EP0798058A2 - Wire forming apparatus, in particular a universal spring coiling machine with cutting device - Google Patents

Abstract

The coil winding machine has a wire feed to supply wire to the winding heads and a cutter (38) which cuts off each coil length. The cutter is driven by a rapid action hydraulic cylinder (80) controlled by a programmable numerically controlled valve (78). The cutting action includes movable supports for the cutting system. These may be used to optimise the working stroke of the tool and to reduce the cutting noise or vibration.

Description

The invention relates to a wire-forming device according to the generic preamble of claim 1.

The invention relates specifically to the cut for separating the coiled spring from the endless wire in spring coiling machines, in particular spring coiling machines of a larger type with a working range of up to 20 mm wire diameter, for example for the production of cold-formed vehicle suspension springs.
Spring coiling machines with a straight cut have been known for a long time (see, for example, CH-Z. Technica, 1968, No. 10, pp. 839-841, especially Fig. 2), in which the springs can be moved up and down in a straight line in a rigidly arranged slide guide be cut off against a stationary cutting mandrel. So far, this is the most used cutting device in spring coiling machines.

In a known spring coiling machine of a larger type ("FUL 10"), the drive for this knife movement takes place from the feed motor. For this purpose, the wire feed (feed rollers) is stopped by means of a coupling when the spring length and number of turns are reached and at the same time switched to drive the cutting shaft. The cutting shaft makes one revolution for each cutting movement. From the cutting eccentric seated on the cutting shaft, its movement is transmitted via several levers, transmission and connecting links to the cutting knife which is slidingly guided on the outside on the front of the machine in a rigidly arranged slide guide. This type of movement and power transmission stores a lot of elastic energy. With the very high cutting forces, this is suddenly released after the cut and leads to large vibrations. However, these vibrations cause a lot of noise when the game is reversed because of the many bearing and articulation points, which together have a large bearing play. Big noise is no longer accepted by the operator of the machine and the professional associations. Even cut shock absorption provided for newer machines does not bring any noticeable improvements. The strong vibrations also destroy modern components and controls of the machine.

The stroke of the knife movement described above must be such that the cutting edge of the knife during the production of form springs, e.g. conical springs, runs through a path that corresponds at least to the maximum possible diameter difference between the largest and smallest spring outer diameter of the spring, so as not to be in the way of the spring during the winding process.

This large path that the cutting knife has to travel takes a considerable amount of time. However, as mentioned above, the wire feed of the machine stops during the cut. The production of a new spring can therefore only begin when the cutting knife has returned to its starting position, that is to say to its upper position.

The invention is therefore based on the object of providing a spring winding machine of the generic type which is drastically reduced in noise (environmental protection), which is low in vibration (longer service life of the machine and its tools), which works more efficiently (larger number of finished springs per unit of time) and which is fast from right-hand winds is convertible to left winds.

This object is achieved according to the invention in a spring coiling machine of the type mentioned in the preamble of claim 1 by the characterizing features of claim 1. Advantageous refinements and developments are characterized in the subclaims.

Because the cutting force in the spring winding machine according to the invention is advantageously introduced directly into the cutting device in the rear extension of the cutting knife without, or to a minimum reduced, play-causing transmission elements, the noise is reduced to a minimum and the harmful vibrations are avoided. This is done by means of an electro-hydraulic NC drive in the form of a fast-acting hydraulic cylinder with an associated control block, which is extended in the line of force of the cutting knife. This self-contained hydraulic drive forms a hydromechanical bearing control circuit and can be operated extremely dynamically. It essentially consists of the following components: hydraulic cylinder, control valve, setpoint specification, feedback, setpoint motor and stroke position adjustment. Such drives are already used in punching and nipple machines (see DE-Z. O + P "Oil Hydraulics and Pneumatics" 36 (1992) No. 10.

The fact that the cutting knife is fixed directly in the lower piston rod end of the cylinder and interacts with the cutting mandrel arranged in the mandrel carrier as a counter knife and that the cylinder is in turn firmly connected to the mandrel carrier, these parts form a compact cutting unit with a closed power flow (cylinder cutting knife cutting mandrel - mandrel carrier cylinder). All bearings of the cutting device of the spring coiling machine, always contain a certain bearing play, are placed outside of this flow of force, which only takes place in a straight line via tension and compression elements.

The electro-hydraulic drive itself is extremely quiet. During the entire working stroke there are no uncontrolled pressure profiles in the hydraulic system, even the actual "blow" during the cutting process - triggered by the tear off of the spring steel wire material - has a reduced effect.

In addition to reducing the cutting noise, this entire compact cutting unit, consisting of cylinder with control block and cutting knife and the mandrel carrier with the cutting mandrel after the cut has been made, in order to circumvent the large knife path required in the prior art for cutting off a coiled form spring to increase the performance of the spring coiling machine program-controlled swung out of the working plane around a swivel axis provided on the cutting cylinder. A major advantage of the embodiment according to the invention is that the center of gravity is far above the cutting knife, so the heavy part of the compact cutting unit is close to the pivot point and therefore hardly needs to be moved. The lower part to be swung away has relatively little mass.

The cutting knife only needs to go through a cutting path that corresponds approximately to the wire diameter to be cut, which can still be adapted to the wire strength if necessary. The machine control computer determines the optimal cutting stroke, which is transmitted to the electro-hydraulic NC drive of the cutting cylinder.

The program-controlled swiveling in of the cutting unit for the cut can already be started during the winding of the end turn of the form spring and the swiveling out after the cut during the knife return stroke. The work sequence for form springs is therefore: pulling in (winching) - with a time overlay swiveling in - cut - swiveling out during the knife return stroke. In the manufacture of cylindrical springs, the cutting unit does not have to be pivoted away. It can be cut immediately after the winding process. Another advantage of the electro-hydraulic NC drive of the cutting unit is that the cylinder piston is always floating between the piston and piston rod side two oil surfaces, so that it does not move to a mechanical stop at top dead center or bottom dead center. This results in excellent hydraulic shock absorption, which leads to a considerable reduction in noise.

It is also advantageous that the stroke position of the working piston of the cylinder can be changed independently of the working stroke. The starting position of the working piston within the overall cylinder stroke at which the working stroke is to begin can thus be freely selected in a CNC-controlled manner. This property of the spring coiling machine according to the invention means that cutting knives of different lengths of the cutting unit, for example re-sharpened knives, can be used, and to be able to compensate for the setting of the height of the cutting mandrel to the spring diameter to be coiled, and that the starting position of the climbing tool of a climbing device, for example after changing from one wind direction to the other wind direction, the retracted wire can be set in a CNC-controlled, reproducible manner without mechanical adjustment means, as will be described in more detail below.
Not only the free programmability of this NC drive of the cutting cylinder of stroke position and working stroke, but also that of speed, acceleration, dwell time and force bring enormous advantages.

Fig. 1

die Ausführungsform in Vorderansicht in teilweise abgebrochener Darstellung,

Fig. 2

eine Seitenansicht von rechts der Ausführungsform mit einem Teil-Längsschnitt nach der Linie II-II in Fig. 1,

Fig. 3

eine teilweise Draufsicht in Richtung III in Fig. 1 mit der Schwenkeinrichtung der Ausführungsform in teilweise geschnittener Darstellung,

Fig. 4

einen Längsschnitt nach der Linie IV-IV durch die Hinterwand der Ausführungsform mit Sicht auf einen Teil der Schwenkeinrichtung,

Fig. 5

eine Ansicht in Richtung V in Fig. 1 auf die rechte Vorderwand mit dem oberen Führungsschlitten der Ausführungsform in teilweise geschnittener Darstellung,

Fig. 6

einen Ausschnitt in Draufsicht in Richtung VI in Fig. 1 mit der Schneideinrichtung der Ausführungsform und

Fig. 7

einen vergrößerten Ausschnitt in Richtung VII von Fig. 1 mit der Höhenverstellung der Schneideinrichtung, teilweise geschnitten dargestellt.

The invention is explained in detail below with reference to the preferred embodiment of the machine according to the invention which is shown by way of example (and in part schematically) in the drawing. It shows

Fig. 1

the embodiment in front view in a partially broken representation,

Fig. 2

a side view from the right of the embodiment with a partial longitudinal section along the line II-II in Fig. 1,

Fig. 3

1 with the pivoting device of the embodiment in a partially sectioned illustration,

Fig. 4

2 shows a longitudinal section along the line IV-IV through the rear wall of the embodiment with a view of part of the swivel device,

Fig. 5

2 shows a view in the direction V in FIG. 1 of the right front wall with the upper guide carriage of the embodiment in a partially sectioned illustration,

Fig. 6

a detail in plan view in the direction VI in Fig. 1 with the cutting device of the embodiment and

Fig. 7

an enlarged section in the direction VII of Fig. 1 with the height adjustment of the cutting device, shown partially in section.

The spring winding machine shown in its entirety in FIGS. 1 and 2 consists mainly of a wire feed 10, a wind station 12 with a gradient device 14 and a cutting device 16. The wire feed 10 is e.g. formed by four pairs of a total of eight wire feed rollers 18, which feed an endless wire 20 straight and horizontally through a wire guide 22 into the wind station 12. The wire feed rollers 18 arranged on a left front wall 26 of the machine frame 28 are driven by a CNC-controllable servo motor, not shown.

In the wind station 12 there are two pin-shaped winding tools 32 and 34 permanently deforming the wire 20 running straight on them, a pitch tool 36 and a cutting tool 38. All tools are adjustable, exchangeable and movable.
The wire 20 is turned by the two winch tools 32 and 34, which are fastened in two winch devices 44 and 46 arranged one above the other on a right front wall 42 of the machine frame 28, depending on the position of the two winch tools 32 and 34, to the right or left-hand (positive or negative helicity) helical springs shaped, ie depending on whether the wire 20 is deflected upward or downward with respect to the wire guide axis 48. The construction and the mode of operation of the two winch apparatuses 44 and 46 correspond to those of the winch apparatuses 30 and 32 described in DE 92 13 164 U1 of the spring coiling machine disclosed therein. The few manipulations described there are also necessary here to convert the two winches 44 and 46 from one wind direction to the other wind direction. For the form drive of the upper winch apparatus 44 for generating the form of form springs sits on the front of the right front wall 42 of the machine on a shaft 52, which is driven by a second CNC-controllable servo motor 54, a disk-shaped control curve 56 designed as a bead curve, which leads to the Implementation of the rotary movement of the shaft 52 via rollers 58 and a lever 60 in a known manner in a translational movement of the wind tool 32 corresponding to the angle of rotation. The coordinated movement of the winch tool 34 of the lower winch apparatus 46 is controlled by a second disk-shaped control curve 64 designed as a bead curve via rollers 66 and a lever 68 as well as an articulated rod 69, which sits below the shaft 52 on another shaft 70 and via a toothed belt gear 72 from the same servo motor 54 is driven.

In a variant of the embodiment, each of the two control shafts 52 and 70 is driven program-controlled intermittently forwards and backwards by its own CNC-controllable servo motor 54 and 74, respectively.

This enables that in the case of form springs which are difficult to manufacture, e.g. with large differences in diameter, e.g. merge into each other in a spring turn (e.g. in the case of windings), the two winch tools 32 and 34 can be moved separately under program control, i.e. can be adapted to special needs.

In the production of right-handed springs, the cutting device 16 with a cutting cylinder 80 is arranged on an upper, activated pivoting device 82, while the rising device 14 with a rising cylinder 86 is arranged on a lower passivated pivoting device 88. Both cylinders 80 and 86 are hydraulic cylinder-piston units and each have a program-controlled NC valve 78 and 84.

For driving the actively acting pivoting device 82, a bracket 94 is fastened to a rear wall 92 of the machine frame 28, which is provided with a recess, onto which an angular planetary gear 96 is screwed, which is driven by a CNC-controllable servo motor 98. A driver flange 102 is arranged on a driven shaft journal 100 of the transmission 96 in a rotationally fixed manner. This is guided by ball bearings in a ring 104 fastened to the bracket 94. On the distal end of the driving flange 102, a toothed disk 110 is then arranged on a spacer ring 108, which, together with a disk-shaped control curve 112 designed as a bead curve, is screwed non-rotatably onto the driving flange 102.

The torque is introduced by the control cam 112 via two rollers 114, which are arranged at the free end of an arm 116 of a two-armed, upper swivel lever 120 which is pivotably mounted on a bolt 118 which is fastened in the bracket 94, bolt 118. At the forked end of the other lever arm 122 of the lever 120 designed as an angle lever, a connecting rod 126 acts on a bolt 124, which connects the pivot lever 120 to an upper fork flange 130 via a bolt 132. The connecting rod 126 consists of two joint heads 134 and 136, which are connected to one another by a turnbuckle 138.

The toothed pulley 110 is connected via a toothed belt to a further toothed pulley which is seated in a rotationally fixed manner on the drive shaft journal of a position sensor (not shown but known). The encoder driven in this way is used for absolute position monitoring of the swivel device 82. An upper mandrel carrier 144 is fastened to the fork flange 130 and is slidably guided laterally between the lateral end face of the right front wall 42 and the lateral end face of the left front wall 26 of the machine frame 28. In a rectangular opening 148 of the upper mandrel carrier 144, a cutting mandrel 150 is clamped by means of a known, not shown in detail, but known mandrel tensioning device 152, which also sits in the breakthrough.

The movable cutting tool 38 of the cutting device 16 interacts with the cutting mandrel 150, which is stationary during the cutting process, as a counter knife. If required for certain types of spring, the mandrel 150 can be withdrawn from the wind area by means of a device, not shown but also known, while the cut is not being made and after the force-locking of the mandrel tensioning device 152 has been released.

The housing 81 of the hydraulically operating cutting cylinder 80 of the cutting device 16 is screwed onto the end of the upper mandrel carrier 144 opposite the fork flange 130. At the end of the cutting cylinder 80 facing the cutting mandrel 150, a cutting tool holder 158 is inserted in its piston rod 154 in a receiving bore 156 and fastened to the piston rod, in which the cutting tool 38 is held clamped. The upper end of a downwardly extending guide rod 164 is mounted in a crossbar 162 connecting the upper end of the right machine front wall 42 to the upper end of the rear wall 92 of the machine frame 28, while the lower end of the guide rod 164 is mounted in a bearing 166 below the crossbar 162 is held firmly clamped on the right front wall 42. An upper guide carriage 170 is slidably mounted on the guide rod 164. An arm 172 of the guide carriage 170 is additionally slidably guided laterally between the lateral end face of the right front wall 42 and the lateral end face of the left front wall 26 of the machine frame 28, and protrudes forward between these two walls out of the spring coiling machine. The arm 172 is bifurcated at its front end and receives two pins 176 of the cutting cylinder 80 of the cutting device 16, which are laterally turned on the cylinder housing, between the fork in bearing bores which are designed in two parts. These two pins 176 form a pivot axis 178 for the torque introduced by the control cam 112 onto the pivot lever 120, which is transmitted via the connecting rod 126 and the fork flange 130 to the upper mandrel carrier 144 to which the cutting cylinder 80 is fastened, as a result of which the entire Cutting device 16, consisting of cutting cylinder 80 with cutting tool 30 and upper mandrel carrier 144 with cutting mandrel 150, together with screwed-on fork flange 130 about this pivot axis 178 from the cutting plane of the cutting device 16, which is approximately parallel with respect to the machine front walls, into a view protruding into the drawing plane of FIG. 1 directed, inclined plane is pivoted away. The cutting tool 30 is thus pivoted back out of the winch plane and releases it. For the swiveling out after a wire cut on a coiled spring and the swiveling in after the winding of a new form spring, the control cam 112, time-controlled by CNC, makes a reciprocating limited rotary movement from the oscillating servo motor 98. The measure of the rotary movement, that is the size of the swivel angle, can also be CNC-controlled.

The entire cutting device 16 with the upper mandrel carrier 144 can be adjusted in a CNC-controlled manner by motor, whereby the position of the cutting mandrel 150 can be adapted to the spring diameter to be wound and to the winding direction.

For this purpose, a bearing 182 is fastened to the crossbar 162 at the upper end of the machine frame 28, on which a worm gear 184 is flanged by means of an intermediate flange 186. The worm gear 184 is driven in a CNC-controlled manner by a controllable servomotor 188 flanged to the gear 184. On the output side, a downwardly projecting spindle 190 is rotatably inserted into the gearbox 184 and is rotatably mounted in the bearing 182 by means of an axial deep groove ball bearing 192 for receiving the axial forces acting on the spindle 190. The spindle 190 is fixed axially adjustable in the bearing 182 by means of an adjusting nut 194. A toothed disk 196 is arranged on the spindle 190 in a rotationally fixed manner below the intermediate flange 186. The toothed pulley 196 is connected via a toothed belt to a further toothed pulley which is seated in a rotationally fixed manner on the drive shaft journal of a position sensor (not shown but known). The encoder driven in this way is provided for position monitoring and / or position display.

The spindle 190 is provided with an external thread 200 approximately on its lower half, which is screwed into a flange threaded bushing 202. The flange 204 of the threaded bush 202 is fastened to the upper guide carriage 170 by means of screws. By CNC-controlled rotation of the spindle 190 by means of the servo motor 188, the upper guide carriage 170 and with it the entire cutting device 16 can be adjusted in its height position upwards and downwards.

In axial extension of the guide rod 164 there is provided a second guide rod 208 (conceivable with it), the upper end of which is fixedly supported in a bearing 210 which is fastened to the right front wall 42 of the machine frame 28, while the lower end of the rod 208 is in the floor the right front wall 42 is mounted. A lower guide slide 216 is slidably mounted on the lower guide rod 208. Here, too, an arm 218 of the guide carriage 216 is additionally slidably guided between the left front wall 26 and the right front wall 42 on the lateral end faces thereof. The arm 218 of the guide carriage 216 is forked at its front end and accommodates two pins 222 of the gradient cylinder 86 of the gradient cylinder 86 of the gradient device 14, which are laterally turned on the cylinder housing, between the fork in two-part bearing bores. The housing 87 of the pitch cylinder 86 is fixedly connected to a lower mandrel carrier 226 by means of screws, which is held laterally between the lateral end face of the right front wall 42 and the lateral end face of the left front wall 26; it has a rectangular opening 224 corresponding to the opening 148 of the upper mandrel carrier 144, in the cutting mandrel 150 is used with the mandrel clamping device 152 when the two tools 36 and 38 are changed after they have been removed from the upper opening 148.

On the side of the cutting mandrel 150 facing the hydraulically operating pitch cylinder 86, a pitch tool receptacle 232, in which the pitch tool 36 is held clamped, is inserted in its piston rod 228 in a receiving bore 230 and fastened to the piston rod. A fork flange 236 corresponding to the fork flange 130 of the cutting device 16 is screwed to the end of the lower mandrel carrier 226 facing away from the pitch cylinder 86. The guide carriages 170 and 216 are provided with a bore for receiving a fixing bolt 240 and the fork flanges 130 and 236 with an internal thread corresponding to the bolt thread. In the case of the incline device 14, the lower guide carriage 216 and the lower fork flange 236 are firmly screwed to one another by means of the fixing bolt 240, see FIG. 2. The unit consisting of the incline cylinder 86 together with the incline tool 36, the lower mandrel carrier 226 and the fork flange 236 is thereby fixed in such a way that it cannot pivot , whereby an unwanted pivoting away of the unit about the axis 244 of the pin 222 of the pitch cylinder 86 is prevented. The pivot axis 244 is thus inactive. A connection from the fork flange 236 to the control cam 112 of the lower pivot axis 88 is therefore not present when winds to the right. It should also be mentioned that the lower guide carriage 216 is connected to the upper guide carriage 170 by means of a connecting rod 248, so that the lower guide carriage 216 also takes part in the above-described CNC-controlled height adjustment of the cutting device 16 with the climbing device 14. As a result, a second controlled positioning axis can be saved for the lower guide slide 216.

Since the gradient device 14, as said by the coupling, makes use of the height adjustment of the cutting device 16, the position of the climbing tool 36 must be adjusted when the cutting device 16 is set to a different spring diameter or when changing from right-hand winds to left-hand winds with respect to the drawn-in wire. However, as mentioned at the beginning, this is not a problem, since the electro-hydraulic NC drive of the gradient device 14 does this automatically via the program-controllable stroke position adjustment of the working piston of the gradient cylinder 86 by the machine control. Of course, the stroke position adjustment could also be entered manually.

It should be mentioned again that the pulling in of the wire, the setting of the outside diameter of a cylindrical spring or the initial diameter of a form spring, the change in diameter when producing form springs, the setting of the cutting tool starting position, the setting of the cutting stroke, the pivoting of the cutting device, the setting of the starting tool position, the incline tool movement, the cutting mandrel clamping, if necessary the mandrel displacement and the height adjustment of the cutting device is carried out completely program-controlled via the sequence program of the spring winding machine.

However, this should not rule out the fact that one or the other work or adjustment process (e.g. the size of the cutting stroke, the swiveling in and out of the cutting device) cannot also take place without computer support.

• ― Maßnahmen zum Umbau der beiden Windeapparate 44 und 46 von Rechts- auf Linkswinden siehe DE 92 13 164 U1.
• ― Der Schneidzylinder wird jetzt zum Steigungszylinder und umgekehrt der Steigungszylinder zum Schneidzylinder, so daß die Schneidwerkzeugaufnahme 158 samt Schneidwerkzeug 38 und die Steigungswerkzeugaufnahme 232 in den jeweils anderen Zylinder getauscht werden müssen und ein Steigungswerkzeug für Linkswinden eingesetzt werden muß.
• ― Wechseln des Abschneidedorns 150 und der Dornspanneinrichtung 152 vom oberen Dornträger 144 in den unteren Dornträger 226.
• ― Entnehmen der Verbindungsstange 126 vom oberen Schwenkhebel 120 und vom oberen Gabelflansch 130 durch Entfernen der Bolzen 124 und 132.
• ― Verbinden des freien Hebelarms 256 des unteren Schwenkhebels 252 mit zwei Rollen 115 und des unteren Gabelflansches 236 mittels der ausgebauten Verbindungsstange 126.
• ― Festsetzen des oberen Gabelflansches 130 und des mit ihm verbundenen oberen Dornträgers 144 an dem oberen Führungsschlitten 170 durch Entfernen des Fixierbolzens 240 aus dem unteren Gabelflansch 236 und sein Einsetzen in den oberen Führungsschlitten 170 sowie Einschrauben in den oberen Gabelflansch 130. Die Schwenkbewegung der Schneideinrichtung 16 aus der Schneidebene heraus leitet jetzt die untere Schwenkeinrichtung 88 ein, während die obere Schwenkeinrichtung 82 inaktiviert, d.h. schwenkunbeweglich ist.

All the details described so far are valid for the production of right-handed springs, in which the spring body forms upward with respect to a horizontal plane with the wire guide axis 48. If the spring coiling machine according to the invention is now to be converted for the production of left-hand coiled springs, in which the wire is deflected downwards during the winding by the winding tools 32 and 34, the procedure is as follows:

• - For measures to convert the two winch units 44 and 46 from right-hand to left-hand winches, see DE 92 13 164 U1.
• - The cutting cylinder now becomes the pitch cylinder and vice versa the pitch cylinder becomes the cutting cylinder, so that the cutting tool holder 158 together with the cutting tool 38 and the pitch tool holder 232 must be replaced in the other cylinder and a pitch tool for left-hand winds must be used.
• - Change the cutting mandrel 150 and the mandrel clamping device 152 from the upper mandrel carrier 144 to the lower mandrel carrier 226.
• - Remove the connecting rod 126 from the upper pivot lever 120 and from the upper fork flange 130 by removing the bolts 124 and 132.
• Connecting the free lever arm 256 of the lower pivot lever 252 to two rollers 115 and the lower fork flange 236 by means of the removed connecting rod 126.
• - Fixing the upper fork flange 130 and the upper mandrel carrier 144 connected to it to the upper guide carriage 170 by removing the fixing bolt 240 from the lower fork flange 236 and inserting it into the upper guide carriage 170 and screwing it into the upper fork flange 130. The pivoting movement of the cutting device 16 the lower swiveling device 88 now initiates from the cutting plane, while the upper swiveling device 82 deactivates, ie is immovable.

The invention is not limited to the above embodiment. A number of changes and modifications can be made without departing from the spirit of the invention. For example, instead of the electro-hydraulic NC (linear) drives for cutting and inclination, electro-pneumatic NC drives can be used, or it could be used for program-controlled swiveling in and out of the cutting unit and for the height adjustment of the cutting device 16 instead of the adjustable ( Electric) servomotors 98 and 188, for example a controllable, hydraulic or pneumatic rotary drive, or a direct-driving linear drive are used.

REFERENCES LIST

10 =

Wire feeding

12 =

Wind station

14 =

Incline device 12

16 =

Cutting device

18 =

Wire feed rollers 10

20 =

wire

22 =

Wire guide

24 =

26 =

Left front wall of the machine frame 28

28 =

Machine frame

30 =

32 =

Winding tool 12

34 =

Winding tool 12

36 =

Incline tool 14

38 =

Cutting tool 16

40 =

42 =

Right front wall of the machine frame 28

44 =

Winch

46 =

Winch

48 =

Wire guide axis 22

50 =

52 =

wave

54 =

adjustable servo motor

56 =

Control curve

58 =

roll

60 =

lever

62 =

64 =

Control curve

66 =

role

68 =

lever

69 =

Articulated rod

70 =

wave

72 =

Timing belt transmission

74 =

adjustable servo motor

76 =

78 =

NC valve

80 =

Cutting cylinder 16

81 =

Housing 80

82 =

upper swivel device

84 =

NC valve

86 =

Incline cylinder 14

87 =

Housing 86

88 =

lower swivel device

90 =

92 =

Rear wall of the machine frame 28

94 =

console

96 =

Angular planetary gear

98 =

adjustable servo motor

100 =

Gearbox drive shaft journal 96

102 =

Drive flange

104 =

ring

106 =

108 =

Spacer ring

110 =

Tooth lock washer

112 =

Control curve

114 =

roll

115 =

roll

116 =

Arm of the upper pivot lever 120

118 =

bolt

120 =

upper pivot lever

122 =

other arm of the pivot lever 120

124 =

bolt

126 =

Connecting rod

128 =

130 =

upper fork flange

132 =

bolt

134 =

Rod end 126

136 =

Rod end 126

138 =

Turnbuckle 126

140 =

142 =

144 =

upper mandrel carrier

146 =

148 =

Breakthrough of the mandrel carrier 144

150 =

Cutting mandrel

152 =

Mandrel clamping device

154 =

Piston rod 80

156 =

Location bore of the piston rod 154 of the cutting cylinder 80

158 =

Cutting tool holder

160 =

162 =

traverse

164 =

Guide rod

166 =

camp

168 =

170 =

upper carriage

172 =

Arm of the carriage

174 =

176 =

Pin of the cutting cylinder 80

178 =

Swivel axis

180 =

182 =

camp

184 =

Worm gear

186 =

Intermediate flange

188 =

adjustable servo motor

190 =

spindle

192 =

Axial deep groove ball bearings

194 =

Adjusting nut

196 =

Tooth lock washer

198 =

200 =

Male thread of spindle 190

202 =

Flange threaded bush

204 =

Flange of the threaded bush 202

206 =

208 =

Guide rod

210 =

camp

212 =

214 =

216 =

lower carriage

218 =

Arm of the guide carriage 216

220 =

222 =

Pin of the pitch cylinder 86

224 =

Breakthrough 226

226 =

lower mandrel carrier

228 =

Piston rod 86

230 =

Location bore of the piston rod 228 of the pitch cylinder 86

232 =

Incline tool holder

234 =

236 =

lower fork flange

238 =

240 =

Fixing bolt

242 =

244 =

(Swivel) axis of the pin 222

246 =

248 =

Connecting rod

250 =

252 =

lower pivot lever

254 =

bolt

256 =

Arm of the pivot lever 252

Claims (13)

Device for forming wire, in particular a universal spring winding machine, with a wire guide (22) which ends at a wire forming station (winding station 12) in which forming tools (winding tools 32 and 34, pitch tool 36) and wire cutting tools (38, Cutting mandrel 150) of a cutting device (16) are arranged, which has a drive (cutting cylinder 80) of its movable cutting tool (38), which interacts with a stationary cutting tool (cutting mandrel 150) to cut the wire at the point where the two cutting tools meet ( 38 and 150), characterized in that a fluid-operated cylinder-piston unit (cutting cylinder 80) with a program-controllable NC valve (78) is provided as the cutting tool (38) - drive, the movable cutting tool (38) by means of a receptacle (158) is attached to the movable unit part (piston rod 154), the direction of movement of which with d he cutting direction of this cutting tool (38) matches; and that
the stationary unit part (housing 81) can be moved translationally and / or rotatably back and forth in at least one direction deviating from the direction of movement of the movable unit part (piston rod 154) from the plane of the shape spanned by the wire guide direction and the shearing direction (FIG. 1). Apparatus according to claim 1, characterized in that the stationary unit part (housing 81) is rotatably mounted on an arm (172) which is stationary during the cutting about a pivot axis (178) which is perpendicular to the direction of movement of the movable unit part (piston rod 154) and is parallel to the wire guide direction and by means of a Swivel drive (98, 96, 100, 112, 114, 120, 126) can be pivoted away and back in at least one direction from the plane of the shape spanned by the wire guide direction and the shearing direction (FIG. 1). Apparatus according to claim 2, characterized in that the stationary unit part (housing 81) is fastened to a part (upper mandrel carrier 144) carrying the stationary cutting tool (cutting mandrel 150) and this with the pivot lever (120) of a positive cam mechanism (cam 112, rollers) 114) of the swivel drive (98, 96, 100, 112, 114, 120, 126) is articulated. Device according to claim 2 or 3, characterized in that the bearing arm (172) is provided with a slide (170) which slides on a guide rod (164) extending parallel to the shearing direction and by means of a displacement drive (motor 188, gear 184, spindle 190) is adjustable. Device according to claims 4 to 3, characterized in that the slide (170) and the tool carrier (upper mandrel carrier 144) can be fixed to one another by means of a releasable, rigid connection (fixing bolt 240). Device according to one of claims 1 to 5, of the molding tools (pitch tool 36) of which one can be moved anti-parallel to the shearing direction of the cutting tool (38) by means of a drive (pitch cylinder 86), characterized in that a second fluid-operated cylinder is used as the shaping tool (36) drive -Piston unit (pitch cylinder 86) with program-controllable NC valve (84) is provided, the movable mold (36) being fastened to the second movable unit part (piston rod 228) by means of a receptacle (232), the direction of movement of which is the direction of movement of the first movable part Unit part (piston rod 154) is opposite. Apparatus according to claim 6, that the second stationary unit part (housing 87) is rotatably mounted about a pivot axis (244) perpendicular to the direction of movement of the second movable unit part (piston rod 228) and parallel to the wire guide direction, on a second arm (218) which is stationary during molding and optionally by means of a second swivel drive (98, 96, 100, 112, 115, 252, 126) can be swiveled away and back in at least one direction from the plane of the shape spanned by the wire guide direction and the shearing direction (FIG. 1). Apparatus according to claims 7 to 3, characterized in that the second stationary unit part (housing 87) is attached to a second part (lower mandrel carrier 226) arranged for the optional carrying of the stationary cutting tool (cutting mandrel 150) and this optionally with a second pivot lever (252 ) a second positive cam mechanism (control cam 112, rollers 115) of the second swivel drive (98, 96, 100, 112, 115, 252, 126) can be connected in an articulated manner. Apparatus according to claim 7 or 8, characterized in that the second bearing arm (218) is provided with a second slide (216) which slides on a guide rod (208) which extends parallel to the shearing direction and by means of a displacement drive (motor 188, gearbox 184 , Spindle 190) is adjustable. Apparatus according to claims 9 to 8, characterized in that the second slide (216) and the second tool carrier (lower mandrel carrier 226) have a releasable rigid connection (fixing bolt 240) to one another. Apparatus according to claim 9 with 4, characterized in that the two carriages (170 and 216) are rigidly connected to one another by means of a rod (248) and are provided with a common displacement drive (188, 184, 190). Apparatus according to claim 8, characterized in that a displaceable rod (126) is provided for the optional articulated connection of the first or second tool carrier (144 or 226) to the first or second pivot lever (120 or 252). Device according to claims 3 and 8, characterized in that the two swivel drives (98, 96, 100, 112, 126 and 114, 120 or 115, 252) except for separate pairs of rollers (114 and 115) on separate swivel levers (120 or 252) are identical.

Images