JP2022167134A - Metal mold rotating device and heading machine - Google Patents

Abstract

To provide a metal mold rotating device configured to rotate either of a fixed metal mold and a movable metal mold oppositely arranged so as to be applicable to work different from heading processing work.SOLUTION: A metal mold rotating device 5 comprises: a fixed metal mold (a die 44) having a central axis line CL, which holds a work-piece W; a movable metal mold (a punch 41), arranged at a position in an extending direction of the central axis line CL to oppose to the fixed metal mold (44), which executes predetermined work to the work-piece W in cooperation with the fixed metal mold (44); and a rotating/driving mechanism 6 that rotates a rotary metal mold (44) which is either of the fixed metal mold (44) and the movable metal mold (41) around the central axis line CL.SELECTED DRAWING: Figure 3

Description

TECHNICAL FIELD The present invention relates to a die rotating device for rotating either a fixed die or a movable die arranged opposite to each other, and a forging machine equipped with this die rotating device.

In a general forging machine, a die (fixed mold) and a punch (movable mold), which are placed opposite each other, jointly carry out forging work on the workpiece, and generate plastic deformation to produce a part with a predetermined shape. . A configuration example of this type of forging machine is disclosed in Patent Document 1. The horizontal continuous multi-stage forging machine of Patent Document 1 includes a ram that can move forward and backward in a first direction, a plurality of punches arranged in a second direction of the ram, and a plurality of punches fixedly arranged in the second direction. and a transfer unit for transferring the work.

Japanese Patent Application Laid-Open No. 2018-8281

By the way, in order to stabilize the operation of conveying the work by the transfer unit, it is sometimes preferable to change the posture of the work that has undergone the forging operation, instead of maintaining the posture. For example, by changing the posture of the workpiece so as to match the shape and operation mode of the fingers that grip the workpiece while considering the position of the center of gravity and the gripping position of the workpiece, it may be possible to reduce the risk of the workpiece falling. However, in a conventional forging machine, it is difficult to change the attitude of the work ejected from the die immediately before it is gripped. Therefore, there is a need for a technique for rotating the die holding the work around the central axis to change the posture of the work together with the die.

In addition, the technology to rotate the die around the central axis is not limited to the configuration of rotating the die or changing the posture of the workpiece, but it is possible to modify the configuration and apply it to other uses. is. For example, the object to be rotated may be punches instead of dice. Further, for example, by rotating the mold, it is possible to perform cutting work and twisting work on the work.

The present invention has been made in view of the problems of the background art described above, and is capable of being applied to work applications different from forging work by rotating either the fixed mold or the movable mold that are opposed to each other. It is an object of the present invention to provide a mold rotating device that is made in such a way as to provide a forging machine equipped with this mold rotating device.

The mold rotating apparatus of the present invention includes a fixed mold having a central axis and holding a workpiece, and a fixed mold arranged at a position in the extending direction of the central axis and facing the fixed mold. a movable mold that jointly performs a predetermined operation on the workpiece; and a rotary drive mechanism that rotates a rotary mold, which is either the fixed mold or the movable mold, around the central axis. .

Further, the forging machine of the present invention comprises a main drive source for reciprocating the movable mold along the central axis to perform the forging work on the workpiece, a mold rotating device for rotating the rotating mold at least one of the time.

In the mold rotating device and forging machine of the present invention, the rotation drive mechanism can rotate either the fixed mold or the movable mold around the central axis, so that the rotation of the mold is different from the forging work. Can be applied to work applications.

BRIEF DESCRIPTION OF THE DRAWINGS It is a top view which shows typically the whole structure of the forging machine which can apply the metal mold|die rotation apparatus of 1st Embodiment. FIG. 2 is a side cross-sectional view showing the configuration of a die corresponding to a rotary mold of a mold rotating device and a rotary drive mechanism; It is the expansion perspective view which looked at a part of mold rotation apparatus from the diagonally downward direction. FIG. 4 is a perspective view illustrating the shape and posture in each process of a work manufactured by a multi-process forging machine. FIG. 5 is a time chart for explaining the operation when changing the posture of the workpiece by the mold rotating device in the third forging process of the forging machine shown in FIG. 4 ; FIG. 10 is a diagram schematically showing a configuration example in which a punch corresponding to a rotary mold cuts a workpiece in the mold rotating device of the second embodiment; 7 is a time chart for explaining the operation in the configuration example of FIG. 6; FIG. FIG. 11 is a diagram schematically showing a configuration example for twisting a workpiece in the mold rotating device of the third embodiment; 9 is a diagram showing the shape of a part manufactured by the configuration example of FIG. 8; FIG.

1. Overall Configuration of Forging Machine 1 First, the overall configuration of a forging machine 1 to which the mold rotating device 5 of the first embodiment can be applied will be described with reference to FIGS. 1 and 2. FIG. The forging machine 1 is a horizontal multi-process forging machine. The forging machine 1 is composed of a frame 2, a ram 3, five sets of punches 41 and dies 44, a workpiece transfer section 49, a main drive section 9, and the like. The forging machine 1 performs forging work on the work W in the first to fifth forging processes composed of five sets of punches 41 and dies 44 . The punch 41 is another name for a movable mold, and the die 44 is another name for a fixed mold. In FIG. 1, the first to fifth heading processes are arranged from top to bottom. Note that the number of forging processes of the forging machine 1 is not limited to 5 processes, and is in the range of about 1 to 8 processes.

The frame 2 is a housing for arranging each part, and is made of iron and formed robustly. The five die holders 21 are arranged side by side in the width direction of the frame 2 . Five dies 44 are replaceably attached to the front side (left side in FIG. 1) of each die holder 21 . A predetermined working die is formed in front of each die 44 . The die 44 has a central axis CL (see FIG. 2) and holds the workpiece W in the working die.

The ram 3 is generally rectangular in plan view, and reciprocates in the front-rear direction (left-right direction in FIG. 1) with respect to the frame 2 . The five punch holders 31 are provided side by side in the width direction on the front side of the ram 3 (on the right side in FIG. 1). Five punches 41 are replaceably attached to the front side of each punch holder 31 . A predetermined working die is formed on the front side of each punch 41 . Each punch 41 reciprocates with the ram 3 . The punch 41 is arranged at a position in the extending direction of the center axis CL and faces the die 44 . The punch 41 performs forging work on the work W in cooperation with the die 44 . The work performed jointly by the punch 41 and the die 44 is not limited to the forging work using the working die, and may be other work.

The forging machine 1 includes a cutting mechanism (not shown). The cutting mechanism has a ring-shaped movable cutter, a wire feeding mechanism, and a pusher mechanism. The movable cutter cuts the long wire inserted into the ring by the wire feeding mechanism to create a columnar workpiece of a predetermined size. A pusher mechanism pushes the workpiece out of the movable cutter. Aluminum, iron, various alloys, and the like can be exemplified as materials for the wire rod and the work.

The work conveying unit 49 is arranged from above the die holder 21 to the front of the die 44 . The work conveying unit 49 is also called a transfer device. The work conveying part 49 has six pairs of fingers for gripping the work. The most upstream first pair of fingers grips the workpiece produced by the cutting mechanism and conveys it to the first forging process. The second to fifth finger pairs grip the work in the upstream forging process and convey it to the downstream forging process. The sixth pair of fingers on the most downstream side grips the work in the fifth forging process and conveys it to a carry-out section (not shown).

A main drive 9 is provided for driving the ram 3 back and forth. The main drive unit 9 is composed of a main drive source 91, various transmission mechanisms, cam mechanisms, and the like. The main drive source 91 can be, for example, an induction motor or a synchronous motor operating on a three-phase AC power supply. The main driving section 9 drives the work conveying section 49 and the cutting mechanism together. The driving force of the main drive source 91 is input to a crankshaft 95 that drives the ram 3 via a flywheel 92 , a disc brake 93 and a speed reduction mechanism 94 . Further, the driving force is branched and transmitted from the crankshaft 95 to the side shaft 97 via the pair of branched gears 96 .

The side shaft 97 branches and transmits the driving force upward. The driving force branched upward drives the transfer cam 98 to rotate. The transfer cam 98 drives the work conveying section 49 . Further, six open-close cams 9A are connected to the side shaft 97 via a transfer drive 99 so as to be rotationally driven. The open/close cams 9A are arranged at regular intervals in the width direction. The open/close cam 9A drives the finger pairs to open and close.

Further, the side shaft 97 is provided with a cutter cam 9B, and is connected to a pusher cam 9C, a feed cam 9D, a wire feeding device 9E, and five kickout cams 9F. A cutter cam 9B, a pusher cam 9C, a feed cam 9D, and a wire feeding device 9E drive the cutting mechanism. The kickout cams 9F are arranged at equal intervals in the width direction and correspond to the positions of the first to fifth forging processes. The kickout cam 9F drives a kickout pin 4A, which will be described later.

2. Configuration Near Die 44 Next, the configuration near the die 44 will be described with reference to FIG. For convenience, the right side of FIG. 2 is the front side and the left side is the rear side. As illustrated, the die holder 21 is configured by connecting a holder member 211, a back plate 212, and a die frame 213 from the front side to the rear side. These three members are each formed in a tubular shape sharing a central axis CL extending in the front-rear direction. Moreover, these three members are pressed together in the front-rear direction.

The cylindrical holder member 211 has a stepped inner peripheral surface, and has a large inner diameter at the front end and in the range from the intermediate position to the rear end. A thrust bearing 214 is provided at a portion having a large inner diameter at the front end of the holder member 211 . A rotation operation space 215 is defined in a rear portion of the holder member 211 having a large inner diameter. The cylindrical back plate 212 has an inner diameter smaller than the outer diameter of the die 44 . The cylindrical die frame 213 has a large inner diameter on the front side and a small inner diameter on the rear side.

The die 44 is held between the thrust bearing 214 and the back plate 212 so as not to move in the longitudinal direction. Also, the die 44 is held inside the holder member 211 so as to be rotatable around the central axis CL. A thrust bearing may be provided on the front side of the back plate 212 to reduce frictional force when the die 44 rotates. The die 44 holds the workpiece W inside a working die formed on the front side. Since the shape of the working mold can be changed in various ways, illustration and description of specific shapes are omitted. The die 44 is generally cylindrical, and the kickout pin 4A is inserted into the die 44 from behind.

The kickout pin 4</b>A performs a projecting operation for projecting the work W on which the forging operation has been performed from the die 44 . The kickout pin 4A is arranged on the central axis CL and supported so as to be movable in the front-rear direction. The kickout pin 4A is formed in the shape of a stepped round bar whose diameter size changes at several points. The tip 4C of the kickout pin 4A can enter the rear part of the die 44 and contact the workpiece W. As shown in FIG. The tip 4C of the kickout pin 4A may serve as a part of the working die of the die 44.

The kickout pin 4A has a large-diameter flange 4B on the rear side. A portion of the kickout pin 4A behind the collar portion 4B is housed inside a substantially cylindrical head adjusting screw 4F. The retracted position of the kickout pin 4A is determined by the contact of the collar portion 4B with the neck adjustment screw 4F. The neck adjustment screw 4F is screwed into a frame body 841 (described later), and its position is adjusted in the front-rear direction. This adjusts the retracted position of the kickout pin 4A. A rear end 4D of the kickout pin 4A is driven by a main drive source 91 via a kickout cam 9F.

While the punch 41 approaches the die 44 and the heading operation progresses, the kickout pin 4A remains in the retracted position shown in FIG. As the forging operation is completed and the punch 41 moves away from the die 44 , the kickout pin 4A is driven to the forward position by the kickout cam 9F to push the workpiece W forward of the die 44 . Thereafter, the kickout pin 4A is pushed rearward by an urging spring 4E, which will be described later, and returns to the retracted position while following the kickout cam 9F.

3. Configuration and Operation of Mold Rotating Device 5 of First Embodiment Next, the configuration and operation of the mold rotating device 5 of the first embodiment will be described with reference to FIGS. 2 and 3. FIG. The mold rotating device 5 is applicable to at least one forging process of the forging machine 1 . The mold rotating device 5 is composed of a die 44, a punch 41, a rotation drive mechanism 6, and the like. The rotary drive mechanism 6 rotates the rotary mold, which is either the die 44 or the punch 41, around the central axis CL. In the first embodiment, the rotary drive mechanism 6 rotates the die 44, which is a rotary mold, and causes the die 44 to change the posture of the work W to change its posture. The rotation drive mechanism 6 is composed of an operation member 61, a spiral groove 62, a guide pin 63, a rotation prevention portion 7, a drive portion 8, and the like.

In FIG. 3, the lower halves of the die 44 and the operating member 61 are shown, and the upper halves are omitted. The operating member 61 is formed in a cylindrical shape and arranged on the outer peripheral side of the die 44 . The inner diameter of the operating member 61 is the same as the outer diameter of the die 44 and has a plus tolerance, or is set slightly larger than the outer diameter of the die 44 . The operation member 61 is arranged in a rotation operation space 215 inside the holder member 211, as shown in FIG. The operating member 61 can move in the extending direction of the central axis CL while sharing the central axis CL.

The spiral groove 62 is provided in the operating member 61 so as to be inclined with respect to the central axis CL, as shown in FIG. The spiral groove 62 is formed linearly so as to have a constant inclination angle with respect to the central axis CL. Alternatively, the spiral groove 62 may be formed in a curved shape so that the inclination angle gradually changes. The inclination angle and groove length of the spiral groove 62 are determined so as to correspond to the desired rotation angle range for rotating the die 44 . In the first embodiment, the spiral groove 62 is formed to accommodate a 25° rotation angle range of the die 44 . The spiral grooves 62 are preferably provided at a plurality of positions in the circumferential direction of the operating member 61 . In the first embodiment, the spiral grooves 62 are provided at two side surfaces of the operating member 61 that are 180° apart in the circumferential direction.

The guide pin 63 is a cylindrical member, and is erected radially outward on the outer peripheral surface of the die 44 . The number of guide pins 63 is the same as the number of spiral grooves 62 . Each guide pin 63 engages with a different spiral groove 62 . The length of the guide pin 63 is set to match the groove depth of the spiral groove 62 or slightly larger than the groove depth. Also, the diameter of the guide pin 63 is set slightly smaller than the groove width of the spiral groove 62 . According to this, the engagement state of the guide pin 63 with respect to the spiral groove 62 is stabilized.

The rotation preventing portion 7 prevents the operation member 61 from rotating around the center axis CL. It is preferable that the rotation preventing portions 7 are provided at a plurality of locations in the circumferential direction. In the first embodiment, the anti-rotation portions 7 are provided at two locations on the lower side and the upper side of the operating member 61 (see FIG. 2). The anti-rotation portion 7 is composed of a flat portion 71 and an anti-rotation body 72 . The planar portion 71 is provided on the outer peripheral surface of the operation member 61 and is formed by cutting, for example. The planar portion 71 is a substantially rectangular planar portion extending in the extending direction of the center axis CL and in the width direction orthogonal to the extending direction.

The anti-rotation member 72 is formed of a rod-shaped member extending in the width direction. Both ends of the anti-rotation member 72 are fixed to the inner peripheral surface of the holder member 211 . The anti-rotation member 72 is in contact with substantially the entire length of the flat portion 71 in the width direction throughout the movement of the operating member 61 in the extending direction of the central axis CL. This prevents the operation member 61 from rotating, thereby stabilizing the rotation of the die 44, which will be described later. Further, the rotation of the die 44 is facilitated by the combination of the plurality of sets of spiral grooves 62 and guide pins 63 and the arrangement of the plurality of anti-rotation portions 7 alternately in the circumferential direction.

The drive unit 8 drives the operation member 61 in the extending direction (front-rear direction) of the center axis CL. The drive section 8 is composed of a plurality of operation pins 81, a drive pin 83, a drive source section 84, a liquid source container 8A, a liquid path operation section 8B, a hydraulic liquid control section 8C, a plate position detection section 8D, and the like.

The plurality of operation pins 81 are positioned equidistantly from the central axis CL and arranged at equal intervals in the circumferential direction. A plurality of operation pins 81 extend parallel to the central axis CL and are arranged to penetrate through the through holes 216 of the back plate 212 . Six operation pins 81 are illustrated in FIG. A front end of each operating pin 81 is coupled to a rear end of the operating member 61 . A rear end of each operating pin 81 is coupled to a flange-shaped flange portion 82 .

A coil-shaped biasing spring 4E is inserted between the collar portion 82 and the collar portion 4B of the kickout pin 4A. A biasing spring 4E biases the kickout pin 4A rearward. A cylindrical drive pin 83 is arranged on the outer peripheral side of the biasing spring 4E. A front end of the drive pin 83 is coupled to the collar portion 82 . The rear end of drive pin 83 is coupled to coupling plate 842 (discussed below).

The drive source 84 is arranged behind the die frame 213 of the die holder 21 . The drive source unit 84 is composed of a frame 841, two hydraulic drive sources 85, two sets of front liquid passages 88 and rear liquid passages 89, a coupling plate 842, and the like. Since a single hydraulic drive source 85 cannot provide a desired operating force, two hydraulic drive sources 85 are used in parallel. The frame body 841 is a hollow frame-shaped member that opens forward and is arranged in contact with the rear side of the die frame 213 .

The two hydraulic drive sources 85 are provided inside the frame 841 toward the rear. In addition, the two hydraulic drive sources 85 are separated and arranged vertically symmetrically when viewed from the center axis CL. A head adjusting screw 4F is arranged between the two hydraulic drive sources 85 .

Each hydraulic drive source 85 has a cylinder 86 and a piston 87 . The cylinder 86 is formed in a bottomed cylindrical shape that opens forward. The piston 87 is arranged inside the cylinder 86 and protrudes forward. The piston 87 is a round bar-shaped member having a small diameter portion on the front side and a large diameter portion on the rear side. A liquid-tight groove and an O-ring (reference numerals omitted) are provided on the outer periphery of the large-diameter portion. This constitutes a liquid-tight structure between the cylinder 86 and the piston 87 .

The coupling plate 842 is elongated vertically. A connecting plate 842 is connected to the front sides of the two pistons 87 using bolts 843 as shown in FIG. A hole provided in the center of the coupling plate 842 is loosely fitted with a neck adjustment screw 4F. A rear end of the drive pin 83 is coupled to the front side of the coupling plate 842 . Therefore, the two pistons 87, the coupling plate 842, the driving pin 83, the operating pin 81, and the operating member 61 move integrally in the front-rear direction.

A closed space defined by the outer surface of the small-diameter portion of the piston 87 and the inner surface of the cylinder 86 serves as a front liquid chamber 861 . A closed space defined by the rear surface of the piston 87 and the inner bottom surface of the cylinder 86 serves as a rear liquid chamber 862 . A front communication port 863 that communicates with the front fluid chamber 861 from the outside is provided through the side surface of the cylinder 86 . Similarly, a rear communication port 864 is provided through the side surface of the cylinder 86 to communicate with the rear fluid chamber 862 from the outside.

The front communication port 863 communicates with the liquid source container 8A via the front liquid path 88 and the liquid path operating section 8B. The rear side communication port 864 communicates with the liquid source container 8A via the rear side liquid path 89 and the liquid path operating portion 8B. The front liquid passages 88 and the rear liquid passages 89 of the two hydraulic drive sources 85, in other words, the four liquid passages have the same length and the same cross-sectional area. As a result, the operating characteristics when the two hydraulic drive sources 85 operate in synchronism well match each other. A resin tube, a metal pipe, or the like is used for the front liquid passage 88 and the rear liquid passage 89 . Hydraulic oil can be exemplified as the hydraulic fluid used for the hydraulic drive source 85, but is not limited to this.

The liquid path operation unit 8B is configured by a combination of pumps and valves (not shown). The liquid path operation section 8B controls the flow of hydraulic fluid flowing between the two hydraulic drive sources 85 and the liquid source container 8A. The hydraulic fluid control portion 8C controls the operation of the fluid path operation portion 8B. The hydraulic fluid control unit 8C is configured using, for example, a computer device having a control signal input/output function. A plate position detector 8D is attached to the hydraulic fluid controller 8C.

The plate position detector 8D detects the position of the coupling plate 842 in the front-rear direction. The plate position detector 8D is composed of an encoder 8E and a linear gauge 8F. The linear gauge 8F is provided on top of the coupling plate 842 and moves back and forth together with the coupling plate 842 . The linear gauge 8F is provided with a scale engraved at a predetermined pitch in the front-rear direction. The encoder 8E is fixedly attached to the frame 841 and arranged to face the linear gauge 8F. The encoder 8E reads the scale of the linear gauge 8F, encodes it, and outputs it to the hydraulic fluid control section 8C. For example, a magnetic detection sensor can be used as the plate position detection unit 8D.

The hydraulic fluid control unit 8C receives the output of the encoder 8E and also receives information regarding the operation status of the main drive source 91. As shown in FIG. The hydraulic fluid control unit 8C obtains the current position of the operating member 61 based on the output received from the encoder 8E. In addition, the hydraulic fluid control unit 8C refers to the operation status of the main drive source 91 and controls the fluid path operation unit 8B in a timely manner to control the operation of the operation member 61. FIG.

In FIG. 2, the front side liquid chamber 861 has the maximum volume, and the rear side liquid chamber 862 has the minimum volume. At this time, the piston 87 is located at the retracted position. When the hydraulic fluid flows out from the front fluid chamber 861 and flows into the rear fluid chamber 862 under the control of the hydraulic fluid control section 8C, the piston 87 moves by a movement amount corresponding to the amount of inflow and outflow of the hydraulic fluid. move forward. Conversely, when the hydraulic fluid flows out of the rear fluid chamber 862 and flows into the front fluid chamber 861, the piston 87 moves backward. The operation member 61 moves forward and backward in synchronization with the forward motion and backward motion of the piston 87 .

Note that if one hydraulic drive source 85 were to flow in and out first, the operating force output to the coupling plate 842 would momentarily be only one. At this time, the operation member 61 does not operate, or operates at a low speed even if it can operate. Then, the inflow and outflow of the hydraulic fluid in the other hydraulic drive source 85 catches up in a short time, and the operating force is output from both hydraulic drive sources 85 to the coupling plate 842 . After that, the two hydraulic drive sources 85 operate synchronously. Therefore, the operating forces output from the two hydraulic drive sources 85 are added together, and the operating member 61 can exert a large operating force.

As shown by arrow M1 in FIG. 3, when the operation member 61 advances from the retracted position in the extending direction of the central axis CL, the guide pin 63 moves along the spiral groove 62 as shown by the arrow M2. move to At this time, since the guide pin 63 is fixed to the die 44, it cannot move in the extending direction of the central axis line CL, and actually only rotates in the circumferential direction. As a result, the die 44 rotates around the central axis CL as indicated by an arrow M3. When the operating member 61 reaches the forward-most forward position, the die 44 is rotated by 25°. Further, when the operation member 61 returns from the forward position to the retracted position, the die 44 is rotated 25 degrees to return to its original state. The rotary motion of the die 44 can be applied to work applications other than heading operations.

Here, the driving section 8 is different from the main driving source 91 and has a degree of freedom of driving independent from the main driving source 91 . Therefore, by setting various drive timings and drive speeds when the drive unit 8 drives the rotation of the die 44, it is possible to apply the rotation of the die 44 to various work applications. In addition, since the drive unit 8 using the hydraulic drive source 85 can be controlled with higher precision than the drive using the kickout cam 9F, the die 44 can be accurately rotated and rotated at an appropriate angle and speed. Rotation timing is realized.

4. Operation Example of Forging Machine 1 Next, an operation example of the forging machine 1 to which the mold rotating device 5 is applied will be described with reference to FIGS. 4 and 5. FIG. In the operation example, the forging machine 1 has first to sixth forging processes (#1 to #6), and the mold rotating device 5 is applied to the third forging process (#3). Further, in the operation example, the work W is subjected to forging work and posture changing work as shown in FIG. 4 corresponds to the upper side of the forging machine 1 , and the lower left direction of the paper corresponds to the lower side of the forging machine 1 . The center axis CL extends in the vertical direction in FIG. In each forging process (#1, #2, #4, #5, #6) other than the third forging process (#3), the shape of the work W after the forging operation is performed is illustrated. there is In addition, in the second and fourth forging steps (#2, #4), a partial cross section obtained by cutting a quarter of the work W is shown.

In the operation example of the forging machine 1, first, the cylindrical workpiece W is cut by the cutting mechanism. In the following first forging step (#1), the two cut end faces of the work W are corrected and pilot holes H1 are formed in the two end faces. In the next second forging step (#2), bottomed holes H2 are formed in the two end faces of the work W by slightly enlarging the pilot holes H1. In the next third forging step (#3), instead of the forging work, an attitude change operation for changing the attitude of the work W is performed (details will be described later).

In the next fourth forging step (#4), an upsetting operation is performed to transform the external shape of the work W from a columnar shape to a rectangular parallelepiped shape. In the next fifth forging step (#5), a through hole H3 having a substantially rectangular cross section is formed in the work W. As shown in FIG. In the final sixth forging step (#6), the shape of the inside of the through hole H3 of the work W is corrected.

Next, the operation of changing the posture of the work W in the third heading process (#3) will be described in detail. FIG. 5 shows a time chart when the work for changing the posture of the work W is performed. The horizontal axis of FIG. 5 is the common time axis t. The three graphs show the stroke characteristics of the punch 41, the operating characteristics of the kickout pin 4A, and the operating characteristics of the operating member 61 in order from the top. FIG. 5 depicts one cycle of motion in which the punch 41 moves forward from the rear dead center PR to the front dead center PF and then moves back to the rear dead center PR. The operating characteristics of the kickout pin 4A are realized by the cam shape of the kickout cam 9F. Further, the operation characteristics of the operation member 61 are realized by the control from the hydraulic fluid control section 8C and the operation of the fluid path operation section 8B.

At time t0 in FIG. 5, the punch 41 is positioned at the rear dead center PR. At this time, the kickout pin 4A is positioned at the forward position KF. At the same time, the operating member 61 is in the retracted position SR and the die 44 is not rotating. The punch 41 moves forward with a sinusoidal stroke characteristic as time elapses after time t0, and reaches the front dead center PF at time t2. On the other hand, the kickout pin 4A has already returned from the forward position KF to the retracted position KR at time t1 before time t2. The operating member 61 maintains the retracted position SR throughout the forward movement of the punch 41 .

During forward movement, the punch 41 performs posture changing work for changing the tilted posture of the workpiece W with respect to the central axis CL instead of the forging work. Specifically, as indicated by an arrow A1 in FIG. 4, the punch 41 changes the horizontal posture in which the work W is parallel to the center axis CL to the upright posture in which the work W is perpendicular to the center axis CL in the vertical direction. change the stance. The applicant of the present application has already disclosed in JP-A-2018-024007 a configuration example of the forging process for changing the tilting attitude of the work W with respect to the central axis CL. The third forging step (#3) has a configuration in which the disclosed configuration described above and the mold rotating device 5 of the first embodiment are combined.

Further, the punch 41 starts the return movement at time t2 and returns to the rear dead center PR at time t9. At time t3 during the return movement of the punch 41, the kickout pin 4A starts advancing from the retracted position KR. Subsequently, at time t4, the operating member 61 starts moving forward from the retracted position SR, and at time t5, the operating member 61 reaches the forward position SF. At time t5, the operations indicated by arrows M1 to M3 in FIG. 3 have ended, and the die 44 has been rotated by 25°. As a result, the work W is changed from the upright posture to the tilted posture inclined by 25°, as indicated by the arrow A2 in FIG. In summary, the rotary drive mechanism 6 rotates the die 44 around the central axis CL when the punch 41 moves back, thereby performing an attitude changing operation of changing the rotational attitude of the workpiece W around the central axis CL. have it implemented.

At time t6, which is slightly later than time t5, the kickout pin 4A reaches the forward position KF. As a result, the work W in the inclined posture is projected forward of the die 44 . Thereafter, the workpiece W in the inclined posture is conveyed to the next fourth forging step (#4) by the work conveying section 49. As shown in FIG. From the fourth forging step (#4 to #6), the work W is forged and transported while maintaining the tilted posture. From time t6 to time t7, the operating member 61 returns from the forward position SF to the retracted position. After the work W is ejected, the die 44 is reversely rotated by 25° to return to its original state, and waits for the next work W to be carried.

Here, the tilted posture in which the work W is tilted from the upright posture by 25° is suitable for the shape of the finger pair of the work transfer section 49 and the operation mode. In other words, the inclined posture of the workpiece W is suitable for the pair of fingers to stably grasp and convey the workpiece. According to this, problems such as the workpiece W dropping during transportation or being unable to be held by the die 44 in the downstream process due to a change in posture are suppressed. As a result, the operational reliability of the forging machine 1 is enhanced. In contrast, in a conventional forging machine that does not have the rotary drive mechanism 6, the pair of fingers grasps the side of the workpiece W in an upright position, so that the workpiece W is more likely to slide downward.

In the mold rotating device 5 of the first embodiment, the rotation drive mechanism 6 can rotate the die 44 around the central axis CL, so that the rotating operation of the die 44 can be applied to work applications other than forging work. be able to. For example, in the forging machine 1 to which the mold rotating device 5 is applied, the rotation of the die 44 can be applied to the work for changing the posture of the work W, thereby suppressing the work W from dropping.

5. Mold rotating device 5A of the second embodiment
Next, the mold rotating device 5A of the second embodiment will be mainly described with reference to FIGS. 6 and 7 in terms of differences from the first embodiment. The mold rotating device 5A of the second embodiment can be applied to any forging process of the forging machine 1. FIG. However, in the second embodiment, the rotation drive mechanism 6A rotates the punch 41A, which is a rotary mold, to perform the cutting work. Details will be described below.

As shown in FIG. 6, the punch 41A has a cutting edge 41K at its tip. The cutting blade 41K is formed in an umbrella shape centering on the central axis CL, and has a plurality of radially extending blades. The rotary drive mechanism 6A is mounted on the ram 3 and has an operating member 61 around the punch 41A. A spiral groove 62 is provided on one of the punch 41A and the operating member 61, and a guide pin 63 is provided on the other of the punch 41A and the operating member 61. As shown in FIG. 6 A of rotation drive mechanisms have the same structure as 1st Embodiment, and rotate the punch 41A around the center axis line CL by the same action. On the other hand, the work WA held by the die 44A has a rotationally symmetrical shape about the central axis CL, and has a bottomed round hole WH on the surface facing the punch 41A.

FIG. 7 shows a time chart when cutting the workpiece WA. The horizontal axis of FIG. 7 is the common time axis t. The three graphs show, in order from the top, stroke characteristics of the punch 41A, operating characteristics of the kickout pin 4A, and operating characteristics of the operating member 61 of the rotary drive mechanism 6A. At time t10 in FIG. 7, the punch 41 is positioned at the rear dead center PR, the kickout pin 4A is positioned at the forward position KF, and the operating member 61 is positioned at the retracted position SR. At time t11 before punch 41A reaches front dead center PF at time t11, kickout pin 4A has already returned from forward position KF to retracted position KR.

At the same time t11, the operating member 61 starts moving forward from the retracted position SR, and at time t12, the operating member 61 reaches the forward position SF. As a result, the punch 41A rotates from time t11 to time t12. Before the punch 41A reaches the front dead center PF, the cutting edge 41K abuts against the front inner edge of the round hole WH of the workpiece WA to carry out the cutting operation. As a result, a chamfered portion WM is formed on the front inner edge of the round hole WH of the work WA.

After that, the punch 41 starts the return movement at time t12 and returns to the rear dead center PR at time t19. The kickout pin 4A moves from the retracted position KR to the forward position KF between time t13 and time t14 to eject the work WA. On the other hand, the operation member 61 moves from the forward position SF to the retracted position SR between time t14 and time t15, and the punch 41A rotates in the reverse direction to return to its original state.

In the mold rotating device 5A of the second embodiment, the rotation drive mechanism 6A rotates the punch 41A around the central axis CL during the forward movement, thereby causing the punch 41A to perform cutting instead of forging. . The cutting work performed by rotating the punch 41A is not limited to the chamfering described above. For example, a drill-shaped cutting edge can be provided at the tip of the punch 41A, and the workpiece WA can be drilled by cutting.

Furthermore, in the forging machine 1 to which the die rotating device 5A is applied, both forging work and cutting work can be used. Therefore, the shape range of the work WA that can be manufactured by the forging machine 1 is expanded.

6. Mold rotating device 5B of the third embodiment
Next, the mold rotating device 5B of the third embodiment will be described with reference to FIGS. 8 and 9, mainly on the differences from the first and second embodiments. A mold rotating device 5B of the third embodiment performs a twisting operation on the work WB. In this mold rotating device 5B, the punch 41B does not reciprocate along the central axis CL. Therefore, the die rotating device 5B is not applied to the forging machine 1 and is configured as a single device. The mold rotating device 5B is composed of a die 44B, a punch 41B, a rotation drive mechanism 6B, and the like.

The die 44B has a central axis line CL and is fixed to a frame (not shown). The punch 41B is provided at a position in the extending direction of the central axis CL, is rotatably supported by the frame, and is arranged to face the die 44B. As shown in FIG. 8, the die 44B and the punch 41B grip the ends of the rectangular bar-shaped workpiece WB. The rotation drive mechanism 6B rotates the punch 41B holding the work WB by a predetermined angle around the central axis CL.

As a result, the die 44B and the punch 41B jointly twist the work WB. After the twisting work is completed, the gripped portion of the work WB is cut. Finally, a twist-shaped part P shown in FIG. 9 is produced. In the third embodiment, the rotating motion of the punch 41B can be applied to the twisting work.

7. Modifications and Applications of the Embodiments In the first embodiment, the plate position detection section 8D of the driving section 8 may be omitted, and the position of the operation member 61 may be calculated based on the flow rate of the working fluid. Further, the drive source section 84 of the drive section 8 is not limited to the hydraulic drive source 85, and may be another type of drive source for driving the operation member 61, such as a motor. Further, contrary to the configuration of the first embodiment, a spiral groove 62 may be provided on the outer peripheral surface of the die 44 and a guide pin 63 may be erected radially inward on the operating member 61 . Moreover, it is possible to use a rotary drive method other than the combination of the spiral groove 62 and the guide pin 63 . For example, the die 44 held rotatably may be provided with an operating lever extending radially outward, and the drive section may rotate the operating lever.

Further, in the third forging step (#3) in FIG. 4, the punch 41 is forwardly moved to perform the forging work, and when the punch 41 is backwardly moved, the die 44 rotates to perform the attitude change work. can do. Further, the use of the rotation of the die 44 is not limited to the posture changing work of the work W. For example, when the kickout pin 4A ejects a workpiece having a helical gear shape, by rotating the die 44, the operating force required for ejection can be reduced. Also, the die 44 may be rotated to change the posture of the work W before the punch 41 moves forward to start the forging operation. The present invention is not limited to the configuration of the embodiment, and various applications and modifications other than those described above are possible.

1: Forging machine 2: Frame 3: Ram 41, 41A, 41B: Punch
44, 44A, 44B: Dies 49: Work transfer unit 4A: Kickout pin
5, 5A, 5B: Mold rotating device 6, 6A, 6B: Rotation drive mechanism
61: Operation member 62: Spiral groove 63: Guide pin
7: Rotation prevention part 71: Flat part 72: Rotation prevention body
8: drive unit 81: operation pin 83: drive pin 842: coupling plate
85: Hydraulic drive source 86: Cylinder 87: Piston 8A: Liquid source container
8B: liquid path operation unit 8C: hydraulic fluid control unit 8D: plate position detection unit
9: main drive unit 91: main drive source
CL: Center axis W, WA, WB: Work WM: Chamfer

Claims (11)

a stationary mold that has a central axis and holds the workpiece;
a movable mold arranged at a position in the extending direction of the central axis, facing the fixed mold, and performing a predetermined operation on the workpiece in cooperation with the fixed mold;
a rotary drive mechanism for rotating a rotary mold, which is either the fixed mold or the movable mold, around the central axis;
A mold rotating device. The rotation drive mechanism is
an operation member movable in the extending direction of the central axis while sharing the central axis;
a spiral groove provided in one of the rotating mold and the operating member so as to be inclined with respect to the central axis;
a guide pin erected on the other side of the rotary mold and the operation member and engaged with the spiral groove;
a drive unit that rotates the rotary mold by driving the operating member in the extending direction of the central axis to relatively move the guide pin along the spiral groove;
The mold rotating device according to claim 1. 3. The mold rotating device according to claim 2, wherein said rotation drive mechanism has a rotation preventing portion that prevents said operation member from rotating around said central axis. The anti-rotation part is
a planar portion formed on the outer peripheral surface of the cylindrical operating member arranged on the outer peripheral side of the rotary mold and extending in the extending direction of the central axis and in the width direction orthogonal to the extending direction;
a rotation preventing body extending in the width direction and in contact with the flat portion in the width direction throughout the movement of the operating member in the extending direction of the central axis;
The mold rotating device according to claim 3. 5. The method according to any one of claims 1 to 4, wherein the fixed mold and the movable mold each grip an end portion of the workpiece, and the movable mold rotates to perform a twisting operation on the workpiece. mold rotating device. a main drive source for reciprocating the movable mold along the central axis to perform forging work on the workpiece;
A mold rotating device according to any one of claims 1 to 4, which rotates the rotating mold during at least one of forward movement and backward movement of the movable mold;
heading machine. The forging machine includes a kickout pin that is driven by the main drive source and ejects the workpiece from the fixed mold,
The rotation drive mechanism has a drive section different from the main drive source,
A heading machine according to claim 6 . The rotation drive mechanism rotates the fixed mold around the central axis when the movable mold moves back, thereby performing an attitude changing operation of changing the rotational attitude of the workpiece about the central axis. Heading machine according to claim 6 or 7, implemented in a die. 9. The movable mold according to any one of claims 6 to 8, wherein during the forward movement, the movable mold performs a posture change operation of changing an inclination posture of the workpiece with respect to the central axis instead of the forging operation. Forging machine. The forging according to claim 6, wherein the rotation drive mechanism causes the movable mold to perform a cutting operation instead of the forging operation by rotating the movable mold around the central axis during forward movement. machine. A multi-process forging machine having a plurality of forging processes including the fixed mold and the movable mold,
The forging machine according to any one of claims 6 to 10, wherein the die rotating device is provided for part or all of the forging process.

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