EP3025803B1 - Antriebsvorrichtung für eine Werkzeugmaschine sowie Werkzeugmaschine mit einer derartigen Antriebsvorrichtung - Google Patents

Antriebsvorrichtung für eine Werkzeugmaschine sowie Werkzeugmaschine mit einer derartigen Antriebsvorrichtung Download PDF

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Publication number
EP3025803B1
EP3025803B1 EP14194914.9A EP14194914A EP3025803B1 EP 3025803 B1 EP3025803 B1 EP 3025803B1 EP 14194914 A EP14194914 A EP 14194914A EP 3025803 B1 EP3025803 B1 EP 3025803B1
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EP
European Patent Office
Prior art keywords
drive
spindle
spindles
wedge gear
side wedge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP14194914.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3025803A1 (de
Inventor
Dennis Tränklein
Jörg Dr. Neupert
Kai Etzel
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 EP14194914.9A priority Critical patent/EP3025803B1/de
Priority to CN201510829619.8A priority patent/CN105618541B/zh
Priority to US14/952,085 priority patent/US9539633B2/en
Priority to JP2015230513A priority patent/JP6639202B2/ja
Priority to KR1020150166774A priority patent/KR101977439B1/ko
Publication of EP3025803A1 publication Critical patent/EP3025803A1/de
Application granted granted Critical
Publication of EP3025803B1 publication Critical patent/EP3025803B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • 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
    • B21D11/00—Bending not restricted to forms of material mentioned in only one of groups B21D5/00, B21D7/00, B21D9/00; Bending not provided for in groups B21D5/00 - B21D9/00; Twisting
    • B21D11/08—Bending by altering the thickness of part of the cross-section of the work
    • 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
    • B21D28/04—Centering the work; Positioning 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
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/02—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of sheet metal by folding, e.g. connecting edges of a sheet to form a cylinder
    • 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
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B21D5/0272—Deflection compensating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J5/00—Methods for forging, hammering, or pressing; Special equipment or accessories therefor
    • B21J5/02—Die forging; Trimming by making use of special dies ; Punching during forging
    • B21J5/022—Open die forging
    • 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
    • B30B1/40—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 wedge means

Definitions

  • the invention further relates to a machine tool, in particular for sheet metal processing, with a machining tool and with a drive device of the above type, by means of which the machining tool is movable.
  • the machine comprises a cross slide provided for supporting a work spindle with two mutually perpendicular slide units, a headstock movable along a machine bed, and a tool turret also movable along the machine bed.
  • To drive the carriage units of the cross slide spindle drives serve with two drive spindles.
  • the spindle and the tool turret are driven by a common spindle drive, which also includes two drive spindles.
  • the drive spindles of all drive spindle pairs run parallel to one another and without mutual offset in their longitudinal direction.
  • Spindle nuts resting on each other seated in pairs associated drive spindles are arranged in the longitudinal direction of the drive spindles each arranged at the same height.
  • a press tool is actuated by means of a wedge gear, comprising two drive-side gear wedges and two tool-side gear wedges.
  • the tool-side gear wedges store the press tool.
  • the drive-side gear wedges are each provided with a spindle nut designed as a spindle drive drive device.
  • the spindle nuts sit on a common drive spindle and each have a drive motor by means of which they can be moved together with the drive-side gear wedges along the drive spindle.
  • a trouble-free workpiece machining by the press tool and / or a high machining accuracy require a high positioning accuracy of the drive-side gear wedges and thus a high positioning accuracy of serving for moving the drive-side gear wedges drive device.
  • the object of the present invention is to provide a compactly constructed drive device.
  • a spindle drive with two drive spindles is provided as the drive device for a machining tool of a machine tool, on each of which a spindle nut movable in the longitudinal direction of the relevant drive spindle is seated.
  • Both drive spindles are stationary in the longitudinal direction and rotatable about a spindle axis by means of a drive.
  • a fixed bearing at one longitudinal end of each drive spindle assumes its support in the drive spindle longitudinal direction. Due to the rotary drive of the drive spindles which are stationary in the longitudinal direction, no drive motors that move along with the spindle nuts are required to produce the longitudinal movements of the spindle nuts. As a result, only relatively small masses are to be moved during longitudinal movements of the spindle nuts. A significant, caused by inertia of the spindle nuts impairment of the positioning accuracy of the spindle nuts in the longitudinal direction of the drive spindles does not occur.
  • both drive spindles have the same length and are identical in terms of their torsional stiffness as well as their axial rigidity.
  • the torsional rigidity of the drive spindles is decisive for the twisting of the drive spindles during operation.
  • the axial stiffness of the drive spindles determines their change in length under axial load. Axial forces can be exerted on the drive spindles, in particular via the spindle nuts. Both the twist and the change in length of the drive spindles under axial load are proportional to the length of the drive spindles.
  • the drive spindles of the drive device can also be identical in terms of their moment of inertia, ie with respect to the resistance they oppose to a change in their rotational movement state.
  • the moment of inertia of a fully cylindrical drive spindle is determined by its mass and its radius, the radius of a fully cylindrical drive spindle also influences its torsional rigidity (torsional rigidity) and its change in length under axial load (tensile rigidity).
  • the drive device according to the invention is characterized in that the spindle nuts lie in the transverse direction of the drive spindles at a small distance from each other, even can cover each other in the transverse direction of the drive spindles. This makes it possible to realize a space-saving design of the drive device according to the invention in the transverse direction of the drive spindles.
  • a uniform drive behavior of the drive spindles for the spindle nuts is also due to the fact that at the beginning of the simultaneous longitudinal movements of the spindle nuts, the distances of the mounted on the spindles spindle nuts of the fixed bearing of the respective associated drive spindle coincide with each other (claim 2).
  • the equidistance of the spindle nuts and the fixed bearings of the drive spindles during the longitudinal movements of the spindle nuts in the longitudinal direction of the drive spindles is maintained.
  • the fixed bearing of the drive spindles are arranged on one and the same side of the spindle nuts for this purpose.
  • the initial equidistance of the spindle nuts and the fixed bearing is maintained when the fixed bearings of the drive spindles are on opposite sides of the spindle nuts.
  • each comprising a drive spindle and a spindle nut spindle drives the drive device according to the invention must be designed such that the spindle nuts move in their longitudinal movements at an identical speed along the drive spindles.
  • the drive device according to the invention is provided on a machine tool, to which cooperate for generating movements of the machining tool, two drive-side wedge gear elements and two tool-side wedge gear elements together.
  • Each of the drive-side wedge gear elements is connected to one of the spindle nuts of the drive device, each of the tool-side wedge gear elements with the machining tool.
  • a drive device, the spindle nuts in a preferred embodiment of the invention by means of the drive spindles simultaneously and with opposite longitudinal movements are movable (claim 3) is used in the case of a preferred type of machine tool according to the invention, connected to the spindle nuts drive side wedge gear elements in opposite directions and thereby the machining tool on the tool side To drive wedge gear elements in the transverse direction of the drive spindles (claim 11). In a transverse movement generated in this way, the machining tool can in particular perform a power stroke.
  • a preferred application of the described in claim 4 embodiment of the inventive drive device results from claim 13.
  • the generated by the drive device according to claim 4 according to claim 4 simultaneous and rectified longitudinal movements of the spindle nuts are evidently used in claim 13 to the associated with the spindle nuts drive side wedge gear elements together with the Tool-side wedge gear elements and the associated tool machining tool of the machine tool to move in the longitudinal direction of the drive spindles.
  • Such longitudinal movements of the machining tool can be carried out in particular for its positioning relative to a workpiece to be machined and / or relative to a complementary machining tool.
  • the space-saving construction of the drive device according to the invention makes use of the machine tool according to the invention according to claim 12.
  • the drive-side wedge gear elements connected to the spindle nuts are spaced from each other at the beginning of their simultaneous longitudinal movements in the longitudinal direction of the drive spindles.
  • the drive-side wedge gear elements can be moved towards one another from their initial positions with simultaneous counter-rotating longitudinal movements without the drive-side wedge gear elements having to pass each other.
  • This in turn makes it possible to approach the drive-side wedge gear elements in the transverse direction of the drive spindles close to each other and even to arrange with mutual overlap in the transverse direction of the drive spindles.
  • the dimension of the wedge gear in the transverse direction of the drive spindles is relatively small. With mutual overlap of the drive-side wedge gear elements in the transverse direction of the drive spindles, moreover, it is possible to guide the two drive-side wedge gear elements in their simultaneous movements in the longitudinal direction of the drive spindles on a common longitudinal guide.
  • the bearing of the drive spindle of the trailing spindle nut according to the invention provided such, in particular arranged so that it can be passed by the leading spindle nut and / or by the leading drive-side wedge gear element in the direction of simultaneous and rectified longitudinal movements of the drive-side wedge gear elements and the spindle nuts.
  • the spindle nut and / or the drive-side wedge gear element which are moved along one of the drive spindles, pass another bearing point, for example a floating bearing, the other drive spindle.
  • the leading spindle nut can pass the bearing of the drive spindle of the trailing spindle nut, the drive spindle of the leading spindle nut in the direction of simultaneous and rectified longitudinal movements of the drive side wedge gear elements and the spindle nuts must extend beyond the end to be passed to the fixed bearing drive spindle of the trailing spindle nut. Since the two drive spindles are the same length, they are for this purpose according to the invention offset in their longitudinal direction against each other.
  • claim 5 provides a Erfindungsbauart, in which between each of the drive spindles and the associated drive motor, a drive train is provided with at least one drive element, via which the respective drive spindle can be driven by the associated drive motor. So that the drive spindles, regardless of the drive trains show a uniform drive behavior for the spindle nuts are the two drive trains identical at least in terms of their torsional stiffness.
  • a uniform axial stiffness of the drive trains is dispensable when the drive trains are supported towards the drive spindles, for example at the fixed bearings of the drive spindles in the axial direction such that changes in length of the drive trains do not affect the drive behavior of the drive spindles.
  • the drive trains are each arranged between the fixed bearing of the drive spindles and the associated drive motor.
  • a uniform torsional stiffness of the spindle extensions is realized in a further embodiment of the invention in a simple manner that the spindle extensions are the same length either with equal cross section or at different lengths have different sized cross-sections (claim 8).
  • a drive device with a spindle extension between at least one of the drive spindles and the associated drive motor (claim 6) is provided on the machine tool according to the invention according to claim 15.
  • the fixed bearing of the recessed in the direction of the simultaneous and rectified longitudinal movements of the drive-side wedge gear elements and the spindle nuts drive spindle can be passed from the leading in the direction mentioned spindle nut and / or from the leading in the direction mentioned drive-side wedge gear element.
  • the spindle extension provided for the recessed drive spindle ensures that sufficient free space is available between the end of the recessed drive spindle and the associated drive motor for receiving the spindle nut moved past the fixed bearing of the recessed drive spindle and / or for receiving the drive-side wedge-gear element connected to this spindle nut. It is conceivable that also in the direction of the simultaneous and rectified longitudinal movements of the drive-side wedge gear elements and the spindle nuts superior drive spindle is provided with a spindle extension. Under certain circumstances, this can be shorter than the spindle extension of the drive spindle recessed in the mentioned direction. If this is the case, the cross section of the longer spindle extension is dimensioned larger than the cross section of the shorter spindle extension (patent claim 8) to standardize the torsional stiffness of the spindle extensions of different length.
  • FIG. 1 has a machine tool designed as a punch press 1 an O-shaped machine frame 2 with horizontal frame legs 3, 4 and vertical frame legs 5, 6.
  • the machine frame 2 encloses a frame interior. 7
  • a punching die 8 is movably guided in the direction of a double arrow 9 on the lower horizontal frame leg 4. At its top, the punching die 8 forms a support for a in the FIGS. 1 and 3 indicated by dashed lines sheet 10. A in the example illustrated circular die opening of the punching die 8 is in FIG. 2 to recognize.
  • the sheet 10 can be perpendicular to the plane of FIG. 1 be moved or positioned.
  • the punch 11 is fixed with its remote from the punching die 8 end in a punch holder 12, which in turn is mounted on a double wedge 13 in the direction of a double arrow 14 rotationally adjustable.
  • the double wedge 13 is formed by two tool-side gear wedges 15, 16, which are the tool-side wedge gear elements of a wedge gear 17.
  • the wedge gear 17 comprises two drive-side gear wedges 18, 19.
  • the drive-side gear wedge 18 and the tool-side gear wedge 15 are associated with each other and form a first Keilgetriebeelement- or gear wedge pair.
  • a second KeilgeInstituteelement- or gear wedge pair includes the drive-side gear wedge 19 and the tool-side gear wedge 16.
  • Der Double wedge 13 with the tool-side gear wedges 15, 16 is suspended from the drive-side gear wedges 18, 19.
  • the drive-side gear wedge 18 along a line 20 relative to the tool-side gear wedge 15 and the drive-side gear wedge 19 along a line 21 relative to the tool-side gear wedge 16 are movable.
  • the spindle drive 22 comprises a first drive spindle 23 and a second drive spindle 24.
  • the first drive spindle 23 and the second drive spindle 24 extend parallel to each other along the upper horizontal frame leg 3 of the machine frame 2.
  • the second drive spindle 24 is covered by the first drive spindle 23.
  • a first spindle axis 25 of the first drive spindle 23 and a second spindle axis 26 of the second drive spindle 24 lie in one and the same horizontal plane.
  • first drive spindle 23 is rotatably mounted on the machine frame 2 about the first spindle axis 25.
  • a second fixed bearing 29 and a second floating bearing 30 rotatably support the second drive spindle 24 about the second spindle axis 26 on the machine frame 2.
  • the first drive spindle 23 and the second drive spindle 24 are structurally identical, in particular the same length. They have an identical torsional rigidity and an identical axial rigidity as well as an identical mass moment of inertia.
  • the first drive spindle 23 is drive-connected to a first drive motor 32.
  • the first drive train 31 comprises a first spindle extension 33 and a first clutch 34.
  • the first spindle extension 33 extends from the end of the first drive spindle 23 the first bearing 27, the first spindle extension 33 is rotatably connected to the first drive spindle 23 and also supported in the longitudinal direction of the first drive spindle 23 on the machine frame 2.
  • the first clutch 34 establishes the connection between the first spindle extension 33 and the motor shaft of the first drive motor 32.
  • a second drive train 35 between the second fixed bearing 29 and a second drive motor 36 comprises a second spindle extension 37 rotatably connected to the second fixed bearing 24 and supported on the machine frame 2 in the longitudinal direction of the second drive spindle 24 and a second clutch 38, to which a drive connection between the second spindle extension 37 and the motor shaft of the second drive motor 36 is made.
  • the first drive train 31 and the second drive train 35 have an identical torsional rigidity, wherein the torsional stiffness of the first drive train 31 from the torsional stiffness of the first spindle extension 33 and the first clutch 34 and the torsional stiffness of the second drive train 35 from the torsional stiffness of the second spindle extension 37 and the assemble second clutch 38.
  • first clutch 34 and the second clutch 38 are identical in terms of their torsional rigidity. The same must apply to the first spindle extension 33 and the second spindle extension 37, so that the entire first drive train 31 and the entire second drive train 35 coincide with each other in their torsional stiffnesses.
  • the longer first spindle extension 33 would have a smaller torsional stiffness than the shorter second spindle extension 37 for identical cross sections.
  • a second partial length 40 of the second spindle extension 37 is compared to the first part length 39 of the second spindle extension 37 and thus reduced cross-section compared to the first spindle extension 33.
  • the first drive motor 32 and the second drive motor 36 may be independently controlled.
  • the direction of rotation of the two drive motors 32, 36 is switchable.
  • a numerical machine control 41 for controlling the first drive motor 32 and the second drive motor 36 is a numerical machine control 41, which in FIG. 3 is indicated and controls all the essential functions of the punch press 1.
  • a first spindle nut 42 By means of the first drive spindle 23 driven by the first drive motor 32, a first spindle nut 42 can be moved in the longitudinal direction of the drive spindles 23, 24. Accordingly, a second spindle nut 43, which is seated on the second drive spindle 24, by means of the driven by the second drive motor 36 second drive spindle 24 in the longitudinal direction of the drive spindles 23, 24 movable.
  • the spindle drives formed by the first drive spindle 23 and the first spindle nut 42 on the one hand and the second drive spindle 24 and the second spindle nut 43 on the other hand are of identical construction.
  • the first spindle nut 42 and the second spindle nut 43 move at identical rotational speeds of the drive motors 32, 36 over identical path lengths along the first drive spindle 23 and the second drive spindle 24.
  • the first spindle nut 42 is connected to the drive-side gear wedge 18, the second spindle nut 43 to the drive-side gear wedge 19.
  • the drive-side gear wedges 18, 19 carry out the longitudinal movements of the spindle nuts 42, 43 in the longitudinal direction of the drive spindles 23, 24.
  • guide shoes 44 and the drive-side gear wedge 19 are guided with guide shoes 45 on guide rails 46, 47 of the machine frame 2, which accordingly form a common guide for the drive-side gear wedges 18, 19 in the longitudinal direction of the drive spindles 23, 24.
  • the punch press is shown in an operating state in which the punch 11 and the punching die 8 are in one of their end positions along the horizontal frame legs 3, 4 of the machine frame 2.
  • the first spindle nut 42 and the second spindle nut 43 are moved on the first drive spindle 23 and on the second drive spindle 24 in positions in which the distance of the first Spindle nut 42 (middle of the first spindle nut 42 in FIG. 2 dash-dotted lines indicated) of the first bearing 27 of the first drive spindle 23 coincides with the distance of the second spindle nut 43 (center of the second spindle nut 43 in FIG FIG. 2 dash-dotted lines indicated) of the second bearing 29 of the second drive spindle 24.
  • first spindle nut 42 and the second spindle nut 43 with a distance d are spaced from each other.
  • the distance d are also the first drive spindle 23 and the second drive spindle 24 and the first fixed bearing 27 and the second fixed bearing 29 in the longitudinal direction of the same length drive spindles 23, 24 offset from each other.
  • the punch 11 is to be lowered along a stroke axis 48 with a working stroke.
  • the first drive spindle 23 and the second drive spindle 24 are driven by means of the first drive motor 32 and the second drive motor 36 with rotational movements about the first spindle axis 25 and the second spindle axis 26.
  • the direction of rotation and the rotational speed of the first drive motor 32 and the first drive spindle 23 and the direction of rotation and the rotational speed of the second drive motor 36 and the second drive spindle 24 are selected such that the first spindle nut 42 and the second spindle nut 43 in the longitudinal direction of the drive spindles 23rd , 24 at the same time and with the same speed while moving in opposite directions to each other.
  • the drive-side gear key 18 move along the line 20 relative to the tool-side gear key 15 and the drive-side gear key 19 along the line 21 relative to the tool-side gear key 16.
  • the punch 11 via the wedge gear 17 from the position according to FIG. 1 along the lifting axis 48 moves down.
  • the punch 11 penetrates the sheet 10 and runs into the die opening of the punching die 8.
  • the described lowering movement of the punch 11 is performed as a linear linear movement along the lifting axis 48 and thus without a movement component in the longitudinal direction of the drive spindles 23, 24.
  • This kinematics of the punch 11 is conditioned by the fact that the drive spindles 23, 24 for the spindle nuts 42, 43 and over these also for the drive-side gear wedges 18, 19 show a uniform drive behavior.
  • the reason for this is on the one hand the fact that at the beginning of the simultaneous longitudinal movements of the spindle nuts 42, 43, the distance between the first spindle nut 42 and the first bearing 27 of the associated first drive spindle 23 and the distance of the second spindle nut 43 of the second fixed bearing 29 of the associated second drive spindle 24 are the same size.
  • the first drive spindle 23 and the second drive spindle 24 coincide with each other in terms of their torsional stiffness and their axial stiffness and also with respect to their moment of inertia.
  • the first drive train 31 of the first drive spindle 23 and the second drive train 35 of the second drive spindle 24 have an identical torsional rigidity.
  • the distance of the first spindle nut 42 from the first bearing 27 of the first drive spindle 23 and the distance of the second spindle nut 43 from the second bearing 29 of the second drive spindle 24 more and differ more from each other has no appreciable effect on the exact straightness of the lowering movement of the punch 11, since the path lengths over which the spindle nuts 42, 43 move in their opposite longitudinal movements, are only relatively short and thus even at the end of the opposite longitudinal movements the first spindle nut 42 and the second spindle nut 43, the distance between the first spindle nut 42 from the first bearing 27 of the first drive spindle 23 from the distance of the second spindle nut 43 from the second bearing 29 of the second drive spindle 24 only slightly different.
  • the punching stroke of the punch 11 is along the lifting axis 48 from its lowered position in the position according to FIG. 1 withdrawn.
  • the first spindle nut 42 and the second spindle nut 43 by means of the first drive motor 32 and the first drive spindle 23 and by means of the second drive motor 36 and the second drive spindle 24 with opposite and directed away longitudinal movements in the longitudinal direction of the drive spindles 23, 24 in the Positions according to FIGS. 1 and 2 moved back.
  • the return stroke of the punch 11 is carried out due to the special design of the spindle drive 22 as an exact linear movement along the lifting axis 48.
  • the punch press 1 is again in the operating state according to the FIGS. 1 and 2 ,
  • the punching die 8 is for this purpose by means of a not shown in detail and also controlled by the numerical control machine 41 positioning drive from the position according to the FIGS. 1 and 2 in the position according to FIG. 3 method.
  • the target position of the punching die 8 is stored in the numerical machine control 41.
  • the wedge gear 17 and the punch 11 are numerically controlled in a target position of the punching die 8 corresponding target position moves by means of the spindle drive 22.
  • the first drive motor 32 and the first drive spindle 23 and the second drive motor 36 and the second drive spindle 24 are operated such that the first spindle nut 42 and the second spindle nut 43 at the same time and at the same speed and with rectified longitudinal movements of their Starting positions according to Figures 1 and 2 in the longitudinal direction of the drive spindles 23, 24 move to their destination positions.
  • the rectified longitudinal movements of the first spindle nut 42 and the second spindle nut 43 are exactly synchronized.
  • the exact synchronization of the rectified longitudinal movements of the first spindle nut 42 and the second spindle nut 43 is of particular importance.
  • first spindle nut 42 and the second spindle nut 43 maintain their initial distance d until the end of their rectified longitudinal movements.
  • the first spindle nut 42 and the drive-side gear wedge 18 are still on the left side of the first fixed bearing 27 of the first drive spindle 23. From the first spindle nut 42 and the drive-side gear part 18 was passed the floating bearing 30 of the second drive spindle 24. Due to a corresponding arrangement and constructive Design of the first spindle nut 42, the drive-side gear wedge 18 and the movable bearing 30, the first spindle nut 42 and the drive-side gear wedge 18 can move past the movable bearing 30 without collision.
  • the second spindle nut 43 and the drive-side gear wedge 19 have in the course of the positioning movement of the wedge gear 17, the first fixed bearing 27 of the first drive spindle 23 in the direction of movement happens. This was due a corresponding arrangement and structural design of the second spindle nut 43 and the drive-side gear wedge 19 and also due to a corresponding arrangement and design of the first fixed bearing 27 of the first drive spindle 23 possible.
  • This free space is created by appropriate dimensioning of the first spindle extension 33 of the first drive train 31 provided between the first fixed bearing 27 and the first drive motor 32.
  • the second drive train 35 may, under the given circumstances, be shorter than the first drive train 31.
  • the second spindle extension 37 of the second drive train 35 is shortened with respect to the first spindle extension 33 of the first drive train 31.
  • the torsional stiffness of the first spindle extension 33 and the second spindle extension 37 are identical, the diameter reduction described above is provided on the second spindle extension 37.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Machine Tool Units (AREA)
  • Punching Or Piercing (AREA)
  • Press Drives And Press Lines (AREA)
EP14194914.9A 2014-11-26 2014-11-26 Antriebsvorrichtung für eine Werkzeugmaschine sowie Werkzeugmaschine mit einer derartigen Antriebsvorrichtung Active EP3025803B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP14194914.9A EP3025803B1 (de) 2014-11-26 2014-11-26 Antriebsvorrichtung für eine Werkzeugmaschine sowie Werkzeugmaschine mit einer derartigen Antriebsvorrichtung
CN201510829619.8A CN105618541B (zh) 2014-11-26 2015-11-25 用于机床的驱动系统以及具有这样的驱动系统的机床
US14/952,085 US9539633B2 (en) 2014-11-26 2015-11-25 Machine tool drive system
JP2015230513A JP6639202B2 (ja) 2014-11-26 2015-11-26 工作機械用の駆動装置並びに該駆動装置を備えた工作機械
KR1020150166774A KR101977439B1 (ko) 2014-11-26 2015-11-26 기계 공구용 구동 시스템 및 그러한 구동 시스템을 구비한 기계 공구

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14194914.9A EP3025803B1 (de) 2014-11-26 2014-11-26 Antriebsvorrichtung für eine Werkzeugmaschine sowie Werkzeugmaschine mit einer derartigen Antriebsvorrichtung

Publications (2)

Publication Number Publication Date
EP3025803A1 EP3025803A1 (de) 2016-06-01
EP3025803B1 true EP3025803B1 (de) 2018-05-30

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US (1) US9539633B2 (ko)
EP (1) EP3025803B1 (ko)
JP (1) JP6639202B2 (ko)
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KR20160063287A (ko) 2016-06-03
US20160144419A1 (en) 2016-05-26
JP6639202B2 (ja) 2020-02-05
JP2016097447A (ja) 2016-05-30
US9539633B2 (en) 2017-01-10
EP3025803A1 (de) 2016-06-01
KR101977439B1 (ko) 2019-05-10
CN105618541A (zh) 2016-06-01
CN105618541B (zh) 2019-05-28

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