EP2319636B1 - Agencement d'entraînement de presse d'une machine-outil - Google Patents

Agencement d'entraînement de presse d'une machine-outil Download PDF

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Publication number
EP2319636B1
EP2319636B1 EP20090014028 EP09014028A EP2319636B1 EP 2319636 B1 EP2319636 B1 EP 2319636B1 EP 20090014028 EP20090014028 EP 20090014028 EP 09014028 A EP09014028 A EP 09014028A EP 2319636 B1 EP2319636 B1 EP 2319636B1
Authority
EP
European Patent Office
Prior art keywords
drive
tool holder
pressure element
spindle
pressing force
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.)
Not-in-force
Application number
EP20090014028
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German (de)
English (en)
Other versions
EP2319636A1 (fr
Inventor
Frank Schmauder
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Trumpf Werkzeugmaschinen SE and Co KG
Original Assignee
Trumpf Werkzeugmaschinen SE and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Trumpf Werkzeugmaschinen SE and Co KG filed Critical Trumpf Werkzeugmaschinen SE and Co KG
Priority to EP20090014028 priority Critical patent/EP2319636B1/fr
Priority to CN201080045581.0A priority patent/CN102574189B/zh
Priority to PCT/EP2010/065666 priority patent/WO2011057879A1/fr
Priority to JP2012538265A priority patent/JP5650232B2/ja
Publication of EP2319636A1 publication Critical patent/EP2319636A1/fr
Application granted granted Critical
Publication of EP2319636B1 publication Critical patent/EP2319636B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • B30B1/18—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 screw means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/088—Characterised by the construction of the motor unit the motor using combined actuation, e.g. electric and fluid actuation

Definitions

  • a press drive arrangement of the above type is known from JP 2001-150191 A ,
  • the prior art relates to a press drive arrangement with a main drive and with an auxiliary drive.
  • the main drive is a hydraulic piston / cylinder drive, the hydraulic piston acts on the workpiece machining provided with a processing tool holder tool.
  • the auxiliary drive is arranged above the main drive and comprises a plunger and an electromotive spindle drive provided for this purpose. By the latter, the plunger of the auxiliary drive can be lowered into the hydraulic cylinder of the main drive, there to increase the oil pressure to increase the available pressing force on the tool holder.
  • the tool holder and the processing punch of the previously known press drive arrangement are initially moved only by the main hydraulic drive in the direction of the workpiece to be machined. After placing the processing stamp on the workpiece is determined by means of a sensor, whether the force applied by the hydraulic main drive pressing force for the workpiece machining sufficient or if an additional pressing force is needed.
  • the plunger of the auxiliary drive is lowered into the hydraulic cylinder of the main drive and thereby generates the required additional pressing force by means of the auxiliary drive.
  • This press drive arrangement comprises a first impact part, by means of which a tool arrangement mounted in an upper tool turret can be acted upon is. Upon being acted upon by the first impact part, a tool mounted on the tool arrangement is moved along a lifting axis in the direction of a metal sheet to be processed. The first impact member is driven by a first piston-cylinder drive.
  • a second impact member is provided on the turret punch press, by means of which the tool assembly is additionally acted upon. The second impact member is driven by a second piston-cylinder unit.
  • the object of the present invention is to provide a press drive arrangement of the type mentioned above with a space-saving design.
  • one of the drive units of the press drive is formed by a spindle drive with a drive spindle, which has an axial receptacle.
  • a spindle drive with a drive spindle which has an axial receptacle.
  • a second pressure element can be added, which acts on the tool holder with an additional pressing force.
  • the connection of the second pressure element is effected by the relative mobility of the tool holder and the second pressure element is inhibited, in particular is canceled.
  • the second pressure element is only used if it proves to be actually necessary. Due to the relative mobility of the tool holder and the second pressure element, the second pressure element, as long as it is not for pressing force is needed, the work stroke is not or at least slower than the tool holder to be moved. Unnecessary acceleration of the second pressure element is avoided. Consequently, the mass to be moved or accelerated is only as large as actually required. In this way, on the one hand, the energy consumption of the press drive arrangement can be reduced, on the other hand, the dynamics can be increased with the same drive power of the press drive arrangement.
  • the drive units can be designed very differently.
  • the first drive unit can be provided with a particularly high dynamic range (eg a maximum acceleration of up to 100 m / s 2 ) but with a relatively low maximum force (eg a maximum force of 40 kN).
  • the second drive unit can be designed to provide higher forces (eg a maximum force of 160 to 250 KN) but lower acceleration values (eg a maximum acceleration up to 10 m / s 2 ). Overall, this results in a highly dynamic press drive which can also provide high pressing forces.
  • the working strokes can be generated exclusively by means of the highly dynamic drive unit.
  • the metal sheet is shifted by 1 mm with respect to the tool, lifting speeds of 1500 strokes per minute can be achieved.
  • z Only in case of need, z.
  • an additional pressing force is initiated by the second drive unit.
  • the tool holder is provided on a plunger on which attack the pressure elements for pressing force introduction. This can be the connection the pressure elements take place in the immediate vicinity of the drive units and there are favorable conditions for the introduction of the pressing force.
  • the plunger is arranged in the axial receptacle of the drive spindle of the spindle drive and at the end facing away from the tool holder end opposite the drive spindle axially projecting and acted upon by one of the pressure elements section.
  • the second pressure element and the tool holder are relatively movable along a working stroke axis along which the working stroke of the tool holder can be generated by means of the press drive arrangement.
  • the second pressure element in the stroke direction are moved slower than the tool holder.
  • the second pressure element can remain unmoved in the stroke direction.
  • the second pressure element even at a caused by the first pressure element working stroke of the tool holder even contrary the stroke direction to be moved. In this way, it can be transferred to a starting position for a subsequent power stroke before the power stroke is completed. Since the press drive arrangement is thus ready for the next working stroke faster after completion of a working stroke, the process time is shortened.
  • the tool holder is acted upon by the second pressure element with an additional pressing force by the relative mobility of the tool holder and the second pressure element is inhibited or canceled only in one direction.
  • the relative mobility is inhibited or canceled at least in a pressing force introduction direction, in which the second pressure element acts on the tool holder with an additional pressing force.
  • the relative mobility In the opposite direction remains according to claim 4, the relative mobility but also obtained at force introduction by the second pressure element. The motion coupling of tool holder and second pressure element is therefore only to the extent necessary.
  • the relative mobility of the tool holder and the second pressure element is inhibited or canceled by a Zuschaltthub, in which a relative movement of the tool holder and the second pressure element is carried out according to claim 5.
  • the second pressure element In the event that the second pressure element is moved toward the tool holder in the stroke direction in the stroke direction, the second pressure element can be accelerated in the stroke direction before introducing an additional pressing force. If the movement of the accelerated pressure element is then inhibited or canceled, the drive power applied to the second pressure element is largely available for acceleration or for loading the tool holder in the stroke direction. The proportion of drive power, which is required for an acceleration of the second pressure element after its connection is reduced.
  • the stroke length of the Zuschaltthubes is dimensioned so that the second pressure element can be accelerated during Zuschaltthub to a desired pressing speed in the stroke direction.
  • the drive power is then completely available for loading the tool holder.
  • the relative mobility of the tool holder and the second pressure element can be canceled by a Zuglerthub a contact surface on the second pressure element comes with a tool holder side contact surface to the plant.
  • the result is a robust and reliable version of the force and motion coupling.
  • the first pressure element By the first pressure element along the Hähubachse immovably connected to the tool holder (claim 7), the first pressure element can constantly initiate pressing force into the tool holder without time delay.
  • additional return means eg. B. return springs, provide deleted.
  • a gearless piezo drive is advantageous due to its high dynamics.
  • a disadvantage of gearless piezoelectric drives but their relatively short stroke lengths.
  • an inductive linear drive in particular a so-called "tube motor” from.
  • the second drive unit is furthermore designed as an electric spindle drive unit, overall results in an electrically driven Pressantriebsan Aunt (claim 8).
  • On hydraulic drive technology can be omitted in this case.
  • the embodiment of the invention according to claim 9 is characterized by a particularly advantageous construction of a press drive arrangement.
  • an embodiment of the invention is provided with a rotary drive unit, by means of which the tool holder is rotatable about the working stroke axis. Due to the rotational adjustability of the tool holder, a tool mounted in the tool holder for workpiece machining can be rotated relative to the workpiece in a desired orientation. In a particularly compact design acts z.
  • a rotary valve with the second pressure element together to take the tool storage to the working stroke axis.
  • the rotary valve can also be arranged separately from the second pressure element, which results in design possibilities of the press drive arrangement, which can be advantageous in particular with regard to the stability of the press drive arrangement.
  • the press drive arrangement can be designed in such a way that automatically an additional pressing force occurs when a certain pressing force introduced into the tool holder by the first pressure element is exceeded is introduced by the second pressure element in the tool holder.
  • detection means are provided, by means of which a need for the initiation of an additional pressing force during the workpiece loading can be determined.
  • the detection means may be formed by displacement and / or force sensors.
  • only the current is consumed, which is consumed by the electric first drive unit. Since the power consumption is a measure of the power provided by the drive, it can be concluded when exceeding a predetermined limit of the power consumption that a connection of the second pressure element is required.
  • the press drive arrangement is controlled so that the second pressure element is switched on for the introduction of the pressing force.
  • FIG. 1 is a machine tool in the form of a punching / forming machine 1 can be seen, which has a C-shaped machine frame 2, in the pharynx 3 a coordinate guide 4 of conventional design is arranged, on which a metal sheet to be machined 5 can be fixed.
  • a processing unit 6 arranged on the upper frame limb of the machine frame 2 comprises a press drive arrangement 7, a tool holder 8 and a processing tool 9 mounted in the tool holder 8.
  • the point to be machined of the metal sheet 5 is arranged by the coordinate guide 4 under the processing tool 9.
  • the tool holder 8 together with the processing tool 9 is then lowered by the press drive arrangement 7 with a working stroke along a working stroke axis 10 in a stroke direction 11 onto the metal sheet 5.
  • a punching is carried out by the machining tool 9, which the metal sheet 5 with a pressing force or punching force is applied, wherein the machining tool 9 during machining with a arranged on the opposite side of the metal sheet 5 second machining tool (not shown) cooperates.
  • the machining tool 9 is raised along the working stroke axis 10 in a return stroke direction 12.
  • the tool holder 8 By means of the press drive arrangement 7, the tool holder 8, together with the machining tool 9, is also rotatable about the working stroke axis 10.
  • editing tools can in the tool holder 8 in addition to punching tools and forming tools, such as embossing, bending and beading tools, etc., are changed.
  • All drives of the punching / forming machine are controlled by a numerical control unit 13.
  • the press drive arrangement 7 of the punching / forming machine 1 FIG. 2 refer to.
  • the tool holder 8 is immovably connected to an elongate plunger 14 whose longitudinal axis coincides with the working stroke axis 10.
  • a first drive unit in the form of a highly dynamic linear motor 15 is provided which forms part of a press drive of the press drive arrangement 7.
  • a likewise secondary secondary part 17 of the linear motor 15 is arranged.
  • the secondary part 17 is provided with a plate-shaped pressure element 19 which is rotatably connected to the plunger 14 by an axial pivot bearing 20 about the working stroke 10, but axially immovable.
  • a damping element may additionally be provided between pressure element 19 and plunger 14.
  • a linear motor in the form of a so-called “tube motor” can be used instead of the linear motor 15 shown.
  • a “tube motor” is characterized by a cylindrical structure, which makes it possible that the secondary part of the motor relative to the primary part is fully rotatable about the lifting axis and can perform a highly dynamic stroke in each relative rotational position.
  • the press drive arrangement 7 has, as part of the press drive, a second drive unit in the form of an electric rotary / lifting drive, which is formed by an electric spindle drive 21.
  • the spindle drive 21 is designed to be less dynamic than the linear motor 15, but can provide a significantly higher pressing force.
  • the spindle drive 21 comprises a drive spindle 22 whose spindle axis coincides with the working stroke axis 10.
  • the drive spindle 22 is provided with two external threads 23 and 24. Both external threads 23 and 24 have the same thread pitch, but are formed in opposite directions.
  • a first drive nut 25 is seated on the first external thread 23, a second drive nut 26 is seated on the second external thread 24.
  • the rotational positions of the drive nuts 25 and 26 about the working stroke axis 10 can be determined by means of sensors 27.
  • a torque motor 28, which is associated with the first drive nut 25, has a frame-fixed stator 29 and a rotor 30 which is formed circumferentially about the working axis 10 and gearless with the drive nut 25 is connected.
  • the stator 29, the rotor 30 and the drive nut 25 overlap each other at least partially along the working stroke axis 10.
  • the second drive nut 26 is associated with a torque motor 31, which is of the same type as the torque motor 28. It has a stator fixed to the stator 32 and a rotor 33 immovably connected to the drive nut 26.
  • the drive spindle 22 is provided with an axial receptacle 34, in which the plunger 14 is arranged.
  • the plunger 14 projects axially through the drive spindle 22.
  • the axial receptacle 34 of the work spindle 22 has a portion of smaller diameter to form a cylindrical shoulder 39.
  • On the inner circumference of the cylindrical shoulder 39 is provided with two radially opposite axial guide grooves 36.
  • the guide grooves 36 extend within the cutting plane according to FIG. 2 ie FIG. 2 shows the inner diameter of the cylindrical shoulder 39 in the peripheral region of the guide grooves 36. In the peripheral region outside the guide grooves 36, the inner diameter of the cylindrical shoulder 39 corresponds approximately to the outer diameter of the plunger 14 (off FIG. 2 not apparent).
  • Two driving wings 35 immovably connected to the plunger 14 project into the axial guide grooves 36 on the inner circumference of the cylindrical shoulder 39.
  • the guide grooves 36 may also be provided in a separate from the cylindrical shoulder 39 axial portion of the receptacle 34, for example in FIG. 2 be arranged offset upwards. Accordingly are in this alternative, the driving wings 35 compared to the in FIG. 2 shown ratios higher up. Since the driver vanes 35 are guided in this case in the guide grooves 36 of the work spindle 22 with a greater radial distance from each other, there is a variant with a more stable mutual guidance of the work spindle 22 and plunger 14th
  • cylindrical shoulder 39 in the in FIG. 2 shown pressing drive 7 on its tool holder side end face a circumferential bearing surface 37.
  • a sensor 39a is used to determine the axial position of the plunger 14 or the tool holder 8 relative to the machine frame 2 and the rotational position of the plunger 14 and the tool holder 8 about the working stroke axis 10th
  • the secondary part 17 of the linear motor 15 performs a corresponding lifting or lowering movement along the working stroke axis 10 relative to the frame-fixed Primary part 16 of the linear motor 15 off.
  • the lifting movement of the secondary part 17 is transmitted via the pressure element 19 and via the axial pivot bearing 20 on the plunger 14. In the same way is one through the Linear motor 15 generated force in the lifting and return stroke 11 and 12 in the plunger 14 introduced.
  • the wings 35 on the drive spindle 22 and the axial guide grooves 36 form an anti-rotation device for the plunger 14.
  • the plunger 14 is rotationally adjustable by means of the spindle drive 21 about the working stroke axis 10.
  • the spindle drive 21 consequently forms a rotary drive unit, by means of which the tool holder 8 provided on the plunger 14 can be adjusted in rotation about the working stroke axis 10.
  • the work spindle 22 is rotated about the working stroke axis 10.
  • the wings 35 serve as a rotary valve, by means of which the plunger 14 is rotated together with the tool holder 8 during the rotational movement of the drive spindle 22 about the working stroke axis 10.
  • the rotational movement of the drive spindle 22 results without the drive spindle 22 also executing a lifting movement along the working stroke axis 10 by the drive nuts 25 and 26 are rotated at the same speed and in the same direction by the torque motors 28 and 31.
  • the plunger 14 can be lowered by means of the spindle drive 21 in the stroke direction 11 or acted upon with an (additional) pressing force in the stroke direction 11.
  • the drive spindle 22 is lowered in the lifting direction 11.
  • the lowering of the drive spindle 22 results without the drive spindle 22 is rotated simultaneously by the drive nuts 25 and 26 are rotated by the torque motors 28 and 31 at the same speed but in opposite directions.
  • a (additional) pressing force generated by means of the spindle drive 21 can be introduced into the plunger 14.
  • the cylindrical shoulder 39 serves as a pressure element, which can act on the plunger 14 and consequently also the tool holder 8 with an (additional) pressing force provided by the spindle drive 21.
  • FIGS. 3a to 3c show three different operating states of the press drive assembly 7 in the punching of a relatively thin metal sheet
  • FIGS. 3a to 3c Punching shown the required pressing force or punching force is generated exclusively by the linear motor 15.
  • FIG. 3a shows the Pressantriebsan Aunt 7 in an operating condition in which the tool holder 8 assumes a starting position before a power stroke.
  • the tool holder 8 is moved together with the machining tool 9 in the lifting direction 11 on the metal sheet 5.
  • the axial movement of the machining tool 8 is effected by the linear motor 15.
  • the spindle drive 21, in particular the drive spindle 22 together with the radial shoulder 39 remains during the stroke movement.
  • the tool holder 8 moves based on the proportions in FIG FIG. 3a in the lifting direction 11 of the cylindrical shoulder 39 away.
  • the tool holder 8 and the cylindrical shoulder 39 perform a relative movement along the working stroke axis 10.
  • FIG. 3b the conditions can be seen when the machining tool 9 just touches the metal sheet 5.
  • the section of the working stroke at which the machining tool 9 only approaches the metal sheet 5 is finished. Since the drive spindle 22 in the same position stopped at the beginning of the working stroke ( FIG. 3a Was arranged), the axial distance between the abutment surface 37 and the inlet surface 38 has increased due to the lowering movement of the plunger 14.
  • the metal sheet 5 in the lifting direction 11 with a pressing force In the following punching processing applied to the processing tool 9, the metal sheet 5 in the lifting direction 11 with a pressing force.
  • the pressing force or punching force with which the machining tool 9 acts on the metal sheet 5 is provided by the linear motor 15.
  • the pressure element 19 connected to the secondary part 17 of the linear motor 15 acts on the plunger 14 with the pressing force.
  • the pressing force is finally applied to the machining tool 9. Since it is a relatively thin metal sheet 5 in the case shown, the maximum of the linear motor 15 to be provided pressing force (about 40 KN) is sufficient to effet fürzustanzen the metal sheet 5.
  • FIG. 3c the operating state of the press drive assembly 7 is shown after the processing tool 9 has punched through the metal sheet.
  • the plunger 14 by means of the linear motor 15 back to the starting position according to FIG. 3a moved with a return stroke.
  • the spindle drive 21 remains stationary during the working stroke and during the return stroke.
  • the punching machining described above can be carried out in a very short time, so that in particular in the thin sheet metal range with the help of the press drive assembly 7 at a pitch of 1 mm stroke numbers up to 1500 strokes / min can be achieved.
  • FIGS. 4a to 4c show three different operating states of the press drive arrangement 7 when punching a relatively thick metal sheet. 5
  • FIG. 4a the conditions can be seen when the processing tool 9 just touches the metal sheet 5.
  • the conditions in FIG. 4a therefore correspond to the circumstances FIG. 3b ,
  • the pressing force with which the machining tool 9 acts on the metal sheet 5 is initially provided exclusively by the linear motor 15. Accordingly, the plunger 14 and thus also the tool holder 8 is acted upon only by the plate-shaped pressure element 19 with a pressing force.
  • the maximum force that can be generated by the linear motor 15 is not sufficient to punch through the relatively thick metal sheet 5.
  • the need for an additional pressing force is determined by the current required by the linear motor 15 by means of the measuring device 18 (FIG. FIG. 2 ) is measured and the measured values are constantly transmitted to the numerical control unit 13.
  • the measured current is compared with a current limit, which corresponds to the current that is consumed by the linear motor 15 at the maximum pressure to be provided by him. If the measured current reaches the predetermined limit value, the numerical control unit 13 evaluates this as necessary for the introduction of an additional pressing force by means of the spindle drive 21.
  • the measuring device 18 and the above-mentioned evaluation part of the numerical control unit 13 thus constitute detection means by means of which the need for initiation an additional pressing force is determined.
  • the numerical control unit 13 triggers a Zuschaltthub, in which the drive spindle 22 moves together with the cylindrical shoulder 39 in the lifting direction 11 by means of the torque motors 28 and 31 becomes.
  • the stroke length of the Zuschaltthubes is sufficient so that the spindle drive 21 can accelerate together with the cylindrical shoulder 39 during the Zuschalthubes to a speed at which the subsequent workpiece machining is performed (press speed).
  • the Zuschaltthub is completed when the contact surface 37 rests against the inlet surface 38.
  • the cylindrical shoulder 39 and the tool holder 8 can not approach further along the working stroke axis 10.
  • the relative mobility of the cylindrical shoulder 39 and the tool holder 8 is thus canceled along the working stroke axis 10 in one direction. It results in the FIG. 4b shown relationships.
  • an additional pressing force is introduced into the tool holder 8 via the introduction surface 38 on the tappet 14, which is generated by the spindle drive 21. Since the spindle drive 21, together with the cylindrical shoulder 39, has already been accelerated to the pressing speed before the abutment surface 37 encounters the introduction surface 38, the spindle drive 21 no longer has to be accelerated further. Its drive power is thus completely available for the acceleration of the plunger 14, the tool holder 8 and the machining tool 9 and for applying the same with an additional pressing force available.
  • the pressing force provided by the linear motor 15 and the additional pressing force provided by the electric spindle drive 21 add up.
  • the sum of the pressing forces is sufficient to punch through the relatively thick metal sheet 5.
  • the conditions after punching the metal sheet 5 are Figure 4c refer to.
  • the processing tool 9 is returned to its original position with a return stroke (FIG. FIG. 3a ) raised by the linear motor 15 and the spindle drive 21 simultaneously moved in the return stroke 12. Under these circumstances, the speed of the machining tool 9 during the return stroke is limited by the speed of the slower spindle drive 21.
  • connection of the spindle drive 21 can be made not only at the time to which a machining tool on the metal sheet 5, but also in the course of the entire workpiece machining or the working stroke.
  • FIG. 5 are again the three main steps in the context of the FIGS. 4a to 4c summarized punching process summarized.
  • the tool holder 8 is acted upon exclusively by the first, plate-shaped pressure element 19 under the introduction of a pressing force ( FIG. 4a ).
  • the second pressure element in this case the cylindrical shoulder 39, is switched on by a Zuschaltthub relative to the tool holder 8 for initiating an additional pressing force.
  • the tool holder 8 through the second Pressure element under introduction of an additional pressing force applied ( FIG. 4b ).
  • the numerical control unit 13 of the punching / forming machine 1 makes it possible to operate the press drive assembly 7 in two different control modes.
  • a basic control mode the press drive assembly is operated according to the procedure described above, i. the processing tool 9 is always lowered only by means of the linear motor 15 on the metal sheet 5 to be processed. Only in case of need an additional pressing force is then initiated by the spindle drive 21.
  • a thick plate control mode can be adjusted. In the thick sheet control mode, the spindle drive 21 is moved from the front. In this way, the time loss caused by the Zuschlthub is avoided.
  • FIG. 6 An alternative type of press drive assembly 40 is FIG. 6 refer to.
  • the press drive assembly 40 assumes its home position prior to a power stroke.
  • the tool holder 41 is provided on a ram 42 extending along the working stroke axis 10.
  • the plunger 42 is rotatable together with the tool holder 41 and a machining tool 43 by means of a rotary drive unit forming a rotary motor 44 about the working stroke axis 10.
  • the rotary motor 44 on a rotating rotor 45, which is gearless connected to the plunger 42.
  • the rotor 45 is arranged within a frame-fixed stator 46.
  • the first spindle drive 47 has a supported on the machine frame 2 stator 49, within which a rotating rotor 50 is provided.
  • the rotor 50 is directly connected to a drive nut 51 which engages with a drive spindle 52.
  • the spindle axis of the drive spindle 52 coincides with the working stroke axis 10.
  • the drive spindle 52 is provided on the tool holder side with a pressure washer 53, which is connected via a thrust bearing 54 with the drive spindle 52.
  • the second spindle drive 48 is arranged on an axial attachment of the drive spindle 52. It has a higher dynamics than the first spindle drive 47, but can only produce a relatively low force.
  • the spindle drive 48 comprises a stator 55, which is supported on the drive spindle 52 of the first spindle drive 47.
  • the second spindle drive 48 has a rotor 56 rotating around the working axis 10.
  • the rotor 56 is gearless connected to a drive nut 57 which engages with a drive spindle 58.
  • the spindle axis of the drive spindle 58 also coincides with the working stroke axis 10.
  • the drive spindle 58 is connected to the plunger 42 via a plate spring 59 and an axial pivot bearing 60.
  • the plate spring 59 is biased in the lifting direction 11 with a spring force which is slightly smaller than the maximum axial force to be provided by the spindle drive 48. Overall, a successive arrangement of the two spindle drives 47 and 48 results.
  • the axial pivot bearing 60 and the disk spring 59 form a first pressure element, which the plunger 42 at its in an axial receptacle 61st Actuate the drive spindle 52 disposed end.
  • the pressure disk 53 forms a second pressure element.
  • FIGS. 7 to 9 show the axial velocity of the drive spindle 52 relative to the machine frame 2 (dashed line) and the axial velocity of the drive spindle 58 relative to the drive spindle 52 (dash-dotted line) in the course of various exemplary workpiece machining operations.
  • the machining tool 43 is lowered exclusively by means of the highly dynamic spindle drive 48.
  • the processing tool 43 hits the metal sheet 5 to be processed.
  • the processing tool 43 now loads the metal sheet 5 with a pressing force provided by the spindle drive 48. This pressing force is transmitted from the drive spindle 58 of the spindle drive 48 via the plate spring 59 and the pivot bearing 60 on the plunger 42.
  • the axial force generated by the spindle drive 48 exceeds the spring force with which the plate spring 59 is biased.
  • the pressing force applied to the machining tool 43 is insufficient to further lower the machining tool 43 placed on the metal sheet 5 by deforming the metal sheet 5, the plunger 42 together with the tool holder 41 and the machining tool 43 stored therein temporarily stops. In the further lowering movement of the drive spindle 58, the plate spring 59 is therefore compressed.
  • the numerical control unit 13 recognizes, as has already been explained with reference to the first type of press drive assembly 7, z. B. by measuring the current required by the spindle drive 48 that the spindle drive 47 must be switched to initiate an additional pressing force. Immediately, ie, almost at time t 2 , the numerical control unit 13 triggers a Zuschaltthub, in which the drive spindle 52 is lowered together with the pressure plate 53 in the stroke direction 11. With the drive spindle 52 and the spindle drive 48 in the stroke direction 11 on the (still) standing plunger 42 is moved, whereby the plate spring 59 is compressed by a further.
  • the stroke length of the Zuschaltthubes is sufficient so that the spindle drive 47 can accelerate during the Zuschaltthubes to a speed at which the subsequent workpiece processing is carried out (pressing speed v p ).
  • the Zuschaltthub is completed when the pressure plate 53 in the stroke direction 11 abuts on the plunger 42 (time t 5 ).
  • the thrust washer 53 and the plunger 42 can not approach further along the working stroke axis 10. Consequently, the relative mobility of the pressure plate 53 and the plunger 42 and thus also the tool holder 41 is repealed in a direction along the working stroke axis 10.
  • the spindle drive 47 now passes via the drive spindle 52 and the pressure plate 53 directly an additional pressing force in the plunger 42 and further into the tool holder 41 a. After completion of the working stroke (time t 6 ), the drive spindle 52 is raised in the return direction 12.
  • FIG. 8 shows the velocity profiles of the drive spindles 52 and 58 in a second, exemplary workpiece machining.
  • the spindle drive 47 serves to extend the working stroke of the machining tool 43 generated by the highly dynamic spindle drive 48.
  • the stroke of the machining tool 43 that can be generated by the spindle drive 48 is relatively short, eg. B. 5 mm.
  • the stroke of the highly dynamic spindle drive 48 is not sufficient, so that in addition the spindle drive 47 must be moved (time t 8 ).
  • the stroke of the machining tool 43 is extended, since the travel paths of the drives 47 and 48 add up.
  • the return stroke can be carried out at least partially by simultaneous operation of both spindle drives 47 and 48 (time period t 9 to t 10 ).
  • the press drive assembly 40 operates in a standard mode. Deviating from this, the press drive arrangement 40 can also be operated in a high-dynamics mode.
  • FIG. 9 the speeds of the drive spindles 52 and 58 can be seen in the course of an exemplary workpiece machining in the high dynamic mode. Also shows FIG. 9 the resulting speed of the machining tool 43 (solid line). For reasons of comparison, the resulting speed of the machining tool 43 is also shown in sections, if it would perform a stroke of about the same length, but only using the low-dynamic drive 47 (line of crosses).
  • the spindle drives 47 and 48 are operated by means of the numerical control unit 13 such that both accelerate and decelerate both drives 47 and 48 during acceleration and deceleration of the machining tool 43. In this way, the fact is made use of that due to the successive arrangement of the spindle drives 47 and 48 whose accelerations add up to a total acceleration of the machining tool 43.
  • the highly dynamic spindle drive 48 is used primarily in the acceleration and deceleration processes.
  • the spindle drive 48 remains during the working stroke and the return stroke even a short time (time t 11 to t 12 and time t 13 to t 14 ).
  • the required pressing force does not exceed the biasing force of the plate spring 59.
  • the Pressantriebsan Aunt 40 is back to its original position.
  • both spindle drives 47 and 48 the same desired positions or the same desired speeds of the machining tool 43 in the course of workpiece machining can be specified, the spindle drives 47 and 48 follow the setpoint specification with different gain factors. In addition, the setpoint specification takes place on condition that the machining tool 43 does not have to be moved faster than the maximum possible speed of the slower spindle drive 47.
  • a highly dynamic Pressantriebsan can result in an analogous manner when using other drive types.
  • Decisive is only that a first drive is provided which drives an actuator in a stroke direction on which a second drive is supported to drive a plunger or a tool holder in the same stroke direction.
  • control means must be provided which allow the operation of the press drive assembly in a high dynamic mode in which a power stroke is generated by simultaneously accelerating and / or decelerating both drives.
  • the switchover stroke does not have to be triggered by the numerical control unit 13. Rather, the Zuschalthub results automatically.
  • the drive spindle 52 becomes common moved in the stroke direction 11 with the pressure disk 53 during the entire working stroke.
  • the machining tool 43 abuts the metal sheet 5 with a pressing force exceeding the spring force of the plate spring 59, the plate spring 59 springs.
  • the processing tool 43 together with the plunger 42 stops for a short time.
  • the drive spindle 52 with the pressure disk 53 immediately approaches the stationary plunger 42 in the stroke direction 11 until the pressure disk 53 bears against the plunger 42. This results in a Zuschalthub.
  • the Einfederungsweg, by which the plunger 42 springs against the drive spindle 52 can be determined for example by means of a measuring device.
  • the currently measured deflection travel is taken into account on the control side.

Landscapes

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

Claims (11)

  1. Dispositif d'entraînement de pression d'une machine-outil, pour produire une course de travail d'un porte-outil (8, 41) prévu sur un poussoir (14, 42), lors de laquelle une pièce (5) peut être sollicitée par un outil (9, 43) monté sur le porte-outil (8, 41),
    - avec un entraînement de pression,
    - avec un premier élément presseur (19, 60), auquel est associée une première unité d'entraînement (15, 48) de l'entraînement de pression et au moyen duquel le porte-outil (8, 41) peut être sollicité par une force de pression fournie par la première unité d'entraînement (15, 48) de l'entraînement de pression, par le fait que le premier élément presseur (19, 60) sollicite le poussoir (14, 42),
    - et avec un deuxième élément presseur (39, 53), auquel est associée une deuxième unité d'entraînement (21, 47) de l'entraînement de pression et au moyen duquel le porte-outil (8, 41) peut être sollicité par une force de pression auxiliaire fournie par la deuxième unité d'entraînement (21, 47) de l'entraînement de pression, par le fait que le deuxième élément presseur (39, 53) sollicite le poussoir (14, 42),
    - sachant que le porte-outil (8, 41) et le deuxième élément presseur (39, 53) sont à mobilité relative lorsque seul le premier élément presseur (19, 60) sollicite le porte-outil (8, 41),
    - et sachant qu'il est prévu des moyens pour entraver, en particulier pour supprimer la mobilité relative du porte-outil (8, 41) et du deuxième élément presseur (39, 53), de sorte que le porte-outil (8, 41), lors de la sollicitation, d'abord exclusivement par le premier élément presseur (19, 60), peut être sollicité, en cas de besoin, par une force de pression auxiliaire fournie par le deuxième élément presseur (39, 53),
    caractérisé en ce que le poussoir (14, 42) est disposé au moins pour partie dans un logement axial (34, 61) d'une broche d'entraînement (22, 52) d'un entraînement à broche (21, 47) qui forme une des unités d'entraînement (15, 21, 47, 48) de l'entraînement de pression.
  2. Dispositif d'entraînement de pression selon la revendication 1, caractérisé en ce que le poussoir (14) est disposé dans le logement axial (34) de la broche d'entraînement (22) de l'entraînement à broche, et en ce que le poussoir (14) présente, à l'extrémité éloignée du porte-outil (8), une partie qui dépasse axialement par rapport à la broche d'entraînement (22) et au niveau de laquelle il peut être sollicité par un des éléments presseurs (19, 39, 53, 60).
  3. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce que le deuxième élément presseur (39, 53) et le porte-outil (8, 41) sont à mobilité relative le long d'un axe de course de travail (10) le long duquel la course de travail du porte-outil (8, 41) peut être produite au moyen du dispositif d'entraînement de pression (7, 40).
  4. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce que le porte-outil (8, 41) peut être sollicité par le deuxième élément presseur (39, 53) par une force de pression auxiliaire par le fait que la mobilité relative du porte-outil (8, 41) et du deuxième élément presseur (39, 53) est entravée ou supprimée dans une seule direction.
  5. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce que le porte-outil (8, 41) peut être sollicité par le deuxième élément presseur (39, 53) par une force de pression auxiliaire par le fait que la mobilité relative du porte-outil (8, 41) et du deuxième élément presseur (39, 53) est entravée ou supprimée par une course enclenchable lors de laquelle a lieu un mouvement relatif du porte-outil (8, 41) et du deuxième élément presseur (39, 53).
  6. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce que le porte-outil (8, 41) peut être sollicité par le deuxième élément presseur (39, 53) par une force de pression auxiliaire par le fait que la mobilité relative du porte-outil (8, 41) et du deuxième élément presseur (39, 53) est supprimée par une course enclenchable lors de laquelle une surface d'appui (37) prévue sur le deuxième élément presseur (39, 53) et une surface d'introduction (38) du côté du porte-outil (8, 41) sont pressées l'une contre l'autre le long de l'axe de course de travail (10).
  7. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce que le porte-outil (8, 41) et le premier élément presseur (19, 60) sont mutuellement reliés sans possibilité de déplacement relatif le long de l'axe de course de travail (10).
  8. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce qu'au moins une unité d'entraînement (21, 47, 48) est réalisée sous forme d'entraînement électrique à broche, et/ou en ce qu'une unité d'entraînement (15) est réalisée sous forme d'entraînement linéaire inductif.
  9. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce que le poussoir (14, 42) peut être sollicité par un élément presseur (39, 60) au niveau d'une partie disposée dans le logement axial (34, 61) de la broche d'entraînement (22, 52).
  10. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu une unité d'entraînement en rotation (21, 44), au moyen de laquelle le porte-outil (8, 41) peut être réglé en rotation autour de l'axe de course de travail (10).
  11. Dispositif d'entraînement de pression selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu des moyens de détection (18, 13) au moyen desquels, lors de la sollicitation du porte-outil (8, 41) exclusivement par le premier élément presseur (19, 60), on peut déterminer si la sollicitation du porte-outil (8, 41) par une force de pression auxiliaire fournie par le deuxième élément presseur (39, 53) est nécessaire.
EP20090014028 2009-11-10 2009-11-10 Agencement d'entraînement de presse d'une machine-outil Not-in-force EP2319636B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP20090014028 EP2319636B1 (fr) 2009-11-10 2009-11-10 Agencement d'entraînement de presse d'une machine-outil
CN201080045581.0A CN102574189B (zh) 2009-11-10 2010-10-19 机床的压力机驱动装置和加工方法
PCT/EP2010/065666 WO2011057879A1 (fr) 2009-11-10 2010-10-19 Dispositif de commande de compression d'une machine-outil, et procédé d'usinage correspondant
JP2012538265A JP5650232B2 (ja) 2009-11-10 2010-10-19 工作機械のプレス駆動装置および加工方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20090014028 EP2319636B1 (fr) 2009-11-10 2009-11-10 Agencement d'entraînement de presse d'une machine-outil

Publications (2)

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EP2319636A1 EP2319636A1 (fr) 2011-05-11
EP2319636B1 true EP2319636B1 (fr) 2013-01-02

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JP (1) JP5650232B2 (fr)
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Publication number Priority date Publication date Assignee Title
CN102259154B (zh) * 2011-06-14 2014-01-29 四川盛堡机电科技有限责任公司 一种锻压机
EP2687359B1 (fr) * 2012-07-18 2016-06-29 Siemens Aktiengesellschaft Machine et procédé d'amélioration de la précision d'un mouvement non linéaire d'un élément de machine
JP6005803B2 (ja) * 2014-07-25 2016-10-12 Thk株式会社 リニアモータ装置及び制御方法
CN106273608B (zh) * 2016-11-03 2018-04-10 西安思源学院 一种双电机螺旋副直驱式回转头压力机
CN106739119B (zh) * 2016-12-30 2019-02-22 江苏扬力数控机床有限公司 一种节能型电动冲头及其工作方法
DE202017006714U1 (de) * 2017-12-21 2018-02-19 Fibro Gmbh Vorrichtung zur Überwachung eines Keiltriebwerkzeugs
AT524824B1 (de) * 2021-02-23 2025-08-15 Trumpf Maschinen Austria Gmbh & Co Kg Elektromechanischer Spindelantrieb

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1484114A (en) * 1923-02-27 1924-02-19 William T Dee Punch
DE500259C (de) * 1928-09-06 1930-06-19 Ludwig Heitmann Vereinigte hydraulische und pneumatisch-hydraulische Lochstanze
CH668103A5 (de) * 1984-05-29 1988-11-30 Sig Schweiz Industrieges Anordnung zum verstaerken der antriebskraft eines steuermotors bei einem linearen stellantrieb.
US5217725A (en) * 1989-04-26 1993-06-08 Canon Kabushiki Kaisha Electrically driven type injection molding apparatus
JPH0825068B2 (ja) * 1991-02-13 1996-03-13 エムテックスマツムラ株式会社 プレス装置
CN2224718Y (zh) * 1995-01-17 1996-04-17 方东 精冲压力机
US5891485A (en) * 1997-05-30 1999-04-06 Sumitomo Heavy Industries, Ltd. Built-in motor type electric injection molding apparatus
JPH1177389A (ja) * 1997-09-05 1999-03-23 Amada Eng Center:Kk リニアモータを用いたプレス機
JP2001009538A (ja) 1999-06-28 2001-01-16 Amada Eng Center Co Ltd 金型打圧装置、及びパンチプレス
JP2001150191A (ja) 1999-11-26 2001-06-05 Hoden Seimitsu Kako Kenkyusho Ltd 加圧装置
JP2003094197A (ja) * 2001-09-21 2003-04-02 Amada Eng Center Co Ltd プレス機械および同プレス機械を用いたプレス加工方法
EP1813412B1 (fr) * 2003-08-25 2011-03-02 Husky Injection Molding Systems Ltd. Ensemble de commande pour faire pivoter et moduler un arbre
FR2859770B1 (fr) * 2003-09-12 2006-02-03 Messier Bugatti Actionneur a deux modes de fonctionnement
JP4547234B2 (ja) * 2004-11-08 2010-09-22 株式会社アマダ タレットパンチプレス
CN201002341Y (zh) * 2007-01-19 2008-01-09 天津市昊鼎精密机械技术有限公司 辊筒摩擦压力机

Also Published As

Publication number Publication date
JP5650232B2 (ja) 2015-01-07
CN102574189B (zh) 2014-12-17
CN102574189A (zh) 2012-07-11
WO2011057879A1 (fr) 2011-05-19
JP2013510003A (ja) 2013-03-21
EP2319636A1 (fr) 2011-05-11

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