Title of Invention	FORMING MACHINE HAVING IMPROVED TRANSMISSION MECHANISMS
Abstract	A forming machine for forging which provides with a die assembly comprising: a cutting mechanism (52) adapted to cut a feed material; a conveying clamp mechanism (53) adapted to deliver a cut section of the feed material (30) from said cutting mechanism (52) to the die assembly;a feeding mechanism (4,4') adapted to advance the feed material to saidcutting mechanism (52);a first transmission mechanism (51) connected to said cutting mechanism (52) and said conveying clamp mechanism; - a drive mechanism (61) driving said first transmission mechanism (51) and - a second transmission mechanism (62) driven by said drive mechanism (61) for driving said feeding mechanism (4,4'), said second transmission mechanism (62) including a driven wheel (622,622') driven by said drive mechanism (61), an elongated swing plate connected to said feeding mechanism (4,40 confronting said driven wheel (622,622') and having an elongated through hole , and an eccentric pin (623) projecting axially from said driven wheel (622,622') and connected slidably to said elongated through hole in said swing plate, said swing plate having a pivot axis which is substantially parallel to an axis of said driven wheel, said eccentric pin sliding relative to said swing plate while rotating along with said driven wheel (622,622') so that said swing plate (63) is turned to and fro in a cycle motion and complete one cycle for each revolution of said eccentric pin (623), wherein said swing plate executes a first stroke movement and a second stroke movement in one cycle, said eccentric pin rotating by a first angle for said first stroke movement and a second angle for said second stroke movement, said first angle being smaller than said second angle, and wherein said driven wheel is a driven gear which is driven by said drive mechanism, said second transmission mechanism further including a reciprocating unit connected to said swing plate and said feeding mechanism.

Title of Invention

FORMING MACHINE HAVING IMPROVED TRANSMISSION MECHANISMS

Abstract

A forming machine for forging which provides with a die assembly comprising: a cutting mechanism (52) adapted to cut a feed material; a conveying clamp mechanism (53) adapted to deliver a cut section of the feed material (30) from said cutting mechanism (52) to the die assembly;a feeding mechanism (4,4') adapted to advance the feed material to saidcutting mechanism (52);a first transmission mechanism (51) connected to said cutting mechanism (52) and said conveying clamp mechanism; - a drive mechanism (61) driving said first transmission mechanism (51) and - a second transmission mechanism (62) driven by said drive mechanism (61) for driving said feeding mechanism (4,4'), said second transmission mechanism (62) including a driven wheel (622,622') driven by said drive mechanism (61), an elongated swing plate connected to said feeding mechanism (4,40 confronting said driven wheel (622,622') and having an elongated through hole , and an eccentric pin (623) projecting axially from said driven wheel (622,622') and connected slidably to said elongated through hole in said swing plate, said swing plate having a pivot axis which is substantially parallel to an axis of said driven wheel, said eccentric pin sliding relative to said swing plate while rotating along with said driven wheel (622,622') so that said swing plate (63) is turned to and fro in a cycle motion and complete one cycle for each revolution of said eccentric pin (623), wherein said swing plate executes a first stroke movement and a second stroke movement in one cycle, said eccentric pin rotating by a first angle for said first stroke movement and a second angle for said second stroke movement, said first angle being smaller than said second angle, and wherein said driven wheel is a driven gear which is driven by said drive mechanism, said second transmission mechanism further including a reciprocating unit connected to said swing plate and said feeding mechanism.

Full Text	FORMING MACHINE HAVING IMPROVED TRANSMISSION MECHANISMS This invention relates to a forming machine, more particularly to a forming machine for producing forged products. A forming machine for producing forged products typically includes a feeding mechanism for feeding a wire material to a cutting mechanism for cutting the wire material into wire sections which are delivered to a die assembly through a conveying clamp mechanism. The forming machine further includes a drive mechanism which drives the cutting mechanism and the conveying clamp mechanism through a first transmission mechanism and which also drives the feeding mechanism through a second transmission mechanism. The first transmission mechanism includes a cam mechanism which has cam plates to cam respectively the cutting mechanism and the conveying clamp mechanism so that the cutting mechanism and the conveying clamp mechanism are actuated intermittently to perform their respective cutting and delivering actions. The second transmission mechanism includes a driven gear driven by a drive gear of the drive mechanism, and a link connected to and reciprocated by the driven gear. The feeding mechanism is driven by the link and advances the wire material in an intermittent manner. The intermittent advancement of the wire material by the feeding mechanism are arranged to alternate with the cutting action of the cutting mechanism and the delivering action of the conveying clamp mechanism. To advance intermittently the wire material, the link of the second transmission mechanism is moved forward and backward by the driven gear. When the driven gear rotates by 180 degrees, the link moves forward to actuate the feeding mechanism so that the wire material is advanced. As the feeding mechanism is actuated, the cutting mechanism and the conveying clamp mechanism are temporarily stopped from proceeding with the cutting action and the forwarding action, respectively. When the driven gear rotates further by 180 degrees, the link moves backward so that the feeding mechanism temporarily stops advancing the wire material. At this time, the cutting mechanism and the conveying clamp mechanism perform the cutting and forwarding actions, respectively. Thus, the frequency ratio of the advancement of the wire material and the cutting and delivering of the cut wire sections is 1:1. In order to increase the speed of such a forming machine, attempts have been made by increasing the rotating speed of the drive gear and the driven gear. However, this increases the speedof the reciprocation of the cam plates, thereby resulting in increased impacts between each cam plate and one of the cutting mechanism and the conveying clamp mechanism. The increased impact forces tend to produce considerable vibrations in the forming machine, thereby increasing an incidence of damaging the machine components. An object of the present invention is to provide a forming machine with improved transmission mechanisms for a feeding mechanism, a cutting mechanism and a conveying clamp mechanism. According to this invention, a forming machine which includes a die assembly, comprises: a cutting mechanism adapted to cut a feed material; a conveying clamp mechanism adapted to deliver a cut section of the feed material from the cutting mechanism to the die assembly; a feeding mechanism adapted to advance the feed material to the cutting mechanism; a first transmission mechanism connected to the cutting mechanism and the conveying clamp mechanism; a drive mechanism driving the first transmission mechanism; and a second transmission mechanism driven by the drive mechanism for driving the feeding mechanism. The second transmission mechanism includes a driven wheel driven by the drive mechanism, a first swing member connected to the feeding mechanism and confronting the driven wheel, and an eccentric pin projecting axially from the driven wheel and connected slidably to the first swing member. The eccentric pin slides relative to the first swing member while rotating along with the driven wheel so that the first swing member is turned to and fro in a cycle motion and completes one cycle for each revolution of the eccentric pin. Other features and advantages of the present invention will become apparent in the following detailed description of the preferred embodiments of the invention, with reference to the accompanying drawings, in which: Fig. 1 is a fragmentary elevation view of the first preferred embodiment of the present invention; Fig. 2 is the same view as Fig. 1 but with a first swing plate being turned rearward; Fig. 3 is a fragmentary plan view of the first preferred embodiment; Fig . 4 is another fragmentary plan view of the first preferred embodiment; Fig. 5 is a fragmentary view showing the first swing plate and a driven gear of the first preferred embodiment; and Fig . 6 is a fragmentary elevation view of the second preferred embodiment of the invention. Before the present invention is described in greater detail, it should be noted that same reference numerals have been used to denote like elements throughout the specification. Referring to Figure 1, a first preferred embodiment of the present invention includes a housing 3, a feeding mechanism 4 disposed at the front of the housing 3. In the housing 3 are provided a drive mechanism 61, a first transmission mechanism 51, a cutting mechanism 52 , a conveying clamp mechatnism 53 , and a second transmission mechanism 62. The housing 3 includes a base 31 that extends in a front-to-rear direction of the housing 3 , a machine body 32 mounted on the base 31 inside the housing 3 for supporting a forging mechanism (not shown) and a die assembly ( not shown) , and a fixed pivot seat 33 mounted on the base 31 at the left side of the machine body 32. The feeding mechanism 4 is provided to advance a feed material (e.g. wire) 30 in a front-to-rear direction. The feeding mechanism 4 includes two upper transmission gears 411 intermeshed with two lower transmission gears 411 and a sector-shaped drive gear 412 intermeshed with the lower transmission gears 411. The upper and lower transmission gears 411 are connected coaxially and respectively to four upper and lower feed rollers (not shown) for pinching the feed material 30 therebetween. The wire material 3 0 is advanced between the upper and lower feed rollers (not shown) . Since the constructions of the base 31, the machine body 32, and the feeding mechanism 4 are known, they are not detailed hereinafter. Referring to Figures 2-4, the cutting mechanism 52 and the conveying clamp mechanism 53 are provided to cut the feed material 30 and to convey and deliver the cut sections of the feed material 30 to a next processing station, i.e. a die assembly (not shown). The cutting mechanism 52 is disposed at a level below the conveying clamp mechanism 53. The first transmission mechanism 51 is a cam mechanism which has a substantially vertical slide plate 511 that is mounted slidably on the machine body 32 in the front -to-rear direction, a first cam pi ate 512 mounted on the slide plate 511 and confronting the cutting mechanism 52, and a second cam plate 516 mounted on the slide plate 511 above the first cam plate 512 and confronting the conveying clamp mechanism 53. The first and second cam plates 512 and 516 are used to actuate the cutting mechanism 52 and the conveying clamp mechanism 53, respectively. The first camplate 512 has a first flat face section 513, a second flat face section 515, and a first inclined surface 514 between the first and second flat face sections 513 and 515. The second cam plate 516 includes an indented part defining a second inclined surface 517, and third and fourth flat face sections 518 , 519 formed respectively on two sides of the second inclined surfaces 517. Since the constructions of the first transmission mechanism 51, the cutting mechanism 52 and the conveying clamp mechanism 53 are known in the art, the details thereof are omitted herein for the sake of simplicity. Referring to Figure 5 in combination with Figures 1 and 2, the drive mechanism 61 includes a drive gear 611 driven by a power unit (not shown), and a crank 612 which includes a front end connected to the vertical slide plate 511 of the first transmission mechanism 51 and a rear end pivoted eccentrically to the drive gear 611 so that the crank 612 is driven by the drive gear 611 and reciprocates the slide plate 511 . The second transmission mechanism 62 includes a reverse gear 621 meshed with the drive gear 611, a driven wheel in the form of a driven gear 622 meshed with the reverse gear 621, an eccentric pin 623 eccentrically connected to the driven gear 622, afirst 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 includes a first connecting rod 641 connected to the first swing member 63, a length adjustment unit 642 mounted movably on the machine body 32 and connected to the first connecting rod 641, and a second connecting rod 644 connected to the length adjustment unit 642. The length adjustment unit 642 has an elongated adjustment hole 643 . A connecting end of the second connecting rod 644 is connected slidably to the adjustment hole 643. A front end of the second connecting rod 644 is connected to a second swing member 413 . The second swing member 413 is disposed coaxially with the sector-shaped drive wheel 412 for synchronous movement. The position of the connecting end of the second connecting rod 644 in the adjustment hole 643 may be changed to adjust the total length of the reciprocating unit 64 (the sum of the lengths of the first and second connecting rods 641, 644 plus the length of a portion of the length adjustment unit 642 ) . As such, the turning angle of the second swing member 413 may be changed to adjust the length of the feed material 30 to be advanced by the feeding mechanism 4 . When a lower end of the length adjustment 642 is turned rearward by the first connecting rod 641, the sector-shaped drive wheel 412 is rotated counterclockwise so that the feed rollers (not shown) connected to the transmission gears 411 rotate and advance the feed material 30. The first swing member 63 includes an elongated swing plate 631 with a bottom end which is pivoted to the pivot seat 33 to turn about a pivot axis 635. The pivot axis 635 is substantially parallel to the axis of the driven gear 623, and the swing plate 631 is confronting the driven gear 623. An elongated through hole 632 is formed in the swing plate 631, and a slide block 633 is mounted within the through hole 632 to slide along the length of the through hole 632. The eccentric pin 623 of the driven gear 622 is connected pivotally to the slide block 633. The first connecting rod 641 is connected pivotally to the swing plate 631. In operation, when the drive gear 611 of the first transmission mechanism 61 is rotated counterclockwise, the crank 612 moves the slide plate 511 forward so that the cutting mechanism 52 and the conveying clamp mechanism 53 are actuated. Simultaneously, the reverse gear 621 is moved clockwise, and the driven gear 622 is turned counterclockwise. Inaddition, the eccentric pin 623 rotates around the axis 620 of the driven gear 622 and moves the slide block 633. The slide block 633 is therefore slid within 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 turned forward to a first position as shown in Figure 4 and rearward to a second position as shown in Figure 5 . Since the first swing member 63 is turned about the pivot axis 630 arranged below the axis 620 of the driven gear 622 and since the position of the pivot axis 630 of the first swing member 63 is more forward than the axis 620 of the driven gear 622 (i.e. the pivot axis 630 is not aligned with the axis 620 along a vertical line and is located forwardly of the vertical line), the turning angle 91 of the eccentric pin 623 which rotates counterclockwise and rearward to swing the first swing member 63 from the first position (figure 1) to the second position (figure 2) is smaller than 180 degrees. When the first swing member 63 is turned rearward to the second position, as shown in Figure 2, the first swing member 63 pulls the first connecting rod 641 rearward so that the bottom end of the adjustment member 42 is moved rearward. The second swing member 413 therefore rotates the sector-shaped driven gear 412 of the feeding mechanism 4 counterclockwise, thereby actuating the feeding mechanism 4 to advance the feed material 30. At that time, the crank 612 of the first transmission mechanism 61 pulls the slide plate 511 rearward so that the cutting mechanism 52 does not cut the wire material 30, and the conveying clamp mechanism 53 does not deliver the cut sections of the feed material 30. When the first swing member 63 is turned from the second position to the first position, the eccentric pin 623 rotates counterclockwise by an angle 92 which is equal to 360 degrees - 61 and which is greater than 180 degrees. At this time, the feeding mechanism 4 does not advance the feed material 30. However, the first transmission mechanism 51 moves the slide plate 511 forward and actuates the cutting mechanism 52 and the conveying clamp mechanism 53 to cut the feed material 30 and to deliver the cut section of the feed material 30 to the die assembly (not shown), respectively. As mentioned above, when the eccentric pin 623 rotates along with the driven gear 622 , the first swing member 63 is swung by the eccentric pin 623 so that the first swing member 63 moves to and fro in a cycle motion and completes one cycle of the cycle motion for each revolution of the eccentric pin 623. The first swing member 63 executes a first stroke movement (from the first position to the second position of the first swing member 63) , and a second stroke movement (the second position to the first position) in one cycle of its cycle motion. The eccentric pin 623 rotates by a first angle 91 for the first stroke movement of the first swing member 63 and by a second angle 92 for the second stroke movement. The first angle 61 is smaller than the second angle 62. In this embodiment, 61 is equal to 140 degrees, whereas 92 is equal to 220 degrees. Thus, the eccentric pin 623 of the driven gear 622 rotates counterclockwise by an angle of 140 degrees to actuate the feeding mechanism 4 to advance the feed-material 30 one time. Since the time taken by the eccentric pin 623 to turn 140 degrees is less than that to turn 220 degrees, the time required by the feeding mechanism 4 to advance the feed material 30 is reduced, compared to the time taken in the course of stopping advancement of the feed material 30. Therefore, the time provided for the cutting mechanism 5 2 and the conveying clamp mechanism 53 to perform their respective cutting and delivering actions can be increased. Referring once again to Figures 2 to 4, since the time needed to activate the cutting mechanism 52 and the conveying clamp mechanism 53 has been prolonged, the first and second inclined surfaces 514, 517 of the first and second cam plates 512, 516 can be increased in length so that the slope angles thereof can be decreased, thereby reducing the pressure induced on the first and second cam plates 512, 516 during their camming actions. Therefore, when the drive gear 611 is speeded up in order to increase the production rate of the forming machine, vibration movements can be reduced. Referring to Figure 6, there is shown a second preferred embodiment of the present invention. In the second embodiment, the feeding mechanism 4' includes an upper sector-shaped driven gear 411' and a lower sector-shaped drive gear 412 which are interftieshed each other and which are connected coaxially and respectively to a pair of feed rollers (not shown) to pinch the feed material 30 therebetween for advancement. When the sector-shaped lower gear 412 rotates clockwise, the feedmaterial 30 is advanced to the cutting mechanism 52 . The direction of the sector-shaped drive gear 412 to advance the feed material 30 in this embodiment is opposite to that of the drive gear 412 in the first embodiment. Furthermore, the direct ion of the driven gear 622' to drive the first swing member 63 is opposite to that of the driven gear 622 in the first embodiment . No reverse gear is provided in this embodiment, and the driven gear 622 ' is meshed directly with the drive gear 611. Thus, 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 connected directly to the slide block 633 in the through hole 632 of the swing plate 631. The swing plate 631 has a bottom end pivoted directly to the left side of the machine body 32 . The length adjustment member 642 is fixed directly to a front side of the swing plate 631 so that the length adjustment member 642 is swung synchronously with the swing plate 631. Therefore, when the driven gear 622' is driven by the drive gear 611 to rotate clockwise, the swing plate 631 turns from the first position to the second position, and the sector-shaped drive gear 412 rotates counterclockwise so that the feed mechanism 4' does not advance the feed material 30. At this time, the cutting mechanism 52 and the conveying clamp mechanism 53 are activated to perform the respective cutting and delivering actions. When the driven gear 622' continues to rotate, the swing plate 631 is turned from the second position to the first position, and the sector-shaped drive gear 412 rotates clockwise so that the feed material 30 is advanced. This embodiment provides the same result as the previous embodiment. WE CLAIM 1. A forming machine for forging which provides with a die assembly comprising: - a cutting mechanism (52) adapted to cut a feed material; - a conveying clamp mechanism (53) adapted to deliver a cut section of the feed material (30) from said cutting mechanism (52) to the die assembly; - a feeding mechanism (4,4') adapted to advance the feed material to said cutting mechanism (52); - a first transmission mechanism (51) connected to said cutting mechanism (52) and said conveying clamp mechanism; - a drive mechanism (61) driving said first transmission mechanism (51) and - a second transmission mechanism (62) driven by said drive mechanism (61) for driving said feeding mechanism (4,4'), said second transmission mechanism (62) including a driven wheel (622,622') driven by said drive mechanism (61), an elongated swing plate connected to said feeding mechanism (4,4') confronting said driven wheel (622,622') and having an elongated through hole , and an eccentric pin (623) projecting axially from said driven wheel (622,622') and connected slidably to said elongated through hole in said swing plate, said swing plate having a pivot axis which is substantially parallel to an axis of said driven wheel, said eccentric pin sliding relative to said swing plate while rotating along with said driven wheel (622,622') so that said swing plate (63) is turned to and fro in a cycle motion and complete one cycle for each revolution of said eccentric pin (623). wherein said swing plate executes a first stroke movement and a second stroke movement in one cycle, said eccentric pin rotating by a first angle for said first stroke movement and a second angle for said second stroke movement, said first angle being smaller than said second angle, and wherein said driven wheel is a driven gear which is driven by said drive mechanism, said second transmission mechanism further including a reciprocating unit connected to said swing plate and said feeding mechanism. 2. The forming machine as claimed in claim 1 wherein said swing plate (631) further has a slide block (633) slidably disposed in said through hole (632), said eccentric pin (623) being connected to said slide block (633). 3. The forming machine as claimed in claim 1 wherein said drive mechanism (61) includes a drive gear (611) to drive said driven gear (622,6220, and a crank (612) connected to said driven gear (611) and said first transmission mechanism (51). A forming machine for forging which provides with a die assembly comprising: - a cutting mechanism (52) adapted to cut a feed material; - a conveying clamp mechanism (53) adapted to deliver a cut section of the feed material (30) from said cutting mechanism (52) to the die assembly; - a feeding mechanism (4,4') adapted to advance the feed material to said cutting mechanism (52); - a first transmission mechanism (51) connected to said cutting mechanism (52) and said conveying clamp mechanism; - a drive mechanism (61) driving said first transmission mechanism (51) and - a second transmission mechanism (62) driven by said drive mechanism (61) for driving said feeding mechanism (4,4'), said second transmission mechanism (62) including a driven wheel (622,622') driven by said drive mechanism (61), an elongated swing plate connected to said feeding mechanism (4,40 confronting said driven wheel (622,622') and having an elongated through hole , and an eccentric pin (623) projecting axially from said driven wheel (622,622') and connected slidably to said elongated through hole in said swing plate, said swing plate having a pivot axis which is substantially parallel to an axis of said driven wheel, said eccentric pin sliding relative to said swing plate while rotating along with said driven wheel (622,622') so that said swing plate (63) is turned to and fro in a cycle motion and complete one cycle for each revolution of said eccentric pin (623), wherein said swing plate executes a first stroke movement and a second stroke movement in one cycle, said eccentric pin rotating by a first angle for said first stroke movement and a second angle for said second stroke movement, said first angle being smaller than said second angle, and wherein said driven wheel is a driven gear which is driven by said drive mechanism, said second transmission mechanism further including a reciprocating unit connected to said swing plate and said feeding mechanism.

Full Text

FORMING MACHINE HAVING IMPROVED
TRANSMISSION MECHANISMS
This invention relates to a forming machine, more
particularly to a forming machine for producing forged
products.
A forming machine for producing forged products
typically includes a feeding mechanism for feeding
a wire material to a cutting mechanism for cutting
the wire material into wire sections which are
delivered to a die assembly through a conveying clamp
mechanism. The forming machine further includes a
drive mechanism which drives the cutting mechanism
and the conveying clamp mechanism through a first
transmission mechanism and which also drives the
feeding mechanism through a second transmission
mechanism.
The first transmission mechanism includes a cam
mechanism which has cam plates to cam respectively
the cutting mechanism and the conveying clamp
mechanism so that the cutting mechanism and the
conveying clamp mechanism are actuated
intermittently to perform their respective cutting
and delivering actions. The second transmission
mechanism includes a driven gear driven by a drive
gear of the drive mechanism, and a link connected to
and reciprocated by the driven gear. The feeding
mechanism is driven by the link and advances the wire
material in an intermittent manner.
The intermittent advancement of the wire material
by the feeding mechanism are arranged to alternate
with the cutting action of the cutting mechanism and
the delivering action of the conveying clamp mechanism.
To advance intermittently the wire material, the link
of the second transmission mechanism is moved forward
and backward by the driven gear. When the driven
gear rotates by 180 degrees, the link moves forward
to actuate the feeding mechanism so that the wire
material is advanced. As the feeding mechanism is
actuated, the cutting mechanism and the conveying
clamp mechanism are temporarily stopped from
proceeding with the cutting action and the forwarding
action, respectively. When the driven gear rotates
further by 180 degrees, the link moves backward so
that the feeding mechanism temporarily stops
advancing the wire material. At this time, the
cutting mechanism and the conveying clamp mechanism
perform the cutting and forwarding actions,
respectively. Thus, the frequency ratio of the
advancement of the wire material and the cutting and
delivering of the cut wire sections is 1:1.
In order to increase the speed of such a forming
machine, attempts have been made by increasing the
rotating speed of the drive gear and the driven gear.
However, this increases the speedof the reciprocation
of the cam plates, thereby resulting in increased
impacts between each cam plate and one of the cutting
mechanism and the conveying clamp mechanism. The
increased impact forces tend to produce considerable
vibrations in the forming machine, thereby increasing
an incidence of damaging the machine components.
An object of the present invention is to provide
a forming machine with improved transmission
mechanisms for a feeding mechanism, a cutting
mechanism and a conveying clamp mechanism.
According to this invention, a forming machine
which includes a die assembly, comprises: a cutting
mechanism adapted to cut a feed material; a conveying
clamp mechanism adapted to deliver a cut section of
the feed material from the cutting mechanism to the
die assembly; a feeding mechanism adapted to advance
the feed material to the cutting mechanism; a first
transmission mechanism connected to the cutting
mechanism and the conveying clamp mechanism; a
drive mechanism driving the first transmission
mechanism; and a second transmission mechanism driven
by the drive mechanism for driving the feeding
mechanism. The second transmission mechanism
includes a driven wheel driven by the drive mechanism,
a first swing member connected to the feeding mechanism
and confronting the driven wheel, and an eccentric
pin projecting axially from the driven wheel and
connected slidably to the first swing member. The
eccentric pin slides relative to the first swing member
while rotating along with the driven wheel so that
the first swing member is turned to and fro in a cycle
motion and completes one cycle for each revolution
of the eccentric pin.
Other features and advantages of the present
invention will become apparent in the following
detailed description of the preferred embodiments of
the invention, with reference to the accompanying
drawings, in which:
Fig. 1 is a fragmentary elevation view of the first
preferred embodiment of the present invention;
Fig. 2 is the same view as Fig. 1 but with a first
swing plate being turned rearward;
Fig. 3 is a fragmentary plan view of the first
preferred embodiment;
Fig . 4 is another fragmentary plan view of the first
preferred embodiment;
Fig. 5 is a fragmentary view showing the first swing
plate and a driven gear of the first preferred
embodiment; and
Fig . 6 is a fragmentary elevation view of the second
preferred embodiment of the invention.
Before the present invention is described in
greater detail, it should be noted that same reference
numerals have been used to denote like elements
throughout the specification.
Referring to Figure 1, a first preferred embodiment
of the present invention includes a housing 3, a
feeding mechanism 4 disposed at the front of the
housing 3. In the housing 3 are provided a drive
mechanism 61, a first transmission mechanism 51, a
cutting mechanism 52 , a conveying clamp mechatnism 53 ,
and a second transmission mechanism 62.
The housing 3 includes a base 31 that extends in
a front-to-rear direction of the housing 3 , a machine
body 32 mounted on the base 31 inside the housing 3
for supporting a forging mechanism (not shown) and
a die assembly ( not shown) , and a fixed pivot seat
33 mounted on the base 31 at the left side of the machine
body 32.
The feeding mechanism 4 is provided to advance a
feed material (e.g. wire) 30 in a front-to-rear
direction. The feeding mechanism 4 includes two
upper transmission gears 411 intermeshed with two
lower transmission gears 411 and a sector-shaped drive
gear 412 intermeshed with the lower transmission gears
411. The upper and lower transmission gears 411 are
connected coaxially and respectively to four upper
and lower feed rollers (not shown) for pinching the
feed material 30 therebetween. The wire material
3 0 is advanced between the upper and lower feed rollers
(not shown) . Since the constructions of the base 31,
the machine body 32, and the feeding mechanism 4 are
known, they are not detailed hereinafter.
Referring to Figures 2-4, the cutting mechanism
52 and the conveying clamp mechanism 53 are provided
to cut the feed material 30 and to convey and deliver
the cut sections of the feed material 30 to a next
processing station, i.e. a die assembly (not shown).
The cutting mechanism 52 is disposed at a level below
the conveying clamp mechanism 53. The first
transmission mechanism 51 is a cam mechanism which
has a substantially vertical slide plate 511 that is
mounted slidably on the machine body 32 in the
front -to-rear direction, a first cam pi ate 512 mounted
on the slide plate 511 and confronting the cutting
mechanism 52, and a second cam plate 516 mounted on
the slide plate 511 above the first cam plate 512 and
confronting the conveying clamp mechanism 53. The
first and second cam plates 512 and 516 are used to
actuate the cutting mechanism 52 and the conveying
clamp mechanism 53, respectively.
The first camplate 512 has a first flat face section
513, a second flat face section 515, and a first
inclined surface 514 between the first and second flat
face sections 513 and 515. The second cam plate 516
includes an indented part defining a second inclined
surface 517, and third and fourth flat face sections
518 , 519 formed respectively on two sides of the second
inclined surfaces 517. Since the constructions of
the first transmission mechanism 51, the cutting
mechanism 52 and the conveying clamp mechanism 53 are
known in the art, the details thereof are omitted
herein for the sake of simplicity.
Referring to Figure 5 in combination with Figures
1 and 2, the drive mechanism 61 includes a drive gear
611 driven by a power unit (not shown), and a crank
612 which includes a front end connected to the
vertical slide plate 511 of the first transmission
mechanism 51 and a rear end pivoted eccentrically to
the drive gear 611 so that the crank 612 is driven
by the drive gear 611 and reciprocates the slide plate
511 .
The second transmission mechanism 62 includes a
reverse gear 621 meshed with the drive gear 611, a
driven wheel in the form of a driven gear 622 meshed
with the reverse gear 621, an eccentric pin 623
eccentrically connected to the driven gear 622, afirst
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 includes a first
connecting rod 641 connected to the first swing member
63, a length adjustment unit 642 mounted movably on
the machine body 32 and connected to the first
connecting rod 641, and a second connecting rod 644
connected to the length adjustment unit 642. The
length adjustment unit 642 has an elongated adjustment
hole 643 . A connecting end of the second connecting
rod 644 is connected slidably to the adjustment hole
643. A front end of the second connecting rod 644
is connected to a second swing member 413 . The second
swing member 413 is disposed coaxially with the
sector-shaped drive wheel 412 for synchronous
movement. The position of the connecting end of the
second connecting rod 644 in the adjustment hole 643
may be changed to adjust the total length of the
reciprocating unit 64 (the sum of the lengths of the
first and second connecting rods 641, 644 plus the
length of a portion of the length adjustment unit 642 ) .
As such, the turning angle of the second swing member
413 may be changed to adjust the length of the feed
material 30 to be advanced by the feeding mechanism
4 .
When a lower end of the length adjustment 642 is
turned rearward by the first connecting rod 641, the
sector-shaped drive wheel 412 is rotated
counterclockwise so that the feed rollers (not shown)
connected to the transmission gears 411 rotate and
advance the feed material 30.
The first swing member 63 includes an elongated
swing plate 631 with a bottom end which is pivoted
to the pivot seat 33 to turn about a pivot axis 635.
The pivot axis 635 is substantially parallel to the
axis of the driven gear 623, and the swing plate 631
is confronting the driven gear 623. An elongated
through hole 632 is formed in the swing plate 631,
and a slide block 633 is mounted within the through
hole 632 to slide along the length of the through hole
632. The eccentric pin 623 of the driven gear 622
is connected pivotally to the slide block 633. The
first connecting rod 641 is connected pivotally to
the swing plate 631.
In operation, when the drive gear 611 of the first
transmission mechanism 61 is rotated
counterclockwise, the crank 612 moves the slide plate
511 forward so that the cutting mechanism 52 and the
conveying clamp mechanism 53 are actuated.
Simultaneously, the reverse gear 621 is moved
clockwise, and the driven gear 622 is turned
counterclockwise. Inaddition, the eccentric pin 623
rotates around the axis 620 of the driven gear 622
and moves the slide block 633. The slide block 633
is therefore slid within 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
turned forward to a first position as shown in Figure
4 and rearward to a second position as shown in Figure
5 .
Since the first swing member 63 is turned about
the pivot axis 630 arranged below the axis 620 of the
driven gear 622 and since the position of the pivot
axis 630 of the first swing member 63 is more forward
than the axis 620 of the driven gear 622 (i.e. the
pivot axis 630 is not aligned with the axis 620 along
a vertical line and is located forwardly of the
vertical line), the turning angle 91 of the eccentric
pin 623 which rotates counterclockwise and rearward
to swing the first swing member 63 from the first
position (figure 1) to the second position (figure
2) is smaller than 180 degrees. When the first swing
member 63 is turned rearward to the second position,
as shown in Figure 2, the first swing member 63 pulls
the first connecting rod 641 rearward so that the
bottom end of the adjustment member 42 is moved
rearward. The second swing member 413 therefore
rotates the sector-shaped driven gear 412 of the
feeding mechanism 4 counterclockwise, thereby
actuating the feeding mechanism 4 to advance the feed
material 30. At that time, the crank 612 of the first
transmission mechanism 61 pulls the slide plate 511
rearward so that the cutting mechanism 52 does not
cut the wire material 30, and the conveying clamp
mechanism 53 does not deliver the cut sections of the
feed material 30.
When the first swing member 63 is turned from the
second position to the first position, the eccentric
pin 623 rotates counterclockwise by an angle 92 which
is equal to 360 degrees - 61 and which is greater than
180 degrees. At this time, the feeding mechanism 4
does not advance the feed material 30. However, the
first transmission mechanism 51 moves the slide plate
511 forward and actuates the cutting mechanism 52 and
the conveying clamp mechanism 53 to cut the feed
material 30 and to deliver the cut section of the feed
material 30 to the die assembly (not shown),
respectively.
As mentioned above, when the eccentric pin 623
rotates along with the driven gear 622 , the first swing
member 63 is swung by the eccentric pin 623 so that
the first swing member 63 moves to and fro in a cycle
motion and completes one cycle of the cycle motion
for each revolution of the eccentric pin 623. The
first swing member 63 executes a first stroke movement
(from the first position to the second position of
the first swing member 63) , and a second stroke
movement (the second position to the first position)
in one cycle of its cycle motion. The eccentric pin
623 rotates by a first angle 91 for the first stroke
movement of the first swing member 63 and by a second
angle 92 for the second stroke movement. The first
angle 61 is smaller than the second angle 62.
In this embodiment, 61 is equal to 140 degrees,
whereas 92 is equal to 220 degrees. Thus, the
eccentric pin 623 of the driven gear 622 rotates
counterclockwise by an angle of 140 degrees to actuate
the feeding mechanism 4 to advance the feed-material
30 one time. Since the time taken by the eccentric
pin 623 to turn 140 degrees is less than that to turn
220 degrees, the time required by the feeding mechanism
4 to advance the feed material 30 is reduced, compared
to the time taken in the course of stopping advancement
of the feed material 30. Therefore, the time
provided for the cutting mechanism 5 2 and the conveying
clamp mechanism 53 to perform their respective cutting
and delivering actions can be increased.
Referring once again to Figures 2 to 4, since the
time needed to activate the cutting mechanism 52 and
the conveying clamp mechanism 53 has been prolonged,
the first and second inclined surfaces 514, 517 of
the first and second cam plates 512, 516 can be
increased in length so that the slope angles thereof
can be decreased, thereby reducing the pressure
induced on the first and second cam plates 512, 516
during their camming actions. Therefore, when the
drive gear 611 is speeded up in order to increase the
production rate of the forming machine, vibration
movements can be reduced.
Referring to Figure 6, there is shown a second
preferred embodiment of the present invention. In
the second embodiment, the feeding mechanism 4'
includes an upper sector-shaped driven gear 411' and
a lower sector-shaped drive gear 412 which are
interftieshed each other and which are connected
coaxially and respectively to a pair of feed rollers
(not shown) to pinch the feed material 30 therebetween
for advancement. When the sector-shaped lower gear
412 rotates clockwise, the feedmaterial 30 is advanced
to the cutting mechanism 52 .
The direction of the sector-shaped drive gear 412
to advance the feed material 30 in this embodiment
is opposite to that of the drive gear 412 in the first
embodiment. Furthermore, the direct ion of the driven
gear 622' to drive the first swing member 63 is opposite
to that of the driven gear 622 in the first embodiment .
No reverse gear is provided in this embodiment, and
the driven gear 622 ' is meshed directly with the drive
gear 611. Thus, 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 connected directly to the slide block
633 in the through hole 632 of the swing plate 631.
The swing plate 631 has a bottom end pivoted directly
to the left side of the machine body 32 . The length
adjustment member 642 is fixed directly to a front
side of the swing plate 631 so that the length
adjustment member 642 is swung synchronously with the
swing plate 631.
Therefore, when the driven gear 622' is driven by
the drive gear 611 to rotate clockwise, the swing plate
631 turns from the first position to the second
position, and the sector-shaped drive gear 412 rotates
counterclockwise so that the feed mechanism 4' does
not advance the feed material 30. At this time, the
cutting mechanism 52 and the conveying clamp mechanism
53 are activated to perform the respective cutting
and delivering actions. When the driven gear 622'
continues to rotate, the swing plate 631 is turned
from the second position to the first position, and
the sector-shaped drive gear 412 rotates clockwise
so that the feed material 30 is advanced. This
embodiment provides the same result as the previous
embodiment.
WE CLAIM
1. A forming machine for forging which provides with a die assembly
comprising:
- a cutting mechanism (52) adapted to cut a feed material;
- a conveying clamp mechanism (53) adapted to deliver a cut section of the
feed material (30) from said cutting mechanism (52) to the die assembly;
- a feeding mechanism (4,4') adapted to advance the feed material to said
cutting mechanism (52);
- a first transmission mechanism (51) connected to said cutting mechanism
(52) and said conveying clamp mechanism;
- a drive mechanism (61) driving said first transmission mechanism (51)
and
- a second transmission mechanism (62) driven by said drive mechanism
(61) for driving said feeding mechanism (4,4'), said second transmission
mechanism (62) including a driven wheel (622,622') driven by said drive
mechanism (61), an elongated swing plate connected to said feeding
mechanism (4,4') confronting said driven wheel (622,622') and having an
elongated through hole , and an eccentric pin (623) projecting axially from
said driven wheel (622,622') and connected slidably to said elongated
through hole in said swing plate, said swing plate having a pivot axis
which is substantially parallel to an axis of said driven wheel, said
eccentric pin sliding relative to said swing plate while rotating along with
said driven wheel (622,622') so that said swing plate (63) is turned to and
fro in a cycle motion and complete one cycle for each revolution of said
eccentric pin (623).
wherein said swing plate executes a first stroke movement and a second
stroke movement in one cycle, said eccentric pin rotating by a first angle for
said first stroke movement and a second angle for said second stroke
movement, said first angle being smaller than said second angle, and
wherein said driven wheel is a driven gear which is driven by said drive
mechanism, said second transmission mechanism further including a
reciprocating unit connected to said swing plate and said feeding
mechanism.
2. The forming machine as claimed in claim 1 wherein said swing plate (631)
further has a slide block (633) slidably disposed in said through hole
(632), said eccentric pin (623) being connected to said slide block (633).
3. The forming machine as claimed in claim 1 wherein said drive mechanism
(61) includes a drive gear (611) to drive said driven gear (622,6220, and
a crank (612) connected to said driven gear (611) and said first
transmission mechanism (51).

A forming machine for forging which provides with a die assembly
comprising:
- a cutting mechanism (52) adapted to cut a feed material;
- a conveying clamp mechanism (53) adapted to deliver a cut section of the
feed material (30) from said cutting mechanism (52) to the die assembly;
- a feeding mechanism (4,4') adapted to advance the feed material to said
cutting mechanism (52);
- a first transmission mechanism (51) connected to said cutting mechanism
(52) and said conveying clamp mechanism;
- a drive mechanism (61) driving said first transmission mechanism (51)
and
- a second transmission mechanism (62) driven by said drive mechanism
(61) for driving said feeding mechanism (4,4'), said second transmission
mechanism (62) including a driven wheel (622,622') driven by said drive
mechanism (61), an elongated swing plate connected to said feeding
mechanism (4,40 confronting said driven wheel (622,622') and having an
elongated through hole , and an eccentric pin (623) projecting axially from
said driven wheel (622,622') and connected slidably to said elongated
through hole in said swing plate, said swing plate having a pivot axis
which is substantially parallel to an axis of said driven wheel, said
eccentric pin sliding relative to said swing plate while rotating along with
said driven wheel (622,622') so that said swing plate (63) is turned to and

fro in a cycle motion and complete one cycle for each revolution of said
eccentric pin (623),
wherein said swing plate executes a first stroke movement and a second
stroke movement in one cycle, said eccentric pin rotating by a first angle
for said first stroke movement and a second angle for said second stroke
movement, said first angle being smaller than said second angle, and
wherein said driven wheel is a driven gear which is driven by said drive
mechanism, said second transmission mechanism further including a
reciprocating unit connected to said swing plate and said feeding
mechanism.

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Patent Number

233670

Indian Patent Application Number

597/KOL/2005

PG Journal Number

14/2009

Publication Date

03-Apr-2009

Grant Date

01-Apr-2009

Date of Filing

06-Jul-2005

Name of Patentee

FWU KUANG ENTERPRISES CO., LTD.

Applicant Address

NO. 239, LANE 202, CHUNG-CHENG W. RD. ERH-HANG TSUN, JEN-TE HSIANG, TAINAN HSIEN

Inventors:

#	Inventor's Name	Inventor's Address
1	YUN-TE CHANG	11F. NO.51, ALLEY 75, LANE 37, SEC. 3, TUNG MEN RD.

PCT International Classification Number

F16H 35/02

PCT International Application Number

N/A

PCT International Filing date

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1			NA