KR19990078138A - Feeding device for the sewing machine - Google Patents

Abstract

The present invention relates to a feed device (189) of a sewing machine (1) for variable and substantially continuous feed movement by means of a pusher (172; 187) which is always in contact with the bar (174). In the clutch 55, the feed motion and the reciprocation motion are made of vibrations of the same cycle with respect to the feed motion. The feed gear 24 used to generate the feed motion is used to drive the support frame 13 which guides the needle bar 11 in the same manner. The feed reducer 24 provides a variable feed movement according to the feed size and feed direction while the sewing machine 1 is rotating.

Description

Feeding device for the sewing machine}

According to the invention there is a definite relationship for transmitting the motion of the drive to the follower. At the same time, the advantage is that the follower is not allowed at any moment, ie always controlled. This results in a continuous feed movement that is unobstructed.

When feed motion occurs, a constant relationship to the feed device with little wear is maintained. Particularly advantageous is the simplicity of its structure and the fact that the three stable forms of main components generally move around one coaxial axis.

The form of the feed device having the features of claims 2 to 7 and 10 results in a simple device and a high reliability.

By the features of claim 8 a simple type for connecting certain components is proposed. Integral parts allow spring-free rotational torque transfer and match spring characteristics.

The development form according to the features of claim 9 increases the transmission torque.

The type according to claim 11 is overlapping space saving. With the development of the device having the features according to claim 12, the spring load required for the rotational torque transmission can be evenly distributed on some friction surfaces, thereby increasing the service life of the main parts.

Another type with the features according to claims 13 and 14 has increased space utilization in order to achieve as large rotational torque transmission as possible.

The development type with the features of claim 15 has a structure which is free from external influences due to its closure, which provides an improvement in the acceptable method of operation of the device.

The development type of the feed apparatus which has the characteristics of Claim 16-20 has the structure which is simple and has high reliability of operation. The type with the features of claim 21 presents a simple setting possibility for correcting manufacturing tolerances of main parts.

The type of development according to claim 22 provides for simple exercise transmission.

The feature of claim 23 makes a simple connection of the drive to the support frame for receiving the needle. This results in the sewing machine having parts which simultaneously drive a suitable coupling.

Feed device with the features of claim 24 provides for easy operation and increased output of the sewing machine. The first feature of claim 25 improves the conveying capacity of the sewing machine.

In order to reduce the friction in the feeder of the sewing machine to obtain a feed movement by a constant transmission ratio.

The present invention relates to a feeder of a sewing machine according to the higher concept of claim 1.

One type of feed device is known from DE 22 23 202 C2 (corresponding to US-PS 3,844,234), whereby a reciprocating drive in the form of a clamping lever treatment delivers this movement by being driven by the driven material of the gear pulley. The motion transmitted to the clamping lever Daewoo by the variable feed reducer overlaps with that of another speed reducer to control the opening and closing movement to the clamping lever Daewoo. The disadvantage of such a reducer is that it can lead to an unstable relationship at this point. In addition, a smaller moment may occur unilaterally. In this case, one clamping lever treatment and the other clamping lever treatment may not be bitten by the gear pulley, and thus a state in which the gear pulley used as a transmission means may be out of control. On the other hand, both clamping lever treatments can cause the opposite phenomenon of momentary engagement with the gear pulley, so that the gear pulley under heavy friction load is stopped. In addition, two phenomena affect the feed motion as a result.

Another disadvantage is the number of parts required for the reducer component, whereby individual motions (feed-and-reciprocation) are produced and combined with the feed motion.

Feed device belonging to the sewing machine in the present invention is based on the problem to be the generation of the feed motion at a constant transmission ratio when friction is reduced.

The solution of the present invention is made according to its features in the device according to the higher concept of claim 1.

Other features and specifications of the present invention have been described with reference to one embodiment according to the drawings.

1 is a front view of a sewing machine

2 is a cross-sectional view of the sewing machine shown in FIG. 1 by the cutting line II-II of FIG.

3 is an enlarged cross-sectional view taken along line III-III of FIG. 1;

FIG. 4 is a partial view of FIG. 3 in the direction of arrow IV of FIG. 3;

5 is a cross-sectional view taken along the cutting line V-V of FIG. 4;

FIG. 6 is a detailed enlarged view according to the cutting line of FIG. 1. FIG.

7 is a reduced cross-sectional view taken along the cutting line VIII-VIII of FIG. 6;

FIG. 8 is a 90 degree turn down clockwise of the portion shown in FIG. 6 along the cutting line VIII-VIII in FIG. 6, FIG.

9 is a reduced view of the arrow 화살표 direction of FIG. 6 of the component shown in FIG. 6, FIG.

FIG. 10 is a 90 degree turn down clockwise of the portion shown in FIG. 6 according to arrow VII of FIG. 6, FIG.

11 is a reduced detail view of the part shown in FIG. 6;

12 is a support of the needle according to the arrow XII of Figure 1,

FIG. 13 is a partial view shown in FIG. 12 according to arrow XIII of FIG. 12;

14 is a partial view of the sewing machine according to the arrow of FIG.

The sewing machine 1 is composed of an arm 2, a stand 3, and a base plate 4. The column 5 is fixed on the base plate 4. The arm 2, the stand 3, and the column 5 are each comprised from a hollow body in general structure. The arm 2 is composed of a free end of the head 6 and bearings 7 and 8 therein and is supported therein to enable rotation of the arm 9. The female shaft 9 ends in the crank drive 10 in the head which is connected to be driven with the needle bar 11. It extends at right angles to the arm axis 9 and has a needle 12 at its lower end. The needle bar 11 is movable in the support frame 13 and has a bearing journal 14. It is housed so that it can pivot in the bearing 15 attached to the head 6. The support frame 13 is composed of a crank journal 18 of the pivot shaft 19 and an upper end 16 connected by a flexible joint by a tension bar 17.

The pivot shaft 19 extends in parallel with the arm shaft 9 and is supported to be able to rotate in the bearings 20 and 21 formed in the arm 2. In the upper part of the stand 3, the pivot shaft 19 is connected to the crank 23 which is a part of the feed gear 24 by a clamping joint 23.

The following describes the structure of the feed gear 24 according to FIGS. 3, 4 and 5. The feed gear 24 is composed of a u-shaped support frame 25 and the legs 26 and 27 facing each other in parallel with each other are mounted in a flexible joint type by bolts 28 and 29. .

The bolts 28, 29 are housed in the bearings 30, 31 in the interior of the arm 2. At the free ends of the legs 26, 27 there are pins 32, 33 which are press-fitted, and the joints 34, 35 of the same length which can be rotated therein are accommodated. The free ends of the joints 34 and 35 hold the pins 36 fixed to one end 37 of the tension bar 38 so as to rotate. The pins 36 are supported such that the joints 39 and 40 having the same length, in which the ends 37 of the tension bars 38 are supported, are rotated therebetween. The free ends of the joints 39 and 40 are fixed to the end 42 of the crank 23 by means of a joint. At the end 43 of the pin 32, which extends out of the leg 26, the tension bar 44 is accommodated for rotation, which is a part of the setting device which is not described in more detail and holds the support frame in its rotational state, ie its position. Let's do it. The position and size of the joints 34, 35, 39, 40 accommodated between the legs 26, 27, including the partial ends 37 and the holes 42 between the joints 39, 40, The joints 34 and 35 are pivoted about the pins 32 and 33 without play, and on the other hand, the joints 39 and 40 are pivoted about the pin 36 without play. At the same time, the clearance free guide along the axial direction of the joints 34, 35, 39, 40 between the legs 26, 27 is made to the same degree. The torsion bar 38 is constituted by a bearing hole 45 and includes a cam 46 fixed on the compression 9.

The feed gear 24 changes the feed motion with respect to the swing width and the swing direction. The feed gear 24 is also referred to as an adjustment gear accordingly, and this adjustment is possible even under the adjustment state and operation of the sewing machine. Adjustment gears of this type are known from DE 30 00 831 C2 (US-PS 4 347 797). See this document for more details.

Another hole 47 in the crank 23 has a pin 48 pressed therein and a joint bearing 49 is supported thereon and fixed axially. A ball socket joint is a kind of ball bearing, also called a cup bearing. The ball socket joint 49 is composed of a torsion bar 50 made of a pipe at one upper end. The torsion bar 50 extends from the feed gear 24 in the vicinity of the arm shaft 9 via the stand 3 to the area of the base plate 4 (FIG. 1). Here, the torsion bar 50 is a ball socket joint 51 again at the free end. It is supported by the pin 52 and fixed in the axial direction. The pin 52 penetrates through the fork 53 which is a component of the first drive unit 54 of the clutch 55.

On the pivot shaft 19 is a crank 57 which is fixed by a clamping joint 56 which is an arm 58 with a hole 59. In the hole 59, a press-fitted pin 60 is contained, on which a ball socket joint 61 is supported and fixed in the axial direction. The ball socket joint 61 is a torsion bar 62 made of a pipe at the upper end. The torsion bar 62 extends from the feed gear 24 in contact with the female shaft 9 to the area of the base plate 4 below through the stand 3 (FIG. 1). Here, the torsion bar 62 is composed of the ball socket joint 63 again at its free end. The torsion bars 50, 62 form a drive joint 64, which is shown in the outline by the broken line in FIG.

Next, the structure of the clutch 55 will be described with reference to FIGS. 6, 8, 9, 10 and 11. The ball socket joint 63 is supported by the pin 65 which is fixed in the hole 66 of the lever 67. The lever 67 is composed of a hole (not shown) and a clamping joint 68. The lever 67 is connected to the hollow shaft 69 fixed in the hole. According to FIG. 6, the hollow shaft 69 is composed of a front face 70 at the left end and a flange 71 at the right end, so that the carriers 72, 73, and 74 extending outward in three radial directions are provided. Listen. Carriers 72, 73 and 74 are arranged uniformly across the circumference, i.e. at 120 [deg.] Intervals. Carriers 72, 73 and 74 are each formed as a friction surface on the outside thereof. They are flat, i.e., flat, and have a shape coincident with part of the annulus. Accordingly, the carrier 72 has a friction surface 75, the carrier 73 has a friction surface 76, and the carrier 74 has a friction surface 77. In short, the friction surface portions 75, 76, 77 form a friction surface 75/76/77 (not shown) of the second drive portion 78 to be further defined. The lever 67 and the hollow shaft 69 together with the carriers 72, 73, 74 form the second drive 78 of the clutch 55.

The hook 53 is part of the crank 79 with a bearing bush 80 pressed into the hole. The crank 79 is composed of components spanning the pot-shaped housing portion 81 and has a flange-shaped edge 83 extending around the cylindrical hollow chamber 82. The edge 83 has three protrusions arranged at 120 ° intervals, of which only protrusions 84 and 85 are shown in FIG. 10. The projections 84 and 85 and the third unshown projections are respectively screw holes.

The housing portion 81 is covered with a cover 87 having a threaded surface 88. Furthermore, the cover 87 is composed of three projections 89, 90 and 91 arranged at 120 ° intervals around the respective through holes 92. The holes 92 and the screw holes 86 are in positions facing each other in a line. The housing portion 81 and the cover 87 are fixed by screws 93, which are contained in the holes 92 and the screw holes 86. This is shown, for example, in FIG.

The cover 87 is a front face 94 protruding with respect to the tightening surface 88 and the corners 95 around its periphery protrude into the grooves (not shown) of the housing portion 81 so that the combination of parts is achieved. Guides are formed in the housing portion 81 and the cover 871. The front face 94 contains three friction surface portions 96, 97 and 98 extending inwardly and arranged at 120 ° angles to each other. In short, the friction surface portions 96, 97, 98 form the friction surface 96/97/98 (not shown) of the first drive portion 54. The friction surface portions 96, 97, 98 are connected to the edges 102, 103, 104 and bounded by edges 99, 100, 101 including a groove 105. According to FIG. 8, the boundary between the friction surface portions 96, 97, and 98 is formed in the groove 105 by the edges 99, 100, and 101 and has sufficient free space with the carriers 72, 73, and 74. The relative rotational movement of about 23 ° is possible.

The groove 105 has a clearance of about 2 mm when the friction surface portions 96, 97, 98 of the cover 87 are parallel to the friction surface portions 75, 76, 77 of the carriers 72, 73, 74 ( 106). The cover 87 is composed of a bearing hole 107 having a clearance and including a hollow shaft 69 (FIG. 6).

The hollow shaft 69 has a hollow shaft 108 is rotatable and is supported without significant play. The hollow shaft 108 has a male thread at one end and a flange 110 at the free end (FIGS. 9 and 11). The flange 110 is formed of four holes 111 and has a front flange 110. Cup springs 112 are arranged with an interior 113 having a hole 114 parallel to the hole 111. The cup spring 112 inside 113 and the flange 110 extend through the holes 111 and 114.

The rivets 115 are fixedly connected to each other.

The cup spring 112 also consists of a ring 116 which is connected to the inner 113 and outer 118 by four legs 117. Legs 117 are opposed to each other are shifted by 90 ° and the legs facing in the radial direction are combined with the inner 113 and the outer 118. On the outside 118, the projections 119, 120 have two holes 121 therein, respectively. The ring 122 has a screw hole (not shown) parallel to the hole 121. The ring 122 is fixed with four screws 123 as two projections 119 and 120. In addition, the ring 122 is, for example, a friction plate 124 fixed to the ring 122 with an adhesive. The free end surface of the friction plate 124 is called a friction surface 125.

As shown in FIG. 11, the cup spring 112 has a shape in which the inside 113 is biased by a distance a of about 2.5 mm with respect to the outside 118 without being stressed. Cup spring 112 is made of an elastic spring steel having a thickness of about 1.0 mm. The cup spring 112 is made of elastic spring steel having a thickness of about 1.0 mm. The shaping of the cup spring 112 enables rotationally fixed transmission of the hollow shaft 108 rotational movement on one side to the friction plate 124. Meanwhile, the elastic deformation along the axial direction of the ring 122 having the friction plate 124 on the hollow shaft 108 enables the load of the cup spring 112. The hollow shaft 108 includes a component fixed thereto to form the follower 126.

Parts screwed together such as the housing portion 81 and the cover 87 form a closed housing 127 to form a friction surface (75/76/77 and 96/97/98 and 125). It will prevent contamination.

According to FIG. 6, on the hollow shaft 108, a lifting gear component, which will be described next, is also received and fixed by a male screw 109 and a bite nut 129 along the axial direction. Nut 129 is also a lock nut, so locknut 130 is shown as an example. The locknut 130, on the other hand, prevents the nut 129 from naturally loosening and also deforms the hollow shaft 108 on the one hand so as to be firmly engaged with the shaft 131 accommodated therein.

The shaft 131 and the bearing bush 80 form bearings 80/131 at their contacts. The hollow shaft 108 and the second drive shaft 78 which is rotatable thereon and slid along the axial direction form a rotation-sliding-bearing 108/69 at its contact (FIG. 6).

The shaft 131 is supported in the bearings 132 and 133 formed in the base plate 4. The shaft 131 has a rotating shaft called the following shaft 134. According to FIG. 6, the first drive part 54, the second drive part 78 and the hollow shaft 108 include all friction surfaces 75/76/77, 96/97/98 and 125 and on the shaft 134. Concentric about.

Next, the lifting gear 128 will be described with reference to FIGS. 6 and 7. The base plate 4 consists of bearings 135 and 136 in which the shaft 137 is supported to rotate. The shaft 137 is parallel to the arm shaft 9 and connected by a gear belt drive 138 to be driven at a gear ratio of 1: 1. The gear belt hole 138 consists of a gear belt pulley 139 on the female shaft 9, a gear belt pulley 14 on the shaft 137, and a gear belt 141.

On the shaft 137, a lock nut 142 fixing cam 143 which is rotatable by the bearing hole 144 of the tension bar 145 is provided. The tension bar 145 is a fork with two legs 146 and 147 at its free end, with a groove 148 bounded therebetween. Legs 146 and 147 are formed with faces 149 and 150 and further with keys 151 and 152 in shape. Faces 149 and 151 end at the narrow edge 153 and another face 150 and 152 end at the narrow edge 154. Legs 146 and 147 thus form faces 149, 151 and 150, 152 and two keys 155 and 156. In Figure 6 the key 155 is shown in dashed lines in its cross section. Another key 156 is shown the same.

The hollow shaft 108 extends through the hole in the disk 157 and the disk is rotated freely on the hollow shaft 108. The disk 157 has a front surface 158 and is in contact with the front surface 70 of the hollow shaft 69. The front face 159 of the disk 157 parallel to the other front face 158 abuts one axis of the disk 160 which is fitted into the hole of the nut 129 groove (not shown). Next to the disk 160 is another disk 161 which is simultaneously inserted into the groove of the nut 129 by a hole and supported in the axial direction.

The disk 157 is composed of two surfaces 162 and 163 and extends along the key-shaped contour surfaces 151 and 152 on one plane. There are protrusions 164 on facets 162 and 163 and there is a front face 158 already mentioned here.

In the assembled state (FIG. 6), the nut 129 has a hollow shaft 108 such that the friction surface 125 is in contact with the friction surface portions 96, 97 and 98 so that the cup spring 112 has a similar surface subjected to initial stress. Is tightened with a male screw (109). As a result, the friction surface 125 is brought into contact with the friction surfaces 96, 97, and 98 by the load of the spring 112. At the same time, the spring 112 load is brought into contact with the device on the one hand with the corresponding reaction force at the free end of the flange 110 together with the bearing bush 80 of the housing portion 81. At the moment shown in FIG. 6, the friction surface portions 75, 76, 77 of the carriers 72, 73, 74 are in contact with the friction surface of the hollow shaft 108.

A sprocket 165 is attached to the shaft 131 and an endless roller chain is wound thereon. The free end of the roller chain 166 is accommodated in the sprocket 168 supported by the bearing 167 in the column 5. Since the sprockets 165 and 168 have the same dimensions, the chain drive 169 has a gear ratio of 1: 1. The sprocket 168 is fixedly coupled to the tooth 170 having a tooth having a tooth of about 1 mm. The tooth 170 is meshed with the upper tooth with the corresponding tooth supported on the bearing 171. The upper gear constitutes the lower bar pusher 172, which projects slightly through the groove (not shown) of the needle plate 173 fixed to the column 5 to the upper part (FIG. 14) so that it is always with the bar bar 174. You will come across.

The sprocket 175 is attached to the shaft 131, and the endless gear belt 176 is hung. The sprocket 177 on the shaft 180 supported by the bearings 178, 179 winds the free end of the gear belt 176. Since the sprockets 175 and 177 have the same dimensions, the speed ratio of the gear belt drive 181 is 1: 1.

In the sewing machine head 6, a shaft 182 provided vertically (FIG. 1) is supported by bearings 183 and 184. The shaft 182 is driven and coupled with one tooth by the first bevel drive 185 and the second bevel drive 186. The tooth is bitten around the lower bar pusher 172 and constitutes the upper bar pusher 187. The upper bar pusher 187 is supported by the bearing arm 188 to allow rotation. The bearing arm 188 is configured such that the upper bar pusher 187 presses the bar 174 to the lower bar pusher 172 in a known manner.

The bar pushers 172 and 187 are each formed in the form of a wheel and are in contact with the bar at all times. Similarly, it is possible to use a bar pusher composed of a band, belt or chain.

Feed components 24 and driving components connected therewith, including feed drive 24, lifting gear 128, clutch 55, and bar pushers 172 and 187, constitute feed device 189.

The operation of the feed device 189 is as follows:

When the arm shaft 9 is rotated one by one, the cam 46 of the tension bar 44 transmits the motion, and the vibrations are applied to the crank 23 by the joints 34, 39, and 40 located in the bearing frame 20. Therefore, it is transmitted to the vibration shaft (19). Depending on the position of the bearing frame 25, the vibratory motion is variable in amplitude between the zero and the maximum endlessly and in its progressive direction (phase forward or backward).

The vibration of the oscillation shaft 19 is transmitted to the bearing frame 13 by the bearing frame 17 by the crank journal 18 and the tension bar 17, thereby reciprocating. Along with the rotational movement of the arm shaft (9), the vertical movement of the needle bar (11) is made by the crank drive (10).

When the cam 46 is correctly set according to the phase of the crank drive 10, the needle 12 is vertically moved by the crank drive 10 by the needle bar 11. When the cam 46 is correctly set according to the phase with respect to the crank drive 10, the needle 12 performs the so-called needle feeding movement from the up and down movement of the needle bar 11 and the reciprocating movement of the bearing frame 13. At the same time, the lower end of the needle 12 enters into the long hole-shaped tamhole in the sewing plate 173 instantaneously.

The crank (57), which is connected to the crank (23) and the oscillation shaft (19), moves up and down the tension bars (50 and 62), so that the first drive unit (54) and the second drive unit (78) are in opposite directions. It is rotated about the axis 131.

The rotational movement is such that the carriers 72, 73 and 74 can move without colliding with respect to the area of the cover 87 having the friction surfaces 97, 97 and 98, respectively.

As the shaft 137 is rotated by the gear belt driving 138 along with the rotation of the arm shaft 9, the cam 143 of the tension bar 145 transmits vibration. Accordingly, the keys 155 and 156 formed on the tension bar 145 induce a reciprocating feed motion in the direction of the axis 131 along the radial direction. At the same time, the reciprocating motion about the axis 131 of the keys 155 and 156, including the other occurring disks 157, is not important at this time.

The movement of the keys 155, 15 is converted to reciprocating motion in the disk 157 so that the flange 71 on the hollow shaft 108 reciprocates against the loading action of the cup spring 112. Under the assumption that the cams 143 and 46 are mutually phase-corrected, the reciprocating rotational motion and the axial motion are superimposed so that the carriers 72, 73, and 74 carry out a lifting motion. Accordingly, the carriers 72, 73, 74 are sometimes connected to be driven with the first driver 54 and sometimes with the second driver 78. More specifically, during some period of time, the friction surface 125 of FIG. 6 122 contacts the frictional sections 75, 76, 77 of the carriers 72, 73, 74, and in some other periods the cover 87 ) Are in contact with the friction surface sections (96, 97, 98). In accordance with the cup spring 112 lowering action, the rotation torque is transmitted by friction.

In Fig. 6, the time of reaction of the ring 123 due to the lifting flow is presented, in which the friction surface 126 instantaneously comes into contact with all other friction surfaces 75, 76, 77 and 96, 97, 98. . The oscillation motion in the drive sections 54 and 78 is allowed in that it reverses its direction of movement immediately at this moment. Neglecting a small tolerance, the reaction of the ring 123 occurs mainly in one moment, and the rotational speed of the drive unit 54, 78 takes a zero value (0).

In the operation method described, a pulse rotational motion is performed on the shaft 131 according to a predetermined direction. From this, the transmission of the rotary motion is transmitted to the lower bar pusher 172 to one side by the chain drive (169). As the rotation is reversed by the intervention of the gear 170, the lower bar pusher 172 pushes the bar 174 in the direction of the arrow 190. Similarly, the bevel drives 185 and 186 allow the feed shaft feed distance of the arm shaft to the bar pushers 172 and 182 to be the same size according to the speed ratio thereof.

By driving coupling between driving of the support frame 13 and driving of the pusher pusher 172 and 187, the needle 12 moves the needle along the direction of the arrow 190 while one of the driving units 54 and 78 is in operation. 54, 78) moves in the opposite direction to the direction of the arrow during operation of the other drive unit.

An advantage for this is one and is matched to each other by being transmitted by the same sliding gear 24. This is because the adjustment of the support frame 25 affects the reciprocation of the support frame 13 and the rotation of the bar pushers 172 and 187 at the same time.

Finally, it should be further noted that the support frame 13 can also be adjusted to convey the finished product 174 in the direction of the arrow 191.

It is considered to be a feed device of a sewing machine that can reduce wear by giving a feed motion according to a constant speed ratio.

Claims (25)

Then A bar pusher (172; 187) that is always in contact with the bar (174) A feed gear 24 for giving a variable reciprocating motion to the first drive 54 and the second drive 78. -The driving parts 54, 78 are formed with friction surfaces (96/97 / 98,75 / 76/77) -The driven part 126 is composed of a friction surface 125 is connected to the driving pusher (172; 187) Reciprocating gear 128 for reciprocating by relative movement between drive section 54 and 78 and follower section 126 At this time, the friction surface 75/76/77 of the first drive unit 54 performs a part of the reciprocating motion and the friction surface 96/97/98 of the second drive unit 78 performs other parts of the reciprocation motion. In the feed device of the sewing machine (1) having the characteristics of those that can be engaged by friction during Drive 54, 78 and follower 126 are concentric about one axis 134 in bearing 80/131, 108/69, At this time, the feed motion in the drive unit 54, 78 is the rotation-vibration-movement in the opposite direction and the same rotation-movement around the axis 134 in the follower 126, Feed device characterized in that the bearings (80/121, 108/69) have a rotation-slide-bearing (108/69) for carrying out reciprocating movements along the longitudinal direction of the shaft (134). The method of claim 1, The feeder (54, 78) and the follower (126) is provided on the shaft (131) surrounding the shaft (134). The method of claim 2, Feed device characterized in that the bearing (80/131, 108/69) has a bearing bush (80) directly received on the shaft (131) and a hollow shaft (108) fixedly received on the shaft (131). The method of claim 2 or 3, Feed shaft, 131 is characterized in that coupled with the friction surface (125). The method of claim 3, Feed shaft, characterized in that the hollow shaft 108 has a flange (110) coupled with the friction surface (125). The method of claim 4, wherein Feed shaft characterized in that it has a flange (110) associated with the friction surface (125). The method of claim 5 or 6, Feed device, characterized in that the flange 110 is attached to the ring 122 having a friction surface (125). The method of claim 7, wherein Between the flange 110 and the ring 122, the cup springs 112 are opposed to each other with respect to the spring load along the axial direction, and the parts 113 and 118 coupled to each other by rotational fixation are considered. Feed device. The method according to claim 7 or 8, Feed ring, characterized in that the ring 122 has a friction lining 124 of the friction surface (125). The method according to any one of claims 1 to 9, Feeding device characterized in that the friction surface (75/76/77, 96/97/98, 125) is perpendicular to the plane with respect to the axis. The method of claim 10, The friction surfaces 96/97/98 of the first drive 54 have several friction surface portions 96, 97, 98 facing each other apart; The friction surfaces 75/76/77 of the second drive 78 have the same number of friction surface portions 75, 76, 77 facing away from each other; A feed apparatus, characterized in that there is a friction surface portion (75, 76, 77) of the second drive (78) adjacent the friction surface portion (96, 97, 98) of the first drive (54). The method of claim 11, Each friction surface 96/97/98 and 75/76/77 of the drive section 54, 78 is composed of three friction surface portions 96,97,98 and 75,76,77 Device. The method according to any one of claims 10 to 12, Friction surface portions 96, 97, 98 and 75, 76, 77 are generally spaced apart from the axis 134 by the same width The method of claim 13, Friction surface portions 96, 97, 98 of the first drive portion 78 are formed in the cover 87 and the cover 87 has a groove 105 so that the friction surface portion of the second drive portion 78 is therein. And (75,76,77) housed therein. The method according to any one of the preceding claims, The friction surface (75/76 / 77,96 / 97 / 98,125) is installed in a sealed housing (127). The method of claim 15, The reciprocating gear (128) is a feed device, characterized in that formed by the key (155; 156) in the tension bar (145). The method of claim 15, The key (155; 156) is in contact with a disk (157) which is supported to be rotatable on an axis. The method of claim 15, And the key (155; 156) abuts (157) on a disk which is supported to be rotatable on the hollow shaft (108). The method according to any one of claims 15 to 18, The tension bar (145) is characterized in that two keys (155,156) are configured with a groove (148) therebetween, through which the shaft (131) extends. The method of claim 17 or 18, Disc (157) is characterized in that the front surface (158) is in contact with the front surface (70) located in the second drive (178). The method of claim 14 further comprising: The tension bar 145 is characterized in that it has a surface 149; 150 in contact with the disk 160, which is supported on the hollow shaft 108 and fixed by an axially tightened nut 129. . The method according to any one of the preceding claims, The feed gear (24) is characterized in that it is connected to the drive (54, 78) to be driven by a tension bar (50, 62) consisting of ball bearings (49, 51, 61, 63). The method of claim 22, The feed gear (24) is characterized in that it is connected to the support frame (13) of the needle bar (11) to be driven. The method of claim 22 or 23, Feed gear (24) is characterized in that the device is composed of a control gear that can be operated during the return of the sewing machine (1). The method according to any one of claims 22 to 24, The follower (126) is characterized in that it is connected to the upper bar pusher (187) to be driven.