2629901 A1 EP2629901 A1 EP 2629901A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- plunger
- press
- drive
- drawing press
- press according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
- B21D22/20—Deep-drawing
-
- 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
- B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
- B21D22/20—Deep-drawing
- B21D22/22—Deep-drawing with devices for holding the edge of the blanks
-
- 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
- B21D24/12—Devices controlling or operating blank holders independently, or in conjunction with dies mechanically
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/10—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism
- B30B1/14—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism operated by cams, eccentrics, or cranks
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
- B30B1/261—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks by cams
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
- B30B1/266—Drive systems for the cam, eccentric or crank axis
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
- B30B1/28—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks the cam, crank, or eccentric being disposed below the lower platen or table and operating to pull down the upper platen or slide
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/14—Control arrangements for mechanically-driven presses
- B30B15/148—Electrical control arrangements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram
- B30B15/20—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram controlling the speed of the ram, e.g. the speed of the approach, pressing or return strokes
Definitions
- the invention relates to a drawing press, which is particularly suitable for integration in press lines, press lines, hybrid presses or transfer presses for the production of body parts.
- the inventive drawing press is particularly suitable for high Hubzah ⁇ len.
- the first press stage is usually a drawing press, which gives a spatial shape to a board which was then the same. This is done in egg ⁇ nem drawing tool, which holds the edge of the board by clamping ⁇ , or can be controlled to slide towards the sheet center, while the enclosed by the blank holder part of the sheet between a die and a stamp ge ⁇ wished spatial shape receives ,
- the drawing press has a press frame, which can be designed in one or more parts. It can include a head, a table and uprights in between. It is a plunger for receiving a Matrizenwerkmaschines provided which is adjustably mounted in a Ver direction of adjustment. At least one tappet drive which has at least one servo motor, which is connected to the plunger via a Koppelge ⁇ gear or a cam mechanism is used to its drive.
- Koppeige drives every gear is understood in which a uniform rotational movement is transformed into a periodically variable movement ⁇ movement. Thus, it has at least one order ⁇ periodic point at which the linear motion generated is reversed without the rotational direction of the driving servomotor takes a reversed.
- Such a movement characteristic can al ternative also be achieved with a cam gear, since, for example, consists of a rotating cam or a cam and a linearly movable cam follower element.
- the tappet in the case of a single press stroke, running servomotor and closed die tool, assumes the reversal point U t in a few steps. at least two temporally spaced points in time TA, TB. Under closed tool while the state is understood in which the die tool is in contact with the workpiece, such as a sheet metal part.
- the plunger drive has the task of closing movement and the generation of the plate holding force. Instead of braking to the reversal point U t , the braking of the servomotor is initiated late, such that an overflow takes place.
- the area of the overflow is preferably of the order of magnitude which results, for example, in an eight-membered press drive with a blank holder.
- the forming process in which the stamping tool deforms the board held at the edge, can be started upon reaching the reversal point U t , ie, clearly before reaching the holding position of the plunger.
- the punch tool to ⁇ ordered table drive can be started.
- be ⁇ accelerates the servo motor of the sheet holding drive, that the plunger, in the reverse direction of rotation such that the two ⁇ te reaching the reversal point at still closed die tool at least approximately with the time of reaching the movement end point the table drive rock ⁇ ⁇ falls.
- the movement end point of the table drive can be an extended position of its coupling elements, if it is designed as Kniehe ⁇ belgetriebe or as an eccentric or other coupling mechanism.
- the ram has the die tool, so the sheet holding drive, the second reaching the reversal point already an output ⁇ speed that accelerates the lifting of the Matrizentechnikmaschines of the sheet metal part.
- ⁇ zeugs is increased as a whole, so that the press, in turn, can work more quickly overall.
- a mechanically identical press of identical design in which the servomotor of the ram drive stops exactly at the reversal point U t , can be achieved by significantly more than 10% increased stroke rates.
- the table drive is designed as a Koppelge ⁇ gear, the elements are on reaching the obe ⁇ ren end position in an extended position.
- structurally simple Exzen ⁇ terantriebe can be used both in Stö ⁇ ßelantrieb and in the stage drive.
- one extending to only 200 degrees of environmental fangs of the drive wheel of the eccentric gear tooth ⁇ voltage is sufficient for the Stö ⁇ ßelantrieb.
- a Verzah ⁇ tion extends, which extends by 120 ° degrees to the drive of the eccentric. 360 ° all-round gears are superfluous. This leads to significantly less expensive designs of the drives.
- the proposed concept allows Buffalo ei ⁇ nes sheet holder which, for example on a stationary abutment can be supported.
- This blank holder rests with respect to the punch tool, which is moved by the movement of the table currency ⁇ end of the drawing operation in the die tool into it.
- the purpose of the table drive Due to the stationary during the drawing operation positioning of the sheet holder, no, or at least almost no energy is required to apply the sheet holding force.
- the die tool tra ⁇ constricting plunger is held by the slide drive substantially in the vicinity of the reversal point U t.
- the plunger drive to a blocking position, to be in the pressure acting on the plunger forces introduced under at least the substantial, if not fully ⁇ constant bypassing the actual drive source such as a servo motor in the press frame. It can find eccentric gear, toggle ⁇ gear, cam gear or similar gear application.
- the eccentric In an extended position the eccentric is the one who ⁇ position in which the lever arm of the eccentric (line connecting the center of rotation of the eccentric and the eccentric means ⁇ point) connected with the connecting rod volatile ⁇ tet.
- the table drive provides the punch stroke, which is required for shaping the sheet metal part, preferably while the ram drive is in blocking position or other rest position.
- the die tool rests during the drawing process, in particular, it applies the sheet holding force against the likewise stationary sheet holder.
- the sheet holding force is thus preferably ⁇ probably the part of the plunger and carried by it die as static initiated ⁇ senge deputy also part of the plate holder in the Pres and need not be of drives are ⁇ done. This reduces the force required to drive the plunger as well as for driving the stage performance uplifting ⁇ Lich. The Leis ⁇ tion required for the movement of the plunger is low.
- the ram drive need only be uniquely constructed prior to the start of a pull stroke, after placing the die tool on the board. It is then held by the press frame sta ⁇ table.
- the sheet holding force can also be applied by a short-stroke sheet metal holder drive ⁇ who.
- the plate holder drive may also have a blocking position.
- it can be designed as the cam drive o- than short-stroke eccentric drive, which biases the blank holder against the edge of Matrizentechnikmaschines and the clamping forces ⁇ initiates directly in the press frame.
- a Blo ⁇ ckier ein is achieved here when the eccentric is in the straight position or a cam drive standing on a No ⁇ ckenabêt maximum radius.
- a movement of the on ⁇ driving servo motor has no or only a negligible minimum sheet holder movement result.
- the proposed press concept minimizes the power to be applied to the ram drive and the table drive and the power exchange between these drives. In that regard, the press comes, compared to presses where an intense exchange of energy between ram drive and die cushion takes place, with the same power with smaller drives.
- the otherwise required total stroke of, for example, 1300 mm in two strokes namely the stroke of the plunger and the stroke of the table, divided.
- the stroke of the ram serves mainly the opening and closing of the tool, the stroke of the table for moving the die and thus to the through ⁇ execution of the actual drawing process used.
- the ram stroke can only be 100 mm and the table stroke can be only 300 or 400 mm.
- the plunger drive can turn out smaller than a conventional drive.
- the linearly movable table can have a group of passages through which supporting elements extend. These support elements, for example in the form of straight pressure pins, extend through these passages and support the blank holder on an abutment.
- the abutment is preferably arranged stationary with respect to the press frame. This means that the Posi ⁇ tion of the sheet holder with respect to the press frame is fixed or optionally fixed via an adjustment.
- the sheet holding force is determined by the springing of the press frame.
- This springing can be in the range of a few millimeters to a few 10 mm.
- the elastically stored in the press frame energy can be transferred back to the Stö ⁇ ßelantrieb the return stroke of the plunger, which further reduces the gross energy ⁇ consumption of the drawing press.
- the adjusting drive can be a short-stroke toggle mechanism or else an eccentric gear or the like.
- the adjustment stroke will typically be at most a few 10 mm.
- the ⁇ ses concept is particularly advantageous if the slide drive between the two points in time in which it has its reverse position U t, some movement carries out, or if he can drive only with a small force into its blocking Stel ⁇ development and be locked there, As it may be the case with a cam mechanism.
- the blank holder force can be applied after blocking the plunger of the short-stroke plate holder drive.
- the displacement stroke of the blank holder drive is then preferably min ⁇ least as large as the total occurring spring back of the press frame.
- both the ram drive and the table drive are preferably servomotor drives.
- the servomotors work on the plunger or the table preferably via gears that have at least one rest position.
- a rest position is a position in which the Un ⁇ ter arrangement between servo motor and plunger or table in at least one point is very large or even infinite. This applies to eccentric gear as well as to Kniehebelge ⁇ gear in the extended position of the elements involved. Multi-membered transmission with a plurality of draft documents can be used ⁇ advantageous way.
- FIG. 1 A drawing press according to the invention in schematic representation ⁇ tjoner with an open tool
- FIG. 2 shows the press according to FIG. 1 at the beginning of a drawing process
- FIG. 3 shows the press according to FIG. 1 upon completion of a drawing process
- FIG. 4 shows a modified embodiment of the drawing press according to the invention in a schematic illustration
- Figure 5 - a modified drive can serve as a ram drive or alternatively as a table drive in the drawing press according to the invention
- FIG. 6 shows a further modified drive which can serve as a ram drive in the drawing press according to the invention
- FIG. 1 illustrates a drawing press 10 which can be used to produce large sheet-metal parts, for example body parts.
- the drawing press 10 includes a press frame, the at least one, preferably meh ⁇ rere, preferably vertically oriented stand 11, 12, ei ⁇ nen head 13, which is supported by the uprights 11, 12 and a pedestal 14 belonging under or between the uprights 11, 12 is arranged.
- the head 13, the stand 11, 12 and the base 14 form a closed frame.
- a plunger 15 is mounted linearly movable in a vertical movement direction 16, for example.
- linear guides 17 provided on the uprights 11, 12 are used.
- the ram 15 serves to receive an upper work ⁇ generating part, which is designed as a female die eighteenth It is shown in section in Figure 1 and has a rim 19 which serves to clamp and hold the edge of a workpiece during the drawing operation.
- the workpiece is a printed circuit board 20, that is, an initially flat sheet forms ge ⁇ .
- the rim 19 surrounds a tool cavity 21 into which the workpiece is to be deformed.
- a ram drive 22 which comprises one or more servo motors 23, 24 which are connected via one or more gear 25, 26 with the plunger 15.
- the two gear 25, 26 are Koppelge ⁇ gear of suitable design.
- In the present,sbei ⁇ game are in each case by way of example to one another mirror-symmetrically constructed eccentric. They umfas ⁇ sen each case an eccentric 27, 28, which is coupled via a connecting rod 29, 30 with the plunger 15 °.
- the drawing press 10 has a press table 31, on which a travel table 32 can be arranged.
- a travel table 32 is used in a known manner the tool change.
- the drive table 32 carries the lower tool part, to which a tool support 33, with a punch tool 34 arranged thereon and a blank holder 35 belong.
- the punch tool 34 is a male whose upper contour corresponds to the cavity 31. It is surrounded by the rectangular-shaped sheet holder 35 in most cases, wherein the sheet holder 35 and the punch tool 34 are movable relative to each other with respect to the movement direction 16.
- the press table 31, or its table drive 36 is linearly movable in the press frame on the uprights 11, 12 and / or the base 14 by means of guide means 37 in the direction of movement.
- To the table drive 36 include a o or more gear 38, 39, which, like the transmission 25, 26, each constructed as a coupling mechanism. They know a blocking position. They are designed, for example, as eccentric gears which bring the press table 31 into drive connection with one or more servomotors 40, 41.
- the gear 38, 39 each comprise an eccentric 42, 43, which is connected via a connecting rod 44, 45 with the press table 31.
- the blank holder 35 is supported on suitable abutment elements, for example in the form of pressure pins 46, on an abutment 47.
- the abutment 47 may be arranged stationary in the simplest case with respect to the base 14. Alternatively, it may be associated with an adjustment device 48 which can adjust the position of the abutment 47 with respect to the direction of movement 16, for example. This usually follows in the no-load condition.
- the Verstellap ⁇ adapter 48 may also be designed so that it can adjust the abutment 47 under load, for example, to specifically influence or regulate the force acting on the sheet holder 35 and thus on the drawing edge of the workpiece force.
- the adjusting apparatus 48 may be in the form of hydraulic cylinders, toggle-lever adjusters, reciprocating spindle adjusters or the like. Between the abutment 47 and the table drive 36 16 oriented linear guides 49 may be provided in the direction of movement.
- the drawing press 1 is in Offenstel ⁇ ment.
- the plunger 15 is moved by appropriate rotation of the eccentric 27, 28 in an upper position.
- the press table 31 is driven by corresponding rotation of the eccentric 42, 43 in a lower position.
- the punch tool 34 protrudes little or not much above the sheet holder 35.
- a substantially planar board 20 can be placed on the blank holder 35.
- the servomotors 23, 24 begin to brake when approaching the reversal point U t , pass through the reversal point U t and then stop, as can be seen from the diagram of FIG. 7, curve I there.
- the plunger 15 thus performs after passing through the time TA a barely noticeable movement away from the reversal point U t .
- the servo motors 23, 24 then stop at the time TC and return immediately or shortly after its direction of rotation about to again the reversal point U t pres ⁇ fen. This happens at the time TB.
- Errei ⁇ chen the gear 38, 39 at precisely this time, marking their expanded positions the completion of the drawing process.
- the opening movement of the die tool 18 starts by moving away from the turnaround point U t in the case of already rotating, ie, in the time interval from TC to TB, pre-accelerated servomotors 23, 24.
- the opening of the mold ge ⁇ schieht therefore very fast, faster anyway, as it the case would be, the servomotors would still stand still at time TB.
- the braking of the servomotors when approaching the plunger position to the reversal point U t can be done relatively late, so that despite possibly full braking power at TA still no engine stall is reached, but only at TC.
- the actual drawing process is initiated via TC to TB, the end of which is illustrated in FIG.
- the servomotors 40, 41 are actuated, so that the eccentrics 42, 43 with the connecting rods 44, 45 go into an extended position, and thus reach the top dead center of the table drive 36.
- the punch tool 34 is fully retracted into the die tool 18.
- the reduction between the servomotors 41, 42 and the press table 31 approaches infinity, so that the punch tool 34 can apply very high pressures to the workpiece.
- the tool consisting of the die tool 18 and the punch tool 34 is opened again as described above, by moving the plunger 15 upwards and the press table 31 downwards while the sheet holder 35 continues to rest.
- the drawing press 10 so far described offers a concept which is suitable for the further use of drawing tools which have hitherto been used in presses with drawing cushions arranged at the bottom.
- the press table 31 has a group 50 of openings 51, 52, 53 through which the support elements 46 can optionally be inserted therethrough. NEN.
- tools of different sizes can be used, whose blank holder 35 span different distances. This results in a geometrically variable introduction of force for the sheet holder 35. This also provides increased freedom or comfort in tool design.
- the presented operating concept with at least two passes through the reversal point U t during a press cycle shortens the cycle time and increases the stroke rate and output.
- the plunger 15 can be moved by the gear 25, 26 pulling when the servomotors 23, 24 are arranged on the base 14.
- the drive of the press table 31 in the ⁇ ser and also in all other imple mentation shapes can be effected by a single servo motor 40 when the gears of the eccentric 42, 43 mesh or if the eccentric 42, 43 in other ways by suitable transmission ⁇ medium are interconnected.
- the eccentric 42, 43 may optionally be formed as a full circle. This measure can also be found in the eccentrics 27, 28 and their gears application.
- Figure 5 shows a drive means for selectively operating both as a slide drive 22 as well as Tischan ⁇ can find application 36.
- this drive has a rest position when its links 52, 53 are in an extended position. In this extended position, a rotation of the antrei ⁇ benden servo motor 23, 24 (or corresponding to 40, 41) causes no or only an extremely low linear adjustment of the connected ⁇ member, for example, the plunger 15 on the ⁇ se acting forces are in a straight path through the links 52, 53 supported on the machine frame without the Load servo motors.
- FIG. 6 schematically shows a transmission 22, which is designed as a cam mechanism 54. It has a cam disk 55 driven by the servomotor 23 and a cam follower 56, eg in the form of a roller, which follows the curve circumference and thus performs a linear, reciprocating movement predetermined by the different radii of the cam disk.
- the cam follower 56 is guided in a linear guide 57 and connected to the plunger 15.
- the cam gear can provide the movement curve II of Figure 7.
- the cam 55 has at its one portion 58 of constant radius. This ⁇ be true the reversal point U t.
- the servomotor 23 may not only reversing, but alternatively also be continuously operatio ⁇ ben.
- the plunger 15 then moves to the reversal point U t , takes this during the time TA, the time TB and possibly other times eg between TA and TB.
- the plate holding force does not have to be applied by the rotating servomotor in this phase, because forces acting on the plunger 15 produce no torque because of the radius of the cam which is constant in this section 58.
- the servomotor 23 can be operated at a constant speed, at a varying speed, with a constant direction of rotation or with alternating directions of rotation. It also eliminates time to slow down and accelerate the servomotor before and after the drawing process. As in the previous example with eccentric this acceleration ⁇ phases can be laid in the time of the drawing process. Alternatively, at least in the embodiment according to FIG. gur 6 acceleration or braking operations are partially or completely omitted.
- the drawing press (10) has to drive its plunger (15) a direction reversing gear (22, 54), eg a coupling gear, and at least one Servomo ⁇ gate (23).
- the servomotor (23) passes through that of the reversal point U t of the plunger movement is determined by the kinematics of the linkage, for example, the extended position of an eccentric drive.
- the servo motor (23) during closing of the tool (18), thus during a pressing ⁇ hubs driven so as to U t this point of reversal passes to ⁇ next, then stops, reverses and then ⁇ again passes to the tool (18) reopen. So ⁇ with the still braking and re-acceleration is the servo motor for the upper ram (15) still or already during the actual drawing process, that takes place during the sheet ⁇ forming, which significantly shortens the cycle time.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Shaping Metal By Deep-Drawing, Or The Like (AREA)
- Press Drives And Press Lines (AREA)
- Control Of Presses (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010060103A DE102010060103B4 (de) | 2010-10-21 | 2010-10-21 | Ziehpresse mit dynamisch optimierter Blechhaltung |
PCT/EP2011/068041 WO2012062532A1 (de) | 2010-10-21 | 2011-10-14 | Ziehpresse mit dynamisch optimierter blechhaltung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2629901A1 true EP2629901A1 (de) | 2013-08-28 |
EP2629901B1 EP2629901B1 (de) | 2016-07-20 |
Family
ID=44801022
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11770114.4A Not-in-force EP2629901B1 (de) | 2010-10-21 | 2011-10-14 | Ziehpresse mit dynamisch optimierter blechhaltung und verfahren zum tiefziehen |
Country Status (9)
Country | Link |
---|---|
US (1) | US9713832B2 (de) |
EP (1) | EP2629901B1 (de) |
CN (1) | CN103402666B (de) |
BR (1) | BR112013009639A2 (de) |
CA (1) | CA2814593C (de) |
DE (1) | DE102010060103B4 (de) |
ES (1) | ES2587231T3 (de) |
MX (1) | MX346221B (de) |
WO (1) | WO2012062532A1 (de) |
Families Citing this family (12)
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DE102011016669B4 (de) * | 2011-04-12 | 2016-03-24 | Schuler Pressen Gmbh | Verfahren zum Betreiben einer Presse mit Unterantrieb und danach betriebene Presse |
DE102013105468B4 (de) * | 2013-05-28 | 2015-10-01 | Schuler Pressen Gmbh | Verfahren zur Steuerung einer Presse mit variabler Getriebeübersetzung |
DE102013105596B4 (de) | 2013-05-31 | 2015-10-29 | Schuler Pressen Gmbh | Presse und Verfahren zum Betreiben der Presse |
EP2843779A1 (de) * | 2013-09-03 | 2015-03-04 | Exmore Group NV | Crimppresse |
US9352375B2 (en) | 2013-09-11 | 2016-05-31 | Stolle Machinery Company, Llc | Actuator with variable speed servo motor for redraw assembly |
CN104353753B (zh) * | 2014-11-11 | 2018-04-06 | 营口锻压机床有限责任公司 | 汽车滤清器壳体拉伸机 |
DE102015110748A1 (de) * | 2015-07-03 | 2017-01-05 | Schuler Pressen Gmbh | Verfahren zur Einstellung eines Phasenversatzes einer mehrfach wirkenden mechanischen Querwellenpresse sowie eine Presse nach diesem Verfahren |
DE102015113267A1 (de) * | 2015-08-12 | 2017-02-16 | Rainer Naroska Verpackungsmaschinen Gmbh & Co. Kg | Tiefziehwerkzeug zum Tiefziehen von Rohlingen |
CN111185513B (zh) * | 2020-02-24 | 2024-07-02 | 苏州斯莱克精密设备股份有限公司 | 高速罐体拉伸机的压边机构 |
US11511332B2 (en) * | 2020-05-28 | 2022-11-29 | Stolle Machinery Company, Llc | Cam driven bodymaker |
CN111618138B (zh) * | 2020-06-05 | 2022-05-10 | 湖南华涟智能智造科技有限公司 | 一种基于齿轮传动原理的五金板材折弯装置 |
CN112139339B (zh) * | 2020-09-15 | 2021-08-10 | 大连理工大学 | 一种金属薄壁曲面件超低温成形设备 |
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US3054496A (en) | 1959-05-18 | 1962-09-18 | Meyer Geo J Mfg Co | Article-orienting means for labeling machines |
EP0302936B1 (de) * | 1986-12-29 | 1993-12-01 | ISHII, Mitoshi | Servolenkvorrichtung fuer eine presse |
US4969348A (en) | 1989-11-06 | 1990-11-13 | Aluminum Company Of America | Feed system for a redraw press |
JP2001062591A (ja) * | 1999-08-24 | 2001-03-13 | Amada Co Ltd | プレス機械 |
DE10117578B4 (de) | 2001-04-07 | 2007-09-13 | Müller Weingarten AG | Ziehpresse |
DE50304160D1 (de) * | 2002-10-18 | 2006-08-17 | Tetra Laval Holdings & Finance | Vorrichtung zum stanzen, prägen und/oder verformen flacher elemente |
CN1227078C (zh) * | 2003-08-26 | 2005-11-16 | 苏州市越海拉伸机械有限公司 | 液压双动拉伸机压边机构 |
JP5050238B2 (ja) * | 2004-06-14 | 2012-10-17 | 株式会社小松製作所 | ダイクッション制御装置及びダイクッション制御方法 |
JP4587752B2 (ja) * | 2004-09-15 | 2010-11-24 | 株式会社小松製作所 | ハイブリッド制御サーボプレスの制御装置およびその制御方法 |
JP4162660B2 (ja) * | 2005-01-13 | 2008-10-08 | アイダエンジニアリング株式会社 | サーボプレス |
DE102005038583B4 (de) * | 2005-08-16 | 2007-12-27 | Schuler Pressen Gmbh & Co. Kg | Pressen-Antriebsmodul und Verfahren zur Bereitstellung einer Pressenbaureihe |
US7765848B2 (en) * | 2006-04-14 | 2010-08-03 | Honda Motor Co., Ltd. | Press working method and press working apparatus |
US20090090161A1 (en) * | 2006-05-09 | 2009-04-09 | Hiroyuki Amino | Underdrive-type press |
DE102006025271B3 (de) | 2006-05-31 | 2007-12-27 | Schuler Pressen Gmbh & Co. Kg | Zieheinrichtung mit hydrostatischer Spindellagerung |
JP4932423B2 (ja) * | 2006-10-17 | 2012-05-16 | 本田技研工業株式会社 | プレス加工装置およびプレス加工方法 |
-
2010
- 2010-10-21 DE DE102010060103A patent/DE102010060103B4/de not_active Expired - Fee Related
-
2011
- 2011-10-14 CN CN201180061521.2A patent/CN103402666B/zh not_active Expired - Fee Related
- 2011-10-14 WO PCT/EP2011/068041 patent/WO2012062532A1/de active Application Filing
- 2011-10-14 BR BR112013009639A patent/BR112013009639A2/pt not_active Application Discontinuation
- 2011-10-14 ES ES11770114.4T patent/ES2587231T3/es active Active
- 2011-10-14 CA CA2814593A patent/CA2814593C/en not_active Expired - Fee Related
- 2011-10-14 US US13/866,107 patent/US9713832B2/en active Active
- 2011-10-14 EP EP11770114.4A patent/EP2629901B1/de not_active Not-in-force
- 2011-10-14 MX MX2013004469A patent/MX346221B/es active IP Right Grant
Non-Patent Citations (1)
Title |
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See references of WO2012062532A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN103402666A (zh) | 2013-11-20 |
ES2587231T3 (es) | 2016-10-21 |
BR112013009639A2 (pt) | 2016-07-12 |
US9713832B2 (en) | 2017-07-25 |
DE102010060103B4 (de) | 2013-04-11 |
WO2012062532A1 (de) | 2012-05-18 |
CN103402666B (zh) | 2016-01-20 |
US20130333437A1 (en) | 2013-12-19 |
MX346221B (es) | 2017-03-09 |
CA2814593A1 (en) | 2012-05-18 |
DE102010060103A1 (de) | 2012-04-26 |
CA2814593C (en) | 2016-12-13 |
MX2013004469A (es) | 2013-10-30 |
EP2629901B1 (de) | 2016-07-20 |
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