JP2006061594A - Sewing machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the tightness of stitches in both left/right needle locations respectively and prevent the stitch skipping, when a needle bar swings between a right needle swing position and a left needle swing position. <P>SOLUTION: A driving force transmission system 50 transmitting a rotating driving force from a lower shaft 48 to a rotating shuttle 8 is provided with a second phase adjusting mechanism 51 capable of transmitting the rotating driving force of the lower shaft 48 and adjusting the rotation phase of the rotating shuttle 8 to the lower shaft 48 by being interlocked with the swing of the needle bar; the driving force transmission system 50 is provided with a driving gear 60 fixed to first and second shuttle driving shafts 56 and 58 and the lower shaft 48, and a driven gear 61 axially movably and externally fitted around the second shuttle driving shaft 58 and threadedly engaged with the driving gear 60; and the second phase adjusting mechanism 51 is provided with a helical spline external tooth 56a formed in the right end of the first shuttle driving shaft 56, a helical spline internal tooth 61c formed in the driven gear 61, and a moving driving mechanism 65 movingly driving the driven gear 61 in the axial direction by being interlocked with the swing of the needle bar. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  In the present invention, not only the rotation phase with respect to the lower shaft of the thread catching hook, but also the rotation phase with respect to the main shaft of the rotary balance can be adjusted as appropriate by swinging the needle bar to the right and to the left. About what you did.

  2. Description of the Related Art Conventionally, a decorative sewing machine such as an eyelet perforated sewing machine, a double chain stitch sewing machine, a staggered sewing machine or the like is generally provided with a rotary balance that rotates in conjunction with a sewing machine main shaft. This type of rotary balance is formed in a substantially T-shape in front view having an upper thread hook portion, and in the middle of the thread path from the thread supply source to the sewing needle when rotating in synchronization with the main spindle of the sewing machine, Since a part of the upper thread fed from the source engages with the upper thread hook, the amount of thread taken by the rotary balance can be adjusted.

  By the way, the texture of stitches (the degree of stitch clogging) often changes depending on the type and thickness of the work cloth, as well as the type and thickness of the sewing thread. Accordingly, various types of rotary balance devices for sewing machines have been proposed in which the phase of the thread take-up amount curve by the rotary balance can be adjusted so as to be advanced or delayed so that the appearance of the texture can be arbitrarily changed.

For example, a rotary sewing machine for a sewing machine of a sewing machine disclosed in Patent Document 1 is a base disk attached concentrically with a sewing machine main shaft, a base disk rotating in the same direction and at the same angular speed as the main shaft, Several inner thread contact pins attached to the disk, one disk supported concentrically on the front surface of the base disk by the inner thread contact pins, and the number attached to the front surface of the disk And an outer sewing thread contact pin, and an adjustment fixing device that can adjust and fix the mounting angle of the disk with respect to the base disk. By adjusting the mounting angle, the shape of the change curve of the thread take-up amount is changed. It is adjusted so that the thread take-up action can be adapted to various sewing conditions.
Japanese Examined Patent Publication No. 37-17183 (pages 1 and 2, FIGS. 1 and 2)

  As described above, in the rotary sewing machine for a sewing machine described in Patent Document 1, the shape of the change curve of the sewing thread take-up is changed and adjusted by adjusting the mounting angle of the adjusting and fixing device. Alternatively, the appearance of stitching can be changed according to consumer preference.

  By the way, for example, in the case of a staggered sewing machine that forms a staggered stitch, the needle bar swings so that the needle drops alternately on the right side and the left side. For this reason, not only does the timing of the contact between the sword tip of the outer hook of the rotary hook and the eye of the sewing needle differ depending on the right policy swing position and the left policy swing position of the needle bar, but also the upper thread loop hooked on the sword tip. The timing for exiting the rotary hook is also different. In other words, when the rotation direction of the rotary hook is counterclockwise as viewed from the operator, the timing of encountering the stitch hole of the sewing needle and the timing of thread removal of the upper thread loop are earlier when the needle swings to the right. Slower when swinging left.

  However, the rotation phase of the rotary balance and the phase of the needle bar's vertical movement are basically set based on when the blade tip of the rotary hook comes to the approximate center of the needle swinging width. There is a problem in that the thread tightening at each of the left needle entry positions is not optimal in any case, and the stitching texture and appearance are poor.

  Furthermore, since the rotation phase of the rotary hook is not adjusted at all, such as changing the rotation phase of the rotary hook in synchronization with the needle swing of the needle bar, depending on the type and thickness of the sewing thread, or the sewing speed However, depending on the sewing conditions, there is a problem that the timing at which the needle meets the sword is not stable and there is a possibility of skipping.

  The sewing machine according to claim 1 is a sewing machine having a needle swing mechanism that swings the needle bar and a thread catching hook that is rotationally driven by the lower shaft, and a driving force that transmits rotational driving force from the lower shaft to the thread catching hook. The transmission system is provided with a phase adjusting mechanism capable of transmitting the rotational driving force of the lower shaft and adjusting the rotational phase relative to the lower shaft of the thread catching hook in conjunction with the needle swing of the needle bar.

  The lower shaft is rotated in synchronization with the main shaft that is rotationally driven by the sewing machine motor, and the rotational driving force of the lower shaft is transmitted to the yarn catching hook by the driving force transmission system. Therefore, the rotation phase with respect to the lower shaft of the thread catching hook is adjusted to the rotation phase suitable for the needle swinging to the right in conjunction with the needle swing of the needle bar by the needle swing mechanism, When the needle is swung, the rotation phase is adjusted to an appropriate value.

  According to a second aspect of the present invention, in the first aspect of the invention, the driving force transmission system is externally fitted to the shuttle drive shaft, the drive gear fixed to the lower shaft, and the shuttle drive shaft so as to be movable in the axial direction. The phase adjusting mechanism is a first engaging portion and a second engaging portion that are engaged with each other via a groove cam and a cam portion that engages with the groove cam. The driven gear is moved in the axial direction in conjunction with the first engaging portion formed on the shuttle drive shaft, the second engaging portion formed on the driven gear, and the needle swing of the needle bar. And a movement drive means.

  According to a third aspect of the present invention, in the invention of the second aspect, the first engaging portion is a first helical spline engaging tooth, and the second engaging portion is engaged with the first helical spline engaging tooth. 2 helical spline engaging teeth.

  According to a fourth aspect of the present invention, in the sewing machine according to any one of the first to third aspects, the phase adjusting mechanism is configured such that the needle bar is positioned when the rotation direction of the yarn catching hook is counterclockwise as viewed from the operator of the sewing machine. When the needle swings to the right, the rotational phase with respect to the lower shaft of the thread catching hook is delayed, and when the needle bar swings to the left, the rotational phase with respect to the lower shaft of the thread catching hook is advanced.

  According to a fifth aspect of the present invention, in the sewing machine according to any one of the first to third aspects, the phase adjusting mechanism is configured such that the needle bar moves to the left when the rotation direction of the yarn catching hook is clockwise when viewed from the operator of the sewing machine. When the needle swings in the direction, the rotational phase with respect to the lower shaft of the thread catching hook is delayed, and when the needle bar swings in the right direction, the rotational phase with respect to the lower shaft of the thread catching hook is advanced.

  According to a sixth aspect of the present invention, in the invention of the second aspect, the movement driving means is provided with an input member that abuts on the axially orthogonal end surface of the driven gear, and is mounted on the shuttle drive shaft to urge the driven gear in the axial direction. It has a spring member and a link mechanism for transmitting the needle swing horizontal movement of the needle bar base drive shaft of the needle swing mechanism to the input member.

  According to a seventh aspect of the present invention, in the sewing machine according to the third aspect, the moving drive means includes an input member that abuts on the axially orthogonal end surface of the driven gear, and a shuttle drive shaft that urges the driven gear in the axial direction. It has a spring member, an actuator for driving the input member toward the driven gear, and a control means for controlling the actuator in synchronization with the needle swing of the needle bar.

  According to an eighth aspect of the present invention, in the invention of the third aspect, the movement driving means includes a braking torque applying mechanism for applying a braking torque to the driven gear, and a needle bar base drive shaft of the needle swing mechanism for the braking torque applying mechanism. And a link mechanism that generates a braking torque by transmitting the horizontal movement of the needle swing.

  According to a ninth aspect of the present invention, in the invention of the third aspect, the movement driving means includes a braking torque applying mechanism that applies a braking torque to the driven gear, an actuator that generates the braking torque in the braking torque applying mechanism, and the actuator And control means for controlling in synchronization with the needle swing of the needle bar.

  The sewing machine according to claim 10 includes a rotary balance interlocked and coupled so as to rotate synchronously with a main shaft of the sewing machine, a needle swinging mechanism that swings the needle bar, and a thread catching hook that is rotationally driven by the lower shaft. A transmission support member that is fixed to a needle bar crank connected to the main shaft and that transmits rotational force to the rotary balance and supports the rotary balance, and a rotational driving force of the transmission support member can be transmitted to the rotary balance and the needle The first phase adjusting mechanism that adjusts the rotational phase relative to the main shaft of the rotary balance in conjunction with the needle swing of the rod, and the driving force transmission system that transmits the rotational driving force from the lower shaft to the yarn catching hook, A second phase adjusting mechanism is provided that can transmit the rotational driving force and adjusts the rotational phase relative to the lower shaft of the yarn catching hook in conjunction with the needle swing of the needle bar.

  According to the first aspect of the present invention, in a sewing machine having a needle swing mechanism that swings the needle bar and a thread catching hook that is rotationally driven by the lower shaft, the rotational driving force is transmitted from the lower shaft to the thread catching hook. Since the phase adjustment mechanism is provided in the driving force transmission system, the rotational driving force of the lower shaft can be transmitted to the yarn catching hook by the driving force transmission system, and the rotation phase with respect to the lower shaft of the yarn catching hook is controlled by the needle swing mechanism. In conjunction with the needle swing of the needle bar, that is, if you swing the needle to the right, you can adjust the rotation phase suitable for it, and if you swing the needle to the left, adjust to the rotation phase that is appropriate for it. Can do.

  Therefore, the encounter between the tip of the sword and the eye of the needle can be realized at the optimal timing for both the needle swing to the right and the needle swing to the left of the needle bar. Time skipping can be reliably prevented.

  According to a second aspect of the present invention, the driving force transmission system includes a shuttle drive shaft, a drive gear fixed to the lower shaft, and an external fit on the shuttle drive shaft so as to be movable in the axial direction and meshing with the drive gear. The phase adjusting mechanism includes a groove cam and a first engagement portion and a second engagement portion that engage with each other via a cam portion that engages with the groove cam, and the shuttle drive shaft A first engagement portion formed on the driven gear, a second engagement portion formed on the driven gear, and a movement drive means for moving and driving the driven gear in the axial direction in conjunction with the needle swing of the needle bar. Therefore, the rotation of the lower shaft is transmitted to the driven gear via the drive gear, and the rotation of the driven gear can rotationally drive the yarn catching hook via the hook drive shaft, and the driven gear is interlocked with the needle swing of the needle bar. Is moved in the axial direction, so that the hook drive shaft having the first engaging portion engaged with the second engaging portion of the driven gear, that is, under the yarn catching hook Or delaying the rotational phase with respect to, it can be adjusted or promoted. Other effects similar to those of the first aspect are obtained.

  According to a third aspect of the present invention, the first engaging portion is a first helical spline engaging tooth, and the second engaging portion is a second helical spline engaging tooth meshed with the first helical spline engaging tooth. Therefore, the phase adjustment of the yarn catching hook is speeded up and smoothed by meshing (engaging) the second helical spline engaging teeth of the driven gear with the first helical spline engaging teeth of the hook driving shaft. Can be achieved. Other effects similar to those of the second aspect are achieved.

  According to a fourth aspect of the present invention, the phase adjusting mechanism is configured such that when the needle bar swings rightward when the thread catching hook is rotating counterclockwise as viewed from the operator of the sewing machine, When the rotation phase of the upper hook loop is delayed and the needle bar swings to the left, the rotation phase of the upper hook loop is advanced. When the needle swings to the right at an early timing, the rotation phase of the thread catching hook is delayed, so that it is possible to achieve optimum thread tightening for needle swinging to the right, and from the thread catching hook of the upper thread loop. Since the rotation phase of the thread catching hook is advanced when the needle swinging to the left where the thread removal timing is slow, the optimum thread tightening for the needle swinging to the left can be realized. Other effects similar to those of any one of claims 1 to 3 are provided.

  According to a fifth aspect of the present invention, the phase adjusting mechanism is configured to capture the thread when the needle bar swings leftward when the rotation direction of the thread catching hook is clockwise as viewed from the operator of the sewing machine. When the needle rotation is delayed to the right and the needle bar swings to the right, the rotation phase with respect to the lower shaft of the thread catching hook is advanced, so the timing of thread removal from the thread catching hook of the upper thread loop When the needle swings quickly to the left, the rotation phase of the thread catching hook is delayed, so that it is possible to achieve optimum thread tightening for the needle swinging to the left, and from the thread catching hook of the upper thread loop. Since the rotation phase of the thread catching hook is advanced when the needle swinging to the right is delayed, the thread tightening optimum for the needle swinging to the right can be realized. Other effects similar to those of any one of claims 1 to 3 are provided.

  According to a sixth aspect of the present invention, the movement drive means includes an input member that abuts on the axial orthogonal end surface of the driven gear, a spring member that is externally mounted on the shuttle drive shaft and biases the driven gear in the axial direction, and a needle. And a link mechanism that transmits the horizontal movement of the needle bar base drive shaft of the swing mechanism to the input member. Therefore, the horizontal movement of the needle bar base drive shaft is transmitted to the input member via the link mechanism and the driven gear. Can be moved and driven in the axial direction in conjunction with the needle swinging, and the movement of the driven gear can be reliably returned by the spring member. Other effects similar to those of the third aspect are achieved.

  According to a seventh aspect of the present invention, the movement drive means includes an input member that abuts on the axial orthogonal end surface of the driven gear, a spring member that is externally mounted on the shuttle drive shaft and biases the driven gear in the axial direction, and an input Since it has an actuator that drives the member toward the driven gear and a control means that controls this actuator in synchronism with the needle swing of the needle bar, it can be input by driving the actuator in conjunction with the needle swing of the needle bar. The driven gear can be reliably electrically driven and driven in the axial direction through the member, and the driven gear can be reliably returned and moved by the spring member.

  Moreover, it is possible to reliably move and return the driven gear by stopping the driving of the actuator. Furthermore, since no needle swing driving force of the needle swing mechanism is used, an increase in size of the needle swing mechanism can be prevented. Other effects similar to those of the second aspect are achieved.

  According to an eighth aspect of the present invention, the movement driving means includes a braking torque applying mechanism that applies a braking torque to the driven gear, and a horizontal movement of the needle bar base drive shaft of the needle swinging mechanism in the braking torque applying mechanism. And a link mechanism that generates braking torque by transmitting the needle swing horizontal movement of the needle bar base drive shaft to the braking torque applying mechanism via the link mechanism, and the braking torque generated by the braking torque applying mechanism is driven. By applying to the gear, the driven gear can be reliably moved and driven in the axial direction in conjunction with the swinging of the needle, so that the driving force for moving the driven gear in the axial direction by the link mechanism can be greatly reduced. In addition, the movement return of the driven gear can be reliably performed by the spring member. Other effects similar to those of the second aspect are achieved.

  According to the ninth aspect of the present invention, the movement driving means includes a braking torque applying mechanism for applying a braking torque to the driven gear, an actuator for generating the braking torque in the braking torque applying mechanism, and the actuator as a needle of a needle bar. Control means that controls in synchronization with the swing, so that the braking torque is generated by the braking torque applying mechanism by driving the actuator in conjunction with the needle swing of the needle bar, so that the generated braking torque is driven. By applying to the gear, the driven gear can be reliably driven to move in the axial direction in conjunction with the needle swing.

  Moreover, it is possible to reliably move and return the driven gear by stopping the driving of the actuator. Furthermore, since no needle swing driving force of the needle swing mechanism is used, an increase in size of the needle swing mechanism can be prevented. Other effects similar to those of the second aspect are achieved.

  According to the tenth aspect of the present invention, the rotary balance that is interlocked and connected to the main shaft of the sewing machine, the needle swinging mechanism that swings the needle bar, and the yarn catching hook that is rotationally driven by the lower shaft. Since the sewing machine has a transmission support member, a first phase adjustment mechanism, and a second phase adjustment mechanism, the rotational phase with respect to the main shaft of the rotary balance is interlocked with the needle swing of the needle bar by the first phase adjustment mechanism. When adjusted to advance relative to the rotational phase of the main spindle, the phase of the take-up thread take-up curve advances with respect to the conventional take-up thread take-up curve (reference) at the center of needle bar swing, and the needle bar When adjusted so as to be delayed with respect to the rotational phase of the main shaft in conjunction with the needle swing, the phase of the take-up thread take-up curve is delayed with respect to the conventional take-up thread take-up curve (reference) at the center of needle bar swinging To the right of the needle bar In any of the needle swing to the needle swing and leftward, it is possible to achieve an interference optimum yarn.

  On the other hand, the rotational driving force of the lower shaft can be transmitted to the yarn catching hook by the driving force transmission system, and the rotational phase with respect to the lower shaft of the yarn catching hook is linked to the needle swing of the needle bar by the needle swinging mechanism, that is, When the needle is swung to the right, it can be adjusted to a rotation phase suitable for it, and when it is swung to the left, it can be adjusted to a rotation phase suitable for it. Can be realized at the optimal timing for both the needle swing to the right and the needle swing to the left of the needle bar, and at the time of the needle swing to the right or left in the stitch formation It is possible to reliably prevent skipping.

  The sewing machine of the present embodiment can transmit the rotational driving force of the transmission support member fixed to the needle bar crank of the needle bar vertical movement mechanism and rotated synchronously with the main shaft to the rotary balance and rotates in conjunction with the needle swing of the needle bar. The rotation phase of the balance with respect to the main shaft can be adjusted by the first phase adjustment mechanism, and the second phase adjustment mechanism provided in the driving force transmission system for transmitting the rotation driving force from the lower shaft to the yarn catching hook, The rotational driving force of the thread catching hook can be adjusted in conjunction with the needle swing of the needle bar.

  As shown in FIGS. 1 to 3, the main shaft 4 disposed in the left-right direction on the arm portion 2 of the staggered sewing machine 1 is rotatably supported at a plurality of locations on the machine frame 2 </ b> A, and the head 2 a of the arm portion 2. , A needle bar vertical movement mechanism 5 that is connected to the left end of the main shaft 4 to drive the needle bar up and down, a needle swinging mechanism 6 that swings the needle bar left and right, and the like are disposed. 8 is provided. First, the needle bar vertical movement mechanism 5 will be briefly described.

  The needle bar 10 is supported by a U-shaped needle bar base 11 that is supported by the machine frame 2A so as to be movable in the left-right direction, and can be moved up and down. On the other hand, a needle bar crank (balance weight) 12 having a connecting pin 12a is fixed to the left end portion of the main shaft 4, and the upper end portion of the needle bar crank rod 13 is pivotally attached to the connecting pin 12a.

  A horizontal slide pin 14 is supported at the lower end of the needle bar crank rod 13 so as to be slidable in the left-right direction, and the left end (tip) of the slide pin 14 is fixed to the vicinity of the upper end of the needle bar 10. 15 is connected. Therefore, the rotation of the main shaft 4 causes the needle bar crank rod 13 to move up and down via the needle bar crank 12, so that the needle bar 10 moves up and down simultaneously via the needle bar holder 15 connected thereto.

  Next, since the needle swing mechanism 6 has a general configuration, it will be briefly described. The needle swing mechanism 6 is connected to a needle swing motor (not shown) formed of a stepping motor, a needle bar base drive shaft 17 connected to the needle swing motor, a slide pin 14, and a needle bar base drive shaft 17. It has a needle bar base 11 and the like.

  When the needle swing motor is driven in the forward direction, as shown in FIGS. 2-1 and 4, the needle bar base drive shaft 17 moves horizontally by a predetermined distance to the right, so that the slide pin 14 moves to the right. While sliding, the needle bar base 11 and the needle bar 10 simultaneously swing to the right hand swing position.

  When the needle swing motor is driven in reverse, as shown in FIGS. 3A and 3B, the needle bar base drive shaft 17 moves horizontally by a predetermined distance to the left so that the slide pin 14 slides to the left. At the same time, the needle bar base 11 and the needle bar 10 simultaneously swing to the left hand swing position.

  Next, the rotary balance device 20 will be described. The rotary balance device 20 is fixed to a needle bar crank 12 connected to the main shaft 4, transmits a rotational force to the rotary balance 9 and supports the rotary balance 9, and rotational drive of the transmission support member 21. A first phase adjusting mechanism 22 that can transmit force to the rotary balance 9 and adjusts the rotational phase of the rotary balance 9 relative to the main shaft 4 in conjunction with the swinging of the needle bar 10 is provided.

  As shown in FIGS. 2-1 to 3-1, a transmission support member 21 for transmitting a rotational driving force to the rotary balance 9 and supporting the rotary balance 9 is fixed to the left end portion of the connecting pin 12a. As shown in FIG. 2A, the transmission support member 21 has a substantially crank shape when viewed from the front, and a columnar connecting portion 21a is formed at the left end portion thereof as shown in FIG. A key member 23 facing left and right is fixed in a protruding manner at one end of the outer peripheral portion.

  Next, the first phase adjustment mechanism 22 will be described. The first phase adjusting mechanism 22 meshes with the internal tooth forming member 25 in which the helical spline internal teeth 25b are formed and the internal tooth forming member 25, as shown in FIGS. An external tooth forming member 26 formed with helical spline external teeth 26a, a horizontal movement transmission mechanism 27 for transmitting the horizontal movement of the needle bar base drive shaft 17 of the needle swing mechanism 6 to the internal tooth forming member 25, etc. ing.

  The inner tooth forming member 25 has helical spline inner teeth 25b concentric with the axis of the main shaft 4 on the inner peripheral portion of the annular tooth forming portion 25a, and the lead angle with respect to the axis of the main shaft 4 is viewed from the left. Thus, helical spline inner teeth 25b having a predetermined angle (for example, about 27 °) are formed counterclockwise. The inner tooth forming member 25 is fitted into the base end portion of the connecting portion 21a, and is supported by the connecting portion 21a so as to be movable in the left-right direction via an annular support wall portion 25c protruding to the inner peripheral side at the right end portion. .

  Further, a key groove 25d facing in the left-right direction is formed at one place on the inner peripheral side of the support wall portion 25c, and is engaged with the key member 23 of the connecting portion 21a so as to be movable in the left-right direction.

  On the other hand, the external tooth forming member 26 in which the helical spline external teeth 26a are formed on the outer peripheral portion has the same lead angle (for example, about 27 °) as the helical spline internal teeth 25b, and the internal tooth forming member 25 from the left side. The left end portion (tip portion) of the connecting portion 21a is fitted into a cylindrical connecting concave portion 26b formed inside thereof, and is connected to the connecting portion 21a by a set screw 28 so as to be rotatable through pressing friction. Has been. The base end portion 9a of the rotary balance 9 is fixed to the left end surface of the external tooth forming member 26 with a plurality of fixing screws (not shown).

  In this way, the inner tooth forming member 25 is parallel to the axis of the main shaft 4 as shown in FIG. 2A with respect to the outer tooth forming member 26 rotatably supported by the left end portion of the transmission support member 21. When the internal tooth forming member 25 is slid to the rightward moving position, the external tooth forming member 26 cannot rotate with respect to the transmission support member 21 via the key member 23 and the key groove 25d. 25b and the helical spline external teeth 26a are rotated clockwise as viewed from the left to advance the rotational phase of the rotary balance 9 relative to the main shaft 4 (see the two-dot chain line in FIG. 1 and FIG. 10).

  On the contrary, as shown in FIG. 3A, the inner tooth forming member 25 is parallel to the axis of the main shaft 4 with respect to the outer tooth forming member 26 rotatably supported by the left end portion of the transmission support member 21. When slid to the leftward movement position, the internal tooth forming member 25 cannot rotate independently with respect to the transmission support member 21 via the key member 23 and the key groove 25d, so that the external tooth forming member 26 becomes the helical spline internal tooth 25b. And the helical spline external teeth 26a, the counterclockwise rotation as viewed from the left is delayed, and the rotational phase of the rotary balance 9 with respect to the main shaft 4 is delayed (see the solid line in FIG. 1 and FIG. 10).

  As shown in FIGS. 1 to 3-1, the rotary balance 9 is composed of a rotating arm portion 9b extending from the base end portion 9a, an upper thread holding portion 9c of the tip end portion, and the like, and rotating with the base end portion 9a. A first upper thread holding point 9d and a second upper thread holding point 9e are formed between the arm portion 9b. By the way, as shown in FIGS. 1 and 2-1, a face plate cover 30 is fixed to an end portion of the machine casing 2A, and a left end portion of the external tooth forming member 26 is inserted into a circular opening 30a formed in the face plate cover 30. It is exposed to the outside.

  As shown in FIGS. 2-1 and 3-1, a balance cover 32 is provided on the head 2a so that the upper thread 18 hooked on the upper thread holding portion 9c of the rotary balance 9 does not come off. The balance cover 32 has a balance recess 32a.

  Therefore, the balance cover 32 is fixed to the face plate cover 30 with a fixing screw 33 via a pair of cylindrical support members 30b formed on the face plate cover 30, and the upper thread holding portion 9c of the rotary balance 9 is connected to the balance recess portion 32a. Therefore, the upper thread 18 is prevented from coming off from the upper thread holding portion 9c during sewing.

  Next, the horizontal movement transmission mechanism 27 will be described. This horizontal movement transmission mechanism 27 causes the internal tooth forming member 25 to move the horizontal movement amount by the needle swing mechanism 6 by a distance (for example, about 3 mm) corresponding to the phase change angle (for example, about 8 °) of the rotary balance 9. 4 has a first link mechanism 35 that is slid in the axial direction.

  That is, as shown in FIGS. 2-1 and 2-2, the connecting pin 36 is fixed to the upper end portion of the needle bar base 11, and is rotated by the pivot pin 37 to the machine frame 2 </ b> A on the rear side of the needle bar base 11. A connecting pin 36 is fitted into a bifurcated portion 38a formed at the front end portion of the first link plate 38 that is pivotally supported. A second link plate 39 disposed in the face plate cover 30 in the front-rear direction is pivotally supported by a pivot pin 40 at the center in the length direction, and the rear end of the first link plate 38 and the second link plate The rear ends of the two link plates 39 are connected to both ends of the third link plate 43 by connecting pins 41 and 42, respectively.

  A roller 44 is pivotally attached to the front end portion of the third link plate 43 and is engaged with an annular groove portion 25e formed in the internal tooth forming member 25 from below. Here, the ratio of the distance from the pivot pin 37 to the coupling pin 36 of the first link plate 38 and the distance from the pivot pin 37 to the coupling pin 42 is about 2.7: 1, and the maximum of the needle bar base drive shaft 17 is. When the needle swing horizontal movement amount (maximum needle swing amount of the needle bar 10) is 8 mm, the slide amount of the internal tooth forming member 25 is reduced to about 3 mm.

  As a result, since the lead angle between the helical spline outer teeth 26a and the helical spline inner teeth 25b is about 27 °, the inner tooth forming member 25 moves rightward relative to the outer tooth forming member 26 in parallel with the axis of the main shaft 4. When the position is slid by about 3 mm, the external tooth forming member 26 is rotated about 8 ° clockwise as viewed from the left, and the rotational phase of the rotary balance 9 relative to the main shaft 4 is advanced by 8 °.

  On the contrary, when the internal tooth forming member 25 slides about 3 mm to the left movement position parallel to the axis of the main shaft 4 with respect to the external tooth forming member 26, the external tooth forming member 26 is viewed from the left. It rotates about 8 ° counterclockwise and delays the rotation phase of the rotary balance 9 relative to the main shaft 4 by 8 °. Here, the first link mechanism 35 is composed of the first to third link plates 38, 39, 43, the pivot pins 37, 40, the connecting pins 36, 41, 42, and the like.

  Next, a lower shaft 48 is disposed in the bed portion 3 in parallel with the main shaft 4. A driving force transmission system 50 is provided on the bed portion 3 and transmits a rotational driving force from the lower shaft 48 to the rotary hook 8. The second phase adjustment mechanism (corresponding to the phase adjustment mechanism) 51 provided in the driving force transmission system 50 will be described.

  First, the driving force transmission system 50 will be described. As shown in FIGS. 7 to 8, a lower shaft 48 facing in the left-right direction that is rotationally driven in synchronization with the main shaft 4 is rotatably supported by bearings 55 at a plurality of locations on the machine frame 3 </ b> A. A first hook drive shaft 56 parallel to the lower shaft 48 is provided on the front side of the lower shaft 48, and a second hook drive shaft 58 that is orthogonal to the first hook drive shaft 56 and is provided in the front-rear direction is provided. Each of the second shuttle drive shafts 56 and 58 is rotatably supported by bearings 57 and 59 at a plurality of locations on the machine casing 3A. The rotary hook 8 is fixed to the rear end portion of the second hook drive shaft 58 in a rearward direction.

  The drive gear 60 fixed to the lower shaft 48 meshes with the driven gear 61 provided at the right end of the first shuttle drive shaft 56, and the first bevel gear 62 provided at the left end of the first shuttle drive shaft 56 and the second A second bevel gear 63 provided at the rear end portion of the shuttle drive shaft 58 is engaged. Therefore, in FIG. 7, when the lower shaft 48 rotates counterclockwise when viewed from the right, the first shuttle drive shaft 56 rotates clockwise when viewed from the right via the drive gear 60 and the driven gear 61. The second shuttle drive shaft 58 rotates counterclockwise through the bell gears 62 and 63 when viewed from the front.

  Next, a second driving force transmission system 50 is provided which can transmit the rotational driving force of the lower shaft 48 and adjusts the rotational phase of the rotary hook 8 relative to the lower shaft 48 in conjunction with the needle swing of the needle bar 10. The phase adjustment mechanism 51 will be described.

  As shown in FIGS. 7 to 9, the second phase adjusting mechanism 51 includes a helical spline external tooth 56 a formed on the right end portion of the first shuttle drive shaft 56 (the first helical spline engagement that is the first engaging portion). A helical spline inner tooth 61c formed on the inner peripheral portion of the driven gear 61 and meshed with the helical spline outer tooth 56a (this corresponds to a second helical spline engaging tooth which is a second engaging portion). And a movement drive mechanism 65 (which corresponds to movement drive means) that drives the driven gear 61 to move in the axial direction in conjunction with the needle swinging of the needle bar 10.

  The helical spline outer teeth 56a have a predetermined lead angle (for example, about 27 °) with respect to the shaft center of the first shuttle drive shaft 56, that is, a lead angle twisted counterclockwise when viewed from the right. In the driven gear 61, helical spline inner teeth 61c having the same lead angle as the helical spline outer teeth 56a are formed on the inner peripheral portion of the first gear forming portion 61a in the substantially right half portion, and in the substantially left half portion. A flat gear 61d that meshes with the drive gear 60 (flat gear) is formed on the outer periphery of the second gear forming portion 61b.

  Therefore, when the driven gear 61 slides to the right movement position shown in FIG. 7 with respect to the first shuttle drive shaft 56 (helical spline outer teeth 56a) when the needle bar 10 is swung to the right, the driven gear 61 is Since the first hook drive shaft 56 cannot rotate independently through meshing with the drive gear 60, the first shuttle drive shaft 56 slightly moves counterclockwise as viewed from the right through meshing of the helical spline inner teeth 61c and the helical spline outer teeth 56a. Since the second shuttle drive shaft 58 slightly moves clockwise in front view, the rotational phase of the rotary shuttle 8 relative to the lower shaft 48 of the sword 8a is delayed (see the two-dot chain line in FIG. 4).

  On the contrary, when the driven gear 61 slides to the left movement position shown in FIG. 8 with respect to the first shuttle drive shaft 56 (helical spline outer teeth 56a) when the needle bar 10 is swung to the left, the driven gear 61 is moved. Since the first hook drive shaft 56 is finely rotated clockwise as viewed from the right through the engagement of the helical spline inner teeth 61c and the helical spline outer teeth 56a. Since the second shuttle drive shaft 58 slightly moves counterclockwise when viewed from the front, the rotational phase of the rotary shuttle 8 relative to the lower shaft 48 of the sword 8a is advanced (see the two-dot chain line in FIG. 5).

  Next, the movement drive mechanism 65 that moves and drives the driven gear 61 in the axial direction in conjunction with the needle swing of the needle bar 10 will be described. As shown in FIGS. 7 and 8, the movement drive mechanism 65 is externally mounted on an input member 66 that is bifurcated, a second link mechanism 67 connected thereto, and a first shuttle drive shaft 56. A compression coil spring 68 (which corresponds to a spring member) that urges the driven gear 61 in the axial right direction is provided.

  As shown in FIGS. 7 and 8, the second link mechanism 67 includes a fourth link plate 70 facing left and right connected to the needle bar base drive shaft 17 of the needle swing mechanism 6, and the fourth link plate 70. The fifth link plate 71 and the like that are connected to the left end of the front and rear. The fifth link plate 71 is pivotally supported on the machine frame 3A by a pivot pin 72 at the center in the front-rear direction, and is connected to the center of the input member 66 by a connection pin 73 at the rear end of the fifth link plate 71. Has been. A roller 74 is pivotally attached to each of both leg portions of the input member 66, and each roller 74 can simultaneously contact the right end surface of the driven gear 61.

  Here, when the maximum needle swing horizontal movement amount of the needle bar base drive shaft 17 (the maximum needle swing amount of the needle bar 10) is 8 mm, the second link mechanism 67 causes the driven gear 61 to move in the same manner as the first link mechanism 35. Slide amount is reduced to about 3mm. When the needle bar 10 swings to the right, as shown in FIG. 7, the input member 66 retreats to the right via the second link mechanism 67, so that the driven gear 61 moves to the first shuttle drive shaft 56. By sliding to the rightward movement position by the spring force of the externally mounted compression coil spring 68, the rotational phase of the rotary hook 8 relative to the lower shaft 48 of the sword 8a is delayed (see FIG. 10).

  That is, since the rotation direction of the rotary hook 8 is counterclockwise as viewed from the operator, when the needle bar 10 swings to the right, the needle hole of the sewing needle 7 is larger than the needle swing to the left. It is necessary to delay the encounter of the tip 8a of the rotary hook 8 with respect to 7a. Therefore, when the needle bar 10 is swung to the right, the rotation timing of the rotary hook 8 with respect to the lower shaft 48 of the sword 8a is delayed, so that the timing of encounter between the eye hole 7a of the sewing needle 7 and the sword 8a can be optimized.

  On the other hand, when the needle bar 10 swings leftward, as shown in FIG. 8, the input member 66 is pressed and moved to the left via the second link mechanism 67, so that the driven gear 61 is a spring of the compression coil spring 68. Slide to the left movement position against the force, and advance the rotation phase of the rotary hook 8 relative to the lower shaft 48 of the sword 8a (see FIG. 10).

  That is, when the needle bar 10 swings to the left, it is necessary to accelerate the encounter of the sword tip 8a with the eye hole 7a of the sewing needle 7 as compared with the needle swing to the right. When the needle is swung, the rotation timing of the rotary hook 8 with respect to the lower shaft 48 of the sword 8a is advanced, so that the timing of the contact between the eye hole 7a of the sewing needle 7 and the sword can be optimized.

  Next, the operation of the staggered sewing machine 1 configured as described above will be described.

  As shown in FIG. 1, at the start of sewing, the upper thread 18 extending from a thread spool (not shown) passes through the first thread guide member 45 provided on the face plate cover 30, and then the rotating arm portion 9 b or the upper thread holding portion of the rotary balance 9. After being hooked on 9c, the upper threading is performed along a predetermined thread path through the second thread guide member 46, through the needle bar thread guide (not shown) to the eye hole 7a of the sewing needle 7. .

  When the sewing start switch is operated after the preparation for sewing is completed, the spindle 4 is rotated in a predetermined rotational direction by a sewing motor (not shown), so that the needle bar 10 is moved via the needle bar vertical movement mechanism 5. And the rotational driving force of the main shaft 4 is sequentially transmitted to the transmission support member 21, the internal tooth forming member 25, and the external tooth forming member 26, and the rotary balance 9 is synchronized with the main shaft 4. Driven by rotation.

  At the same time, the needle bar 10 is alternately switched between the left policy swing position and the right policy swing position by the needle swing mechanism 6, and the rotary hook 8 is moved by the lower shaft 48 and the driving force transmission system 50 connected to the main shaft 4. It is rotated in a predetermined rotation direction (counterclockwise as viewed from the operator). Therefore, staggered stitches are sequentially formed on the work cloth by the cooperation of the sewing needle 7 and the sword tip 8 a of the rotary hook 8.

  By the way, since the rotation direction of the rotary hook 8 is counterclockwise as viewed from the operator, when the needle bar 10 swings to the right by the needle swing mechanism 6 (see FIG. 4), the eye hole of the sewing needle 7 The timing at which the upper thread loop extending from 7a comes out of the rotary hook 8 is advanced. Therefore, as described above, when the needle bar 10 swings to the right, it is necessary to delay the encounter of the sword tip 8a of the rotary hook 8 with the eye hole 7a of the sewing needle 7.

  Therefore, when the needle bar 10 swings to the right, as shown in FIG. 7, the input member 66 is retracted to the right via the second link mechanism 67 and the driven gear 61 is moved to the right position. As described above, the rotational phase of the rotary hook 8 with respect to the lower shaft 48 of the sword 8a can be delayed, and the timing of contact between the eye hole 7a of the sewing needle 7 and the sword 8a can be optimized.

  Further, when the needle bar 10 swings to the right, as described based on FIGS. 2-1, 2-2, and 4, the first link mechanism 35 of the horizontal movement transmission mechanism 27 is used. Since the internal tooth forming member 25 slides to the right movement position by about 3 mm, the external tooth forming member 26 rotates clockwise as viewed from the left, and the rotary balance 9 fixed to the external tooth forming member 26 Advance the phase by approximately 8 °. As a result, as shown in FIG. 11, a take-up thread curve (phase advance) obtained by advancing a predetermined phase (about 8 °) with respect to the conventional take-up thread curve (reference) at the center of needle swing is obtained. .

  On the other hand, when the needle bar 10 swings to the left by the needle swing mechanism 6 (see FIG. 5), the timing at which the upper thread loop extending from the eye hole 7a of the sewing needle 7 comes out of the rotary hook 8 is delayed. Therefore, as described above, when the needle bar 10 swings leftward, it is necessary to accelerate the encounter of the sword tip 8a of the rotary hook 8 with the eye hole 7a of the sewing needle 7.

  Therefore, when the needle bar 10 swings leftward, as shown in FIG. 8, the input member 66 is pressed and moved to the left via the second link mechanism 67, and the driven gear 61 is moved to the left position. As described above, the rotational phase of the rotary hook 8 with respect to the lower shaft 48 of the sword 8a can be advanced, and the timing at which the eye 7a of the sewing needle 7 meets the sword 8a can be optimized.

  Further, when the needle bar 10 swings leftward, as explained based on FIGS. 3-1, 3-2, and 5, the first link mechanism 35 of the horizontal movement transmission mechanism 27 is used. Since the internal tooth forming member 25 slides to the left movement position by about 3 mm, the external tooth forming member 26 rotates counterclockwise as viewed from the left, and the rotary balance 9 fixed to the external tooth forming member 26. Delay the phase of approximately 8 degrees. As a result, as shown in FIG. 11, a take-up thread curve (phase delay) delayed by a predetermined phase (about 8 °) with respect to the conventional take-up thread curve (reference) at the center of needle swing is obtained.

  Here, as the change of the needle bar 10 to the left and right needle swing positions by the needle swing mechanism 6 is executed in the vicinity of the substantially uppermost position of the needle bar 10, the rotational phase of the rotary balance 9 with respect to the main shaft 4 changes at that time. Since the rotational phase of the rotary hook 8 with respect to the lower shaft 48 is also changed at that time, it is absolutely impossible to cause any trouble at each stitch formed while performing the needle swinging. Absent.

  Thus, the driving force transmission system 50 is movable in the axial direction of the first and second shuttle drive shafts 56 and 58, the drive gear 60 fixed to the lower shaft 48, and the first shuttle drive shaft 56. The second phase adjusting mechanism 51 includes a helical spline external tooth 56 a formed on the first shuttle drive shaft 56 and a helical gear formed on the driven gear 61. Since the spline inner teeth 61c and the movement drive mechanism 65 for moving and driving the driven gear 61 in the axial direction in conjunction with the needle swing of the needle bar 10 are provided, the rotation of the lower shaft 48 is driven via the drive gear 60. The rotation of the driven gear 61 is transmitted to the gear 61 so that the rotary hook 8 can be driven to rotate via the first and second hook drive shafts 56 and 58, and the driven gear 61 is pivoted in conjunction with the needle swing of the needle bar 10. Since it is moved in the direction of the heart, the helical gear of the driven gear 61 Or delaying the rotational phase with respect to the lower shaft 48 of the first shuttle drive shaft 56, i.e. the rotary hook 8 having a helical spline teeth 56a which mesh with the in-line teeth 61c, it can be adjusted or promoted.

  Therefore, when the rotation direction of the rotary hook 8 is counterclockwise as viewed from the operator, the rotational phase of the rotary hook 8 with respect to the lower shaft 48 is delayed when the needle bar 10 swings the needle to the right. Since the rotation phase of the yarn catching hook is delayed when the needle swinging from the loop yarn catching hook to the right is early, the optimum thread tightening for the rightward needle swing can be realized. Moreover, when the needle bar 10 swings leftward, the rotational phase with respect to the lower shaft 48 of the rotary hook 8 is advanced, and therefore the needle swinging to the left with a slow timing of thread removal from the thread catching hook of the upper thread loop is delayed. Sometimes the rotational phase of the yarn catching shuttle is advanced, so that it is possible to achieve optimum thread tightening for needle swinging to the left.

  Further, since the rotary balance 9, the transmission support member 21, and the first phase adjusting mechanism 22 that are interlocked and connected to the main shaft 4 are provided, the main phase 4 of the rotary balance 9 is provided by the first phase adjusting mechanism 22. Is adjusted so as to advance with respect to the rotational phase of the main shaft 4 in conjunction with the needle swing of the needle bar 10, the phase of the take-up thread take-up curve is the conventional take-up thread take-up at the center of needle bar swinging. When it is advanced to the amount curve (reference) and adjusted so as to be delayed with respect to the rotational phase of the main shaft 4 in conjunction with the needle swing of the needle bar 10, the phase of the take-up thread take-up curve becomes Since it will lag behind the conventional balance thread take-up curve (reference) at the center of movement, optimum thread tightening can be achieved with both the needle swing to the right and the needle swing to the left. Can be made.

  Next, a modified embodiment in which the embodiment is partially modified will be described.

  [1] As shown in FIG. 12, a phase adjustment solenoid 75 (which corresponds to an actuator) is adopted instead of the second link mechanism 67, and the input member 66 is retracted in the same manner as in FIG. You may make it move, and you may make it carry out the press movement similarly to FIG. In this case, as shown in FIG. 13, the phase adjusting solenoid 75 is configured to be driven and controlled by a control device 76 (which corresponds to control means).

  That is, the control device 76 includes a CPU 76a, a ROM 76b, a RAM 76c, and the like, and a movement position detection that detects a movement position when the needle bar base drive shaft 17 moves horizontally by the forward or reverse drive of the needle swing motor. A right policy swing signal and a left policy swing signal are received from a sensor (not shown), and the phase adjustment solenoid 75 is driven and controlled based on the needle swing signal.

  Here, the moving drive mechanism 65A includes an input member 66 that abuts on the axial orthogonal end surface of the driven gear 61, a compression coil spring 68 that is externally mounted on the first shuttle drive shaft 56 and urges the driven gear 61 rightward in the axial direction. The phase adjusting solenoid 75 drives the input member 66 toward the driven gear 61, and the control device 76 controls the phase adjusting solenoid 75 in synchronization with the needle swinging of the needle bar 10.

  Therefore, when the needle bar 10 swings rightward by the needle swing mechanism 6, the output shaft 75a is retracted without driving the phase adjusting solenoid 75, so that the rotary hook 8 can be moved in the same manner as in FIG. The rotational phase with respect to the lower shaft 48 of the sword tip 8a can be delayed. On the other hand, when the needle bar 10 swings to the left by the needle swing mechanism 6, the phase adjusting solenoid 75 is driven to advance the output shaft 75a, so that the sword tip 8a in the rotary hook 8 is the same as in FIG. The rotational phase with respect to the lower shaft 48 can be advanced.

  Therefore, the same effect as the above-described embodiment can be obtained, and the driven gear 61 is directly moved to the left pressing position by the needle swing driving force by the needle swing mechanism 6 by the second link mechanism 67 used in the embodiment. Compared with the case of making it, the enlargement of the needle swing mechanism 6 can be prevented.

  [2] As shown in FIGS. 14 and 15, the movement drive mechanism 65 </ b> B includes a braking torque applying mechanism 80 that applies a braking torque to the driven gear 61 </ b> A, and a needle bar base of the needle swing mechanism 6. You may make it comprise the 3rd link mechanism 81 etc. which transmit the needle swing horizontal movement of the drive shaft 17 grade | etc.,.

  The braking torque applying mechanism 80 will be described. Helical spline external teeth 61e having the same twisting direction and lead angle as the helical spline external teeth 56a are formed on the outer peripheral portion of the first gear forming portion 61a of the driven gear 61A. A cylindrical first braking gear 82 that meshes with the driven gear 61A and a second braking gear 83 that meshes with the first braking gear shaft 56 are fitted on the right end portion of the first shuttle driving shaft 56. The right end portion of the drive shaft 56 is rotatably and axially restricted by a bearing 84.

  Helical spline inner teeth 82a meshing with the helical spline outer teeth 61e are formed on the inner peripheral portion of the cylindrical portion in the substantially left half portion of the first braking gear 82. The helical spline is formed on the outer peripheral portion of the pivot portion in the substantially right half portion. Helical spline outer teeth 82b having smaller leads than the spline inner teeth 82a are formed. Helical spline inner teeth 83 a that mesh with the helical spline outer teeth 82 b are formed on the inner peripheral portion of the cylindrical portion of the substantially left half of the second braking gear 83.

  That is, the first braking gear 82 is supported by the first shuttle drive shaft 56 so as to be rotatable and axially movable in synchronization with the driven gear 61A, and the second braking gear 83 is rotated in synchronization with the first braking gear 82. The first shuttle drive shaft 56 is supported so as to be movable in the axial direction. The third link mechanism 81 includes a left-right sixth link plate 81a connected to the needle bar base drive shaft 17 of the needle swing mechanism 6 and a front-rear direction connected to the left end portion of the sixth link plate 81a. It consists of a seventh link plate 81b and the like.

  An input member 66 is connected to the tip of the seventh link plate 81b. Further, the brake shoes 85 are fixed to both legs of the input member 66 connected to the third link mechanism 81 configured as described above, and these brake shoes 85 are used when pressing the right end surface of the second brake gear 83. The generated braking torque can be applied.

  Since the braking torque applying mechanism 80 is configured as described above, the needle bar 10 is moved to the right by the needle swinging mechanism 6 while the lower shaft 48 and the first shuttle drive shaft 56 are rotationally driven in the illustrated rotational direction. In the case of the swing, the input member 66 is retracted to the right via the third link mechanism 81 as shown in FIG.

  At this time, since the brake shoe 85 of the input member 66 is not pressed against the second braking gear 83, the driven gear 61A is engaged with the helical spline inner teeth 61c and the helical spline outer teeth 56a of the first shuttle drive shaft 56. The first braking gear 82 is also meshed with the helical spline inner teeth 82a and the helical spline outer teeth 61e of the driven gear 61A, and is meshed with the helical spline outer teeth 82b and the helical spline inner teeth 83a of the second braking gear 83. Move to the right via

  However, when the first braking gear 82 contacts the second braking gear 83 and cannot move to the right, that is, the driven gear 61A contacts the first braking gear 82 and cannot move to the right in FIG. When retracted to the rightmost position shown, as described above, the rotation phase of the rotary hook 8 relative to the lower shaft 48 of the sword 8a can be delayed, and the timing when the eye 7a of the sewing needle 7 meets the sword 8a is optimized. it can.

  On the other hand, when the needle bar 10 swings leftward by the needle swinging mechanism 6, the input member 66 is pressed and moved to the left via the third link mechanism 81 as shown in FIG. At this time, since the brake shoe 85 of the input member 66 presses the right end surface of the second braking gear 83 to generate braking torque, the braking torque is first applied to the second braking gear 83 and the second braking gear 83 is also applied. The braking torque is applied to the first braking gear 82 that meshes with the first braking gear 82, and the braking torque is also applied to the driven gear 61 </ b> A that meshes with the first braking gear 82.

  As a result, the first braking gear 82 moves to the left via the engagement between the braking torque received from the second braking gear 83 and the second braking gear 83, and the driven gear 61 </ b> A receives the braking torque received from the first braking gear 82. It moves to the left pressing position through meshing with the first braking gear 82. Therefore, as described above, the rotation phase of the rotary hook 8 with respect to the lower shaft 48 of the sword 8a can be advanced, and the timing of encounter between the eye hole 7a of the sewing needle 7 and the sword 8a can be optimized.

  Thus, the driven gear 61A can be moved to the left pressing position with the braking torque generated by pressing the right end surface of the second braking gear 83 with the brake shoe 85 of the input member 66. In addition to obtaining the same effect, the pressing force of the input member 66 by the third link mechanism 81 can be greatly reduced as compared with the case where the third link mechanism 81 moves the driven gear 61A directly to the left pressing position. Can do.

  [3] As shown in FIGS. 16 and 17, the movement drive mechanism 65C employs a phase adjustment solenoid 90 (corresponding to an actuator) instead of the third link mechanism 81 used in the modified embodiment [2]. The input member 66 is retracted and moved in the same manner as in FIG. 14 by the phase adjusting solenoid 90, and is also pressed and moved in the same manner as in FIG. 15, so that the braking torque applying mechanism 80A similar to the above-described modified form [2] is employed. It may be. In this case, as shown in FIG. 18, the phase adjusting solenoid 90 is configured to be driven and controlled by a control device 76A (which corresponds to the control means).

  That is, the control device 76A includes a CPU 76a, a ROM 76b, a RAM 76c, and the like, and a movement position detection that detects a movement position when the needle bar base drive shaft 17 moves horizontally by the forward or reverse drive of the needle swing motor. A right policy swing signal and a left policy swing signal are received from a sensor (not shown), and the phase adjustment solenoid 90 is driven and controlled based on the needle swing signal.

  Here, the movement drive mechanism 65C includes a braking torque applying mechanism 80A that applies a braking torque to the driven gear 61A, a phase adjusting solenoid 90 that drives the braking torque applying mechanism 80A toward the driven gear 61A, and the phase adjusting solenoid. The control unit 76A is configured to control 90 in synchronization with the needle swinging of the needle bar 10.

  Therefore, when the needle bar 10 is swung to the right by the needle swing mechanism 6, the rotary shaft 8a is driven in the same manner as in FIG. The rotational phase of the sword tip 8a with respect to the lower shaft 48 can be delayed. On the other hand, when the needle bar 10 swings leftward by the needle swinging mechanism 6, the phase adjusting solenoid 90 is driven to drive the output shaft 90a forward, so that the sword tip in the rotary hook 8 is the same as in FIG. The rotational phase with respect to the lower shaft 48 of 8a can be advanced.

  Thus, the driven gear 61A is pushed to the left by the braking torque generated by driving the phase adjusting solenoid 90 and pressing the right end surface of the second braking gear 83 with the brake shoe 85 fixed to the input member 66. The third link mechanism 81 used in the modified embodiment [2] allows the driven gear 61A to be moved to the left by the needle swing driving force of the needle swing mechanism 6. Compared to the case of direct movement to the pressing position, the needle swing mechanism 6 can be prevented from being enlarged.

  [4] As shown in FIG. 19, one or a plurality of (for example, four) spiral groove cams 26c are formed at equal intervals on the outer peripheral portion of the external tooth forming member 26A. One or a plurality of (for example, four) helical cam portions 25f that can be engaged with the groove cams 26c are formed on the peripheral portion, and the internal tooth forming member 25A is formed via the groove cams 26c and the cam portions 25f. And the external tooth forming member 26A may be engaged with each other. Moreover, you may make it comprise the cam part 25f with a pin member.

  Further, one or a plurality of (for example, four) helical cam portions are formed on the outer peripheral portion of the outer tooth forming member 26A, and one or a plurality (for example, four) are formed on the inner peripheral portion of the inner tooth forming member 25A. ) Spiral groove cam, and the inner tooth forming member 25A and the outer tooth forming member 26A may be engaged with each other through the groove cam and the cam portion. Moreover, you may make it comprise a cam part with a pin member.

  [5] As shown in FIG. 20, one or a plurality of (for example, four) spiral groove cams 56b are formed at equal intervals on the outer peripheral portion of the first shuttle drive shaft 56A, and the inner periphery of the driven gear 61A. One or a plurality of (for example, four) helical cam portions 61e that can be engaged with the groove cams 56b are formed in the portion, and the driven gear 61A and the first gear 61a are connected to each other via the groove cams 56b and the cam portions 61e. The shuttle drive shafts 56A may be engaged with each other. Further, the cam portion 61e may be constituted by a pin member that can be engaged with the groove cam 56b.

  Further, one or a plurality of (for example, four) helical cam portions are formed on the outer peripheral portion of the first shuttle driving shaft 56A, and one or a plurality (for example, four) are formed on the inner peripheral portion of the driven gear 61A. Alternatively, the inner tooth forming member 25A and the outer tooth forming member 26A may be engaged with each other through the groove cam and the cam portion. Moreover, you may make it comprise a cam part with a pin member.

  [6] When the rotation direction of the rotary hook 8 is clockwise as viewed from the operator, the rotation phase of the rotary balance 9 is advanced and the needle bar 10 is moved to the right when the needle bar 10 swings the needle to the left. When rotating the needle, the rotational phase of the rotary balance 9 may be delayed. In this case, when the needle threading of the upper thread 18 from the rotary hook 8 is early, the thread tightening by the rotary balance 9 is accelerated, so that the optimum thread tightening for the needle swinging to the left is realized. When the needle threading of the upper thread 18 from the rotary hook 8 is delayed to the right, the thread tightening by the rotary balance 9 is delayed, so that the optimum thread tightening for the needle swinging to the right is realized. be able to.

  [7] When the rotation direction of the rotary hook 8 is clockwise when viewed from the operator, the needle bar 10 delays the rotation phase with respect to the lower shaft 48 of the rotary hook 8 when the needle bar 10 swings the needle to the left, and the needle bar When the needle 10 swings to the right, the rotational phase with respect to the lower shaft 48 of the rotary hook 8 may be advanced. In this case, since the rotational phase of the rotary hook 8 is delayed at the time of needle swinging to the left where the thread removal timing from the rotary hook 8 of the upper thread loop is early, optimum thread tightening for needle swinging to the left should be realized. In addition, it is possible to advance the rotation phase of the rotary hook 8 when the needle threading from the rotary hook 8 of the upper thread loop is delayed to the right, so that the optimum thread tightening for the rightward needle swing is realized. be able to.

  [8] The first link mechanism 35 of the horizontal movement transmission mechanism 27 may be configured by various link mechanisms in which one or a plurality of link plates are combined. In this case, the first link mechanism 35 can be configured such that the slide amount of the internal tooth forming member 25 with respect to the maximum needle swing amount of the needle bar 10 can be varied.

  [9] The first link mechanism 35 may be omitted, and the internal tooth forming member 25 may be directly driven by a solenoid or an air cylinder, or may be driven by an electric actuator such as a stepping motor or a DC servo motor. Also good. Further, instead of the phase adjustment solenoids 75 and 90, the actuator may be driven by an actuator such as an air cylinder, or an electric actuator such as a stepping motor or a DC servo motor.

  [10] The lead angle and twist direction of the helical spline inner teeth 25b, 61c, 82a, 83a and the helical spline outer teeth 26a, 56a, 61e, 82b are determined by the amount of needle swing and the sliding amount of the inner tooth forming member 25 and the driven gear 61. It may be set appropriately according to the above.

  [11] DLC coating on the helical spline inner teeth 25b, helical spline outer teeth 26a, cam portion 25f, etc. (When diamond-like carbon coating is applied, the helical spline can be driven with a smaller driving force due to the low friction coefficient effect of the DLC coating. The internal teeth 25b can be slid and driven.

  [12] Of course, the present invention can be applied to various types of sewing machines having a rotary balance, such as an eyelet sewing machine that forms an eyelet sewing machine, a decorative sewing machine, and the like.

It is the side view of the head which removed the balance cover of the staggered sewing machine which concerns on the Example of this invention. It is a front view which shows the internal structure (right policy swing state) of the head of a staggered sewing machine. It is a top view of the link mechanism of a right policy swing state. It is a front view which shows the internal structure (left policy swing state) of the head of a staggered sewing machine. It is a top view of the link mechanism of the left policy swing state. It is a rear view of a needle bar and a rotary hook that are swung to the right. It is a rear view of the needle bar and the rotary hook that are swung to the left. It is a disassembled perspective view of a transmission support member, an internal tooth formation member, and an external tooth formation member. It is a bottom view explaining the internal mechanism (at the time of the needle swing to the left) of a bed part. It is a bottom view explaining the internal mechanism (at the time of the needle swing to the right) of a bed part. It is a disassembled perspective view of a 1st shuttle drive shaft and a driven gear. It is a table | surface explaining the correlation of the needle swing of a needle bar, the phase of a rotary balance, and the phase of a rotary hook. FIG. 6 is a diagram showing a shuttle thread amount curve and a balance thread take-up amount curve when swinging left and right. FIG. 8 is a diagram corresponding to FIG. 7 according to a modified embodiment. It is a block diagram of the control system which drives and controls a phase adjustment solenoid with a control device. FIG. 8 is a diagram corresponding to FIG. 7 according to a modified embodiment. FIG. 9 is a diagram corresponding to FIG. FIG. 8 is a diagram corresponding to FIG. 7 according to a modified embodiment. FIG. 9 is a diagram corresponding to FIG. It is a block diagram of the control system which drives and controls a phase adjustment solenoid with a control device. FIG. 7 is a diagram corresponding to FIG. 6 according to a modified embodiment. FIG. 10 is a diagram corresponding to FIG. 9 according to a modified embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Staggered sewing machine 4 Main shaft 6 Needle swing mechanism 8 Rotary hook 9 Rotary balance 10 Needle bar 12 Needle bar crank 17 Needle bar base drive shaft 21 Transmission support member 22 First phase adjusting mechanism 25 Internal tooth forming member 25b Helical spline internal tooth 26 External teeth forming member 26a Helical spline external teeth 27 Horizontal movement transmission mechanism 50 Driving force transmission system 51 Second phase adjustment mechanism 56 First hook drive shaft 56a Helical spline external teeth 58 Second hook drive shaft 60 Drive gear 61 Driven gear 61A Driven Gear 61c Helical spline inner teeth 61e Helical spline outer teeth 65 Movement drive mechanism 65A Movement drive mechanism 65B Movement drive mechanism 65C Movement drive mechanism 66 Input member 67 Second link mechanism 68 Compression coil spring 75 Phase adjustment solenoid 76 Controller 76A Controller 80 Braking Torque applying mechanism 80A Braking torque applying machine Structure 81 Third link mechanism 82 First braking gear 82a Helical spline inner teeth 82b Helical spline outer teeth 83 Second braking gear 83a Helical spline inner teeth

Claims (10)

In a sewing machine having a needle swing mechanism that swings a needle bar and a thread catching hook that is rotationally driven by a lower shaft,
The driving force transmission system that transmits the rotational driving force from the lower shaft to the yarn catching hook can transmit the rotational driving force of the lower shaft and is linked to the needle swinging of the needle bar with respect to the lower shaft of the yarn catching hook. Provided a phase adjustment mechanism to adjust the rotation phase,
A sewing machine characterized by that. The driving force transmission system includes a shuttle drive shaft, a drive gear fixed to the lower shaft, and a driven gear externally fitted to the shuttle drive shaft so as to be movable in the axial direction and meshed with the drive gear,
The phase adjustment mechanism includes:
A first engagement portion and a second engagement portion that are engaged with each other via a groove cam and a cam portion that engages with the groove cam, the first engagement portion formed on the shuttle drive shaft; A second engagement portion formed on the driven gear;
A movement driving means for moving and driving the driven gear in the axial direction in conjunction with the needle swing of the needle bar;
The sewing machine according to claim 1, wherein:   The first engagement portion is a first helical spline engagement tooth, and the second engagement portion is a second helical spline engagement tooth meshed with the first helical spline engagement tooth. Item 3. The sewing machine according to Item 2.   When the needle catcher swings to the right when the direction of rotation of the thread catching hook is counterclockwise when viewed from the operator of the sewing machine, the phase adjusting mechanism rotates the rotation phase relative to the lower shaft of the thread catching hook. The sewing machine according to any one of claims 1 to 3, wherein the rotational phase of the thread catching hook relative to the lower shaft is advanced when the needle bar is swung to the left.   When the rotation direction of the thread catching hook is clockwise when viewed from the operator of the sewing machine, the phase adjusting mechanism adjusts the rotational phase relative to the lower shaft of the thread catching hook when the needle bar swings leftward. 4. The sewing machine according to claim 1, wherein when the needle bar is delayed and the needle bar swings to the right, the rotational phase of the thread catching hook relative to the lower shaft is advanced.   The movement drive means includes an input member that abuts on an axial orthogonal end surface of the driven gear, a spring member that is externally mounted on the shuttle drive shaft and biases the driven gear in the axial direction, and a needle bar base drive of the needle swing mechanism The sewing machine according to claim 2, further comprising a link mechanism that transmits a horizontal movement of the shaft to the input member.   The movement drive means includes an input member that abuts on an axially orthogonal end surface of the driven gear, a spring member that is externally mounted on the shuttle drive shaft and biases the driven gear in the axial direction, and the input member is moved toward the driven gear. 3. The sewing machine according to claim 2, further comprising an actuator for driving the actuator and a control means for controlling the actuator in synchronization with the needle swinging of the needle bar.   The movement drive means generates a braking torque by transmitting a horizontal movement of the needle bar base drive shaft of the needle swing mechanism to the braking torque applying mechanism and a braking torque applying mechanism for applying a braking torque to the driven gear. The sewing machine according to claim 2, further comprising a link mechanism.   The movement driving means includes a braking torque applying mechanism that applies a braking torque to the driven gear, an actuator that generates the braking torque in the braking torque applying mechanism, and a control that controls the actuator in synchronization with the needle swing of the needle bar. The sewing machine according to claim 2, further comprising: means. In a sewing machine having a rotary balance that is interlocked and coupled to rotate synchronously with a main shaft of the sewing machine, a needle swinging mechanism that swings a needle bar, and a thread catching hook that is rotationally driven by a lower shaft.
A transmission support member which is fixed to a needle bar crank connected to the main shaft and transmits a rotational force to the rotary balance and supports the rotary balance;
A first phase adjustment mechanism capable of transmitting a rotational driving force of the transmission support member to a rotary balance and adjusting a rotational phase of the rotary balance with respect to the main shaft in conjunction with a needle swing of a needle bar;
Provided in a driving force transmission system that transmits the rotational driving force from the lower shaft to the thread catching hook, is capable of transmitting the rotational driving force of the lower shaft and is linked to the needle swing of the needle bar. A second phase adjusting mechanism for adjusting the rotational phase with respect to the shaft;
A sewing machine characterized by providing