JP4648253B2 - Forging press - Google Patents

Description

  The present invention relates to a forging press.

  As shown in FIG. 4, in the forging press, in order to realize high-speed forging while maintaining a large forging energy, in addition to the eccentric shaft E, a high-speed rotating shaft HS called a single-stage shaft is provided on the rear surface of the press. Yes. The high-speed rotation shaft HS is provided with a small-diameter flywheel FW that rotates at high speed at one end and a pinion gear P at the other end. The pinion gear P is meshed with a main gear G provided at one end of the eccentric shaft E, and the torque is transmitted to the eccentric shaft E.

However, in the forging press having the structure as described above, the rotation of the high-speed rotation shaft HS is decelerated by the pair of pinion gears P and the main gear G and transmitted to the eccentric shaft E. Then, when an appropriate reduction ratio of about 1: 5 is obtained between the high-speed rotation shaft HS and the eccentric shaft, the main gear G has to be enlarged in order to secure the tooth strength. Since the weight becomes very large, there is a problem that maintenance is very poor and it takes time to manufacture.
Further, the eccentric shaft E is provided with a brake B at the end opposite to the end where the main gear G is provided, but the weight of the main gear G is very large. The weight of the end portion on the main gear G side is much heavier than the weight of the end portion on the brake B side, and the weight balance of the eccentric shaft E is deteriorated. For this reason, the vibration, noise, etc. which generate | occur | produce at the time of forging become large, and the problem that the bush which supports the eccentric shaft E generates heat arises.
Moreover, since the high-speed rotating shaft HS is provided in addition to the eccentric shaft E, there is a problem that the press becomes large.

There exists a technique of patent document 1 as a technique which prevents the enlargement of a forging press.
As shown in FIG. 5, in the technique of Patent Document 1, a driving device 100 in which a motor M, a clutch C, a brake B, and a flywheel FW are integrated is attached to one end of an eccentric shaft E via a speed reducer D. Discloses a configuration for making a forging press compact.

However, in the case of the technique of Patent Document 1, a drive system that drives the eccentric shaft E is all provided at one end of the eccentric shaft E. For this reason, it is difficult to improve the problem that the weight balance of the eccentric shaft E deteriorates and the vibration generated during forging increases. And the problem that the space which installs a press becomes large arises.
Further, the driving device 100 includes the motor M, the clutch C, the brake B, and the flywheel FW, and the reduction gear D is provided between the driving device 100 and the eccentric shaft E. For this reason, even when only the motor M is maintained, disassembly of the clutch C or the like is necessary, and in order to maintain the reduction gear D, the drive device 100 must be removed, resulting in a problem of poor maintainability. .
Furthermore, since both the driving device 100 and the speed reducer D are attached to one end of the eccentric shaft E, the equipment for the next process must be installed outside the driving device 100 due to maintainability. Absent. For this reason, the conveyance apparatus from a forging press to the next process equipment becomes long, and since there is a drive apparatus on the conveyance apparatus, there arises a problem that installation of the conveyance apparatus is extremely restricted.

JP 61-276797

  In view of the above circumstances, an object of the present invention is to provide a forging press capable of reducing vibrations generated during forging and realizing downsizing of the press.

A forging press according to a first aspect of the present invention is a forging press provided with an eccentric shaft for operating a slide, wherein the eccentric shaft is a through-hole penetrating in the axial direction, and the central axis is in the eccentric shaft. A shaft arrangement hole formed so as to be coaxial with the center axis of both ends supported rotatably on the frame of the forging press is provided, and the axis arrangement hole of the eccentric shaft is rotated with respect to the eccentric shaft. A transmission shaft is provided that is freely disposed so as to be coaxial with the central axis of the shaft arrangement hole of the eccentric shaft, and the transmission shaft is connected to a driving means for rotating the transmission shaft at one end thereof. The other end is connected to a transmission means for transmitting the rotation of the transmission shaft to the eccentric shaft.
The forging press according to a second aspect of the present invention is the forging press according to the first aspect, wherein the drive means is provided at one end of the transmission shaft, and is provided with a clutch brake having a flywheel, and a drive source connected to the flywheel of the clutch brake. It is characterized by comprising.
The forging press according to a third aspect of the present invention is the forging press according to the first aspect, wherein the driving means includes a main gear provided at one end of the transmission shaft and a plurality of driving gears disposed around the main gear and meshing with the main gear. It is characterized by comprising a gear and a plurality of AC servo motors whose main shafts are connected to the plurality of drive gears.
A forging press of a fourth invention is characterized in that, in the first invention, the driving means is an AC servo motor, and the main axis of the AC servo motor is directly connected to one end of the transmission shaft.
The forging press according to a fifth aspect of the present invention is the forging press according to the first, second or third aspect, wherein the transmission means is a speed reducer that decelerates the rotation of the transmission shaft and transmits it to the eccentric shaft.

According to the first invention, since the transmission shaft is disposed in the eccentric shaft, it is possible to prevent the press from being enlarged due to the provision of the transmission shaft. And since the drive means and the transmission means are arranged separately at both ends of the transmission shaft, that is, both ends of the eccentric shaft, the weight balance is improved, vibrations generated during forging can be reduced, and problems such as vibration and noise Can be improved. Further, since the drive means and the transmission means exist independently, the maintainability of each means can be improved. Furthermore, since the length of the portion protruding from the press frame can be shortened at each end of the eccentric shaft, the degree of freedom in layout of press peripheral devices such as a transport device can be increased.
According to the second aspect of the invention, the clutch / brake and the flywheel can be separately installed from the speed reducer, so that the maintainability of the clutch / brake and the flywheel can be improved.
According to the third aspect of the invention, since the transmission shaft is driven by the AC servomotor, it is not necessary to provide a brake or a clutch, and the press can have a more compact configuration. In addition, since the reduction ratio from the AC servomotor to the transmission shaft can be increased, even a press that requires a large forging energy can be driven by a high-speed, low-torque AC servomotor. Since a driving force can be supplied to one main gear from a plurality of AC servomotors, a large torque can be generated on the transmission shaft even if the torque generated by one AC servomotor is small. Furthermore, if any one of the plurality of AC servomotors functions as a brake, the safety of the press can be increased.
According to the fourth invention, since the transmission shaft is driven by the AC servomotor, it is not necessary to provide a brake or a clutch, and the press can have a more compact configuration.
According to the fifth aspect of the invention, the driving force can be decelerated and transmitted from the transmission shaft to the eccentric shaft, so that a large torque can be generated for the eccentric shaft.

Next, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic front view of a forging press P of this embodiment. The forging press P of this embodiment is characterized by a drive mechanism that supplies a driving force to the eccentric shaft ES that operates the slide S. First, the overall structure of the forging press P of this embodiment is simplified. explain.

In FIG. 1, symbol B indicates a bed of the forging press P, and a lower die of the mold C is attached to the upper surface of the lower die holder DH provided on the upper surface of the bed B. The upper mold of the mold C is attached to the lower surface of the upper die holder DH provided on the lower surface of the slide S.
The slide S is connected to the eccentric portion H of the eccentric shaft ES via a connecting rod CR. The eccentric shaft ES has a journal portion J supported rotatably on the crown CW. The eccentric shaft ES is a so-called full eccentric crankshaft, and has a pair of journal portions J having a coaxial and coaxial diameter so as to sandwich the eccentric portion H. The eccentric shaft ES has a pair of journal portions J and J supported rotatably by a support portion SP of a crown CW made of a bush or the like, and a drive described later at one end portion (right end portion in FIG. 1). It is connected to the mechanism.
For this reason, when the eccentric shaft ES is rotated by the drive mechanism, the slide S moves up and down, and when the slide moves downward, the material is sandwiched between the upper and lower molds of the mold C and forged. It is.

Next, the drive mechanism that is a feature of the present invention will be described.
As shown in FIG. 1, the eccentric shaft ES is formed with a shaft arrangement hole h which is a through hole penetrating between the shaft ends. The shaft arrangement hole h passes through the pair of journal portions J and J and the eccentric portion H, and is formed so that the central axis thereof is coaxial with the pair of journal portions J and J of the eccentric shaft ES.
A transmission shaft 11 is disposed in the shaft arrangement hole h. The transmission shaft 11 has a shaft diameter slightly smaller than the inner diameter of the shaft arrangement hole h. The transmission shaft 11 has a central axis coaxial with the central axis of the shaft arrangement hole h, that is, a pair of journal portions of the eccentric shaft ES, by a case 20c of the transmission means 20 and a main body portion of the clutch brake 30 described later. It is coaxial with the central axis of J and J, and is held so as to be rotatable with respect to the eccentric shaft ES.

Further, the transmission shaft 11 is formed in such a length that both ends thereof protrude from both ends of the eccentric shaft ES in a state where the transmission shaft 11 is disposed in the shaft arrangement hole h of the eccentric shaft ES. One end (right end in FIG. 1) of the transmission shaft 11 is connected to a transmission means 20 which is a known planetary reduction gear.
As shown in FIG. 1, a sun gear 21 of the transmission means 20 is fixed to a portion protruding from the end of the eccentric shaft ES at the right end of the transmission shaft 11. A plurality of planetary gears 22 are engaged with the sun gear 21, and the plurality of planetary gears 22 are engaged with teeth provided on the inner surface of the case 20 c of the transmission means 20. The plurality of planetary gears 22 are attached to the rotating member 23 so that the central axes of the respective gears are all the same distance from the central axis of the transmission shaft 11. The rotating member 23 is rotatably supported on the transmission shaft 11 via a bearing or the like. The rotating member 23 is coupled to a driven member 24 fixed to the right end of the eccentric shaft ES by a gear coupling.

For this reason, when the transmission shaft 11 rotates, the plurality of planetary gears 22 revolve around the sun gear 21 while rotating, so that the rotating member 23 rotates around the central axis of the transmission shaft 11. Then, since the rotating member 23 and the driven member 24 are rotated in a state where they are coupled by the gear coupling, the eccentric shaft ES rotates around the central axis together with the driven member 24.
If the number of teeth of the sun gear 21 and the planetary gear 22 is adjusted, the rotational speed of the eccentric shaft ES can be reduced to a predetermined ratio with respect to the rotational speed of the transmission shaft 11, so that it is larger than the eccentric shaft ES. Torque can be generated.

As shown in FIG. 1, a clutch brake 30 having a fly hole 31 is attached to a portion protruding from the eccentric shaft ES at the left end of the transmission shaft 11. The clutch brake 30 has a main body portion fixed to the crown CW, and is configured such that the flywheel 31 and the transmission shaft 11 are connected when the clutch is turned on. The flywheel 31 of the clutch brake 30 is connected to a main shaft of a main motor 35 serving as a power source via a V belt 32.
For this reason, if the clutch is turned on while the main motor 35 is operated, the drive of the main motor 35 can be supplied to the transmission shaft 11 via the flyhole 31.
The clutch brake 30, the V-belt 32, and the main motor 35 provided with the flyhole 31 are driving means referred to in the claims.

As described above, the forging press P of the present embodiment is provided with the transmission shaft 11 that transmits the driving force generated by the driving means to the eccentric shaft ES via the transmission means 20. 11 is disposed in the eccentric shaft ES. For this reason, since it is not necessary to provide the special space for arrange | positioning the transmission shaft 11 in the forge press P, the enlargement of the press by providing the transmission shaft 11 can be prevented.
In addition, since the clutch brake 30 and the transmission means 20 are arranged separately at both ends of the transmission shaft 11, that is, at both ends of the eccentric shaft ES, the difference in weight between the ends of the eccentric shaft ES can be reduced. Therefore, the weight balance of the eccentric shaft ES is improved, vibration and noise generated during forging can be reduced, and problems such as heat generation in the support portion SP of the crown CW due to weight unbalance can be improved.

Moreover, since the clutch brake 30 and the transmission means 20 exist independently, only the clutch brake 30 or only the transmission means 20 can be disassembled. As a result, only the clutch brake 30 or only the transmission means 20 can be maintained, so that maintainability can be improved.
Furthermore, only one of the clutch brake 30 and the transmission means 20 is provided at each end of the eccentric shaft ES. For this reason, compared with the case where both the clutch brake 30 and the transmission means 20 are provided at one end of the eccentric shaft ES, the length of the portion protruding from the crown CW of the forging press P is shortened. Then, since the distance from a conveying apparatus, entrance / exit side installation, etc. arrange | positioned in the vicinity of the forge press P to a forge press can be shortened, the freedom degree of the layout of press peripheral equipment can be made high.

Further, since only one of the clutch brake 30 and the transmission means 20 is provided at each end of the eccentric shaft ES, the structure of the member provided at each end of the eccentric shaft ES can be adjusted. It is also possible to make the weights at both ends of the eccentric shaft ES substantially the same. Then, since the weight balance in the axial direction of the eccentric shaft ES is improved, vibration and noise generated during forging can be reduced.
Moreover, both ends of the eccentric shaft ES are lifted by balancer cylinders or the like so that the gap between the journal portion J and the support portion SP of the crown CW becomes small. If the weights at both ends are substantially the same, the driven system including the eccentric shaft ES can be lifted by the same balancer. Then, since the surface pressure difference of each part by lifting can be made small, the clearance gap between the journal part J of the eccentric shaft ES and the support part SP of crown CW can be brought close to 0 efficiently.

Further, in the forging press P of the present embodiment, the driving means for supplying the driving force to the transmission shaft 11 is not limited to the configuration as described above, and may be configured as follows.
In FIG. 2, the code | symbol 35B has shown the AC servomotor. The main body of the AC servo motor 35B is fixed to the crown CW so that the central axis of the main shaft is coaxial with the central axis of the transmission shaft 11. The main shaft of the AC servo motor 35B is directly connected to the transmission shaft 11.
For this reason, since the rotation of the transmission shaft 11 can be controlled only by stopping the rotation of the AC servo motor 35B, there is no need to provide a brake or a clutch, and the press can be made more compact.

As shown in FIG. 3, a main gear 41 is fixed to the left end of the transmission shaft 11, a plurality of drive gears 42 that mesh with the main gear 41 are provided, and each drive gear 42 is fixed to the crown CW by a frame or the like. Alternatively, each of the plurality of AC servomotors 35C may be fixed to the main shaft.
Then, since the driving force is transmitted from the small-diameter driving gear 42 to the large-diameter main gear 41, the rotational speed of the AC servomotor 35C can be decelerated and transmitted to the transmission shaft 11. Moreover, since the reduction ratio can be increased by adjusting the diameters of the drive gear 42 and the main gear 41, even a press that requires large forging energy can be driven by a high-speed, low-torque AC servomotor 35C. Can do. In addition, since the high-speed and low-torque AC servomotor 35C is smaller than the low-speed and high-torque AC servomotor, the degree of freedom of arrangement of the AC servomotor 35C is increased, and the driving means can be downsized.
If one of the plurality of AC servomotors 35C functions as a brake, the safety of the press can be increased.

Needless to say, the plurality of AC servomotors 35C are arranged such that the central axis of the main shaft is the same distance from the central axis of the transmission shaft 11.
Furthermore, if an intermediate gear is provided between the drive gear 42 and the main gear 41, the reduction ratio can be further increased. Then, even if the AC servo motor 35C having a high speed and a low torque is used, it is possible to generate a larger torque, so that it can be adopted for a press that requires a larger forging energy. Specifically, if a pinion fixed to the main shaft of the AC servomotor 35C and an intermediate gear meshing with the pinion are provided, and a rotation shaft connected to the intermediate gear and the drive gear 42 is provided, the AC servomotor 35C The rotation can be further decelerated and transmitted to the main gear 41.

  Further, since driving force can be supplied from one or more AC servomotors 35C to one main gear 41, even if the torque generated by one AC servomotor 35C is small, a large torque can be generated in the transmission shaft 11. Is possible. Since the torque generated in the eccentric shaft E can be adjusted only by adjusting the number of AC servo motors 35C, the press can be used for various purposes.

  When the press is versatile, the load applied to the AC servomotor 35C can be made substantially constant regardless of the product to be forged by controlling the rotational speed of the AC servomotor 35C. For example, when forging a small object with a small load and low forging energy, the rotational speed of the AC servo motor 35C is set to a high speed. When a large object with a large load and large forging energy is forged, the rotation of the AC servo motor 35C is performed. If the number is low, the load applied to the AC servomotor 35C can be made substantially constant.

  The forging press according to the present invention is a forging press provided with a crankshaft such as an eccentric shaft for operating a slide, and is suitable for forging parts for automobiles and parts for construction machinery.

It is a schematic explanatory drawing of the forge press P of this embodiment. It is a schematic explanatory drawing of the forge press P of other embodiment. It is a schematic explanatory drawing of the forge press P of other embodiment. It is a principal part schematic explanatory drawing of the conventional forge press. It is a principal part schematic explanatory drawing of the conventional forge press.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Transmission shaft 20 Transmission means 35 AC servomotor 41 Main gear 42 Drive gear 20 Control part P Forging press ES Exchen shaft h Shaft arrangement hole

Claims (5)

A forging press equipped with an eccentric shaft for operating a slide,
The eccentric shaft is
A shaft arrangement hole which is a through-hole penetrating in the axial direction and formed so that its central axis is coaxial with the central axis of both ends of the eccentric shaft that are rotatably supported by the frame of the forging press With
A transmission shaft is provided in the shaft arrangement hole of the eccentric shaft so as to be rotatable with respect to the eccentric shaft and coaxial with the central axis of the shaft arrangement hole of the eccentric shaft,
The transmission shaft is
A driving means for rotating the transmission shaft is connected to one end thereof,
A forging press, characterized in that a transmission means for transmitting the rotation of the transmission shaft to the eccentric shaft is connected to the other end.   The drive means
A clutch brake having a flywheel provided at one end of the transmission shaft;
A drive source coupled to the flywheel of the clutch brake
The forging press according to claim 1. The drive means
A main gear provided at one end of the transmission shaft;
A plurality of drive gears arranged around the main gear and meshing with the main gear;
The forging press according to claim 1, comprising a plurality of AC servo motors having main shafts coupled to the plurality of drive gears. The drive means is an AC servo motor;
The forging press according to claim 1, wherein the main axis of the AC servomotor is directly connected to one end of the transmission shaft. Said transmission means, the forging press of claim 1, 2, 3 or 4, wherein the decelerating rotation of the transmission shaft is a reduction gear for transmitting the eccentric shaft.

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