KR100668475B1 - Forming machine having transmission mechanisms for transmitting movements from a drive mechanism to a cutting mechanism, a conveying clamp mechanism and a feeding mechanism - Google Patents

Abstract

A molding machine with a power transfer device for transferring power from a driving device to a cutting device, a transfer clamp device, and a feeding device is provided to reduce vibration and prohibit parts from being broken even if increasing the rotary speed of the driving and driven gears. A molding machine is composed of a cutting device(52) cutting a feed material; a transfer clamp device(53) transferring the cut section of the feed material to the die assembly; feeding devices(4); a first power transfer device(51) connected with the cutting and transfer clamp devices; a driving device(61) driving the first power transfer device; and a second power transfer device(62) driven by the driving device. The second power transfer device contains driven wheels(622), a first swing member(63) facing the driven wheels, and an eccentric pin(623) slidingly connected with the first swing member. The first swing member is installed with a long swing plate(631) having a penetration hole(632). The swing plate has a pivot shaft(630) practically horizontal to shafts(620) of the driven wheels.

Description

FORMING MACHINE HAVING TRANSMISSION MECHANISMS FOR TRANSMITTING MOVEMENTS FROM A DRIVE MECHANISM TO A CUTTING MECHANISM, A CONVEYING CLAMP MECHANISM AND A FEEDING MECHANISM }

1 is an elevational view of a first preferred embodiment of the present invention.

FIG. 2 is similar to FIG. 1 but shows that the first swing plate is turned rearward.

3 is a plan view of the first preferred embodiment of the present invention.

4 is another plan view of the first preferred embodiment of the present invention.

Fig. 5 is a view showing the first swing plate and the drive gear of the first preferred embodiment of the present invention.

6 is an elevational view of a second preferred embodiment of the present invention.

The present invention relates to a molding machine, more preferably a molding machine for producing a forged product.

Molding machines for manufacturing forgings generally include a feeding mechanism for feeding a wire material to a cutting device for cutting into a wire section which is transferred to a die assembly via a transfer clamp mechanism. The molding machine further includes a driving mechanism for driving the cutting mechanism and the transfer clamp mechanism through the first power transmission mechanism and also for driving the feeding mechanism through the second power transmission mechanism.

The first power transmission mechanism includes a cam mechanism having a cam plate that acts on the cutting mechanism and the transfer clamp mechanism, respectively, to cause the cutting mechanism and the transfer clamp mechanism to intermittently execute their respective cutting and transmission operations. The second power transmission mechanism includes a driven gear driven by a drive gear of the drive mechanism, and a link connected to the drive gear and reciprocated. The feeding mechanism is driven by the link and intermittently advances the wire rod.

In the intermittent advance of the wire rod by the feeding mechanism, the cutting operation of the cutting mechanism and the transfer operation of the transfer clamp mechanism are alternately performed. In order to advance the wire rod intermittently, the link of the second power transmission mechanism is moved back and forth by the drive gear. When the drive gear is rotated 180 degrees, the link moves forward to operate the feed mechanism to advance the wire rod. As the feeding mechanism operates, the cutting mechanism and the transfer clamp mechanism temporarily stop respective cutting operations and transfer operations. When the drive gear is rotated 180 degrees again, the link moves backward, causing the feeding mechanism to temporarily stop the advancement of the wire rod. At this time, the cutting mechanism and the transfer clamp mechanism each perform a cutting operation and a transfer operation. Thus, the recovery ratio with respect to the advancement of the wire rod and the transfer of the cut and cut wire sections is 1: 1.

In order to increase the speed of such a molding machine, it has been attempted to increase the rotational speed of the drive gear and driven gear. However, this increase in rotational speed has resulted in increasing the reciprocating speed of the cam plate, thereby increasing the respective impact between the cam plate and the cutting mechanism and the transfer clamp mechanism. The increased impact forces create considerable vibrations in the molding machine, increasing the risk of damaging the components of the molding machine.

It is an object of the present invention to provide a molding machine having an improved power transfer mechanism for a feeding mechanism, a cutting mechanism, and a transfer clamp mechanism.

According to the present invention, a molding machine comprising a die assembly includes a cutting mechanism for cutting a feed material, a transfer clamp mechanism for transferring a cut section of the feed material from the cutting mechanism to the die assembly, the feed material A feeding mechanism for advancing the cutting mechanism to the cutting mechanism, a first power transmission mechanism connected to the cutting mechanism and the transfer clamp mechanism, a driving mechanism for driving the first power transmission mechanism, and the driving mechanism to drive the feeding mechanism. It includes a second power transmission mechanism driven by. A second power transmission mechanism is driven wheel driven by the drive mechanism, a first swing member connected to the feeding mechanism and facing the driven wheel, and protruding in the axial direction from the driven wheel and the first wheel. An eccentric pin slidably connected with the swing member. The eccentric pin is slid relative to the first swing member while being rotated with the driven wheel so that the first swing member is turned back and forth in cycle operation to complete one cycle for one rotation of the eccentric pin.

Other features and advantages of the present invention will become apparent from the following detailed description of preferred embodiments with reference to the accompanying drawings.

In describing the present invention in detail, the same reference numerals are given to the same members in advance.

Referring to FIG. 1, the first preferred embodiment of the present invention includes a housing 3 and a feeding mechanism 4 disposed in front of the housing 3. Inside the housing 3, a drive mechanism 61, a first power transmission mechanism 51, a cutting mechanism 52, a transfer clamp mechanism 53, and a second power transmission mechanism 62 are provided.

The housing 3 is mounted on the base 31 inside the housing 3 to support the base 31 extending in the front-rear direction of the housing 3, the molding machine (not shown) and the die assembly (not shown). A machine body 32 and a fixed pivot seat 33 mounted on the base 31 on the left side of the machine body 32.

The feeding mechanism 4 is provided to advance the feeding material (for example, wire rod) 30 in the front-rear direction. The feeding mechanism 4 includes two upper power transmission gears 411 that mesh with two lower power transmission gears 411, and a half moon drive gear 412 that meshes with two lower power transmission gears 411. . The upper and lower power transmission gears 411 are respectively coaxially connected to the four upper and lower feeding rollers (not shown) so that the feeding material 30 is sandwiched between these feeding rollers. The feed material 30 is advanced between the upper feed roller and the lower feed roller. The configurations of the base 31, the machine main body 32, and the feeding mechanism 4 are well known and will not be described in detail.

With reference to FIGS. 2 to 4, the cutting mechanism 52 for cutting the feed material 30 and the cut section of the feed material 30 are transferred and transferred to the next process station, ie a die assembly (not shown). A feed clamp mechanism 53 is provided. The cutting mechanism 52 is disposed below the feed clamp mechanism 53. The first power transmission mechanism 51 is mounted on the substantially vertical slide plate 511, the slide plate 511 and slidably mounted in the front-rear direction on the machine body 32, and faces the cutting mechanism 52. A cam mechanism having a first cam plate 512 and a second cam plate 516 mounted on the slide plate 511 on the first cam plate 512 and facing the transfer clamp mechanism 53. The first cam plate 512 and the second cam plate 516 are used to operate the cutting mechanism 52 and the transfer clamp mechanism 53, respectively.

The first cam plate 512 may include a first flat surface portion 513, a second flat surface portion 515, and a first inclined surface portion 514 between the first flat surface portion 513 and the second flat surface portion 515. Have The second cam plate 516 includes a concave portion forming the second inclined surface portion 517, and third and fourth flat surface portions 518 and 519 formed on both sides of the second inclined surface portion 517, respectively. . Since the structure of the 1st power transmission mechanism 51, the cutting mechanism 52, and the transfer clamp mechanism 53 is a well-known technique, the detailed description is abbreviate | omitted.

Referring to FIG. 5 in combination with FIGS. 1 and 2, the drive mechanism 61 includes a drive gear 611 driven by a power unit (not shown), and a crank 612 having a front end and a rear end. . The front end is connected to the vertical slide plate 511 of the first power transmission mechanism 51, and the rear end is pivoted eccentrically with the drive gear 611 so that the crank 612 is driven by the drive gear to move the slide plate 511. Reciprocate.

The second power transmission mechanism 62 is a driven wheel 621 engaged with the drive gear 611, a driven wheel in the form of a driven gear 622 engaged with the reverse gear 621, and an eccentric with the driven gear 622. It includes an eccentric pin 623 connected to, a first swing member 63 connected to the eccentric pin 623, and a reciprocating unit 64 connected to the first swing member 63.

The reciprocating unit 64 is a first connecting rod 641 connected to the first swing member 63, a length adjusting unit 642 movably mounted on the machine body 32 and connected to the first connecting rod 641, And a second connecting rod 644 connected to the length adjusting unit 642. The length adjustment unit 642 has an elongate adjustment hole 643. The connecting end of the second connecting rod 644 is slidably connected to the adjustment hole 643. The front end of the second connecting rod 644 is connected to the second swing member 413. The second swing member 413 is disposed coaxially with the half moon drive gear 412 for the synchronous movement. The position of the connecting end of the second connecting rod 644 near the adjustment hole 643 is determined by the total length of the reciprocating unit 64 (the total length of the first and second connecting rods 641 and 644 and the length adjusting unit 642). The length of the part). Similarly, the forward angle of the second swing member 413 may be changed for adjusting the length of the feed material 30 to be advanced by the feed mechanism 4.

When the lower end of the length adjusting unit 642 is turned backward by the first connecting rod 641, the semi-rolling drive gear 412 is rotated counterclockwise to connect with the power transmission gear 411 (not shown) Is rotated to advance the feed material (30).

The first swing member 63 includes an elongated swing plate having a lower end pivoted to the pivot sheet 33 so as to be turned about the pivot axis 635. The pivot shaft 635 is substantially parallel to the axis of the driven gear 622, and the swing plate 631 faces the driven gear 622. An elongated through hole 632 is formed in the swing plate 631, and a slide block 633 is mounted inside the through hole 632 to slide along the length of the through hole 632. The eccentric pin 623 of the driven gear 622 is pivotally connected to the slide block 633. The first connecting rod 641 is pivotally connected to the swing plate 631.

In operation, when the drive gear 611 of the drive mechanism 61 is rotated counterclockwise, the crank 612 moves forward of the slide plate 511 to cut the cutting mechanism 52 and the transfer clamp mechanism 53. To operate. At the same time, the reverse rotation gear 621 is rotated clockwise, and the driven gear 622 is rotated counterclockwise. In addition, the eccentric pin 623 rotates around the axis 620 of the driven gear 622 and moves the slide block 633. Therefore, the slide block 633 slides inside the through hole 632 of the swing plate 631. As the slide block 633 is moved, the swing plate 631 of the first swing member 63 is advanced to the first position shown in FIG. 4 and back to the second position shown in FIG. 5.

The first swing member 63 is redirected about the pivot shaft 630 disposed below the shaft 620 of the driven gear 622, and the position of the pivot shaft 630 of the first swing member 63 is adjusted. Because the swing member 63 is in front of the axis 620 of the driven gear 622 (ie, the pivot axis 630 is located in front of the vertical line rather than aligned with the axis 620 along the vertical line), the swing member 63 The forward angle θ1 of the eccentric pin 623 rotated counterclockwise to swing from the first position (FIG. 1) to the second position (FIG. 2) is less than 180 degrees. When the first swing member 63 is turned to the rear second position (FIG. 2), the first swing member 63 pulls the first connecting rod 641 backward so that the lower end of the adjustment member 42 is reversed. do. Accordingly, the second swing member 413 rotates the semi-lunar driven gear 412 of the feeding mechanism 4 counterclockwise, thereby operating the feeding mechanism 4 to advance the feeding material 30. At this time, the crank 612 of the drive mechanism 61 pulls the slide plate 511 backward so that the cutting mechanism 52 does not cut the feed material 30 and the feed clamp mechanism 53 feeds the feed material ( Do not transfer the cut section of 30).

When the first swing member 63 is turned from the second position to the second position, the eccentric pin 623 is rotated counterclockwise by an angle θ2 greater than 360 degrees by subtracting θ1 from 360 degrees. At this time, the feeding mechanism 4 does not advance the feeding material 30. However, the first power transmission mechanism 51 moves the slide plate 511 forward to operate the cutting mechanism 52 and the transfer clamp mechanism 53 to cut the feed material 30, respectively, and feed the feed material 30. To deliver the cut section of the die assembly (not shown).

As described above, when the eccentric pin 623 is rotated together with the driven gear 622, the first swing member 63 is swinged by the eccentric pin 623 so that the first swing member 63 is moved back and forth in a cycle operation. Moved to complete one cycle of operation of one rotation of the eccentric pin 623. The first swing member 63 performs the first stroke movement (moving from the first position of the first swing member 63 to the second position) and the second stroke movement (the first swing member 63) in one cycle operation. Move from the second position to the first position). The eccentric pin 623 rotates by the first angle θ1 with respect to the first stroke movement of the first swing member 63 and rotates by the second angle θ2 with respect to the second stroke movement. The first angle θ1 is smaller than the second angle θ2.

In this embodiment, θ1 is 140 degrees and θ2 is 220 degrees. Thus, the eccentric pin 623 of the driven gear 622 rotates counterclockwise by an angle of 140 degrees to operate the feed mechanism 4 to advance the feed material 30 once. Since the time taken to turn the eccentric pin 623 140 degrees is shorter than the time taken to turn 220 degrees, the time required for the feeding mechanism 4 to advance the feed material 30 is the advancement of the feed material 30. It is short compared to the time taken to stop the process. Thus, the time provided for the cutting mechanism 52 and the transfer clamp mechanism 53 to perform their respective cutting and transferring operations can be increased.

Referring again to FIGS. 2-4, the first and second cam plates 512, 516 of the first and second cam plates 512, 516 are extended because the time required to operate the cutting mechanism 52 and the transfer clamp mechanism 53 has been extended. The two inclined surface portions 514 and 517 can be increased in length to reduce the inclination angle, thereby reducing the pressure applied to the first and second cam plates 512 and 516 during the cam operation. Thus, even when increasing the speed of the drive gear 611 to increase the output of the molding machine, the vibration movement can be reduced.

6 shows a second preferred embodiment of the present invention. In the present embodiment, the feeding mechanism 4 'includes an upper meniscus driven gear 411' and a lower meniscus drive gear 412, which are interlocked with each other and each pair of feeding rollers (not shown). Each of them is coaxially connected so that the feed material 30 is sandwiched between these feed rollers so as to be advanced. When the lower menstrual drive gear 412 is rotated clockwise, the feed material 30 is advanced toward the cutting mechanism 52.

The direction of the meniscus drive gear 412 for advancing the feed material 30 in this embodiment is opposite to that of the drive gear 412 in the first embodiment. Further, the direction of the driven gear 622 'for driving the first swing member 63 is opposite to the direction of the driven gear 622 of the first embodiment. In this embodiment, no reverse gear is provided, and the driven gear 622 ′ directly engages with the drive gear 611. Therefore, when the drive gear 611 rotates counterclockwise, the driven gear 622 'rotates clockwise.

The first swing member 63 includes an elongated swing plate 631. The eccentric pin 623 of the driven gear 622 'is directly connected to the slide block 633 in the through hole 632 of the swing plate 631. The swing plate 631 has a lower end pivoted directly to the left side of the machine body 32. The length adjusting unit 642 is directly fixed to the front of the swing plate 631 so that the length adjusting unit 642 swings in synchronization with the swing plate 631.

Therefore, when the driven gear 622 'is driven by the drive gear 611 and rotates clockwise, the swing plate 631 is turned from the first position to the second position, and the half moon type drive gear 412 is counterclockwise. Direction so that the feeding mechanism 4 'will not advance the feeding material 30. As shown in FIG. At this time, the cutting mechanism 52 and the transfer clamp mechanism 53 are activated to perform each cutting operation and the transfer operation. When the driven gear 622 'continues to rotate, the swing plate 631 is turned from the second position to the first position, and the half moon drive gear 412 rotates clockwise to allow the feed material 30 to advance. . In this embodiment, the position of the pivot shaft 630 of the swing plate 631 is also located ahead of the shaft 620 'of the driven gear 622'.

According to the present invention, even if the rotational speed of the driving gear and the driven gear is increased, a molding machine having a power transmission mechanism that does not generate impact force and vibrations with respect to the feeding mechanism, the cutting mechanism, and the transfer clamp mechanism, thereby reducing the risk of component damage. Is provided.

Claims (6)

In a molding machine comprising a die assembly, Cutting mechanism 52 for cutting the feed material, A transfer clamp mechanism 53 for transferring the cut section of the feed material 30 from the cutting mechanism 52 to the die assembly, Feeding mechanisms 4, 4 'for advancing the feeding material to the cutting mechanism 52, A first power transmission mechanism 51 connected to the cutting mechanism 52 and the transfer clamp mechanism 53, A drive mechanism 61 for driving the first power transmission mechanism 51; and A second power transmission mechanism 62 driven by the drive mechanism 61 to drive the feeding mechanisms 4, 4 ′; Including, The second power transmission mechanism 62 is connected to driven wheels 622 and 622 'driven by the drive mechanism 61, the feeding mechanisms 4 and 4', and the driven wheels ( 622, 622 ′ facing the first swing member 63, and an eccentric pin protruding axially from the driven wheels 622, 622 ′ and slidably connected to the first swing member 63. pin) 623, The eccentric pin 623 is slid relative to the first swing member 63 while being rotated together with the driven wheels 622 and 622 'so that the first swing member 63 is moved back and forth in a cycle operation. One cycle for one rotation of the eccentric pin 623 is completed Molding machine. The method of claim 1, The first swing member 63 has an elongated swing plate 631 having an elongated through hole 632 facing the driven wheels 622, 622 ′, and the eccentric pin 623 is provided with the through hole ( 632, which is slidably connected, wherein the swing plate 631 has a pivot axis 630 substantially parallel to the axes 620, 620 ′ of the driven wheels 622, 622 ′. . The method of claim 2, The swing plate 631 further includes a slide block 633 slidably disposed in the through hole 632, and the eccentric pin 623 is connected to the slide block 633. . The method of claim 2, The driven wheels 622, 622 ′ are driven gears driven by the drive mechanism 61, and the second power transmission mechanism 62 is the first swing member 63 and the feeding mechanisms 4, 4. And a reciprocating unit (64) connected to the "). The method of claim 4, wherein The drive mechanism 61 is a drive gear 611 for driving the driven gears 622, 622 ′, and a crank 612 connected to the drive gear 611 and the first power transmission mechanism 51. Molding machine comprising a. The method of claim 4, wherein The first swing member 63 performs a first stroke movement and a second stroke movement for one cycle, and the eccentric pin 623 rotates by a first angle θ1 for the first stroke movement and the second stroke movement. And a first angle (θ1) is smaller than the second angle (θ2) for a stroke movement.

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