Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
  • B21D22/02—Stamping using rigid devices or 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
  • 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
• • 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
  • B21D5/04—Bending sheet metal along straight lines, e.g. to form simple curves on brakes making use of clamping means on one side of the work
  • B21D5/042—With a rotational movement of the bending blade

Definitions

• the invention relates to a bending machine comprising a machine frame, an upper beam with an upper beam tool and a lower beam with a lower beam tool, the upper beam and the lower beam being movably mounted on the machine frame, and at least one drive for moving the upper beam tool and the lower beam tool around one work between the flat material lying between them.
• Bending machines of this type are known from the prior art.
• the drive is usually dimensioned in such a way that it can generate sufficiently large forces to hold a workpiece between the upper beam and the lower beam.
• the invention is therefore based on the object of improving a bending machine of the generic type in such a way that forces which are as large as possible and which act on the workpiece from the upper beam tool and lower beam tool can be achieved as cost-effectively as possible.
• This object is achieved according to the invention in a bending machine of the type described in the introduction in that the at least one drive has at least one traversing drive for generating an opening and closing movement of the upper cheek and lower cheek relative to one another and at least one power drive for generating a greater force than the traversing drive for reshaping the Workpiece arranged between the upper cheek die and the lower cheek die, and that the traversing drive stands still and is blocked during forming.
• shaping is to be understood to mean shaping a workpiece under the interaction of the upper beam tool and the lower beam tool.
• Such forming includes, for example, closing and compressing bends or envelopes, embossing beads or any other type of forming process in flat materials.
• the power drive can be designed particularly favorably if it is designed with a lower travel speed than the travel drive when generating a force to move the upper beam tool and the lower beam tool toward one another. In this way, in particular, the drive power for the power drive can be kept small in spite of the large force generated, and the fast traversing movements running over long travels can be shifted to the traction drive.
• the force that can be generated by the power drive exceeds the force that can be generated by the travel drive by a factor of at least two, better at least five, even better at least ten.
• An advantageous exemplary embodiment provides that the end of the upper cheek is arranged with at least one drive each comprising a traversing drive and a power drive.
• the drive unit effects a relative movement of the upper cheek to the lower cheek and thereby acts on the upper cheek and the lower cheek
• the drive unit only directly and directly on the upper cheek and the lower cheek must act.
• one of the cheeks, in particular the lower cheek is firmly connected to the machine frame.
• the drive unit also acts within the meaning of the invention only between the upper cheek and the lower cheek when the drive unit engages the machine frame, since this is firmly connected to one of the cheeks and thus also the drive unit between this cheek firmly connected to the machine frame and the movable cheek is connected.
• the traversing drive comprises a blocking device effective at standstill.
• This blocking device makes it possible to ensure that the traversing drive in any case does not perform any movement when it is at a standstill and that the entire force of the power drive can thus be effective.
• another advantageous solution provides that the traversing drive is blocked by self-locking when it is at a standstill.
• This solution has the advantage that the blocking device can be dispensed with or at least, if it is still present for safety reasons, can be designed such that it has to absorb lower forces.
• the traversing drive is designed as a spindle drive, comprising a threaded spindle and a spindle nut.
• an inexpensive solution provides that the spindle nut is driven by a self-locking gear.
• the power drive is designed as a hydraulic drive.
• the hydraulic drive comprises a plurality of piston surfaces acting in parallel.
• the hydraulic drive could be indirect, that is to say effective via an intermediate gear, but it is particularly expedient if the hydraulic drive is arranged in a direct-acting manner in the drive unit, that is to say the hydraulic drive brings about the relative movement of the upper beam and lower beam even without an intermediate gear.
• a hydraulic unit of the hydraulic drive is arranged on one of the cheeks.
• the power drive comprises a lever gear with a drive for it.
• the drive for the lever mechanism can be either a swivel drive or a linear drive. It is even conceivable to provide a pneumatically or hydraulically actuated cylinder as a linear drive.
• the bending machine according to the invention can be made simpler if a control is provided which uses either the traversing drive or the power drive, so that in particular the traversing drive does not have to work under conditions in which the greater force of the power drive is effective.
• the force that can be generated by the power drive can be controlled by the control so that the full force of the power drive can be used in a metered manner only in the respective corresponding machining operations.
• a particularly advantageous solution provides that the controller uses the power drive depending on the respective machining process.
• control finally uses the power drive when clamping the workpiece to bend it by means of a bending cheek, so that the power drive always has the final effect on the workpiece Power creates.
• control finally uses the power drive each time the workpiece is loaded by means of the upper beam tool and the lower beam tool for processing the workpiece, and thus the force that can be generated by the power drive can be used in any case for the processing.
• Figure 1 is a perspective front view of an inventive
• FIG. 2 shows a section along line 2-2 in FIG. 1;
• FIG. 3 shows a section along line 3-3 in Figure 1 in a first embodiment of a bending machine according to the invention
• Figure 4 is an enlarged view of area A in Figure 3;
• Figure 5 is a partial representation of a first example of a
• Figure 6 is an illustration similar to Figure 5 of a second example of a
• Figure 7 is a section similar to Figure 3 through a second embodiment of a bending machine according to the invention.
• Figure 8 is a section similar to Figure 3 through a third embodiment of a bending machine according to the invention.
• FIG. 1 An embodiment of a bending machine according to the invention, shown in FIG. 1, comprises a machine frame, designated as a whole by 10, with lateral stands 12 and 14, between which, as shown in FIG. 2, an upper beam 16 and a lower beam 18 extend.
• the lower beam 18 is fixedly connected to the stands 12 and 14, while the upper beam 16 can be moved relative to the lower beam 18.
• the upper cheek 16 carries an upper cheek tool 20 and the lower cheek 18 a lower cheek tool 22, between which a workpiece 24 made of flat material, for example made of sheet metal, can be clamped in such a way that a rag protruding from the upper cheek tool 20 and the lower cheek tool 22 from a through the lower beam tool 22 and the upper beam tool 20 definable plane 28 can be bent out.
• the bending machine is provided, for example, with a bending beam 30 which extends between the bending beam holders 32 arranged at the ends thereof and can be moved about a pivot axis 34 with these bending beam holders 32, the pivot axis 34 preferably being located above the clamping plane 28.
• the bending beam acts with a bending beam tool 36 on the flap 26 of the workpiece to be bent for bending, the entire bending beam 30 being pivotable about the pivot axis 34.
• the bending machine In order to move the upper beam 16 relative to the lower beam 18 in a direction of movement 40, so that the workpiece 24 is either acted upon by the upper beam 16 with the upper beam tool 20 and pressed against the lower beam 18 with the lower beam tool 22 or the workpiece 24 between that of the lower beam 18 lifted upper cheek 16 and the lower cheek 18 is freely movable, the bending machine according to the invention is provided with a drive which can be controlled by a control 42, comprising two drive units 46 and 48, each in end regions 52 and 54 of the Upper cheek 16 and the lower cheek 18 are arranged, and a relative movement between the upper cheek 16 and the lower cheek 18, in the example shown a lifting of the upper cheek 16 with the upper cheek tool 20 from the workpiece 24 resting on the lower cheek 18 with the lower cheek tool 22, or a loading of the latter Effect workpiece 24 with the upper beam tool 20 against the lower beam tool 22.
• a drive which can be controlled by a control 42, comprising two drive units 46 and 48, each in end regions 52 and 54 of the Upper cheek 16
• each of the drive units in this case the drive unit 46 shown, comprises a travel drive 56 and a power drive 58, both of which are directly coupled to one another, so that the drive unit 46 is mounted on a bearing element 62 acts, which is fixedly connected to the upper beam 16 and on the other hand acts on the lower beam 18 via a bearing element 64 fixedly connected to the lower beam 18.
• the drive unit 46 is constructed such that both the traversing drive 56 and the power drive 58 act either alternately or jointly on the bearing element 62 and on the bearing element 64, depending on how they are controlled by the controller 42.
• the traversing drive 56 comprises a threaded spindle 66 which is held non-rotatably and which extends with its longitudinal axis 68 transversely to the clamping plane 28 and thereby passes through a spindle nut 70 which in the direction of the longitudinal axis 68 of the threaded spindle 66 by two bearings 72 and 74 is held immovably, but rotatable about the longitudinal axis 68 in the bearing element 64 designed as a bearing housing.
• this is provided on the circumferential side with an external toothing 76, in which a worm 78 engages, so that the worm 78 and the external toothing 76 form a worm gear.
• the worm 78 can be driven by a common drive shaft 80 which extends between the two drive units 46 and 48 and in turn can be driven by a motor 84 via a reduction gear 82, so that the spindle nuts 70 of both drive units 46 and 48 are always synchronized with one another via the Motor 84 can be driven.
• the entire traversing drive 56 that is to say the entirety of threaded spindle 66, spindle nut 70, worm gear 76, 78, reduction gear 82 and motor 84, is designed in such a way that when the motor 84 is at a standstill, because of the self-locking, the threaded spindle 66 moves in the direction of its longitudinal axis 68 blocked.
• the threaded spindle 66 is fixedly connected at one end 88, preferably at the end 88 facing the upper cheek 16, to a piston rod 92 of a triple piston 94 which, as in FIGS. 3 and 4, has three in the direction a longitudinal axis 96 of the piston rod 92 comprises successively arranged annular piston surfaces 102, 104, 106, facing which cylinder chambers 112, 114, 116 are arranged in a cylinder housing 118, with the cylinder chambers 112, 114, 116 simultaneously being able to be supplied with hydraulic medium via a distribution channel 120 in the cylinder housing 118 is so that a large force can be generated by acting on the piston surfaces 102, 104, 106 with a small design of the power drive 58.
• the cylinder chambers 112, 114, 116 are supplied by a hydraulic unit 122, which is preferably arranged seated on the upper cheek 16 and can be controlled by the controller 42 in order to generate pressurized hydraulic medium for moving the piston 94 relative to the cylinder housing 118.
• the cylinder housing 118 in turn is seated on the bearing element 62 which is fixedly connected to the upper beam 16, namely on a side thereof facing away from the lower beam 18, so that exposure to the cylinder chambers 112, 114, 116 with hydraulic medium leads to the cylinder housing 118 on the bearing element 62 acts and this acts together with the upper beam 16 in the direction of the lower beam 18 and thus displaces the cylinder housing 118 relative to the piston rod 92 in the direction of the lower beam 18.
• a plate spring assembly 124 is provided on a side of the bearing element 62 opposite the cylinder housing 118, which is supported on the one hand on the bearing element 62 and on the other hand on a support ring 126, which at the same time represents a connection to the end 88 of the spindle 66.
• the plate spring assembly 124 causes the bearing element 62 together with the upper cheek 16 to move in the direction away from the lower cheek 18 when the cylinder chambers 112, 114, 116 are depressurized and the cylinder housing 118 thus moves against the piston 94 in the direction from the lower cheek 18 can move away.
• the plate spring assembly 124 is dimensioned such that the cylinder housing 118 is displaced in the direction away from the lower beam 18 up to a mechanical stop without pressurizing the cylinder chambers 112, 114, 116.
• the threaded spindle 66 is fixed in a rotationally fixed manner relative to the upper cheek 16 by frictional engagement via the prestressed disk spring assembly 124, which fixes the unit comprising the support ring 126, piston rod 92 and threaded spindle 66 in a rotationally fixed manner relative to the bearing 62.
• the force is sufficient, for example in many bending operations by means of the bending beam 30, to clamp the workpiece 24.
• the power drive 58 can be used, which is capable of generating a force which exceeds that of the traversing drive 56 by more than twice, more preferably five times, preferably more than ten times.
• the power drive 58 only allows speeds of relative movement between the upper beam 16 and the lower beam 18 in the range of a few millimeters per second or less.
• the much higher force that can be generated with the power drive 58 offers the advantage of also being able to use the bending machine, as shown in FIG. 5 or FIG. 6, to implement additional operations, for example reshaping the workpiece.
• the bending machine as shown in FIG. 5 or FIG. 6, to implement additional operations, for example reshaping the workpiece.
• the power drive 58 is always used with the traversing drive 56 at a standstill, none of which due to the force of the power drive 58 Reaction on the traversing drive 56 in such a way that it would also adjust, because - as already explained - the traversing drive 56 is designed to be self-locking.
• the traversing drive 56 in the drive unit 46 ′ is designed in the same way as in the first exemplary embodiment.
• the power drive 58 ' is not designed as a direct-acting hydraulic drive, but as a lever mechanism 130 with a long lever 132 and a short lever 134, starting from a common articulated connection point 136, the long lever 132 with a joint 138 with the upper cheek 16 is connected, while the short lever is connected via a joint 140 to a force transmission rod 142, which in turn is connected to the end 88 of the threaded spindle 66.
• the distance between the articulation points 138 and 140 can thus be varied and thus also generate a large force for moving the upper beam 16 relative to the lower beam 18.
• a linear drive 142 is provided for moving the articulation point 136, which can be, for example, a hydraulic drive, but alternatively also a spindle drive.
• the linear drive 142 is in turn also connected to the upper beam 16 via an articulation point 144 and can thus be moved with it.
• each of the drive units in this case comprises the drive unit 46 ", a power drive 58 which corresponds to that of the first embodiment, while the travel drive 56 'by a Hydraulic cylinder 150 is formed, which can be fed by a hydraulic unit 152 to move the upper beam 16 away from the lower beam 18 up and down.
• the hydraulic cylinder 150 In order to be able to use the power drive 58 when the hydraulic cylinder 150 is at a standstill, the hydraulic cylinder 150 must also be able to absorb the forces applied by the power drive 58. Since this can only be implemented with problems with the hydraulic cylinder 150, the traversing drive 56 ′ is provided with a blocking device 154.
• this comprises a toothed rod 158 arranged as an extension of a piston rod 156 of the hydraulic cylinder 150 and two holding jaws 162 and 164 which are toothed on the front and are arranged in a housing 160 penetrated by the toothed rod 158 and which are connected via pressure chambers 166 and 168 in the direction of the toothed rod 158 or can be moved away from it, the holding jaws 162 and 164 engaging in a positive manner in the state in which the toothed rod 158 is loaded.
• the hydraulic unit 152 is preferably operated in such a way that it always inevitably activates the blocking device 154 when the hydraulic cylinder 150 is at a standstill and thus the traversing drive 56 'is automatically blocked against movement when the hydraulic cylinder 150 is at a standstill, so that the traversing drive 56' is always at a standstill Is able to absorb the forces possibly generated by the power drive 58.
• the operation of the traversing drives 56, 56 'and of the power drives 58, 58' can be carried out in the same way as in the first exemplary embodiment by means of the controller 42, so that in this respect reference is made in full to the statements relating to the first exemplary embodiment ,

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Bending Of Plates, Rods, And Pipes (AREA)
• Shaping Of Tube Ends By Bending Or Straightening (AREA)
• Press Drives And Press Lines (AREA)
• Secondary Cells (AREA)
• Inorganic Insulating Materials (AREA)
• Crystals, And After-Treatments Of Crystals (AREA)

Applications Claiming Priority (3)

Publications (2)

Family

ID=31984321

Family Applications (1)

Country Status (9)

Families Citing this family (6)

Family Cites Families (16)

• 2002
  • 2002-09-26 DE DE10245778A patent/DE10245778A1/de not_active Ceased
• 2003
  • 2003-06-26 WO PCT/EP2003/006730 patent/WO2004033124A1/fr active IP Right Grant
  • 2003-06-26 DK DK03740347T patent/DK1545808T3/da active
  • 2003-06-26 AT AT03740347T patent/ATE361160T1/de active
  • 2003-06-26 JP JP2004542256A patent/JP2006500223A/ja active Pending
  • 2003-06-26 PT PT03740347T patent/PT1545808E/pt unknown
  • 2003-06-26 ES ES03740347T patent/ES2285142T3/es not_active Expired - Lifetime
  • 2003-06-26 DE DE50307192T patent/DE50307192D1/de not_active Expired - Lifetime
  • 2003-06-26 EP EP03740347A patent/EP1545808B1/fr not_active Expired - Lifetime
• 2005
  • 2005-03-24 US US11/088,590 patent/US7069762B2/en not_active Expired - Lifetime

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events