EP2926920A1 - Dispositif de presse destiné au traitement d'une pièce - Google Patents

Dispositif de presse destiné au traitement d'une pièce Download PDF

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Publication number
EP2926920A1
EP2926920A1 EP14163064.0A EP14163064A EP2926920A1 EP 2926920 A1 EP2926920 A1 EP 2926920A1 EP 14163064 A EP14163064 A EP 14163064A EP 2926920 A1 EP2926920 A1 EP 2926920A1
Authority
EP
European Patent Office
Prior art keywords
tool unit
cylinder housing
press
counter
bridging
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.)
Withdrawn
Application number
EP14163064.0A
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German (de)
English (en)
Inventor
Berthold Daub
Daniel Hesse
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.)
Grabener Pressensysteme & Co KG GmbH
Original Assignee
Grabener Pressensysteme & Co KG GmbH
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 Grabener Pressensysteme & Co KG GmbH filed Critical Grabener Pressensysteme & Co KG GmbH
Priority to EP14163064.0A priority Critical patent/EP2926920A1/fr
Priority to TW103142573A priority patent/TW201538308A/zh
Priority to KR1020140190401A priority patent/KR20150114379A/ko
Priority to US14/611,492 priority patent/US20150273779A1/en
Priority to CN201510150641.XA priority patent/CN104972684A/zh
Priority to JP2015075183A priority patent/JP2015196195A/ja
Publication of EP2926920A1 publication Critical patent/EP2926920A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/02—Dies; Inserts therefor; Mounting thereof; Moulds
    • B30B15/026—Mounting of dies, platens or press rams
    • 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
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/002—Drive of the tools
    • 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
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
    • B21D28/16—Shoulder or burr prevention, e.g. fine-blanking
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/28—Arrangements for preventing distortion of, or damage to, presses or parts thereof

Definitions

  • the invention relates to a press device, in particular a toggle press, for machining a workpiece with a lower tool unit and with a movable upper tool unit, wherein the upper tool unit a hold-down device with a plunger part, by means of which the workpiece to be machined against the lower tool unit is untenable, and the lower tool unit a Counter holding device with a further plunger part, by means of which the workpiece to be machined against a tool part of the upper tool unit is untenable, comprising, wherein the plunger parts in each case by means of a drive device relative to the upper tool unit and / or the lower tool unit are displaced.
  • Generic press devices are known from the prior art. In some forming processes, such as gene cutting, a down and an anvil are needed to precisely machine the workpiece.
  • the holding-down device is located as a ram part in an upper tool unit and lies in a forming process flush on the material to be formed of the workpiece in order to counteract the compressive and tensile stresses occurring during the forming process.
  • the counterholder is located as a further plunger part immediately below the material to be formed. It keeps during the entire forming process with a force as constant as possible against a cutting punch coming from above to ensure a controlled forming process. Following the forming process can the counter-holder or the related additional plunger part serve as an ejector for the cut part.
  • Lower and counter holders can be designed mechanically (for example, by mechanical spring elements), pneumatically or hydraulically (for example, by pneumatically or hydraulically driven spring elements).
  • the invention has for its object to further develop generic devices such that their manufacturing precision and reliability are further increased.
  • a press device for machining a workpiece with a lower tool unit and with a movable upper tool unit, in which the upper tool unit a hold-down device with a plunger part, by means of which the workpiece to be machined against the lower tool unit can be held down , and the lower tool unit comprises a counter holding device with a further plunger part, by means of which the workpiece to be machined against a tool part of the upper tool unit is untenable, the plunger parts are each displaced by means of a drive means relative to the upper tool unit and / or the lower tool unit, and wherein the press device characterized in that the counter-holding device and / or the hold-down device bridging means for bridging an acceleration phase of the respective Antriebssei include in which the respective drive means can be accelerated to the respective ram speed.
  • a counterholder of the lower tool unit can move from the beginning exactly synchronously with the movement of the upper tool unit or a related punch or the like.
  • the manufacturing precision can be significantly increased.
  • a response time with a sufficiently large time window is available for the actual drive device in order to likewise accelerate the respective drive device to the respective ram speed before, for example, the drive device subsequently drives the counter-holder.
  • the respective plunger part can be structurally very easily accelerated independently of its actual drive device by the respective corresponding plunger part.
  • the essential goal is achieved to provide a total drive, by means of which at the beginning of a cutting process a precise synchronization of the movement, in particular of the counter-holder can be made to a plunger part speed of the upper tool unit.
  • the respective plunger part whose speed has been synchronized according to the invention for example, take over an ejector function, which is preferably freely programmable with respect to its path.
  • pressing device in the context of the invention describes any type of presses in which the upper tool unit relative to the lower tool unit or vice versa, to thereby machine the workpiece by means of at least one tool. It is understood that this press device can be configured almost arbitrarily. It is particularly advantageous if it is designed as a toggle press and in this case especially as a precision cutting and forming press with servo toggle lever drive, since this is often involved in a variety of high-precision machining processes. Additional advantages are explained in detail below in connection with a press apparatus designed by way of example as a precision cutting and forming press with servo toggle lever drive.
  • upper tool unit herein describes a press ram of a press, which is moved to edit the workpiece against a press table.
  • lower tool unit herein describes a press table of a related press.
  • a tool or tool part used on the present press device can be of different nature.
  • it may be a cutting tool, as will be explained later.
  • the plunger part of the hold-down device comprises a hold-down device. Accordingly, the further plunger part of the counter-holding device comprises a counter-holder.
  • the movement of the hold-down device is not stopped.
  • the hold-down device acts as a scraper during the upward movement of the upper tool unit via a defined path. While the stripping, the movement of the hold-down device must continue to run synchronously with the plunger movement.
  • two operating modes are provided for operating the low or counter holding devices: setting up and automatic.
  • the operator can automatically approach a pre-entered target position or a coupling position suitable for the press position in set-up mode.
  • the low or counter holding devices can be moved independently but never several at a time.
  • automatic mode the selected device is activated and coupled via a cam to the movement of the upper tool unit.
  • the values set in set-up mode are valid. Several facilities can be selected and activated together here.
  • the present bridging means it is advantageously possible to bridge the period of time required to accelerate the respective drive device in suitable catfish to the speed of the plunger part in order to exclusively drive, with a time delay, the plunger part assigned to it.
  • the bridging means provided in the context of the invention can be of various shapes.
  • a pneumatic spring device can be configured structurally simple in the lower tool unit or the upper tool unit.
  • the present pneumatic spring device is structurally particularly expediently realized when the pneumatic spring device comprises a nitrogen spring.
  • the bridging means comprise a reaction path of more than 10 mm or more than 20 mm, preferably 25 mm.
  • a reaction path of more than 10 mm or more than 20 mm, preferably 25 mm.
  • the present reaction spring travel of 25 mm can be provided structurally simple and reliable by means of the nitrogen spring.
  • a lesser reaction path of 10 mm or 20 mm may be sufficient to provide a required bridging period.
  • Such a required bridging period can be reliably provided in any case when the reaction path is 25 mm.
  • reaction path can be chosen even larger. However, this does not make sense, since a response time of 25 mm can provide a sufficiently long response time. In addition, larger reaction spring travel only need unnecessarily much space.
  • reaction path is simply formulated in a constructive manner if the reaction path is interrupted by means of a pressure chamber filled with a pressure medium a piston bottom of the piston part and a cylinder housing end wall of the cylinder housing is formed.
  • the pressure medium can be of various types. It preferably comprises nitrogen.
  • the bridging means can be structurally particularly advantageous integrated into the upper tool unit or in the lower tool unit of the present press device, when the bridging means between the plunger part and the drive means are arranged.
  • the bridging means comprise a cylinder housing and a piston part, wherein the plunger part is arranged on the cylinder housing.
  • a region of the lower tool unit facing the upper tool unit can be overcome in a structurally simple manner by bridging means arranged within the lower tool unit, when the plunger part is arranged at a distance from the cylinder housing end wall on the cylinder housing by web elements.
  • the bridging means can be addressed in a structurally simple and rapid manner if the bridging means comprise a cylinder housing and a piston part guided therein, the cylinder housing being displaceably arranged in the lower tool unit in the pressing direction of the upper tool unit.
  • the bridging means have a cylinder housing and a piston part guided therein, the cylinder housing being displaceably guided in a guide bush of the upper tool unit or the lower tool unit on the one hand, the cylinder housing are moved relative to the upper tool unit or the lower tool unit and, on the other hand, relative to the piston part.
  • the bridging means comprise a cylinder housing and a piston part guided therein, wherein the cylinder housing is displaceable by means of the piston part with respect to the upper tool unit or the lower tool unit.
  • the cylinder housing via the piston part by means of the drive device can be easily moved constructively. This is the case, for example, if the further plunger part of the counter-holding device is to be moved synchronously with the upper tool unit, or if the further plunger part of the counter-holding device is to function as an ejector for a machined workpiece.
  • the respective plunger part can easily be displaced with respect to the upper tool unit or the lower tool unit if the bridging means comprise a cylinder housing and a piston part guided therein, wherein the piston part is arranged on a connecting rod part of an eccentric drive of the drive device.
  • a sufficient counterforce can be applied, in particular, to the further plunger part of the lower tool unit if the pneumatic spring device is preloaded with a spring biasing force F having a value of more than 100 kN or a value of more than 200 kN, preferably a value of 300 kN.
  • a key feature of the present invention is in particular a synchronization of the other plunger part or the counter-holder on the speed of the plunger part and the upper tool unit at a time, which represents the beginning of about a cutting process or the like.
  • a press device for machining a workpiece with a lower tool unit, with a movable thereto upper tool unit, and with an overload protection unit to protect the press device in case of malfunction
  • the upper tool unit a Hold-down device with a plunger part, by means of which the workpiece to be machined with respect to the lower tool unit is untenable
  • the lower tool unit comprises a counter holding device with a further plunger part, by means of which the workpiece to be machined against a tool part of the upper tool unit is untenable
  • the plunger parts in each case by means of a drive device relative to the upper tool unit and / or the lower tool unit are displaceable
  • the press device is characterized in that the Schmidteinrichtun g and / or the hold-down device comprise bridging means for bridging a tripping time for triggering the overload protection unit.
  • a malfunction may occur due to any failure of the press apparatus. For example, a workpiece from a previous cycle is not properly removed and it is still in the tool of the lower tool unit. Or the counter-holder device does not deviate due to a malfunction of its drive device
  • the overload protection unit can be of very different design. It is preferably such that, in the event of an error, in particular the drives of the counter-holding device and / or the hold-down device are switched torqueless (Safe Torque Off), so that a drive device designed essentially as a sliding-crank drive can be pressed into its lower stretched position, so that the respective one Plunger part no critical hold-down or counter-holding forces are generated.
  • the drives of the counter-holding device and / or the hold-down device are switched torqueless (Safe Torque Off) so that a drive device designed essentially as a sliding-crank drive can be pressed into its lower stretched position, so that the respective one Plunger part no critical hold-down or counter-holding forces are generated.
  • a triggering of the actual overload safety unit can be made reliable when the press device comprises a control and / or regulating device, by means of which the overload protection unit in response to the bridging means can be triggered.
  • the overload protection unit can be addressed quickly and in a timely manner.
  • a first independent overload protection element can be provided, by means of which a mechanical overload of functional components on the press device can be avoided, even if it does not trigger the actual overload safety unit of the press device.
  • the reaction path also immediately provides an overload spring travel.
  • the first independent overload protection element can be arranged structurally simply close to a point at which overload forces structurally simple at least partially absorbed and compensated. This applies in particular to the pneumatic spring device.
  • precision cutting and forming presses meet in particular increasing quality requirements and increasing demands on minimum tolerances and especially the requirements, especially of suppliers in the automotive sector.
  • components with a higher level of smooth cutting can be produced.
  • the present press apparatus is particularly advantageous for users in the quality field of normal and precision cutting, as these users can significantly expand their production spectrum and produce parts with increased cutting quality.
  • the production costs can be reduced by manufacturing high-precision parts in progressive or transfer tools.
  • minimal post-processing requirements save time-consuming process steps and accordingly reduce handling costs.
  • the precision cutting and toggle presses with servo toggle drive for even greater system rigidity, enabling tight component tolerances and reliable repeatability accuracy, with different material thicknesses and strengths.
  • additional process steps can be upstream or downstream.
  • the precision cutting and forming presses with servo toggle drive during a press passage specifically allows cutting, pulling, embossing, punching and / or calibrating.
  • upstream or downstream processes such as thread forming, joining or welding can be integrated here.
  • the tappet profile can be optimally adapted to a forming and / or cutting process.
  • the use of retrofittable low- and counter-holder modules makes it possible to produce sectional parts with an increased proportion of smooth cuts. For the customer, this means an increase in flexibility, output and tool life.
  • manufacturing processes according to DIN 8580 are subdivided into six main groups, namely altering primary forms, forming, separating, joining, coating and material properties.
  • the separation is made by changing the shape of a solid body, whereby the cohesion is locally canceled completely.
  • the final shape is included in the starting form.
  • the decomposition of composite bodies is also assigned to the separation.
  • the main group separating in turn is further subdivided into cutting, cutting and ablation. Cutting or shearing is part of the subdivision. Precision cutting describes in the context of this work the production of cut parts with a cutting quality, which is to be classified between shear cutting and fine cutting.
  • a further subdivision is made on the basis of the cutting process, depending on the cutting surface to the workpiece boundary.
  • a cutting tool consists essentially of a cutting punch, a die or cutting plate and a hold-down.
  • the hold-down prevents bending and overflowing of the material.
  • the material to be cut of the workpiece can be pushed in the form of boards, as a band or as a strip between the punch and die and separated by downward movement of the cutting punch.
  • the breakthrough through the die is usually not cylindrical, but it is provided with a clearance angle.
  • the actual tool design depends on the requirements of the cut workpiece.
  • Shearing can be divided into five phases.
  • the hold-down device first applies to the sheet and a hold-down force F NH is built up.
  • the cutting punch is placed on the sheet, and there is an elastic deformation of the press device and tool. Due to the cutting gap, a bending moment arises in the sheet, which leads to a bending deformation. In the area of the cutting gap, an annular zone is formed. This is the contact area between the sheet surface and the cutting element.
  • the stamp penetrates into the sheet and it is plastically deformed.
  • the fluidity of the material is exhausted. It comes to a separation break and the remaining cross-section of the sheet breaks.
  • the cut slug into the die channel Due to the sudden demolition of the press device and especially the Upper tool unit or the press ram excited to vibrate.
  • the height of fracture surface and smooth cut is evaluated as a proportion of the sheet thickness s. Based on these proportions sheets of different thicknesses can be compared.
  • a high-quality cut part is characterized by a low edge indentation, a small fracture surface fraction and a small cutting burr with a high level of smooth cut and a fracture surface angle of 90 °.
  • the quality of the sectional image is mainly determined by the cutting gap u.
  • Counter cutting is also a two-step process.
  • a special feature of this method is the double presence of the tool active elements.
  • the sheet is cut from one side to just before the break occurs.
  • the workpiece is separated from the other side by the second tool.
  • burr-free and an improved smooth cut portion are achieved.
  • the last modified shear cutting method mentioned is normal cutting with a small cutting gap u ⁇ 0.05 x sheet thickness s.
  • fineblanking according to DIN 8580 belongs to the main group separating, to the subdivision division.
  • fineblanking involves modified process parameters, which lead to improved quality characteristics of the cut part.
  • Characteristic of the process are the tool design, the forces acting, the ring point and the cutting gap. With the placement of the blank holder ring prongs are pressed into the sheet.
  • a counter punch presses from below against the sheet. The compressive stresses generated thereby influence the separation process such that the smooth cut portion extends over the entire thickness of the sheet.
  • the hold-down acts as a scraper.
  • the counter punch acts as an ejector, which pushes the part up out of the die where the cutout is taken.
  • the forces for the ring point and counterholder are generated hydraulically.
  • the cutting force is generated mechanically for machines up to approx. 1,600 kN ( ⁇ 160 t) and hydraulically for larger machines from 2,500 kN to 14,000 kN.
  • the changed process parameters result in a different cutting force profile during fineblanking in contrast to Shearing.
  • the elastic phase and the cutting phase are identical, but the tear-off phase and the swing phase are missing, so there is no cutting hit.
  • the quality of the cut surface is determined by the cutting gap. While the cutting gap in normal shear cutting is between five and ten percent, this is about 0.5% of the sheet thickness s to be cut during fineblanking.
  • Pressing device 1 shown is a toggle press 2 and especially to a precision cutting and forming press 3 with a servo toggle lever drive 4. Since such a toggle lever drive 4 is known from the prior art, its components and operation will not continue here received.
  • the press device 1 has a welded press stand 5, on which on its upper side 6 the toggle lever drive 4 is arranged. Below the servo toggle lever drive 4, a press ram 7 is guided displaceably on the press stand 5 as an upper tool unit 8 in the vertical direction z (pressing direction or ejection direction).
  • the upper tool unit 8 carries as a tool part 9, for example, a cutting punch 10 (see FIGS. 2A to 2C ).
  • a press table 12 is arranged as a lower tool unit 13, by means of which the press stand 5 is fixed on a base foundation 14.
  • the lower tool unit 13 carries a further tool part 15, which in this embodiment a die 16 (see FIGS.
  • the press apparatus 1 additionally comprises an overload safety unit, not shown here, which then comes into action when a malfunction occurs during a machining operation in order to avert greater damage from the press apparatus 1.
  • the upper tool unit 8 comprises a hold-down device 20.
  • This hold-down device 20 has a plunger part 21 in the form of a hold-down 22.
  • the plunger part 21 is in this case displaceable by means of a drive device 23 with respect to the upper tool unit 8; in the direction z.
  • the lower tool unit 13 is equipped with a counter-holding device 24.
  • the counter-holding device 24 has a further plunger part 25 in the form of a counter-holder 26.
  • the further plunger part 25 is displaceable here by means of a further drive device 27 with respect to the lower tool unit 13; and also in the direction z.
  • the two separately acting and working drive means 23 and 27 are designed substantially identical except for their respective plunger member 21 and 25 and in this embodiment each comprise an eccentric drive 28 and 29, which is driven by a motor 30 and 31 respectively.
  • the press device 1 has bridging means 50 (see Figures 2 ) for bridging a response time for safe acceleration, in particular the further drive means 27 (see in particular Figures 2 ), wherein these bridging means 50 are preferably implemented directly in the hold-down device 20 and / or in the counter-holding device 24.
  • the further plunger part 25 can be accelerated solely by the movement of the plunger part 21, thus bypassing the further drive device 27.
  • the bridging means 50 are explained in more detail by way of example in connection with the counter holding device 24, wherein the reference numerals for clarity on the individual FIGS. 2A to 2D are arranged distributed.
  • the bridging means 50 are arranged between the further plunger part 25 and a connecting rod 51 of the drive device 27, wherein the bridging means 50 in this embodiment is designed as a pneumatic spring device 52 with a nitrogen spring 53.
  • the pneumatic spring device 52 has a cylinder housing 54 and a piston part 55 guided therein, wherein the cylinder housing 54 and the piston part 55 include a pressure chamber 57 filled with nitrogen N 2 as pressure medium 56.
  • the height 58 of the pressure chamber 57 is in this case selected such that the further plunger part 25 of the counter-holding device 24 can be displaced by approximately 25 mm in the direction z, bypassing the drive device 27.
  • a sufficiently large time window is available in order to accelerate the drive device 27 accordingly, before the further plunger part 25 is driven with it.
  • the additional plunger part 25 can be displaced downwards by at least 25 mm in the event of an emergency, without the piston part 55 or the drive device 27 having to be moved in this case. This time is gained until the actual overload protection unit can be activated.
  • the pneumatic spring device 52 as a whole provides a reaction path 59 of 25 mm.
  • This reaction path 59 is thus formed by means of the height 58 of the pressure chamber 57 between a piston head 60 of the piston part 55 and a cylinder housing end wall 61 of the cylinder housing 54.
  • the pressure chamber 57 and in particular the piston head 60 are located in a cavity 62 formed overall by the cylinder housing 54.
  • the cylinder housing 54 is displaceably guided in a guide bush 63 of the lower tool unit 13, independently of the piston part 55.
  • the entire cylinder housing 54 during a machining operation in the direction z down to the drive means 27 to be moved.
  • the piston part 55 does not have to displace correspondingly with the cylinder housing 54.
  • the cylinder housing 54 is displaceable relative to the lower tool unit 13 by means of the piston part 55, since the piston head 60 can interact with a shoulder region 64 of the cylinder housing 54 in such a way that the cylinder housing 54 is entrained by the piston part 55 when the piston part 55 moves downward in the direction z is moved to the ground foundation 14.
  • the plunger part 25 by web elements 65 (only exemplified here) spaced from the cylinder housing end wall 61, wherein the web elements 65 through holes 66 (here only exemplified) a top plate 67 of the lower tool unit 13 are performed.
  • the first phase of countering can be described as a "die cushion phase”. After the upper tool unit 8 has passed through its bottom dead center, then begins the second phase of ejection.
  • FIGS. 2A to 2D By way of example, four positions are shown using the example of the counter-holding device 24 during various operating states that are running correctly. The same mechanical conditions preferably also apply to the hold-down device 20.
  • the further plunger part 25 is located on the underside of the metal strip 19.
  • the further drive device 27 has been set such that the cylinder housing 54 has been moved toward the upper tool unit 8 in the direction z by means of the piston part 55.
  • the pressure medium 56 located in the pressure chamber 57 has been compressed such that the piston part 55 is displaced in the cavity 62 by 5 mm in the direction of the cylinder housing end wall 61, whereby the pressure chamber 57 is correspondingly reduced.
  • the upper edge of the cylinder housing 54 - and thus indirectly also the fixedly connected to the cylinder housing 54 counter-holder 26 - abuts against a stop 68.
  • the nitrogen spring 53 which at once designed a mechanical overload protection, this is thus feathered by 5 mm.
  • the pneumatic spring device 52 can serve as a "die cushion".
  • the further plunger part 25 is in its lowest position, from which it is moved by means of the drive means 27 again in the direction z on the upper tool unit 8.
  • the pressure medium 56 is compressed in the pressure chamber 57 again according to the manner described above and the cycle starts again from the beginning.
  • FIG. 3 is an example of the function of the drive means 23 and 25 simplified by means of a sliding crank drive 75 with r - radius of the crank 76 (eccentricity) [mm]; l - length of the connecting rod 51 [mm]; z - stroke of the plunger part 25 [mm]; ⁇ - angle of rotation of the crank 76 [°] and ⁇ - ratio between crank length and connecting rod length illustrated.
  • the speed can be calculated as follows.
  • v N r * ⁇ * sin ⁇ + ⁇ 2 * sin 2 ⁇ ⁇
  • Equation [3.10] describes only the required moment, which exerts the load on the drive.
  • the acceleration torque must also be taken into account.
  • the function of the counter-holding device 24 can be divided into two separate phases.
  • the first phase is the "die cushion phase” in which the counter-holding device 24 deviates from a defined position in synchronism with the movement of the upper tool unit 8 and serves as a counterholder for the tool part 9 or the workpiece 18.
  • the second phase is the "ejection phase”. Upon reaching the bottom dead center of the upper tool unit 8, the first phase is completed.
  • the counter-holder device 24 remains in the position reached until then until the defined starting angle (crank angle of the press device 1) is reached at the beginning of the ejection phase.
  • the direction of movement of the counter-holding device 24 is reversed.
  • the ejection phase is terminated at the latest when reaching the top dead center of the press device 1.
  • the movement of the counter-holding device 24 begins with the start of the press device 1 at top dead center.
  • the defined position, from which the counter-holding device 24 must be synchronous with the upper tool unit 8, describes the position of the plunger before the bottom dead center.
  • the upper tool unit 8 takes about 0.4 seconds to reach the position.
  • the counter-holding device 24 must have moved to a position of -5 mm.
  • a coordinate system 90 for example, functional characteristics are shown using the example of the further plunger part 25 or of the respective counter-holder 26 in connection with the plunger part 21 or the respective cutting punch 10.
  • the crank angle of the respective drive device 23 or 27 is plotted on the abscissa axis 91 of the coordinate system 90.
  • the path 93 of the counter-holder 26 on the one hand and the path 94 of the cutting punch 10 on the other hand are removed.
  • the counter-holder 26 is displaced into the position 95 by means of the further drive device 27 and subsequently raised by the pneumatic spring device 52 of the bridging means 50 by a further 5 mm and thereby pressed against the underside of the workpiece 18 (cf. FIG. 2A ). If the cutting punch 10 is then moved toward the workpiece 18 from above (cf. FIG. 2B ), the backstop 26 is already at the beginning 96 of the Cutting process to the speed of the cutting punch 10, bypassing the actual further drive means 27 synchronized, up to the time 97, at which the cutting punch 10 is moved back up. Subsequently, the counter-holder 26 can pass through a freely programmable ejector movement 98, wherein the counter-holder 26 in this case is driven by the further drive device 27.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Punching Or Piercing (AREA)
EP14163064.0A 2014-04-01 2014-04-01 Dispositif de presse destiné au traitement d'une pièce Withdrawn EP2926920A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP14163064.0A EP2926920A1 (fr) 2014-04-01 2014-04-01 Dispositif de presse destiné au traitement d'une pièce
TW103142573A TW201538308A (zh) 2014-04-01 2014-12-08 用於將工作物加工的壓製裝置
KR1020140190401A KR20150114379A (ko) 2014-04-01 2014-12-26 피가공재 가공용 프레스 장치
US14/611,492 US20150273779A1 (en) 2014-04-01 2015-02-02 Press for machining a workpiece
CN201510150641.XA CN104972684A (zh) 2014-04-01 2015-04-01 用于加工工件的冲压装置
JP2015075183A JP2015196195A (ja) 2014-04-01 2015-04-01 被加工材を加工するプレス装置

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EP3219429B1 (fr) * 2016-03-17 2019-07-31 TRUMPF Werkzeugmaschinen GmbH + Co. KG Machine-outil équipée d'un dispositif d'estampage et d'un dispositif d'usinage laser et procédé d'usinage de pièces à l'aide d'une telle machine-outil
AT519014B1 (de) * 2016-10-20 2018-03-15 Trumpf Maschinen Austria Gmbh & Co Kg Fertigungsanlage mit Manipulationsvorrichtung
EP3437848B1 (fr) * 2017-08-03 2024-03-20 Nienstedt GmbH Machine-outil
EP3831590A1 (fr) 2019-12-05 2021-06-09 Lapmaster Wolters GmbH Coulisseau de presse pour presse de découpage fin
CN112792249B (zh) * 2021-04-02 2021-06-22 浙江易锻精密机械有限公司 一种曲柄压力机过载保护系统
CN113478897B (zh) * 2021-06-22 2022-07-08 浙江斯特隆科技有限公司 一种压力机用内爆式过载保护装置及方法
CN116274617B (zh) * 2023-05-24 2023-12-12 湖南第一师范学院 一种计算机机箱加工用冲孔设备

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CN104972684A (zh) 2015-10-14
US20150273779A1 (en) 2015-10-01
KR20150114379A (ko) 2015-10-12
TW201538308A (zh) 2015-10-16

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