EP0592848B1 - Falzvorrichtung - Google Patents

Falzvorrichtung Download PDF

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Publication number
EP0592848B1
EP0592848B1 EP19930115381 EP93115381A EP0592848B1 EP 0592848 B1 EP0592848 B1 EP 0592848B1 EP 19930115381 EP19930115381 EP 19930115381 EP 93115381 A EP93115381 A EP 93115381A EP 0592848 B1 EP0592848 B1 EP 0592848B1
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EP
European Patent Office
Prior art keywords
sheet
subframe
toggle
flange
tool
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.)
Expired - Lifetime
Application number
EP19930115381
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English (en)
French (fr)
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EP0592848A1 (de
Inventor
Gerald A. Brown
William R. Hartley
Mark P. Jehmlich
Jeffrey S. Mcnamara
John C. Verzura
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Western Atlas Inc
Original Assignee
Western Atlas International Inc
Western Atlas Inc
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Publication of EP0592848A1 publication Critical patent/EP0592848A1/de
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Publication of EP0592848B1 publication Critical patent/EP0592848B1/de
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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
    • 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
    • B21D39/021—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 for panels, e.g. vehicle doors

Definitions

  • This invention relates to hemming sheet metal and more particularly to an apparatus for forming a hem on an edge of a sheet of a structural member such as a vehicle body panel.
  • Door, hood, and trunk deck lids of vehicles have been formed of one unitary outer skin of sheet metal joined around its periphery to a second inner reinforcing panel of sheet metal by hemming a generally upturned flange along each edge of the outer sheet over an adjacent edge of the inner panel.
  • This hemming has been accomplished in two separate stages.
  • the reinforcing panel Prior to performing the first stage, the reinforcing panel is nested within the outer panel fixtured on an anvil die on a base of a prehemming machine.
  • a tool of the machine commonly referred to as a hemming steel, engages and bends an edge of the outer panel to an acute included angle with respect to the outer panel.
  • both panels are released, transferred to and fixtured in a second hemming machine where a second tool completely bends the prehemmed edge of the outer panel over the peripheral edge of the reinforcing panel to secure and attach the panels together as a unitary structural member for assembly on a vehicle.
  • a plurality of both prehemming and final hemming machines are respectively grouped around the periphery of a panel to perform all prehemming and hemming operations for one assembly either sequentially or substantially simultaneously.
  • This type of hemming process and equipment has proven to be commercially successful and is still in widespread use.
  • this hemming process has disadvantages.
  • Such a two stage hemming process is costly and inefficient by requiring multiple components, namely a prehemming machine, a transfer mechanism and a final hemming machine to perform the entire hemming assembly operation.
  • a considerable amount of tooling and transfer equipment is required for this type of process, it consumes a great deal of valuable manufacturing floor space and it increases the likelihood of equipment malfunction which can undesirably delay production.
  • the process requires numerous steps to completely hem a single component. For example, the assembly must be fixtured, prehemmed, released, transferred, fixtured and final hemmed resulting in a low finished part production rate.
  • this two stage process requires a relatively larger sheet flange depth which increases component weight and cost.
  • This two stage process is also susceptible to quality control problems.
  • the panels may loosen from each other, become skewed with respect to each other, or not be properly located with respect to the final hemming station resulting in a finished hemmed assembly of lesser quality and poor structural integrity.
  • An assembly with these characteristics may have to be repaired or scrapped, thereby increasing production costs and lowering profits.
  • an ill-assembled structural member with these flaws if incorporated into an assembled vehicle may fit poorly and affect perceived quality by prospective purchasers, thereby reducing vehicle sales and profits.
  • An assembled defective structural member may further lose integrity as the vehicle is subjected to road vibration during use and possibly require replacement and negatively impact an owners' future vehicle purchasing decision.
  • Hemming machines have been designed which perform both the prehem and final hem operation in a single machine tool station which eliminates the need for a complex transfer mechanism. Hemming machines of this type vary in the kind of mechanism used and the manner of carrying out the hemming operations. Representative of these hemming machines are U.S. Patents: Kollar et al 3,191,414; E. R. St. Denis 3,276,409; Dacey Jr. 4,706,489; and Dacey Jr. 5,083,355.
  • the hemming machines embodied in the Kollar '414 and E. R. St. Denis '409 patents are of similar construction and operation. Both patents disclose a pair of fluid powered drives carried by a frame of the machine for driving a single hemming steel through both the prehem and final hemming stages. Each machine utilizes one drive to control the sideward motion of the hemming tool toward the anvil and sheet during the prehem operation and a second drive for downwardly moving the tool to clinch the flange in a hem overlapping the structural reinforcing panel.
  • a disadvantage of these single station prior art machines is that the hemming tool or steel continuously contacts the sheet edge during both stages of bending the flange which may produce undesirable distortion and highlighting in the sheet.
  • a further drawback is that failure to maintain precise actuation sequencing of the first and second drives during hemming may result in the outer panel being defectively hemmed to the reinforcing panel causing the costly scrapping of the assembly.
  • they have an abrupt motion of the hemming steel due to cam drives and high actuation forces.
  • the equipment to accurately sequence the actuation of each drive adds to the complexity of the machine, requiring additional costly maintenance while reducing reliability.
  • the sequencing complexity of this type of hemmer limits the number of assemblies which may be produced during a given period of time.
  • Dacey Jr. '489 discloses a hemming machine utilizing a single drive and hemming steel connected by a complicated system of linkages and a cam and follower arrangement to perform both the prehem and final hem operations.
  • Dacey Jr. '355 discloses a hemming machine having dual drives and a single hemming steel connected by a linkage and eccentric shaft arrangement to perform both the prehem and final hem operations.
  • the outer panel bends immediately adjacent the edge of the inner panel rather than at a predetermined desired break point which results in undesirable variations and inconsistencies from one panel assembly to another.
  • the drive and sequencing machanism is also complicated and requires frequent and costly production-delaying adjustment and is prone to unacceptable wear limiting the machines commercial usefulness.
  • Document WO-A-89/09101 discloses a press for hemming an edge of a sheet, comprising a frame; an anvil; a first subframe connected by a pair of first links to said frame for generally arcuate movement relative to said frame; a first hemming tool carried by the first subframe for bending a flange adjacent an edge of a sheet to a prehem position; a second subframe connected to said frame by a pair of second links for arcuate movement relative to the frame; a second hemming tool carried by said second subframe for bending the flange of the sheet from the prehem position to a hem position; and a drive operably connected with said first and second subframes.
  • the first hemming tool has a transverse movement while engaged with the sheet metal flange which produces significant wiping and scrubbing between them with the disadvantages of an inconsistent and variable break point of the bend in the panel, an inaccurate location of the edge of the bend, a scraping, scrubbing and scuffing of the flange portion, and a distortion and highlighting of the panel in the hem area which shows up when the panel is painted.
  • a press according to the invention is characterized by the features of claim 1.
  • Each steel is mounted on a separate carrier or subframe pivotally mounted by links in a main frame and each driven through separate toggle joints to produce the force for bending the sheet by the steels.
  • the pre-hem carrier is also eccentrically as well as pivotally mounted on the main frame.
  • the toggle joints are connected through rocker arms to the prime mover and the linkage provides a dwell in the movement of the prehemming steel so that it does not interfere with movement of the final hemming steel.
  • Objects, features and advantages of this invention are to provide a combined prehemming and hemming press which eliminates highlights, provides a consistent break point in the outer panel, produces a hem with improved tolerances, requires only one prime mover to drive both the prehemming and hemming steels, utilizes mechanical linkage to sequence and synchronize the movement of both steels, is of relatively simple design, compact construction and arrangement and is rugged, reliable, durable, of economical manufacture and assembly, has a long useful life in service and requires relatively little maintenance and repair in use.
  • Figs. 1-3 illustrate a hemming press 20 embodying this invention with a prehemming tool 22 and a hemming tool 24 for prehemming and final hemming an upright flange 26 along an edge 28 of a sheet metal panel 30.
  • the edge 28 to be hemmed is supported by an anvil 32 fixed to a main frame 34.
  • Each tool or steel 22 & 24 is received on a separate carrier or subframe 36 & 38 assembly mounted on the main frame 34.
  • Each steel 22 & 24 is driven by a seprate toggle linkage assembly 40 & 42 both of which are powered by a single prime mover 44, such as a fluid actuated cylinder assembly.
  • a single press 20 may be used to produce a finished hem along an edge of a single sheet or an edge of an outer panel of a nested assembly 46 of inner 48 and outer panels 50. However, frequently either two or four of these presses are arranged around the periphery of a sheet 30 or panel assembly 46 to either sequentially or simultaneously hem either two or four peripheral edges of the sheet 30 or assembly 46.
  • the main frame has two pairs of upright inner 52 and outer 54 or long and short upstanding support plates fixed at their lower ends to a base or a base plate (not shown).
  • the prehemming carrier 36 is mounted on the inner plates 52 and the final hemming carrier 34 is mounted on all of the plates.
  • the anvil 32 is also supported by all of the plates.
  • the prehemming steel 22 extends longitudinally the length of the flange to be hemmed 26 and, as shown in Fig. 1, has a horizontally projecting lip 58 with a downwardly and inwardly inclined face 60 which in use bears on the flange 26 to bend it over an adjacent portion of the sheet 30, usually to an acute included angle of about 35° to 55° and preferably about 45°.
  • the face 60 is inclined downwardly and inwardly at an angle of about 45° to the horizontal.
  • it is constructed so that its bottom edge bears on a shoulder 62 in the anvil 32 when the steel 22 is fully advanced by the press 20.
  • the steel 22 is secured by cap screws 64 to a mounting plate 66 of the carrier or subframe assembly 36.
  • the mounting plate 66 is fixed such by welding to a pair of spaced apart and parallel side plates 68.
  • the carrier 36 is pivotally mounted on the main frame 34 for movement in a generally arcuate path by a pair of torque tubes 70,72 journalled for rotation by bearings 73 received in the side plates 68 and eccentrically mounted for pivotal movement on the main frame 34.
  • Each tube 70,72 is eccentrically mounted by stub shafts 74 journalled in bearings carried by the inner support plates 52 of the main frame. So that the torque tubes 70,72 can be rotated in unison to advance and retract the carrier 36 and steel 22, a pair of spaced apart arms 76,78 are fixed to each tube and connected by a link 80 and pivot pins 82 received in the arms.
  • each stub shaft 74 of the tubes 70,72 is in the lower right hand quadrant of the tube when the prehemming steel 22 and carrier 36 is in the fully retracted or raised position.
  • the carrier 36 and steel 22 are driven through a toggle joint assembly 40 which provides a mechanical advantage multiplying the force applied to the flange 26 of the sheet 30 as the steel 22 approaches its fully advanced position.
  • the toggle assembly 40 has a pair of spaced apart arms 84 fixed to a shaft 86 journalled for rotation on the upright inner plates 52 of the frame 34 and pivotally connected by a pin 88 to one end of a link 90, the other end of which is received between and pivotally connected by a pin 92 to one end of a pair of arms 94 fixed to the lower torque tube 70.
  • the toggle joint 40 is powered by a drive assembly 44 having a single fluid, preferably air, actuated cylinder 96 connected through linkage to the toggle joint 40.
  • a piston rod 98 of the cylinder is connected by a clevis 100 and pin 102 to one end of an arm 104 fixed to a drive torque tube 106 journalled for rotation by a pair of stub shaft and bearing assemblies 108 mounted on the outer plates 54 of the main frame 34.
  • the toggle joint 40 is operably connected with the torque tube 106 through an arm 110 which is fixed at one end to the torque tube 106 and at the other end pivotally connected by a pin 112 to one end of a link 114, the other end of which is pivotally connected by a pin 116 to one end of the pair of arms 84 fixed to the shaft 86 of the toggle joint assembly 40.
  • the housing of the cylinder 96 is pivotally mounted on the inner plates 46 of the main frame 34 by stub shaft and bearing assemblies 118 and a yoke 120 secured to the housing.
  • the prehemming steel 22 dwells in its retracted position while the hemming steel 24 is in its extended position, as shown in Fig. 1.
  • This dwell is provided by the arcuate or circumferential location of the arm 110 on the torque tube 106 relative to the toggle assembly 40 when the piston rod 98 of the cylinder 96 is fully extended.
  • the final hemming steel 24 extends longitudinally the full length of the flange 26 to be hemmed and has a preferably slightly arcuate bottom face 122 which bears on the prehemmed flange 26 and bends it to the final fully hemmed position (Fig. 10), as the steel 24 is fully advanced by the press 20.
  • the steel 24 is removably received on a spacer plate 126 which is secured to a mounting plate 128 of the carrier assembly 38.
  • the mounting plate 128 of the carrier assembly 38 is fixed to the upper end of the carrier or subframe assembly.
  • the carrier 38 has a pair of spaced apart and parallel side plates 130 fixed by welds to spacer plates 132 disposed on their front edges.
  • the carrier is pivotally mounted on the main frame for generally arcuate movement by four link assemblies 134.
  • Each link assembly has a pair of spaced apart arms 136 pivotally connected adjacent one end by a pin 138 to one of the carrier side plates 130 and fixed adjacent the other end to a bushing 140 journalled on a pin and bearing assembly 142 mounted on each pair of inner 52 and outer 54 plates of the main frame 34.
  • Each toggle assembly 42 has an arm 146 fixed at one end to the main drive tube 106 and adjacent the other end pivotally connected by a pin and bearing assembly 148 to one end of a pair of toggle links 150, the other ends of which are pivotally connected by a pin and bearing assembly 152 to one of the side plates 130 of the carrier assembly.
  • the prehemming operation is initiated by energizing the cylinder 96 to advance its piston rod 98.
  • the hemming tool 22 and carrier 36 are moved downwardly in a generally arcuate path to bear on and bend the flange 26 from the position shown in Fig. 5 to that shown in Fig. 7 by movement of the drive linkage and toggle 40 from the position shown schematically in solid line Fig. 4 to that shown in Fig. 6.
  • the toggle joint 40 moves to its mid point position (Fig. 6), it provides the maximum multiplication of the force produced by the cylinder 96 and applied to the steel 22 as the steel approaches its fully extended position to complete the prehemming bend of the flange 26.
  • the curve of the generally arcuate movement of the steel 22 is designed to substantially eliminate relative sliding motion between the flange 26 and the inclined face 60 of the tool 22 as it forces the flange 26 into its prehemmed position. This is accomplished by constructing and arranging the eccentric mounting of the carrier 36 to produce a path of movement of the steel 22 complementary to that of the flange 26 during bending about its desired break point.
  • the steel 22 is retracted by continuing advancement of the cylinder piston rod 98 which continues to rotate the arm 84 of the toggle joint 40 clockwise (from the position shown in Fig. 6) to the position shown in phantom in Fig. 4.
  • This movement of the toggle joint 40 rotates the carrier torque tubes 70,72 clockwise which raises and thereby retracts the carrier 36 and hence the steel 22 along the generally arcuate path to its fully raised or retracted position.
  • the carrier 38 and hence the final hemming steel 24 is also lowered or advanced in a generally arcuate path from the solid line to the phantom line positions shown in Fig. 8 to bear on the prehemmed flange 26 and bend it into the fully hemmed position, shown in Fig. 10, to form a return bend with the flange 26 overlying and firmly engaging an edge 154 of the inner panel 48.
  • the clockwise rotation of the drive tube 106 moves the toggle joints 146,150 from the solid line position to the phantom line position in which the toggle joints 146,150 approach their respective mid points m to thereby lower or advance the steel 24 to its fully extended position.
  • toggle joints 146,150 approach their mid point position m , they produce the greatest multiplication of the force produced by the cylinder 96 and applied to the steel 24 as the steel approaches its fully advanced position to complete the bend and force the flange 26 into firm engagement with the underlying edge 154 of the reinforcing panel 48 to complete the hem 156.
  • the steel 24 is retracted by actuating the cylinder 96 to move its piston rod 98 to the fully retracted position.
  • the prehemming steel 22 will be initially again moved to its advanced position and then retracted. However, since the hem 156 has already been completed, the prehemming steel 22 will not strike it when it is advanced.
  • a generally rectangular hood assembly may have an outer panel with upturned flanges along all four sides to be hemmed.
  • This panel assembly could be received on a fixture disposed between four hemming presses each positioned to hem one of the flanges of the hood panel assembly.
  • all four edges of the panel could be prehemmed and final hemmed simultaneoulsy.
  • one pair of generally opposed flanges can be prehemmed and hemmed simultaneously by two of the presses and thereafter the other opposed pair of flanges can be prehemmed and hemmed simultaneoulsy by the other two presses.
  • each press is operated simultaneoulsy or in a rapid sequence
  • a screw and servo motor 158 in lieu of a fluid acutated cylinder.
  • This servo motor and screw drive 158 provides a more accurate and precise control of the cycle of each press which facilitates synchronizing the cycle and operation of two or more presses.
  • Fig. 11 illustrates a suitable screw and servo motor prime mover 158 with a screw 160 journalled for rotation in a housing 162 and driven by a reversible servo motor 164 which is preferably a stepper motor.
  • the housing is pivotally mounted on the main frame 34 by a pair of stub shaft bearing assemblies 108 secured to the upright inner plates 52 of the frame 34.
  • a traveling nut 166 preferably with recirculating ball bearings, is received on the screw 160 and pivotally connected to a pair of arms 104 fixed to the main drive tube 106.
  • the use of a servo motor 164 also facilitates manual "jogging", by controlled stepping or manual cycling of a press for setup, maintenance and repair purposes, such as when installing, adjusting or changing the prehemming 22 and hemming steels 24.

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

Claims (13)

  1. Presse (20) zum Falzen einer Kante (28) eines Blechs (30), mit:
       einem Rahmen (34);
       einem durch den Rahmen (34) getragenen Amboß (32) zum Aufnehmen und Tragen der zu falzenden Kante (28) des Blechs (30);
       einem ersten Hilfsrahmen (36);
       einem Paar von ersten Schwingen (70, 72), die jeweils an einem ersten Punkt drehbar durch den Rahmen (34) gehalten werden und an einem von dem ersten Punkt entfernten zweiten Punkt schwenkbar mit dem ersten Hilfsrahmen (36) verbunden sind, zum im wesentlichen kreisförmigen Bewegen des ersten Hilfsrahmens (36) relativ zu dem Rahmen (34);
       einem durch den ersten Hilfsrahmen (36) getragenen ersten Falzwerkzeug (22) zum Biegen eines Flanschs (26) an der Kante (28) des Blechs (30) in eine Vorfalzstellung;
       einem zweiten Hilfsrahmen (38);
       einem Paar von zweiten Schwingen (136), die jeweils an einem dritten Punkt (142) schwenkbar durch den Rahmen gehalten und an einem von dem dritten Punkt beabstandeten vierten Punkt (138) schwenkbar mit dem zweiten Hilfsrahmen (38) verbunden sind, zum im wesentlichen kreisförmigen Bewegen des zweiten Hilfsrahmens (38) relativ zu dem Rahmen (34);
       einem durch den zweiten Hilfsrahmen (38) getragenen zweiten Falzwerkzeug (24) zum Biegen des Flanschs (26) des Blechs (30) aus der Vorfalzstellung in eine das Blech (30) überlappende Falzstellung mit Rückbiegung; und mit
       einem Antrieb (44), der zum Bewegen des ersten Falzwerkzeugs (22) zum Biegen des Flanschs (26) des Blechs (30) in die Vorfalzstellung mit dem ersten Hilfsrahmen (36) und zum Bewegen des zweiten Falzwerkzeugs (24) zum Biegen des Flanschs (26) in die Falzstellung mit dem zweiten Hilfsrahmen (38) verbunden ist;
    dadurch gekennzeichnet, daß
       die ersten Punkte des Paars von ersten Schwingen (70) auf einer ersten Geraden voneinander beabstandet sind, und daß die dritten Punkte des Paars von zweiten Schwingen (136) auf einer von der ersten Geraden beabstandeten und zu dieser im wesentlichen parallelen zweiten Geraden voneinander beabstandet sind;
       mindestens ein erster Kniehebel (40) mit dem ersten Hilfsrahmen (36) und dem Antrieb (44) verbunden ist und eine durch den ersten Rahmen (34) schwenkbar getragene erste Gelenkschwinge (84) aufweist, die mit dem Antrieb (44) verbunden ist, sowie eine zweite Gelenkschwinge (90), die an ihrem einen Ende an der ersten Gelenkschwinge (84) und an ihrem gegenüberliegendem Ende mit dem ersten Hilfsrahmen (36) schwenkbar verbunden ist, zum Zustellen des ersten Werkzeugs (22), wenn die erste (84) und die zweite (90) Gelenkschwinge sich einer Mittelstellung ihres Bewegungsbereichs annähern, in der die erste (84) und die zweite (90) Gelenkschwinge im wesentlichen längs zueinander ausgerichtet sind, und zum Vervielfachen der durch das erste Werkzeug (22) auf den Flansch (26) des Blechs (30) wirkenden Kraft, wenn die erste (84) und die zweite (90) Gelenkschwinge sich in der Nähe ihrer Mittelstellung befinden und im wesentlichen längs zueinander ausgerichtet sind, um das erste Werkzeug (22) vollständig auszufahren, und zum Zurückführen des ersten Werkzeugs (22) von dem Blech (30), wenn die erste (84) und die zweite (90) Gelenkschwinge von ihrer Mittelstellung wegbewegt werden;
       mindestens ein zweiter Kniehebel (42) mit dem zweiten Hilfsrahmen (38) und dem Antrieb (44) verbunden ist und eine dritte Gelenkschwinge (146) aufweist, die schwenkbar durch den Rahmen (34) gehalten und mit dem Antrieb (44) gekoppelt ist, sowie eine vierte Gelenkschwinge (150), die an ihrem einen Ende an der dritten Gelenkschwinge (146) und an ihrem anderen Ende mit dem zweiten Hilfsrahmen (38) schwenkbarverbunden ist, zum Zustellen des zweiten Werkzeugs (24), wenn die dritte (146) und die vierte (150) Gelenkschwinge sich einer Mittelstellung ihres Bewegungsbereichs annähert, in der die dritte (146) und die vierte (150) Gelenkschwinge im wesentlichen längs zueinander ausgerichtet sind, und zum Vervielfältigen einer durch das zweite Werkzeug (24) auf den Flansch (26) des Blechs (30) ausgeübten Kraft, wenn sich die dritte (146) und die vierte (150) Gelenkschwinge in der Nähe ihrer Mittelstellung befinden und im wesentlichen längs zueinander ausgerichtet sind, um das zweite Werkzeug (24) vollständig auszufahren, und zum Zurückführen des zweiten Werkzeugs (24) von dem Blech (30), wenn die dritte (146) und die vierte (150) Gelenkschwinge von ihrer Mittelstellung wegbewegt werden; und daß
       der erste und der zweite Kniehebel (40, 42) so aufgebaut und angeordnet sind, daß, wenn einer der Kniehebel in der Mittelstellung seines Bewegungsbereichs steht, der andere der Kniehebel im wesentlichen von der Mittelstellung des Bewegungsbereichs entfernt ist.
  2. Presse nach Anspruch 1, dadurch gekennzeichnet, daß das Paar von ersten Schwingen ein Paar von den ersten Hilfsrahmen (36) auf den Rahmen (34) beweglich tragenden Exzentern (70, 72) aufweist, zur im wesentlichen kreisförmigen Hin- und Herbewegung, sowie einen an einem der Exzenter (70) befestigten und mit dem ersten Kniehebel (40) verbundenen Arm (94) zum Verschwenken der Exzenter, um den ersten Hilfsrahmen (36) und das erste Falzwerkzeug (22) in einer im wesentlichen kreisförmigen Bewegung zu dem Amboß (32) und dem Flansch (26) des Blechs (30) zuzubewegen, um den Flansch (26) in die Vorfalzstellung zu biegen.
  3. Presse nach Anspruch 2, gekennzeichnet durch einen an jedem Exzenter (70, 72) befestigten zweiten Arm (76, 78) und eine Schwinge (80), deren eines Ende an einem der zweiten Arme (76, 78) und deren anderes Ende an dem anderen der zweiten Arme (76, 78) schwenkbar befestigt ist.
  4. Presse nach Anspruch 1, dadurch gekennzeichnet, daß das Paar von ersten Schwingen zwei voneinander beabstandete und den ersten Hilfsrahmen (36) auf dem Rahmen (34) tragende Exzenter (70, 72) aufweist, die mit dem ersten Kniehebel (40) verbunden sind, um gemeinsam zum Bewegen des ersten Hilfsrahmens (36) in einer in wesentlichen kreisförmigen Bewegung zu dem Amboß (32) und dem Flansch (26) des Blechs (30) verschwenkbar zu sein, um den Flansch (26) in die Vorfalzstellung zu biegen.
  5. Presse nach Anspruch 1, dadurch gekennzeichnet, daß das erste Falzwerkzeug (22) eine abgeschrägte Vorwärtsfläche (60) zum Berühren des Flanschs (26) des Blechs (30) aufweist, um den Flansch (26) in die Vorfalzstellung zu biegen.
  6. Presse nach Anspruch 1, dadurch gekennzeichnet, daß der Antrieb (44) eine durch den Rahmen (34) drehbar gelagerte Röhre (106) aufweist, sowie mindestens einen an der Röhre (106) befestigten Arm (110), eine Ausgleichsschwinge (114), deren eines Ende mit dem einen Arm (110) der Röhre (106) und deren anderes Ende mit der ersten Gelenkschwinge (84) des ersten Kniehebels (40) schwenkbar verbunden ist, um das erste Werkzeug (22) in einer von dem Amboß (32) entfernten Stellung zu halten, wenn die Ausgleichsschwinge (114) und der Arm (110) der Röhre (106) im wesentlichen längs zueinander ausgerichtet sind, während das zweite Werkzeug (24) zu dem Amboß (32) zugeführt ist und den Flansch (26) des Blechs (30) berührt, um den Flansch (26) aus der Vorfalzstellung in die Falzstellung zu biegen, in der der Flansch (26) eine Rückbiegung aufweist und das Blech (30) überlappt.
  7. Presse nach Anspruch 6, dadurch gekennzeichnet, daß ein an der Röhre (106) befestigter und am Umfang von dem an der Röhre (106) befestigten einen Arm (110) beabstandeter Stellhebel (104) vorgesehen ist, und daß der Antrieb (44) einen mit dem Stellhebel (104) der Röhre (106) verbundenen fluidbetätigten Zylinder (96) aufweist.
  8. Presse nach Anspruch 6, dadurch gekennzeichnet, daß ein Stellhebel (104) an der Röhre (106) befestigt und am Umfang von dem an der Röhre (106) befestigten einen Arm (110) beabstandet ist, und daß der Antrieb (44) eine mit dem Stellhebel (104) der Röhre (106) verbundene und durch einen Servomotor (164) angetriebene Schraube (160) aufweist.
  9. Presse nach Anspruch 1, dadurch gekennzeichnet, daß der Antrieb (44) eine mit einem Servomotor (164) verbundene Schraube (160) aufweist.
  10. Presse nach Anspruch 1, dadurch gekennzeichnet, daß der zweite Hilfsrahmen (38) ein Paar von voneinander beabstandeten und das zweite Falzwerkzeug (24) tragenden Tragplatten (130) aufweist und daß mindestens eine der Tragplatten (130) mit der vierten Gelenkschwinge (150) des zweiten Kniehebels (42) schwenkbar verbunden ist, um den zweiten Hilfsrahmen (38) und das zweite Falzwerkzeug (24) zum Biegen des Flanschs (26) des Blechs (30) aus der Vorfalzstellung in eine Endfalzstellung mit einer Rückbiegung zu bewegen, in der der Flansch (26) das Blech (30) überlappt.
  11. Presse nach Anspruch 1, dadurch gekennzeichnet, daß der zweite Hilfsrahmen (38) ein Paar von voneinander beabstandeten und das zweite Falzwerkzeug (24) tragenden Tragplatten (130) aufweist und daß der erste Kniehebei (42) mindestens zwei vierte Gelenkschwingen (150) aufweist, die jeweils mit einer der Tragplatten (130) schwenkbar verbunden sind, um den zweiten Hilfsrahmen (38) und das zweite Falzwerkzeug (24) zum Biegen des Flanschs (26) des Blechs (30) aus der Vorfalzstellung in eine Endfalzstellung mit Rückbiegung zu bewegen, in der der Flansch (26) das Blech (30) überlappt.
  12. Presse nach Anspruch 1, dadurch gekennzeichnet, daß der Antrieb (44) eine durch den Rahmen (34) drehbar gelagerte Röhre (106) aufweist und daß der zweite Kniehebel (42) mindestens zwei der dritten Gelenkschwingen (146) aufweist, die jeweils an der Röhre (106) zur gleichmäßigen Drehung mit der Röhre (106) befestigt sind.
  13. Presse nach Anspruch 12, dadurch gekennzeichnet, daß der Antrieb (44) einen an der Röhre (106) befestigten Stellhebel (104) und eine an dem Stellhebel (104) befestigte und durch einen Servomotor (164) angetriebene Schraube (160) aufweist.
EP19930115381 1992-10-14 1993-09-23 Falzvorrichtung Expired - Lifetime EP0592848B1 (de)

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US96095592A 1992-10-14 1992-10-14
US960955 1992-10-14

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EP0592848B1 true EP0592848B1 (de) 1996-06-12

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FR2735049B1 (fr) * 1995-06-09 1997-08-22 Peugeot Unite de presertissage et de sertissage du bord d'une tole
ES2154529B1 (es) * 1997-12-17 2001-10-16 Ingemat Sa Perfeccionamientos introducidos en los sistemas modulares de sobremesa para union por pestañado de piezas metalicas.
DE10108687C2 (de) * 2001-02-23 2003-02-27 Audi Ag Falzvorrichtung
CN108994187B (zh) * 2018-09-05 2023-09-15 上汽通用五菱汽车股份有限公司 一种内窗框包边方法及机构

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SE461194B (sv) * 1988-03-21 1990-01-22 Volvo Ab Bockningsanordning
US5005398A (en) * 1990-06-01 1991-04-09 Craftmation, Inc. Hemming machine
GB2259879B (en) * 1991-09-27 1994-03-23 D V Associates Limited Press

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ES2088206T3 (es) 1996-08-01
CA2089813A1 (en) 1994-04-15
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EP0592848A1 (de) 1994-04-20
MX9301209A (es) 1994-04-29
DE69303141T2 (de) 1997-01-30

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