TWI448339B - Wire spring forming device - Google Patents

Description

Wire spring forming device

The present invention relates to a plurality of forming tools arranged in a radial shape centering on a quill of a guiding wire, and rotating a desired angle around a center line of the axis to form a desired forming tool pair A wire spring forming device in which a center line of a shaft center advances at a right angle or a slightly right angle and abuts against a wire fed from a front end portion of the shaft to form a wire spring.

The wire spring forming device described in the following Patent Document 1 includes: a shaft center, a turntable, a slide unit, and a slide plate; the shaft center guides the wire; the turntable is disposed to surround the axis Rotating; the sliding unit is radially arranged in a plurality of places in the circumferential direction of the turntable, and is movable forward and backward in a radial direction of the turntable; the slide is disposed on the outer side of the turntable and in a radial direction Where the circumferential direction corresponding to the sliding unit is slightly divided into a plurality of points, the servo motor belonging to the driving source is used to drive the forward and backward movement in the radial direction; wherein the required sliding plate advancement is located in the radial direction corresponding to the sliding plate The sliding unit at the position is pushed forward, and is advanced at a right angle or a right angle with respect to the center line of the shaft center, and the tool mounted on the sliding unit abuts against the wire fed from the front end portion of the shaft center, thereby The wire spring is formed.

[Advanced technical literature] [Patent Literature] [Patent Document 1]

Japanese Patent No. 3355092 (Japanese Patent Laid-Open No. 10-29028)

In the wire spring forming device shown in the above Patent Document 1, for example, a slide unit is provided at eight points in the circumferential direction of the turntable, and the slide plate for advancing the slide unit and the servo motor belonging to the drive source thereof are also disposed in the circumferential direction, and the like. Divided into 8 places. However, since the adjacent slides in the circumferential direction are separated from each other, the predetermined direction of the slide is not disposed and the slide unit cannot be advanced. That is, there is a large number of directions (dead angles) in which the tool cannot be brought close to the wire (in the eighth direction of the embodiment), and thus the wire may not be bent in an optimum direction, which may cause high-precision spring forming. The problem has happened.

The reason is that the inventors considered increasing the number of slides in the radial configuration, and reducing the direction (dead angle) that could not hold the tool against the wire. However, it is true that there is a reduction in dead angle and high-precision spring forming, but there are two new problems as shown below.

First, the number of servo motors also needs to be exactly equal to the number of slides, resulting in a significant increase in the cost of the wire spring forming device.

Secondly, the sliding units adjacent to each other in the circumferential direction are disposed apart from each other, and thus the dead angle cannot be completely eliminated.

Therefore, the inventors have considered increasing the number of slide plates disposed on the outer side of the turntable for the first problem described above, and each of the pair of slide plates adjacent in the circumferential direction is correspondingly provided with a servo motor, if driven by the servo motor. By making the corresponding pair of slides advance one by one, the direction (dead angle) of the tool can not be reduced, and the number of servo motors is also half of the number of slides.

Further, in the second problem, it is considered that if the slide plates adjacent to each other in the circumferential direction are arranged as close as possible in a range that does not interfere with each other, the turntable is rotated at a predetermined angle and is predetermined. The angularly inclined sliding unit must correspond to any of the slides in the radial direction so that the tool can be pressed against the wire (eliminating dead angles) from all directions of 360 degrees.

Therefore, the actual test device was used to verify the effect, and the result was confirmed to be very effective, so the patent application was filed this time.

The present invention has been completed on the basis of the problems of the prior art and the above findings of the inventors, and the first object thereof is to reduce the direction (dead angle) of the tool against the wire and increase the outer side of the turntable. The number of slide plates is configured without the need to increase the number of servo motors belonging to the drive source.

Furthermore, the second object is to provide a wire spring forming device that can hold the tool against the wire (completely free of dead ends) from all directions of 360 degrees.

In order to achieve the above first object, the wire spring forming device of the first and second aspects of the patent application includes: an axis, a turntable, a sliding unit, and a slide; the axis guides the wire; the rotary table The arrangement is rotatable about the circumference of the shaft; the sliding unit is radially arranged in a plurality of places in the circumferential direction of the turntable, and is movable forward and backward in a radial direction of the turntable; the slide is disposed on the swing a portion of the outer side of the stage that is slightly equally divided in the radial direction corresponding to the circumferential direction of the sliding unit, can be moved forward and backward in the radial direction by driving with a servo motor belonging to the driving source; and the required sliding plate advancement is located a sliding unit corresponding to the position of the sliding plate in the radial direction, protrudes and advances at a right angle or a right angle with respect to a center line of the shaft center, so that the tool mounted on the sliding unit abuts against the front end portion of the shaft center a wire is formed to form a wire spring; wherein the structure is configured to provide a servo motor corresponding to each pair of slide plates adjacent in the circumferential direction, and the servo horse is utilized So that the pair of drive sled alternatively proceeds.

As a specific slide drive mechanism that selectively advances a pair of slides by driving of a servo motor, for example, a rack-and-pinion type power transmission mechanism and a deformed Geneva-type power transmission mechanism can be considered.

The rack-and-pinion type power transmission mechanism is composed of a pair of racks and a semi-arc pinion as shown in the first item of the patent application scope; the pair of racks are disposed on the pair of slide plates, And extending in a radial direction; the semi-arc pinion gear is slightly orthogonal to the pair of slide plates, and is pivotally connected to an output shaft of the servo motor disposed between the pair of racks, and is coupled to the one Selectively engage the rack.

Furthermore, the modified Geneva-style power transmission mechanism is constituted by a rotating disk and a pair of notches as shown in the second item of the patent application scope; the rotating disk is pivotally connected to the one servo motor disposed between the pair of sliding plates An output shaft protruding from a pair of plugs that are equidistantly spaced from the center of rotation thereof at a predetermined distance in the radial direction and spaced apart at a predetermined angle in the circumferential direction; the pair of notches are opposite to the rear end of the pair of slides The side is disposed to be engaged with the pair of bolts within a half rotation of the output shaft of the servo motor.

(acting) in the state where the rotary table is rotated so that the required sliding unit (tool) is rotated at a desired angle around the center line of the shaft center, if the required servo motor is driven to advance the required slide plate, The required sliding unit (tool) pushed by the skateboard advances the center line of the shaft at a right angle or a right angle and abuts against the wire fed from the front end of the shaft.

Since a pair of adjacent slides in the circumferential direction are driven by the corresponding one of the servo motors, the total number of servo motors necessary for advancing (forward and backward movement) of the slide unit (tool) is as long as the number of slides is Half can be.

Furthermore, by increasing the number of slides by a factor of 2 without increasing the number of servo motors, the tool can be held against the wire from a more difficult direction of the conventional device (reducing the angle at which the tool cannot be held against the wire) (dead corner)).

Further, in the first aspect of the patent application, a pair of racks extending in a radial direction on the pair of slide plates are disposed on the pair of racks in a manner orthogonal to the pair of slides The output shaft of the servo motor is pivoted by a semi-arc pinion that is selectively engaged with the pair of racks within a half rotation of the output shaft.

(Action) A pair of adjacent slide plates in the circumferential direction are selectively advanced by the forward and reverse rotation of the output shaft of the servo motor corresponding to the pair of slide plates (the semi-arc pinion gears pivoted thereon).

For example, as shown in Fig. 5(a), if the output shaft (semi-arc pinion) of the servo motor rotates in the positive direction (clockwise), the semi-arc pinion meshes with one of the racks. The bar (skateboard) will advance to the intended position. Then, as shown in Fig. 5(b), if the output shaft (semi-arc pinion) of the servo motor is rotated in the reverse direction (counterclockwise) to the original position, the rack (skateboard) at the advanced position is provided. Will retreat to the original location. During this period, since the semi-arc pinion does not mesh with the other rack, the other rack (skateboard) does not advance or retreat.

On the other hand, as shown in Fig. 6(a), when the output shaft (semi-arc pinion) of the servo motor rotates in the opposite direction (counterclockwise), then as shown in Fig. 6(b), it faces in the positive direction ( When rotated clockwise, the semi-arc pinion meshes with the other rack, the rack (skateboard) advances to the predetermined position, and then retreats to the original position. During this period, since the semi-arc pinion does not mesh with the other rack, the other rack (skateboard) does not advance or retreat.

Furthermore, the second aspect of the patent application scope is formed on the output shaft of the servo motor disposed between the two slide plates in a manner orthogonal to the pair of slide plates, and is pivotally protruded from the center of rotation thereof at a radius a rotating disk that is equidistantly spaced in the direction and spaced apart from the pair of pins at a predetermined angle in the circumferential direction, and oppositely disposed on the rear end side of the pair of slide plates, opposite to the output shaft of the motor A pair of notches in which the pair of bolts are selectively engaged.

(Action) A pair of skateboards are advanced by the forward and reverse rotation of the output shaft (rotary disk) of the servo motor. For example, a tension coil spring is interposed between a pair of slide plates and a turntable, and a pair of slide plates often maintain a spring accumulating force toward the outer side in the radial direction. Then, as shown in Fig. 7(a), if the spring force of the tension coil spring is resisted, the output shaft (rotary disk) of the servo motor is rotated in the positive direction (clockwise), and the notch of one of the slide plates is engaged therein. A bolt, one of which is pushed forward in the radial direction and advanced to a predetermined position. Then, if the output shaft (rotary disk) of the servo motor is rotated in the reverse direction (counterclockwise) to the original position, the spring force of the tension coil spring is facilitated to retract the slider (notch) at the advanced position to the original position. At the office. During this period, since the right side of the bolt does not engage with the notch of the right slide, the right slide does not advance or retreat.

On the other hand, as shown in Fig. 8, when the spring force of the tension coil spring is reversed, the output shaft (rotary disk) of the servo motor is rotated in the opposite direction (counterclockwise), and then rotated in the positive direction (clockwise). The gap of the other slide plate will be engaged with the other bolt, and the other slide plate (the notch) will be pushed forward in the radial direction and advanced to the predetermined position, and then retracted to the original position by the spring force of the tension coil spring. During this period, since one of the bolts does not engage with the notch of one of the slide plates, one of the slide plates does not have a forward and backward movement.

Further, in order to achieve the above-mentioned second object, the third aspect of the invention is the wire spring forming device according to the first aspect of the invention, wherein the slide plate is not adjacent to each other in the circumferential direction. The areas that will interfere with each other are arranged in an annular shape.

In addition, in the fourth aspect of the invention, the wire spring forming device according to the second aspect of the invention, wherein the slide plates are adjacent to each other in the circumferential direction The phases of the interference are arranged close to each other in an annular shape.

(Action) Since the slide plates are arranged in an annular shape in such a manner as to be close to each other in the circumferential direction, the tool can be abutted against the wire even in any direction from 360 degrees (there is no direction in which the tool cannot be pressed against the wire ( Dead end)).

The wire spring forming device according to any one of claims 1 to 4, wherein the front end portion of the slide plate is provided with a center of curvature of the inner surface thereof. An arc cam that is substantially aligned with an arc of a center line of the shaft center; and a cam follower that abuts the arc cam of the slider at a rear end portion of the slide unit.

(acting) the sliding unit is pushed and advanced by the sliding plate. When the advancing and retracting direction of the sliding unit is deviated from the advancing and retracting direction of the sliding plate, the abutting portion between the sliding plate and the sliding unit generates a load such as friction or bending moment, and hinders sliding. The possibility of smooth advancement of the unit, but if the cam follower at the rear end of the sliding unit is located within the range of the arc cam that can abut the front end of the slider, the cam follower will be used when the slider pushes the sliding unit The inner surface of the circular arc cam is rolled, and the load such as friction or bending moment generated by the abutting portion between the sliding plate and the sliding unit is suppressed.

According to the wire spring forming device of the present invention, the number of servo motors can be reduced to half compared to conventional devices requiring a servo motor for each of the sliders (although the number of servo motors is small, the conventional wire spring can be obtained. The equivalent performance of the device) can greatly reduce the cost of the wire spring forming device.

Furthermore, by increasing the number of slides by, for example, two times, the tool can be brought into close contact with the wire from a direction that is difficult in the conventional device (reducing the angle (dead angle) that the tool cannot be pressed against the wire), thereby greatly increasing the line. The performance of the spring forming device.

Furthermore, according to the first item of the patent application scope, since the forward and backward movement of the rack and pinion type power transmission mechanism rack (skateboard) does link (follow) the rotation of the semi-arc pinion, it is not necessary to return the skateboard. Components such as spring members for the initial position simplify the structure of the device.

Furthermore, according to the second item of the patent application, in addition to the modified Geneva-type power transmission mechanism, the tension spring member for returning the slide plate to the initial position is required, and although the number of components which are the advance and retreat mechanisms of the slide plate is increased in this part, Compared with the rack and pinion type power transmission mechanism, the deformation of the Geneva-type power transmission mechanism is relatively simple, and this part makes the design of the skateboard advance and retreat mechanism easier, and the device can be provided at low cost.

According to Items 3 and 4 of the patent application, since the wire can be processed in any direction from 360 degrees (there is no way to make the tool abut against the direction of the wire (dead angle)), high-precision wire spring forming can be performed.

According to the fifth item of the patent application scope, even if the advancing and retracting direction of the sliding unit is somewhat offset from the advancing and retracting direction of the sliding plate, the abutting portion between the sliding plate and the sliding unit does not generate a load such as friction or bending moment, thereby ensuring the sliding unit ( The smooth progress of the tool) ensures long-term durability of the device.

Hereinafter, the method and apparatus for forming the wire spring of the present invention will be described in detail based on the drawings.

In FIGS. 1 and 2, the component symbol 1 supports the upper chassis 2 at its upper portion, and has a servo motor built therein (a pair of nip roller drive servo motors M1 for the pressure feed wire 41 and a rotary drive table 10 are rotatively driven). The servo motor M2 and the servo motor M3 for performing the forward/reverse movement of the slide unit 15 are positioned to drive the multi-axis numerical control device (in the illustrated embodiment, the slide unit 15 is eight, and thus the ten-axis numerical control device ). All 10 servo motors and mechanical components for forming the wire springs are mounted on the upper chassis 2.

As shown in Fig. 2, the component symbol 3 is a pair of nip rollers for the crimping wire 41, and is driven via a gear train that meshes with a gear fixed on the drive shaft 3a of the servo motor M1, and will be just the same. The wire 41 of a predetermined length is set to be fed toward the axis (guide guide of the wire 41) 6.

As shown in FIG. 4, the component symbol 5 is a mandrel that is rotatably supported by a cross-roller bearing on the upper chassis 2, and a central portion detachably fixes the shaft center. 6. The shaft center 6 is rotatable about the center line of the insertion hole of the wire (ie, the center line of the shaft center 6), and is fixed to the bearing press ring 2a fixed on the upper chassis 2, and is in a non-rotatable state. And use.

The component symbol 9 is fixed to the intermediate axis of the upper chassis 2, and the wire 41 is guided by the axial center 6 via the intermediate shaft 9 and fed to the front surface of the apparatus to form a wire spring.

The component symbol 10 is a turntable that is rotatably supported by the upper chassis 2 via a cross roller rotation bearing centered on the center line of the spindle center 6, as shown in FIG. 4, by being meshed on the output shaft of the servo motor M2. The ring gear 11 of the fixed gear 13 is rotated about the center line of the shaft center 6 and is positioned to be driven at a predetermined turning position.

On the surface of the turntable 10, as shown in Figs. 3 and 4, eight ball-type linear guides 16 composed of the guide rail 14 and the slide unit 15 are arranged at right angles with respect to the center line of the shaft center 6, and are arranged to radiate. shape. The guide rail 14 extends in the radial direction on the surface of the turntable 10, and the slide unit 15 is slidably assembled along the guide rail 14.

The axis 6 side of the linear guide 16 is referred to as a "front portion", and the outer side of the rear side of the linear guide 16 is referred to as a "rear portion", and the slide unit 15 is slid toward the axis 6 side to be "advanced" and will be slid in the opposite direction. Called "backward."

Then, as shown in FIGS. 3 and 4, a forming tool (a coil forming tool, a cutting tool, a holder tool, a heart tube, etc.) T is attached to the front end side of the slide unit 15, and at the rear end portion of the slide unit 15. A cam follower 21 that abuts on the circular arc cam 40 provided at the front end portion of the slider 33 to be described later is provided. Further, between the front end portion side of the slide unit 15 and the rear end portion of the guide rail 14, as shown in Figs. 3 and 5, a tension coil spring 24 belonging to the spring member is interposed, and the tab at the rear end side of the slide unit 15 is interposed. 22 is placed in contact with the stopper 23 on the rear end side of the guide rail 14, and the initial position of the slide unit 15 is set.

As shown in Fig. 1, Fig. 3, and Fig. 4, the outer side of the turntable 10 is disposed at a position slightly equal to 16 in the circumferential direction, and is arranged radially so as to be movable in the radial direction. The 16 slides 33 are circumferentially oriented. Each pair of adjacent ones is guided by a sliding guide 32 and assembled to be slidable in a radial direction, respectively. Further, as shown in Figs. 4, 5, and 6, the pair of slide plates 33, 33 adjacent in the circumferential direction are configured to be alternately advanced and retracted by the drive of the corresponding single servo motor M3.

Further, as shown in FIG. 3 and FIG. 4, the arc cam 40 mounts the inner surface 40a constituting the circular arc toward the axis 6 and is driven by the servo motor M3 to advance and retreat. The slide plate 33 (the arc cam 40 at the leading edge portion) advances the slide unit 15 to the reference position at the most advanced position toward the axis 6 so that the wire 41 fed from the front end of the shaft 6 abuts against the forming tool T forms the wire spring.

In this case, the inner surface 40a of the circular arc cam 40 is designed such that the center of curvature thereof coincides with the center line of the axial center 6 at the position of the circular arc cam 40 when the sliding unit 15 is advanced to the reference position, if available In the predetermined angle at which the circular cam 40 operates the linear guide 16, even if the position of the linear guide 16 is at any angle within the range, the progress of the forming tool T that advances to the reference position does not change. status.

In particular, since the cam follower 21 abuts against the circular cam 40 is provided at the rear end portion of the slide unit 15, the arc cam 40 pushes the cam follower 21 as the slide 33 advances, even if The advancing direction of the slide plate 33 and the advancing direction of the slide unit 15 are angularly displaced by the cam follower 21 along the inner surface 30a of the circular arc cam 40, and the abutment between the slide plate 33 and the slide unit 15 is still not A load such as friction or bending moment is generated, so that the slide unit 15 can be smoothly advanced.

Further, the circular arc cam 40 is arranged such that the adjacent cams 39 do not interfere with each other in the circumferential direction, and are arranged in an arc shape in close proximity, so that the tool T can be abutted against the wire even in any direction from 360 degrees. 41 (There is no way to make the tool T abut against the direction of the wire 41 (dead angle)).

Further, the related operation such as the retraction of the formed slide unit 15 and the rotation of the linear guide 16 is performed by an operation completely opposite to that when the forming tool T advances, and this can be easily adjusted by multi-axis numerical control.

Further, the pair of slide plates 33, 33 are provided with a pair of racks 17, 17 extending in the radial direction, and on the other hand, the output of a servo motor M3 disposed between the pair of racks 17, 17. On the shaft 35, a semi-arc pinion 36 that is in mesh with the pair of racks 17, 17 is pivoted within a half rotation of the output shaft 35.

In other words, between the pair of slide plates 33 and 33 and the output shaft 35 of the servo motor M3 corresponding thereto, the teeth of the forward and backward movements of the pair of slide plates 33 and 33 are alternately driven by the drive of the servo motor M3. ‧ pinion type power transmission mechanism A.

Specifically, the rack ‧ pinion type power transmission mechanism A is composed of a pair of racks 17 and 17 and a semi-arc pinion 36 . The pair of racks 17, 17 are fixed to the pair of slide plates 33, 33 and extend in the radial direction. The semi-arc pinion gear 36 is pivotally connected to the output shaft 35 of a servo motor M3 disposed between the pair of racks 17, 17 and is within a half rotation of the output shaft 35. The racks 17, 17 are alternatively engaged. The pinion gear 36 forms a tooth portion 36a that meshes with the tooth portion of the rack 17 only in a half area in the circumferential direction, and the tooth portion 36a is selected by the rotation direction of the output shaft 35 (pinion gear 36) of the servo motor M3. Engage only in one of the racks 17.

Next, with respect to the driving by the servo motor M3, the corresponding pair of slide plates 33, 33 are alternately advanced and retracted, and the slide unit 15 corresponding to the slide plates 33, 33 in the radial direction is moved forward and backward. The function of the pinion type power transmission mechanism A will be described with reference to Figs.

As shown in FIG. 5(a), at the position where the slide unit 15 corresponds to one of the pair of slide plates 33 (33A), 33 (33B) 33A in the radial direction, if the output shaft 35 of the servo motor M3 (semicircle) When the arcuate pinion gear 36) rotates in the positive direction (clockwise) indicated by the symbol R1, the semi-arc pinion gear 36 meshes with one of the racks 17 (17A); as shown in Fig. 5(b), one of them The rack 1717A (slide 33A) is advanced to a predetermined position. Therefore, the slide unit 15 which is pushed by the circular arc cam 40 at the front end portion of the slider 33 starts from the initial position where the rear end portion abuts against the stopper 23, and resists the spring force of the tension spring 24, so that the front end forming tool T Advance to the reference position that is opposite the axis 6.

Then, if the output shaft 35 (semi-arc pinion 36) of the servo motor M3 is rotated in the reverse direction (counterclockwise) to the original position as indicated by the symbol R2, the rack 17A (slide 33A) at the advanced position is provided. Then, it retreats to the original position shown in Figure 5(a). Therefore, as the slide plate 33A retreats, the slide unit 15 is retracted to the original position (initial position) shown in Fig. 5(a) by the spring force of the tension spring 24.

During this period, since the semi-arc pinion 36 does not mesh with the other rack 17B, the other rack 17B (slide 33B) does not move forward and backward.

On the other hand, as shown in Fig. 6(a), at the position where the slide unit 15 corresponds to the other slide plate 33B in the radial direction, when the output shaft 35 (semi-arc pinion 36) of the servo motor M3 faces the symbol R2 When the opposite direction (counterclockwise) is rotated and then rotated in the positive direction (clockwise) as indicated by the symbol R1, the semi-arc pinion 36 meshes with the other rack 17B, as shown in Fig. 6(b). It is shown that the other rack 17B (slide 33B) advances to a predetermined position and then retreats to the original position shown in Fig. 6(a). At this time, the slide unit 15 which is pushed by the slider 33B counteracts the spring force of the tension spring 24, advances the forming tool T at the front end to the reference position facing the axis 6, and then retreats with the retreat of the slider 33B. Go to the initial position shown in Figure 6(b).

In the meantime, since the semi-arc pinion gear 36 is not engaged with one of the racks 17A, one of the racks 17A (slide plate 33A) does not advance or retreat.

In addition, the basic function of the forward and backward movement of the slide unit 15 (forming tool T) will be described, and the rotary positioning drive operation of the turntable (sliding unit 15) by the servo motor M2 and the circular cam by the servo motor M3 will be described. The front-rear positioning drive operation of the 40 (forming tool T) and the rotational positioning drive operation of the nip roll 3 for feeding the wire 41 by the servo motor M1 are mutually synchronized by the multi-axis numerical control device.

7 and 8 show a slide driving mechanism (deformation Geneva type power transmission mechanism) which is a main part of the second embodiment of the wire spring forming device of the present invention.

In the first embodiment (Figs. 1 to 6), a power transmission mechanism (slide driving mechanism) interposed between a pair of slide plates 33 and 33 and a servo motor M3 corresponding thereto is a pair of racks 17 And 17, a semi-arc pinion 36 formed by a rack ‧ pinion type power transmission mechanism A. The pair of racks 17, 17 are disposed on the pair of slide plates 33, 33 and extend in the radial direction. The semi-arc pinion gear 36 is pivotally disposed on the output shaft 35 of a servo motor M between the pair of racks 17 and 17 so as to be orthogonal to the pair of the slide plates 33 and 33, and is in the servo The output shaft 35 of the motor M3 is selectively engaged with the pair of racks 17, 17 within a half rotation of the front and the back. However, in the second embodiment, the power transmission mechanism interposed between the pair of slide plates 33 and 33 and the servo motor M3 corresponding thereto is composed of a rotary disk 38 and a pair of notches 37 and 37. The deformation Geneva type power transmission mechanism B is constructed. The rotating disc 38 is pivotally connected to the output shaft 35 of a servo motor M disposed between the pair of slide plates 33, 33, and protrudes from the center of rotation thereof at equal distances in the radial direction and in the circumferential direction. A pair of bolts (cam followers) 39, 39 that exit at a predetermined angle. The pair of notches 37, 37 are disposed opposite to each other on the rear end side of the pair of slide plates 33, 33, and are slightly rotated within a half rotation of the output shaft 35 of the servo motor M3 with a pair of bolts (cam followers) 39, 39 choose a phase to engage.

That is, the output shaft 35 of the servo motor M3 disposed between the pair of slide plates 33, 33 is pivotally provided with a pair of plugs that are equidistant from the center of rotation in the radial direction and are separated at a predetermined angle in the circumferential direction ( Rotating disk 38 of cam followers 39, 39. On the other hand, a pair of notches 37, 37 are provided to face the rear end sides of the pair of slide plates 33, 33. The pair of notches 37, 37 are engaged with a pair of plugs (cam followers) 39, 39 on the side of the rotary disk 38 within a half rotation of the output shaft 35 of the servo motor M3.

Next, for the driving by the servo motor M3, the corresponding pair of slide plates 15, 15 are alternately advanced and retracted, so that the sliding unit 15 corresponding to the slide plates 33, 33 in the radial direction advances and retracts the Geneva-type power transmission. The action of the mechanism B will be described with reference to Figs.

As shown in Figs. 7 and 8, a tension coil spring 34 is interposed between the front end side of the pair of slide plates 33, 33 and the outer peripheral portion of the upper chassis 2, and the pair of slide plates 33, 33 are held at their respective rear end portions. The spring is stored in the direction in which the stopper 23a of the upper chassis 2 is disposed.

Then, as shown in FIG. 7(a), at the position where the slide unit 15 corresponds to one of the pair of slide plates 33 (33A), 33 (33B) in the radial direction, if the output shaft 35 of the servo motor M3 (rotary disk) 38) Rotate in the positive direction (clockwise) as indicated by the symbol R1, as shown in Fig. 7(b), wherein the notch 37 (37A) of one of the slide plates 33A and one of the plugs (cam followers) 39 (39A) When the phases are engaged, the slider 33A is pushed forward in the radial direction, and thus the slider 33A is moved against the spring force of the tension spring 34 and advanced to a predetermined position. Therefore, the slide unit 15 which is protruded by the circular arc cam 40 at the front end portion of the slider 33A reversing the spring force of the tension spring 24, and advances the forming tool T at the leading end to the reference position facing the axis 6.

Then, if the output shaft 35 (rotary disk 38) of the servo motor M3 is rotated to the original position in the opposite direction (counterclockwise) as indicated by the symbol R2, the slider 33A located at the advanced position utilizes the spring force of the tension coil spring 34, Go back to the original position shown in Figure 7(a). Therefore, with the retreat of the slide plate 33A, the slide unit 15 is retracted to the original position (initial position) shown in Fig. 7(a) by the spring force of the tension coil spring 24.

During this period, since the other plug (cam follower) 39B does not engage with the notch 37B of the other slider 33B, the other slider 33B does not advance or retreat.

On the other hand, as shown in Fig. 8(a), at the position where the slide unit 15 corresponds to the other slide plate 33B in the radial direction, when the output shaft 35 (rotary disk 38) of the servo motor M3 is directed in the opposite direction to the symbol R2 When (counterclockwise) is rotated and then rotated in the positive direction (clockwise) as indicated by the symbol R1, the other slider 33B (the notch 37B) is protruded toward the front in the radial direction by the other plug (cam follower) 39B. The spring force against the tension coil spring 34 is pushed forward to a predetermined position, and then retracted to the original position shown in Fig. 8(a). At this time, the slide unit 15 which is pushed by the slide plate 33B counteracts the spring force of the tension coil spring 24, and advances the forming tool T at the front end to the reference position facing the axis 6 and then retreats with the retraction of the slider 33B. Go to the initial position shown in Figure 8(a).

During this period, since one of the bolts (cam followers) 39A is not engaged with the notch 37A of one of the slide plates 33A, one of the slide plates 33A does not have a forward and backward movement.

Further, in the first and second embodiments described above, with respect to the driving by the servo motor M3, the corresponding pair of slide plates 15, 15 are alternately advanced and retracted so as to correspond to the slide plates 33, 33 in the radial direction. The sliding unit 15 (forming tool T) at the position, the rack-and-pinion type power transmission mechanism A that generates the forward and backward movements, and the deformed Geneva-type power transmission mechanism B are explained, but the drive of the servo motor M3 is used to make the corresponding The other sliding unit driving mechanism for the forward and backward movement of the pair of sliding plates 15 and 15 may be selected, and the double eccentric cam which is integrated with the eccentric cam in the axial direction may be considered to be pivotally connected to the output shaft of the servo motor M3. The double eccentric cam type power transmission mechanism that advances and retracts is selectively generated by the slide plates 15, 15 by mimicking the action of one of the eccentric cams provided on the slide plates 15, 15 respectively.

1. . . shelf

2. . . Upper chassis

2a. . . Bearing pressurizing ring

3. . . Pinch roll

3a. . . Drive shaft

5. . . Mandrel

6. . . Axis

9. . . Intermediate axis

10. . . Turntable

11. . . Ring gear

13. . . Fixed gear

14. . . guide

15. . . Sliding unit

15a. . . Cam follower (bolt)

16. . . Linear Guides

17, 17A, 17B. . . rack

twenty one. . . Cam follower

twenty two. . . Patch

23, 23a. . . Stop

twenty four. . . Tension coil spring (for sliding unit)

32. . . Sliding guide

33, 33A, 33B. . . skateboard

34. . . Tension coil spring (for skateboard)

35. . . Output shaft

36. . . Semi-arc pinion

36a. . . Tooth

37, 37A, 37B. . . gap

38. . . Rotating disk

39, 39A, 39B. . . Bolt (cam follower)

40. . . Arc cam

40a. . . Arc cam inner surface

41. . . Wire

A. . . Rack ‧ pinion type power transmission mechanism

B. . . Deformed Geneva power train

M1. . . Servo motor (for nip roll)

M2. . . Servo motor (for ring gear)

M3. . . Skateboard drive servo motor

T. . . Forming tool

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a front elevational view showing a first embodiment of a wire spring forming device of the present invention.

Figure 2 is a left side view of the same device.

Figure 3 is an enlarged front elevational view of the upper chassis of the same device.

Figure 4 is a longitudinal sectional view of the upper chassis (a cross-sectional view taken along line V-V of Figure 3).

Figure 5 is a slide drive mechanism (rack ‧ pinion type power transmission mechanism) of the main part of the wire spring forming device, (a) is a front view of the slide drive mechanism before one of the slide plates advances, and (b) one of the slide plates is advanced Front view of the skateboard drive mechanism.

Figure 6 is a slide drive mechanism (rack ‧ pinion type power transmission mechanism) of the main part of the wire spring forming device, (a) is a front view of the slide drive mechanism before the other slide is advanced, and (b) is another slide forward Front view of the skateboard drive mechanism.

Figure 7 is a view showing a slide driving mechanism (deformation Geneva type power transmission mechanism) of a main portion of a second embodiment of the wire spring forming device of the present invention, wherein (a) is a front view of a slide driving mechanism before a slide plate is advanced, and (b) is a A front view of the skateboard drive mechanism after a skateboard advances.

Figure 8 is the same as the slide drive mechanism (rack ‧ pinion type power transmission mechanism), (a) is the front view of the slide drive mechanism before the other slide is advanced, and (b) is the front view of the slide drive mechanism after the other slide is advanced .

2. . . Upper chassis

2a. . . Bearing pressurizing ring

3. . . Pinch roll

3a. . . Drive shaft

5. . . Mandrel

6. . . Axis

9. . . Intermediate axis

10. . . Turntable

11. . . Ring gear

13. . . Fixed gear

14. . . guide

15. . . Sliding unit

16. . . Linear Guides

17. . . rack

twenty one. . . Cam follower

twenty two. . . Patch

twenty three. . . Stop

32. . . Sliding guide

35. . . Output shaft

36. . . Semi-arc pinion

40. . . Arc cam

41. . . Wire

M1. . . Servo motor (for nip roll)

M2. . . Servo motor (for ring gear)

M3. . . Skateboard drive servo motor

T. . . Forming tool

Claims (5)

A wire spring forming device is provided with: an axis which guides a wire; a turntable configured to be rotatable around the axis; and a sliding unit which is slightly equally divided in the circumferential direction of the turntable a plurality of places are arranged in a radial shape and are movable forward and backward in a radial direction of the turntable; and a slide plate is disposed on an outer side of the turntable and is slightly equally divided in a radial direction corresponding to a circumferential direction of the sliding unit Wherein, the driving is driven by a servo motor belonging to the driving source to advance and retreat in a radial direction; and the required sliding advance is such that the sliding unit located at a position corresponding to the sliding position in the radial direction is opposite to the center line of the axis Pushing and advancing at right angles or slightly right angles, so that the tool mounted on the sliding unit abuts against the wire fed from the front end portion of the shaft to form the wire spring; characterized in that the pair is formed in the circumferential direction Each pair of adjacent slides is correspondingly provided with a servo motor, and the driving of the servo motor is used to advance the pair of slides one by one; on the pair of slides, the phase a pair of racks extending in a radial direction; on an output shaft of the servo motor that is slightly orthogonal to the pair of slide plates and disposed between the pair of racks, pivoting positively on the output shaft A semi-arc pinion gear that meshes with the pair of racks in a half rotation. A wire spring forming device is provided with: an axis which guides a wire; a turntable configured to be rotatable around the axis; and a sliding unit which is slightly equally divided in the circumferential direction of the turntable a plurality of places are arranged in a radial shape and are movable forward and backward in a radial direction of the turntable; and a slide plate is disposed on an outer side of the turntable and is slightly equally divided in a radial direction corresponding to a circumferential direction of the sliding unit Wherein, the driving is driven by a servo motor belonging to the driving source to advance and retreat in a radial direction; and the required sliding advance is such that the sliding unit located at a position corresponding to the sliding position in the radial direction is opposite to the center line of the axis a right angle or a slightly right angle pushes and advances, so that the tool mounted on the sliding unit abuts against the wire fed from the front end portion of the shaft, and the wire spring is formed; characterized in that the pair is formed in the circumferential direction Each pair of adjacent slides is correspondingly provided with a servo motor, and the driving of the servo motor is used to advance the pair of slides one by one; slightly orthogonal to the pair of slides And disposed on the output shaft of the servo motor of the two sliding blocks, pivoting the disc, the rotating disc protruding from the center of rotation at an equidistant distance in the radial direction and leaving at a predetermined angle in the circumferential direction a pair of plugs; and a notch provided on the rear end side of the pair of slide plates to be oppositely disposed within a half rotation of the motor output shaft and which is engaged with the pair of plugs. The wire spring forming device according to claim 1, wherein the slide plate is arranged in an annular shape in a range in which the adjacent members do not interfere with each other in the circumferential direction. The wire spring forming device according to claim 2, wherein the slide plate is arranged in an annular shape in a range in which the adjacent members do not interfere with each other in the circumferential direction. The wire spring forming device according to any one of claims 1 to 4, wherein the front end portion of the slide plate is provided with an arc having a center of curvature of the inner surface which is substantially coincident with a center line of the axis An arc cam; a cam follower that abuts against the arc cam of the slide plate is provided at a rear end portion of the slide unit.