EP1396295B1 - Machine de cintrage avec outils de cintrage disposés aux côtés opposés d'un support porte-outils - Google Patents

Machine de cintrage avec outils de cintrage disposés aux côtés opposés d'un support porte-outils Download PDF

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Publication number
EP1396295B1
EP1396295B1 EP20030005462 EP03005462A EP1396295B1 EP 1396295 B1 EP1396295 B1 EP 1396295B1 EP 20030005462 EP20030005462 EP 20030005462 EP 03005462 A EP03005462 A EP 03005462A EP 1396295 B1 EP1396295 B1 EP 1396295B1
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EP
European Patent Office
Prior art keywords
bending
workpiece
drive
slide rail
tool carrier
Prior art date
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Expired - Lifetime
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EP20030005462
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German (de)
English (en)
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EP1396295A1 (fr
Inventor
Frank Schmauder
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Trumpf Rohrtechnik GmbH and Co KG
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Trumpf Rohrtechnik GmbH and Co KG
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Priority claimed from EP02020012A external-priority patent/EP1396294A1/fr
Application filed by Trumpf Rohrtechnik GmbH and Co KG filed Critical Trumpf Rohrtechnik GmbH and Co KG
Priority to EP20030005462 priority Critical patent/EP1396295B1/fr
Priority to US10/798,105 priority patent/US7021102B2/en
Publication of EP1396295A1 publication Critical patent/EP1396295A1/fr
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    • 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
    • B21D7/00—Bending rods, profiles, or tubes
    • B21D7/02—Bending rods, profiles, or tubes over a stationary forming member; by use of a swinging forming member or abutment
    • B21D7/024—Bending rods, profiles, or tubes over a stationary forming member; by use of a swinging forming member or abutment by a swinging forming member

Definitions

  • the invention relates to a bending machine for bending rod and / or rod-like workpieces, in particular pipes, with a bending device comprising bending tools, of which at least one is provided on one side and at least one on the opposite side of a tool carrier, wherein a bending tool can be used on one side of the tool carrier to create a bend, while at the same time a bending tool on the opposite side of the tool carrier can not be used to create a bend, wherein the bending tools each have at least one bending die and at least one pressure piece in the form of a clamping jaw and the bending dies are arranged along a bending axis extending in the workpiece transverse direction, the clamping jaws provided on a swivel arm pivotable about the bending axis and for the transfer driven in a functional or in an inoperative position in the workpiece transverse direction are moved back and forth and a workpiece near functional position of at least one jaw of the bending tool used on one side of the tool carrier a non-functional
  • a generic bending machine is disclosed in DE-A-33 02 888.
  • This machine has a bending head for joint processing of two tubes.
  • the bending head is provided with two simultaneously usable rotary bending tools.
  • the clamping jaws of the two rotary bending tools are jointly by means of a single piston-cylinder unit in a functional or in an inoperative position transferred.
  • the slide rails of the two prior art rotary bending tools are moved by a single piston-cylinder unit together in the workpiece transverse direction between a workpiece near functional and a workpiece distant non-functional position back and forth.
  • a feed drive for moving the slide rails during pipe processing is accordingly not provided.
  • the slide rails of both bending tools are pulled back together by a common piston-cylinder unit to its original position.
  • the present invention has set itself the goal.
  • clamping jaws on both sides of the tool carrier for movement in the workpiece transverse direction are drivingly coupled together in the case of the invention. Accordingly, at least one clamping jaw is moved on the one jointly with at least one clamping jaw on the other side of the tool carrier in the workpiece transverse direction.
  • This drive concept makes it possible to use one and the same drive elements for moving clamping jaws, which occupy different positions on both sides of the tool carrier, namely on the one hand a functional and on the other hand an inoperative position.
  • This results in a structurally simple designed drive configuration regardless of the diversity of the jaws on both sides of the tool carrier assumed positions.
  • With the multiple use one and the same drive elements a small volume of the overall drive connected. This in turn makes it possible to accommodate the drive for the jaws in the immediate vicinity of the bending tools. This results in short drive trains with low masses.
  • a clamping jaw on a used bending tool is moved into its functional position in which it acts on the workpiece to be bent, then forcibly the associated jaw or clamps are moved on the opposite side of the tool carrier in the opposite direction and thus into an area which is that area , which is assigned to the relevant bending tool the workpiece, lying down and in which consequently no collisions with any kind of obstacles are to be feared.
  • the associated jaw or clamps are moved on the opposite side of the tool carrier in the opposite direction and thus into an area which is that area , which is assigned to the relevant bending tool the workpiece, lying down and in which consequently no collisions with any kind of obstacles are to be feared.
  • Claim 2 relates to the application of the inventive concept according to claim 1 on bending machines with slide rails. At least one slide rail on the side of the tool carrier opposite the used bending tool is in the non-functional position and thus seen in the workpiece transverse direction in a position in which, in particular, collisions with the associated bending die are excluded.
  • the Erfindungsbauart according to claim 3 combines the advantages of a driving coupling of jaws on both sides of the tool carrier and an opposite mobility of these jaws in the workpiece transverse direction with the advantages of driven in the workpiece longitudinal direction movable slide rails.
  • driven in the workpiece longitudinal direction movable slide rails for example, a unfavorable for the processing result relative movement of slide rail and workpiece can be reduced or completely avoided.
  • the slide rails drivingly coupled to each other in the workpiece longitudinal direction are rectilinearly movable on both sides of the tool carrier in the workpiece longitudinal direction (claim 5). In this way it is ensured that the mutually associated slide rails of the used and the unused bending tool seen in the workpiece longitudinal direction always occupy corresponding positions.
  • the respective slide rails are all located either in the advanced or in the retracted position. If the slide on the used bending tool in the workpiece longitudinal direction their withdrawn starting position, so the associated slide on the unused bending tool can not be in an advanced position in which they would block the workpiece to be executed pivoting movement of the bending arm to the bending axis.
  • Such bending machines have on both sides of the tool carrier bending tools or bending dies with different bending radii.
  • Each of these bending dies are assigned as further bending tool parts at least one clamping jaw and at least one slide rail.
  • the sliding rail of the used bending tool located in the functional position on the workpiece to be deformed is moved in the workpiece longitudinal direction during bending with the workpiece to be deformed.
  • this slide rail with at least one slide rail of an unused bending tool on the opposite side of the tool carrier.
  • the unused slide moves simultaneously with the slide located in the functional position in the workpiece longitudinal direction.
  • Both the slide rail of the used bending tool and the slide rail of the unused bending tool rush thereby the one or more associated ones Jaws to.
  • the jaws of the used bending tool and the clamping jaws of the unused bending tool are arranged on one and the same pivot arm and therefore, when bending the workpiece, collectively perform a pivotal movement about the bending axis. Due to the different bending radii on the both sides of the tool carrier arranged bending tools result in different radii of the arc in the working position clamping jaws described during workpiece machining arc around the bending axis.
  • the speed at which the sliding rail located in the functional position moves in the workpiece longitudinal direction is matched to the speed of the associated clamping jaw acting on the workpiece to be machined.
  • the slide follows the leading jaw, especially in the initial phase of the bending process with the smallest possible distance in the workpiece longitudinal direction.
  • the speed of the slide of the unused, forming a relatively small bending radius bending tool is consistent with the speed of the slide of the used, a larger bending radius forming bending tool. That is, even the slide rail of the bending tool with a smaller bending radius moves at a relatively high speed in the workpiece longitudinal direction. If the clamping jaw of the unused bending tool is arranged with a smaller bending radius near the associated bending die, then it moves in the case of the bending tool used by Benden bending process to the bending axis on a circular arc with a relatively small radius and thus over a relatively short arc length.
  • At least one common transverse drive motor is provided for driving coupling of jaws and / or slide rails, for movement in the workpiece transverse direction (claim 7).
  • a further preferred type of bending machines according to the invention for the drive coupling of moving in the workpiece longitudinal direction slides at least one common longitudinal drive motor.
  • spindle drives are just as suitable for driving clamping jaws and / or slide rails according to the invention as well as due to their positioning accuracy.
  • a particularly expedient form of floating support of the joint longitudinal drive motor results from claim 14.
  • the claims 12 and 13 relate to further preferred features of the longitudinal drive according to the invention for slide rails on both sides of the tool carrier.
  • a bending machine 1 for bending pipes has a machine frame 2, on the upper side of which a pipe feed carriage 3 is movable in the pipe longitudinal direction and which supports a bending device 5 on a front end face 4.
  • Attached to the tube feed carriage 3 is a collet 6 for fixing the distal end of the bending device 5 of pipes to be machined.
  • the tubes by means of the tube feed carriage 3 and the collet 6 relative to the bending device 5 both in the tube longitudinal direction translationally movable and rotatable about the tube axis.
  • the illustration of a pipe to be bent has been omitted in FIG. 1 for reasons of clarity.
  • the bending device 5 is rotatably mounted about a rotation axis 7 on a support arm 8.
  • the support arm 8 is in turn pivotable about a pivot axis 9 relative to the machine frame 2.
  • Bending tools 10, 11 are arranged on opposite sides of a tool carrier 12 of the bending device 5.
  • either the bending tool 10 or the bending tool 11 can be used for workpiece machining.
  • With the bending machine 1 can be generated either right or left bends accordingly. Deviating from the illustrated conditions, the use of multi-level bending tools is possible.
  • the bending tool 10 comprises, as usual, a bending die 13, a clamping jaw 14 and a slide rail 15.
  • a bending die 16, a clamping jaw 17 and a slide rail 18 are provided as parts of the bending tool 11.
  • the diameter of the bending die 13 and thus its bending radius exceeds the diameter and the bending radius of the bending die 16.
  • Both bending dies 13, 16 are rotatable about a common bending axis 19.
  • supports 23, 23 of the slide rails 15, 18 are translationally movable in the workpiece transverse direction.
  • the supports 22, 23 are shown in FIG.
  • the lines of mobility of the supports 22, 23 and thus the slide rails 15, 18 in the transverse direction of the pipe to be bent are illustrated in Figure 2 by the double arrow 24.
  • the slide rails 15, 18 are displaceable in the case of supports 22, 23 that are stationary in this direction.
  • a common transverse drive motor 26 which is an electric motor in the example shown. Due to its small construction volume, the transverse drive motor 26 can readily be accommodated in the part 21 of the tool carrier 12.
  • a pinion 28 which meshes with axially parallel pinions 29, 30.
  • With the pinion 29 is a spindle 31, with the pinion 30 is a spindle 32 rotatably connected.
  • the spindle 31 forms with a spindle nut 33, a spindle drive 34, the spindle 32 with a spindle nut 35, a spindle drive 36th
  • the spindle nut 33 is movably connected to the support 22 and the slide rail 15, the spindle nut 35 with the support 23 and the slide rail 18. In one of their directions of movement, ie in one of the directions of the double arrow 24, the spindle nuts 33, 35 via damping elements 39, 40 of damping devices 41, 42 to the support side Supported drivers 37, 38. This support takes place via slides 43, 44 of the damping devices 41, 42.
  • the spindle nuts 33, 35 are held at a gap 45 or with a gap 46 spaced apart from the support-side drivers 37, 38.
  • the slides 43, 44 are displaceable against an elastic restoring force exerted by the damping elements 39, 40 in the axial direction of the spindles 31, 32 and in the direction of the support-side drivers 37, 38.
  • the slide rail 15 assumes its functional position shown in FIG. 2, in which it supports the pipe to be machined in the usual manner in the radial direction during the bending operation, then the slide rail 18 on the opposite side of the tool carrier 12 becomes one of the pipe to be machined moved spaced position procedure.
  • the slide rail 18 is transferred in the workpiece transverse direction in their workpiece-near functional position.
  • the damping devices 41, 42 serve to protect the drive trains of the supports 22, 23 in the event of overload.
  • the support side driver 37 comes with his right in Figure 2 side to rest on the opposite him in its direction of the surface formed on the tool carrier 12 drive housing. If the transverse drive motor 26 continues to be operated and consequently the spindle nut 33 continues to move in the longitudinal direction of the spindle 31, then the gap 45 closes in front of the spindle nut 33 until the spindle nut 33 comes to rest on the side of the support-side driver 37 facing it 37 acts as an end stop for the spindle nut 33. The emergence of the spindle nut 33 on this end stop is damped by the damping device 41. The closing of the gap 45 by the spindle nut 33 is namely against the action of the damping element 39, which is to be compressed by the spindle nut 33 by displacing the slider 43.
  • the damping device 41 also assumes the function of an overload protection during movement of the support 23 or the slide rail 18 in the workpiece distant end position. Due to the drive-driven coupling of the spindle nuts 33, 35 is arranged with overload-related emergence of the movement with the support 23 and the slide rail 18 connected to the spindle nut 35 on its left in Figure 2 side and formed by a bearing 32 of the spindle end stop the gap 45th closed between the spindle nut 33 and the support-side driver 37.
  • the damping device 42 is used for overload protection both in the movement of the support 23 and the slide rail 18 in the right in Figure 2 end position as well as movement of the support 22 and the slide rail 15 in the left end position in Figure 2.
  • damping devices 41, 42 are also effective when the slide rails 15, 18 run into an obstacle in their movement from a workpiece distant non-functional in the workpiece near functional position undesirable in the workpiece transverse direction. If the slide rail 15 is blocked, then the damping device 41 responds. When blocking the slide rail 18, the damping device 42 comes into operation.
  • spindles 47, 48 by means of which the slide rails 15, 18 can be moved in the same direction in the workpiece longitudinal direction in the case of supports 22, 23 which are stationary in the workpiece longitudinal direction.
  • This longitudinal movement serves at the functional position in the workpiece transverse direction engaging slide rail 15, 18, for example, to avoid a relative movement between the slide rail 15, 18 and the workpiece to be bent during workpiece machining.
  • the drive-like coupling of the unused with the located in the functional position slide 15, 18 makes it possible to move the two slides 15, 18 with a simply configured drive, in particular with a single, joint longitudinal drive motor in the workpiece longitudinal direction.
  • the drive-like coupling of the slide rails 15, 18 in their movement in the workpiece longitudinal direction does not necessarily assume that - as shown in Figure 2 - the supports 22, 23 and slide rails 15, 18 are also coupled in the workpiece transverse direction drivingly or in opposite directions.
  • FIG. 3 shows a section through the swivel arm 20 with the clamping jaws 14, 17 guided thereon in the radial direction of the bending axis 19.
  • the clamping jaw 14 assumes its functional position in the workpiece transverse direction, in which it acts on the pipe to be bent (not shown) against the associated bending die 13.
  • the clamping jaw 17 is moved to a position in which it is relatively far from the associated bending die 16.
  • the clamping jaws 14, 17 are as well as the slide rails 15, 18 for driving in the workpiece transverse direction drivingly coupled and movable in opposite directions.
  • the drive provided for this purpose is configured in accordance with the transverse drive of the supports 22, 23 or slide rails 15, 18.
  • a common electric transverse drive motor 49 which drives the clamping jaw 14 via a spindle drive 50 with spindle 51 and spindle nut 52, the clamping jaw 14 and a spindle drive 53 with spindle 54 and spindle nut 55 in the workpiece transverse direction.
  • a damping device 57 with damping element 58 and slider 59 is provided between the spindle nut 52 and a clamping jaw cam 56 .
  • a damping device 60 with damping element 61 and slide 62 between the spindle nut 55 and a schisverbündenen with the clamping jaw 17 Spannbackenmit commentary 63 is effective.
  • Each of the damping devices 57, 60 forms, corresponding to the damping devices 41, 42, an overload protection during the movement of the clamping jaws 14, 17 perpendicular to the bending axis 19.
  • FIG. 4 shows the conditions on the front end face 4 of the machine frame 2 of the bending machine 1 in plan view.
  • the collet 6 for fixing the bending tool distal end to be machined pipes and the bending tool 10 with the tool parts described in detail above are to be seen in particular.
  • FIGS. 5a, 5b show diagrammatically the conditions actually realized on the bending machine 1 in the plan view of the bending device 5.
  • the bending tool 10 with the bending die 13, the clamping jaw 14 and the slide rail 15 is used for processing and is with solid lines, the bending tool 11 with the bending die 16, the clamping jaw 17 and the slide 18 remains unused and is shown in dashed lines.
  • the clamping jaw 14 on the bending die 13 and the slide rail 15 assume their functional positions. In these positions, the clamping jaw 14 and the slide rail 15 have been moved starting from a shifted in Figure 5a to the right non-functional position in the workpiece transverse direction. Connected with the movement of the clamping jaw 14 and the slide rail 15 in the functional position was an opposite movement of the clamping jaw 17 and the slide rail 18 of the bending tool 11 in the illustrated workpiece distant Außerfurimies ein.
  • the clamping jaw 14 acts on the tube to be deformed against the bending die 13.
  • the tube is consequently clamped between the bending die 13 and the clamping jaw 14.
  • the slide rail 15 bears against the workpiece and supports it against a movement directed to the right in FIG. 5a.
  • the swivel arm 20 with the clamping jaws 14, 17 is pivoted about the bending axis 19 in the usual way. This is accompanied by a rotational movement of the bending dies 13, 16 about the bending axis 19.
  • the tube clamped between the bending die 13 and the clamping jaw 14 is bent around the bending die 13.
  • the clamping jaw 14 moved about the bending axis 19 follows the slide rail 15 together with the undeformed part of the workpiece on a rectilinear trajectory in the workpiece longitudinal direction, i. in the downward direction of the double arrow 25.
  • the bending die 16 rotates jointly with the bending die 13 of the Biegewerkzeüges 10 to the bending axis 19.
  • the clamping jaw 17 of the bending tool 11 performs with the clamping jaw 14 of the bending tool 10 is a pivoting movement about the bending axis 19.
  • the slide rail 18 of the bending tool 11 moves due to the existing drive coupling in the same direction with the slide rail 15 in the workpiece longitudinal direction.
  • the speed of the slide rail 18 in the workpiece longitudinal direction corresponds to the speed of the slide rail 15.
  • the slide rail 15 of the clamping jaw 14 of the bending tool 10 in use to follow at a small distance.
  • FIG. 5b The conditions when the workpiece is bent by an angle ⁇ are shown in FIG. 5b.
  • the slide rail 15 of the bending tool. 10 is the associated jaw 14 still closely adjacent.
  • the reason for this is the fact that the clamping jaw 17 is moved with a larger radius about the bending axis 19 than the clamping jaw 14 and consequently a larger arc length travels than the clamping jaw 14, while at the same time the slide rails 15, 18 are moved at the same speed.
  • the positions of the clamping jaw 14 and the slide rail 15 in Figure 6a correspond to those positions which occupy these bending tool parts in Figure 5a.
  • the clamping jaw 17 and the slide rail 18 are in accordance with Figure 6a in the workpiece transverse direction but not in opposite directions to the jaw 14 and the Slide rail 15 moved into an extra function position in which the clamping jaw 17 would lie with respect to the bending axis 19 radially outside of the clamping jaw 14. Rather, the clamping jaw 17 and the slide rail 18 of the bending tool 11 are not in use in the workpiece transverse direction also in their functional positions.
  • Figures 7 to 12 show a bending device 105, which differs from the bending device 5 described above by the type of bending tools used. So are at one Tool carrier 112 of the bending device 105 as bending tools 110, 111 multi-level bending tools provided, each comprising two individual tools. Of the thus existing four individual tools four different bending radii are formed.
  • the bending tool 110 comprises bent bending dies 113, 164 arranged one above the other along a bending axis 119.
  • the bending tool 111 accordingly has bending dies 116, 165.
  • the bending dies 113, 164 are assigned as further tool parts clamping jaws 114, 166 and slide rails 115, 167.
  • the bending tool 111 comprises in addition to the bending dies 116, 165 clamping jaws 117, 168 and slide rails 118, 169.
  • By appropriate positioning relative to the machine frame 2 of the bending machine 1 can be either one of the bending dies 113, 116, 164, 165 with the respective associated bending tool parts for processing use a pipe, not shown for the sake of clarity.
  • the bending device 105 is in its operating state assigned to the beginning of a tube processing.
  • the bending die 113, the clamping jaw 114 and the slide rail 115 are used for the machining of the tube. Accordingly, the clamping jaw 114 moves into its working position in the workpiece transverse direction, and when it is taken in, it acts against the bending die 113.
  • the clamping jaw 166 With the clamping jaw 114, the clamping jaw 166 is connected in terms of movement. In a corresponding manner, the slide rails 115, 167 form a movement unit. As well as the jaw 114 and the slide rail 115 consequently also take the jaw 166 and the slide rail 167 a workpiece near position.
  • the clamping jaws 117, 168 of the bending tool 111 are correspondingly drivingly coupled to the slide rails 115, 167 of the bending tool 110 in the workpiece transverse direction in a workpiece distant position transferred.
  • transverse drive motors which are housed inside a pivot arm 120 and a stationary part 121 of the tool carrier 112 and corresponding in construction and operation the Querantriebsmotören 26, 49 of Figures 2 and 3 ,
  • the clamping jaw 114 and the slide rail 115 of the bending tool 110 is based on the conditions according to Figures 7, 8, the pivot arm 120 about the bending axis 119 in the position shown in Figures 9, 10 moves.
  • the clamped by means of the bending die 113 and the clamping jaw 114 tube is bent around the bending die 113.
  • the slide rail 115 supports the tube laterally.
  • the drive-like coupling of the slide rails 115, 167 on the one hand and the slide rails 118, 169 on the other hand is effected by means of a common longitudinal drive motor 171, which can be seen in detail in FIGS. 8 and 10 and which in the illustrated example is an electric motor.
  • the longitudinal drive motor 171 is mounted on the tool carrier 112 by means of a three-jointed arrangement 172.
  • the three-jointed arrangement 172 comprises a long rocker 173 and a short rocker 174.
  • the long rocker 173 is on the slide rail side about a pivot axis 175, the short rocker 174 is mounted on the slide rail side about a pivot axis 176.
  • a common hinge axis 177 of the long rocker 173 and the short rocker 174 is parallel to the pivot axes 175, 176 and coincides with the geometric axis of the motor shaft of the longitudinal drive motor 171 together.
  • a longitudinal feed gear 178 is provided between the slide rails 115, 167 and the longitudinal drive motor 171.
  • This comprises a spindle drive 179 and a belt drive 180.
  • the spindle drive 179 has a spindle nut 181 rotatably mounted on a support 122 for the slide rails 115, 167 and a gear spindle 182 cooperating therewith.
  • the axis of rotation of the spindle nut 181, the longitudinal axis of the gear spindle 182 and the pivot axis 175 of the long rocker 173 of the three-jointed arrangement 172 coincide with each other.
  • the spindle nut 181 attached thereto is movable in the workpiece transverse direction.
  • the gear spindle 182 of the spindle drive 179 is displaceably guided on the stationary part 121 of the tool carrier 112 with the slide rails 115, 167 in the workpiece longitudinal direction.
  • the spindle nut 181 To drive the gear spindle 182 and the slide rails 115 167 in the workpiece longitudinal direction, the spindle nut 181 to rotate about its axis.
  • the drive belt 183 in turn is driven by the longitudinal drive motor 171 and forms a geared connection between the longitudinal drive motor 171 and serving as slide rail side gear member spindle nut 181. With the long rocker 173 of the drive belt 183 pivotable about the pivot axis 175.
  • a longitudinal feed gear 184 in this case comprises a spindle drive 185 and a Belt drive 186.
  • a spindle nut 187 of the spindle drive 185 is mounted on a support 123 which is movable in the workpiece transverse direction and cooperates with a gear spindle 188 which is movable jointly with the slide rails 118, 169 in the workpiece longitudinal direction.
  • a drive belt 189 of the belt drive 186 forms a geared connection between the longitudinal drive motor 171 and the spindle drive 185 and is pivotable about the pivot axis 176 with the short rocker 174.
  • the spindle nut 187 forms a slide rail side transmission element.
  • the three-jointed structure of the bearing of the longitudinal drive motor 171 and the longitudinal feed gear, 178, 184 allows the slide rails 115, 167 on the one hand and the slide rails 118, 169 on the other hand, regardless of their Beweglichtkeit in the workpiece transverse direction by means of a single drive motor, namely by means of the common longitudinal drive motor 171, in the workpiece longitudinal direction to proceed.
  • a total of four drive motors on the flexures 5, 105 are sufficient to bend tubes of different bending radii and in opposite directions.
  • two transverse drive motors are required, one longitudinal drive motor and one swing motor.
  • the transverse drive motors serve for the opposite movement of the clamping jaws 14, 17 opposite the tool carriers 12, 112; 114, 166; 117, 168 as well as on the two sides of the tool holder 12, 112, provided slide rails 15, 18; 115, 167; 118, 169.
  • the longitudinal drive motor By means of the longitudinal drive motor, the slide rails 15, 18; 115, 167; 118, 169 rectified shifted in the workpiece longitudinal direction.
  • the pivot drive motor is used to execute the pivotal movement of the pivot arms 20, 120 about the bending axes 19, 119. All drive motors are available in a size that allows accommodation of the drive motors directly to the tool carriers 12, 112.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Claims (14)

  1. Machine de cintrage, pour cintrer des pièces d'oeuvre se présentant sous forme de barres et/ou de tiges, en particulier des tubes, avec un dispositif de cintrage (5, 105), comprenant des outils de cintrage (10, 11 ; 110, 111), dont au moins l'un est prévu sur un côté, et au moins l'un est prévu sur le côté opposé d'un porte-outil (12, 112), un outil de cintrage (10, 11; 110, 111), situé sur un côté du porte-outil (12, 112), étant utilisable pour réaliser un cintrage tandis que, simultanément, un outil de cintrage (10, 11 ; 110, 111), situé sur le côté opposé du porte-outil (12, 112), n'est pas utilisable pour produire un cintrage, les outils de cintrage (10, 11 ; 110, 111) présentant chacun au moins une matrice de cintrage (13, 16 ; 113, 164 ; 116, 165) ainsi qu'au moins une pièce de pressage ayant la forme d'une mâchoire de serrage (14, 17 ; 114, 166 ; 117, 168), et les matrices de cintrage (13, 16 ; 113, 164; 116, 165) étant disposées le long d'un axe de cintrage (19, 119) s'étendant dans la direction transversale de la pièce d'oeuvre, les mâchoires de serrage (14, 17 ; 114, 166 ; 117, 168) étant prévues sur un bras pivotant (20, 120) susceptible de pivoter autour d'un axe de cintrage (19, 119) et étant déplaçables, dans un sens et dans l'autre, de façon entraînée, dans la direction transversale de la pièce d'oeuvre, pour transfert en une position en fonction ou en une position hors fonction et, à une position en fonction, proche de la pièce d'oeuvre, d'au moins une mâchoire de serrage (14, 17 ; 114, 166 ; 117, 168) de l'outil de cintrage (10, 11 ; 110, 111) utilisé, sur un côté du porte-outil (12, 112), est susceptible d'être associée une position hors de fonction d'au moins une mâchoire de serrage (14, 17 ; 114, 166 ; 117, 168) de l'outil de cintrage (10, 11 ; 110, 111) non utilisé, située sur le côté opposé du porte-outil (12, 112), position dans laquelle la mâchoire de serrage (14, 17 ; 114, 166 ; 117, 168) concernée est rétractée par rapport à sa position en fonction, et où la pièce d'oeuvre est susceptible d'être enserrée sur l'outil de cintrage (10, 11 ; 110, 111) utilisé, entre la matrice de cintrage (13, 16 ; 113, 164 ; 116, 165) et au moins une mâchoire de serrage (14, 17; 114, 166 ; 117, 168) prenant sa position en fonction et sollicitant alors la pièce d'oeuvre contre la matrice de cintrage (13, 16 ; 113, 164 ; 116, 165) et étant susceptible d'être cintrée, à l'état enserré, avec pivotement du bras pivotant (20, 120), avec la ou les mâchoire(s) de serrage (14, 17 ; 114, 166 ; 117, 168) autour de la matrice de cintrage (13, 16 ; 113, 164 ; 116, 165), caractérisée en ce qu'au moins une mâchoire de serrage (14, 17 ; 114, 166 ; 117, 168), sur un côté, et au moins une mâchoire de serrage (14, 17 ; 114, 166 ; 117, 168), sur le côté opposé, du porte-outil (12, 112) sont couplées en entraînement, pour produire un déplacement en direction transversale de la pièce d'oeuvre, sachant que, avec le déplacement, effectué dans la direction transversale à la pièce d'oeuvre, pour le transfert de la ou des mâchoire(s) de serrage (14, 17 ; 114, 166 ; 117, 168), sur un premier côté du porte-outil (12, 112), à la position en fonction, la ou les mâchoire(s) de serrage (14, 17 ; 114, 166 ; 117, 168) associée(s), sur le côté opposé du porte-outil (12, 112), est (sont) déplaçable(s) en direction transversale à la pièce d'oeuvre, en sens inverse, à la position hors de fonction.
  2. Machine de cintrage selon la revendication 1, caractérisée en ce que les outils de cintrage (10, 11 ; 110, 111) présentent chacun au moins une pièce de pressage ayant la forme d'un rail de glissement (15, 18 ; 115, 167 ; 118, 169) et des rails de glissement (15, 18 ; 115, 167 ; 118, 169), associés les uns aux autres, étant prévus, dont au moins l'un est disposé sur un côté et au moins l'un est disposé sur l'autre côté du porte-outil (12, 112), déplaçables dans un sens et dans l'autre de façon entraînée en direction transversale par rapport à la pièce d'oeuvre et en sens inverse, et, en observant dans la direction longitudinale de la pièce d'oeuvre, sur le côté situé à l'écart du cintrage à réaliser, de mâchoires de serrage (14, 17 ; 114, 166 ; 117, 168) des outils de cintrage (10, 11 ; 110, 111) concernés, la pièce d'oeuvre, sur l'outil de cintrage (10, 11 ; 110, 111) utilisé, étant susceptible d'être cintrée autour de la matrice de cintrage (13, 16 ; 113, 164 ; 116, 165), sous l'effet d'une sollicitation agissant dans la direction transversale à la pièce d'oeuvre, à l'aide d'au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) prenant sa position en fonction, proche de la pièce d'oeuvre, et, lors du cintrage autour de la matrice de cintrage (13, 16 ; 113, 164 ; 116, 165), étant susceptible d'être soutenue en direction transversale à la pièce d'oeuvre, à l'aide d'au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) prenant sa position en fonction dans la direction transversale par rapport à la pièce d'oeuvre, au moins un rail de glissement (15, 18 ; 115, 167; 118, 169), sur un côté, et au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169), sur le côté opposé, du porte-outil (12, 112) étant couplés en entraînement, pour produire le déplacement dans la direction transversale à la pièce d'oeuvre, à une position en fonction d'au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) de l'outil de cintrage (10, 11 ; 110, 111) utilisé, sur un côté du porte-outil (12, 112), étant susceptible d'être associée une position hors de fonction d'au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) de l'outil de cintrage (10, 11 ; 110, 111) non utilisé, sur le côté opposé, du porte-outil (12, 112), position dans laquelle le rail de glissement (15, 18 ; 115, 167 ; 118, 169) concerné est rétracté par rapport à sa position en fonction, et où, avec le déplacement effectué en direction transversale à la pièce d'oeuvre, pour le transfert du ou de rail(s) de glissement (15, 18 ; 115, 167 ; 118, 169), sur un côté, du porte-outil (12, 112) à la position en fonction, le ou les rail(s) de glissement (15, 18 ; 115, 167 ; 118, 169) associé(s), sur le côté opposé du porte-outil (12, 112), est (sont) déplaçables dans la direction transversale à la pièce d'oeuvre, en sens inverse, pour passer à la position hors de fonction.
  3. Machine de cintrage selon la revendication 2, caractérisée en ce qu'au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169), prenant sa position en fonction en direction transversale à la pièce d'oeuvre, de l'outil de cintrage (10, 11; 110, 111) utilisé est déplaçable lors du cintrage de la pièce d'oeuvre, avec celle-ci, de façon entraînée, dans la direction longitudinale de la pièce d'oeuvre.
  4. Machine de cintrage selon la revendication 3, caractérisée en ce que, à au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) de l'outil de cintrage (10, 11; 110, 111) utilisé, déplaçable avec la pièce d'oeuvre dans cette direction longitudinale lors de la prise de sa position en fonction dans la direction transversale à la pièce d'oeuvre, est couplé eb entraînement au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) d'un outil de cintrage (10, 11 ; 110, 111) situé sur le côté opposé du porte-outil (12, 112), pour produire le déplacement dans la direction longitudinale de la pièce d'oeuvre.
  5. Machine de cintrage selon la revendication 4, caractérisée en ce que les rails de glissement (15, 18; 115, 167; 118, 169), couplés en entraînement ensemble pour produire le déplacement dans la direction longitudinale de la pièce d'oeuvre de part et d'autre du porte-outil (12, 112), sont déplaçables dans le même sens, dans la direction longitudinale de la pièce d'oeuvre.
  6. Machine de cintrage selon la revendication 5, caractérisée en ce que, sur l'un des côtés du porte-outil (12, 112) est prévu au moins un outil de cintrage (10, 11 ; 110, 111), avec une matrice de cintrage (13, 16 ; 113, 164 ; 116, 165) produisant un rayon de cintrage plus grand que celui de la matrice de cintrage (13, 16 ; 113, 164 ; 116, 165) d'au moins un outil de cintrage (10, 11 ; 110, 111) situé sur le côté opposé du porte-outil (12, 112).
  7. Machine de cintrage selon l'une des revendications précédentes, caractérisée en ce que, pour le couplage en entraînement de mâchoires de serrage (14, 17 ; 114, 166 ; 117, 168), ou de mâchoires de serrage (14, 17; 114, 166; 117, 168) et de rails de glissement (15, 18 ; 115, 167 ; 118, 169), de part et d'autre du porte-outil (12, 112), pour le déplacement dans la direction transversale à la pièce d'oeuvre, est prévu au moins un moteur d'entraînement transversal (26, 49) commun.
  8. Machine de cintrage selon l'une des revendications 4 à 7, caractérisée en ce que, pour le couplage en entraînement des rails de glissement (15, 18 ; 115, 167 ; 118, 169), de part et d'autre du porte-outil (12, 112), est prévu au moins un moteur d'entraînement longitudinal (171) commun, pour le déplacement dans la direction longitudinale de la pièce d'oeuvre.
  9. Machine de cintrage selon l'une des revendications précédentes, caractérisée en ce que des mâchoires de serrage (14, 17 ; 114, 166 ; 117, 168) associées entre elles, ou des mâchoires de serrage (14, 17; 114, 166 ; 117, 168) associées entre elles et des rails de glissement (15, 18 ; 115, 167; 118, 169) associés entre eux, de part et d'autre du porte-outil (12, 112), sont déplaçables en sens inverse, dans la direction transversale à la pièce d'oeuvre, au moyen d'éléments d'entraînement, susceptibles d'être entraînés en sens inverse et reliés cinématiquement entre eux, en ce que, pour les éléments d'entraînement sont prévues des butées de fin de course, agissant chacune dans leurs deux sens de déplacement, sur lesquelles viennent accoster les éléments d'entraînement, lors d'un ralentissement du déplacement, en particulier lors de la mise à l'arrêt de la ou des mâchoires de serrage (14, 17; 114, 166; 117, 168) associées entre elles, ou des mâchoires de serrage (14, 17 ; 114, 166 ; 117, 168) associées entre elles et des rails de glissement (15, 18 ; 115, 167 ; 118, 169) associés entre eux, et lors du déplacement, continué malgré cela, des éléments d'entraînement, et en ce que, entre chaque élément d'entraînement et l'une de ces butées de fin de course, est prévu un dispositif d'amortissement (41, 42 ; 57, 58), au moyen duquel l'accostage de l'élément d'entraînement sur la butée de fin de course est susceptible d'être amorti, sachant que des butées de fin de course, agissant dans une direction de déplacement coïncidente des éléments d'entraînement, sont amorties, et sachant que, lors de l'accostage d'un des éléments d'entraînement sur une butée de fin de course non amortie, chaque fois l'autre élément d'entraînement, déplacé en sens inverse, vient accoster sur la butée de fin de course agissant dans sa direction de déplacement et amortie au moyen du dispositif d'amortissement (41, 42 ; 57, 58), et les éléments d'entraînement déplacés en sens inverse étant reliés entre eux avec une fonction de transmission de l'amortissement.
  10. Machine de cintrage selon la revendication 9, caractérisée en ce que sont prévues, en tant qu'éléments d'entraînement en sens inverse, des broches (31, 32 ; 51, 54) et/ou des écrous à broches (33, 35 ; 52, 55) de transmissions à broches (34, 36 ; 50, 53), entraînant, en direction transversale par rapport à la pièce d'oeuvre, les mâchoires de serrage (14, 17 ; 114, 166 ; 117, 168), ou les mâchoires de serrage (14, 17 ; 114, 166; 117, 168) et les rails de glissement (15, 18 ; 115, 167 ; 118, 169).
  11. Machine de cintrage selon la revendication 8, caractérisée en ce qu'un moteur d'entraînement longitudinal (171) commun, pour le déplacement de rails de glissement (15, 18 ; 115, 167 ; 118, 169) couplés ensemble, en direction longitudinale de la pièce d'oeuvre, est relié en entraînement aux rails de glissement (15, 18 ; 115, 167 ; 118, 169) situés de part et d'autre du porte-outil (12, 112), chaque fois par l'intermédiaire d'une transmission d'avancement longitudinale (178, 184), qui comprend un élément de transmission (181, 187) situé côté rail de glissement, déplaçable sur le porte-outil (12, 112) dans la direction transversale à la pièce d'oeuvre et, entre cet élément de transmission et le moteur d'entraînement longitudinal (171), comprend une liaison de transmission (183, 189), et en ce que les liaisons de transmission (183, 189), entre le moteur d'entraînement longitudinal (171) et les éléments de transmission (181, 187) situés côté rail de glissement, de part et d'autre du porte-outil (12, 112), sont susceptibles de pivoter chacune, avec leur côté de moteur d'entraînement, conjointement avec le moteur d'entraînement longitudinal (171), autour de l'élément de transmission (181, 187) associé, situé du côté rail de glissement, et les liaisons de transmission (183, 189) sont reliées ensemble de façon articulée sur leurs côtés de moteur d'entraînement, l'axe d'articulation (177) commun des liaisons de transmission (183, 189), sur le côté du moteur d'entraînement, et les axes de pivotement (175, 176) des liaisons de transmission (183, 189), sur les éléments de transmission (181, 187) situés du côté rail de glissement, s'étendent parallèlement entre eux, dans la direction longitudinale de la pièce d'oeuvre.
  12. Machine de cintrage selon la revendication 11, caractérisée en ce que l'axe d'articulation (177) commun des liaisons de transmission (183, 189) est réalisé, du côté du moteur d'entraînement, par l'arbre du moteur d'entraînement longitudinal (171).
  13. Machine de cintrage selon la revendication 11 ou 12, caractérisée en ce qu'au moins une transmission d'avancement longitudinal (178, 184), entre un moteur d'entraînement longitudinal (171) commun et les rails de glissement (15, 18 ; 115, 167 ; 118, 169), comprend une transmission à broche (179, 185), avec des éléments de transmission à broche ayant la forme d'une broche de transmission (182, 188) s'étendant dans la direction longitudinale de l'outil, et un écrou à broche (181, 187) monté sur celle-ci, sachant qu'au moins un rail de glissement (15, 18 ; 115, 167 ; 118, 169) est déplaçable en direction longitudinale de la pièce d'oeuvre, de façon couplée à l'un des éléments de transmission par broche, et l'autre élément de transmission à broche constitue un élément de transmission situé côté rail de glissement, et en ce que, en tant que liaison de transmission entre le moteur d'entraînement longitudinal (171) commun et l'élément de transmission à broche formant l'élément de transmission situé du côté rail de glissement, est prévu un élément d'entraînement, en particulier une courroie d'entraînement (183, 189), susceptible d'être entraînée par le moteur d'entraînement longitudinal (171) commun et circulant sans fin, élément ou courroie au moyen duquel ou de laquelle l'élément de transmission par broche, formant l'élément de transmission de côté rail de glissement, est susceptible d'être entraînée autour de l'axe de la broche de transmission (182, 188).
  14. Machine de cintrage selon l'une des revendications 11 à 13, caractérisée en ce que les éléments de transmission situés côté rail de glissement sont prévus sur les deux côtés du porte-outil (12, 112), chaque fois sur un dispositif support déplaçable en direction transversale à la pièce d'oeuvre sur le porte-outil (12, 112), en ce qu'un balancier (173, 174) est monté à pivotement sur chacun des dispositifs support, le pivotement se faisant autour de l'axe de pivotement (175, 176) de la liaison de transmission (183, 189) concernée, et en ce que les balanciers (173, 174) sont reliés ensemble de façon articulée, à distance de leur montage en palier, sur les dispositifs support et servent de palier au moteur d'entraînement longitudinal (171) commun, sachant que l'axe d'articulation (177) commun des balanciers (173, 174) et leurs axes de pivotement (175, 176) s'étendent sur les dispositifs support, parallèlement entre eux, dans la direction longitudinale de la pièce d'oeuvre.
EP20030005462 2002-09-05 2003-03-15 Machine de cintrage avec outils de cintrage disposés aux côtés opposés d'un support porte-outils Expired - Lifetime EP1396295B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20030005462 EP1396295B1 (fr) 2002-09-05 2003-03-15 Machine de cintrage avec outils de cintrage disposés aux côtés opposés d'un support porte-outils
US10/798,105 US7021102B2 (en) 2003-03-15 2004-03-10 Bending machine with bending tools on opposite sides of a tool platen

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP02020012 2002-09-05
EP02020012A EP1396294A1 (fr) 2002-09-05 2002-09-05 Machine de cintrage avec outils de cintrage disposés aux côtés opposés d'un support porte-outils
EP20030005462 EP1396295B1 (fr) 2002-09-05 2003-03-15 Machine de cintrage avec outils de cintrage disposés aux côtés opposés d'un support porte-outils

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EP1396295B1 true EP1396295B1 (fr) 2006-06-21

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Cited By (1)

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US11440069B2 (en) 2013-11-15 2022-09-13 Greenlee Tools, Inc. Bender having a sensor configured to sense a workpiece

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DE102016101908B4 (de) * 2016-02-03 2017-11-02 Dengler Tubetec Gmbh Vorrichtung und Verfahren zum Biegen von Rohren
CN108405686B (zh) * 2018-03-26 2024-02-23 奥美森智能装备股份有限公司 折弯机的随动装置
CN115008727B (zh) * 2022-06-01 2024-01-26 宁波敏达智行汽车零部件有限公司 一种车辆密封条的加工设备

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JPS57193236A (en) * 1981-09-17 1982-11-27 Chiyoda Kogyo Kk Both right and left bending type bender
JPS591024A (ja) * 1982-06-26 1984-01-06 Chiyoda Kogyo Kk 二本同時曲げベンダ−
IT1251934B (it) * 1991-10-16 1995-05-27 Macchine Curvatubi Crippa Agos Macchina curvatubi polifunzionale
US6038903A (en) * 1998-03-09 2000-03-21 Eaton Leonard, Inc. Dual headed bending machine
US6192728B1 (en) * 2000-05-30 2001-02-27 Yin Lin Machine Industrial Co., Ltd Pipe bending machine accurately controlling bent angles of pipes
ES1049666Y (es) * 2001-06-15 2002-05-16 Talleres Enrique Tejero S L Maquina curvadora perfeccionada

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11440069B2 (en) 2013-11-15 2022-09-13 Greenlee Tools, Inc. Bender having a sensor configured to sense a workpiece

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