JPS62230435A - Transporter - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates generally to transfer machines for moving workpieces sequentially through a series of processing stations in a machine, and more particularly to transfer machines that move workpieces sequentially through a series of processing stations in a machine. S
uofy) Patent Nos. 3,155,241 and 3.42
This invention relates to an improvement in a transfer device of the type disclosed in US Pat. Like the previously filed and patented device, the device of the present invention is primarily intended for use with presses and the like, and is particularly outstanding when used with presses and the like. The device of the present invention is
Although it operates basically in the same way as the transfer device of the prior patent, it is capable of operating at significantly higher speeds, does not produce destructive vibrations during use, and has a single station feature that can be optionally incorporated. It is also possible to lift and transport workpieces from one station to the next station. Due to the special design of the lifting and transport function, it is also possible to incorporate this function into all processing stations, as well as other means of transport that simply slide or index the workpiece from one station to another with a linear traversal movement. They can also be used in combination.

A transfer device according to the invention moves a pair of elongated and opposed workpiece holding jaw blades back and forth in a horizontal plane by means of a first drive means. The jaw blades are mounted parallel to each other on opposite sides of a series of machining stations, and in use, the jaw blades initially move horizontally inward toward the machining stations to engage the workpiece within the station. do. The jaw blades are then directed horizontally along the station line by the second drive means to simultaneously advance the plurality of workpieces to one of the series of stations. After all the workpieces have been advanced one station, the jaw blades are moved apart by the first drive means to release the workpieces and are then retracted to the starting position by the second drive means.

The redrive means are mechanical linkages suitably interconnected and driven by rams, which are structural members of prior art presses, to move the workpiece retaining jaw blades in a series of motions as will be described below. Each transfer linkage has an oscillating shaft that oscillates back and forth during actuation of the drive means, and the oscillating motion of the oscillating shaft is transmitted to the workpiece holding jaw blade via a cam and a cam follower.

Because clearance must exist in the drive linkage, the linkage is susceptible to vibration during use.

The vibrations associated with such operation cause the press to
While this is not a problem if the press is running at speeds as low as 8 cycles, if the press is running at higher speeds the vibrations become a serious problem and can even be destructive. An important part of the idea of the invention lies in the finding that the above-mentioned undesirable destructive vibrations can be avoided by means of a braking mechanism associated with one or both of the drive linkages and cooperating with the rocking shaft. Incorporating one or more brake mechanisms at specific locations on the transfer device allows the press to operate satisfactorily at speeds several times higher than it could operate without the brake mechanisms. The improved transfer device of the present invention therefore significantly increases and improves the manufacturing capacity of the press.

As suggested, the transfer device according to the invention in its basic idea operates in a single horizontal plane.

The jaw blades first move inward to grab the workpiece, then move sideways to slide multiple workpieces simultaneously into adjacent stations, then move away to disengage the workpieces, and finally then retreats to the initial position value, ie, the starting position. However, due to the shape of the workpiece or the forming operations to be performed on the workpiece, is it inconvenient to simply slide the workpiece from one station to the next at some or all stations? Or it may be impossible. at one or several or all stations, lifting the workpiece out of the forming die for transfer to an adjacent station;
It may be necessary to drop the workpiece into a die at each station after arriving at an adjacent station. It is a unique feature of the present invention that the workpiece clamping jaws can be modified to incorporate lifting and transport functions at all stations or at selected few stations as required. Thus, a straight transverse movement of the jaws may also simply slide the workpiece from one station to the next, lifting the workpiece from each station if required by the workpiece geometry and the particular forming operation. It can also be taken out and dropped into the next station. In other words, it is also possible to introduce a lifting transport type in all stations, and it is also possible to combine linear transversal movement with lifting transport.

For illustrative purposes, in the drawings depicting the preferred embodiment of the invention, reference numeral 10 designates a standard punch press, which includes the reference numerals 15, 16, 17, 18, 19, .
A series of stations designated 20 and 22 (see Figure 2)
The die shoe 12 supports a plurality of lower die members 13 inside the die shoe 12 .

Workpiece 14 is formed by die member 13 interlocking with an upper die member (not shown) supported by punch shoe 24 which is driven in a known manner by a power ram. The punch shoe 24 moves downwardly under the force of the ram 26 to form the workpiece 14 within a plurality of equally spaced stations 15-22, and after the forming operation is completed the punch shoe is moved downwardly by the ram 26. be forced to retreat.

For the particular press 10 and workpiece shown in the drawings,
Manually or by suitable automatic means, a flat disc-shaped workpiece 14 is placed in a loading station 15 and a hole 28 is formed in its center in a second processing station 16. In the second processing station 17 a centrally disposed upright collar 30 is formed. At a third processing station, spaced parallel slots 32 are formed on opposite sides of the workpiece 14, and at a fourth processing station 19, a portion of the workpiece intermediate the slots is bent downward to form a hanging tab 34. do. At the fifth processing station 20, apertures 36 are punched in opposite sides of the intermediate portion of the tab 34 of the workpiece 14. The finished workpiece 14 is
Unloading station 2 by manual or suitable automatic means
taken out from 2.

The conveying device according to the invention is mounted on a die shoe 12 located on opposite sides and at one end of the series of processing stations 15 to 22, and is in operative connection with a ram 26 - for each cycle of the press. 10, all workpieces 14 are advanced one by one to the internal stations at the same time. More specifically, during operation, the conveying device moves elongated jaw blades 38 and 40 located on opposite sides of processing stations 15 to 22 to first engage workpiece 14 in a clamping manner and then As the ram 26 rises and retreats, it advances the workpiece one stage at a time within the press, and as the ram moves downward to bring the die together for a forming operation, the transport system moves the jaw blades 38 and 40.
are pulled apart to release the workpiece and then both jaw blades are retracted to their initial or starting position.

For a more detailed explanation of the transport mechanism, station 1
Elongated bearings 46 and 4 extend laterally outwardly from 5-22.
2, which shows the jaw blade 38 supported on a pair of spaced parallel rods 42 and 44, each reciprocatingly mounted within the jaw blade 38. Jaw blade 40 is supported by a pair of rods 50 and 52 that also slidably operate within elongated bearings 54 and 56. The two jaw blades 38 and 40 extend substantially the entire length of the processing stations 15-22, with the inner edges of the blades being arcuate as indicated at 58. The arcuate portions 58 are shaped to match and are spaced apart to receive the periphery of the workpiece 14 in each station. As can be seen, the jaw blades 38 and 40 are disposed on opposite sides of a series of stations, johns 15-22, with the arcuate portion 58 being the same distance apart as the stations so that the jaw blade support rod 42 .44 and 50
．． As 52 advances or moves inwardly toward each station icon within bearings 46.48 and 54.56,
Each arcuate portion engages and tightens the peripheral edge of the workpiece inside the combined station. In practice, the jaw blades 38 and 40 approach each other so that the clamps engage opposite sides of the workpiece at the beginning of the transfer, and the workpiece is advanced into one stationary cone within the machine by means detailed below. After this, the jaw blades separate or move away to disengage the workpiece.

The jaw blades 38 and 40 are moved into the workpiece 1 by actuator means 57 and 59 arranged at the outer ends of the rods 42.44 and 50.56, respectively.
4 and the clamp are engaged or the clamp is disengaged.

More specifically, the actuator means 57 in combination with the jaw blade 38 are located at stations 15 to 22.
It consists of horizontal swing shafts 60 parallel to one side of and generally laterally spaced apart.

Shaft 60 is mounted for oscillation within spaced apart bearings 62 and 64 that are mounted and fixed to die shoe 12. Upright swing arms 66 and 68 on and fixed to opposite ends of swing shaft 60
supports a horizontal par of 70. Spaced apart rolls 72 and 74 at the rear or outer end of rod 42 surround and closely receive transverse parr 70. Similarly, rolls 76 and 7 are spaced apart from the outer end of rod 44.
8 surrounds and closely receives the horizontal par 70. When the rocking shirt 60 pivots in the bearings 62 and 64 in the clockwise direction as seen in FIG. 74 and 78 to slide rods 42 and 44 inwardly within bearings 46 and 48 to bring jaw blade 38 into clamping engagement with workpiece 14. Conversely, when rocker shaft 60 rotates counterclockwise, it acts through outer rolls 72 and 76 to retract jaw blade 38 and release workpiece 14.

On the other hand, similar means are provided for moving the jaw blade 40 in combination with the actuator means 69 into and out of clamping engagement with the workpiece 14. A rocking shaft 80 disposed parallel to the stations 15 to 22 on laterally opposite sides thereof is supported by and fixed to the Gui Shu 12 in spaced bearings 82 and 8.
It is attached to 4. The upper ends of upright swing arms 86 and 88, which are fixed to opposite ends of swing shaft 80, are connected to transverse pars 90. Spaced apart rolls 92 and 94 on rod 50 surround and fit snugly with lateral parr 90, and similarly spaced rolls 96 and 98 on rod 52 surround and fit tightly with lateral parr 90. Since the fit is tight, the swing shaft 80
The vibratory motion of acts through rolls 92.94 and 96.98 to slide rods 50 and 52 back and forth within bearings 54 and 56, causing jaw blade 40 to move against workpiece 14.
and tightening cause engagement and disengagement.

In practice, the rocking shafts 60 and 80 are rotated simultaneously by the two actuator means 57 and 59 at the beginning of the transfer operation, so that the jaw blades 38 and 40
are advanced from opposite sides of processing stations 15-22 into clamping engagement with workpiece 14. After advancing the workpiece 14 one station within the machine by means detailed below, the oscillating shafts 60 and 80 are again actuated simultaneously in opposite directions so that the jaw blades 38
and 40 away from processing stations I5-22 to disengage from workpiece 14.

As best seen in FIG. 2, the means for vibrating the swing shaft 60 is attached to an actuator bar 102 that is supported by and suspended from a portion of the corner of the punch shoe 24, and is vertically aligned with the actuator bar. It consists of a cam bar 100 that can be moved in any direction. A cam bar 100 extends downwardly along the swing arm 66 and spaced laterally therein such that a cam slot 104 in the cam bar is rotatably mounted over the clutch arm 108 and It receives a cam follower roll 106 disposed laterally on the clutch arm, which is loosely attached to the swing shaft 60 on the outside of the swing arm 66. Come Thrower) 104
end portions 110 and 112 are vertically disposed within the cam bar 100 and are laterally offset from each other and interconnected by an angled slot portion 114. As best seen in FIG. 2, upper terminal portion 110 is disposed adjacent the outer edge of cam bar 100, and intermediate portion 114 is located between processing stations 15 and 2.
2, the lower terminal portion 112 slopes downwardly and inwardly toward the
is located adjacent the inner edge of the cam bar.

The swinging arm 6 allows the swinging shaft 60 to be operated by hand.
6 and clutch arm 108 are releasably interconnected by a clutch mechanism 115.

More particularly, a spring-loaded clutch member 116 is supported on swing arm 66 and is resiliently engaged with a pin 118 projecting laterally from the swing arm. When the ram 26 is at the lower end of its stroke, i.e. in the fully "down" position, the cam follower roll 106
At or adjacent to the upper end of the slot 104, the upper terminal portion 110 of the slot
00, the oscillating shaft 60 is in the limit position of counterclockwise oscillating movement when viewed in FIG. 2, and the jaw blade 38 associated with the oscillating shaft is pulled rearward and the workpiece 14 and the engagement with the workpiece 14 is released. As ram 26 moves backward or upwardly within press 10, it pulls cam bar 100 upwardly and cam follower roller 106 moves downwardly within cam slot 104.

During the initial movement of retracting ram 26 as the upper goug supported by punch shoe 24 is moving away from workpiece 14 within stations 15-22, The cam roll 10 is moved without any influence as far as the transfer device is concerned.
6 is simply the linear upper terminal portion 1 of the cam slot lO4
Just cross 10. However, after the initial backward movement of the ram 26 is completed, the cam roll 106 enters the sloping intermediate portion 114 of the cam slot 104 and as the cam roll passes through the slot portion 114, the cam roll is rotated toward the right, i.e. moving toward stations 15 to 22, clutch arm 108 and swing arm 66
to rotate the swing shaft 60 clockwise in the drawing, thereby swinging the transverse par 70 in the direction of stations 15 to 22 and causing the rods 42 and 44 to advance as described above. The jaw blade 38 engages the adjacent edge portion of the workpiece 14 in a clamping manner.

Clutch member 116 is spring-loaded against pin 118 with sufficient force so that clutch arm 108 and oscillation do not occur except in the event of a snag, which could occur if one of the workpieces were to dislodge from the processing station. The movable arm 66 always moves together and slides the combined jaw blade assembly. In the event of a jam, the clutch member 116 releases the pin 118, allowing the ram to move fully backwards without affecting the transfer system, thereby preventing the transfer system from operating during normal operation of the equipment. Prevent destruction.

Conversely, cam roll 106 is located at or near the bottom of lower slot portion 112.

When the ram 26 is at the upper end of its travel stroke within the press 10 and the ram is moving downward during the process stroke, the cam roll 106 is actuated through the cam slot 104 in the reverse order described above. As a result, the rocker shaft 60 rotates counterclockwise, pulling the jaw blade 38 out of the processing station 15-22 and releasing the engagement between the jaw blade and the workpiece.

The transfer device portion associated with the jaw blade 40 on the opposite side of the processing stations 15-22 is similarly driven so that the jaw blade clamps into or out of engagement with the workpiece 14. Move the jaw blade to Two actuator means 57 and 5
9 are similar in construction and operation, to fully understand the construction and operation of the transfer device, it is necessary to refer to the jaw blade 4.
There is no need to describe the actuator that drives 0 in detail. Cam bar 12 similar to cam bar 100
Suffice it to say that 0 is attached to and is driven by the ram 26 at a location adjacent to the rear left corner of the ram as viewed in FIG. cam bar 12
0 has a slot (not shown) similar to the cam slot 104, and a cam roll (not shown) on the clutch arm 122, which is loosely attached to the rocking shaft 80, has a slot (not shown) similar to the cam slot 104.
The swinging shaft and swinging arm 8 move inside the slot.
6 and 88 to swing the horizontal bar 90 and slide drive the rods 50 and 52 associated with the horizontal bar to move the jaw blade 40 toward or away from the stations 15 to 22 in a row. let The clutch arm 122 is detachably connected to the swing arm 86 so that the clutch mechanism 123 can be manually operated. More particularly, the clutch arm 122 normally seats on a pin 126 on the swing arm 86 and supports a spring-loaded clutch member 124 holding the bin, so that the cam and cam follower means Lateral movement of the clutch arm moves actuator means 59 in unison to drive the jaw assembly reciprocally as described above.

a jaw assembly (i.e., jaw blades 38 and 40;
By moving the rods 42.44 and 50.52 and the bearings 46.48 and 54.56 parallel to the -row stations 15 to 22, each workpiece is moved forward and into engagement with the jaws. 14 are indexed from station to station by sequentially advancing a distance equal to the spacing between adjacent stations. For this purpose, two bearings 46 and 48 are mounted and fixed on transverse bearings 12B and 130, which are fixed on a shaft 132, which is connected to a stationary plate 137, which is part of Gui Shu 12 (see FIG. 1). Bearing block 1 fixed to
34 and 136 for reciprocating movement.

Similarly, bearings 54 and 56 are fixed to transverse bearings 138 and 140 supported and fixed on shaft 142, which is reciprocatably mounted on bearing blocks 144 and 146 fixedly attached to plate 137. . One end of each of the shafts 132 and 142 are interconnected by a transverse bar 148, with an ear 150 extending laterally outwardly at approximately the center of the transverse bar pivotable to an actuator generally designated by the reference numeral 152. and is slidably connected to.

The actuator means 152 comprises a rocking shirt 154 (see FIG. 4) rotatably supported in spaced bearings 156 and 158 mounted inside a housing 160, which is connected to the processing stations 15-22. The die shoe 12 is supported and fixed at one end of the die shoe 12. At one end of the housing 160 there is an upright support 162 that is integral with the housing and has a vertical passage 164 formed on its outer side, within which a slide 166 is provided for vertical translational movement. It is freely contained. A vertical cam slot 168 (see FIG. 2) within slide 166 is positioned next to a swing arm 172 (see FIG. 4) connected to one end of swing shaft 154 by a key 174. A cam driven roll 170 is received. As perhaps best seen in FIG.
6 and a lower end portion 178, which end portions are different from each other and have an angled central or intermediate portion 180.
are interconnected by.

As can be seen in FIGS. 1 and 2, actuator means 152 is disposed to the right of stations 15-22, and the upper end portion 176 of cam slot 168 is a slight difference to the right of the lower end portion 178. . Thus, the effect of upward movement of slide 166 within passageway 164 is that cam follower roll 170 moves through sloped intermediate portion 180 of cam slot 168.
2 to rotate the swing arm 172 and swing shaft 154 in a counterclockwise direction as viewed in FIG. vice versa,
The downward movement of the sliding portion 166 is caused by the cam driven roll 17
0 is used through the cam follower roll 170 to rotate the swing arm 172 and swing shaft 154 clockwise as it moves through the middle portion 180 of the cam slot 168. Upper and lower terminal portions 1 of cam slot 168
76 and 178 as well as the movement of the cam driven roll 170 within the swing arm 172 or swing shaft 154.
It does not affect any of them and does not drive any of them.

The slide 166 is driven by the ram 26 via an actuator bar 182 (see FIG. 1) and a striking block 184 extending laterally inwardly from the actuator bar. The striking block 184 extends laterally into a vertically elongated recess 186 formed in the outer surface of the slide 166 that is longitudinally and laterally interleaved with the cam slot 168. When the ram 26 is at the lower limit of movement within the press 10, the striking block 184 is disposed at the lower end of the recess 186.

During the initial upward movement of the ram 26, the actuator means 15
The striking block 184 moves into the recess 186 without any influence as far as the operation of 2 is concerned. Thereafter, the continuous upward movement of the ram 26 causes the striking block 1 to
84 to raise the slide 166 within the passageway 164, and as the slide moves upwardly into the passageway, the cam follower roll 170 moves downwardly within the cam slot 168 as described above. The swing arm 172 and swing shaft 154 are rotated counterclockwise. On the contrary, Ram 2
When 6 moves downward during the upward process stroke,
Since the striking block 184 simply moves across the internal recess 186 of the slide 166, the initial movement has no effect on the actuator member 152. However, when the striking block 184 reaches the lower end of the recess 186, it moves the slide 166 downwardly within the passageway 164 and moves the cam follower roll 170 upwardly within the cam slot 168. , swing arm 17
2 and the swing shaft 154 are rotated clockwise.

The oscillating motion of the oscillating shaft 154 is controlled by a clutch arm 188 which is rotatably secured to one end of the oscillating shaft 154 opposite the oscillating arm 172 by a key 190.
(See Figures 2, 3 and 4)
8 and located at the upper end of the clutch arm 188 and generally designated by the reference numeral 192 is loosely attached to the rocker shaft 154 between the clutch arm and the adjacent end of the housing 160. A clutch arm is connected to the swing arm 194. As the roll 196 on the crossbar ear 150 moves within a vertical passage 198 provided within the rocker arm 194, counterclockwise vibrations of the rocker shaft 154 cause the clutch arm 188 and
Clutch mechanism 192, swing arm 194, and roll 1
96, a horizontal bar 148, and two shafts 132 and 14.
2 to move the entire jaw assembly to the left as viewed in FIGS. In practice, the movement described above takes place when the jaw blades 38 and 40 are in clamping engagement with the workpiece 14, and the cams causing the movement occur.
The sloped intermediate portion 180 of the slot 168 is dimensioned to allow the jaw assembly and workpiece to move a distance equal to the spacing between adjacent stations 15-22.

Accordingly, upon completion of the oscillating movement of the oscillating shaft 154, all workpieces 14 advance within the press 10 by -stations. Conversely, clockwise movement of the rocker shaft 154 acts through the linkage described above to move the jaw assembly the same distance to the right in the drawing. In practice, the movements described below occur when the jaw assembly is retracted out of engagement with workpiece 14.

Next, for a detailed explanation of the clutch mechanism 192, the third
Let's pay attention to Figure and Figure 4. A clutch member 200 is slidably mounted below the roll 196 within the passageway 198, and a compression spring 202 contained between the road bottom and the clutch member causes the clutch member to be normally lifted and stretched. It is held in the correct position. If desired, the upper and lower terminal portions of spring 202 may be retained within sockets 204 and 206 provided in clutch member 200 and the bottom of passageway 198, thereby allowing the clutch member to remain in passageway 198. It can help hold it inside. clutch arm 1
The roll 208 supported by the clutch member 2
It is seated in a curved recess 210 at the top of the 00, and is firmly held in pressure engagement by a compression spring 202. In practice, for manual operation by the rocker shaft 154, the spring 2 is applied with sufficient force to releasably engage the clutch arm 188 and the rocker arm 194.
02 presses the clutch member 200 against the roll 208. However, if any damage occurs to the indexing movement of the conveying device, the roll 208 will roll out against the elastic force of the spring 202 and disengage the clutch arm 188 and the swing arm 194. The mechanical part driven by the ram 26 is free to complete the movement without driving the transfer device, thus preventing damage to the transfer device.

Although only the clutch mechanism 192 has been described in detail in this specification, the clutch mechanism 155 connects the swing arm 66 to the clutch arm 108 and the clutch mechanism 12 connects the swing arm 86 to the clutch arm 122.
2, both have similar structures to the clutch mechanism 192 and operate similarly.

As alluded to above, an important part of the technical idea that makes this invention patentable is that incorporating a brake mechanism into one or more linkages drives the jaw blades 38 and 40 during transfer operations. This is based on the knowledge that the press 10 can be operated at fairly high speeds without causing undesirable destructive vibrations in the various linkages involved.

Incorporating a braking mechanism into the indexing actuator means 152 is of paramount importance since the indexing actuator must move the combined jaw assembly and parts the greatest distance, and the It is also important to incorporate a brake mechanism into the actuator 152 as described above, since the largest volume and weight are added to the indexing movement. On the other hand, the linkages 57 and 59, which move the jaw assembly into and out of clamping engagement with the workpiece 14, are only required to move a relatively short distance; Its bulk and weight are also quite small. Accordingly, the braking mechanism disclosed herein may include indexing actuator means 152.
Although only incorporated in the actuator means 57 and 59, it will be readily appreciated that similar braking mechanisms can be incorporated in the actuator means 57 and 59 if necessary or desired.

To explain in more detail, the brake mechanism is provided in the housing 16.
0 and a laterally outwardly extending plate-like brake member 2 on the clutch arm 188 and slightly spaced laterally of the support member.
It consists of 14.

Elongated brake housing 21 with a square transverse shape
6 has a corresponding shape and is slidably attached to an opening 218 inside the support part 212. Brake member 214 overlaps a portion of opening 218, and brake housing 216 is formed with a recess 220 for receiving the overlapping portion of the brake member.

Furthermore, the recess 220 is at least slightly wider than the brake member 214 so that the clutch arm 188 does not directly interfere with the housing 216 and can accommodate the brake member 214.
14 vibrates freely. However, the oscillatory motion of member 214 is caused by the oscillatory motion of member 214 disposed in opposing sockets 226 and 228 on opposite sides of recess 220 and disposed within socket 228 between the bottom of the socket and brake shoe 224. Braking is achieved by shoes 222 and 224 which are pressed against opposite sides of brake member 214 under the action of compression spring 230 which is enclosed in the brake member 214 .

In operation, the brake housing 216 is located within the opening 21.
8 to accommodate irregularities in the brake member 214, and as the brake member 214 oscillates with the clutch arm 188, the spring 230 holds the brake shoes 222 and 224 at all times. It is firmly pressed into engagement with the brake member 214. The pressure exerted on the brake member 214 by the brake shoes 222 and 224 absorbs play or drive between the interconnected and relatively movable parts of the actuator means 152, particularly the interaction between the brake shoes and the brake member. Due to the action, when the sliding portion 166 moves up and down,
Cam follower roll 170 is brought into pressure engagement with one side or the other of cam slot 168 . Experience has shown that the brake mechanism allows the press 10 to cycle at significantly higher speeds without undesirable destructive vibrations of the transfer device.

In the case of relatively large and heavy transfer devices, it may be desirable to incorporate a brake mechanism on all of the actuator means 57, 59 and 152, whereas in the case of relatively light transfer devices, a single brake mechanism in combination with the linkage 152 may be used. It has also been found through experience that it is appropriate to use only the brake mechanism.

The following is a brief description of the operation of the press 10 and the transfer device associated therewith. The transfer device shown in FIG. 1 shows the press fully closed and the working cycle completed. The transfer device begins to operate when the ram 26 is pulled upwards. However, cam slot 10
Due to the rest area provided by the upper cam slot portion of 4 and the recess 186 inside the slide 166, the initial movement does not move the transfer device. The cam surfaces of the intermediate cam slot portions 114 within the two actuator means 57 and 59 engage the clutch arms 10B and 12.
The horizontal pars 70 and 9 contact the cam driven part attached to 2.
The first movement of the Transfer 1# action begins when the jaw blades 38 and 40 are forced into clamping engagement with the workpiece 14 by forcing the jaw blades 38 and 40 inward toward stations 15-22.

The striking block 184 is inserted into the recess 186 inside the sliding portion 166.
A forward indexing effect occurs after passing the rest area given by . The striking block 184 does not reach the end of the recess, and the jaw blades 38 and 40 strike the workpiece 14.
Begin lifting the sliding part 166 until you have finished holding it in your mouth. However, as soon as slide 166 begins to rise, cam slot 168 forces cam follower roll 170 to the left as viewed in FIG. 2, causing clutch arm 188 and swing arm 194 to swing in the same direction. let As the swing arm 194 rotates counterclockwise as described above, the swing arm 194 drives the roll 196 and the lateral par 148 to the left, causing the jaw assembly to index. The processed workpiece 14 is moved to each station inside the press 10.

The brake mechanism shown in FIG.
68 and is also a means for preventing movement between other interconnected and relatively movable members that would cause wobbling and vibration of the mechanism during use. Due to the raised state of the brake housing 216, the contact pressure of the brake pads 222 and 224 against the brake member 214 is always maintained at a constant pressure. The final upward stroke of ram 26 completes forward transport of the workpiece.

Once the ram 26 begins to move downwards within the press 10 after the stamping operation on the workpiece has been completed, the action of the conveying device is reversed. Cam bars 100 and 120 force the jaw assemblies apart, disengaging jaw blades 38 and 40 from workpiece 14. Slider 166 forces downwardly moving cam follower 196 to the right in FIG. 2, returning transverse parr 148 and jaw assembly to the initial or starting position.

As pointed out above, the lifting and transporting mechanism shown in FIGS. 6 and 7 can be easily incorporated into a transfer device as a special feature device. Although the lifting and transporting mechanism shown here is incorporated into only one station, it is possible to provide similar lifting and transporting equipment at all stations or at a selected number or locations, depending on the requirements of the particular circumstances. Of course, it is possible to do so. If the shape of the workpiece makes it difficult or impossible to simply slide and orient the workpiece in an apparatus of the type described above, it is generally common to move the workpiece from one station to the next. It is necessary to lift and carry 14.

In accordance with the present invention, the optional component lifting and conveying means includes a pair of laterally spaced apart parts supported by and welded or otherwise attached to the jaw blades (jaw blade 40 is shown for convenience of illustration) at the station location. The upright mounting consists of brackets 232 and 234. In this regard, it will be readily appreciated that both jaw blades 38 and 40 may be provided with mutually opposed lifting mechanisms whenever it is necessary to lift and remove a component 14 from a station.

If a lifting device is used, the jaw blade of the station to which the lifting device is attached must have an arcuate portion 58 for engaging the workpiece.

In such a case, the installation would involve positioning the brackets 232 and 234 at the rear of the jaw blades, and in other cases cutting off the jaw blades extending forward of the brackets, as shown at 236, to create a gap for receiving the workpiece 14. .

Therefore, the portions of the jaw blades 38 and 40 that support the lifting device do not function as jaws that engage and hold the workpiece 14, but merely act as supports that support the lifting device.

The illustrated lifting device is located at the processing station in line with the bearing, and the third attachment is such that the bracket 238 is welded or otherwise welded to the bearing 54 directly behind the bracket 234.
is fixed to. However, if the lifting device is at any other station, the shaft 142 can of course be provided with another suitable support for supporting the bracket 238.

The jaw blade 240 is attached to the front brackets 232 and 234.
The front brackets 232 and 234 are slidably mounted along the rear bracket 238 between the front brackets 232 and 234
The front edge of the jaw blade portion that extends forward of the
A recess 242 is provided for receiving the marginal edge of the workpiece 14. Front mounted spaced cam rolls 244 and 246 disposed intermediate brackets 232 and 234 are free to rotate on pins 248 and 250. pin 2
48 and 250 extend laterally to the roll, and the protruding portions of these pins are press fit into appropriate openings in brackets 232 and 234. As can be seen, roll 246 is above and behind roll 244, and both rolls operate within a single cam slot 252 in jawblade 240. Although the cam slot 252 is straight, it is sloped upwardly and rearwardly, similar to and at the same angle as the rolls 244 and 246. A pin 2 which extends in the lateral direction of the roll and whose extension portion is mounted at the rear is embedded and retained in a bracket 238.
56, a third cam roll 254 is rotatably attached and held. The roll 254 is the jaw blade 2
The rear mount located at the rear of 40 operates an L-shaped cam slot 258 located along bracket 238. As can probably be best seen by looking at Figure 7,
The cam slot 258 has an upper horizontal portion 260 and a vertical portion 26 extending downwardly from the rear end of the upper horizontal portion 260.
2.

In use, cam rolls 244 and 246 move back and forth within cam slot 252 and jaw blade 38
and 40 move into stations I5-22 and away from stations 15-22, the cam roll 254 simultaneously enters the L-shaped cam slot 258 and moves from one portion 260 of the cam slot to the other 262. In this connection it should be noted that the jaw blades 38 and 40 move just as in the first described embodiment of the invention.

The only difference is that instead of the workpiece being engaged and clamped by the workpiece receiving arc 58, it is received in a recess 242 within the jaw blade 240 but does not necessarily need to be clamped.

At the beginning of a cycle of operation utilizing a lifting and transporting mechanism, the jawblades 38 and 40 are pulled down or laterally removed from the line of the workpiece 14, and the cam rolls 244 and 246 associated with each mechanism Positioned at the upper or lower end of the slot 252, as shown in FIG. 6, a cam roll 254 is located at the front or inner end of the horizontal cam slot 260. As the jaw blades 38 and 40 move forward or inward toward the line of the workpiece 14, the mounting of each mechanism is attached to the bracket 23.
2 and 234 move with attached jaw blades 38 and 40 and cam rolls 244 and 246
The entire jaw blade 240 is moved through the work piece 1.
4 to engage the recess 242 of the jaw with the workpiece brought to the station by the mechanism. As the jaw blade 240 advances, the cam roll 254 moves to the rear or outer end of the horizontal cam slot 260. In fact, at the same time that recess 242 receives and engages workpiece 14, roll 254 seats on jawblade 240 at the rearward end of cam slot 260. When this occurs, cam roll 254 prevents further forward movement of jaw blade 240. However, Jawblade 4
0 continues to advance toward the workpiece, causing the rear cam roll 254 to move downwardly within the vertical cam slot 262 while the two front cam rolls 244 and 246 move downwardly within the inclined cam slot 252. move inside. As a result, the jaw blade 240 moves vertically upward, as shown in FIG. A horizontal pointing movement is provided by the section actuator means 152 to point to an adjacent station.

After the workpiece 14 has been directed or moved to an adjacent station within the press 10, the jaw blades 38 and 40
workpiece 1 in which two opposing lifting mechanisms are supported by a retracting or outward horizontal movement as described above.
4 and lower it to the transferred station. As each jawblade moves horizontally away from the station, the combined jawblade 240 cannot move with the jawblade 40 because the jawblade 240 is held by the cam roll 254. However, the vertical cam slot 262 moves downwardly on the rear cam roll 254 and the two front cam rolls 2
As 44 and 246 move to the right in the angled cam slot 252, the initial backward movement of jawblade 40 causes jawblade 40 to move jawblade 240 vertically downward. Forward cam rolls 244 and 24
6 reaches the upper outer end of the slanted cam slot 252 and the rear cam roll 254 enters the vertical cam slot 262.
By the time the upper limit of the roll 254 is reached, the horizontal cam
Now in position to move forward within slot 260, roll 254 releases jawblade 240 and moves jawblade 40 rearwardly. Thereafter, jaw blade 240 retreats together with jaw blade 40.

When jaw blade 240 begins to retract, it pulls workpiece 14 out of engagement. During the final retraction movement of the jaw blade 4o, the jaw blade 240 moves away from the processing station and returns to the initial starting position of the respective workpiece of the lifting mechanism.

[Brief explanation of drawings]

FIG. 1 is a partial perspective view of a known press equipped with a transfer device according to the invention. FIG. 2 is an enlarged perspective view of the transfer device itself. FIG. 2A is an elevational view showing a set of cam bars and cam follower rolls in combination with the cam bars for driving portions of the transfer mechanism to grip or release workpieces. FIG. 3 is an enlarged partial perspective view of a portion of the linkage mechanism for advancing workpieces within the press; the transfer actuator linkage is shown in FIG. FIG. 3 shows a braking mechanism to avoid destructive vibrations occurring within the mechanism. FIG. 4 is a vertical sectional view taken along line 4-4 in FIG. 3. FIG. 5 is a horizontal sectional view taken along line 5--5 in FIG. 4. FIG. 6 is a partial perspective view of a modified lifting and transporting embodiment of the transfer device, with the transfer device in an initial or starting position with the jaw blades disengaged from the workpiece; FIG. 7 is a partial perspective view similar to FIG. 6 showing the jaw blades engaged with the workpiece and the workpiece raised or lifted within the work station; 10... Press, 14... Processed piece, 15-22...
・Station, 26... Ram, 38.40,...
Jaw blade, 57.59... Actuator means, 60... Rocking shaft, 66... Rocking arm.

Claims (2)

[Claims] (1) A workpiece transfer device that has a ram that can freely reciprocate and that transfers a workpiece from one processing station to another within a press of a multi-stage processing station, the counter being connected to an actuator driven by the ram. a first of the actuators reciprocally drives the jaw blade transversely to the processing station to engage and separate the jaw blade from a workpiece in the processing station; a second actuator of the actuators is configured to drive the jaw blade while the jaw blade engages the workpiece to move the workpiece to a next adjacent processing station. In the workpiece transfer device having a lifting device for vertically raising and lowering the workpiece before and after the movement, the lifting device 232, 234, 238, 240, 252 in at least one of the processing stations is attached to the jaw blades 38, 40, said lifting device being attached to said jaw blades 38, 40;
members 132, 142, 46, 48 which are attached to and only move said jaw blades 38, 40 and said movement;
, 54, 56, respectively;
A second jaw blade 240 is attached to the front and rear brackets, and cam rolls and cam slots 244, 246, 252 move the second jaw blade 240 in response to lateral movement of the jaw blades 38, 40. A transfer device characterized by being provided to move a blade 240 up and down. (2) the cam roll and the cam slot are connected to the second
Slanted cam slot 25 in jaw blade 240
2 and supported by the front brackets 232, 234 are operable in the second jaw blade 240 and include horizontal and vertical portions 260, 262.
A second cam slot 258 is provided in the second jaw blade 240 having a
2. A transfer device according to claim 1, wherein a cam roll 254 supported at 38 is operable in said second cam slot.