EP0160174B1 - Maschine zur Erzeugung von Schraubenfedern - Google Patents

Maschine zur Erzeugung von Schraubenfedern Download PDF

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Publication number
EP0160174B1
EP0160174B1 EP85102219A EP85102219A EP0160174B1 EP 0160174 B1 EP0160174 B1 EP 0160174B1 EP 85102219 A EP85102219 A EP 85102219A EP 85102219 A EP85102219 A EP 85102219A EP 0160174 B1 EP0160174 B1 EP 0160174B1
Authority
EP
European Patent Office
Prior art keywords
spring
bending
station
central member
coil spring
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
Application number
EP85102219A
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German (de)
English (en)
French (fr)
Other versions
EP0160174A3 (en
EP0160174A2 (de
Inventor
Ernst Zängerle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Spuehl AG
Original Assignee
Spuehl AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP0160174A2 publication Critical patent/EP0160174A2/de
Publication of EP0160174A3 publication Critical patent/EP0160174A3/de
Application granted granted Critical
Publication of EP0160174B1 publication Critical patent/EP0160174B1/de
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F35/00—Making springs from wire
    • B21F35/02—Bending or deforming ends of coil springs to special shape

Definitions

  • the invention relates to a machine for producing coil springs according to the preamble of patent claim 1.
  • Spring mattresses for beds and seating contain a number of double-conical coil springs, the ends of which are knotted in a known manner.
  • B. can consist of a twist of the spring end with the adjacent spring turn.
  • machines are customary which, starting from a wire supply, automatically wind the springs, knot their two ends with the respectively adjacent spring winding and eject the finished springs into a stacking channel in order to feed them from there to an assembly machine.
  • the invention is based on such prior art as is known from DE-C-1 073 995, which goes back to the same applicant.
  • the machine known there forms the end turns of the helical spring into a round cross section and fixes the respective end of the helical spring in such a way that the end of the spring is twisted with the adjacent spring turn.
  • US-A-2 581 686 discloses a spring core in which the free ends of the coil springs are interlocked with the end turns of the adjacent coil springs. This spring core is not suitable for automatic production, because the interlocking of the coil springs is difficult to achieve.
  • the coil springs are connected to one another along straight, comparatively long side areas.
  • the manufacture of such coil springs is relatively complex and requires a lot of wire.
  • the invention has for its object to develop a machine of the type mentioned so that coil springs can be quickly made without knotting the end turns, and that the end turns are U-shaped.
  • a feature of the present invention is that the knotting devices known from DE-C-1 073 995 are replaced by bending stations which bend the end turns of the respective helical spring approximately in a U-shape and provide a number of mutually spaced bending points.
  • An approximately U-shaped end turn is now bent from the end turn, which was previously round, which has the advantage that the end turn offers a larger contact surface in the direction of the upholstery and is better able to absorb the forces acting at an angle to the spring axis.
  • the attachment of bending points in the area of the end turns of the coil spring has the further advantage that with the aid of these bending points the coil spring can be positioned (aligned) very precisely in a mounting channel, which means that the speed of a spring mounting machine connected thereafter can be increased significantly and the Accuracy in the composition of the innerspring can be improved.
  • two opposite spring bending stations are provided, one spring bending station providing the one end turn of the coil spring with the intended bending points, while at the same time the opposite spring bending station providing the other end turn of the coil spring with the same bending points.
  • the center piece and the bending tools are arranged on a common tool plate, the bending tools being arranged opposite one another at a distance from the center piece and pointing in a star shape to the center piece.
  • the bending tools and the center piece have recesses, tips, heads and edges and bevels in mutual cooperation corresponding to bending points and a kink end on the helical spring that is inclined at an angle to the spring axis.
  • the base of the U-shaped curved end winding is accordingly formed by a relatively long first web, on the two sides of which a short first side area and on the opposite side a longer, second side area.
  • This second, longer side area is followed by a second, relatively short web, to which a kinking end (also called a "tail”) connects at an oblique angle to the spring axis.
  • a kinking end also called a "tail”
  • the kinking end is bent inwards in the direction of the spring axis and always points into the inside of the coil spring, with which several advantages are connected at the same time.
  • the kinked end compensates for wire ends of different lengths, because when a longer wire has been cut and processed, the excess is accommodated in the kinked end, which is inclined at an angle to the spring axis.
  • the kink end is also inclined inwards to the spring axis in order to avoid chafing on the upholstery in a composite spring core.
  • alignment cams which are directed diagonally into one another are provided for aligning the spring, so that the helical spring can be precisely aligned and, in this position, transferred to a downstream assembly machine.
  • a particularly precise bend results from the fact that a hold-down device rests on the outer circumference of the center piece. This prevents the end turn from falling off the center piece during the bending process.
  • the respective bending tool only disengages from the end turn of the helical spring when the bending tool following the cycle is already in engagement with the end turn.
  • one of the bending tools always has form-locking contact with the end turn of the helical spring, thus preventing inadmissible movement and bending of the end turn on the outer circumference of the center piece.
  • the cam plate is driven via a spring-loaded engaging and disengaging dog clutch in such a way that the dog clutch connects the cam disc exactly one revolution to the motor shaft and then separates it.
  • the five different bending points on the end turn of the coil spring are thus carried out exactly during one revolution of the cam, after which the cam is then separated and stopped via the claw coupling of the motor shaft.
  • the spring alignment station has at least two pivotable alignment levers, with alignment cams at the front ends. It is provided that the alignment cams are directed diagonally to one another, which has the advantage that the end turn rotated and fixed by the alignment cams is clamped exactly in this position in the conveyor belt and is fed via the conveyor belt to the assembly machine. Further advantageous configurations result from the further subclaims.
  • the coil spring 10 shown in FIGS. 1 and 2 is a double-conical coil spring which is formed from a piece of wire and has two open end turns 11 and two screw turns 15, 16.
  • the end windings 11 provided on the end face are approximately U-shaped and lie one above the other as seen in the direction of the spring axis 17.
  • a first bending point 5 is attached in the area of the end turn 11, which is followed by a first, relatively short and curved side area 13.
  • the side region 13 is closed by a second bending point 6, which is followed by a relatively long, curved web 18, which in turn is closed by a third bending point 7.
  • a second side area 12 is passed through, which is parallel to the first area 13, but is longer than this, and is terminated by a fourth bending point 8, which is adjoined by a short, second web 18a, the longitudinal axis of which extends obliquely to the longitudinal axis of the first web 18 and which in turn is terminated by a fifth bending point 9, which is followed by the bent end 14 protruding from the plane of FIG. 2 and projecting obliquely upwards.
  • FIG. 3a shows schematically a machine for producing such coil springs 10 using the bending stations 178, 179 according to the invention.
  • a plurality of gripper arms 182-185 are arranged on a motor-driven turntable 181 and are distributed radially evenly around the circumference.
  • the free end of each gripper arm 182-185 is provided with a claw 187, which can be activated by a clamping mechanism, not shown.
  • the turntable 181 with the gripper arms 182-185 rotates in the direction of rotation 186, the helical spring 10 being manufactured being gripped by the claw 187 from an overhead spring winding station 177 and fed in the direction of rotation 186 to the first bending station 178, where the end winding 11 is placed on the center piece 66 shown in more detail in FIG. 3b.
  • the gripping arm 183 is then rotated 186 in the stepping cycle moved on, then the opposite end turn 11 of the Coil spring 10 gets into the area of the second bending station 179 and there this end turn is provided with the five bending points 5-9 described.
  • the helical spring 10 thus finished is then brought between the glow runners of a spring annealing station 180 known per se, where the stresses caused by the cold deformation are compensated at a temperature of approximately 300 degrees C.
  • the spring rotates slightly, so that an immediate supply of the coil spring 10 leaving the spring annealing station 180 to an assembly machine would not be possible because the coil spring is slightly rotated in itself.
  • the spring annealing station 180 is therefore followed by the spring straightening station 200 described in FIGS. 15-18, where an exact alignment of the coil spring 10 in the region of a conveyor belt 207 is possible on the basis of the bending points attached in the region of the end turns 11 of the coil spring 10.
  • the completed springs are successively placed in the transport channel of the conveyor belt 207 and fed to a spring core assembly machine in accordance with the technical teaching of DE-A-3 101 014.
  • FIG. 3b schematically shows a section of the illustration in FIG. 4, namely the assignment of the individual bending tools to the center piece 66.
  • the end turn 11 to be provided with the five bending points is placed with radial play on the outer circumference of the center piece 66, which is shown in the illustration in FIG. 3a via the gripper arms 182-185 provided with claws 187.
  • the first bending point 5 is attached via a bending tool 78 which has two tips, which are separated from one another by an intermediate recess 167.
  • the top lying in the illustration in FIG. 3b is designed as a bevel 168 which bears against the center piece 66 parallel to the assigned surface.
  • the recess 167 has an approximately U-shaped profile and merges into a tip 166 which engages in the recess 167 at an angle.
  • the first bending point 5 is hereby achieved by pressing and bending the end turn 11 over the tip 100 of the center piece 66.
  • the second bending point 6 is produced via the bending tool 70, which can be displaced radially in relation to the center piece 66 in the direction of its longitudinal axis and which likewise has a tip 71 which is opposite a recess in the center piece.
  • a recess 76 in the bending tool 70 which in turn is followed by a button 73 which is opposite a recess in the center piece 66.
  • the tip 71 and the head 73 thus move into the associated recesses on the center piece 66 when the bending tool 70 is radially advanced, while the bending point 6 is reached by the tip 77 of the center piece 66 resting on the end turn 11.
  • the holding-down device 23 Before any of the bending tools undertakes a bending process, the holding-down device 23 first moves its head 176 into the recess 80 on the center piece 66, as a result of which the end turn 11 of the coil spring 10 is held under the head 176 of the holding-down device 23. Only when the end turn 11 is fixed to the center piece in this way do the bending tools move in succession against the center piece, with the bending tool 78 performing the first bending point 5, the bending tool 70, the second bending point 6 and the wedge-shaped bending tool 64 the third bending point 7 .
  • the fourth bending point 8 is carried out via the bending tool 87 which, together with a further bending tool 79, is displaced radially inwards in the direction of the center of the center piece 66.
  • the bending tool 87 consists of two edges 174 lying next to one another, approximately at the same height, which are interrupted by a recess 175 lying between them.
  • the bending point 8 is in this case achieved by moving the edges 174 into associated recesses on the center piece 66, as a result of which the end turn is bent over the tip 173 of the center piece 66.
  • the bending tool 79 which is simultaneously advancing with the bending tool 87 presses the remaining spring end piece which forms the free end of the end turn 11 onto the surface of the bending tool 169, which is designed in the form of an oblique spatula.
  • the bending tool 169 can be moved upwards perpendicular to the plane of the drawing in FIG. 3b, so that the inward bent end 14 of the end turn 11 is thereby formed.
  • the bending tool 169 lies against a fixed support 170.
  • the head 171 of the bending tool 169 moves so far into the recess 172 on the center piece 66 so that it is possible to reach under the wire lying on the surface of the bending tool 169.
  • FIGS. 4-9 show further details of the bending tools and the sliders connected to them.
  • the hold-down device 23 in FIGS. 4 and 5 executes a movement in the direction of its longitudinal axis.
  • the axial longitudinal movement of the hold-down device 23 is achieved via the lever 2, which extends through the tool plate 3 in the region of a guide 21 and engages on the rear side via a bolt 24 with a control roller 26 arranged thereon in the cam track of the motor-driven cam 19.
  • FIG. 5 shows the slide 1, which is connected to the bending tool 169 (see FIG. 3b) and which bends the end 14 at the End turn 11 attaches.
  • this slider 1 performs a tilting movement perpendicular to the plane of the drawing, while in FIG. 5 the slider 1 performs a movement in the direction of the arrow 108 shown.
  • the pivot point is formed by a bolt 48, the pivoting movement taking place under the force of a compression spring 61.
  • the compression spring is arranged between a tab 31, which is fastened with a screw 40, and a heavy dowel pin 69 on the opposite, pivotable part.
  • the bolt 48 is fixed via a pin 54.
  • the pivotal movement of the bending tool 169 and the slide 1 in the direction of the arrow 108 takes place via a cam 47 which is fastened to the slide 1 by a screw 41.
  • the cam has a lower wedge surface 51, which is assigned a wedge surface in the region of a cam 57 connected to the cam disk 19.
  • the cam 47 is raised and the slide 1 tilts about the axis 39 in the bolt 48.
  • the tilting movement is limited here by a stop 30 to which a heavy-duty pin 68 is assigned in the region of a guide plate 32.
  • Each bending tool 64, 70, 78, 87, 169 is connected to an associated slide 1, 35, 45, 55, which in each case passes through the tool plate 3 and, according to FIG. 7, has a bolt 36 on its underside on which a roller 38 is rotatably mounted is.
  • the bolt 36 is fixed here with a pin 54.
  • the slides can be adjusted according to FIGS. 7 and 4 with associated adjusting screws 50 in their longitudinal displacement in the direction of the center piece, while the lateral adjustment takes place via lateral adjusting screws 49, which are seated in assigned lateral guide blocks.
  • the tool plate is designed in two parts.
  • a harder intermediate plate 29 is fastened on the relatively soft tool plate 3 with the aid of fastening screws 46 and the guide 27 for the various slides is arranged on this intermediate plate 29, the guide 27 having mutually opposite guide grooves 60 which are provided with additional lubrication grooves 59, in which the slides are guided to be longitudinally displaceable (see FIG. 8).
  • the guide 27 is fixedly connected to the tool plate 3 by means of a screw 44, while the opposite side is formed by a guide block 63 which is fastened by means of two spaced adjusting screws 49, which are seated in assigned nuts 58. are adjustable. An indirect adjustment of the slide 35 itself is thus possible.
  • the guides 21 (FIG. 9) each consist of plastic plates which are fastened to the tool plate 3 with the aid of screws 42.
  • FIGS. 4 and 7 also show that above the tool plate 3, a mounting plate 4 each serves to receive the center piece 55.
  • FIGS. 10 to 14 The details of the drive of the cam disc 19 are shown in FIGS. 10 to 14, the drive having to have the following basic functions:
  • the cam disc 19 must be driven to rotate exactly one revolution and must be stopped after the revolution has been completed.
  • cam disc 19 has both internal cam tracks 163 which are designed as channels which are open at the top and cam tracks which run along the outer circumference of the cam disk 19.
  • the cam disc 19 which has an eccentric outer circumference, is coupled in a rotationally fixed manner to an eccentric shaft 112, the eccentric shaft in turn being connected in the region of its ring flange to a locking eccentric 125, the function of which will be explained in more detail later with reference to FIG. 14.
  • the eccentric shaft 112 is rotatably supported in the drive housing 109 by two spaced bushes 153, 155.
  • the eccentric shaft 112 is driven by a claw coupling 154, which consists of two opposing teeth 94, 97 which, when engaged, mesh with one another.
  • the sleeve assigned to the upper toothing 94 is spring-loaded by a compression spring 95 and pressed against the lower toothing 97, provided that the dog clutch 154 is engaged.
  • the outer periphery of the claw coupling 154 has an external toothing which engages with an associated gear 89 which is connected in a rotationally fixed manner to a shaft 122 which is also rotatably mounted in the drive housing 109 via corresponding bushes 147, 148.
  • the shaft 122 is driven by a further gearwheel 119, which, however, is not connected to the shaft 122 in a rotationally fixed manner.
  • the overload clutch described below is arranged on a pinion 129 which is seated on the motor shaft 84 and is connected in a rotationally fixed manner to the motor shaft and this toothed wheel 119 of the shaft 122.
  • On the outer circumference of the gear 119 a plurality of fastening screws are arranged distributed around the circumference, which engage in an associated clutch ring 110.
  • the coupling ring 110 is firmly connected to the fastening screws.
  • the clutch ring 110 is rotatably mounted on a needle bearing 92 with respect to a hub 96 connected in a rotationally fixed manner to the shaft 122 via a wedge.
  • a second clutch ring 102 Coaxial with the clutch ring 110 is a second clutch ring 102, which is connected to the first clutch ring 110 via spring-loaded rollers 91.
  • the first clutch ring is otherwise mounted with a spacer 132 opposite a flange 121 fixed to the housing, the spacer 132 absorbing the axial forces.
  • the rollers 91 of the clutch ring 102 run in a U-shaped profiled annular groove 93, being pressed against the first clutch ring 110 under the force of a plate spring 88.
  • the plate spring 88 rests with its upper side on the underside of the coupling ring 102 and with its opposite side on a flange 82 fixed to the housing.
  • the hub 96 is fastened to the end face of the shaft 122 with the aid of a fastening screw 90. If the torque on the shaft 122 becomes too great, for example because the cam plate 19 is loaded too heavily, then the rollers 91 run out of their annular grooves 93 and the plate spring 88 is thereby pressed together.
  • the electric motor works here with its drive shaft on the motor shaft 84, which is mounted in two spaced ball bearings, which are separated from one another by a ring 140.
  • the lower ball bearing is supported via a spacer ring 137 on a clutch collar 99 of a further clutch, on which there are elastic elements 98 for the frictional force transmission, which engage in the associated ring groove tracks of a clutch 139, which downwardly with a spacer ring 138 supported on the drive housing 109.
  • This area is covered by a clutch bell 111, a motor plate 114 attaching to the bottom of the drive housing 109, to which the electric motor is flanged (not shown in more detail).
  • the claw clutch 154 is engaged by the fact that compressed air is applied to the cylinder 115, which thus moves the clutch lever 118 into the dot-dash position against a stop fixed to the housing, the pivot point of the clutch lever being in a bolt 128.
  • the coupling lever is pivoted counter to the force of a spring 81.
  • the clutch lever 118 is connected in a rotationally fixed manner to a control arm 116 which is seated on the outer circumference of the toothing 94 of the dog clutch 154. If the clutch lever 118 is pivoted into the dash-dotted position, the control arm 116 falls out of engagement with the toothing 94 and the claw coupling 154 engages with its sleeve 146 under the force of the coil spring 95, so that the two toothings 94, 97 are in Engagement.
  • a further cylinder 117 is provided, which is controlled by the same valve, so that both cylinders 115, 117 are actuated at the same time.
  • the cylinder 117 acts on the locking lever 106, which is rotated here about its pivot axis 126.
  • the pivot axis 126 is in this case formed by a bolt which is mounted in a stand 101 which is part of the drive housing 109.
  • the roller 135 attached to the locking lever 106 runs along the outer circumference of the locking eccentric 125. Only towards the end of the complete rotation, ie shortly before its completion, does the locking lever pivot under the force of the helical compression spring 105 into a control curve 127 which leads from the outer circumference of the locking eccentric 125 designed as a disc 164 to the inner circumference.
  • the locking edge 161 located at the opposite end of the control curve 127 serves as a stop for the assigned control edge 162 of the locking lever 106.
  • the control edge 162 of the locking lever 106 strikes the assigned stop surface of the locking edge 161.
  • the entire cam plate 19 could inadvertently kick back in the opposite direction due to the snap-in impact.
  • a spring-loaded latch 144 is provided, which comes into the opposite position with the locking edge 161 and the locking eccentric 125 and so that the cam disc 19 avoids.
  • the trap 144 engages with its front end in the disc 164 and strikes the opposite side of the locking edge 161, so that this is held on the one hand by the locking lever 106 and on the other hand by the trap 144.
  • the engagement takes place softly because the control edge 162 attached to the locking lever 106 is designed as a Vulkollan plate 134.
  • FIG. 14 shows the same conditions again, the locking lever 106 being shown in section and it being visible that the locking eccentric 125 consists of a disk 164 of enlarged diameter, in the outer circumference of which the control curve 127 is arranged.
  • the roller 135 of the locking lever 106 thus runs on the outer circumference of the disc 164 until it reaches the area of the control curve 127.
  • the locking lever 106 is in this case rotatably mounted on a bolt 149, the bearing on the locking eccentric 125 taking place via the locking block 131, which is mounted in the locking lever 106 via a Vulkollan plate 133.
  • the pivot bearing of the locking lever 106 is formed by the bolt 151, which is fixed in the stand 101.
  • the claw coupling 154 has a counter cam 165 with a wedge-shaped inclined surface on which the associated bevel of the cam 142 connected to the bush 146 runs and thereby moves the bush 146 upward in the direction of arrow 103 and thus separates the toothings 94, 97 from one another . Due to the still rotating cam 19, the counter cam 165 is still moved over the cam 142, so that the cam 142 falls again in the opposite direction to the arrow direction 103 and the clutch is free for a new revolution.
  • the control arm 116 thus engages and locks the toothing 94.
  • the release lever 107 With the release lever 107, the dog clutch 154 can be disengaged, but not engaged.
  • the release lever 107 is pivotally mounted in a bearing 156 on the drive housing 109 and engages with its front pivotable end in the region of the toothing 94 of the sleeve 146 which can be displaced counter to the force of the coil spring 95.
  • the helical spring 95 is supported at its upper end against a spring plate 145, which transfers its axial force to a bush 155.
  • the bush 155 is mounted in a bearing 124 in the drive housing 109.
  • the stop for the locking lever 106 is arranged at an angle 150, which with its cover 130 strikes the stop designed as rubber elements when the cylinder 117 is activated.
  • the advantage of the drive device described with reference to FIGS. 10-14 lies in the fact that all slides and tools of the bending device are driven by one and the same central drive. This results in a relatively inexpensive and easy to manufacture arrangement compared to four separate drives, which would have to be synchronized accordingly.
  • a similar second bending station 179 is arranged behind the first bending station 170 at a cycle distance.
  • the other end turn 11 of the coil spring 10 is provided with the five bending points described.
  • the second bending station 179 is identical to the first bending station 178 in every detail.
  • Figure 3a shows that the coil spring completed by the second bending station 179 is subsequently introduced into a spring annealing station 180, the two end windings being placed in a current-locking manner between the current-carrying runners of the spring annealing station 100, after which the coil spring 10 is heated to approximately 300 degrees C and which is heated by the cold deformation resulting tensions can be compensated.
  • the coil spring deforms slightly, i.e. it twists and changes its length, which means that when the gripper arm 185 places the fully annealed coil spring 10 on the downstream conveyor belt, the coil springs stored there are not aligned exactly the same.
  • the transport device is described in DE-A-3 101 014.
  • the coil springs are each placed in a conveyor belt 207, which consists of two opposite and synchronously driven conveyor belts.
  • the spring straightening station 200 arranged in the area of the conveyor belt will now be explained, where the helical spring 10 is precisely aligned using the five bending points provided with the bending station according to the invention.
  • FIG. 15 shows one half of the conveyor belt 207 with its conveyor belt running there, which is driven in the direction of arrow 208.
  • the coil spring 10 is only shown with its one end turn 11, which with the in 15 and 16, the spring straightening station shown is rotated, while the opposite end turn 11 of the coil spring 10 is rotated with the spring straightening station shown in FIGS. 18 and 19.
  • the helical spring is aligned in that a slide 210 is attached to the machine housing in a stationary manner and can be pivoted about the axis 211 perpendicular to the plane of the drawing.
  • the pivoting takes place here with the aid of a compressed air cylinder 212, which acts with its piston rod 213 via a rubber element 214 on the extended arm 215 of the control lever 216, which is pivotably mounted in the axis 211.
  • the alignment lever 218 is attached, which has the alignment cam 219 at its lower, free end. According to FIG. 15, the alignment cam engages in the bending point 7 of the helical spring 10, which thus serves as a fulcrum and fixing point for the alignment.
  • a second alignment lever 221 is provided opposite the alignment lever 218 and also carries an alignment cam 222.
  • This alignment lever 211 is pivotally mounted on the machine housing in the pivot axis 224 in the direction of the arrow 223 and can be pivoted into its position 221 ′.
  • the alignment cam 222 engaging in the first bending point 5 of the end turn 11 of the coil spring 10. Because the alignment cams 219, 222 engage in diagonally opposite bending points 5, 7 of the end turn 11 of the coil spring 10, a stable straight position of the coil spring is achieved, which is thus rotated exactly so that the bending point 7 is always at the top.
  • the lower alignment lever 221 is pivoted via a compressed air cylinder 226, which is connected to the alignment lever 221 with its piston rod 227 via a joint piece 228 and a pivot pin 229, but is pivotable. By shifting the piston rod 227, the alignment lever 221 can thus be pivoted into the position shown in the direction of the arrow 223 and thus assumes its position 221 '.
  • left and right side stops 248, 249 which limit the respective end positions of the alignment lever 221.
  • a further compressed air cylinder 230 which, with its piston rod, presses the alignment lever 221 designed as a leaf spring in the direction of the arrow 232, so that its alignment cam 222 disengages from the end turn 11 of the coil spring 10.
  • the alignment lever 221 is not designed as a leaf spring, but is rigid in itself, this rigid element being pivotable in a pivot bearing arranged on the machine housing in the direction of arrow 232 and in the opposite direction to this.
  • FIGS. 17 and 18 show the opposite spring alignment station 200, where the alignment of the opposite end turn 11 of the coil spring 10 takes place with the alignment means shown there.
  • a control slide 233 can be pivoted perpendicularly to the plane of the drawing in FIG. 18, specifically in the manner of the alignment lever 218 shown previously.
  • the control slide 233 has a control cam 234 which engages in the bending point 6 of the end turn 11 of the helical spring 10.
  • the swiveling of the helical spring 10 into the position 10 'with the swivel center in the area of the bending point 6 around the control cam 234 takes place via a control slide 236 which can be moved downward in the direction of arrow 240 in FIG. 18 and which carries a lower, front control cam 237, which in the area of the web 18 of the end turn 11 of the helical spring strikes it and the end turn turns in the direction of arrow 235 into position 10 '.
  • the control slide 236 is driven via a piston rod 239 by a compressed air cylinder 230 in a vertical direction (according to FIG. 18).
  • control cam 237 abuts only on the outside of the end turn 11 of the helical spring and thus allows the spring a certain amount of torsional play around the control cam 234.
  • the one alignment station according to FIGS. 15, 16 and the opposite alignment station according to FIGS. 17, 18 are driven synchronously, so that the alignment of the two end windings 11 of the coil spring 10 takes place at the same time.
  • control cams 219, 222, 234, 237 with the associated control rails are brought out of engagement with the end windings 11 of the spring.
  • the spring thus aligned is conveyed further in the direction of arrow 208 in the conveyor belt 207 in the direction of a transfer device, where it is fed to the spring core assembly machine.
  • control slide 233 is driven by a compressed air cylinder 241, which is shown in a side view in FIG. 18 and in a top view in FIG. 17.
  • An advantage of the invention is therefore that the bending points can be attached in the region of the two end turns of the coil spring with a relatively simple bending machine in the course of the manufacturing process of the coil spring, the bending points attached by the bending machine simultaneously for exact alignment of the coil spring for feeding into a downstream assembly machine can be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Wire Processing (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)
EP85102219A 1984-04-30 1985-02-28 Maschine zur Erzeugung von Schraubenfedern Expired EP0160174B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3416110A DE3416110C2 (de) 1984-04-30 1984-04-30 Maschine zur Erzeugung von Schraubenfedern
DE3416110 1984-04-30

Publications (3)

Publication Number Publication Date
EP0160174A2 EP0160174A2 (de) 1985-11-06
EP0160174A3 EP0160174A3 (en) 1987-10-21
EP0160174B1 true EP0160174B1 (de) 1989-08-02

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EP85102219A Expired EP0160174B1 (de) 1984-04-30 1985-02-28 Maschine zur Erzeugung von Schraubenfedern

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EP (1) EP0160174B1 (env)
JP (1) JPS6130247A (env)
AU (1) AU566780B2 (env)
CA (1) CA1263070A (env)
DE (2) DE3416110C2 (env)
ES (1) ES286293Y (env)
MX (1) MX161118A (env)
ZA (1) ZA851969B (env)

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WO1996037320A1 (en) * 1995-05-26 1996-11-28 Sleepyhead Manufacturing Company Limited Spring formation
DE19542844A1 (de) 1995-11-17 1997-05-22 Spuehl Ag Transfereinrichtung für Federn zu einer Montagemaschine
DE19542846A1 (de) 1995-11-17 1997-05-22 Spuehl Ag Federtransporteinrichtung mit Servo-Antrieb
CH693482A5 (de) * 1998-12-24 2003-08-29 Spuehl Ag St Gallen Anlage zum Transport von schraubenlinienförmig gewundenen Federn.
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CA1263070A (en) 1989-11-21
EP0160174A3 (en) 1987-10-21
EP0160174A2 (de) 1985-11-06
ES286293Y (es) 1986-06-01
JPH0129611B2 (env) 1989-06-13
JPS6130247A (ja) 1986-02-12
ZA851969B (en) 1985-11-27
AU566780B2 (en) 1987-10-29
AU4055485A (en) 1985-11-07
ES286293U (es) 1985-11-01
MX161118A (es) 1990-07-31
DE3416110C2 (de) 1986-10-02
DE3416110A1 (de) 1985-11-07
DE3571944D1 (en) 1989-09-07

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