KR100570573B1 - 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 of the sewing machine {FEEDING DEVICE FOR THE SEWING MACHINE}

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1 is a front schematic view of a sewing machine.

2 is a cross-sectional view of the sewing machine according to FIG. 1, taken along the cutting line II-II of FIG. 1.

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

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

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

6 is a detailed enlarged view taken along 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 cross-sectional view taken along the cutting line VIII-VIII of FIG. 6 and is a reduced cross-sectional view of the portion shown in FIG. 6 rotated by 90 ° clockwise.

FIG. 9 is a reduced view of the portion shown in FIG. 6 in the direction of arrow Ⅸ of FIG. 6.

FIG. 10 is a view illustrating the direction shown by the arrow 의 of FIG. 6, and is a reduced view of rotating the portion shown in FIG. 6 by 90 ° in a clockwise direction.

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

12 is a view of the needle bar shown in the arrow XII direction of FIG. 1.

FIG. 13 is a partial view of FIG. 12 shown in the direction of arrow XIII of FIG. 12.

14 is a partial view of the sewing machine shown in the arrow direction of FIG.

The present invention relates to a feed device for a sewing machine according to the preamble of claim 1.

German Patent Publication No. 22 23 202 C2 (corresponding to US Patent Publication No. 3,844,234) is known in which one type of feed device is known, in which a reciprocating drive in the form of a clamping lever treatment is caught by a driven member of a gear pulley. Pass these exercises. The movement transmitted to the clamping lever treatment by the variable feed reducer is superimposed with another reducer to control the opening and closing movement of the clamping lever treatment. The disadvantage of such a reducer is that an unstable relationship can be achieved. In addition, smaller moments may be generated, in which case one clamping lever treatment and other clamping lever treatments do not bite with the gear pulley, and thus a state in which the gear pulley used as the transmission means may be out of control. On the other hand, the opposite phenomenon, in which both clamping lever treatments may instantly engage the gear pulley, may occur, so that the gear pulley under heavy friction load is stopped. These two phenomena affect the feed motion as a result.

Another disadvantage is the number of parts required for the reducer component, whereby separate motions (feed and reciprocating motions) are generated and combined with the feed motion.

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An object of the present invention is to provide a feed motion at a constant transmission ratio when friction is reduced in a feed device belonging to a sewing machine.

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This object of the invention is achieved according to the features of the device according to the preamble of claim 1.
According to the present invention, it is possible to reliably transmit the motion of the drive unit to the follower unit. In addition to this, the follower can always be controlled. As a result, continuous feed movement can be achieved without interruption. In the case where the feed movement takes place, wear of the feed device hardly occurs. Particularly advantageous is the simplicity of the structure and the generally three stable forms of the main components moving around one coaxial axis.
According to the feed device having the features of claims 2 to 7, and 10, the manufacturing is simple and reliable.
According to the feature of claim 8, a simple type for connecting certain components is presented. The integral part allows for free rotational torque transmission while matching the spring characteristics.
According to the feature of claim 9, the transmission torque is increased.
According to claim 11, the overlapping space is saved. According to claim 12, the spring load required for the rotational torque transmission can be uniformly distributed on some friction surface to increase the life of the main parts.
According to claims 13 and 14, the space utilization is increased to achieve as much rotational torque transmission as possible.
According to claim 15, a seal is formed which is free from external influences, which improves the acceptable method of operation of the device.
According to the feed device having the features of claims 16 to 20, the structure is simple and has high reliability of operation. According to the feature of claim 21, a simple setting for correcting the manufacturing tolerances of the main parts is presented. According to claim 22, a simple exercise delivery is achieved.
According to the feature of claim 23, a simple connection of the drive to the support frame for accommodating the needle rod is made. This results in the sewing machine having parts which simultaneously drive a suitable coupling. The feed device having the features of claim 24 provides for easy operation and increased output of the sewing machine. According to the feature of claim 25, the conveying capacity of the sewing machine is improved.
Other features, advantages and details of the invention will now be described with reference to the embodiments shown in the drawings.
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 to enable rotation of the arm shaft 9 therein. The female shaft 9 has an in-head crank drive device 10 connected to the needle bar 11 to be driven at the distal end. It extends at right angles to the arm shaft 9 and has a needle 12 at its lower end. The needle bar 11 is movable in the support frame 13 and consists of 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 comprised by the tension bar 17 with the upper end part 16 connected to the crank journal 18 of the pivot shaft 19 by the flexible joint.

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 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 inside 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 joints 39 and 40 of the same length, in which the ends 37 of the tension bars 38 are supported, are rotated therebetween. The pins 41 fixed to the holes 42 of the crank 23 at the free ends of the joints 39 and 40 are supported by a joint. At the end 43 of the pin 32, which extends out of the leg 26, the tension bar 44 is received for rotation, which is part of the setting device, which is not described in 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 housed between the legs 26, 27, including the portion between the joints 39, 40 (end 37 and hole 42), On one side, the joints 34 and 35 are pivoted around the pins 32 and 33 without play, and on the other side, the joints 39 and 40 are pivoted around the pins 36 without play. At the same time, the clearance free guidance along the axial direction of the joints 34, 35, 39, 40 between the legs 26, 27 is achieved to the same degree. The tension bar 38 is constituted by a bearing hole 45 and includes a cam 46 fixed on the female shaft 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, which adjustment is possible even under the adjustment state and operation of the sewing machine. Adjustment gears of this type are known from German Patent Publication No. 30 00 831 C2 (US Pat. No. 4,347,797). For further details, refer to the above document.

Another hole 47 in the crank 23 has a pin 48 press-fitted therein, and a joint bearing 49 is supported thereon and fixed in the axial direction. A ball socket joint is a type of ball bearing, also called a cup bearing. Joint bearing 49 is composed of a torsion bar 50 made of a pipe at one upper end. The torsion bar 50 extends downward 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 the joint bearing 51 again at the free end. It is supported by the pin 52 and fixed in the axial direction. The pin 52 penetrates 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 joint bearing 61 is supported and fixed in the axial direction. The joint bearing 61 is a torsion bar 62 made of a pipe at the top. 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). The torsion bar 62 is here comprised by the joint bearing 63 again in the free end. The torsion bars 50, 62 form a drive joint 64, shown schematically in a single line in FIG.

Next, the structure of the clutch 55 will be described with reference to FIGS. 6, 8, 9, 10, and 11. The joint bearing 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, whereby carriers 72, 73, 74 extending outward in three radial directions are provided. Listen. The carriers 72, 73, 74 are arranged uniformly across the circumference, ie at intervals of 120 °. Carriers 72, 73 and 74 are each formed as a friction surface on the outside thereof. They are flat, ie extend in plane and have a shape consistent 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 78 to be further defined. The lever 67 and the hollow shaft 69 together with the carriers 72, 73, 74 accompanying them form the second drive 78 of the clutch 55.

The fork 53 is part of a crank 79 with a bearing bush 80 pressed into the hole. The crank 79 is composed of a part that spans the pot-shaped housing part 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 the protrusions 84 and 85 are shown in FIG. 10. The projections 84 and 85 and the third unshown projection are respectively screw holes.

The housing portion 81 is covered with a cover 87 having a screw tightening surface 88. In addition, the cover 87 is composed of three projections 89, 90, 91 arranged at intervals of 120 DEG around them, through which respective through holes 92 are drilled. 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. For example, this is shown in FIG.

The cover 87 has a front face 94 protruding with respect to the tightening surface 88, and the edge 95 around its periphery protrudes into a groove (not shown) of the housing portion 81 so as to combine the parts. Guides are formed in the housing portion 81 and the cover 87. The front face 94 contains three friction surface portions 96, 97 and 98 extending inwardly, which are arranged at an angle of 120 ° 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 54. The friction surface portions 96, 97, 98 are connected by edges 102, 103, 104 and bounded by edges 99, 100, 101 including one groove 105. According to FIG. 8, the boundary of the friction surface portions 96, 97, 98 is characterized by the fact that the flange 71 in the groove 105 by the edges 99, 100, 101 has a sufficient freedom with the carriers 72, 73, 74. It has a space so that it can perform relative rotational movement of about 23 °.

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) away. The cover 87 is comprised by the bearing hole 107 which has a clearance, and includes the hollow shaft 69 (FIG. 6).

The hollow shaft (69) has a hollow shaft (108) that can be rotated and supported without significant play. The hollow shaft 108 has a male screw 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 the flange 110 of the front face is disposed with the inner 113 having a hole 114 parallel to the hole 111. It is. The cup spring 112 inside 113 and the flange 110 are fixedly connected to each other by rivets 115 extending through the holes 111 and 114.

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The cup spring 112 also consists of a ring 116 which is connected to the inner 113 and outer 118 by four legs 117. The legs 117 are biased by 90 ° with respect to each other, and the legs facing each other along the radial direction form an engagement with the inner 113 and the outer 118. On the outside 118, the facing projections 119 and 120 are provided with 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 cross section 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. The cup spring 112 is made of elastic spring steel having a thickness of about 1.0 mm. This 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, a load is applied to the cup spring 112 during elastic deformation along the axial direction of the ring 122 having the friction plate 124 on the hollow shaft 108. This hollow shaft 108 includes the parts fixed thereto to form the follower 126.

Components screwed together, such as the housing portion 81 and the cover 87, form a closed housing 127 to contaminate the components having the friction surfaces 75/76/77, 96/97/98, 125. Will be prevented.

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 nut 129 engaged with the male screw 109 along the axial direction. The nut 129 is also a lock nut so that the lock nut 130 is shown as an example. The lock nut 130 prevents the nut 129 from loosening on the one hand and on the other hand firmly engages the shaft 131 accommodated therein by deforming the hollow shaft 108.

The shaft 131 and the bearing bush 80 form bearings 80/131 at their contact areas. The hollow shaft 108 and the second drive shaft 78 rotatable thereon and slid along the axial direction form a rotary sliding bearing 108/69 in its contact area (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 an axis 134 hereinafter. According to FIG. 6, the first drive 54, the second drive 78 and the hollow shaft 108 comprise all friction surfaces 75/76/77, 96/97/98, 125 and on the shaft 134. Concentric about.

Next, the lifting gear 128 will be described according to FIGS. 6 and 7. The base plate 4 consists of bearings 135 and 136, in which the shaft 137 is supported and rotated. The shaft 137 is parallel to the female shaft 9 and is connected by the gear belt drive device 138 to be driven at a gear ratio of 1: 1. The gear belt drive device 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 of 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 the shape of keys. Faces 149 and 151 finish at the narrow edges 153 and another face 150 and 152 finish at the narrow edges 154. The legs 146, 147 thus form their faces 149, 151 and 150, 152, two keys 155, 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 rotates 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 front face 158 is in contact with one axis of the disk 160 fitted in 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 the hole and supported in the axial direction.

The disk 157 is composed of two surfaces 162 and 163 and extends along the keyed contour surfaces 151 and 152 on one plane. Between the faces 162, 163 is a projection 164, with the front face 158 already mentioned.

In the assembled state (FIG. 6), the nut 129 has a hollow shaft 108 such that the friction surface 125 abuts the friction surface portions 96, 97, 98 so that the cup spring 112 has a similar surface that is initially stressed. It is tightened with the external thread 109 of. As a result, the friction surface 125 comes into contact with the friction surfaces 96, 97, and 98 by the spring 112 load. At the same time the load of the spring 112 is on one side the housing 127 is in contact with the device with the bearing bush 80 of the housing part 81 with a corresponding reaction force at the free end of the flange 110. As shown in FIG. 6, the friction surface portions 75, 76, 77 of the carriers 72, 73, 74 abut 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 housed in a sprocket 168 supported by a 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 a corresponding tooth supported on the bearing 171. The upper tooth constitutes the lower bar pusher 172, which projects slightly upward through the groove (not shown) of the needle plate 173 secured to the column 5 so as to be in contact with the bar bar 174 at all times. do.

The sprocket 175 is attached to the shaft 131, and the endless gear belt 176 is caught. The sprocket 177 on the shaft 180 supported by the bearings 178, 179 winds up 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 device 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 drive-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.

These bar pushers 172 and 187 are each formed in the form of a wheel and are in contact with the bar at all times. Equally possible is a bar pusher consisting of a band, belt or chain.

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

The operation method of the feed device 189 is as follows.

When the arm shaft 9 rotates, the cam 46 of the tension bar 44 transmits a motion. 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 zero and maximum and its magnitude direction (phase) is variable in the forward or reverse direction.

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. In addition to the rotational movement of the arm shaft 9, the vertical movement of the needle bar 11 is made by the crank drive device 10.

When the cam 46 is correctly set in accordance with the phase with respect to the crank drive device 10, the up-and-down movement of the needle bar 11 is performed by the crank drive device 10 by the needle 12. When the cam 46 is correctly set in accordance with the phase with respect to the crank drive device 10, the needle 12 makes a so-called needle conveyance movement from the up-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 cranks 57 connected to the crank 23 and the vibration shaft 19 perform vertical movement of the tension bars 50 and 62, so that the first driving unit 54 and the second driving unit 78 are opposite to each other. It is rotated about the axis 131.

The rotational movement allows the carriers 72, 73, 74 to move without colliding with respect to the area of the cover 87 with the friction surfaces 97, 97, 98, respectively.

As the shaft 137 is rotated by the gear belt driving device 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 rotational movement about the axis 131 of the keys 155 and 156 including the disk 157 which occurs simultaneously is not important.

The movement of the keys 155, 156 is converted to reciprocating motion in the disk 157 such that the flange 71 on the hollow shaft 108 reciprocates against the load of the cup spring 112. Under the assumption of mutual phase correction of the cams 143 and 46, the superimposition of the reciprocating rotational motion and the axial motion is made so that the carriers 72, 73 and 74 carry out a lifting motion. The carriers 72, 73, 74 are thus connected to be driven with the first drive 54 and sometimes the second drive 78. More specifically, during some period of time, the friction surface 125 of the ring 122 is in contact with the friction surface portions 75, 76, 77 of the carrier 72, 73, 74, and during another period of time the cover The friction surface portions 96, 97, 98 of 87 are in contact with each other. In accordance with the cup spring 112 lowering action, rotational torque is transmitted by friction, respectively.

The reaction time of the ring 123 due to the lifting movement is shown in FIG. 6, in which the friction surface 126 is instantaneously in contact with all other friction surfaces 75, 76, 77 and 96, 97, 98. The oscillation movement in the drives 54 and 78 reverses its direction of movement at this moment. Neglecting a small tolerance, the reaction of the ring 123 occurs mainly in one instant, and the rotational speed of the drive units 54 and 78 takes a zero value.

In the operation method described above, a pulse rotational motion is performed on the shaft 131 along a predetermined direction. From this, the transmission of the rotary motion is transmitted to the lower bar pusher 172 by one side by the chain drive device 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 drive devices 185, 186 allow the delivery feed distance of the arm shaft to the bar pushers 172, 187 to be the same size, depending on their speed ratio.

By combining the support frame 13 driving device and the rod pusher 172, 187 driving device, the needle 12 moves the needle movement along the direction of the arrow 190 during operation of one of the driving units 54, 78. It is moved in the opposite direction to the direction of the arrow during the operation of the other drive of the drive (54, 78).

An advantage of this is that the transmission is made by one and the same sliding gear 24. Thus, the adjustment of the support frame 25 simultaneously affects the reciprocating motion of the support frame 13 and the rotational motion of the bar pushers 172 and 187.

Finally, it should be further noted that the support frame 13 may be adjusted to convey the article 174 along the direction of the arrow 191.

Provided is a feed device for a sewing machine that can reduce feed by giving a feed motion according to a constant speed ratio.

Claims (25)

A sewing pusher (172, 187) which is always in contact with the sewing product (174), A feed gear 24 for variable reciprocating motion of the first drive 54 and the second drive 78, -The driving parts 54 and 78 are formed with friction surfaces 96/97/98 and 75/76/77, The follower 126 is composed of a friction surface 125 which is in drive connection with the bar pushers 172 and 187, A reciprocating gear 128 for reciprocating by relative movement between the drives 54, 78 and the follower 126, Performing part of the reciprocating motion with the friction surface 75/76/77 of the first drive 54 and performing other parts of the reciprocation with the friction surface 96/97/98 of the second drive 78 In the feed device of the sewing machine 1, which can be engaged by friction in the Drive 54, 78 and follower 126 are concentric about one axis 134 in bearings 80/131, 108/69, in which feed movement is reversed in the opposite direction As a vibrating movement and in the follower 126 an equal rotational movement around the axis 134 is possible, Feed device characterized in that the bearings (80/131, 108/69) have a rotary sliding bearing (108/69) for carrying out reciprocating motion along the longitudinal direction of the shaft (134). The method of claim 1, The feeder (54, 78) and the follower (126) are installed on the shaft (131) surrounding the shaft (134). The method of claim 2, The bearings 80/131 and 108/69 are characterized by having a bearing bush 80 directly received on the shaft 131 and a hollow shaft 108 fixedly received on the shaft 131. Feed device. The method according to claim 2 or 3, A feed device, characterized in that the shaft (131) is engaged with the friction surface (125). The method of claim 3, The 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 A feed device, characterized in that the shaft (131) has a flange (110) engaged with the friction surface (125). The method of claim 5, Feed flange, characterized in that the ring 122 is provided with a friction surface (125). The method of claim 7, wherein Between the flange 110 and the ring 122, there are provided parts 113 and 118 which are coupled to each other in a rotationally fixed manner while allowing the cup spring 112 to slide against each other with respect to the spring load along the axial direction. Feed device, characterized in that. The method according to claim 7 or 8, Feed device, 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 3, Feed surface, 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 surface 96/97/98 of the first drive 54 has a number of 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 device, characterized in that the friction surface portion (75, 76, 77) of the second drive (78) is positioned adjacent to 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 consists of three friction surface portions 96, 97, 98 and 75, 76, 77. Device. The method of claim 10, The friction device portion (96, 97, 98 and 75, 76, 77) is equally spaced apart from the shaft (134). 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 of the second drive portion 78 in the groove. Feed device, characterized in that the face portion (75, 76, 77) is received. The method according to any one of claims 1 to 3, Feed surface, characterized in that 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 characterized in that it is formed by the keys (155, 156) in the tension bar (145). The method of claim 15, A feed device, characterized in that the key (155, 156) abuts a disk (157) which is rotatably supported on an axis (131). The method of claim 15, A feed device, characterized in that the key (155, 156) abuts a disk (157) which is rotatably supported on the hollow shaft (108). The method of claim 15, Feed device, characterized in that the tension bar (145) consists of two keys (155, 156) with grooves (148) therebetween so that the shaft (131) extends through the grooves. The method of claim 17, Feed device, characterized in that the disk (157) is in contact with the front surface (70) located in the second drive (78) by the front surface (158). The method of claim 14, The tension bar 145 is provided with the surfaces 149 and 150 contacted by the disk 160 supported on the hollow shaft 108 and fixed by the nut 129 tightened along the axial direction. Feed device. The method according to any one of claims 1 to 3, Feed device (24) is characterized in that connected to the drive unit (54, 78) to be driven by a tension bar (50, 62) consisting of joint bearings (49, 51, 61, 63). The method of claim 22, Feed device (24) is characterized in that connected to the support frame (13) of the needle bar (11) to be driven. The method of claim 22, The feed gear (24) is characterized in that it consists of an adjusting gear operable during the operation of the sewing machine (1). The method of claim 22, The follower 126 is a feed device, characterized in that connected to the upper bar pusher (187) to be driven.

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