JP3151261U - Forging machine - Google Patents

Abstract

There is provided a forging machine capable of accurately operating a knockout pin means without being shifted from a crankshaft to a pin drive shaft of the knockout pin means in synchronism with advancing and retreating operation of a ram. A pin drive shaft 31 of a knockout pin means 30 is linked to a crankshaft 9 via a first parallel link rotation mechanism 40 and a second parallel link rotation mechanism 50. The first parallel link mechanism 40 includes an eccentric wheel 41 provided on the crankshaft 9, a crank 42 provided on the pin drive shaft 31, and a connecting body 43 that connects both links. The second parallel link rotation mechanism 50 has a drive gear 51 provided on the crankshaft 9, a driven gear provided on the pin drive shaft 31, and a transmission gear 53 that meshes with the drive gear 51 and an interlocking gear that meshes with the driven gear. The interlocking shaft having 55, the crankpin provided on the transmission gear 53, the crankpin provided on the interlocking gear 55, and a connecting body for connecting both the links. [Selection] Figure 1

Description

  The present invention relates to a forging machine in which a material is forged by a die and a punch that is disposed so as to face the die and moved back and forth to form a product having a predetermined shape.

  In general, a forging machine is configured such that a die placed at a predetermined position on a machine base, a punch disposed so as to face the die and moved forward and backward by a ram, and rotated by a drive motor to move the ram toward the die. It is known to have a crankshaft that moves forward and backward, and a knockout pin means that pushes a material driven into the die by a punch out of the die in synchronism with the forward and backward movement of the ram.

In that case, for example, Japanese Utility Model Publication No. 3-273 discloses drive means for moving the ram forward and backward and drive means for driving the pin drive shaft of the knockout pin means in synchronization with the forward and backward movement of the ram. The crankshaft rotated by the drive motor and moves the ram forward and backward toward the die, and the knockout pin means for pushing the material driven into the die by the punch to the outside in synchronization with the forward and backward movement of the ram The pin drive shaft is coupled to the crankshaft via a transmission mechanism including a vertical transmission shaft and a horizontal transmission shaft provided with a bevel gear. The rotation of the crankshaft causes the ram to move forward and backward toward the die block, and the pin drive shaft is rotationally driven via a transmission mechanism including a vertical transmission shaft and a horizontal transmission shaft provided with a bevel gear. By rotating, the knockout pin of the knockout pin means is moved back and forth in synchronism with the advancing / retreating operation of the ram.
Japanese Utility Model Publication No. 3-273

  However, according to the drive means from the conventional crankshaft to the pin drive shaft of the pin means for knockout, there are many transmission mechanisms in which the pin drive shaft is composed of a vertical transmission shaft or a horizontal transmission shaft with a bevel gear on the crankshaft. Therefore, a large transmission force cannot be transmitted from the crankshaft to the pin drive shaft without using a large bevel gear. Therefore, there is a problem in that the power transmission is deviated and the knockout pin means cannot be operated in a timely manner in synchronism with the forward / backward movement of the ram.

  Therefore, in the case of transmitting the power of the crankshaft to the pin drive shaft of the knockout pin means, the present invention knocks out accurately from the crankshaft to the pin drive shaft of the knockout pin means in synchronism with the forward and backward movement of the ram. An object of the present invention is to provide a forging machine capable of operating a pin means for use.

  In order to solve the above-described problem, the device according to claim 1 of the present application includes a die disposed at a predetermined position of the machine base, a punch disposed so as to face the die and moved forward and backward by a ram, A crankshaft that is rotated by a drive motor to move the ram forward and backward toward the die, and a knockout pin means that pushes the material driven into the die by the punch out of the die in synchronism with the forward and backward movement of the ram. A forging machine having a pin drive shaft of a knockout pin means coupled to a crankshaft via a first parallel link rotation mechanism and a second parallel link rotation mechanism. Is provided with a drive link provided on the crankshaft, a driven link provided on the pin drive shaft, and a connecting body for connecting both the links. A drive gear provided on the link shaft, a driven gear provided on the pin drive shaft, a transmission shaft having a transmission gear meshing with the drive gear, an interlocking shaft having an interlocking gear meshing with the driven gear, and a transmission gear. A driving link, a driven link provided in the interlocking gear, and a connecting body for connecting both the links, and one of the first and second parallel link rotating mechanisms. When the driving link and the driven link in the front are at the front dead center or the rear dead center, which is disadvantageous for transmitting the rotational force, the driving link and the driven link in the other parallel link type rotating mechanism are advantageous for transmitting the rotational force. The drive link and the driven link in the other parallel link type rotating mechanism are compared with the drive link and the driven link in one parallel link type rotary mechanism so as to be located between the dead center and the rear dead center. Link and is characterized by being provided with a predetermined phase difference with respect to the circumferential direction of the crank shaft or pin drive shaft.

  Further, in the invention according to claim 2 of the present application, the drive link of the first parallel link mechanism according to claim 1 is composed of an eccentric wheel fixed with a certain amount of eccentricity with respect to the crankshaft, One end is rotatably supported on the outer periphery of the eccentric ring via a bearing, and the other end is rotatably supported on the outer periphery of a driven link comprising a crank provided with a certain amount of eccentricity to the pin drive shaft. The driving link and the driven link of the two parallel link type rotation mechanism are composed of crank pins provided in the transmission gear and the interlocking gear with a certain amount of eccentricity with respect to the respective shaft cores, and both ends of the connecting body are connected to these crank pins. It is connected and supported so as to be freely rotatable.

  According to the present invention, the ram is moved back and forth toward the die by the rotation of the crankshaft by the rotation of the driving motor, and the material is driven into the die by the punch and forged. At the same time, the drive link of the first parallel link rotation mechanism provided on the crankshaft and the drive gear of the second parallel link rotation mechanism are rotated, and the first parallel link rotation mechanism is rotated by the rotation of the drive link. Further, the second parallel link rotation mechanism is rotated by the rotation of the drive gear, and the pin drive shaft of the knockout pin means is rotated. In that case, the rotational power of the crankshaft is transferred from the drive link of the first parallel link type rotation mechanism provided on the crankshaft to the connecting body, and from the connecting body to the driven link of the knockout pin means provided on the pin drive shaft. Each will be transmitted per surface. As a result, it is possible to suppress deviation in power transmission from the crankshaft to the pin drive shaft, and it is possible to accurately perform the push-out timing by the knockout pin in the knockout pin means of the material driven into the die. It becomes.

  In addition, when the first and second parallel link type rotating mechanisms are used, and the driving link and the driven link in one of the parallel link type rotating mechanisms are at the front dead center or the rear dead center position which is disadvantageous for transmitting the rotational force, The drive link and the driven link in one parallel link type rotation mechanism so that the drive link and the driven link in the other parallel link type rotation mechanism are located between the front dead center and the rear dead center which are advantageous for transmitting the rotational force. Since the drive link and the driven link in the other parallel link rotation mechanism are provided with a predetermined phase difference with respect to the circumferential direction of the crankshaft or the pin drive shaft with respect to the link, When the front dead center or rear dead center of the movement trajectory is exceeded, the other connected body must be positioned at an intermediate position between the front dead center or the rear dead center of the moving trajectory and the other connected body is pushed or pulled. Pi It can be transmitted reliably rotational torque to the drive shaft.

  In addition, the second parallel link rotation mechanism includes a drive gear provided on the crankshaft, a driven gear provided on the pin drive shaft, a transmission shaft having a transmission gear meshing with the drive gear, and an interlocking gear meshing with the driven gear. And a drive link provided in the transmission gear, a driven link provided in the linkage gear, and a connecting body for connecting both the links. Rotational torque can be reliably transmitted to the pin drive shaft via the coupling body, the interlocking gear, and the driven gear, and the rotational power is taken out from the interlocking gear arranged on the pin drive shaft side, for example, for chuck block driving Power can be effectively transmitted to the mechanism and the chuck opening / closing mechanism.

  In addition, the drive link of the first parallel link mechanism is composed of an eccentric wheel fixed with a certain amount of eccentricity with respect to the crankshaft, and one end of the connecting body is rotatably supported on the outer periphery of the eccentric wheel via a bearing. And the other end of the second parallel link type rotating mechanism is connected to the transmission gear while the other end is rotatably supported on the outer periphery of a driven link made of a crank provided with a fixed amount eccentric to the pin drive shaft. And the interlocking gears are made up of crankpins that are offset by a certain amount with respect to the respective shaft cores. This is preferable because the first and second parallel link mechanisms having an accurate and constant link (crank) length can be obtained.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 is a schematic plan view of a forging machine according to the present invention. A die block 3 is disposed at a predetermined position of a machine base 2 in the forging machine 1. A plurality of dies 4... 4 are arranged in parallel at regular intervals. Further, the same number of punches 6 ... 6 as the dies 4 ... 4 are held on the front surface of the ram 5 mounted on the machine base 2 in front of the die block 3 so as to face the dies 4 ... 4, respectively. At the same time, the rear end of the ram 5 is connected to the crankshaft 9 integrated with the flywheel 8 rotated by the driving motor 7 of the forging machine 1 via the connecting member 10, so that the ram 5 is connected to the die block 3. It is designed to move back and forth.

  Further, as shown in FIG. 1, on the side of the die block 3, a material supply quill (not shown) for supplying the wire A to the forging station constituted by the die 4 and the punch 6 is attached to the die 4. A cutting mechanism 11 having a cutter 11a for cutting the material A supplied from the material supply quill into a certain size is provided. Further, a material supply means 12 such as a feed roller that intermittently supplies a long material A made of a wire material toward the material supply quill at a rear position of the machine base 2 at a rear position of the material supply quill. Is arranged.

  On the other hand, on the inner peripheral surface of the front end of the support frame 16 supported by the support shaft 15 having the front end portion placed on the die block 3 and the rear end portion temporarily mounted on the machine base 2, the chuck block 17 It is supported so that it can reciprocate in the direction in which the dies 4. On the front surface of the chuck block 17, a plurality of material transfer chucks 18... 18, which are a pair of left and right, are attached in the same number as the dies 4 at the same intervals. Further, on the machine base 2, a chuck opening / closing shaft 20 is rotatably supported in front of the support shaft 15 in parallel with the support shaft 15, and each chuck 18... 18 is mounted on the chuck opening / closing shaft 20. Each of the chuck opening / closing cams 21... 21 is fixed, and a driven sprocket 22 driven by power from the pin drive shaft 31 described later is fixed at one end. Then, by rotation of the chuck opening / closing shaft 20, the material transfer chucks 18... 18 are opened / closed in synchronism with the advance / retreat operation of the ram 5 via the chuck opening / closing cam 21. Further, one side of the chuck block 17 is pivotally attached to one end of a chuck block driving lever 23 supported on the machine base 2 side, and the lever 23 is swung by power from a pin driving shaft 31 side described later. The swing member 24 is connected. Then, the chuck block drive lever 23 is reciprocated in the lateral direction as the swing member 24 swings, so that the chuck block 17, that is, the material transfer chucks 18... Thus, each die 4... 4 is moved to the front position and its lateral replacement position.

  Further, behind the die 4, a knockout pin means 30 having a pin drive shaft (KO camshaft) 31 with a cam 32... 32 for pushing out the material A driven by the punch 6 from within the die is disposed. ing. The knockout pin means 30 is configured such that the rotation of the pin drive shaft 31 causes the knockout pin drive levers 33... 33 to swing through the cams 32. 1) is moved back and forth in synchronism with the forward and backward movement of the punches 6... 6, the material A driven into the dies 4. It is supposed to be pinched. The knockout pin means 30 is known and will not be described in detail.

  In the present invention, as a power transmission mechanism from the crankshaft 9 of the forging machine 1 configured as described above to the pin drive shaft 31 of the pin means 30 for knockout, the first parallel link type rotary mechanism 40, the second They are interlocked and connected via a parallel link type rotation mechanism 50.

  Specifically, as shown in FIGS. 2 and 3, the first parallel link mechanism 40 includes a drive link (referred to as an eccentric ring) 41 composed of an eccentric ring fixed to the crankshaft 9 by a fixed amount a. , A driven link (hereinafter referred to as a crank) 42 provided eccentrically on the pin drive shaft 37 by a certain amount a and one end thereof are rotatably fitted and supported on the outer periphery of the eccentric ring 41 via a bearing, and the other end is cranked. A coupling body 43 is provided on the outer periphery of 42 so as to be freely rotatable via a bearing.

  The second parallel link rotation mechanism 50 includes a drive gear 51 provided on the crankshaft 9 inside the eccentric wheel 41, a driven gear 52 provided on the pin drive shaft 37 inside the crank 42, and a drive gear. 51, a transmission shaft 54 having a transmission gear 53 meshing with 51, an interlocking shaft 56 having an interlocking gear 55 meshing with the driven gear 52, and a crank pin (drive) that is provided in the transmission gear 53 so as to be eccentric by a certain amount a with respect to the axis (Link) 57, a crank pin (driven link) 58 provided on the interlocking gear 55 with a certain amount of eccentricity a with respect to its axis, and a connecting body 59 for connecting both the crank pins 57, 58. In that case, the transmission shaft 54 having the transmission gear 53 is disposed below the drive gear 51, and the interlocking shaft 56 having the interlocking gear 55 is disposed above the driven gear 52.

  Of these first and second parallel link rotating mechanisms 40, 50, for example, the eccentric wheel 41 and the crank 42 in one parallel link rotating mechanism 40, in other words, the connecting body 43 is disadvantageous for transmitting the rotational force. Drive link 57 and driven link 58 in the other parallel link type rotation mechanism 50, in other words, the front dead center and the rear death which are advantageous for the connecting body 59 to transmit the rotational force when in the position of the front dead center or the rear dead center. The crank pin 57 and the crank pin 58 in the other parallel link rotation mechanism are connected to the crankshaft 9 or the crank 42 in the other parallel link rotation mechanism 40 so as to be positioned between the points. A predetermined phase difference is provided with respect to the circumferential direction of the pin drive shaft 33.

  On the other hand, as shown in FIG. 5, a rotating shaft 62 having a rotating gear 61 that meshes with the interlocking gear 55 is provided above the interlocking shaft 56. The rotating shaft 62 includes swing cams 71 and 72 constituting a part of a chuck block swing mechanism 70 for swinging the swing member 24 of the chuck block 17 in synchronization with the advancing and retreating operation of the ram 5, A drive sprocket 81 constituting a part of the chain transmission mechanism 80 for rotating the driven sprocket 22 of the chuck opening / closing shaft 20 in synchronization with the forward / backward movement operation 5 is fixed.

  Further, as shown in FIG. 5, a crank pin 44 is provided on the outer surface of the eccentric ring 41, and the crank pin 44 and a sliding member 11 b constituting a part of the cutting mechanism 11 are connected by a connecting operation member 45. By rotating the eccentric ring 41, the sliding member 11b is reciprocated through the connection actuating member 45, and accordingly, the cutter 11a of the cutting mechanism 11 is reciprocated in the direction in which the dies are arranged side by side. .

  Further, as shown in FIG. 1, a chain transmission mechanism 13 is interposed between the pin drive shaft 31 and the material supply mechanism 12, and a feed roll (not shown) of the material supply mechanism 12 is driven by the rotational power of the pin drive shaft 31. It has come to be.

  Next, the operation of the forging machine configured as described above will be described.

  As shown in FIG. 1, the rotation of the drive motor 7 causes the crankshaft 9 to rotate via the flywheel 8, and thereby the ram 5 moves forward and backward from the crankshaft 9 via the connecting member 10 toward the die block 3. The material A from the punches 6... 6 is moved into the dies 4... 4 facing the punches 6.

  When the crankshaft 9 is rotated, the first parallel link rotation mechanism 40 composed of the eccentric ring 41, the crank 42 and the coupling body 43 is rotated by the eccentric ring 41 provided on the crankshaft 9, and the pin drive shaft 31. Will be rotated.

  At the same time, a drive gear 51 provided on the crankshaft 9 is used to provide a second parallel link type comprising a drive gear 51, a driven gear 52, a transmission gear 53, an interlocking gear 55, a crankpin 57, a crankpin 58, and a connecting body 59. The rotation mechanism 50 is rotated and the pin drive shaft 31 is rotated.

  In that case, it is possible to transmit the rotational power of the crankshaft 9 from the eccentric wheel 41 to the connecting body 43 and from the connecting body 43 to the crank 42 on a per-surface basis. It is possible to suppress the occurrence of deviation in power transmission to the vehicle. As a result, it is possible to accurately perform the push-out timing of the material A driven into the die by the knock-out pin by rotationally driving the pin drive shaft 31 constituting the knock-out pin means 30 at an accurate timing.

  Further, the first and second parallel link type rotating mechanisms 40 and 50 are used, and of these, for example, the eccentric point 41 and the crank 42 in the first parallel link type rotating mechanism 40 are disadvantageous to the front dead center or the rear which is disadvantageous for transmitting the rotational force. When in the dead center position, the first parallel link is such that the crank pins 57 and 58 in the second parallel link type rotating mechanism 50 are located between the front dead center and the rear dead center which are advantageous for transmitting the rotational force. With respect to the eccentric wheel 41 and the crank 42 in the rotary mechanism 40, the crank pins 57 and 58 in the second parallel link rotary mechanism have a predetermined phase difference with respect to the circumferential direction of the crankshaft 9 or the pin drive shaft 31. Therefore, when one connected body exceeds the front dead center or the rear dead center of the movement trajectory, the other connected body must be positioned at an intermediate position between the front dead center or the rear dead center of the movement trajectory. And this other connection It can convey the extrusion or reliably rotating torque to the pin drive shaft 31 by the tension.

  Further, in the above embodiment, the drive link in the first parallel link type rotating mechanism 40 is constituted by the eccentric ring 41 fixed to the crankshaft 9 by being decentered by a certain amount a, and one end of the coupling body 43. Is rotatably supported on the outer periphery of the eccentric ring 41 via a bearing, and the other end is rotatably supported on the outer periphery of a driven link comprising a crank 42 provided with a pin a eccentricity a by a certain amount a. On the other hand, the drive link and the driven link in the second parallel link type rotating mechanism 50 are composed of crank pins 57 and 58 provided on the transmission gear 53 and the interlocking gear 55 by being decentered by a certain amount with respect to the respective axes. Since both ends of the connecting body 59 are rotatably supported by the crank pins 57 and 58, the first and second parallel members having a highly accurate and constant link (crank) length a are provided. Link mechanism can be obtained.

  Further, with the rotation of the eccentric wheel 41, the rotational power is transmitted to the cutting mechanism 11 through the connection actuating member 45, and the material A is cut at a timing synchronized with the advance / retreat operation of the punches 6. On the other hand, along with the rotation of the interlocking shaft 56 positioned above the pin drive shaft 31, the rotational force is transmitted from the interlocking gear 55 to the rotating shaft 62 positioned further upward via the rotating gear 61. Thereby, the rotational power of the rotary shaft 62 is transmitted to the chuck block 17 via the chuck block swing mechanism 70, and the chuck opening / closing shaft 20 is rotated via the chain transmission mechanism 80, so that the punches 6. The material A pushed out from the dies 4... 4 at the timing synchronized with can be sandwiched between the material transfer chucks 18.

  The drive link and the driven link are a concept that is constrained by the crankshaft or the pin drive shaft, and moves circularly with the rotation of the crankshaft or the pin drive shaft, and is eccentric as described in the embodiment. It may be a ring or a crank, or may be a rod-shaped link rod.

  It is a schematic plan view of the forging machine of the present invention.   It is a side view which shows a 1st, 2nd parallel link type rotation mechanism.   It is plane explanatory drawing which showed the connection relationship of the both rotation mechanisms easily.   It is a side view which shows the operation state of a 1st, 2nd parallel link type rotation mechanism.   It is a side view which shows the combined state of a 1st, 2nd parallel link type | formula rotation mechanism and another mechanism.

DESCRIPTION OF SYMBOLS 1 Forging machine 2 Machine base 3 Die block 4 Die 5 Ram 6 Punch 7 Drive motor 9 Crank shaft 30 Knockout pin means 31 Pin drive shaft 3 Die block 40 First parallel link type rotation mechanism 41 Eccentric wheel (drive crank)
42 Crank (driven crank)
43 connecting body 50 first parallel link rotation mechanism 51 drive gear 52 driven gear 53 transmission gear 54 transmission shaft 55 interlocking gear 56 interlocking shaft 57 crank pin (driving crank)
58 Crankpin (driven crank)
59 Conjugate

Claims (2)

  A die disposed at a predetermined position on the machine base, a punch disposed so as to face the die and advanced and retracted by a ram, and a crankshaft rotated by a drive motor to advance and retract the ram toward the die A forging molding machine having knockout pin means for extruding a material driven into the die by punching out of the die in synchronism with advancing and retreating operation of the ram, and a pin drive shaft of the knockout pin means on the crankshaft Are coupled to each other via a first parallel link rotation mechanism and a second parallel link rotation mechanism, and the first parallel link mechanism is provided on a drive link provided on the crankshaft and on a pin drive shaft. The second parallel link rotation mechanism has a driven gear provided on the crankshaft and a driven provided on the pin drive shaft, while being provided with a driven link and a connecting body for connecting both the links. A transmission shaft having a transmission gear meshing with the drive gear, an interlocking shaft having an interlocking gear meshing with the driven gear, a drive link provided on the transmission gear, a driven link provided on the interlocking gear, and both of these links A front dead center having a connecting body to be connected and disadvantageous for the drive link and the driven link in one of the first and second parallel link rotation mechanisms to transmit the rotational force. Or, when in the rear dead center position, one of the parallel links is rotated so that the driving link and the driven link in the other parallel link type rotating mechanism are positioned between the front dead center and the rear dead center which are advantageous for transmitting the rotational force. The drive link and driven link in the link type rotating mechanism and the drive link and driven link in the other parallel link type rotating mechanism are predetermined in the circumferential direction of the crankshaft or pin drive shaft. Forging molding machine, characterized in that provided at a phase difference.   The drive link of the first parallel link mechanism is composed of an eccentric wheel fixed with a certain amount of eccentricity with respect to the crankshaft, and one end of the coupling body is rotatably supported on the outer periphery of the eccentric wheel via a bearing, While the other end is rotatably supported on the outer periphery of a driven link made of a crank provided with a certain amount of eccentricity to the pin drive shaft, the drive link and driven link of the second parallel link type rotating mechanism are connected to the transmission gear and interlocking 2. The crank pin is provided with a certain amount of eccentricity with respect to each axis of the gear, and both ends of a connecting body are rotatably supported by these crank pins. Forging machine.

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