EP1181749B1 - Feed device for feeding electric contact elements into crimping tools of a crimping press - Google Patents

Description

The invention relates to a device for supplying electrical contact elements in the crimping tools of a crimping press, wherein the contact elements are supplied in the form of a band product in which they are juxtaposed or aligned in series over at least factory-internal standardized scrap webs together.

In the crimping tools, a crimped contact element is separated from the belt at the same time as it is crimped with a severing knife.

A distinction is made between the production and the transport between two types of wound-up tape, between tape with longitudinally or transversely arranged in the band contact elements. In the band with the juxtaposed (transversely) contact elements, the individual contact elements via scrap bridges defined length and width are interconnected. In the band with the longitudinally (successively) arranged contact elements, the individual contact elements via connecting webs between the insulating claw of the upstream in the band contact element and the contact part of the downstream in the band contact element are connected. The separation of a longitudinal contact element takes place simultaneously with the crimping by means of a separating knife.

The feeding of the contact elements is usually carried out using a transport finger.

The transport finger is actuated by a drive device. The drive can in principle be done in two different ways, either a separate drive, e.g. is provided pneumatically or hydraulically, which is controlled in dependence of the plunger position of the crimping press or the up and down movement of the press ram is used via a mechanical coupling to drive the transport finger.

The transport finger engages e.g. behind an edge of a contact element and pushes the tape towards the crimping tool. In this case, e.g. Inertia, acceleration and friction forces are considered.

Such a feeder with a drive for the transport means mechanically coupled to the ram is e.g. known from US-PS-2,494,137. The device has a pivotally mounted on the frame of the device lever, which cooperates with the plunger at its upstroke unilaterally and in the process alternately the contact element band moves stepwise over a delivery mandrel. The provision is made via a tension spring which is articulated on the lever and on the frame.

From DE-AS-1 515 396 a feeding device for a terminal strip is known. This feeder has a bottom slotted conveyor channel for the terminal strip. Surrounding the channel sits a transport carriage in the transport stroke direction, displaceable in the channel longitudinal direction transport carriage, which has a transporting finger, which passes through the bottom of the slot opening of the channel and transports the terminal element strip in the channel. The return stroke of the transport carriage and thus the biasing of the compression spring via a multi-part, adjustable pivot lever gear, which secured by a plunger Betätigungskeilsteg is driven in the downward stroke. The further transport of the terminal strip is thus carried out during the upward stroke of the plunger by the biased during the downward stroke of the plunger, acting on the transport carriage compression spring. Such a spring-loaded transport is not reliable due to the limited conveying force of the compression spring, for example, the occurrence of temporary higher delivery requirement, such as hooking or tilting of the terminal strip on the role.

Furthermore, such a device is complicated and constructed in many parts. The high number of Gleitreibpaarungen and - joints requires a high maintenance.

In a feeding device according to WO-98/00892, the drive of a transport finger and thus of the contact element strip takes place during the downward stroke of the plunger of the crimping press. The drive in this case takes place via a cam track web attached to the plunger whose cam track interacts with one end of a first leg lever. The other end of the first lever has a partial toothing, with which it meshes with a reverse toothing of a second pivot lever. The other end of the second pivot lever cooperates with a third pivot lever acting as a drag lever, at its free end a carrying and adjusting device for the transport finger sits. The carrying / adjusting device carries the transport finger, which thus performs a pivoting movement about the rotation / storage point of the third lever during the downward stroke of the plunger. Here it is in contact with a contact element of the contact element strip and pushes the foremost contact element in the transport direction into the region of the crimping tools.

The return stroke is effected by a compression spring which is supported at one end on the device frame and at the other end at one end of the second pivot lever.

Such a device has, inter alia, the disadvantage that only a small amount of time remains between the arrival of a contact element in its crimping position in the crimping tool and the crimping process for the correct feeding and insertion of the wire ends in the core or insulation claws of the contact elements, since shortly after the end positioning of the Contact element already crimping takes place.

In addition, the device is complicated and constructed in many parts. In rapid Hubabläufen the transport finger can swing against the spring pressure due to the inertia beyond its desired end position, which can cause inaccurate positioning of the contact element in the crimping tool. Inaccurate positioning of the contact element in the crimping tool can cause a poor crimp connection or, in unfavorable cases, damage or even destruction of the crimp top or crimp bottom tool.

In a further feeding device described in EP 0 525 952 A2, an up and down movement of the press ram is converted into an oscillating rotary motion of the toothed wheel by means of a rack mounted on the outside of the ram and a first gear meshing with the latter. The rack and the first gear are constantly engaged. The first gear drives via one or more other spur gears to a clutch hub of a rotary-slip clutch. The clutch hub has distributed over its circumference a plurality of radially outwardly spring-loaded, seated in corresponding blind holes Reibbolzen on. The Reibkupplungsnabe and the friction pin engages around a friction clutch bell with a cylindrical inner surface. The friction clutch bell and the friction clutch hub are rotatable relative to each other on a common axis of rotation. The friction pins are pressed by the compression springs with an end face against the inner circumferential surface of the friction clutch bell and thus ensure a frictional torque transmission of up to a limit torque the friction clutch hub to Reibkupplungsglocke. Extensively clamping the friction clutch bell, an output drive ring sits with a jib, at the end of which the drive finger is articulated via a carrier block. On the output ring adjustable rotation stops are provided which limit the rotation of the friction clutch bell against a frame-fixed counter-stop in both directions. About the rotation stops the transport stroke of the transport finger can be preset.

If a rotation stop reaches its counter stop, the slip clutch bell stops abruptly and thus the movement of the conveyor finger is stopped abruptly. As the plunger continues to move and the clutch hub continues to be forcibly driven further, the friction bolts slide along the inner circumferential surface of the friction clutch bell. The friction clutch thus acts in the manner of a slip clutch. Such a device has a complicated structure and is subject to high wear, in particular in the friction clutch.

In addition, the start of delivery and the braking of the contact element strip takes place abruptly and abruptly, so that longitudinal vibrations in the contact element strip can occur, which can lead to inaccurate positioning of the contact element to be crimped in the tool. When higher conveying forces occur for the contact element strip, for example due to entanglements on the roller, the slip clutch can slip unintentionally and thus a defined positioning can not always be ensured. Furthermore, adverse vibrations in the device can be generated by slip-stick effects, in particular in the region of the reversal points of the plunger. These vibrations are transmitted to the contact elements in particular during the downstroke until shortly before crimping via the transport finger and can thus cause inaccurate positioning in the crimping tool.

The object of the invention is to provide a feeding device for electrical contact elements in crimping tools of a crimping press, which ensures accurate positioning of the contact elements in the crimping tool, is simple and low-wear constructed and to optimize the contact element feeding a gentle start or acceleration and decay or deceleration Transport movement guaranteed.

This object is achieved with a device having the features of claim 1. Advantageous embodiments are specified in the subclaims.

According to the invention, the supply device to solve the task on a step gearbox. A step transmission according to the invention is a mechanical transmission with a drive member and a driven member, which converts a drive movement of the drive member by a defined, periodic engagement of the gear members in a defined, periodic, in particular bumpless output movement of the output member. Furthermore, the indexing gear has a locking mechanism, which blocks the output movement of the output member, preferably in a form-fitting manner, outside the engagement of the gear members. The drive gear member is mechanically coupled to the plunger in conjunction. The transport finger is connected for example via a coupling rod in the manner of a crank gear with the output member of the step transmission.

According to a preferred embodiment, the step transmission is jerk-free in its transfer function, ie configured with a constant course of acceleration and deceleration. The indexer has, for example, an oscillating rotating drive pulley with an eccentric and a pivotally mounted swash plate with a slot recess, wherein the eccentric periodically engages in the slot recess, preferably tangentially into the slot recess at the beginning and end of the engagement phase. Furthermore, on the Drive disc a locking bar fixed, which locks the swash plate when the eccentric and the swash plate are disengaged.

Fig. 1

eine erfindungsgemäße Zuführvorrichtung in einer perspektivischen Ansicht auf die Getriebeseite;

Fig. 2

die erfindungsgemäße Zuführvorrichtung gemäß Fig. 1 in einer teilfreigeschnittenen perspektivischen Ansicht auf die Getriebeseite;

Fig. 3

die Zuführvorrichtung gemäß Fig. 1 in einer perspektivischen Ansicht auf die Förderseite;

Fig. 4

eine perspektivische Detailvorderansicht der Getriebeglieder des Schrittgetriebes;

Fig. 5

eine perspektivische Detailrückansicht der Getriebeglieder des Schrittgetriebes;

Fig. 6 bis Fig. 11

den Bewegungsablauf des Schrittgetriebes in sechs Schritten;

Fig. 12

eine perspektivische Ansicht auf die Getriebeseite der erfindungsgemäßen Zuführvorrichtung am Beginn des Transportfingerrückhubes;

Fig. 13

eine perspektivische Ansicht auf die Getriebeseite der erfindungsgemäßen Zuführvorrichtung während des Transportfingerrückhubes;

Fig. 14

eine perspektivische Ansicht auf die Getreibeseite der erfindungsgemäßen Zuführvorrichtung am Ende des Transportfingerrückhubes;

Fig. 15

eine perspektivische Ansicht auf die Getriebeseite der erfindungsgemäßen Zuführvorrichtung mit dem Schrittgetriebe in einer gesperrten Stellung.

In the following the invention will be explained by way of example with reference to the drawing. Show it:

Fig. 1

a supply device according to the invention in a perspective view of the transmission side;

Fig. 2

the supply device according to the invention of Figure 1 in a partially cutaway perspective view of the transmission side.

Fig. 3

the supply device of Figure 1 in a perspective view of the delivery side.

Fig. 4

a perspective detail front view of the gear members of the step transmission;

Fig. 5

a detailed perspective rear view of the gear members of the step transmission;

Fig. 6 to Fig. 11

the sequence of movements of the stepper in six steps;

Fig. 12

a perspective view of the transmission side of the feed device according to the invention at the beginning of the Transportfingerrückhubes;

Fig. 13

a perspective view of the transmission side of the feeding device according to the invention during the Transportfingerrückhubes;

Fig. 14

a perspective view of the driving side of the feeding device according to the invention at the end the transport finger return stroke;

Fig. 15

a perspective view of the transmission side of the feed device according to the invention with the indexer in a locked position.

A feeding device 1 according to the invention has a carrier part 2, a plunger 4 displaceable in a vertical double arrowed direction 3 (= plunger working direction), a step transmission 5, with a drive pulley 6 and a swashplate 7 of thickness D and one in a double arrowed double direction 8 (= working direction of the transporting finger ) on a guide rail 9 slidably mounted transport carriage 10. The transport carriage 10 is coupled via a coupling rod 11 in the manner of a crank gear to the swash plate 7. The support part 2 is seated on a horizontal base plate 12.

The support part 2 is formed in one piece and has a first higher column 13 and a downstream in a conveying direction 14 of the first higher column 13 second lower column 15. The second column 15 rests on the base plate 12. The first column 13 is seated on a cantilever web 16 extending from the base plate 12 counter to the conveying direction 14 on its end 17. Between the first pillar 13 and the second pillar 15, the second pillar 15 extends protruding a distance from the boom web 16 a vertical support beam 18 so that a slot opening 19 bounded by the boom web 16, the pillars 13, 15 and a lower edge 20 of the support cheek is trained. Downstream in the conveying direction 14, on the column 15 in the direction 14 hinauskragend is a vertical bearing plate 21 integrally formed on the support cheek 18.

The support arm 18 and the bearing plate 21 have a tappet 4 and a contact element band (not shown) to be transported facing the transport side 22 and an opposite side gear 23. The bearing plate 21 is on the transport side 22 executed thickened relative to the support arm 18. On the transmission side, the support cheek 18 and the bearing plate 21 are aligned (FIG. 2).

On the transport side of the bearing plate 21 is a flat-shaped in cross-section groove recess 24 is formed, which extends longitudinally in the direction 3 of the plunger 4 over the entire bearing plate 21 and the transverse extent in the conveying direction 14 is about 3/4 of the bearing plate 21, so that on both sides the groove 24 limiting webs 25, 26 are formed.

On the transport side 22 of the boundary webs 25, 26 is parallel to the groove 24, a holding web 27, 28 attached to the bearing plate 21, wherein the holding webs 27, 28 projecting respectively in the transverse direction of the groove 24 a piece on the groove 24, so that a in Cross-section T-shaped guide groove 24a is formed (see also Fig. 3).

In the groove 24a is seated positively, axially in the working direction 3 of the plunger 4 (double arrow 3) slidably sliding plate 30 with a groove bottom of the T-slot 24a facing sliding surface 31 and a groove opening of the T-slot 24a facing plunger side 32nd

On the plunger side 32 of the holding webs 27, 28 of the substantially cuboid plunger 4 is fixed. The plunger 4 has an output side 35 facing the conveying direction 14, a front side 36 pointing in the conveying direction 14, a side 37 facing away from the carrier part 2, an upper actuating end face 38 and a crimping tool underside 39.

The actuating side 38 carries in a known manner a coupling piece 40 for kupplenden connecting the plunger 4 with the working punch of a hydraulic crimping press, for example. At the bottom 39 are receptacles in a known manner (not shown) for an upper tool half (not shown) of a crimping tool (not shown).

On the output side 35 of the plunger 4 is adjacent to the holding web 27 a parallel to the double arrow 3 extending rack 45 with a longitudinal extent, which is preferably slightly larger than the stroke of the plunger 4 between its top dead center TDC (shown in Fig. 3) and its lower Dead center UT (shown in Fig. 1, 2). The teeth 46 of the toothed rack 45 face counter to the conveying direction 14.

The rack 45 is continuously engaged with a gear 47, which is non-rotatably mounted on a shaft 48 with a longitudinal axis 49. The longitudinal axis 49 of the shaft 48 is perpendicular to the double arrow directions 3 and 8. The shaft 48 passes through the retaining web 27 and the bearing plate 21 and is rotatably supported there in the double arrow direction 50.

At the transmission-side end of the shaft 48 sits, preferably integrally connected to the shaft 48, the circular disk-shaped drive pulley 6 with the longitudinal axis 49 as the central axis. The drive pulley 6 has a radius R (FIG. 6) which is preferably greater than the radius of the pitch circle of the gear 47. The drive pulley 6 (FIGS. 4, 5) has a first flat side 51 facing the shaft 48 and one of the shaft 48 facing away from the second flat side 52 and sits with play in a the dimensions of the drive pulley 6 corresponding cylindrical disc-shaped flat recess 53 in the transmission side 23 of the bearing plate 21 such that the second flat side 52 comes to lie approximately flush with the transmission side 23 (Fig. 1, 2) ,

Eccentrically at a distance t <R (Fig. 5, 6) in the radial outer region of the drive pulley 6 is an axle pin 54 with its axis 55 as a central axis perpendicular from the flat side 52 of the drive pulley 6 from. The axle pin 54 (FIG. 5) carries a first cylindrical disk-shaped roller 56 adjacent to the flat side 52 as a roller and the first roller 56, the transmission side coaxial upstream of a similar cylindrical disc-shaped second roller 57 as a roller (Fig. 4). The rollers (56, 57) are each mounted independently of each other rotatably about the axis 55 on the pin 54 and have a radius r, which is preferably about 1/4 of the radius R. The roller 56 has a peripheral surface 58; the roller 57 has a circumferential surface 59.

The thickness of the rollers 56, 57 is in each case about half the thickness D of the swash plate 7.

Opposite the rollers 56, 57 is formed as a blocking element of a locking mechanism on the flat side 52 a cross-sectionally approximately square, in its longitudinal extent arcuate barrier web 60 with a center line 62 (Fig. 8). The locking bar 60 extends over an angular range φ symmetrical to an imaginary diameter line 61 through the centers of rotation of the drive pulley 6 and the rollers 56, 57th

The center line 62 has a radius R ₁ <R. The blocking web 60 has an inner flank 65, an outer flank 66, a first end 67 and a second end 68 and an upper side 69. The flanks 65, 66 are tapered toward the ends 67, 68, in particular tangentially rounded in the flanks 65, 66. The upper side 69 is arranged approximately at a distance D / 2 from the flat side 52.

On the transmission side 23 of the bearing plate 21, the swash plate 7 is pivotally mounted at the same vertical height as the drive pulley 6 about an axis parallel to the axis of rotation 49 about an axle 70a. The axis 70 is arranged downstream of the axis of rotation 49 in the conveying direction 14 at a distance L, the distance L being a fraction greater than the radius R of the drive disk 6.

Axle pin 70a is single ended in a bore (not shown) in the bearing plate 21 and the other end with a support bearing 71 pivotally supported. The support bearing 71 has a support bearing block 72, which is attached with respect to the axis 70 in the conveying direction 14 downstream of the bearing plate 21. From the support bearing block 72, extends opposite to the conveying direction 14 parallel spaced from the bearing plate 21, a support bearing plate 73 in the end region of a bearing bore 74 is provided for the axle 70a. Between the support bearing plate 73 and the bearing plate 21 sits adjacent to the bearing plate 21 with a bore 75 (Fig. 4), the swash plate 7 on the axle pin 70a.

As described above, the swashplate 7 (FIGS. 4, 5) is a disc-shaped body of thickness D and has a flat first flat side 76 facing the bearing plate 21 and a second flat side 77 facing away from the bearing plate 21. The swash plate 7 extends from the bore 75, approximately symmetrically, to a plane 78 which is perpendicular to the transmission side 23, beak-like in the direction of the drive pulley 6, wherein the first flat side 76 of the swash plate 7, the second flat side 52 of the drive pulley 6 at least partially covered. The swash plate 7 has on both sides of the plane 78 to this adjacent a first beak land 80 and a second beak web 81. The beak webs 80, 81 have Schnabstegenden 82, 83, in a pivotal position of the swash plate 7, wherein the axis 49 in the plane 78th is approximately in the range of the horizontal center of the drive pulley 6 are (see approximately Fig. 9).

Parallel to the plane 78 extends from the beak ends 82, 83 to a piece in front of the bore 75 has a U-shaped slot recess 84. The slot recess 84 has bearing plate side, a first pair of running edges 85 and adjacent to this a second pair of running edges 86, which each have opposite, parallel running edges 85a, 85b and 86a, 86b. The distance between the pairs of running edges 85a, 85b and 86a, 86b is in each case the same size and an amount X is greater than the diameter the rollers 56, 57. The running edges 85a, 85b; 86a, 86b each have a width of about half the thickness (D / 2) of the swash plate 7 and are mutually offset in a direction transverse to the plane 78 a piece, in particular offset by the amount X, so that in each case between the running edges 85a, 86a; 85b, 86b on each side of the recess 84, a step 88 is formed.

In particular, the step 88 or the distance between the running edges 85a, 86a; 85b, 86b arranged so that in each case the running edge 85a to the running edge 86b and the running edge 85b to the running edge 86a has a parallel distance corresponding to the diameter of the rollers 56, 57, so that the roller pair 56, 57 in the slot recess 84 can be inserted without play.

The running edges 85a, 85b; 86a, 86b have guide surfaces 85c, 86c which widen the slot recess 84 in each case towards the respective end of the bridge bar 82 or 83. The guide surfaces 85c, 86c are curved to ensure a gentle inlet and outlet of the rollers 56, 57 and run tangentially into the respective associated running edges 85a, 85b; 86a, 86b.

By such a configuration of the slot recess 84, it is possible to make the operation of the swash plate 7 by the coaxially arranged in diameter equal rollers 56, 57 of the drive pulley 6 - as described below in detail-wear-free and backlash, since the rollers 56 and 57 each defined on a running edges 85b and 86a roll and the respective other edge 85a, or 86b have a defined distance. The backlash of the operation is ensured because the running edges 85b and 86a - as described above - have a distance from one another, which corresponds to the diameter of the rollers 56, 57.

The slot recess 84 is bounded by a bottom boundary surface 89. It is arranged so that in a position of Drive pulley 6 and the swash plate 7 to each other, wherein the axis of rotation 55 of the rollers 56,57 between the axes of rotation 49 and 70 in the plane thereof (approximately a position shown in FIG. 9), the peripheral surfaces 58, 59 spaced a distance from the bottom boundary surface 89 are.

Starting from the plane of symmetry 78, starting on both sides starting in a region between the bottom boundary surface 89 of the slot recess 84 and the bore 75, at an obtuse angle to the slot recess 84, a vertical upper and a vertical lower slot recess 90 and 91 respectively. The slot recesses 90 and 91 penetrate the swash plate 7 and are extended from about the middle of the swash plate 7 to the bearing side flat side 76 out, designed so that a circumferential stop step 92 is formed approximately in the region of the median plane of the swash plate 7. The second flat side 77 has in the region of the slot recesses 90, 91 an ablation 93 of small depth, so that a support plane 95 and guide edges 94 are formed. The guide edges 94 each extend rectilinear, spaced and parallel to the slot recesses 90, 91 on the slot recess 84 side facing.

In the extended area of the slot recess 90, 91, a sliding block 96, 97, which is flush on one side flush with the first flat side 76 and rests on the stop step 92 on the other side, is seated in a form-fitting manner displaceably in its longitudinal direction. The sliding blocks 96, 97 each have threaded bores 98 in their longitudinal end regions, whose center axes are perpendicular to the disk center plane of the swashplate 7.

On the support plane 95 and adjacent to the leading edge 94, sitting respectively communicating to the sliding blocks 96, 97 holding plate 99, 100, which also have in the end regions through-holes 101, which communicate with the threaded holes 98 of the sliding blocks 96, 97. By the plane 78 each closer holes 98, 101 is from the second flat side 77 ago a fixing screw 102 for fixing the retaining plates 99, 100 with respect to the sliding blocks 96, 97 screwed. The respective outer bores 98, 101 optionally serve for fastening a first joint eye 110 of the coupling rod 11 (FIG. 1).

By moving the sliding blocks 96, 97 with the holding plate 99, 100 and the hinged joint eye 110 of the coupling rod 11, the length of the coupling lever for the coupling rod 11 with respect to the axis 70 can be adjusted. This adjustment can be determined by tightening the screws 102 and a fixing screw 103 for the joint eye 110 by clamping.

Starting from the support plane 95, the swashplate 7 has a further ablation 111 in the region of the bore 75, so that a surface 112 and two straight, mutually obtuse edges 113 are formed.

In the first flat side 76 of the swash plate 7 are in the beak lands 80, 81 the Langlochausnehmungen 90, 91 upstream in the direction of the billets 82, 83, respectively arcuate locking grooves 120, 121 provided (Fig. 4 to 8), which as counter-locking elements for the barrier web 60 serve. The locking grooves 120, 121 have at least partially the same cross-section and the same radius as the Spersteg 60 of the drive pulley 6, so that the locking bar 60 fits positively into each of the locking grooves 120, 121. The locking grooves 120, 121 lead from a peripheral edge 123 of the swashplate 7 circular arc in the direction of the slot recess 84, wherein the locking groove 120 opens into the slot recess 84 and the locking groove 121 ends approximately half the arc length between the peripheral edge 123 and the slot recess 84. The position of the locking grooves 120, 121 is constructively chosen so that in a first end position (see Fig. 6) of the swash plate 7, the locking web 60 of the drive pulley 6 is inserted by rotation of the same in the locking groove 121 and continue the barrier web 60 in one second end position (see Fig .. 5) of the swash plate 7 by rotation of the drive pulley 6 with the End 67 can be moved forward in the locking groove 120. The barrier rib 60 and; the locking grooves 120, 121 thus form a locking mechanism which, in an anticyclical manner for engaging the rollers 56, 57, locks the pivotability of the swashplate 7.

The locking grooves 120, 121 each have side arc surfaces 124, 125 and a respective base 126. The side arc surfaces 124, 125 are each chamfered in the mouth region of the locking grooves 120, 121 to the peripheral edge 123 of the swash plate 7, in particular tangentially curved expanded.

Within the tangential arch extension, the side arc surfaces 124, 125 of the grooves 120, 121 are over some distance, e.g. about 4 mm, a distance from each other, which corresponds to the spacing of the flanks 65, 66, so that locking surfaces 124a, 125a are formed, which ensure a positive guidance of the locking web 60. Within the locking surfaces 124a, 125a, the side arc surfaces 124, 125 have a greater distance from each other, so that the barrier rib 60 can be inserted in this area with play. Such a configuration of the locking grooves 120, 121 ensures a hook-free moving into each other of the locking web 60 in the locking grooves 120, 121 (see Fig. 7).

The guide rail 9 extends on the transmission side 23 of the support arm 18 in the direction of the double arrow 8 between the first column 13 and the second column 15 a piece above the lower edge 20. It is e.g. fastened with screws 130 to the support arm 18 and has at its longitudinal edges 131 channel-shaped guide grooves 132.

On the guide rail 9 sits axially in the double arrow 8 slidably the guide rail 9 encompassing, a Schlittengleitteil 133, which is designed as a recirculating ball guide with a sealing lip 134.

On a side facing away from the guide rail 9 outer surface 135 of the Schlittengleitteils 133 a carriage bracket 136 is attached. The slide bracket 136 has vertically upward, the slide slide 133 protruding, to exactly the height of the axis 49 reaching a coupling lug 137, which has a bore 138 in its end region (Fig. 2). The bore 138 is perpendicular to the central axis of the transmission side 23 and serves to attach a second hinge eye 139 of the coupling rod 11 by means of a screw 140 and a nut 141st

To facilitate accessibility of the screw 140, 141, the support cheek 18 in the region of the screw 140, 141 an opening 142.

Below the slide sliding part 133 of the slide bracket 136 passes through the slot recess 19 cantilevered and has on the transport side 22 of the support cheek 18 a vertical flange plate 143 with a mounting surface 144. The mounting surface 144 has a plurality of parallel vertical grooves 145 and a horizontally extending slot 146. The transport finger carrier 147 supports an adjusting device 150. The adjusting device 150 allows a knurled screw 151 to fine-tune a transporting finger carrier 152 in the double arrowed direction 8 with respect to the transport finger carrier 157. The transport finger carrier 152 has a horizontally away from the support arm 18 bearing pin 154 and a below the bolt 154 at a distance extending support strip 155. On the bolt 154 a transport finger holder 156 is spring-loaded pivotally mounted. The transport finger holder 156 cantilevers a piece in the transport direction 14, so that its pivotability is limited downwards by the support strip 155. On a side surface 157a of the transport finger holder 156 carries a vertical plate-shaped transport finger 158th

The transport finger 158 has an upper edge 159, a ramp edge 160 rising from the forward end of the upper edge 159 in the conveying direction 14, and a vertical leading end edge 161, so as to form a pointed jaw 162 which rests on edges of the contact elements or in predetermined recesses of the contact element strip, e.g. can intervene in the scrap bridge.

During a movement of the transport carriage 10 in the conveying direction 14, the engagement corner 162 hooks on suitable edges or in suitable recesses of the contact element band (not shown) from below and transports this in a form-fitting manner. In a return movement counter to the conveying direction 14 of the transport finger slides with the ramp edge 160 at the contact elements resiliently ratcheting down evasive along.

Between the hinge eyes 110 and 139, the coupling rod 11 extends. The coupling rod 11 is cantilevered rigid and each pivotally mounted about the central axes of the screws 103, 140 on the swash plate 7 and on the coupling plate 137. The coupling rod 11 is part of a crank mechanism, consisting of the swash plate 7, the coupling rod 11 and the linearly displaceable in the double arrow 8 slide 10 and is used to convert the oscillating pivotal movement of the swash plate 7 in an oscillating linear motion in the double arrow 8 of the carriage 10th

In the following the operation of the feeding device 1 will be explained in more detail:

As starting position I, an arrangement of the individual components of the feeding device 1 according to FIGS. 3, 6, 12 is defined. In position I, therefore, the plunger 4 is in its top dead center (TDC) (FIGS. 12, 3); the rack 45 is engaged at its vertical lower end with the gear 47 (FIG. 3). In this position I are the rollers 56, 57 outside the slot recess 84, for example vertically above the axis of rotation 49 of the drive pulley 6 (FIG. 6). The locking ridge 60 rests with its end 68 in the locking groove 121 and causes via its flanks 65, 66 which rest positively on the locking surfaces 124a, 125a of the locking groove 121, a locking or blocking the swash plate 7 about the pivot axis 70th In this position I, the median plane 78 between the running edges 85b, 86a of the swash plate 7 forms a tangential plane E to an imaginary cylindrical surface Z with the axis 49 as the central axis and the radius t (FIG. 6). The tangential plane E touches the imaginary cylinder surface Z in an imaginary contact line B. Furthermore, according to FIG. 12, the coupling rod 11 is fastened with its first joint eye 110, for example, to the holding plate 99 or the corresponding sliding block 96 lying vertically above the axis 70. Thus, the carriage 10 is adjacent to the second column 15 at the front end of the guide rail 9 in the conveying direction 14 (FIG. 12). The transport finger 158 is located in a forwardmost end position in the conveying direction 14 (FIG. 3). The foremost contact element of the contact element band is correctly positioned in this position in the crimping tool and fixed by a possibly present transport brake (not shown) in this position.

If the plunger 4 is actuated in its working stroke direction 3a starting from top dead center (FIG. 12), then the drive disk 6 is set in a rotational movement of the arrow direction 50a. The rollers 56, 57 are moved in the direction of the mouth of the slot recess 84, the barrier web 60 is simultaneously pulled out of the locking groove 121. The swash plate 7 and thus also the carriage 10 are still in their starting position.

In a position II, the central axis 55 coincides with the imaginary touch line B. In this position, the rollers 56, 57 have threaded through the guide surfaces 85c, 86c tangentially into the slot recess 84 smoothly incoming, so that the roller 57, the running edge 86a and the roller 56 touches the running edge 85b. The swash plate 7 is thus free of play with the drive pulley 6 engaged. At the same time, the locking bar 60 passes out of the locking groove 121 and gives the swivel plate 7 pivotally free.

By a further movement of the plunger 4 in the direction of the arrow 3a, the swash plate 7 is gently accelerated by the roller 56, in particular smoothly, in a pivoting movement in the direction of an arrow 170a direction (Fig. 8) about the axis 70 (position III). Likewise, the first joint eye 110 of the coupling rod 11 describes such a jerk-free accelerated pivoting movement and transmits it via the coupling rod 11 to the carriage 10, which accelerates from its rest position smoothly, linearly in a return stroke 8a of the transport finger 158 (Fig. 13) against the conveying direction 14 on the column 13, in motion. The transport finger 158 thus begins its return stroke.

In a position IV (FIGS. 9, 13), the axes 70, 55, 49 are in one plane. The rollers 56, 57 reach a reversal point in the slot recess 84. The carriage 10 and thus the transport finger 158 reach a middle position between their front and rear reversal point. The instantaneous speed of the pivoting movement of the swashplate 7 relative to the drive pulley 6 reaches a maximum.

A further movement of the plunger 4 in its working direction 3a causes further rotation of the drive pulley 6 in the direction of the arrow 50a to a position V (Fig. 10). During this movement, the pivoting movement in the direction of arrow 170a of the swashplate 7 is gently, in particular smoothly delayed; the instantaneous speed of the pivoting movement reaches zero in the position V.

In the position V, the center plane 78 again represents a tangential plane E 'to the imaginary cylindrical surface Z described by the axis 55, whose imaginary contact line B' coincides again with the axis 55. In this position V has the

Barrier 60 reaches with its first end 67, the mouth of the locking groove 120, which has been pivoted by the pivoting movement in the career of the locking bar 60. The rollers 56, 57 are again in the mouth region of the slot recess 84, wherein they touch the running edges 85b and 86a in the transition region between the running edges 85b, 86a and the guide surfaces 85c, 86c.

Analogous to the swashplate 7, which is in its second limit position, the carriage 10 also reaches the speed zero without jerking, its rear end position at a distance F from the column 13 (FIG. 14).

Starting from the position V leave the rollers 56, 57 in a further movement of the plunger 4 in its working direction 3a, the slot recess 84 tangentially and thus jerk-free, so that to the bottom dead center (UT) (Fig. 15) of the plunger 4, the engagement of the rollers 56, 57 is canceled in the swash plate 7. At the same time, the blocking web 60 penetrates the pivotability of the swivel disk 7 in a form-locking manner into the locking groove 120. The carriage 10 thus remains in spite of a further rotation of the drive pulley at a distance F from the column 13 (FIG. 15) (position VI). The position of the drive pulley 6 and the swash plate 7 in the bottom dead center of the plunger 4, Fig. 11.

During the entire phase of engagement of the rollers 56, 57 in the slot recess 84, the roller 56 rolls downwardly on the running edge 85b during the downward stroke of the plunger 4. Between the roller 56 and the opposite edge 85a, a gap remains, so that the free rotation of the roller 56 about the axis 55 is not hindered.

In the above-described downward stroke of the plunger 4, the roller 57 rolls during the engagement phase on the running edge 86a without load or almost no load in the opposite direction to the roller 56 from.

During the return or upward stroke of the tappet 4, starting from the bottom dead center (UT) to the top dead center (TDC), the above-described processes turn directionally.

The conveyor finger 158 hooks in this case in an edge of a contact element or a transport opening in the contact element band and is gently, in particular jerk-free, accelerated by the step gear 5, as described above, and gently slowed until it reaches its foremost end in the conveying direction 14, in particular smoothly decelerated.

By moving the sliding block 96 in the slot 90, the total stroke of the carriage 10 can be predetermined and fixed by clamping. The setting of the target end position of the transporting finger 158 can be made roughly by shifting the transport finger carrier 147 with respect to the flange plate 143 and finely by means of the adjusting device 150.

If the delivery of the contact elements during the downward stroke of the plunger 4, so the coupling rod 11 can be attached to the second sliding block 97.

According to a further embodiment of the feeding device 1 according to the invention, the locking mechanism is arranged separately from the indexing gear 5, the locking element of the locking mechanism being e.g. is formed as a pair of locking fingers with two vertical locking fingers, which are respectively mounted above and below the swash plate 7 fixed to the plunger 4 and, for. the bearing plate 21 around or intervening in corresponding counter-locking elements, e.g. Locking holes or locking slots of the swash plate 7 engage when it is in one of their limit positions.

A feeding device according to the invention thus enables a precise positioning of the contact elements in the crimping tool. The form-fitting force-transmitting step transmission in both directions, which is also jerk-free, ie having a steady course of acceleration, configured, reliably ensures a smooth start and deceleration or decay of the transport movement of the contact elements. Thus, unwanted vibrations in the contact element band, which could have an imprecise positioning of the contact element in the crimping result, reliably avoided. In particular, this also contributes to the locking mechanism which locks the transport finger in its end positions outside its conveying or return stroke movement.

Claims (33)

1. Device for feeding contact elements into a crimping tool of a crimping press, comprising a carrier part (2) in which a plunger (4) is mounted such that it can be displaced in an operating direction (3), and a device (45, 47, 48, 6, 7, 11, 10) for converting the reciprocating movement of the plunger (4) into an oscillating transport movement with a delivery stroke and a return stroke of a transport finger (158), characterized in that the conversion device (45, 47, 48, 6, 7, 11, 10) has a stepping mechanism (5) with a drive mechanism element (6, 56, 57), a driven mechanism element (7) and a locking mechanism (60, 120, 121), the drive mechanism element (6, 56, 57) being coupled mechanically to the plunger (4) and engaging periodically with the driven mechanism element (7).
2. Device according to Claim 1, characterized in that the locking mechanism (60, 120, 121) has a locking element (60) and at least one matching locking element (120, 121), the locking element (60) engaging with the matching locking element (120, 121) in an anticyclic manner to the engagement of the mechanism elements (6, 7), locking the driven mechanism element (7), and the driven mechanism element (7) being coupled mechanically to the transport finger (158).
3. Device according to Claim 1 and/or 2, characterized in that the stepping mechanism (5) is configured to operate in a jolt-free manner.
4. Device according to one of Claims 1 to 3, characterized in that the drive element (6) is coupled to the plunger (4) via a rack and pinion mechanism (45, 47).
5. Device according to one of Claims 1 to 4, characterized in that the delivery finger (158) is part of a linearly displaceable transport slide (10), which is coupled to the driven element (7) via a coupling rod (11) in the manner of a crank mechanism, the stroke of the linearly displaceable transport slide (10) being adjustable.
6. Device according to one of Claims 1 to 5, characterized in that the stepping mechanism (5) has a rotatably mounted drive disc (6) with an eccentric (56, 57) and a pivoting disc (7) which is mounted such that it can pivot parallel to the drive disc (6) and has a slot cutout (84), the eccentric (56, 57) engaging periodically with the slot cutout (84).
7. Device according to one of Claims 1 to 6, characterized in that the locking mechanism (60, 120, 121) comprises a locking web (60) on the drive disc (6) and locking grooves (120, 121) in the pivoting disc (7), which are engaged when the eccentric (56, 57) is located outside the slot cutout (84).
8. Device according to one of Claims 1 to 7, characterized in that the transport finger (158) can be actuated in a delivery direction (14) of the contact elements during the operating stroke or during the return stroke of the plunger (4).
9. Device according to one of Claims 1 to 6, characterized in that the locking mechanism is arranged separately from the stepping mechanism (5) and, for example, has at least one locking pin fixed to the plunger and corresponding locking holes or locking slots in the pivoting disc (7), which are engaged when the eccentric (56, 57) is located outside the slot cutout.
10. Device according to one of Claims 6 to 9, characterized in that the eccentric (56, 57) comprises a first eccentrically positioned roller (56) as a running roller and a second eccentrically positioned roller (57) as a running roller, which are mounted such that they can rotate independently of each other about an eccentric axis of rotation (55) parallel to an axis of rotation (49) of the drive element (6).
11. Device according to one of Claims 1 to 10, characterized in that the carrier part (2) is formed in one piece and has a first higher column (13) and a second lower column (15) which is arranged downstream of the first higher column (13) in the delivery direction (14), the carrier part (2) with the second column (15) being seated on a baseplate (12), the first column (13) being seated on the end (17) of an outrigger web (16) that extends from the baseplate (12) in the direction opposite to the delivery direction (14), a vertical supporting cheek (18) extending between the first column (13) and the second column (15); projecting beyond the second column (15) at a distance from the outrigger web (16), so that a slot opening (19) bounded by the outrigger web (16), the columns (13, 15) and a lower edge (20) of the supporting cheek (18) is formed, a vertical bearing plate (21) being integrally moulded onto the supporting cheek (18) in one piece, downstream in the delivery direction (14) and projecting beyond the column (15) in the direction (14), the supporting cheek (18) and the bearing plate (21) having a transport side (22) facing the plunger (4) and the contact element tape to be transported and an opposite mechanism side (23), the bearing plate (21) being of thickened design on the transport side (22) opposite the supporting cheek (18), and the supporting cheek (18) and the bearing plate (21) being flush on the mechanism side, a grooved depression (24) with a cross section shaped like a flat rectangle being introduced on the transport side of the bearing plate (21), extending longitudinally over the entire bearing plate (21) in the operating direction (3) of the plunger (4) and its transverse extent in the delivery direction (14) being about ¾ of the bearing plate (21), so that bounding webs (25, 26) are formed on both longitudinal sides of the groove (24), a holding web (27, 28) being fixed to the bearing plate (21) on the transport side (22) of the bounding webs (25, 26), in each case parallel to the groove (24), the holding webs (27, 28) in each case projecting slightly beyond the groove (24) in the transverse direction of the groove (24), so that a guide groove (24a) with a T-shaped cross section is formed, a sliding plate (30) with a sliding face (31) facing the bottom of the T groove (24a) and a plunger side (32) facing the groove opening of the T groove (24a) being seated with a form fit in the groove (24a) but capable of being displaced axially in the operating direction (3) of the plunger (4), the plunger (4) being fixed on the plunger side (32) between the holding webs (27, 28), and having a driven side (35) pointing in the direction opposite to the delivery direction (14), a front side (36) pointing in the delivery direction (14), a side (37) pointing away from the carrier part (2), an upper actuating front side (38) and a crimping-tool underside (39), the actuating side (38) bearing a coupling piece (40) to connect and couple the plunger (4) to the operating punch of a crimping press, for example a hydraulic crimping press, and holding devices for an upper tool half of a crimping tool being fitted to the underside (39).
12. Device according to Claim 11, characterized in that, on the driven side (35) of the plunger (4), adjacent to the holding web (27), the rack (45) running parallel to the direction of the double arrow (3) is seated, and has a longitudinal extent which is preferably somewhat greater than the stroke of the plunger (4) between its top dead centre (OT) and its bottom dead centre (UT) and its teeth (46) point in the direction opposite to the delivery direction (14), the rack (45) constantly engaging with a gear (47), forming the rack and pinion mechanism (45, 47), the gear (47) being seated firmly on a shaft (48) so as to rotate with it, and the shaft (48) having the axis of rotation (49) as mid-axis, the axis of rotation (49) of the shaft (48) being at right angles to the operating direction of the plunger and at right angles to an operating direction (8) of the delivery finger (158), the shaft (48) reaching through the holding web (27) and the bearing plate (21) and being mounted there such that it can rotate in the direction of a double arrow (50), on the mechanism-side end of the shaft (48), preferably attached in one piece to the shaft (48), there being seated the circular disc-like drive disc (6) which has the axis of rotation (49) as mid-axis, the drive disc (6) having a radius (r) which is preferably greater than the radius of the rolling circle of the gear (47), the drive disc (6) having a first flat side (51) facing the shaft (48) and a second flat side (52) facing away from the shaft (48) and being seated with play in a cylindrical disc-like flat recess (53), corresponding to the dimensions of the drive disc (6), in the mechanism side (23) of the bearing plate (21), in such a way that the second flat side (52) comes to lie approximately flush with the mechanism side (23).
13. Device according to one of Claims 10 to 12, characterized in that, eccentrically at a distance (t < R) in the radial outer region of the drive disc (6), an axle pin (54) with the axis (55) as mid-axis extends at right angles from the flat side (52) of the drive disc (6), the axle pin (54) bearing the first cylindrical disc-like roller (56) adjacent to the flat side (52) and, arranged coaxially upstream of the first roller (56) on the mechanism side, bearing the identical cylindrical disc-like second roller (57).
14. Device according to one of Claims 10 to 13, characterized in that the roller (56) has a circumferential surface (58) and the roller (57) has a circumferential surface (59), the rollers (56, 57) having a radius (r) which is preferably about ¼ of the radius (R).
15. Device according to one of Claims 10 to 14, characterized in that the pivoting disc (7) has a thickness (D), and the rollers (56, 57) have a thickness which in each case is about half the thickness (D).
16. Device according to one of Claims 7 to 15, characterized in that the locking web (60) is approximately square in cross section and is shaped approximately like a circular arc in its longitudinal extent, and is integrally moulded onto the flat side (52) opposite the rollers (56, 57), the locking web (60) extending over an angular range ϕ symmetrical to an imaginary diameter (61) through the rotational centres of the drive disc (6) and the rollers (56, 57).
17. Device according to one of Claims 7 to 16, characterized in that the locking web (60) has a centre line (62) shaped like a circular arc with a radius (R₁ < r) and an inner flank (65), an outer flank (66), a first end (67) and a second end (68) and also an upper side (69), the flanks (65, 66) being designed tapered towards the ends (67, 68), in particular rounded running tangentially into the flanks (65, 66).
18. Device according to one of Claims 11 to 17, characterized in that the pivoting disc (7) on the mechanism side (23) of the bearing plate (21) is mounted at the same vertical height as the drive disc (6) such that it can pivot on an axle pin (70a) about an axis (70) parallel to the axis of rotation (49), the axis (70) being arranged downstream at a distance (L) in the delivery direction (14) of the axis of rotation (49), and the distance (L) being slightly greater than the radius (r) of the drive disc (6), the axle pin (70a) being held at one end in a hole in the bearing plate (21) and at the other end by a supporting bearing (71), the supporting bearing (71) having a supporting bearing block (72) which, downstream with respect to the axis (70), is fixed to the bearing plate (21) and, from the supporting bearing block (72) outwards, in the direction opposite to the delivery direction (14), parallel to and at a distance from the bearing plate (21), there extending a supporting bearing lug (73), in whose end region a bearing hole (74) for the axle pin (70a) is provided, the pivoting disc (7) being mounted such that it can pivot with a hole (75) on the axle pin (70a).
19. Device according to one of Claims 6 to 18, characterized in that the pivoting disc (7) has a planar first flat side (76) facing the bearing plate (21) and a second flat side (72) facing away from the bearing plate (21) and, from the hole (75) outwards, extends approximately symmetrically with respect to a plane (78) which is at right angles to the mechanism side (23), in the manner of a beak in the direction of the drive disc (6), the first flat side (76) of the pivoting disc covering the second flat side (52) of the drive disc (6), at least in some regions, the pivoting disc (7) having on both sides of the plane (78) and adjacent to the latter a first beak web (80) and a second beak web (81), the beak webs (80, 81) having beak web ends (82, 83) which, in a pivoted position of the pivoting disc (7), in which the axes (49) lie in the plane (78), come to lie-approximately in the region of the horizontal centre of the drive disc (6), the slot cutout (84) being designed with a U shape and running parallel to the plane (78) from the beak ends (82, 83) as far as shortly in front of the hole (75).
20. Device according to one of Claims 6 to 19, characterized in that the slot cutout (84) has, on the bearing plate side, a first pair of running edges (85) and, adjacent thereto, a second pair of running edges (86), the pairs of running edges (85, 86) each having opposite, parallel running edges (85a, 85b, 86a, 86b), the distance between the pairs of running edges (85a, 85b; and 86a, 86b) in each case being of the same size and, in terms of magnitude, being a little (X) greater than the diameter of the rollers (56, 57), the running edges (85a, 85b and 86a, 86b) in each case having a width of about half the thickness of the pivoting disc (7), the pairs of running edges (85, 86) being arranged to be offset slightly, in particular by the amount (X), in a direction transversely with respect to the plane (78), so that in each case a step (88) is formed between the running edges (85a, 86a; 85b, 86b) in each case on one side of the cutout (84), the distance between the running edge (85a) and the running edge (86b) and between the running edge (85b) and the running edge (86a) in each case corresponding to the diameter of the rollers (56, 57), so that the pair of rollers (56, 57) can be inserted without play into the slot cutout (84), the running edges (85a, 85b; 86a, 86b) having guide surfaces (85c, 86c) which widen the slot cutout (84) towards the respective beak web end (82) and (83), the guide surfaces (85c, 86c) being of convex configuration and in particular running tangentially into the respectively associated running edges (85a, 85b; 86a, 86b).
21. Device according to one of Claims 6 to 20, characterized in that the depth of the slot cutout (84) is bounded by a bottom bounding surface (89), the bottom bounding surface (89) being arranged in such a way that, in a position of the drive disc (6) and the pivoting disc (7) with respect to each other, in which the axis of rotation (55) of the rollers (56, 57) lies between the axes of rotation (49 and 70), in their plane, the circumferential surfaces (58, 59) are arranged at a short distance from the bottom bounding surface (89).
22. Device according to one of Claims 19 to 21, characterized in that the pivoting disc (7) has slotted cutouts (90, 91) which, starting from the plane of symmetry (78) and beginning on both sides, begin in an area between the bottom bounding surface (89) of the slot cutout (84) and the hole (75) and run out at an obtuse angle to the slot cutout (84), the slotted cutouts (90, 91) being designed to widen towards the flat side (76) on the bearing side, so that a circumferential stop step (92) is formed approximately in the area of the mid-plane of the pivoting disc (7), the second flat side (77) having a removed portion (93) of lower depth in the area of the slotted cutouts (90, 91), so that a supporting plane (95) and guide edges (94) are formed, the guide edges (94) respectively being spaced apart rectilinearly and running parallel to the slotted cutouts (90, 91) on their side facing the slot cutout (84), in each case a sliding block (96, 97) being seated in the slotted cutouts (90, 91), in the widened area thereof, such that it can be displaced with a form fit in the longitudinal direction, the said sliding block (96, 97) ending with the first flat side (76) and resting on the stop step (92), the sliding blocks (96, 97) each having threaded holes (98) in their longitudinal end regions, the mid-axes of said holes being at right angles to the mid-plane of the pivoting disc (7).
23. Device according to Claim 22, characterized in that retaining platelets (99, 100) are arranged on the supporting plane (95), communicating with the sliding blocks (96, 97), the said platelets resting on the guide edges and having in the end regions through-holes (101) which communicate with the threaded holes (98) in the sliding blocks (96, 97), a fixing screw (102) being screwed in through respectively the holes (98, 101) respectively closer to the plane (78), from the second flat side (77), in order to fix the retaining platelets (99, 100) with respect to the sliding blocks (96, 97).
24. Device according to either of Claims 22 and/or 23, characterized in that a first joint eye (110) can be fixed to the respective outer holes (98, 101) in the coupling rod (11), it being possible for the length of the attachment lever for the coupling rod (11) to be adjusted and fixed by displacing the sliding blocks (96, 97) with the retaining platelets (99, 100), together with the fixed joint eye (110) belonging to the coupling rod, with respect to the axis (70).
25. Device according to one of Claims 7 to 24, characterized in that the locking grooves (120, 121) are shaped like circular arcs and, at least in some regions, have the same cross section and the same radius as the locking web (60) of the drive disc (6), so that the locking web (60) fits with a form fit into each of the locking grooves (120, 121).
26. Device according to one of Claims 7 to 25, characterized in that the locking grooves (120, 121) in the first flat side (76) of the pivoting disc (7) are arranged in the area of the beak webs (80, 81), arranged upstream of the slotted cutouts (90, 91) in the direction of the beak ends (82, 83).
27. Device according to one of Claims 7 to 26, characterized in that the locking grooves (120, 121) run from a circumferential edge (123) of the pivoting disc (7) in the shape of a circular arc in the direction of the slot cutout (84), the locking grooves (120, 121) running as far as the slot cutout (84) if required, opening into the latter.
28. Device according to one of Claims 7 to 27, characterized in that the locking grooves (120, 121) are arranged in such a way that, in a first end position of the pivoting disc (7), the locking web (60) of the drive disc (6) can be inserted into the locking groove (121) as a result of rotation of the said drive disc (6) and, in a second end position of the pivoting disc (7), the locking web (60) can be inserted into the locking groove (120) with the end (67) in front as a result of rotation of the drive disc (6).
29. Device according to one of Claims 7 to 28, characterized in that the locking grooves (120, 121) are a matching locking element for the locking web (60), forming the locking mechanism with the latter.
30. Device according to one of Claims 7 to 29, characterized in that the locking grooves (120, 121) each have a first curved side surface (124), a second curved side surface (125).and a bottom surface (126) in each case, the curved side surfaces (124, 125) in each case being chamfered towards the circumferential edge (123) of the pivoting disc (7) in the opening area of the locking grooves (120, 121), in particular being designed to be widened tangentially in the shape of an arc, the curved side surfaces (124, 125) of the locking grooves (120, 121) within the tangentially arcuate widening having, at. least over a certain distance, for example about 4 mm, a spacing from one another which corresponds to the spacing of the flanks (65, 66) of the locking web (60), so that locking surfaces (124a, 125a) ,are formed, which ensure form-fitting guidance of the locking web (60), the curved side surfaces (124, 125) within the locking surfaces (124a, 125a) having a greater spacing from each other, so that the locking web can be inserted into this area with play.
31. Device according to one of Claims 11 to 30, characterized in that on the mechanism side (23) of the supporting cheek (18), in the direction of the double arrow (8) between the first column (13) and the second column (15), slightly above the lower edge (20), a guide rail (9) extends horizontally which, for example with screws (130) on the supporting cheek (18) and on its longitudinal edges (131), has channel-like guide grooves (132), the slide (10) being seated on the guide rail (9) such that it can be displaced axially in the direction of the double arrow (8) and having a slide sliding part (133) with longitudinal sliding webs (134), which are seated with a form fit in the guide grooves (132), a slide bracket (136) being fixed to an outer surface (135) of the slide sliding part (133), facing away from the guide rail (9), the said bracket (136) projecting vertically upwards beyond the slide sliding part (133), reaching as far as somewhat beyond the height of the axis (49) and having a coupling lug (137) which has a hole (138) in its upper end region, the hole (138) having its mid-axis at right angles on the mechanism side (23) and being used to fix a second joint eye (139) of the coupling rod (11) by means of a screw (40) and a nut (141), the supporting cheek (18) having an aperture (142) in the area of the screw connection (140, 141) in order to ensure easier access (140, 141).
32. Device according to Claim 31, characterized in that the slide bracket (136) reaches through the slot cutout (19) underneath the slide sliding part (133) and, on the transport side (22) of the supporting cheek (18), has a vertical flange plate (143) with a mounting surface (144), the mounting surface (144) having a large number of flutes (145) running vertically parallel and having a slot (146) extending horizontally, on the fluted mounting surface (144) there being seated a transport finger base carrier (147) which can be displaced in the direction of the double arrow (8) with respect to the flange plate (143) and can be fixed by screws (148) and which holds an adjusting device (150), it being possible for a transport finger carrier (152) to be adjusted finely with respect to the transport finger base carrier (157) in the direction of the double arrow (8) via the adjusting device (150), the transport finger carrier (152) having a bearing pin (54) pointing away horizontally from the supporting cheek (18) and a supporting strip (155) running at a distance underneath the pin (154), a transport finger holder (156) being mounted on the pin (154) such that it can be pivoted under spring load and the transport finger holder (156) projecting somewhat in the transport direction (14), so that its ability to pivot downwards is limited by the supporting strip (155), the transport finger (158) being seated on a side surface (157a) of the transport finger holder (156), the transport finger (158) having an upper edge (159), a ramp edge (160) rising from the front end of the upper edge (159) in the delivery direction (14) and having a vertical, front terminating edge (161), so that a sharp-pointed engagement corner (162) is formed, which can engage on edges of the contact elements or in predetermined recesses in the contact element tape, for example in the scrap web.
33. Device according to Claim 32, characterized in that the coupling rod (11) extends between the joint eyes (110 and 139), the coupling rod (11) being mounted on the pivoting disc (7) and on the coupling lug (137) in a cantilevered manner, rigidly and in each case such that it can pivot about the mid-axes of the joint eyes (110 and 139) and of the fixing screws (103, 140).