JPH03202096A - Sewing machine - Google Patents

Abstract

PURPOSE: To reduce the inertia moment of a rotary housing and to accelerate the possible work speed of a sewing machine by separating a needle bar driving device and a needle thread take-up driving device and crossing the rotation axis of the rotary housing with a needle bar axis. CONSTITUTION: A swing driving device for a swing frame 67 and the needle bar driving device 87 for a needle bar are positioned on one side 91 of the swing frame 67, that is on one side of the rotary housing 28. A needle thread take-up 92 including the needle thread take-up driving device 93 is provided on the other side of the swing frame 67, that is on the side 94 facing the one side 91 of the rotary housing 28. The needle thread take-up 92 and the needle thread take-up driving device 93 are disposed at the lower part of an auxiliary shaft 55. In such a manner, the structure height of the rotary housing 28 is reduced. To the contrary, a shaft 82 is disposed at the upper part of the auxiliary shaft 55, and the needle bar driving device 87 on one hand and the swing driving device on the other are relatively highly positioned upwards inside the rotary housing 28 by a well-known method. It is also useful for the reduction of the structure height.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Field) The present invention relates to a sewing machine according to the generic concept of claim 1.

(Prior Art) This type of sewing machine is generally known. In such sewing machines, the needle bar drive on the one hand and the thread take-up drive on the other hand are driven directly by an arm shaft arranged in the upper arm of the sewing head.

This type of sewing machine is described in West German patent specification 341117, for example.
7A1 (corresponding to US Pat. No. 4,553,489). In such a sewing machine, the sewing head has a so-called rotating housing, and a needle bar drive device including a needle bar and a balance drive device including a balance are disposed in the rotating housing. Such a sewing head with a rotating housing allows for so-called tangential sewing.
Mainly used in automatic sewing machines with biaxial guidance of the sewing material. In this known sewing machine with a rotary housing, the take-up drive and the needle bar drive are also driven directly by a shaft arranged in the crank housing.

In all the sewing machines mentioned above, the take-up drive with the take-up thread and the needle bar drive are located on one side of the needle bar, which in the last mentioned sewing machines leads to a significant narrowing of the design possibilities and to the rotating In a machine equipped with a housing, the moment of inertia of the rotating housing increases.

German Patent Specification No. 1158800B deals with an automatic sewing machine equipped with a feed device for generating a relative movement in two axes between the sewing product and the sewing head, in which case a rotary housing is supported on the sewing head. A needle bar supporting the needles is supported in the rotating housing so as to be movable up and down by a crank transmission driven by a main drive shaft of the sewing machine. The rotating housing is rotatable about the needle axis and is provided with a balance drive. Furthermore, a needle feed movement is provided.

The rotary housing and the looper support are driven by a servo motor, which is controlled by a scanning body which is guided along a curve corresponding to the desired sewing curve. The needle feed movement is carried out by the needle bar guide being supported by the frame together with the presser foot and looper support attached to the needle bar, and these are controlled by an eccentric drive device that allows the sewing head to move in the direction of movement relative to the fixed sewing product. It is possible to move in the opposite direction. For this purpose, the shaft and gear wheels for the needle bar drive and the looper drive are designed to be movable in the axial direction. The rotary housing is provided with a balance and a balance link, the drive of which is structurally impracticable due to a laterally movable frame with needle bar guide and looper bearing and is therefore not disclosed. do not have.

OBJECT OF THE INVENTION The present invention provides a sewing machine of the configuration mentioned at the outset in such a way that a large degree of structural freedom is achieved with respect to the form and arrangement of the needle bar drive on the one hand and of the thread take-up drive on the other hand. Use it as the basis of the assignment.

(Means for Solving the Problem) This problem is solved according to the present invention by the feature of claim 1. In conventional sewing machines, the needle bar drive and the thread take-up drive are separated, so that the thread take-up can be arranged with special freedom of operation. In sewing machines with a rotary housing, the moment of inertia of the rotary housing is thus reduced at the same time and the possible working speed of the sewing machine is thereby increased, since the axis of rotation of the rotary housing intersects the axis of the needle bar. In particular, the solution according to the invention enables the configuration according to claim 2 and the configuration according to claim 3, i.e. the balance together with the balance drive to form a unit or to be assembled as a whole as a unit.

Furthermore, the design according to the invention makes possible a design according to claim 6, whereby a change in the phase position of the needle bar relative to the balance can be achieved.

In a preferred embodiment, the shaft and the separate shaft are integrally connected to each other. However, instead of claim 8 as described in claim 9, a so-called electrical shaft can be provided for the driving connection of the shaft and a separate shaft. A simple configuration for this purpose is claimed in claim 1.
0, in particular the embodiment according to claim 11 makes it possible to achieve a change in the phase of the needle bar relative to the take-up and in fine steps and continuously, with the change in the phase position also being dependent on the sewing cycle. It will be done.

Embodiment The automatic sewing machine shown has a frame 2, which consists of a middle part 2 and two side parts 3 and 4. A sewing head 5, whose base plate 6 is fixed on the central part 2, is arranged on the central part of the pedestal 1. Furthermore, the sewing head 5 has an upright portion 7 projecting high above the base plate 1, from which an upper arm 8 extends above and parallel to the base plate 6.
stands out. A workpiece holder 10 is provided in the region of the stitch-forming tool according to the extent of the base plate 6 and the free ends of the arms 8. The sewing product holder is movable in two coordinate directions, namely in the mutually orthogonal y-direction and in the x-direction. For this purpose, the part holder 10 is mounted on an xy carriage system. This system is
It has a y-carriage 11 which is supported and guided on a carriage 12 and is movable in the y-direction relative thereto and directly supports the sewing product holder 10. The X carriage 12 is movable in the X direction with respect to the pedestal 1. y carriage 1
1 and the sewing product holder 10 are thereby both movable relative to the pedestal 1 in the X and Y directions.

The X-carriage 12 is fixedly attached to the pedestal 1 and movably disposed on two mutually parallel guide rods 13. For driving the X-carriage, a drive motor 14 is provided on the side part 3 shown on the left in FIG. 1, which drives the upper X-carriage 2 via a toothed belt transmission W15.

A guide rod 16 is mounted on the X carriage, and a Y carriage 11 is disposed on the guide rod so as to be movable in the y direction. The drive of the y-carriage 11 takes place via a drive motor 17 which drives a shaft 18 which is supported on both sides 3 and 4 of the frame 1. Two toothed belt transmissions 19.19'' are driven by the shaft 18. These toothed belt transmissions 19.19'' are connected to a guide rail 20 pointing in the X direction, which in turn has a thrust bearing 21. Guide rod 22. by .21°.
22", and the guide rod is movable on y
It extends in the direction and is mounted on the side parts 3 and 4 of the pedestal l. The guide rail 20 engages in a matched guide groove 23 of the Y-carriage 11. The y-carriage 11 in the y-direction is driven by the guide rail 20 in the y-direction.
A tilt-free drive is achieved. A movement of the y-carriage 11 in the X-direction together with the X-carriage 12 is immediately possible, since the guide rail 20 runs absolutely parallel to the guide rail 13, ie in the X-direction.

The drive motors 14,17 are step motors or direct current motors with a position feedback control for very precisely programmed drive of the X-carriage 12, the Y-carriage 11 and thus of the sewing material holder in the x-y direction. Control unit for program controlled drive
The entry 24 has a receptacle for a program carrier 25 . A sewing item 26 is held in the sewing item holder 10,
Stitches 27 are formed on the sewing product by the stitch forming tool 9.

The rotating housing 28 is located on the lower side of the free end of the arm 8! 2
It is rotatably supported around 9.

A needle 30 concentric with this axis 29 and a needle bar 3 supporting it
1 is also provided. A base plate 6 is also formed as a housing below the rotary housing 28 and concentrically with the axis 29.
A looper support 32 is supported on the top, and the looper support can be rotated through the same angle as the rotary housing 28 . The pivoting drive of the rotary housing 28 and the looper bearing 32 is provided by a servo shaft 3 supported in the upright part 7 parallel to the axis 29.
3 via a belt transmission 34,35 with rotating housing. A belt transmission 34 with a rotary housing in the 7-m 8 drives the rotary housing 28 via a shaft 36 concentric with the axis 29. A lower toothed belt drive 35 on the base plate 6 drives the looper bearing 32 via a hollow shaft 37 . Since both toothed belt transmissions 34, 35 have the same reduction ratio, the rotary housing 28 and the looper support 32 are each driven to rotate at the same rotation angle.

The driving of the needle bar 31 together with the needle 30 and the driving of the looper 38 in the looper bearing 32 takes place by a common main drive shaft 39 via a toothed belt transmission 40,41.

The upper toothed belt transmission 40 attached to the arm 8 ends in a double toothed belt 742, which is connected to the shaft 36 concentrically with respect to the axis 29. A lower toothed pulley gear 41 on the base plate 6 drives a looper bearing shaft 43 on the hollow shaft 37 .

The main drive shaft 39 is driven from a main drive motor 44 mounted on the upright part 7 via a toothed belt transmission 45 . The drive of the servo shaft 33 takes place via a servo motor 46 which is arranged in the housing-shaped plate 6 and a transmission 47 following this.

The sewing machines mentioned so far are, for example, West German patent specification 3632046AI (US patent specification 478732).
No. 6), to which reference is made in order to avoid repetition. The double toothed pulley 42 includes, in addition to a toothed pulley 48 attached to the toothed belt transmission 40, a large force pulley 49 which is rotatably fixed thereto and is formed as a toothed pulley. This drives an output pulley 51 on the rotary housing 28 via the toothed heald 50, which is also designed as a toothed pulley and is supported on the rotary housing 28 and parallel to the axis 29. It is rotatably coupled to the shaft 52. The input pulley 49, the toothed belt 50 and the output IJ 51 form a partial transmission 53. The reduction ratio 11 of this partial transmission 53 is smaller than l, corresponding to the diameter d49 of the manual pulley 49 and the diameter d51 of the toothed pulley 51, because the diameter d51 of the toothed pulley 51 is the diameter d49 of the input pulley 49. This is because it is smaller than . This reduction ratio 11 is 1l
=d51/d49<1. One partial transmission 53
Since is formed by a toothed belt transmission, this also corresponds to the ratio of the teeth 54 shown in FIG. 4 only as input pulley 49 of the corresponding toothed boot. The ratio of the number z51 of teeth 54 on the output pulley 51 to the number z49 of teeth 54 on the input pulley 49 is determined in the same way as 1l=z51/Z4
9〈1.

An auxiliary shaft 55 is rotatably supported in the rotary housing 28 , the axis 56 of which is perpendicular to a plane 58 that includes the axis 29 and the axis 57 of the shaft 52 .
intersects with 7. A further input gear 60 having teeth 59 and in the form of a bevel gear is mounted in a rotationally fixed manner on the shaft 52, the input gear being connected in a rotationally fixed manner to the auxiliary shaft 55;
It meshes with another output gear 62 which likewise has teeth 61 and is formed as a separate bevel gear. The input gear 60 and the output gear 62 form a 20-part transmission 63. As can be seen from FIG. 5, the diameter d60 of the input gear 60 is smaller than the diameter d62 of the output gear 62. The same thing applies to the tooth 6 of the output gear 62.
The number of teeth 59 of the human gear 60 relative to the number of 1s z62 z60
This leads to the ratio of

Here, the reduction ratio 12 of the 26-part transmission 63 is 12=d
62/d60=z62/z60>1. Full speed ratio 11
xi2=l. The auxiliary shaft 55 is driven at the same rotation angle as the input gear 49. For example i 1 = z 51
/z49=22/33=2/3, then 12=1.5 is satisfied. This arrangement brings the axes 57 and 29 relatively close together, ie the structural depth of the rotary housing in the direction of the plane 58 can be made particularly small. The speed ratio is 0.5<il<0.8
and correspondingly 2>12>1.25.

The auxiliary shaft 55 drives a toothed booby +J 64 that is non-rotatably coupled to the auxiliary shaft, and the toothed pulley 66 of the needle bar driving device is driven from the toothed pulley via a toothed belt 65. The speed ratio of the toothed pulleys 64 and 66 of the needle bar drive device is 1.

The needle bar 31 is mounted so as to be longitudinally movable in a wobble frame 67 around a wobble bearing 68 in the upper region of the rotary housing 28 along an axis 6 perpendicular to the plane 58.
It is possible to swing around 9. Shaking frame 67 and therefore needle bar 3
1 is pivotable about an axis 69 in or parallel to the plane 58, for which purpose a correspondingly sized recess 70 is provided in the underside of the rotary housing 28. A presser rod 71 equipped with a presser foot 72 is disposed on the swing frame 67 in a conventional manner, although the method of operation thereof is not shown.

The swinging frame (swinging frame) 67 is swung by a swinging (swinging) drive device 73. The swinging frame has an eccentric body 74 arranged on the auxiliary shaft 55, the eccentric body being connected to a tension rod 75.
It is connected to an angle lever 77 via a joint 76. This angle lever 77 is connected to the rotating housing 2.
It is supported by a fixed position bearing 78 in 8. A tension rod 79 is pivotally supported at the other end of the angle lever 77 by a joint 80, and the tension rod is pivotally supported by the swing frame 67 by a joint 81. Auxiliary shaft 5
During each rotation of 5, the swing frame 67 swings back and forth once.

The needle bar drive toothed pulley 66 is mounted on a shaft 82 which is rotatably supported within a flange bearing housing 85 by means of a needle bearing 83 and a ball bearing 84.

The flange bearing housing is secured within the rotating housing 28 by springs 85a.

A crank 86 of a needle bar drive device 87 is rotatably attached to the end of a shaft 82 located within the rotating housing 28, and a crank rod 88 is pivotally supported on the crank by a crank joint 89. crank rod 8
The other end of 8 is pivotally supported on the needle bar 31 by a needle bar joint 90.

To this end, with each rotation of the auxiliary shaft 55, the needle bar 31 carries out an upward and downward movement.

In particular, as can be seen from FIG.
It is located inside. The swing drive 73 for the swing frame 67 and the needle bar drive 87 for the needle bar are located on one side 91 of the swing frame 67 and thus on one side of the rotary housing 28 . The balance 92 including the balance drive 93 is connected to the other side of the wobble frame 67 and thus to the rotary housing 28.
on one side 91 and the opposite side 94 of.

On the auxiliary shaft 55 on the other side 94 there is a toothed boot IJ which drives in a one-to-one ratio a toothed pulley 97 which is also rotatably supported in the rotary housing by means of a toothed belt 96.
95 is attached non-rotatably. This toothed pulley 97 is rotatably mounted on a shaft 98 supported in the rotary housing 28, and a crank 98 is further mounted on the shaft.
9 is attached. A crank 92 formed as a balance is pivotally supported on a crank pin 100 of a crank 99. A balance link 102 is pivotally supported in the center of the balance 92 by a joint 101, and the balance link is supported in a fixed position in the rotating housing by a bearing 103. This bearing 103 is mounted in a flange bearing housing 104 for the shaft 98 and is fixed to the rotary housing 28 by a bearing spring 104. This causes the balance drive device 93 to
2 can be assembled or disassembled as an integral structure with the flange bearing housing 104.

The said arrangement of the crank 99 of the balance 92, the balance link 104 and the flange bearing 104 forms a four-bar rotation chain. The thread take-up 92 has a needle thread hole 106 for the needle thread 107.
Rotating housing 2 with its free end 105 formed with
8 through the extraction portion 108 and protrudes outward. During one rotation of the auxiliary shaft 55, an up-and-down swinging motion is performed that unwinds the needle thread 107 for the needle 30. Balance 92 is swung in a plane parallel to plane 58. The needle thread 107 is pulled out from a needle thread roll 107a disposed on the arm 8.

As can be seen from FIG. 7, the balance 92 and the balance drive device 93 are arranged below the auxiliary shaft 55. The structural height of the rotating housing 28 is thus reduced. In contrast, the shaft 82 is arranged above the auxiliary shaft 55, and in a manner known per se the needle bar drive 87 on the one hand and the oscillating drive 73 on the other hand move upwardly in the rotary housing 28. It is located relatively high. This also helps reduce the structure height.

The rotary housing 28 is provided with removable portions 1109 and 110 shown by dotted lines in FIG. 3 on both sides thereof.
The lid is specially fitted with a toothed belt transmission device 64.65.6 on the one hand.
6 and on the other hand toothed belt transmission 95.96.9
Cover 7. Pull-out part 10 for balance link 92
8 and located between the sides 91 and 94 is a similarly removable lid 11 on the end face 111 of the rotary housing 28.
2 is provided.

The embodiment shown in FIGS. 9-13 shows a sewing head 120 for double chainstitch ξ-thin, which in a conventional manner connects a substrate 121 formed in the form of a housing with a conventional lower stitch formation. an upper arm 12, also formed like a housing, connected thereto on the tool and upright part 122;
It has 3.

A housing-shaped arm 123 has an upper removable lid 124 and a similarly removable end lid 1.
It has 25.

An arm shaft 126 is rotatably supported in the arm 123 in a bearing 127128. A handle 129 and a drive device toothed pulley 130 are rotationally fixedly attached to the drive device via a motor (not shown) at the lower end attached to the upright portion 122.

A needle bar 131 is mounted vertically movably in an upper needle bar guide bearing 132 and a lower needle bar guide bearing 133 in the end face area of the arm 123. Needle bar 131 has a needle 134 at its lower end. A needle bar drive device 135 serves to drive the needle bar 131 up and down. The needle bar drive device is an arm shaft 126
having a crank 136 attached to an adjacent end of the
A crank rod 137 is pivotally supported on the crank by a crank joint 138. crank rod 13
The other end of 7 is pivotally supported on the needle bar 131 by a needle bar joint 139. During each rotation of the arm shaft 126, the needle bar 13
1 performs an ascending and descending movement.

As shown in FIG. 11, in addition to the needle bar 131, a conventional presser device 140 includes a presser foot 141 that surrounds the needle 134.

An auxiliary shaft 142 is rotatably and axially movably supported on the arm 123 in bearings 143, 144, 145. The auxiliary shaft 142 is arranged parallel to the arm shaft 126. A toothed pulley 146 is mounted on an auxiliary shaft 142, covered by a lid 125 along the end of the arm 123, and the toothed pulley controls another toothed pulley 148 via a toothed belt 147. l vs l
Drive with. Both toothed pulleys 146 , 148 and the toothed belt 147 form a toothed belt drive 149 . This toothed belt drive 149 serves for driving a balance drive 150 . The balance drive device is rotatably supported by the arm 123 and has a shaft 151 that is rotatably connected to the toothed pulley 148, and a crank 152 is attached to the shaft. A balance 154 is pivotally supported on a crank pin 153 of this crank 152. A balance link 156 is pivotally supported at the center of this balance 154 by a joint 155, and the balance link is further supported by a bearing 15.
7 in a fixed position on the arm 123.

For example, this bearing 157 is attached to a flange bearing housing 158 of the shaft 151, and the flange housing is fixed to the arm 123 by screws 158a. 1st
As shown in FIGS. 2 and 13, a balance drive device 150
is very similar to the toothed heald drive 149, which is provided in the embodiment according to FIGS. 1 to 8. Here again, the balance drive device 150 is connected to the balance 1.
54 and flange bearing housing 158 to form an integral structural unit.

The thread take-up 154 projects outwardly with its free end 159 in which a needle thread hole 160 for a needle thread 161 is formed.

When the auxiliary shaft 142 rotates, the thread take-up 154 performs an up-and-down rocking motion that sends out the needle thread 161 to the needle 134.

The drive of the auxiliary shaft 142 and thus of the balance drive 150 takes place via a regulating transmission 162 . The adjustment transmission has a shift gear 163 on the arm shaft 126 which is rotationally fixed by a groove-fitting spring connection 162a but movable in the longitudinal direction of the arm shaft 126. Set the shift gear 164
meshes with a long drive gear 165 rotationally fixedly coupled on the auxiliary shaft 142. The shift gear 163 has a groove 166
A switching fork 167 is engaged with the groove. The switching fork is connected to a switching rod 168 which is movably guided in the arm 123 and into which a switching drive 169, designed as a linear drive, is engaged by a joint 170. The switching drive unit W169 is designed as a piston cylinder drive unit capable of applying air pressure, the cylinder 171 of which is pivotally supported on the arm 123 and the piston rod 172 of the switching drive unit W169.
is connected to joint 170. Compressed air connection pipe 1
Upon application of compressed air via 73, the piston rod 172 moves to its end position, in which position the switching fork 167
and the shift gear 163 are in the position shown by the solid line on the left in FIGS. 9 and 10. This position is the first switching position 174
It is.

When the cylinder 171 is energized with compressed air via another compressed air connection pipe 175, the piston rod 172 and with it the switching fork 167 and with it the shift gear 163 move into the second position indicated by the dashed line in FIG. Move to switching position. Between the two switching positions 174 and 176 there is a switching stroke a. The length of the non-drive gear 165 is such that the shift gear 165 meshes with the shift gear 163 in both switching positions 174 and 176.

The switching drive 169 can also be designed as a multiposition cylinder with a binary control, and a large number of switching positions are possible.

As shown in FIGS. 9 and 10, the shift gear 163 on the one hand and the non-drive gear 165 on the other hand are each provided with diagonal teeth 177, 178, so that from the first switching position 174 During the movement to the second switching position 176 and vice versa, the non-drive gear 165 is rotated relative to the arm axis 126. Switching stroke length a
and the angle of inclination of the diagonal teeth 177 and 178.
The angle through which the arm can be rotated relative to the arm axis 126 is determined by the switching step 2 formed. This makes it possible to adjust the balance drive and to optimize the position of the balance 154 relative to the respective position of the needle 134.

9 and 10, a needle bar drive 135 on the one hand and a balance drive 150 with a balance 154 on the other hand are located diametrically opposite the needle bar 131. It is clear that it is placed on the side. The needle bar drive 135 is on the side of the needle bar 131 facing the upright part 122, while the balance drive 1
50 is on the side 181 opposite the upright portion 122 and facing the end lid 125 .

In the embodiment shown in FIGS. 14 and 15, FIGS.
Parts that are the same as those in the illustrated embodiment are represented by the same reference numerals, and parts that are functionally the same but slightly different in structure are represented by the same reference numerals with a dash (') added thereto. To that extent, there is no need for a completely new description. A needle bar drive 135'' serves to drive the needle bar 131', its crank 136''
is not directly connected to the arm shaft 126'' but is driven via a toothed belt transmission device 182, its toothed pulley 183 is rotatably fixedly mounted on the arm shaft 126°, and the other toothed pulley is A toothed pulley 185 driven via a belt 184 is rotatably coupled to the crank 136''. An auxiliary shaft 142' is connected to the opposite side of the toothed pulley 183 from the arm shaft 126', and the auxiliary shaft is coaxial with the arm shaft 126', and is rotatably fixedly connected to the arm shaft or integrally connected thereto. It is formed.

Balance drive 1 via toothed belt transmission 149
The drive and construction of 50 is similar to the embodiment according to FIGS. 9-13. The balance drive is arranged as an integral unit on one side of the needle bar 131'. As shown in FIG. 15, the arm 123' is thinner over most of its length than the arm 123 according to the embodiment according to FIGS. 9-13. Only in the area of its end faces are the arms connected to the needle bar drive 135 and the balance drive 150.
A toothed pulley 185 is provided on the outside thereof, which is covered only by a lid 187, with a housing region 185 projecting toward the operator for housing the toothed pulley, so that the toothed pulley is easily accessible. will arrive. The needle bar drive device 135 includes one toothed pulley 1 as in the embodiment shown in FIGS. 1 to 8.
85 is mounted in a flange bearing housing 188, which is removably secured within a projecting housing region 186.

The embodiment shown in FIGS. 16 and 17 is different from FIG.
The difference is insofar as the regulating transmission 162 is omitted. Instead, the auxiliary shaft 142" and the arm shaft 126"
There is an electrical connection with, a so-called electrical axis. Identical parts are designated by the same reference numerals as in the embodiment according to FIGS. 9-13. Similar parts are indicated with “”.

A motor 189 is rotationally fixedly attached to the auxiliary shaft 142'' by a clutch 190.

The motor itself is fixed to the motor support 191 by screws 192 attached to the arm 123.

The pulse generating disk 1 is fixedly rotated on the arm shaft 126”.
93 is attached, and the disk is provided with light-transmissive slit-like openings 194 arranged at equal angular intervals over its entire circumference. The region of the pulse-generating disk with this opening 194 crosses a light transmitter/receiver device 195 which is fixedly arranged on the arm 123 and which transmits the pulses through a conductor 196 as it passes through each individual aperture 194. via the adjustment switch 197. The pulse generating disk 193 and the light emitting/receiving device 195 form a pulse generator 198 which, during each rotation of the arm shaft 126'', generates a number of pulses corresponding to the number of apertures 194 on the disk 193 to the regulator 197. A motor 189, configured as a DC motor or a stepping motor, is controlled via the output 199 of a regulator 197, which has the effective rotation angle of the arm 126'' as a guided variable from a pulse generator 198. And the motor 189 is guided depending on this guide value. The regulator 197 is program-controlled, ie a program is input to the regulator via its program carrier 200 in which the setpoint value is maintained. In this way, a constant and fine phase angle change is achieved, which in the embodiment according to FIGS. 9 to 13 is achieved by means of the adjusting transmission device 162. In this way, the phase angle between needle bar drive 135 and thread take-up drive 150 can be permanently determined. However, on the other hand, the phase angle can be varied depending on the rotational speed of the arm shaft 126'', ie depending on the pulses per unit time provided by the number of pulse generators 198.

For example, an EPROM can be used as program carrier 200.

[Brief explanation of drawings]

Fig. 1 is a plan view of an automatic sewing machine equipped with a device for generating relative motion in two coordinate axes of the sewing head with respect to the sewing product, and Fig. 2 is a partially cutaway view of the sewing head of the sewing machine shown by vertical arrows. 3 is a cross-sectional view of the rotating housing of the sewing head, FIG. 4 is a sectional view of the rotating housing taken along the line ■-IV in FIG. 3, and FIG. 5 is a cross-sectional view of the rotating housing taken along the line
6 is a side view of the rotary housing taken along the arrow ■ in FIG. 3, FIG. 7 is a side view of the rotary housing taken in the arrow ■ in FIG. FIG. 9 is a partial sectional view of the rotary housing taken along arrows ■-■ in FIG. 3, FIG. 9 is a partial plan view of the arm of the sewing head of a sewing machine according to another embodiment of the present invention, and FIG. FIG. 11 is a vertical cross-sectional view of the sewing head taken along line XI-XI of FIG. 10 showing the needle bar and needle bar drive device; FIG. 12 is a vertical cross-sectional view of the sewing head taken along line X--X of FIG. xn in Figure 1O showing the balance drive device
- a vertical cross-section of the arm of the sewing head along line XII;
13 is an end view of the arm of the sewing head along arrow xm in FIG. 9 showing the flange bearing housing for the thread take-up drive; FIG. 14 is the end of the arm of the sewing head of the third embodiment of the sewing machine; FIG. 15 is a vertical partial vertical cross-sectional view of the 14th
14 is a plan view along arrow XV in FIG. 14 of the open configuration of the arm shown in the figure; FIG. 16 is a vertical partial vertical sectional view of the end of the arm of the sewing head of the fourth embodiment of the sewing machine; and FIG. 17 is a plan view taken along arrow XV in FIG. is a cross-sectional view of the arm taken along the line X-X in Figure 16... Sewing head... Needle, Needle bar 126''... Shaft, Needle bar drive device... Take-up... Take-up balance drive device... ...Shaft...One side of the needle bar

Claims (1)

[Claims] 1. Supporting the needle (30, 134) and supporting the shaft (82, 126,
126', 126") to the needle bar drive device (87, 135")
, 135'), the needle bars (31, 13') can be driven up and down.
1, 131') and a balance drive (93, 15
In a sewing machine equipped with a sewing head (5, 120, 120') having a thread take-up (92, 154) that can be driven via the needle bar (31
, 131, 131') and the balance drive (93, 150) on one side (180, 180) of the needle bar (31, 131').
131, 131') on the other opposite side (180,
181), one drive being driveable by a shaft (82, 126, 126', 126'') and the other driving by a separate shaft (82, 126, 126', 126'').
98, 151), with both shafts (
82, 98, 126, 126', 126", 151) are drivingly connected to each other. 2. The thread take-up drive (93, 150) is formed as an independent component unit. 3. The sewing machine according to claim 1, wherein the thread take-up drive (93, 150) is arranged in the flange bearing housing (104, 158). 4. The shaft (82, 126). , 126', 126'') and the further axes (98, 151) are arranged parallel to each other. 5. The balance drive device (93, 150) is connected to the auxiliary shaft (55,
142, 142', 142'') through the needle bar drive (
shafts (82, 126) that drive the shafts (87, 135, 135')
, 126', 126''). 6. The shaft (126) and the further shaft (151) are connected to the needle bar (131).
) adjustment gear (162) for adjustment of the relative position of the
2. The sewing machine according to claim 1, wherein the sewing machine is interconnected via a . 7. The balance drive device (93, 150) is a four-section rotation chain (
92, 99, 102, 104; 152, 154, 156
, 158). The sewing machine according to claim 3, wherein the sewing machine is configured as: , 158). 8. The sewing machine according to claim 1, wherein both shafts (82, 98, 126, 151) are integrally connected to each other. 9. The sewing machine according to claim 1, wherein the shaft (126") and the further shaft (151) are electrically connected to each other. 10. The shaft (126") is connected to a pulse generator (198). , another axis (151) can be driven by an electric motor (189), and a pulse generator (198)
10. Sewing machine according to claim 9, characterized in that the regulator (197) is connected to the motor (189) via a regulator (197). 11. Sewing machine according to claim 10, wherein the regulator (197) is program controlled.