JP2000334531A - Spring forming device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To work with easily retreating an other tool so that a tool is not interfered, to easily work a complicated shaped spring without restricting the degree of freedom of a spring working shape and to reduce a production cost as well as to improve productivity with facilitating a numerical control program. SOLUTION: The device is provided with circulation guide mechanisms 20A-20C to circulate plural circulating moving tables 23-25 together with each actuation mechanism 40-60 along the circulation orbit of circulation guide bodies 21, 22 around a quill 14 axial line, circulation drive mechanisms 30A-30C to respectively circulate each circulation moving table 23-25, reciprocation drive mechanisms 70-90 respectively reciprocating together with each working tool T1-T4 and a control means to relevantly each drive mechanism so that one or plural working tools are moved/positioned to in circulation setting positions and reciprocation setting positions, a wire rod W fed out from a quill 14 is bent, wound or cut.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD OF THE INVENTION

[0002] The present invention relates to a quill for guiding a wire fed from a rear surface side of a molded substrate to a spring molding space on a front surface side,
A plurality of tool operating mechanisms that movably carry forward and backward movable processing tools for bending, winding, or cutting a wire in front of the quill; and a coil having a curved or straight hooking leg. The present invention relates to a spring forming apparatus for manufacturing a spring, a wire spring, a wire component other than a spring member, and the like.

[0003]

[Prior art]

[0004] Conventional spring forming devices include:
For example, Japanese Patent Application Laid-Open No.
-29028 (hereinafter referred to as conventional publication A), Japanese Patent Laid-Open No. 10-763 relating to a tool operating device of a coil spring manufacturing machine.
An invention disclosed in Japanese Patent Publication No. 40 (hereinafter referred to as conventional publication B) and the like is known. In the following description of these prior arts, the reference numerals described in the respective publications are used, so that the reference numerals of the related art or the present invention overlap with each other. This is applied only to the column of (1).

[0005] On the other hand, the invention disclosed in the conventional publication A is a wire spring in which three or more forming tools can advance and retreat at a right angle to the center axis of the quill 6 as shown in FIGS. A turning table 10 capable of radially mounting a slide unit 15 (corresponding to a tool operating mechanism of the present invention) on which each forming tool is mounted and capable of turning around a quill 6; A first drive means for rotating and driving the forming tool to a predetermined turning position, and a second drive means for radially disposing at least the number of the slide units 15 outside the swivel table 10 to advance and retreat each forming tool, And a third driving means for feeding the wire.

Further, in the apparatus having the above-described structure, after the desired forming tool is stopped at a predetermined turning position by turning the turning table 10 by the first driving means, the desired forming is stopped by the second driving means. This is a method in which a tool is advanced to a predetermined forward position, and a desired forming tool is abutted against a wire fed from the quill 6 by a third driving means to form a wire spring. The turning table 10 of the conventional publication A corresponds to the revolving moving table of the present invention, but the revolving moving table of the present invention is constituted by a plurality.

[0007] The prior art A discloses that the wire can be wound, bent or cut from a desired turning angle position with respect to the prior art cited at the time of the invention. And easy to form springs of complex shapes,
It describes that setup work can be simplified and time can be reduced.

However, the invention of the conventional publication A is
The plurality of second driving means are respectively moved by the respective arc cams 39 which can be moved forward and backward by the respective slide units 1.
5, a desired forming tool is moved forward and backward through a cam follower 21 provided in the cam follower 2.
The effective advance / retreat operation angle at which 1 can contact the inner surface 39a of the arc cam 39 is clockwise and counterclockwise with respect to the advance / retreat movement axis of the arc cam 39 shown in FIG.
2.6 180 × 10 ^-1 rad [15 °] (5.2360 × 10 ^-1 rad [3 over the entire area that can contact the inner surface 39a of the arc cam 39)
0 °]).

That is, even if a maximum of eight forming tools are arranged, the cam follower 21 corresponding to a desired forming tool can be used.
Is pivotally positioned in an inoperative space formed between the adjacent circular arc cam 39 and the circular cam 39, which cannot move forward and backward, and moves the desired forming tool clockwise and clockwise from the linear movement axis of the circular cam 39. 2.6180 each counterclockwise
More than × 10 ^-1 rad [15 °] 5.2360 × 10 ^-1 rad [30
°] within 2.6180 × 10 ^-1 rad [15 °].

In order to reduce the inoperative space, the servomotor 12 of the first driving means and the servomotor 34 of the second driving means are controlled in two stages or are controlled in parallel, so respectively clockwise and counterclockwise the cam follower 21 corresponding to the forming tool relative to the forward and backward movement axis of the arcuate cam 39, 3.4907 × 10 ^-1
Even if it is positioned at the maximum turning angle position of rad [20 °] (6.9813 × 10 ^-1 rad [40 °] in the entire area where it can come into contact with the arc cam 39), the desired forming tool can be moved forward and backward along the axis of the arc cam 39. Clockwise and counterclockwise from
3.4907 × 10 ^-1 rad [20 °] exceeded 4.3633 × 10 ^-1 r
You cannot move back and forth between 8.7266 × 10 ^-2 rad [5 °] within ad [25 °].

Further, in the invention of the conventional publication A, since the arc cam 39 is provided on the upper base 2, when at least one of the slide units 15 is advanced to the forward position, a plurality of slide units 15 are provided. Cannot be swiveled.
That is, as shown in FIG. 3, for example, when the slide unit 15 illustrated directly above the quill 6 is moving forward, the turning unit 10 is turned to move the slide unit 15 immediately above. Arc cam 39
This is because the right or left adjacent slide unit 15 collides and interferes.

Further, in the invention of the conventional publication A, since each forming tool is moved forward and backward by the plurality of arc cams 39 via the cam followers 21 provided in each slide unit 15, for example, as shown in FIG. When the slide unit 15 shown immediately above the quill 6 is moving forward and the slide unit 15 on the right or the left side is advanced, the arc cam 3 to be brought into contact with the quill 6 is moved forward.
9 and the arc cam 39 interfere and cannot be advanced.

Next, as shown in FIGS. 4 to 6, the invention disclosed in the other conventional publication B is a front surface of the unit mounting frame 2 which allows the cutting and bending tool to advance and retreat at symmetrical positions with the quill 10 interposed therebetween. The cutting and bending units 20 and 20 arranged in the quill 10 can move forward and backward in the quill axis direction at a position in front of the quill 10, and can rotate about the quill axis.
A tool holder 50 rotatably provided about a vertical axis perpendicular to the quill axis and having a plurality of tools detachably provided around the vertical axis; and a tool holder 50 capable of positioning the tool holder 50 forward and backward. 1 drive means, second drive means capable of rotationally positioning the tool holder 50 about the quill axis, and third drive means capable of rotationally positioning the tool holder 50 about a vertical axis. Device.

In the apparatus having the above-mentioned structure, the tool holder 50 is advanced to a predetermined forward position by the first drive means, and the tool holder 50 is moved by the second drive means.
Is rotated to a predetermined rotation angle position around the quill axis,
A desired tool is selected by rotating and positioning the tool holder 50 by the third driving means, and the bending tool of the bending unit 20 is advanced as required to form a coil spring.

In this conventional publication B, a tool holder 50 to which a plurality of tools can be attached and detached is rotated about a quill axis around a vertical axis with respect to the prior art cited in the invention. Since it is possible to form the wire from a free rotation angle position around the quill axis, there is no restriction on the spring forming direction, and complicated spring forming becomes extremely easy. With
Since it does not take much time to adjust the molding timing,
It is described that a wide variety of small amounts of springs can be easily formed.

However, the invention of the conventional publication B is
The tool holder 50 is configured to move a desired tool selected from a plurality of tools forward and backward in the quill axis direction and to rotate around the quill axis, as in the cutting and bending units 20 and 20. It cannot move forward or backward in a direction perpendicular to the quill axis. For this reason, the process of bending the wire rod by advancing the tool in a direction perpendicular to the quill axis depends solely on the bending tool of the bending unit 20 that cannot rotate around the quill axis, and during the processing of the spring, The tool cannot be selectively rotated to the optimal rotation setting position. Further, the tool operating device 40 and the tool holder 50 can be provided only at a position in front of the quill 10.

[0017]

[Problems to be solved by the invention]

As described above, in the invention according to the conventional publication A, the effective advance / retreat operation angle of the forming tool is limited by the inoperative space in which the forming tool cannot move forward / backward. There is a problem that a spring having a complicated shape cannot be easily processed due to restrictions.

In order to make up for this problem, for example, a large number (eight) of forming tools must be arranged as in the embodiment, so that the structure becomes complicated and the equipment and the forming tools are not provided. The manufacturing cost is high, and the numerical control program for controlling each driving means is complicated, so that there is a problem that the manufacturing cost cannot be reduced and the productivity cannot be improved.

The above-mentioned inactive space can be reduced by controlling the servomotor 12 of the first driving means and the servomotor 34 of the second driving means in two steps or in parallel. There is a problem that the numerical control program for controlling each driving means is complicated, and the machining cycle time per spring becomes long, so that it is impossible to improve the productivity and reduce the manufacturing cost.

Further, the drive source mounting table 2 'shown in FIG.
It is possible to reduce the inactive space by adding the auxiliary cam 40 shown in FIG. 7 to the arc cam 39. However, this involves a problem that unnecessary setup man-hours are required and the numerical control program becomes complicated. there were.

Further, when at least one of the slide units 15 has advanced to the forward position, the plurality of slide units 15 cannot be swiveled. After retreating to the end position, it is necessary to turn the slide unit 15, and when changing tools for changing the spring working process, there is a disadvantage that the slide unit 15 cannot be turned simultaneously with the forward and backward movement. For this reason, the numerical control program for controlling each driving means is complicated, and the machining cycle time per spring becomes long, so that it is not possible to improve the productivity and reduce the manufacturing cost. was there.

Further, when the adjacent slide units 15 are to be advanced, respectively,
9 and the arc cam 39 interfere with each other and cannot be advanced, so that the degree of freedom of the spring processing shape is restricted, and there is a problem that a spring having a complicated shape cannot be easily processed.

Next, the invention according to the other conventional publication B is as follows:
As described above, each processing tool of the tool holder 50 is cut,
Unlike the bending units 20 and 20, they cannot be moved back and forth in the direction perpendicular to the quill axis,
Each of the processing tools of the cutting and bending units 20 and 20 cannot be selectively rotated to the optimum rotation setting position about the quill axis, so that the degree of freedom of the spring processing shape is restricted and a complicated shape is required. There is a problem that the spring cannot be easily processed.

The tool operating device 40 and the tool holder 50
Means that it can be provided only at the front position of the quill 10, so that the workability of exchanging working tools and adjusting test windings is poor, and requires a great deal of man-hours, thereby improving productivity and reducing manufacturing costs. There was a problem that it was not possible.

The present invention has been made in view of the above-described problems, and has as its object the purpose of one or more processing tools to make the quill axis move around the quill axis during spring processing. To be able to revolve to the optimal revolving setting position, and to allow other processing tools to be easily evacuated and processed so as not to interfere with the relevant processing tool. Springs of various shapes can be easily processed, and the numerical control program can be simplified to reduce manufacturing costs and improve productivity.
An object of the present invention is to provide a spring forming apparatus that can simplify the structure of the spring forming apparatus and reduce the manufacturing cost of the apparatus and the forming tool.

[0027]

[Means for Solving the Problems]

In order to achieve the above object, according to the present invention, there is provided a quill for guiding a wire fed from a rear surface of a molded substrate to a spring molding space on a front surface, and substantially converges on the quill axis. Each of the sliding members that can move forward and backward along each radial movement axis is individually provided, and each processing tool that bends, winds, or cuts the wire in front of the quill is movably supported. A spring forming apparatus including a plurality of tool operating mechanisms, wherein the plurality of tool operating mechanisms are individually detachable on a front surface of the molded substrate, and are arranged on a trajectory around a quill axis. A circulating guide mechanism that circulates a plurality of circulating carriages that can individually circulate along the circling guide mechanism, and a circulating drive mechanism that individually circulates each circulating carriage of the circulating carriage with a respective tool operating mechanism; each A reciprocating drive mechanism for individually moving the respective sliding bodies of the tool operating mechanism together with the respective working tools, and one or more working tools of the respective tool operating mechanisms in a circling setting position and a reciprocating setting position, respectively. Control means for controlling the orbiting drive mechanism and the reciprocating drive mechanism in relation to move and position, so as to orbit and / or reciprocate one or more working tools around the quill axis. This is a spring forming device that is moved and positioned.

According to the first aspect of the present invention, each of the tool operating mechanisms enables the individually removably movable orbiting carriage to be individually orbitably movable along the orbit, so that one or more of the orbiting carriages can be moved around the quill axis.
Since one or a plurality of processing tools are positioned by orbiting and / or moving forward and backward, the processing tools can be selectively orbitally moved to an optimum rotation setting position during processing of a spring, and This has the effect that other processing tools can be easily retracted and processed so as not to interfere with each other.

By this action, a spring having a complicated shape can be easily machined without restricting the degree of freedom of the spring machining shape, and productivity can be improved by simplifying a machining program. In addition, since the number of processing tools to be provided can be reduced, the manufacturing cost of the processing tools and the structure of the spring forming device can be simplified to reduce the manufacturing cost.

The orbiting guide mechanism according to the second aspect of the present invention is the orbiting guide mechanism wherein the orbiting surface fixed to the molded substrate and capable of orbiting each of the orbital moving bases is formed along the orbital path. A guide body, each of the orbital moving tables provided so as to face the orbiting guide body, respectively, and engaged with the orbital moving table to engage with the orbital surface of the orbiting guide body and rotate. And a plurality of rolling wheels that can revolve, and by the orbiting guide body and each of the rolling wheels,
Each of the orbiting moving tables can be individually orbitally moved together with each of the tool operating mechanisms.

According to the second aspect of the present invention, in the orbiting guide mechanism, each orbital moving base is provided on the orbital track together with the respective tool operating mechanism by the orbiting guide body and each of the rolling wheels capable of rotating and revolving. Since the tool can be individually orbited along, it is possible to smoothly move the working tool to the orbit setting position and smoothly retract other working tools.

In the orbiting guide of the orbiting guide mechanism according to the third aspect of the present invention, the orbiting surface is formed in a convex or concave shape, and the convex or concave portion is formed toward the quill axis. The inner raceway surface, and the outer raceway surface formed outward, the rolling wheels,
At least two rolling wheels that can be engaged with the inner raceway surface and the outer raceway surface are attached to each of the orbital moving tables.

According to the third aspect of the present invention, the orbiting guide body of the orbiting guide mechanism is configured such that the orbital raceway surface is formed of a convex or concave inner peripheral raceway surface and an outer peripheral raceway surface and is engaged with these. Since at least two rolling wheels are provided, it is possible to secure the holding force of each of the orbital moving tables that orbits each of the tool operating mechanisms.

Further, the orbiting drive mechanism according to the invention of claim 4 is a plurality of mechanisms for individually orbiting the orbital moving tables of the orbital guide mechanism together with the respective tool operating mechanisms, The mechanisms are individually provided on each of the orbiting moving tables of the orbiting guide mechanism.

According to the fourth aspect of the present invention, the orbiting drive mechanisms are individually provided on the orbital moving tables of the orbital guide mechanism, respectively. Depending on the required number of machining tools,
Each of the orbiting moving tables of the orbiting guide mechanism can be selectively and easily added and removed together with each of the tool operating mechanisms. In addition, assuming the maximum required number of machining tools, it is possible to eliminate waste such as constructing a revolving drive mechanism corresponding to the maximum required number in advance, thereby simplifying the structure of the spring forming device and reducing the manufacturing cost. Can be achieved.

Further, according to a fifth aspect of the present invention, the orbiting drive mechanism is integrally fixed to the molding substrate at a position near the orbital guide mechanism and has a tooth shape on a circumference centered on the quill axis. The fixed gears provided, the rotating gears provided so as to be meshable with the fixed gears at positions near the orbiting moving tables of the orbiting guide mechanism, and the respective rotating gears respectively attached to the orbiting moving tables. Each rotation driving servomotor for individually rotating the rotation driving servomotor, and the control means controls each rotation driving servomotor individually for rotation positioning. By rotating the gears individually, each of the orbital moving tables is individually orbitally moved together with the respective tool operating mechanism, and each of the working tools is positioned at the orbital setting position.

According to the fifth aspect of the present invention, the orbiting drive mechanism controls each of the orbital drive servomotors individually for rotational positioning control, so that each orbital moving table can be moved along the orbital path together with the respective tool operating mechanism. To move around individually
Since each processing tool is positioned at the rotation setting position, one or a plurality of processing tools can be selectively positioned easily at an appropriate time to the processing advance position or the retreat standby position. In addition, since the setup change time for changing a processing tool or the like can be reduced, productivity can be improved.

Further, the advance / retreat drive mechanism according to the invention of claim 6 is a plurality of mechanisms for individually advancing / retreating the respective sliding bodies of the respective tool operating mechanisms together with the respective working tools. Are individually provided on each of the orbiting moving tables of the orbiting guide mechanism.

According to the sixth aspect of the present invention, each of the forward / backward drive mechanisms is individually provided on each of the orbiting moving tables of the orbiting guide mechanism. Depending on the required number of machining tools,
Each of the orbiting moving tables of the orbiting guide mechanism can be selectively and easily added and removed together with each of the tool operating mechanisms. In addition, assuming the maximum required number of machining tools, it is possible to eliminate waste such as constructing an advance / retreat drive mechanism corresponding to the maximum required number in advance, thereby simplifying the structure of the spring forming apparatus and reducing the manufacturing cost. Can be achieved.

Further, the advancing / retracting drive mechanism according to the invention of claim 7 is provided such that each of the sliding members is provided integrally with each of the sliding members and is rotatable. Each of the reciprocating operation cams, each having a cam curved surface of an undulating trajectory capable of satisfying the amount of reciprocating movement of each sliding body, and each of the reciprocating operation cams attached to each of the orbital moving tables of the orbital guide mechanism to individually turn the respective reciprocating operation cams Each of the forward and backward drive servomotors to be moved, and each of the cam biasing springs for biasing each of the cam followers so as to be always in contact with each of the forward and backward operation cams, wherein the control means individually controls each of the forward and backward drive servomotors. By rotating each of the advance / retreat operation cams individually by each of the advance / retreat drive servo motors, the respective sliding members of the respective tool operation mechanisms can be removed. By advance and retreat individually with respective machining tool along the respective forward and backward movement axis, in which so as to position each machining tool in each of the forward and backward set position.

According to the seventh aspect of the present invention, the forward / backward drive mechanism controls each of the forward / backward drive servomotors individually for rotational positioning control, so that each of the sliding bodies of each of the tool operating mechanisms together with each of the machining tools. Since each of the processing tools is moved individually along the axis of the reciprocation movement to position each processing tool at the reciprocation setting position, the processing tool is selectively advanced to the optimal reciprocation setting position during the processing of the spring,
The other working tool that has advanced in the previous working step can be processed by being retracted.

By this operation, a spring having a complicated shape can be easily processed without restricting the degree of freedom of the spring processing shape, and productivity can be improved by simplifying a processing program. Further, in combination with the above-described operation of the circulating drive mechanism, the number of processing tools to be provided can be reduced.
The manufacturing cost of the working tool and the structure of the spring forming device can be simplified to reduce the manufacturing cost.

At least one of the respective tool operating mechanisms according to the invention of claim 8 is capable of turning, moving and reciprocating two or more working tools for bending, winding or cutting the wire. A tool operating mechanism configured to be a sliding body for carrying, comprising: a turning tool holder integrally fixed to the sliding body; and a turning axis parallel to the quill axis on the turning tool holder. A revolving tool table pivotally supported so as to be revolvably movable and detachable with the two or more processing tools;
A turning drive actuator attached to the turning tool holder for turning the turning tool table, wherein the control means controls the turning drive actuator so that the turning drive can be controlled by the turning drive actuator. By turning the turning tool table, the working tool of the two or more working tools is positioned at a tool turning setting position at which it can abut or engage with the wire.

According to the eighth aspect of the invention, at least one tool operating mechanism carries two or more processing tools for bending, winding, or cutting a wire so as to be capable of turning and moving forward and backward. As a result, the turning drive actuator is turned and the turning tool table is turned to thereby turn the turning tool table, whereby the tool turning setting position at which the corresponding one of the two or more working tools can be abutted or engaged with the wire rod. Since one tool operating mechanism is moved to the rotation setting position for positioning, the machining tool capable of responding to the spring machining process is appropriately selected from two or more machining tools. It is possible to select the timing and to perform the processing by positioning it at the set position.

By this operation, a spring having a complicated shape can be easily processed without restricting the degree of freedom of the spring processing shape, and productivity can be improved by simplifying a processing program. In addition, since the number of tool operating mechanisms can be reduced, the configuration of the spring forming device can be simplified and the manufacturing cost can be reduced.

The directions of the "circular movement" and the "turning movement" according to the present invention are not limited to one direction. Unless otherwise specified, the "spring forming space" is a space through which the wire fed from the quill must pass, and each processing tool for bending, winding or cutting the fed wire. It includes a space that must abut or engage with the wire and a space that must pass through the portion formed in the upstream processing step in the process of bending or winding the wire.

[0048]

BEST MODE FOR CARRYING OUT THE INVENTION

An embodiment of a spring forming apparatus according to the present invention will be described below with reference to FIGS. 1 is a front view of a spring forming apparatus, FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1, and FIG. 3 is a partially enlarged front view of a linear tool operating mechanism and its forward / backward drive mechanism. FIG. 4 is a cross-sectional view taken along the line BB of FIG. 3, FIG. 5 is a partially enlarged front view of the rotating tool operating mechanism and its advance / retreat driving mechanism,
6 is a cross-sectional view taken along the line CC of FIG. 5, FIG. 7 is a partially enlarged front view of the turning tool operating mechanism and its reciprocating drive mechanism, and FIG.
FIG. 9 is a cross-sectional view taken along the line DD in FIG. 7; FIG. 9 is an explanatory view of the orbital guide mechanism and its orbital drive mechanism; FIG. FIG. 6 is an explanatory view, and is a plan view taken along the line FF in FIG.

The spring forming apparatus of the present embodiment is roughly divided into FIGS. 1 and 2, in which a machine frame 1 on which the following mechanisms are mounted, a wire rod feeding mechanism 10 for feeding a wire, and a tool operating mechanism are respectively shown. Circumferential guide mechanism 20 for individually circulating guide together with machining tools
A, 20B, 20C, and a circling drive mechanism 30A, 30 for individually circulating each tool operating mechanism together with each machining tool.
B, 30C, a plurality of tool operating mechanisms (straight tool operating mechanism 40, rotating tool operating mechanism 50, turning tool operating mechanism 60) that carry each processing tool so as to be able to advance and retreat, and individually advance and retract each machining tool. A plurality of forward / backward drive mechanisms 70, 8 to be moved
0, 90, the wire rod feeding mechanism 10, the circling drive mechanism 30A,
Numeral control means (not shown) capable of controlling the rotary tool operating mechanism 50, the rotary tool operating mechanism 60, and the forward / backward drive mechanisms 70, 80, 90 in a related manner.

The machine frame 1 is for mounting each mechanism in association with each other. As shown in FIG. 2, the machine frame 1 is provided in a housing shape on a machine base (not shown), (Left side in the figure)
A molded substrate 2 is provided upright. A wire feed mechanism 10 is mounted on the machine frame 1 so as to sandwich the formed substrate 2. On the front surface of the formed substrate 2, mechanisms related to wire processing are related to each other around the quill axis. It is installed.

Subsequently, the wire rod feeding mechanism 10 is a mechanism for feeding a wire rod into a spring forming space, and as shown in FIG.
A pair of feed rollers 11A and 11B are provided inside the machine frame 1,
The wire W is provided so as to be capable of sending and returning by pinching and rotating the wire W.
However, it is erected so as to protrude from the front surface.

The quill holder 12 has a wire guide 13 at a position penetrating the molded substrate 2 and a spring molding space 3.
A quill 14 is inserted near each axis to form a wire guide hole through which the wire W can be inserted and guided in a straight line, and is embedded so as not to move. Quill 14
The wire W is guided to be led out to the spring forming space 3, and a load in a direction intersecting with the quill axis is applied by each working tool acting on the wire W for spring working.

Therefore, the front end of the quill 14 is formed to have a thickness that can tolerate this load, but the portion formed in the upstream processing step must be passed in the process of bending or winding the wire. To secure space,
A part of the front end is cut out and thinned. For this reason, the direction of advance of each processing tool is limited so that a load is not applied to the thin portion of the quill 14. In this example,
Since the plurality of tool operating mechanisms described below are configured to be capable of orbiting around the quill axis, the problem can also be solved.

The wire feeding mechanism 10 constructed as described above is driven by a driving means (not shown) under the control of a numerical control means (not shown).
By rotating A and 11B, the wire W is sent out or returned by a predetermined length from the rear surface side of the formed substrate 2 to the spring forming space 3 in front of the quill 14, and the wire W is transferred to the wire W as shown in FIGS. Bending, winding or cutting is performed by abutting or engaging the respective processing tools shown in FIG. Note that the pair of feed rollers 11A and 11B is not limited to a pair, and a plurality of pairs may be arranged in parallel according to the wire diameter of the wire W or the like.

Subsequently, the circulation guide mechanisms 20A, 20B, 2
0C is a mechanism that individually guides each tool operating mechanism together with each processing tool along a trajectory around the quill axis, and as shown in FIG. 1, FIG. 2, and FIG. An inner guide 21 and an outer guide 22, which are common guides for the movable portion of the guide mechanism, are formed in an annular shape around the axis of the quill 14, respectively. Is fixed to the front surface of the molded substrate 2 near the quill holder 12, and the outer periphery guide 22 is fixed to the vicinity of the outer periphery of the front surface of the molded substrate 2, respectively.

The inner peripheral guide 21 and the outer peripheral guide 22
As shown in FIGS. 4, 6, 8, and 9, the inner circumferential guide 21 has an inner circumferential raceway surface 2 that is convex toward the quill axis.
1a is formed, and the outer peripheral guide body 22 is formed with an outer peripheral raceway surface 22a that is convex toward the outside of the quill axis, and each rolling wheel 26a of each of the later-described circular guide mechanisms 20A, 20B, and 20C. ~ 26c, 26d ~ 26f, 2
6g-26i, the orbiting moving table 23, 2
4 and 25 are individually guided around.

Each of these orbiting moving tables 23, 24, 25
Are provided so as to face the inner guide 21 and the outer guide 22 described above, respectively. As shown in FIG. 1, the orbiting moving table 23 is provided with an orbiting drive mechanism 30A, a rectilinear tool operating mechanism 40, and an advancing / retreating mechanism. The driving mechanism 70 is connected to the
The rotation driving mechanism 30B and the rotating tool operating mechanism 5
0 and the forward / backward drive mechanism 80, and the orbital moving table 25
A revolving drive mechanism 30C, a revolving tool operating mechanism 60, and a reciprocating drive mechanism 90, which will be described later, are attached to each other, and individually revolve along a revolving orbit about the quill axis.

As shown in FIGS. 3, 4, and 9, the rolling wheel 26a is provided on the orbiting moving table 23 of the orbiting guide mechanism 20A with the convex inner circumferential raceway surface of the inner circumferential guide 21. 21a
And the rolling wheels 26b, 2
6c is formed in a concave shape which can be engaged with the convex outer raceway surface 22a of the outer guide body 22, and rotates on the rear surface 23b of the orbital moving base 23 facing the inner guide body 21 and the outer guide body 22, respectively. As possible, the rolling wheel 26a and the rolling wheel 26b, 2
6c, the inner peripheral guide body 21 and the outer peripheral guide body 22 are pinched so as to rotate and revolve.
Further, the orbiting moving table 23 has a rectilinear tool operating mechanism 40 on its front surface 23a and an advancing / retracting drive mechanism 70 at an end farther than the quill 14 can advance and retreat along an advancing / retreating axis converging on the quill axis. , Respectively.

The circling guide mechanism 20A thus configured
The rolling wheels 26a and the rolling wheels 26b and 26c are guided by the inner peripheral guide body 21 and the outer peripheral guide body 22 to rotate and revolve, so that the rolling wheels 26a and the rolling wheels 26b and 26c move along the orbit around the quill axis. The orbiting moving table 23 is guided to orbit together with the orbiting driving mechanism 30A, the rectilinear tool operating mechanism 40, and the reciprocating driving mechanism 70.

Next, as shown in FIGS. 5, 6, and 9, the rolling wheels 26 are mounted on the orbiting moving table 24 of the orbiting guide mechanism 20B.
d is formed in a concave shape capable of engaging with the convex inner peripheral raceway surface 21a of the inner peripheral guide body 21, and the rolling wheels 26e and 26f are formed.
Are formed in a concave shape capable of engaging with the convex outer raceway surface 22a of the outer guide body 22, and the inner guide body 21 and the outer guide body 2 are formed.
2 is rotatable on the rear surface 24b of the orbiting moving table 24 facing the rolling wheel 26, and the rolling wheels 26d and 26e, 26f are respectively rotatable.
Thus, the inner peripheral guide body 21 and the outer peripheral guide body 22 are pinched so as to rotate and revolve. Further, the orbiting moving table 24 has a rotating tool operating mechanism 50 on the front surface 24a thereof and an advance / retreat driving mechanism 80 at an end farther from the quill 14 to advance / retreat along the advance / retreat axis which converges on the quill axis. Where possible, each is attached.

The circling guide mechanism 20B thus configured
Is that the rolling wheel 26d and the rolling wheels 26e and 26f are guided by the inner peripheral guide body 21 and the outer peripheral guide body 22 to rotate and revolve, so that the rolling wheels 26d and 26f move along the orbit around the quill axis. The orbiting moving table 24 is guided to orbit together with the orbiting drive mechanism 30B, the rotary tool operating mechanism 50, and the advance / retreat drive mechanism 80.

Next, as shown in FIGS. 7, 8, and 9, the rolling wheel 26 is provided on the orbiting moving table 25 of the orbiting guide mechanism 20C.
g is formed in a concave shape engageable with the convex inner peripheral raceway surface 21a of the inner peripheral guide body 21, and the rolling wheels 26h, 26i are formed.
Are formed in a concave shape capable of engaging with the convex outer raceway surface 22a of the outer guide body 22, and the inner guide body 21 and the outer guide body 2 are formed.
2 is rotatable on the rear surface 25b of the orbiting moving table 25 facing the rolling wheel 26, and the rolling wheels 26g and 26h, 26i are respectively rotatable.
Thus, the inner peripheral guide body 21 and the outer peripheral guide body 22 are pinched so as to rotate and revolve. Further, the orbiting moving table 25 has a revolving tool operating mechanism 60 on the front surface 25a thereof and an advance / retreat driving mechanism 90 at an end farther from the quill 14 so as to advance / retreat along an advance / retreat axis which converges on the quill axis. , Respectively.

The circling guide mechanism 20C thus configured
The rolling wheels 26g and the rolling wheels 26h and 26i are guided by the inner peripheral guide body 21 and the outer peripheral guide body 22 to rotate and revolve, so that the rolling wheels 26g and the rolling wheels 26h and 26i follow the orbit around the quill axis. , The orbiting moving table 25 is orbitally guided together with the orbiting drive mechanism 30 </ b> C, the turning tool operating mechanism 60 and the reciprocating drive mechanism 90.

Then, these circulating guide mechanisms 20A, 2A
0B and 20C are individually driven to rotate by rotation driving mechanisms 30A, 30B and 30C, which will be described later, under the control of numerical control means (not shown).
0, the turning tool operating mechanism 50 and the turning tool operating mechanism 60 are individually or relatedly circulated around the working tool to form a wire W
It is positioned at a circling set position where it can be bent, wound or cut.

In this embodiment, the inner raceway surface 21a of the inner circumference guide 21 and the outer raceway surface 22a of the outer circumference guide 22 are formed in a wedge-shaped convex shape.
Each rolling wheel 26a-26c, 26d-26f, 2
6g-26i can also be configured to engage that shape.

Subsequently, the circling drive mechanisms 30A, 30B, 3
Reference numeral 0C denotes a mechanism for individually moving the orbiting moving tables 23 to 25 of the orbiting guide mechanisms 20A to 20C described above, and as shown in FIGS. A fixed gear 31 common to the movable portions 30B and 30C has a tooth shape formed on an annular outer periphery centered on the quill axis, and is fixed to the front surface of the molded substrate 2 near the inner peripheral guide 21. .

The fixed gear 31 cooperates with respective rotary gears 32a, 32b, 32c which are keyed and meshed with orbiting drive servomotors 33, 34, 35, which will be described later, to cooperate with each of the orbiting moving tables 23, 24, 24. 25 are individually rotated clockwise or counterclockwise.

The circulating drive servo motors 33, 3
Numerals 4 and 35 are rotatable and positionable under the control of the numerical control means. On the annular center line 39 centered on the quill axis, the orbiting drive servomotor 33 is connected to the orbital moving table 23 by the orbital drive servomotor. 34 is the orbiting carriage 24
In addition, the orbital drive servomotors 35 are individually attached to the orbital moving table 25, respectively. The rotary drive servomotor 33 has a rotary gear 32a, and the rotary drive servomotor 34 has a rotary gear 32b.
5, a rotation gear 32c is keyed to each output shaft.

The rotating gears 32a, 32b and 32c meshing with the fixed gear 31 are individually rotated by the orbiting drive servo motors 33, 34 and 35 to orbit around the annular center line 39. Move individually around the axis. To describe these positional relationships in detail, the orbital drive servomotor 34 of the orbital drive mechanism 30B is provided with a front surface 24a of the bulging portion 24c of the orbital moving base 24 shown in FIGS.
As shown in FIG. 10, the output shaft is mounted so as to protrude near the fixed gear 31, and a rotary gear 32b is keyed to the output shaft so as to mesh with the fixed gear 31.

The orbital drive servomotor 33 of the orbital drive mechanism 30A has an output shaft fixed on the front surface 23a of the bulging portion 23c of the orbital moving base 23 shown in FIGS. 3 and 4, as shown in FIG. A rotation gear 32 a is keyed to the output shaft so as to mesh with the fixed gear 31. The orbiting drive servomotor 35 of the orbiting drive mechanism 30C is attached to the front surface 25a of the bulging portion 25c of the orbiting moving base 25 shown in FIGS. 7 and 8 so that its output shaft projects near the fixed gear 31. A rotary gear 32c shown in FIG. 9 is keyed to the output shaft so as to mesh with the fixed gear 31.

Next, the orbiting drive mechanism 30A configured as described above rotates the orbital drive servomotor 33 under the control of numerical control means (not shown) to move and position the linear tool operating mechanism 40 to the orbital setting position. With this, the revolving operation of the rotating gear 32a meshing with the fixed gear 31 moves and moves the orbiting moving table 23 to which the rectilinear tool operating mechanism 40 is attached to the orbit setting position.

The circulating drive mechanism 30B is provided with a circulating drive servo motor 34B, similarly to the circulating drive mechanism 30A described above.
Is rotated, the orbiting moving table 24 to which the rotating tool operating mechanism 50 is attached is moved to the orbit setting position and positioned. Similarly to the above-described orbiting drive mechanisms 30A and 30B, the orbiting drive mechanism 30C rotates the orbital drive servomotor 35 to move the orbiting moving table 24 on which the turning tool operating mechanism 60 is attached to the orbit setting position. To move to position.

Then, these revolving drive mechanisms 30A, 3
0B and 30C individually or relatedly rotate the orbiting drive servomotors 33, 34 and 35 under the control of a numerical control means (not shown), so that the linear tool operating mechanism 40, the rotating tool operating mechanism 50, and the turning tool operating are operated. The respective working tools of the mechanism 60 are individually or related to orbital movement, and are positioned at the orbital setting positions where the wire W can be bent, wound or cut.

In the present embodiment, the orbiting moving tables 23, 24,
Each of the circulating drive servo motors 33, 34, and 35 is formed by forming a bulging portion on each of the ridges 25.
When it is necessary to bring the rectilinear tool operating mechanism 40, the rotating tool operating mechanism 50, and the turning tool operating mechanism 60 closer to each other, the bulging portion is made as small as possible, or the bulging portion is not formed. It is preferable to configure.

Subsequently, the plurality of tool operating mechanisms (the straight tool operating mechanism 40, the rotating tool operating mechanism 50, and the turning tool operating mechanism 60) include the aforementioned control means and the orbital driving mechanism 30A,
A mechanism for supporting each machining tool positioned at the rotation setting position by 30B and 30C so as to be able to advance and retreat along each radial advance and retreat movement axis substantially converging on the quill axis, as shown in FIGS. As shown in FIG.
Is a winding tool T1 for winding a coil portion or bending a hanging leg, a turning tool operating mechanism 50 is a bending tool T2 for bending a hanging leg, and a turning tool operating mechanism. 60
Carries a pitch tool T3 for giving a pitch to the coil portion, and a cutting tool T4 for cutting the wire rod, respectively.

Of these, the linear tool operating mechanism 40 is
As shown in FIGS. 3 and 4, the sliding guide body 41 has a recess 41a formed on the front side, and an inner side surface 41 of the recess 41a sandwiching a radial advance / retreat movement axis passing through the quill axis in FIG.
Guide grooves 41d are formed in b and 41c, respectively, and are attached to the front surface 23a of the orbiting moving base 23. A sliding member 42 is formed in the concave portion 41a of the sliding guide member 41 so as to be slidable with the concave portion 41a and engageable with each of the guide grooves 41d, and is engaged with the sliding member 42 so as to be able to move forward and backward on the forward and backward moving axis. ing.

The front surface 42 of the sliding body 42 on the quill 14 side
A linear tool holder 43 is attached to a by forming a concave portion 43a on the front side. A tool base 44 is pivotally supported by a pin 46 in the recess 43a so as to be swingable, and is positioned at a winding set angle position by an adjusting screw body 45. A winding tool T1 is formed on the tool base 44 so as to be capable of winding or bending a wire W sent out in front of the quill 14 and is screwed thereto.

The linear tool operating mechanism 4 configured as described above
0 is set by an advance operation of the advance / retreat drive mechanism 70 described later.
By moving the winding tool T1 forward with the sliding body 42 to the advance / retreat setting position (FIGS. 3 and 4 show the processing advance position), the winding tool T1 is brought into contact with the wire W in the spring forming space 3 by The coil part is wound into a predetermined coil diameter, or the hook leg is bent into a predetermined bending diameter.

Next, the rotating tool operating mechanism 50 is shown in FIG.
As shown in FIG. 6, the sliding guide body 51 is provided with a recess 5 on the front side.
1a are formed, and inner side surfaces 51b, 51 of a concave portion 51a sandwiching a radial advance / retreat movement axis passing through the quill axis in FIG.
A guide groove 51d is formed in each of c, and is attached to the front surface 24a of the orbiting carriage 24. A sliding body 52 is formed in the concave portion 51a of the sliding guide body 51 so as to be slidable with the concave portion 51a and engageable with each guide groove 51d, and is engaged so as to be able to advance and retreat on the advance and retreat movement axis. ing.

The front surface 52 of the sliding body 52 on the quill 14 side.
In FIG. 3A, a bent tool holder 53 formed in a U-shape is formed upright with a guide groove 53a formed inside the U-shape and an escape hole 53b formed on the sliding body 52 side. This guide groove 53
a, a bearing base 54 is formed so as to be slidable, is engaged in parallel with the quill axis, and is screwed to the bending tool holder 53 so as not to move at the position determined by the adjusting screw body 55. Have been.

A hollow bulging portion 54a is formed on the sliding body 52 side of the bearing 54 so as to be inserted into a relief hole 53b of the bending tool holder 53, and a pair of rolling bearings is formed on the inner periphery thereof. It is installed. A bending tool holding shaft 56 is rotatably supported on the pair of rolling bearings so as to be rotatable around a rotation axis orthogonal to the quill axis. The bending tool holding shaft 56 has a bending tool T at one end on the quill 14 side.
2 is screwed integrally, and a driven gear 57 is keyed to the other end.

The bending tool T2 has two bent projections T2a, T2a shown in FIG. 6 at its front end, and the wire W is sandwiched between the bent projections T2a, T2a at the forward position. The wire W is bent by being inserted and rotated. Further, a bending rotation servomotor 59 which can be rotated and positioned by the control of the numerical control means is attached to the flange portion 54b of the bearing base 54, and a driving gear 58 is mounted on an output shaft thereof.
Are keyed to be able to mesh with the driven gear 57.

The rotating tool operating mechanism 5 configured as described above
0 is set by the forward operation of the forward / backward drive mechanism 80 described later.
The bending tool T2 is advanced together with the sliding body 52 to the set forward / backward position (FIGS. 5 and 6 show a retreat standby position), and the wire W of the spring forming space 3 is sandwiched between the bent projections T2a and T2a. The bending tool T2 is turned at a set angle by turning the bending turning servo motor 59 under the control of the numerical control means, thereby bending the hook leg to a predetermined bending angle. I do.

Next, the turning tool operating mechanism 60 is shown in FIG.
As shown in FIG. 8, the sliding guide 61 is provided with a concave portion 6 on the front side.
1a are formed, and inner side surfaces 61b, 61 of a concave portion 61a sandwiching a radial advance / retreat movement axis passing through the quill axis in FIG.
A guide groove 61d is formed in each of the c. A sliding body 62 is formed in the concave portion 61a of the sliding guide body 61 so as to be slidable with the concave portion 61a and engageable with each of the guide grooves 61d, and is engaged so as to be able to advance and retreat on the advance and retreat movement axis. ing.

On the front surface 62a of the sliding body 62, a rolling bearing is mounted on a center line parallel to the quill axis at a front end position on the quill 14 side, and a turning tool holder 63 formed in a U-shape is provided. It is erected. One of the rolling bearings mounted on the sliding body 62 and the other rolling bearing are mounted on the top plate portion 63a of the revolving tool holder 63 at a position on a straight center line (the revolving axis), and these rolling bearings are mounted. In addition, a turning tool table 64 is pivotally supported so as to be able to turn. In this turning tool table 64, a pitch tool T3 can be detached from a concave portion 64b and a cutting tool T4 can be detached from a concave portion 64c formed so as to be orthogonal to the turning axis, and each of these processing tools is turned to an arbitrary angular position. It is something to move.

The top plate 63a of the turning tool holder 63
The turning drive servo motor 69 of the turning drive actuator that can be turned and positioned under the control of the numerical control means
Is mounted coaxially with the turning tool stand 64, and its output shaft is keyed to a shaft hole 64 a of the turning tool stand 64.
The revolving tool table 64 is revolved by the revolving drive servomotor 69 to revolve the pitch tool T3 and the cutting tool T4 around a revolving axis parallel to the quill axis.

The turning tool operating mechanism 6 configured as described above
0, the turning tool table 64 is turned by the turning drive of the turning drive servo motor 69 under the control of the numerical control means, and the machining tool capable of responding to the spring machining step is selected from the pitch tool T3 and the cutting tool T4. Is selected and positioned at a tool turning setting position where it can abut or engage with the wire W (FIG. 7 shows the cutting tool T4 having the tool turning setting position).
The working tool is advanced to an advance / retreat setting position by an advance operation of an advance / retreat drive mechanism 90 described later (FIGS. 7 and 8 show a retreat standby position), and the wire is processed into a predetermined shape, or
Cut to a predetermined length.

The rectilinear tool operating mechanism 40, the rotating tool operating mechanism 50, and the turning tool operating mechanism 60 are controlled by numerical control means (not shown) so that each of the advance / retreat driving mechanisms 7 described later is controlled.
By moving the working tools 0, 80, and 90 forward, the respective working tools are individually or relatedly moved to the forward / backward set positions, and the wire W is bent, wound, or cut.

Subsequently, each of the forward / backward drive mechanisms 70, 80, 90
Is a mechanism that is provided in each of the above-described straight tool operating mechanism 40, rotating tool operating mechanism 50, and turning tool operating mechanism 60, and moves each of the sliding bodies 42, 52, and 62 individually along with each processing tool. As shown in FIGS. 1 and 2, each of the tool operating mechanisms 40, 50, and 60 is rotated so that each of the forward and backward operating cams 73, 83, and 93 is engaged with the rear end of each tool operating mechanism. 40, 50, 60 sliding bodies 4
2, 52 and 62 are moved forward and backward.

As shown in FIGS. 3 and 4, the advancing / retracting drive mechanism 70 is configured such that the shaft bearing cylinder 71 has a center parallel to the quill axis at the rear end position of the slide guide 41 of the linear tool operating mechanism 40. Mounted on the axis. A pair of rolling bearings are mounted on the shaft bearing cylinder 71, and a cam rotation shaft 72 is rotatably supported by the pair of rolling bearings. The cam rotation shaft 72 is provided with an advance / retreat operation cam 73,
The cam surface 73a of the undulation locus capable of satisfying the amount of advance and retreat movements
And is keyed to one end of the cam rotation shaft 72 so as to protrude from the front surface 42 a of the sliding body 42.

On the opposite side of the advancing / retracting operation cam 73, an advancing / retracting drive servomotor 74, which is rotatable and positionable under the control of the numerical control means, is coaxial with the cam rotation shaft 72 on the rear surface 23 b of the orbiting moving table 23. The other end of the rotating shaft 72 is keyed to the attached output shaft. Therefore, the advance / retreat operation cam 73 is rotated together with the cam rotation shaft 72 by the rotation of the advance / retreat drive servomotor 74.

On the front surface 42a on the rear end side of the sliding member 42, a roller pivoting member 75 is fixed by forming a U-shaped fork at a position facing the cam curved surface 73a of the reciprocating operation cam 73. ing. A roller shaft 75a is fixed to the roller pivot 75 so as to penetrate the U-shaped portion. A cam follower 76 is rotatably connected to the roller shaft 75a so as to be in contact with the cam curved surface 73a of the advance / retreat operation cam 73 so as to be rotatable.

Further, a moving-side engaging member 77 is screwed at a position near the roller pivoting member 75 of the sliding member 42, and a fixed-side engaging member 78 is fixed at the rear end position of the sliding guide 41. Have been. The movable side locking member 77 and the fixed side locking member 78
In order to keep the cam follower 76 in contact with the reciprocating operation cam 73 at all, urging springs 79, 79 for urging the cam follower 76 together with the sliding body 42 are attached.

The forward / backward drive mechanism 70 thus configured
Is the forward / backward drive servomotor 7 controlled by the numerical control means.
4, the reciprocating operation cam 73 is rotated, and the urging spring 79,
The winding tool T1 of the rectilinear tool operating mechanism 40 is moved forward and backward together with the sliding body 42 via the cam follower 76 circumscribed by 79.

Next, as shown in FIGS. 5 and 6, the advancing / retracting drive mechanism 80 moves the bearing tube 81 on the center axis parallel to the quill axis at the rear end position of the sliding guide body 51 of the rotary tool operating mechanism 50. It is attached to. A pair of rolling bearings are mounted on the shaft bearing cylinder 81, and a cam rotation shaft 82 is rotatably supported by the pair of rolling bearings. The cam rotation shaft 82 is formed with a cam curved surface 83a of an up-and-down trajectory capable of satisfying the amount of advance / retreat movement of the slide body 52 so that the advance / retreat operation cam 83 protrudes from the front surface 52a of the slide body 52. , Is keyed to one end of the cam rotation shaft 82.

On the opposite side of the advancing / retracting operation cam 83, an advancing / retracting drive servomotor 84, which can be rotated and positioned by the control of numerical control means, is provided coaxially with the cam rotation shaft 82 on the rear surface 24 b of the orbiting moving table 24. The other end of the rotating shaft 82 is keyed to the output shaft. Therefore, the forward / backward operation cam 83 is rotated together with the cam rotation shaft 82 by the rotation of the forward / backward drive servomotor 84.

On the front surface 52a on the rear end side of the sliding member 52, a roller pivoting member 85 is fixed by forming a U-shaped fork at a position facing the cam curved surface 83a of the reciprocating operation cam 83. ing. A roller shaft 85a is fixed to the roller pivot body 85 so as to penetrate the U-shaped portion. A cam follower 86 is rotatably connected to the roller shaft 85a so as to be in contact with the cam curved surface 83a of the advance / retreat operation cam 83 and to be rotatable.

A moving-side hooking member 87 is screwed at a position near the roller pivot 85 on the sliding body 52, and a fixed-side hooking member 88 is fastened at the rear end position of the sliding guide 51. Have been. The moving side hooking member 87 and the fixed side hooking member 88
In order to keep the cam follower 86 in contact with the reciprocating cam 83 at all times, urging springs 89, 89 for urging the cam follower 86 together with the sliding body 52 are attached.

The forward / backward drive mechanism 80 thus configured
Is the forward / backward drive servo motor 8 controlled by the numerical control means.
4, the reciprocating operation cam 83 is rotated, and the urging spring 89,
The bending tool T2 of the rotary tool operating mechanism 50 is moved forward and backward together with the slide body 52 via the cam follower 86 circumscribed by 89.

Next, as shown in FIGS. 7 and 8, the advancing / retracting drive mechanism 90 moves the bearing tube 91 on the central axis parallel to the quill axis at the rear end position of the sliding guide 61 of the turning tool operating mechanism 60. Has been attached. A pair of rolling bearings are mounted on the shaft bearing cylinder 91, and a cam rotating shaft 92 is rotatably supported by the pair of rolling bearings. The cam rotation shaft 92 is formed with a cam curved surface 93 a of an up-and-down locus capable of satisfying the amount of advance / retreat movement of the sliding body 62 so that the advancing / retreating operation cam 93 protrudes from the front surface 62 a of the sliding body 62. , And is keyed to one end of the cam rotation shaft 92.

On the opposite side of the advancing / retracting operation cam 93, an advancing / retracting drive servomotor 94, which is rotatable and positionable under the control of the numerical control means, is provided coaxially with the cam rotation shaft 92 on the rear surface 25 b of the orbiting carriage 25. The other end of the rotating shaft 92 is keyed to the output shaft. Therefore, the forward / backward operation cam 93 is rotated together with the cam rotation shaft 92 by the rotation of the forward / backward drive servomotor 94.

On the front surface 62a on the rear end side of the sliding member 62, a roller pivoting member 95 is fixed by forming a U-shaped fork at a position facing the cam curved surface 93a of the reciprocating operation cam 93. ing. A roller shaft 95a is fixed to the roller pivot body 95 so as to penetrate the U-shaped portion. A cam follower 96 is rotatably connected to the roller shaft 95a so as to be in contact with the cam curved surface 93a of the reciprocating operation cam 93 so as to be rotatable.

A moving-side hooking member 97 is screwed on the sliding body 62 near the roller pivot 95, and a fixed-side hooking member 98 is fastened on the rear end of the sliding guide 61. Have been. The moving side hooking member 97 and the fixed side hooking member 98
In order to keep the cam follower 96 in contact with the reciprocating cam 93 at all times, urging springs 99, 99 for urging the cam follower 96 together with the sliding body 62 are attached.

The forward / backward drive mechanism 90 thus configured
Is the forward / backward drive servo motor 9 controlled by the numerical control means.
4, the forward / backward operation cam 93 is rotated, and the urging springs 99,
The pitch tool T3 and the cutting tool T4 of the turning tool operating mechanism 60 are moved forward and backward together with the slide body 62 via a cam follower 96 circumscribed by 99.

Then, each of the forward / backward drive mechanisms 70, 80, 90
By rotating the forward / backward drive servomotors 74, 84, 94 individually or relatedly under the control of a numerical control means (not shown), the linear tool operating mechanism 40, the rotating tool operating mechanism 50, and the turning tool operating mechanism 60 are controlled. Each sliding body 42,5
2, 62 are individually or associatedly moved forward and backward together with each working tool.

That is, the forward / backward drive mechanism 70 is driven by the forward / backward drive cam 73 that rotates together with the forward / backward drive servomotor 74 via the cam follower 76 to move the straight tool operating mechanism 4
The sliding member 42 of the rotary tool operating mechanism 50 and the sliding member 52 of the rotary tool operating mechanism 50 via a cam follower 86 by an advancing / retracting operation cam 83 that rotates together with an advancing / retracting drive servomotor 84. Reference numeral 90 denotes a revolving tool operating mechanism 60 via a cam follower 96 by a reciprocating operation cam 93 which rotates together with an advancing / retracting drive servo motor 94.
Are moved forward and backward respectively.

Subsequently, in the spring forming apparatus of the present embodiment configured as described above, the related operation, operation, and the like between the working tool for spring working and each mechanism are shown in FIG. The following description will be made with reference to FIGS. 12 to 23 showing the form of each processing tool in each processing step. In the following description, the relationship with the numerical control means is omitted, but the operation of each drive mechanism is controlled by the multi-axis numerical control means. FIG.
23 to 23, the position display of each processing tool will be described on coordinates where the axis of the quill 14 is the origin, the horizontal axis is the X axis, and the vertical axis is the Y axis.

The spring of this working example is formed by the working tools T1 to T4 of the plurality of tool operating mechanisms 40 to 60 described above.
The end portion Sa (first processing step), the twisted bent portion Sb (second processing step), the straight portion Sc (third processing step) shown in FIG.
A hook-shaped hook leg composed of a bent portion Sd (fourth machining process) and a straight leg Se (fifth machining process), a coil portion Sf (sixth machining process), and a straight hook leg Sg (first 7) and a torsion coil spring S formed with a cut surface Sh (eighth processing step). As shown in FIG. 11 (b), the end Sa of the torsion coil spring S is 3.8397 × 10 ⁻¹ rad [3.8397 × 10 ⁻¹ rad [with respect to the wire axis of the straight leg Se by bending the torsion bent portion Sb three-dimensionally. 22 °].

As shown in FIG. 11 (a), the coil axis of the coil portion Sf is perpendicular to the straight leg Se and the straight hooking leg Sg. The pitch of the set interval is formed. Also, the straight hook leg Sg is parallel to the wire axis of the straight leg Se in FIG. 11A, and is a coil portion with respect to the straight hook leg Sg in FIG. 11B. 5.236 on the Sf side
It forms an inclination angle of 0 × 10 ^-1 rad [30 °].

[0111] Further, the conventional publication A cited in the prior art above.
According to the invention according to Japanese Patent Application Laid-Open No. Hei 10-29028, the length of the wire rod of the straight leg Se is 3.8397 ×
A twist angle of 10 ^-1 rad [22 °] cannot be formed. That is, the invention according to the conventional publication A is shown in FIG.
Of the cam follower 21 is 2.6180 × 10 ^-1 rad [15 °] or 3.4907 × 10 ^-1 rad [15 °] in the clockwise direction and the counterclockwise direction, respectively, with respect to the axis of movement of the arc cam 39. 20 °].

Therefore, in the clockwise and counterclockwise directions
When the effective advance / retreat operation angle is set to 2.6180 × 10 ^-1 rad [15 °], the angle from the advance / retreat movement axis of the arc cam 39
Over 180 × 10 ^-1 rad (15 °) 5.2360 × 10 ^-1 rad
Within [30 °], and even when set at 3.4907 × 10 ^-1 rad [20 °] clockwise and counterclockwise,
3.4907 × 10 ^-1 rad [20 °] exceeded 4.3633 × 10 ^-1 ra
The range within d [25 °] cannot be processed.

In this machining example, before machining the first torsion coil spring S, each tool operating mechanism 40 is prepared for the first machining step shown in FIG.
Each of the machining tools T1 to T4 of FIGS.
By orbiting each of the orbiting drive mechanisms 30A to 30C shown in FIG. 9 and controlling the orbiting drive mechanisms 70 to 90 to retreat, as shown in FIG. And stand by at the respective retreat standby positions.

That is, in processing the torsion coil spring S, the winding tool T1 of the rectilinear tool operating mechanism 40 first engages with the wire W in the sixth processing step of processing the coil portion Sf. Equipped with the circling drive mechanism 30
By controlling the rotation of the rotation drive servomotor 33 of A, the rotation movable table 23 of the rotation guide mechanism 20A is rotated, and
The advancing / retreating axis is positioned at a rotation setting position substantially on the Y axis above the quill 14 shown in FIG. 12A, and the advancing / retracting drive servo motor 74 of the advancing / retracting drive mechanism 70 shown in FIGS. By performing the movement control, the sliding body 42 is moved backward together with the winding tool T1 and is kept at the retreat standby position. Further, the winding tool T1 is used to set the abutting position of the inclined action surface which abuts on the wire W in the spring forming space 3,
The adjustment screw body 45 is positioned together with the tool stand 44 at the winding set angle position.

The bending tool T of the rotary tool operating mechanism 50
2 first engages with the wire W in the second processing step of processing the torsionally bent portion Sb. Therefore, in preparation for this processing step, the rotation drive servo motor 34 of the rotation drive mechanism 30B is controlled to rotate. Orbital moving table 2 of orbital guide mechanism 20B
4 and the axis of its movement is shown in FIG.
The quill 14 is positioned 3.8397 × 10 ^-1 rad [22 °] counterclockwise from the Y axis below the quill 14 in the fourth quadrant as shown in FIG. The bending tool T2 is rotated by controlling the rotation of the bending rotation servomotor 59 of 50.

Then, the bending protrusion T2 of the bending tool T2 is used.
a, the rotation position of T2a is positioned at a bending standby position where the wire W can be inserted near the front end of the quill 14 symmetrical with respect to the quill axis, and the advance / retreat drive servo motor 84 of the advance / retreat drive mechanism 80 is rotated. By performing the motion control, the sliding body 52 is moved backward together with the bending tool T2, and waits at the backward waiting position.

The pitch tool T3 and the cutting tool T4 of the revolving tool operating mechanism 60 are prepared for this processing step because the pitch tool T3 first engages with the wire W in the sixth processing step of processing the coil portion Sf. Then, the orbiting drive table 25 of the orbital guide mechanism 20C is orbited by controlling the rotation of the orbital drive servomotor 35 of the orbital drive mechanism 30C, and its advance / retreat movement axis is set to the left of the quill 14 shown in FIG. 7 and 8, the turning drive servo motor 69 of the turning tool operating mechanism 60 shown in FIGS.
Is turned to select a pitch tool T3 for giving a pitch to the coil by the pushing action.

The pitch tool T3 is positioned at a tool turning set position parallel to an axis of reciprocal movement which can apply a pitch to a coil to be wound, and rotates the reciprocating drive servomotor 94 of the reciprocating drive mechanism 90. By controlling the slide 6
2 is moved backward together with the pitch tool T3 so as to wait at the retreat standby position.

Thus, the preparatory work before machining the first torsion coil spring S is completed, but the next torsion coil spring S is completed.
This preparation work is unnecessary from the processing of (1). That is, the processing tool that has finished processing in each processing step is positioned at a retreat standby position, a bending standby position or a tool turning setting position, at a revolving setting position where each processing is possible, in preparation for a downstream processing step. This is because they are kept on standby.

The first processing step shown in FIG. 12 is a step for processing the end Sa, and is performed by controlling the rotation of a pair of feed rollers 11A and 11B of the wire rod feeding mechanism 10 shown in FIG. As shown in FIG. 12B, the end portion Sa is formed by feeding the wire W from the front end of the quill 14 for a set length and stopping it.

The set length of the wire W to be sent out is equal to the end Sa.
, The required length of the torsionally bent portion Sb formed continuously with the end Sa, and the required processing length that does not hinder the operation of the processing tool in the next second processing step. It is. The length and angle of the end portion Sa are determined by processing the twisted bent portion Sb in the next second processing step.

Next, the second machining step shown in FIGS. 13 and 14 is a step of machining the torsion bent portion Sb with the bending tool T2 of the rotary tool operating mechanism 50, and the advance / retreat drive mechanism shown in FIG. By controlling the rotation of the forward / backward drive servomotor 84 at 80, the bending tool T2 positioned at the bending standby position at the retreat standby position at the rotation setting position in the preparation stage of the previous first processing step is moved to the processing forward position. As shown in FIG. 13 (a), the end S is moved between the bent projections T2a, T2a.
The wire W of a is inserted.

The processing of the twisted bent portion Sb is performed as shown in FIG.
By rotating the bending tool T2 by the rotation control of the bending rotation servomotor 59 shown in FIG.
As shown in (b), the wire rod W sandwiched between the bent protrusions T2a, T2a is rotated counterclockwise to 1.5708 rad [90 °, which is the bending set angle of the end portion Sa and the straight portion Sc. 〕When,
After being bent by a processing set angle obtained by adding a springback equivalent angle, as shown in FIG. 14B, the bent projections T2a, T2a sandwiching the wire W are clockwise rotated by springback equivalent. By returning the angle by an angle, the bending angle between the end portion Sa and the straight portion Sc shown in FIG. 15B is set to 1.5708 rad [90
°].

Further, the torsionally bent portion Sb is formed so that the bending tool T2 is turned counterclockwise from the Y axis at the position below the quill 14.
Since the bending is performed at the circling setting position inclined at 3.8397 × 10 ⁻¹ rad [22 °], the wire axis of the end portion Sa shown in FIG. 15A is 3.8397 × 10 ^{−1 at the} upper right with respect to the X axis. rad
[22 °] It is formed so as to be inclined.

In this way, the bending tool T2 after processing the torsionally bent portion Sb controls the rotation of the advance / retreat drive servomotor 84 in preparation for the fourth downstream processing step for processing the bent portion Sd. To move backward, as shown in FIG.
The bending projections T2a, T2a are retracted to a processing standby position away from the wire W at the end Sa, and the bending tool T2 is rotated clockwise by rotation control of the rotation driving servo motor 34 to advance and retreat. The moving axis is positioned at the rotation setting position on the substantially Y-axis, and is made to stand by.

Next, the third processing step shown in FIG. 15 is a step of processing the linear portion Sc, and by controlling the rotation of the pair of feed rollers 11A and 11B, the third processing step shown in FIG.
As shown in (b), the linear material Sc is formed by feeding the wire W from the front end of the quill 14 for a set length and stopping.

The set length of the wire W to be sent out is determined by the linear portion S
c, the required length of the bent portion Sd formed continuously with the straight portion Sc in the next fourth processing step,
This is a set length including a required processing length that does not hinder the operation of the bending tool T2. The length and angle of the straight portion Sc are determined by processing the bent portion Sd in the next fourth processing step.

Thus, the straight portion Sc and the bent portion Sd
And the bending tool T2 after processing the twisted bent portion Sb in the previous second processing step.
Prepares for the next fourth processing step of processing the bent portion Sd,
As shown in FIG. 16 (b), the bending protrusions T2a, T2a are rotated by the rotation control of the bending rotation servomotor 59.
The quill 1 is positioned symmetrically about the quill axis.
(4) In the vicinity of the front end, the wire W of the straight portion Sc is positioned at a bending standby position where the wire W can be inserted, and is made to wait.

Next, in the fourth machining step shown in FIGS. 16 and 17, the bending tool T2 of the rotary tool operating mechanism 50 uses the bending portion S
In the step of machining d, the rotation of the advance / retreat drive servomotor 84 of the advance / retreat drive mechanism 80 is controlled so that after the machining in the previous third machining step, the bending standby position is set at the machining standby position of the rotation setting position. The bending tool T2 positioned at the position (1) is advanced to the processing advance position, and as shown in FIG. 16 (a), the wire W of the linear portion Sc is sandwiched between the bending projections T2a, T2a.

The bending portion Sd is processed by rotating the bending tool T2 by rotation control of the bending rotation servomotor 59, that is, as shown in FIG.
The wire rod W sandwiched between the bent protrusions T2a, T2a is rotated counterclockwise by 1.5708 rad [90 °], which is the bending set angle of the straight portion Sc and the straight leg Se, and the springback equivalent angle. Then, as shown in FIG. 17 (b), the bent projections T2a, T2a sandwiching the wire W are returned clockwise by an angle equivalent to springback, as shown in FIG. The bending angle between the straight line portion Sc and the straight leg portion Se shown in FIG. 18B is set to 1.5708 rad [90 °]. The bent portion Sd is formed such that the wire axis of the straight portion Sc shown in FIG. 18A matches the X-axis.

In this way, the bending tool T2 after processing the bent portion Sd is rotated by the advance / retreat drive servomotor 84 in preparation for preventing tool interference in the downstream eighth processing step of processing the cut surface Sh. The bending tool T2a is moved backward by the dynamic control so that the bending projections T2a and T2a are retracted to the retreat standby position farthest away from the wire rod W of the linear portion Sc. The orbit is moved in the counterclockwise direction, and its forward / backward movement axis is positioned at the orbital setting position shown in FIG. 18 (a) inclined about 7.8540 × 10 ^-1 rad [about 45 °] counterclockwise from the Y axis. Evacuate.

Next, the fifth processing step shown in FIG. 18 is a step of processing the straight leg Se, and the wire W is moved from the front end of the quill 14 by controlling the rotation of the pair of feed rollers 11A and 11B. The straight leg Se is formed by feeding and stopping by the set length. The set feeding length of the wire W is a required length for forming the straight leg Se, and a required processing length up to the start of winding of the coil portion Sf continuously formed on the straight leg Se in the next sixth processing step. And the set length.

The length and angle of the straight leg Se are determined by processing the coil portion Sf in the next sixth processing step. The set torsion angle 3.839 between the end Sa and the straight leg Se shown in FIG.
7 × 10 ^-1 rad [22 °] is determined by processing the straight leg Se.

In this way, the wire rod W forming the straight leg Se and the start of winding of the coil Sf is sent out, and the bending tool T2 after the bending Sd is processed in the previous fourth processing step. 19A, the bending tool T2 is rotated by the rotation control of the bending rotation servomotor 59 of the rotation tool operating mechanism 50 in preparation for the processing of the next torsion coil spring S, and shown in FIG. In this way, the turning positions of the bending projections T2a, T2a are positioned at the bending standby position where the wire W can be inserted near the front end of the quill 14 symmetrical with respect to the quill axis, and the standby is performed.

Next, the sixth machining step shown in FIGS. 19 and 20 is a step of machining the coil portion Sf with the winding tool T1 of the rectilinear tool operating mechanism 40 and the pitch tool T3 of the turning tool operating mechanism 60. And the coil part Sf by the winding tool T1
In the winding process, the rotation of the forward / backward drive servomotor 74 of the forward / backward drive mechanism 70 for moving the straight tool operation mechanism 40 forward / backward is controlled.
The winding tool T1 that has been waiting at the retreat standby position at the revolving setting position above the quill 14 is advanced to position the winding tool T1 at the processing advance position shown in FIG. 20A, and a pair of feed rollers of the wire rod feeding mechanism 10. By controlling the rotation of 11A and 11B, the wire rod W is continuously sent out from the front end of the quill 14, and the coil portion Sf is wound.

Further, the coil portion Sf by the pitch tool T3
The pitch is given to the quill 14 in the revolving set position on the left side of the quill 14 in the preparatory stage of the first machining step by controlling the rotation of the advance / retreat drive servomotor 94 of the advance / retreat drive mechanism 90. The pitch tool T3 that has been set is moved forward, and as shown in FIG.
The front end working surface of the coil part Sf positions the lower side surface of the coil part Sf wound in front of the wire rod feeding hole of the quill 14 at the processing advance position where the coil part Sf can be pressed in the coil generation direction, and gives the coil part Sf a pitch of a set interval. I do.

That is, as shown in FIG. 20 (b), the wire having the set coil diameter is wound by abutting the wire W against the inclined action surface of the winding tool T1, and the wire W is wound as shown in FIG. 20 (a).
As shown in (1), the lower side surface of the coil being wound is pressed in the coil generation direction by the front end working surface of the pitch tool T3, thereby forming a pitch of the set interval in the coil portion Sf.

The coil portion Sf has its free length formed by the number of turns and the pitch, and the required developed length of the wire W is determined by the coil diameter and the number of turns. Therefore, by sending out the wire W of the required developed length from the front end of the quill 14 and stopping, the coil portion Sf shown in FIG. 11 is formed, and the straight hook leg for the straight leg Se shown in FIG. The inclination angle of the portion Sg is determined.

In this way, the winding tool T1 after processing the coil portion Sf controls the rotation of the forward / backward drive servomotor 74 of the forward / backward drive mechanism 70 in preparation for the next working of the torsion coil spring S. And is positioned at a retreat standby position shown in FIG. 21A (that is, the same position as before the first processing step shown in FIG. 12A) and made to stand by. Also,
Pitch tool T3 after applying pitch to coil portion Sf
In order to prepare for the downstream eighth machining step for machining the cut surface Sh, the forward / backward drive servomotor 94 of the forward / backward drive mechanism 90 is rotated backward to be retracted, positioned at the retreat standby position and made to stand by.

Next, the seventh processing step shown in FIG. 21 is a step of processing the straight hook leg Sg, and by controlling the rotation of the pair of feed rollers 11A and 11B,
As shown in FIG. 21B, the wire W is sent out from the front end of the quill 14 by a set length for forming the straight hooking leg Sg, and is stopped. It should be noted that the straight hook leg Sg
Is to determine the length by cutting the cut surface Sh in the following eighth processing step.

In this way, the wire W forming the straight hooking leg Sg is fed out, and the coil portion Sf is transferred to the coil portion Sf in the sixth processing step in preparation for the next eighth processing step of processing the cut surface Sh. The pitch tool T3 to which the pitch has been applied is replaced with the cutting tool T4, and the cutting tool T4 is circulated counterclockwise.

That is, the turning tool base 64 is turned by controlling the turning of the turning drive servomotor 69, and the cutting tool T4 is replaced with the quill 14 instead of the pitch tool T3.
Side, and the cutting tool T4 has a cutting edge side substantially in sliding contact with the front end face of the quill 14 in the processing advance position,
In addition to positioning the wire W at a tool turning setting position at which cutting can be performed, the orbiting drive servo motor 3C of the orbiting drive mechanism 30C
FIG. 22 (a)
As shown in (2), the advance / retreat movement axis of the cutting tool T4 is positioned below the quill 14 at a rotation setting position on the substantially Y-axis.

Next, in the eighth machining step shown in FIGS. 22 and 23, the cutting surface T is cut by the cutting tool T4 of the turning tool operating mechanism 60.
h, which is a final step of cutting the h.
The cutting tool T4, which has been waiting at the retreat standby position at the rotation set position substantially on the Y-axis at a position below the quill 14 in the previous seventh processing step, is moved forward by controlling the rotation of the advance / retreat drive servomotor 94. Move it, as shown in FIG. 23,
By the shearing action between the cutting blade of the cutting tool T4 and the front end face of the quill 14, the cut surface Sh at the end of the straight hooking leg Sg is cut.
By this cutting, the length of the straight hooking leg portion Sg is determined, and the torsion coil spring S shown in FIG.

After processing the cut surface Sh in this manner, the cut surface Sh is prepared for the next processing of the torsion coil spring S.
The cutting tool T4 after machining is retracted and the pitch tool T
3 and the pitch tool T3 is rotated clockwise while the bending tool T2 is rotated clockwise. That is, the cutting tool T4 and the pitch tool T3 are connected to the forward / backward drive servomotor 9 of the forward / backward drive mechanism 90.
The turning tool 4 is retracted by controlling the rotation of the turning tool table 64, and the turning tool table 64 is turned by controlling the turning of the turning drive servomotor 69 of the turning tool operating mechanism 60.
Instead of 4, the pitch tool T3 is selected on the quill 14 side.

The pitch tool T3 is positioned at a tool turning setting position at which a pitch can be given to the next torsion coil spring S at a position parallel to the advance / retreat movement axis, and waits at a retreat standby position. The orbiting drive servomotor 35 is orbitally controlled by rotating control, and its forward / backward movement axis is positioned at the orbital setting position on the substantially X-axis at the left position of the quill 14 shown in FIG. Let it.

Further, after the bending tool T2 processes the bent portion Sd in the previous fourth processing step, the bent projections T2a and T2 are formed.
Since the rotation position a is set to the bending standby position and is kept on standby, it is rotated clockwise by the rotation control of the rotation drive servomotor 34, and its advance / retreat movement axis is set to the position shown in FIG. At a position below the quill 14 in the four quadrants, the quill 14 is positioned at a circling set position inclined 3.8397 × 10 ^-1 rad [22 °] counterclockwise from the Y-axis line, and waits.

Thus, one cycle of the processing step for processing the torsion coil spring S is completed, and the above-described first to eighth processing steps are repeated under the control of the multi-axis numerical control means.
It can be mass-produced. In addition, the multi-axis numerical control means is controlled by the numerical control processing program to perform the automatic repetitive processing, so that the operation of a plurality of spring forming apparatuses can be managed by one operator or can be performed unattended.

The spring forming device according to the present invention is not limited to the above-described embodiment, but can be configured in various forms without departing from the gist of the present invention. For example, in order to bring each tool operating mechanism closer to each other, each circulating drive mechanism is provided on the rear side of each tool operating mechanism, or the machining cycle time per spring is further reduced to improve productivity. Therefore, the quill can be configured to be rotatable, or the spring can be machined by freely selecting the number of tool operating mechanisms and the type of machining tool according to the shape of the spring to be machined and the required accuracy. You can do it.

[0149]

【The invention's effect】

The present invention has been made as described above, and has the following effects.

According to the first aspect of the present invention, each of the tool operating mechanisms enables the individually removably movable orbiting moving table to be individually orbitable along the orbital path, and one or a plurality of the orbiting moving tables are provided around the quill axis. The tool is positioned by orbiting and / or moving forward and backward, so that the degree of freedom of the spring processing shape is not restricted and a spring with a complicated shape can be easily processed. The effect that improvement can be achieved is produced. In addition, since the number of processing tools to be provided can be reduced, there is an effect that the manufacturing cost of the processing tools and the structure of the spring forming device can be simplified to reduce the manufacturing cost.

According to the second aspect of the present invention, the orbiting guide mechanism is configured such that each orbital moving table and each tool operating mechanism are moved by the orbiting guide body and each of the rolling wheels that can rotate and revolve. Are arranged so that they can be individually circulated along the axis, so that the working tool can be smoothly circulated to the circulating set position, and the other working tools can be evacuated smoothly.

According to the third aspect of the present invention, the orbiting guide body of the orbiting guide mechanism is configured such that the orbital raceway surface is composed of a convex or concave inner peripheral raceway surface and an outer peripheral raceway surface. Since at least two rolling wheels that can be combined are provided, there is an effect that it is possible to secure the holding force of each of the orbital moving tables that orbits each of the tool operating mechanisms.

According to the fourth aspect of the present invention, each of the orbital driving mechanisms is individually provided on each of the orbital moving tables of the orbital guide mechanism. According to the present invention, it is possible to selectively and easily add or remove each orbiting moving base of the orbiting guide mechanism together with each of the tool operating mechanisms in accordance with the required number of machining tools. In addition, assuming the maximum required number of machining tools, it is possible to eliminate waste such as constructing a revolving drive mechanism corresponding to the maximum required number in advance, thereby simplifying the structure of the spring forming device and reducing the manufacturing cost. The effect that can be aimed at is produced.

According to the fifth aspect of the present invention, the orbiting drive mechanism controls each of the orbital drive servomotors individually for rotational positioning control so that each of the orbital moving tables together with the respective tool operating mechanisms is on the orbital track. The individual tools are moved individually along the circle to position each machining tool at the rotation setting position, so that one or more machining tools can be selectively moved to the machining advance position or the retreat standby position at the appropriate time. This has the effect of being able to perform positioning. Further, since the setup change time for exchanging a processing tool or the like can be reduced, there is an effect that productivity can be improved.

According to the sixth aspect of the present invention, each of the forward / backward drive mechanisms is individually provided on each of the orbiting moving tables of the orbiting guide mechanism. According to the present invention, it is possible to selectively and easily add or remove each orbiting moving base of the orbiting guide mechanism together with each of the tool operating mechanisms in accordance with the required number of machining tools. In addition, assuming the maximum required number of machining tools, it is possible to eliminate waste such as constructing an advance / retreat drive mechanism corresponding to the maximum required number in advance, thereby simplifying the structure of the spring forming apparatus and reducing the manufacturing cost. The effect that can be aimed at is produced.

According to the seventh aspect of the present invention, the forward / backward drive mechanism controls each of the forward / backward drive servomotors individually for rotational positioning control, so that each sliding body of each tool operating mechanism can be moved together with each machining tool. Since each machining tool is moved individually along the respective axes of reciprocation to position each machining tool at the reciprocation setting position, the degree of freedom of the spring processing shape is not restricted, and a spring with a complicated shape can be easily machined. There is an effect that productivity can be improved by facilitating the machining program. Further, in combination with the effect of the above-described circulating drive mechanism, the number of processing tools to be provided can be reduced, so that the manufacturing cost of the processing tool and the structure of the spring forming device can be simplified to reduce the manufacturing cost. The effect that can be performed.

Further, according to the invention of claim 8, at least one tool operating mechanism enables two or more working tools for bending, winding or cutting a wire to be capable of turning and moving forward and backward. By holding the turning drive actuator to control the rotation and positioning of the turning tool table, the turning tool table is turned to position the working tool among the two or more working tools at a tool turning setting position at which the wire tool can be engaged. Since the degree of freedom of the spring processing shape is not restricted, a spring having a complicated shape can be easily processed, and there is an effect that productivity can be improved by simplifying a processing program.
In addition, since the number of processing tools to be provided can be reduced, there is an effect that the manufacturing cost of the processing tools and the structure of the spring forming device can be simplified to reduce the manufacturing cost.

[Brief description of the drawings]

FIG. 1 is an overall explanatory view showing an example of an embodiment according to the present invention, and is a front view of a spring forming apparatus.

FIG. 2 is an overall explanatory view showing an example of an embodiment according to the present invention, and is a cross-sectional view taken along the line AA of FIG.

3 is an explanatory view of a straight tool operating mechanism and a forward / backward drive mechanism thereof according to the present invention, and is an enlarged front view of the portion shown in FIG.

4 is an explanatory view of a straight tool operating mechanism and a forward / backward drive mechanism thereof according to the present invention, and is a cross-sectional view taken along line BB of FIG.

FIG. 5 is an explanatory view of a rotary tool operating mechanism and an advance / retreat driving mechanism thereof according to the present invention, and is an enlarged front view of the portion shown in FIG.

6 is an explanatory view of the rotary tool operating mechanism and the advance / retreat driving mechanism thereof according to the present invention, and is a cross-sectional view taken along the line CC of FIG. 5;

FIG. 7 is an explanatory view of a turning tool operating mechanism and its forward / backward drive mechanism according to the present invention, and is an enlarged front view of the portion shown in FIG.

8 is an explanatory view of the turning tool operating mechanism and the advance / retreat driving mechanism thereof according to the present invention, and is a cross-sectional view taken along the line DD of FIG. 7;

9 is an explanatory view of a circulating guide mechanism and a circulating drive mechanism according to the present invention, and is a plan view taken along the line EE in FIG. 2;

FIG. 10 is an explanatory view of the orbiting drive mechanism according to the present invention, and is a plan view taken along the line FF of FIG. 5;

11A and 11B are explanatory views showing an example of a spring processed by the spring forming apparatus according to the present invention, wherein FIG. 11A is a front view of a torsion coil spring, and FIG. 11B is a side view of FIG.

12A and 12B are explanatory views showing a first processing step of the torsion coil spring, wherein FIG. 12A is a front view, and FIG. 12B is a side view near the quill of FIG.

13A and 13B are explanatory views showing a second processing step of the torsion coil spring, wherein FIG. 13A is a front view, and FIG. 13B is a side view near the quill of FIG.

14 (a) is a front view, and FIG. 14 (b) is a side view near the quill of FIG. 13 (a).

15A and 15B are explanatory views showing a third processing step of the torsion coil spring, wherein FIG. 15A is a front view, and FIG. 15B is a side view near the quill of FIG.

16A and 16B are explanatory views showing a fourth processing step of the torsion coil spring, wherein FIG. 16A is a front view, and FIG. 16B is a side view near the quill of FIG.

FIG. 17 is an explanatory view showing the same fourth processing step as in FIG. 16, wherein (a) is a front view and (b) is a side view near the quill of (a).

FIGS. 18A and 18B are explanatory views showing a fifth processing step of the torsion coil spring, wherein FIG. 18A is a front view, and FIG. 18B is a side view near the quill of FIG.

19A and 19B are explanatory views showing a sixth processing step of the torsion coil spring, wherein FIG. 19A is a front view, and FIG. 19B is a side view near the quill of FIG.

20 is an explanatory view showing the same sixth processing step as FIG. 19, wherein (a) is a front view and (b) is a side view near the quill of (a).

21A and 21B are explanatory views showing a seventh processing step of the torsion coil spring, wherein FIG. 21A is a front view, and FIG. 21B is a side view near the quill of FIG.

FIGS. 22A and 22B are explanatory views showing an eighth processing step of the torsion coil spring, wherein FIG. 22A is a front view, and FIG. 22B is a side view near the quill of FIG.

23 is an explanatory view showing the same eighth processing step as FIG. 22. FIG. 23 (a) is a front view, and FIG. 23 (b) is a side view near the quill of FIG.

[Explanation of symbols]

2 Formed Substrate 3 Spring Forming Space 10 Wire Feeding Mechanism 11A, 11B Feed Roller 14 Quill 20A, 20B, 20C Circumferential Guide 21 Inner Guide 21a Inner Track 22 Outer Guide 22a Outer Track 23, 24, 25 Orbital moving table 26a to 26i Rolling wheel 30A, 30B, 30C Orbital driving mechanism 31 Fixed gear 32a, 32b, 32c Rotating gear 40 Straight tool operating mechanism 41 Sliding guide 42 Slider 43 Straight tool holder 50 Rotating tool operating mechanism REFERENCE SIGNS LIST 51 sliding guide 52 sliding body 53 bending tool holder 60 turning tool operating mechanism 61 sliding guide 62 sliding body 63 turning tool holder 64 turning tool table 69 turning drive servomotor (turning actuator) 70, 80, 90 Drive mechanism 73, 83, 93 Forward / backward operation cam 76, 86, 96 A S torsion coil spring T1 spirally wound tool T2 bending tool T2a bent projections T3 pitch tool T4 cutting tool W wire

Claims (8)

[Claims] 1. A quill for guiding a wire fed from a rear surface side of a molded substrate to a spring forming space on a front surface side, and respective sliding bodies capable of moving forward and backward along respective radially moving forward and backward moving axes substantially converging on the quill axis. Having a plurality of tool operating mechanisms that movably carry each processing tool that bends, winds, or cuts the wire in front of the quill. On the front surface of the molded substrate, the plurality of tool operating mechanisms are individually detachable, and
A circulating guide mechanism that circulates and guides a plurality of circulating carriages that can individually circulate along a circling track centered on the quill axis, and each circulating carriage of this circulating guide mechanism is individually associated with each tool operating mechanism. A circulating drive mechanism that circulates, and an advance / retreat drive mechanism that individually advances / retreats each sliding body of each of the tool operating mechanisms together with each processing tool,
The rotation drive mechanism and the advance / retreat drive mechanism can be relatedly controlled to move and position one or a plurality of processing tools among the tool operation mechanisms to a rotation set position and an advance / retreat set position, respectively. A spring forming apparatus comprising: a control means for positioning one or more processing tools by orbiting and / or advancing and retreating about a quill axis. 2. The orbiting guide mechanism includes an orbiting guide body fixed along the orbital surface, the orbital guide surface being fixed to the molding substrate and capable of orbiting each of the orbital moving bases. A plurality of the orbital moving bases provided so as to face the body, and a plurality of the rotatable and revolving mated to the respective orbital moving bases and engaged with the orbital surfaces of the orbital guides. The rolling wheels are provided so that each of the orbiting moving tables can be individually orbitally moved by the orbiting guides and each of the rolling wheels together with a respective tool operating mechanism. A spring forming apparatus according to claim 1. 3. The orbital guide body of the orbital guide mechanism, wherein the orbital raceway surface is formed in a convex or concave shape, and the convex or concave portion has an inner circumferential orbital surface formed toward the quill axis. And each of the rolling wheels is configured to move at least two rolling wheels capable of engaging with the inner circumferential raceway surface and the outer circumferential raceway surface. The spring forming apparatus according to claim 2, wherein the spring forming apparatus is attached to a table. 4. The orbiting driving mechanism is a plurality of mechanisms for individually orbiting the orbiting moving tables of the orbiting guide mechanism together with respective tool operating mechanisms, wherein each of the orbiting driving mechanisms includes the orbiting guide mechanism. The spring forming apparatus according to any one of claims 1 to 3, wherein the spring forming apparatus is individually provided on each of the orbiting moving tables. 5. A circulating drive mechanism comprising: a fixed gear fixedly attached to the forming substrate at a position near the circulating guide mechanism and having a tooth shape formed on a circumference centered on a quill axis; Each of the rotating gears provided to be able to mesh with the fixed gear at a position near each of the orbiting moving tables of the orbiting guide mechanism, and each of the turning gears attached to each of the orbiting moving tables to individually turn the respective rotating gears. A rotating drive servomotor, wherein the control means is capable of individually rotating and controlling each of the rotating drive servomotors, and individually rotating each of the rotating gears by each of the rotating drive servomotors. 5. The method according to claim 1, wherein each of the orbiting moving tables is individually orbitally moved together with each of the tool operating mechanisms to position each of the processing tools at a orbit setting position. 6. To Mounting is a spring forming apparatus. 6. The reciprocating drive mechanism is a plurality of mechanisms for individually reciprocating each sliding body of each of the tool operating mechanisms together with a respective processing tool. The spring forming apparatus according to any one of claims 1 to 5, wherein the spring forming apparatus is individually provided on each of the orbiting moving tables. 7. The reciprocating drive mechanism is provided integrally with each of the slides and is rotatable, and each cam follower is rotatable, and at least the amount of advance and retreat of each of the slides is abuttable on each of the cam followers. Reciprocating operation cams each having a cam curved surface of an undulating trajectory capable of satisfying the following conditions, and reciprocating drive servomotors respectively attached to the revolving moving tables of the revolving guide mechanism and individually rotating the reciprocating operation cams. And each cam biasing spring that constantly biases each of the cam followers so as to be able to always contact with each of the advance / retreat operation cams, wherein the control means is capable of individually controlling the rotation / position of each of the advance / retreat drive servomotors. As described above, by individually rotating the respective advance / retreat operation cams by the respective advance / retreat drive servo motors, the respective sliding bodies of the respective tool operation mechanisms are moved together with the respective processing tools. 7. The method according to claim 1, wherein each of the working tools is moved to and retracted along a respective moving axis of each of the moving tools so as to position each of the processing tools at a respective set position of the moving tool. Spring forming equipment. 8. At least one of the tool operating mechanisms is a sliding body that carries two or more processing tools for bending, winding, or cutting the wire so as to be capable of turning and moving forward and backward. A swivel tool holder integrally engaged with the sliding body, and a pivotally movable pivotally movable to the swivel tool holder about a pivot axis parallel to the quill axis. A turning tool table which is supported and on which the two or more processing tools can be attached and detached, and a turning drive actuator which is attached to the turning tool holder and turns the turning tool table; A drive actuator is capable of rotational positioning control, and the turning tool table is turned by the turning drive actuator, so that the working tool among the two or more working tools is the wire rod. And a spring forming apparatus according to claim 1, characterized in that so as to position the abutment or engageable tool pivot setting position.