DE2036697A1 - Linking machine - Google Patents

Description

The invention relates to a linking machine with a continuously progressing fountain needle ring, which on its circumference with fountain needles with in the longitudinal direction running frames to accommodate the Kettelggut is equipped and with a central drive for a needle bar with a sewing needle used for stitch formation interacts with a gripper or a thread-guiding thread layer (stitch-forming system).

First, the structure and the method of operation, the known Linking machines explained:

The stitch formation tool (needle bar - sewing needle) is driven by a central drive point, the is located on the main machine shaft and consists of an eccentric connecting rod and push rod drive with a constant stroke consists. The sewing needle pierces from the inside to the outside or vice versa above each fountain needle the Kettelgut, i.e. the warp seam is once on the outside and on the other on the inside of the Kettel good educated.

Linking machines are also known (Italian

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Patent specification 757 021), which with a hook needle and work a thread layer, the hook needle is partially rotating around its longitudinal axis and stands out from the inside out. The method of working with a needle piercing from the outside in is also known. Of the The stroke of the needle bar or the hook needle is also constant in these cases.

The known linking machines also have a swivel drive that controls the following movement and the return movement controls the needle bar with respect to the fountain needle ring. The follow and return movement must be adapted to the rotation of the fountain needle ring and the stroke size of the needle bar and depending on the division of the fountain needle rim. The consequence and return movement is achieved by a pivot cam adapted to the aforementioned conditions. However, it is disadvantageous here that for each of the possible Divisions of the fountain needle ring (number of needles per inch) correspondingly changed swivel cam shapes required are. These swivel cams are usually designed as open cams that are inside or are spring tensioned on the outside.

In terms of efficient production, it is desirable to select the number of stitches in the linking machine as high as possible. However, this condition can only be met by strengthening the spring that tensions the open cam disks. This measure corresponds to a quadratic function of the one resulting from the speed of the control cams Mass acceleration and the moments resulting from the acceleration. The increase in the number of stitches under these conditions, however, are fine mechanical

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Devices, such as those also represented by linking machines, are subject to limits in terms of force and space.

From the above-mentioned basic physical laws it follows that normal, externally or internally strained, open cams that make up the swivel cams, reach their limit of use at a speed that corresponds to the number of stitches, between 1100 and 1300 rpm « In order to reach the upper limit of the stitches mentioned, however, a high-precision production is already necessary, which is correspondingly expensive, necessary.

The same conditions can be found in the known linking machines in the gripper or thread-laying kinematics. Here, the gripper or thread layer is via radial and / or axial curves with external or controlled internally tensioned follower rollers. For the upper limits of those specified in the previous paragraph The same laws apply to the tensioning of the springs and the production of these curves, so that here too these drives are subject to limits with regard to increasing the number of stitches.

The known linking machines have another major disadvantage because, due to the structural design mentioned in the introduction, they are only able to either to form the warp seam on the outside or on the inside of the opened warp item. What this disadvantage, in particular with regard to efficient production, is intended to be based on an example to be discribed:

It is assumed here that a cuff with a lapel part is to be chained to a cardigan or the like.

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The condition here is that the warp seam, be it on the cuff or on the lapel, is in the finished state Bear must remain invisible.

In the case of a linking machine that stings from the inside out, the kettler must first remove the item (cardigan) with the upper side facing the fountain needle ring, i.e. with the left side facing the fountain needles of the Open the linking machine. The cuff is then pushed open according to the same push-open principle to the first kink of the reverse part. Now a first linking process can follow. After that, that will Kettelgut removed from the fountain needle rim and in the next step the goods part and the reverse part reversed to ensure that the warp seam is invisible. This process follows a second warp seam, which takes place up to the next following kink of the reverse part. Thereupon the Kettelgut must be removed from the fountain needle ring again - according to the first step pushed open and ready-to-be-linked in a third linking process.

It is of course possible to keep the same type of push-up, but then one must be used for the second linking process Linking machine with a sewing needle that pierces from the outside to the inside or vice versa for the third linking process will. Another possibility is that the first linking process is carried out on a linking machine with a sewing needle sticking from the inside to the outside (the top of the item is on that of the fountain needle ring facing side pushed open) and the second on another linking machine - while maintaining of the belching process - with an inside out

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makes a piercing hook needle and finishes the third linking process on the first machine.

This previous working method is extremely time-consuming, so that the stitched goods are made correspondingly expensive got to.

The object of the invention is therefore to create a linking machine in which a continuous warp seam for certain linking work - depending on your wishes - alternately on the inside or outside of the once-opened { Kettelgutes can be formed.

This object is achieved according to the invention in that in a linking machine of the type mentioned above, a second stitch-forming system is provided, the stitch formation (looping) compared to the first stitch-forming system System takes place on different sides of the warp material, with the two stitch-forming systems alternately between a rest and a working position, in which it is connected to the central drive are arranged switchable.

A preferred embodiment is given according to the invention in that, in addition to a first pivot arm bearing to which a needle bar holder with a needle bar and a thread-guiding sewing needle is attached, another pivot arm bearing with a needle bar holder and a needle bar with a hook / or. Latch needle is provided, with either the gripper or the thread layer with their respective movement sequences being in a corresponding position to the respectively corresponding needle bar for the stitch formation, depending on the respective switching position. By using a sewing needle or

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Hook needle or latch needle can be used as desired Form a chain on the desired side of the goods · One Switching is facilitated by the fact that, according to the invention, the two stitch-forming systems are coupled to each other for switching · In addition, there are adjustment means for changing the stroke sizes provided according to the selection of stitch-forming systems

In a linking machine, from the central drive of which there is a drive connection to the needle bar via an eccentric, There is a connecting rod, thrust lever, thrust joint, thrust bearing and thrust fork, a slight coupling of the two Working systems to a drive system in that the push fork has a coupling point (slot) for receiving the drive connection for the needle bar and the connecting rod and the thrust lever on one Stellager are attached, which is slidably mounted on a shaft lying in the housing.

As an extension of the object of the invention, a drive system with a swivel drive for control is intended be created for the follow-up or return movement of the needle bar in relation to the fountain needle ring, which enables backlash-free positive control for the follow-up and return movement for the needle bar will. Such a system can generally also be used in linking machines of the type mentioned at the beginning and not limited to the two-system arrangement. The problem is solved by the fact that within of the slew drive, a kinematic chain fixed to the housing is switched on. A particularly advantageous one Execution is given here in that the kinematic chain contains four links. This results in

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the lowest total tolerance of the bearings · by the Application. The kinematic chain is a perfect mass balance for any speed and is associated with it an increase in the number of stitches is possible. In a further embodiment of the invention, it is provided here that to adapt the follow-up and return movement of the needle bar to any division of the needle roller assembly In addition to the kinematic chain, further gear elements are provided that have an adjustable rocker arm with continuously variable transmission ratio included.

Furthermore, the coupling of the kinematic chain is pivotably mounted on the eccentric via a needle bearing has two vertically offset pins. This makes it possible at the coupling of the kinematic Chain to articulate a plurality of links.

Furthermore, a linking machine is to be created by the invention, which with very high stitch numbers per Minute works at a low noise level. For linking machines with cam sets to control the Gripper or thread layer height and transverse movement (individual movements) this is achieved in that for control a pair of cams for each of the individual movements is provided whose curved paths are spatially offset from one another in accordance with the desired sequences of movements and are in control connection with at least two scanning elements for each pair of cams. Such a one The arrangement is basically applicable to all linking machines. Especially with two-system linking machines the use of kinematic chains as a forced control for gripper or thread layer movement would be one so great constructive effort mean that the

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Production is not cost-effective and it causes technical hindrances. Included the technical feasibility is basically jeioch to be answered in the affirmative. An easy switchability is given according to the invention that to control the Greiferbzw. Fadehlegerhöhenbewegung, as well as the transverse movement are each provided a corresponding common curve block is.

A positive control with switchover option is being developed for the two-system linking machine the embodiment according to the invention thereby errel cht that the honing control cam block from each a pair of control cams, consisting of a control and a catch cam, for the hook and thread layer height movement composed, and that the transverse control curve block in an analogous manner to the height control curve block composed of corresponding control and catch curves for the hook or thread layer transverse movement.

A common switchover of the looper or thread layer control system with the commissioning of the various chain systems is thereby made possible that preferred the elevation control cam block and the transverse control cam block between shift forks, which are fastened together on a push rod, stored and displaceable with this are arranged.

Furthermore, it is preferably provided for the positive adjustment of the scanning shafts to the pair of cams, that the angle levers are designed with three arms and are mounted on eccentric bolts. When training the angle lever made of plastic, the pretensioning spring otherwise required for rigid parts is advantageously dispensed with.

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The sewing or hook needle or latch needle of the two-system arrangement is arranged so as to engage below the fountain needle.

Further details of the invention are shown in an exemplary embodiment and with reference to the drawing are described in more detail below. It shows:

1 shows an overall view of a linking machine according to the invention in a simplified representation;

2 shows a central drive point according to the area | II from Fig. 1;

FIG. 3 the area III according to FIG. 1; FIG.

FIG. 4 shows the top view in the direction of arrow "A" according to FIG. 1;

FIG. 5 shows the various systems in FIG Work or rest position;

6 shows the area VI according to FIG. 4 in a schematic representation;

Fig. 7 shows a part of the machine upper arm according to the

Area VII from FIG. 1; 'm

Fig. 8 shows the front part of the machine upper arm according to the area VIII from FIG. 1;

9 shows the plan view of the upper arm according to FIGS. 1 and 8 in a simplified representation;

10 and 11 the cams for the gripper movement;

12 shows the basic movement path of the Fadenleejer a hook needle;

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13 shows the basic movement path of a gripper of a sewing needle.

The linking machine 1 shown in Fig. 1 is composed of the following main components:

Inside a cladding 2 there is a housing 3, of which only the one above a fountain needle ring 4 outward part is visible. The fountain needle ring 4 is equipped on its circumference with fountain needles 9, on which the goods to be linked are pushed. An upper arm housing 6 is arranged on the housing 3, the linking tools 7 (e.g. thread-guiding thread layer, gripper or the like), while the stitch-forming tools 8 (e.g. needle with needle bar) inside the cover 2 are arranged, as will be explained in more detail below. A machine stand 9 carries the linking machine 1 and their operating elements 10. The drive of the stitch-forming tools 8, the fountain needle ring 4 and the linking tools 7 are carried out by a drive motor 11 via a main machine shaft 12.

First, the central drive point according to area II from FIG. 1 is described.

The machine main shaft 12 (FIG. 2) is mounted inside the housing 3 via two self-aligning ball bearings 13 »14. Since the linking machine 1 has two stitch formation systems, for each stitch formation tool 8 (needle bar and needle) a pivot arm bearing 15 and 16 is provided, the pivot arm bearing 16 in a bore 17 of the pivot arm bearing 15 is centered and the pivot arm bearing 15 is rotatably mounted within a housing bore 18. To the

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Overhead pivot arm bearing 16 is followed by a helical gear 19 which is attached to the main machine shaft 12 is, from which the drive of the stitch forming tools 8 takes place centrally, as will be described in more detail below.

The swivel arm bearing 15 has a control cam 20, in which a roller 21, which is mounted on an eye 22, can run. The eye 22 is arranged on an actuator 23 · The purpose of the actuator 23 »its position is functionally related to which the control cam 20 is in connection with the description of Stitch forming tools 8 mentioned. There is also the control cam 20 and a further control level 24, which is on Swivel arm bearing 16 is arranged, a functional relationship.

Structure and drive of one of the stitch forming tools 8 (Fig. 3):

First of all, the functional relationship between the lifting movement - Swivel movement for a system (sewing needle - gripper system) described, with these relationships analogous to the next, with differences to be described existing system (hook needle - thread layer system) apply.

Lifting motion transmission:

The helical gear 19 (FIG. 3) mounted on the machine main shaft 12 drives via a further helical gear 25 an eccentric 26. The drive movement is via a bearing 27 forwarded to a connecting rod 28, which is fixed pivotably on a bearing 29 of the actuator 23 is. A push lever 30, which slides in a push joint 31, transmits this pivoting movement to a push bearing 32 which is connected to a push fork 33 (Fig. 5) · The push fork 33 is on one in the housing 3

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within a bore 34 clamped guide rod 35 slidably disposed. The (oscillating) back and forth going thrust movement is a needle bar 36, which is within a needle bar holder attached to the pivot arm bearing 15 37 is axially guided via the following connection:

The push fork 33 has a transverse to the longitudinal axis extending through slot 39 (Fig. 5), in which a push roller 40 is located, which is connected to a needle bar sleeve 41 via a bearing screw 42. Between of the needle bar sleeve 41 and the push roller 40 is a thrust washer 43 and a deep groove ball bearing 44 arranged. The latter rolls within an elongated hole 45 of a rod guide 46 during the stroke its front end is fastened to the needle bar holder 37 by means of two screws 47. Through this arrangement the transmission of the drive movement from the machine main shaft 12 to the needle bar 36 takes place with the least Frictional losses.

The sewing needle 49 attached to the front end of the needle bar 36 via a clamp connection 48 sticks during the linking process one after the other below the fountain needles 5. The fountain needles 5 are in a ring or in individual segments 50 anchored and are additionally supported by clamping plates 51. The drive of the wreath plate 52 takes place from helical gear 19 via its externally toothed ring gear 53 *

During the linking process, the needle bar 36 must go back and forth related stroke movement - list depending on the number of stitches in the machine. During the piercing of the sewing needle 49 into the Kettelgut, the needle bar 36 must rotate

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of the fountain needle ring 4, ie the needle bar 36 must execute a first pivoting movement (follow-up movement), the direction of which is predetermined by the direction of rotation of the fountain needle ring. If the sewing needle 49 is outside the fountain needle frame, the needle bar 36 executes a further, rapid pivoting movement which runs in the opposite direction to the previously mentioned follow-up movement. At the end of this pivoting movement, the sewing needle 49 is in its starting position, ie _{e in} front of the next following fountain needle 5. The actual linking process takes place in a manner known per se.

Swivel motion transmission:

The drive system for the swivel movement is based on 3 and 4 described. The helical gear 19 meshes, as already mentioned, with the helical gear 25, which is between the eccentric 26 and a driver 55 is mounted on a shaft 56. The shaft 56 is within a Bearing eye 57 of the housing 3 via a needle bearing 58 each rotatably mounted. At the end of the shaft 56 opposite the eccentric 26, a helical gear 59 is arranged, which is in drive connection with an underlying helical gear 60. The axial forces between the Helical gear 25 and the helical gear 59 are received by thrust ball bearings 61 and 62. The helical gear 60 is non-rotatably mounted on a further shaft 63 by a driver 64 which, like the shaft 56, is in bearing eyes 65 and 66 is stored. Another eccentric 67 is arranged at the end of the shaft 63 in the area VI, on which a coupling 68 is pivotably mounted via a needle bearing 69. This coupling 68 has two to each other vertically offset pins 70 and 71 (Fig. 3), of which

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der Zapfen.71 carries a slot nut 72, which within a guide track 73 of a pivot lever 74 slides

The pin 70 is mounted within a rocker 75, which is passed below the coupling 68 and the pivot lever 74 and on a set screw 76 with a pin 77 is pivotably mounted. The set screw 76 is arranged fixed to the housing in a bearing eye 78 «,

The pivot lever 74 is designed as an angle lever and around a pin 79 »the housing in a bearing eye 80. is held firmly, pivoted. The downwardly extending arm 81 of the pivot lever 74 (FIG. 3) has a Guide track 82, in which a bearing pin 83 engages in an eye 84 at the counter end of an adjusting rocker 85 is attached. At the upper end of the swing arm 85 there is another eye 86, in the bore 87 of which a joint piece 88 engages. This joint piece 88 is firmly connected to a thrust head 89, which via a spring-loaded control pin 90 with a in the Needle bar holder 37 screwed roller bolt 91 is in operative connection. Instead of the control pin 90 a different position securing and actuation can also be provided.

The four-link kinematic The chain consists of the housing 3 »eccentric 67» the coupling 68 and the rocker 75 (Fig. 6; area VI from Fig. 4), wherein the pivot lever 74 and the adjusting rocker 85 represent additional gear elements that are rotated by 90 ° are drawn. Within the adjusting rocker 85 (FIG. 3) there is an adjusting pin 99 T-nut 92, which is arranged so that it can be displaced in height with respect to the rocker arm 85. Of the

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Adjusting pin 93 can, in order to meet this condition, be moved into a bearing eye 94 fixed to the housing and is tightened by a nut 95 after adjustment.

The sequence of movements of this partial transmission (four-link kinematic chain, additional transmission elements) is as follows:

When rotating the eccentric 67 by 360 ° in the specified The direction of rotation (clockwise) is given to the thrust head 89 »starting from the starting position shown 90 ° issued a quick move to the left. This means that the needle bar 36 after the stitch has been formed quickly returns to its original position while pushing the thrust head over the remaining 270 ° range a slow movement to the right is given. The relatively large angular range of 270 ° is used Follow-up movement of the needle bar 36, since the needle 49 lies within the fountain needle frame during the forward and reverse movement must follow the movement of the fountain needle crown.

By adjusting the adjusting pin 93, the pivoting movement can be achieved by changing the transmission ratio can be varied, i.e. the follow-up and return movement can be infinitely variable according to any pitch of the fountain needle ring be adjusted.

Two-system design of the linking machine:

In order to meet the requirement with regard to the desired position of the warp seam, the needle bar holder 37 an additional similarly constructed needle bar holder 96 (FIGS. 4, 5) with a further needle bar

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assigned, at the front end of which a latch or hook needle is attached. The needle bar holder 96 is attached to the upper pivot channel 16 (FIG. 2). The needle bar holders 37 and 96 are connected via an arch element 98 (FIG. 4) to which an adjusting lever 99 is attached. When this control lever 99 is actuated while simultaneously releasing the spring-loaded control pin 90 (Fig. 3), which process can also be carried out by means of servo elements, the push roller 40 slides out of the slot 39 and interrupts the drive connection to the helical gear 19. The needle bar holder 96 can now be inserted into the Working position are given away, the drive of the needle bar 97 then taking place via the same drive connection described above. After pivoting, the control pin 90 automatically engages in the corresponding, identically designed roller bolt, while the stitch-forming tool that is not required. 8 is guided against a fixed stop 100 (or * 101 at opposite pivotal movement) "In order to prevent _s that the respective, is 8, the track-and-return movement of the stitch-forming tool 8 in the working position runs in the rest position stitch forming tool located, have the junctions 102 and 103 (Figure 4) of the arch element 98 with the respective needle bar holder 37 and 96 on a game.

For the functionality of this two-system linking machine, using a hook needle, are also The following requirements, each determined by the stitch-forming tool 8 in the working position will meet?

a) The strokes of the two needle bars 36 and 96 must have different lengths, which is due to the

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Conditions of stitch formation is determined and

b) the operation of the linking machine 1 must be operated by the gripper can be switched to thread layer operation or vice versa.

When using an appropriately designed latch needle, condition a) can be omitted

The condition mentioned under a) is solved as follows:

In Fig..4 the system "sewing needle - gripper" stands with long stroke in working position · If the adjusting lever 99 is now swiveled clockwise, the second lever is activated System "hook needle - thread layer" in working position, while the sewing needle system comes to rest against the fixed stop 100 (FIG. 5). Since both needle bar holders 37 and 96 each with a pivot bearing 15 and 16 are connected, they pivot by the same amount.

The roller 21 engaging in the control cam 20 (Fig. 2) moves the actuator 23 on one, mounted in a lower eye 104 and an upper eye 105 in the housing 3, inclined and torsion-proof shaft 106 upwards. Here, together with the actuator 23 the thrust lever 30 (Fig. 3) is moved upwards, so that when the needle bar is driven, the hook needle is a smaller stroke compared to that of the sewing needle. This A smaller stroke is necessary because otherwise there is a risk that the thread loop will fall behind when the hook needle returns the fountain needle ring 4 would slide out of the hook.

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In order to meet the requirement mentioned under b), an arrangement according to FIG. 7 or, 8, 9 is used. The upper arm housing 6 is placed on the upwardly projecting (FIG. 1) housing 3. In housing 3 and in the front Part of the upper arm housing 6 (Fig. 7) is the machine main shaft 12, which is upward via a Coupling 107 separated, continued by a splined shaft 108 · This splined shaft 108 is at one end in a lower deep groove ball bearing 109 and at the other end in an upper deep groove ball bearing 110, which is in a cover 111 is centered, rotatably mounted. To control the A honing control cam block is used by the gripper or thread layer movement 112 and a lateral control curve block 113 »the both are arranged on the spline shaft 108. The elevation control curve block 112 is made up of a height snap curve 114, as well as a height control curve 115 for the Thread layer 141 of the hook or latch needle and a Höhenf angkurve 116 and a height control curve 117 for the gripper 141 of the sewing needle 49 together. The lateral control curve block 113 is composed in an analogous manner of a transverse catch curve 118 and a transverse control curve 119 for the thread layer 141 and a transverse catch curve 120 as well a transverse control cam 121 for the gripper 141 together. The height snap curves 114, 116 and cross snap curves 118, are complementary curves to the corresponding height control and aileron control curves 115, 117 and 119 and 121, respectively.

To transfer the control movement to the gripper or Thread layers 141 serve three-armed angle levers 122, 123 mounted on eccentric bolts 124, 125, which preferably made of plastic, the angle lever 122 the height control cam block 112 and the bell crank 123 is assigned to the transverse control curve block 113.

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The angle levers 122, 123 each carry two cam rollers via roller bolts 125 at their front ends 126, 127, of which the first-mentioned on the height control curve 117 or transverse control curve 121 and the others Cam rollers 127 - correspondingly offset in height - rest on the height catch curve 116 or on the transverse catch curve 120

These relationships are shown in simplified form in FIG. 9, the curve control blocks 112 and 113 being circular are drawn. The third arm of the angle lever 122 or 123 (the latter is opposite the first in the same plane rotated around the central axis by 180 °) is connected to a joint head 128 and 129, in which Push rods 130 and 131 are attached. The push rod 130 transmits the height control movement via a further joint head 132 and a gripper lever 133 »the designed as an angle lever and in a bearing 134 (Fig. 8) is pivotable fixed to the housing. The gripper lever 133 transmits the control movement to a cylinder pin 135, which is pressed into a thrust head 136. The thrust head 136 is connected by a clamping sleeve 137 a gripper tube 138 connected, which is slidably mounted in a guide sleeve 139 and on the lower The end of the gripper or thread layer 141 carries by means of a clamping ring 140.

The gripper lever 133 thus transmits the from the push rod 130 executed control movement on the gripper or thread layer 141 and thereby generates a vertical movement these parts.

The push rod 131 stands over a further joint head 142 with a pivot fork 143, which is attached to the push head

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is attached, in drive connection. The tax movement the push rod 131 is thus noticeable through a partial rotation of the gripper tube 138 about its longitudinal axis.

FIGS. 10, 11 show the height control curves 116, 117 (Height catch and height control cam) for the gripper height movement and the transverse control cams 120, 121 (Siuerfang- and transverse control cam) for the gripper transverse movement. The corresponding control cams for the thread layer of the Hook needles are constructed in the same way "

The requirement mentioned under b) is achieved by moving the corresponding cam blocks 112, 113 on the spline shaft 108 reached, with the choice of the control cams (height and lateral control cams) and the corresponding Search curves for the thread layer or the gripper 141 the cam rollers 126, 127 rest.

Located between the two curve blocks 112 and 113 an upper and a lower switching device 144, 145, which are attached to a push rod 146 (Fig. 7). This runs parallel to the central axis of the machine main shaft 12 within the upper arm housing 6 or the housing 3 and has at its lower end (Fig. 2) a fork 147 in which a roller 148 is rotatably mounted which rests on the control level 24. When switching the systems, as before using the needle bar switch described, the upper gchwenkarmlager 16 is also pivoted and the push rod 146 with the shift forks 144, 145 and the two cam blocks 112, 113 shifts due to their own weight and the slope of the control plane 24 downwards, so that the elevation or transverse control curves and the corresponding

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Catch curves for the thread layer on the cam rollers 126, .127 are present.

Before switching over the systems, the curve blocks 112, 113 must be set to a reference diameter (FIGS. 10, 11, dash-dotted lines shown) are brought into their zero position · This setting is carried out automatically by the Positioning and stopping the machine.

The superimposed movement of the Transverse and height control for the thread layer 141 described. The path of movement of the thread layer runs essentially circular with a pause point "V. During this period the thread layer stands still, the The loop is inserted and the hook needle runs back out of the frame. The retention period ends when the The needle is again at its foremost reversal point. The thread layer 141 then rotates further and lays a new loop in the hook of the needle.

The path of movement of the gripper 141 (FIG. 13) runs from the rightmost rest position to the left, the gripper 141 picks up the thread loop. This The process is polluted at the extreme left turning point. The gripper 141 then descends, i.e. a downward movement to the lowest point of reversal. this has With the single-thread gripper, there is no chain technology Meaning »With the two-thread gripper, on the other hand, the needle pierces the formed one during this process Thread triangle · From the lowest reversal point, the movement runs to the right to the extreme right reversal point thrown from the gripper "

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As a functional description, the chaining of a cuff and a lapel piece, a.B. on a cardigan. The prerequisite for this stitching is that the stitching of the finished cardigan is not visible on the wearer side.

For this purpose, the front of the cardigan is pushed onto the fountain needles 5 of the fountain needle ring 4. Then the cuff and the lapel part are pushed open over their entire length. So that the warp seam up remains invisible to the first kink on the reverse part, the warp seam must first be formed with the "hook needle thread layer" system. Then the last loop of the seam locked and the machine switched to the "sewing needle - gripper" system, whereby this switchover takes a few seconds. Then the reverse part is linked up to the next kink point with the sewing needle, starting with the last stitch point formed by the hook needle. In the further process, the last chain is locked again, - Switch to the "hook needle - thread layer" system and the linking process can be ended

All work processes can be carried out with a very high number of stitches and are therefore very economical of the chain.

A system reversal is possible in such a way that, contrary to the described design, which pierces from the inside to the outside, with both »systems piercing from the outside to the inside, switchable can be worked. The latter version, however, requires a larger construction Expenditure.

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Claims (1)

Claims 1. Linking machine with a continuously advancing ring of fontura needles attached to its circumference with fontura needles is equipped with frames running in the longitudinal direction for receiving the goods to be linked and with a central drive for a needle bar with a sewing needle, which is used for stitch formation with a hook or a thread-guiding thread layer (stitch-forming system) interacts, characterized, that a second stitch-forming system (97, needle 141) is provided whose stitch formation (looping) compared to the first stitch-forming system (36, 49, 141) takes place on different sides of the warp item, the two stitch-forming systems (97, needle 141 or 36, 49, 141) alternating between a resting and a working position in which they are connected to the central drive (11, 12, 19, 25), switchable are arranged. 2. linking machine according to claim 1, characterized in that in addition to a first pivot arm bearing (15) »on the one The needle bar holder (37) is attached to a needle bar (36) and a thread-guiding sewing needle (49) further swivel arm bearing (16) with a needle bar holder (96) and a needle bar (97) with a hook / or latch needle is provided, depending on the respective switching position either the gripper or the thread layer (141) with their respective movement sequences in a corresponding position but in each case corresponding The needle bar (36, 97) stand for the stitch formation. 10 98 85/0961 - 24 - 3. linking machine according to claims 1 and 2, characterized in that that the two stitch-forming systems (97, needle 141 or 36, 49, 141) switch with one another are coupled. 4. Linking machine according to claim 1, characterized in that adjusting means (15, 20, 21, 23, 29, 30) for the change the stroke sizes according to the selection of the stitch-forming systems (97, needle 141 or 36, 49, 141) are. 5. linking machine according to claims 1 and 4, wherein from the central drive from a drive connection to Needle bar via an eccentric, a connecting rod, a thrust lever, a thrust joint, a thrust bearing and a Push fork consists, characterized in that the push fork (33) has a coupling point (slot 39) to accommodate the drive connection (40, 42, 43 »44, 41) for the needle bar (36) and fastened the connecting rod (28) and the thrust lever (30) on an adjusting bearing (23) which is slidably mounted on a shaft (106) lying in the housing (3) « 6β linking machine with a slewing drive for controlling the follow-up or return movement of the needle bar with respect to the fountain needle ring, in particular after Claim 1, characterized in that within the swivel drive a fixed to the housing kinematic chain (3, 67, 68, 75) is switched on. 109885/0961 7. linking machine according to claim 6, characterized in that that the kinematic chain (3, 67, 68, 75) contains four links, 8 «linking machine according to claims 6 and 7, characterized in that that in addition to the kinematic chain (3, 67, 68, 75) further gear elements (85, 92, 93, 88, 89) are provided which have an adjustable rocker arm (85) with a continuously variable »transmission ratio contain. 9 linking machine according to at least one of claims 6 " to 8, characterized in that the coupling (68) of the kinematic chain (3 * 67, 68, 75) on the eccentric (67) is pivotably mounted via a needle bearing (69) and has two vertically offset pins (70, 71). 10. linking machine, in particular according to claim 1, with cam sets for controlling the gripper or Thread-laying vertical and transverse movement (individual movements), characterized in that that to control each of the individual movements Pair of cams (114 - 115, 116 - 117, 118 - 119, | 120 - 121) is provided, their cam tracks accordingly the desired motion sequences are spatially offset from one another and for each pair of cams (114 115, 116 - 117, 118 - 119, 120 - 121) are in control connection with at least two scanning elements (126, 127) 11. linking machine according to claim 10, characterized in that for controlling the gripper or thread layer height movement and a corresponding common cam block (112, 113) is provided in each case for the transverse movement. 10S88S / 0961 - 26 - 203669 12. linking machine according to claims 10 and 11, characterized characterized in that the elevation control cam block (112) each from a pair of control cams (114 - 115 »116 117), consisting of a control and a catch curve for the hook and thread layer height movement, and that the lateral control cam block (113) in a manner analogous to the height control curve block (112) composed of corresponding control and catch curves for the looper or thread layer transverse movement, 13 * linking machine according to at least one of the claims 1 to 12, characterized in that the height control cam block (112) and the transverse control cam block (113) between shift forks (i44, 145) »which are connected to one Push rod (146) are attached, mounted and arranged to be displaceable with this. 14. Linking machine according to one of the preceding claims 1 to 13 »characterized in that the angle lever (122, 123) designed with three arms and on eccentric bolts (124, 125) are stored. 15 linking machine according to claim 14, characterized in that that the angle levers (122, 123) are made of plastic. 16. Linking machine according to at least one of the claims 1 to 15, characterized in that the maneuvering needle (49) arranged engaging below the fountain needles (5) 109885/0981