US3322011A

US3322011A - Flying punch

Info

Publication number: US3322011A
Application number: US375069A
Authority: US
Inventors: George J Kocian
Original assignee: Yoder Co
Current assignee: Intercole Bolling Corp
Priority date: 1964-06-15
Filing date: 1964-06-15
Publication date: 1967-05-30
Anticipated expiration: 1984-05-30

Description

May 30, 1967 G. J, KoczlANl 3,322,011

FLYING PUNCH Filed June l5, 1964 5 Sheets-Sheet l 78 May 3o, 1967 Filed June l5, 1964 G. J. KOCIAN FLYING PUNCH 3 Sheets-Sheet 2 ATTORNEYS May 30, 1967 G. J. KoclAN 3,322,011

FLYING PUNCH Filed June 15, 1964 5 Sheets-Sheet 3 um |52 l fin l e "hm/11"' IN VEN TOR.

@50H65 11. KocfAlv |66 K |74k 23 24 mmgwm ATTORNEYS United States Patent O Ohio Filed June 15, 1964, Ser. No. 375,069 17 Claims. (Cl. 83-285) This invention relates generally as indicated to a ilying punch and more particularly to a punching mechanism for use in forming mills and the like for the placement of holes or indentations of various shapes into the work sections before, after or during the forming thereof.

Conventionally, the punching of holes or indentations of various shapes in rolled stock requires the use of a prenotch die and press or other types of specialized equipment which usually punch the stn'p stock before the roll shaping thereof. If holes or slots are required only adjacent the ends of the cut to length pieces, this can sometimes be accomplished by special adaptations of the cut-off press. However, with perforations throughout the length of the workpiece, two machines are usually necessary, one placed at the entry end and the other at the exit end of the forming line. The necessity for the additional press at the entry end of the line arises when the finished shapes have deep legs or flanges, as in a box or channel shape, and also when slots or irregular cuts have to be made in these flanges. Ordinarily, this can only be done on the fiat metal strip before the forming thereof. The use of such additional presses not only adds to the equipment investment, but also requires a substantial amount of space for installation. It would, therefore, be highly desirable to punch holes of various shapes into the rolled sections, even in the deep legs or anges of such sections, after or during the forming thereof. It would also be highly desirable to accomplish this without adding substantially to equipment costs as well as space requirements.

It is accordingly a principal object of the present invention to provide a punching mechanism for the placement of holes of various shapes into rolled sections before, after or during the forming operation.

A further principal object is the provision of a ying punch for use in forming mills which constitutes a moditied standard rolling mill housing.

Another object is the provision of a flying punch for use in rolling mills which will place slots, perforations, deformations, or the like in the anges r legs of the sections of rolled shapes before, after or during the forming thereof.

Still another object is the provision of a flying punch for use with rolling mills which can produce perforations in rolled stock at substantially any desired spacing.

Yet another object is the provision of a low cost space economizing punching mechanism for use in conjunction with rolling mills which will perform its operation on the travelling work before, after or during the forming operation without the stopping thereof.

A further object is the provision of a iiying punch of the type set forth which can operate at uniform or varied intervals.

A yet further object is the provision of a punch modified from a standard mill housing wherein one shaft may actuate the punch and the other may accelerate the die.

Other objects and advantages of the present invention will become apparent as the following description proceeds.

To the accomplishment of the foregoing and related ends, the invention, then, comprises the features hereinafter fully described and particularly pointed out in the claims, the following description and the annexed drawings setting forth in detail certain illustrative embodiments of the invention, these being indicative, however,

of but a few of the various ways in which the principles of the invention may be employed.

In said annexed drawings:

FIG. 1 is an end elevation partially broken away and in section of a punching mechanism in accordance with the present invention;

FIG. 2 is a fragmentary horizontal section taken substantially on the line 2 2. of FIG. l;

FIG. 3 is a vertical section taken substantially on the line 3 3 of FIG. 2;

FIG. 4 is a somewhat enlarged fragmentary vertical section corresponding to FIG. 1 illustrating a modification of the present invention for the punching of holes in the flanges of the rolled sections;

FIG. 5 is a fragmentary view similar to FIG. 1 illustrating the addition of a clutch and stop index mechanism;

FIG. 6 is a fragmentary vertical section taken substantially on the line 6 6 of FIG. 5;

FIG. 7 is a fragmentary vertical section of the drive housing side of the machine illustrating still another way to employ a clutch and index mechanism in which both the upper and lower shafts can have selected and intermittent rotation; and

FIG. 8 illustrates a mechanism which to accelerate the die mechanism from spindle.

Referring now to the embodiment of the invention illustrated in FIGS. l through 3, there is shown a basic inboard type of roll stand used in roll forming machines suitably modified for the practice of the present invention. Roll forming is, of course, a process whereby a at strip of metal or other material, usually from a coil, is passed through a series of rolls arranged in tandem and progressively formed into the ultimate sectional shape desired. A cut-off press then severs the shape into the desired lengths.

The roll forming machine is thus comprised of a series of roll stands arranged in Vtandem with the rolls which progressively shape the work being mounted on the spindles journalled in the roll stands. Roll forming machines may be classified into two general types with regard to the spindle supports or housings: those with overhung spindles usually being referred to as the outboard type; and those with spindles supported at both ends being referred to as the inboard type. FIGS. l through 3 illustrate an inboard type roll stand such as that manufactured by The Yoder Company of Cleveland, Ohio.

The machine ycomprises, a base 1 on which the various stands may be tandemly arranged :and the illustrated stand comprises a drive housing 2 and Ian outboard housing 3 between which extend top and

bottom spindles

4 and 5, respectively, ou which the forming rolls are normally mounted. The profile of a forming roll 6 which would norm-ally be supported 'by the top spindle 4 is illustrated in phantom lines in FIG. l. Both the drive and the outboard housing may be secured to the base 1 and the out-board housing may be adjusted toward and away from the drive housing. Slots in the base l accommodate fasteners 7 permitting such transverse adjustment of the outboard housing. In fact, when desired, the illustrated machine could be converted to an outboard machine simply by pushing the outboard housing 3 against the drive housing 2 thus obtaining overhung spindles with added #bearing support for 'such spindles on the drive side.

The lower spindle 5 is supported at 9 and 10 in the drive housing 2 by precision tapered roller bearings and at 11 in the outboard housing 3 by roller bearings, rotating in hardened sleeves, keyed to the roll spindles. The upper spindle 4 is journalled at 13 in precision tapered roller bearings in block 14 and at 15 in roller bearings rotating in a hardened sleeve keyed to the spindle 4 in block 16. The

blocks

14 and 16 are mounted lfor vertical may be employed the revolving lower adjustment in

windows

17 and 18 in the drive and outboard housings, respectively. The

blocks

14 and 16 are mounted on vertically extending rods extending through

micrometer screws

18 and 19 on the top of the drive and outboard housings, respectively, by which accurate vertical adjustment yof the top spindle 4 may be obtained. Hardened Spanner

type clamping nuts

20 and 21 are secured to the ends of the

spindles

4 and 5, respectively.

Each drive housing 2 of the forming machine is provided with a Worm shaft 23 and chain type iiexible couplings may be employed to interconnect the worm shafts of the individual roll stands of the machine to form a driven line or back shaft extending longitudinally yof the machine. A hardened steel worm 24 is mounted -on the shaft 23 and meshes with a high strength 'bronze worm gear 25 keyed to the shaft 5 between

sleeves

26 and 27. A pinion 28 is also secured to the sha-ft 5 Ibetween the sleeve 27 and sleeve 29, such pinion driving a toggle type idler gear train 30 which includes gear 31 keyed to the end of upper spindle 4. The toggle type gear train, which includes meshing gears joined by toggle links, permits maximum roll spindle adjustment while maintaining constant pitch-line mesh. In the toggle type gear train, gears with either equal or unequal lratio may be provided. Normally, when the sections `are to be formed which have deep proles, such as a conventional channel, the upper or male rolls mounted on the spindle 4 have a larger pitch or driving diameter than the lower rolls, mounted on the spindle 5. Accordingly, the number of revolutions per minute of the spindle mounting the larger -roll should be smaller in order that the peripheral speed of both the upper and lower rolls will be the same. The speed ratios of the shafts or spindles 4 4and 5 may thus be the same or varied depending upon the selection of the gear ratios in the train 30. In -any event, the speed ratios wil-l depend upon the relative sizes `of the rolls employed upon the spindles.

The micrometer dials provided at 18 and 19 may enable rthe operator to set the upper roll in correct alignment with the lower roll, such dials accurately indicating the clearance or lspacing lbetween the top and bottom roll. In forming non-symmetrical shapes, the

separate micrometer screws

18 and 19 may be employed to apply more pressure along one side of the strip where the greater amount of forming is done. The drive housing 2 maybe entirely enclosed so that the gearing therein will Ibe -provided in an oil tight case for proper lubrication purposes. Each spindle may be provided with a longitudinally extending keyway as indicated at 33 to permit the lforming rolls to be secured thereto at the desired location.

The machine above described comprises a conventional roll stand of a roll forming machine and .per se forms no part of the present invention. However, by utilizing lsuch standard rolling mill housing with only minor modications, there is provided a punching mechanism capable of punching holes of various shapes into the rolled sections after or during the forming. With the roll 6 removed rfrom the

spindles

4 and 5, the ypunching mechanism may readily be mounted between the drive and out-board housgIhe punching mechanism consists of two die

slides

40 and 41 seen in FIG. l which are secured together in vertically spaced relation by elongated fasteners such as the recessed head cap screws 42 passing through collars or spacers 43 interposed between the die slides 40 and 41 holding the same rmly in the lspaced apart position. As seen in FIG. 2, there may be six such fasteners for the die slides 40 and 41, three on each side. The

slides

40 and 41 are then firmly held together to form a unitary die structure. Each die slide is provided with laterally eX- tending longitudinally elongated T-bars as indicated at 45 'and 46 which ride in T-shaped slots 47 in

tracks

48 and 49 which are supported by angle brackets 50 and 51, respectively. Such brackets may be secured by fasteners 52 through bed plate 53 to the base 1. Both the

angles

4 and 51 as well as the

tracks

48 and 49 may be cut away as indicated at 55 in FIG. 3 to accommodate the lower spindle 5. The

tracks

48 and 49 may be secured to the angles by suitable fasteners for ease `of assembly within the roll stand. The die assembly formed 'by the 4die slides 4t) and 41 is thus mounted for `sliding movement longitudinally of the mill line 4or normal to the plane of FIG. l bythe T-bar and slot connect-ion between the dies and the tracks.

The spacing of the dies 40 and 41 by means of the collars 43 provides a passage 57 therebetween accommodating the traveling work W.` Such work may be moving through the mill in the `direction of the arrow 58 as seen in FIG. 2 and may comprise, for exam-ple, a completely or partially shaped channel section having anged legs accommodated in

grooves

59 and 60 in the top die slide 40. The bottom 61 of the channel W will move through the passage 57 between the die slides contiguous with the top surface of the bottom die slide 41.

A punch 63 is mounted in the top die slide in bushing 64 and is provided with an oblate head 65. A compression spring 66 extends between the top of the top die slide 40 and the under side of the head actively urging the punch 63 upwardly toward cam 68 mounted kon the top spindle 4. A lstop ring 69 may be provided on the shank of the punch beneath the top die slide 40 to limit upward movement of the punch. The punch 63 thus constitutes the male punching die and the female die may be provided in the form of circular aperture 70 in the bottom die slide 41 communicating with recess 71 through which the removed portions of the workpiece W may fall.

Such workpiece is guided through the passageV 57 in the carriage formed by the top and bottom die slides 40 and 41 and such die slides are held against

stops

73 and 74 in the

tracks

48 and 49, respectively (see FIG. 2), by

springs

75 and 76. Such springs may be secured at one end as indicated at 77 to the die slides and at the opposite ends to dowel

pins

78 and 79 secured to the

tracks

48 and 49, respectively. The

springs

75 and 76, which may be termed return springs, then resiliently hold the carriage formed by the die slides 40 and 41 against the

stops

73 and 74. In such position, the work W will be guided through the carriage held in such position. Y

Referring now to FIG. 3, will be seen that the cam 68 has a spanking or Working surface 80 of approximately 2" in circumferential extent which will depress the punch 63 its maximum extent. With the spindle 4 rotating in a counterclockwise direction as viewed in FIG. 3, the cam 68 will engage the oblate top 65 of the punch and start to depress the same against the pressure ofthe spring 66. When the surface 80 of the same diameter reaches the top 65, the punch 63 will be depressed to its maximum extent having entered the bottom 61 of the channel W. As the punch enters the work, the Work will then become locked Vto the

slides

40 and 41 since the male punch Y63 will enter the female die perforating the bottom 61 of the work W. This causes the die slides 40 and 41 to move to the right as seen in FIG. 3 with the work W against the pressure of the

springs

75 and 76. 'I'his in turn causes the punch top 65 to move from beneath the cam 68 and when Y clear, the spring 66 will -cause the punch 63 to move upwardly stripping the same from the bottom 61. When the punch 63 has cleared the workpiece, the

springs

75 and 76 will pull the carriage comprised of the die slides 40 and 41 back against the

stops

73 and 74. When the die slides have in this manner been reset, the punch top 65 will then be repositioned directly beneath the cam 68 to be spanked or depressed as the surface 80 again engages the top 65. The clearance between the cam 68 and Ythe top 65 indicated in FIGS. l and 3 reduces frictional drag and permits the

springs

75 and 76 quickly to return the carriage to its initial position when the punch 63 is cleared from the work.

The present invention may also be utilized t-o punch holes of different shapes in the side walls 83 and` 84 of the channel shape section W as seen in FIG. 4.

Angle brackets

85 and 86 similar to the brackets 50 and 51 shown in FIG. 1 may |be provided supporting

tracks

87 and 88 extending in the direction of the travelling work between the outboard and drive housings of the roll stand. Such tracks are provided with T-

shape slots

89 and 90, respectively, receiving T-

bars

91 and 92 extending longitudinally and secured to the sides of die slide 93. An upper die slide member 94 is removably secured to the die slide member 93 by fasteners 95 or the like and the die slide members 94 and 93, when secured together, mate to form a longitudinal passage through the die slide carrage formed thereby to receive the channel shape workpiece W. The die member 94 includes a central chamber 96 forming downwardly projecting walls 97 and 9S adjacent the interior surface of the legs S3 and 84 of the channel section workpiece. Mounted in such legs are female

die buttons

99 and 100.

Each side of the die slide member 93 is provided with

Vertical passages

102 and 103 as well as intersecting

horizontal passages

104 and 105. Mounted in the

passages

104 and 105 are punches 106 and 107, respectively, slidably mounted in

bushings

108 and 109 tted in the inner reduced diameter portions of the

passages

104 and 105. Compression springs 110 and 111 extend between the shoulders formed by such reduced diameter portions and the ends of the

bushings

108 and 109, and rings 112 and 113 on the punch Shanks forming spring shoulders. Such springs thus actively urge the punches 106 and 107 to a laterally withdrawn position clear of the legs 83 and 84 of the workpiece W.

The ends of the punches 106 and 107, remote from the workpiece W, are provided with inclined or cam surfaces 115 and 116 which engage similarly inclined surfaces 117 and 118 on the bottom of

cams

119 and 120, respectively. The

cams

119 and 120 aremounted in the upper ends of the

vertical passages

102 and 103, respectively, in bushings 121 and 122.

Pins

124 and 125 are mounted in the respective cams and project into aligned vertical slots in the lbushings and die slide 93 as indicated at 126 and 127. These pins fitting within such slots keep the

cams

119 and 120 from rotating about their vertical axes to maintain the cam surfaces on the bottom thereof properly oriented with the surfaces 115 and 116 on the ends of the punches. Compression springs 128 and 129 surround the shanks of the

cams

119 and 120, respectively, and extend between the die slide 93 and the heads or tops 130 and 131 of the cams. The tops 130 and 131 may be of a similar oblate shape as the top 65 of the punch 63 shown more clearly in FIG. 2. Restrictions may be provided in the

slots

126 and 127 to limit upward movement of the

cams

119 and 120 but in any event, the

springs

128 and 129 actively urge the cams upwardly toward

rotating cams

133 and 134 keyed to the spindle 4. The

cams

133 and 134 may be of the same type .as the carn 68 shown in FIG. 3.

It can now be seen that when the

cams

133 and 134 depress or spank the

cams

119 and 120, the cam surfaces 117 and 118 will move downwardly causing the punches 106 and 107 to move inwardly to punch an aperture of the desired configuration in the side walls 83 and S4'of the workpiece W. The die slide 93 will be connected to return springs 136 and 137 similar to the

springs

75 and 76 which will hold the die slide resiliently against a stop. When the punches 106 and 107 enter the work, the die slide 93 will be locked to the work for travelling therewith. When the tops 130 and 131 of the

cams

119 and 120 clear the

cams

133 and 134, respectively, the springs 110 and 111 as well as the

springs

128 and 129 will then cause or permit the punches to be withdrawn or stripped from the work thus releasing the die slide 93 from the work and the return springs 136 and 137 will then return the die slide to its initial position against the stops.

It can now be seen that the side walls of the work can be perforated in a manner similar to the bottom as indicated in the FG. 3 embodiment simply by interposing a linear cam between the rotating cam and the punch. This interposing of the linear cam then translates the vertical movement obtained by the rotating cam into a horizontal movement ena-bling the perforating of the side walls or flanges of the workpiece W.

It will be appreciated that the die block 94 may be provided with a vertically extending punch extending downwardly into the chamber 96 and that a further carn may be provided on the spindle 4 so that both the side walls and bottom of the channel shape work may be punched or perforated simultaneously. The throughbores or passages 102 through 10S facilitate the assembly or disassembly of the punches or cams and provide access for lubrication.

As an example, suppose it is desired to place holes in a channel shape workpiece of the type illustrated, either in the bottom, in the legs, or both, on 24 centers. The shape may be rolled to size up to the second last pass. Then between the ultimate and penultimate pass roll stands, the punching mechanism of the present invention may be situated simply as an additional stand. Then in order to Iget the spacing desired utilizing a 2 diameter spindle, the cam utilized would have an operating radius of 3.8197 inches. The spacing of the apertures, of course, can be varied by changing the gear ratios of the train between the

shafts

5 and 4 or by utilizing different size cams or specialized cams with peripherally spaced contact points. The varieties in shapes and spacing of apertures along the formed or partially formed sections are practically limitless.

Referring now to FIGS. 5 and 6 -a cam 140 may be provided which is journalled as indicated at 141 on the shaft 4 and includes a clutch plate 142 also journalled on such shaft. Between the cam and the clutch plate, there is provided an index section 143 having a radially ex tending stop surface 144. The clutch plate 142 may be connected or disconnected from electrical clutch member 145 which is keyed to the shaft 14 as indicated at 146. The electrical clutch mechanism 145, which may be provided with internal slippings, may be energized by the electrical connection 147.

A stop index arm 149 is proximally pivoted at 150 and also at 151 to the lower end of armature 152 of solenoid 153. It can now -be seen that the cam .140 may be caused to lbe driven through one complete revolution by the energization of the clutch as well as the solenoid 153, the latter withdrawing the arm 149 from the stop surface 144. Both the solenoid 153 and the proximal pivot 150 may be mounted above the cut-otf on suitable brackets. It will be understood that in lieu of the stop index illustrated, a brake mechanism may be substituted such as is conventional in one revolution clutch mechanisms. By energizing the clutch and solenoid, it is then possible to punch at any selected interval 4as opposed to the uniform spacing obtained in the embodiment illustrated in FIGS. 1 through 3. The clutch need not be electric as indicated, but may be air actuated, or mechanical unidirectional, or other conventional varieties. Limit switches operated 'by the cam itself may deenergize the device or set the brake at the proper times in the cycle.

In FIG. 7, there is illustrated another embodiment of the invention utilizing a clutch and brake mechanism to drive intermittently and selectively both the upper and lower shafts. The worm shaft 23 which has mounted thereon the worm 24 drives worm gear 160 which is journalled at 161 on the extension 162 of the lower shaft 5. The worm gear is, however, fastened as at 163 to quill 164 which is in turn journalled at 165 to bearing block 166 mounted on the exterior of the drive housing 2. The outer end of the quill 164 is journalled at 168 to the reduced diameter extension 169 of the shaft 5. The outer end of the quill is keyed at 170 to clutch drive member 9171 and the shaft extension 169 is keyed at 172 to the clutch driven member 173. A brake mechanism 174 is mounted on frame 175 and a stationary power pick-up 176 is connected to power line 177 for operation of the clutch.

It can now be seen that the clutch and brake mechanism illustrated in FIG. 7 will rotate the bottom spindle 5 selectively as well as the top spindle 4 through the gearing 28. Since the worm shaft 23 is continuously rotating, it will he seen that the punching machine can be located anywhere in the mill line and does not necessarily have to lbe at an end pass.

It Will be appreciated that the embodiments thus far described are intended for shapes sufficiently stiff or rigid to push or pull the die slide forward. However, for shapes lacking sufficient stiffness or strength to punch die forward without buckling or tearing, a powered die slide may be provided. Referring now to FIG. 8, there is illustrated a mechanism for driving the die from the lower spindle 5. A ,gear segment 180 of suitable radius may be keyed to the lower spindle 5 and such segment may have a 30 to 45 circumference as required. Such gear segment meshes with rack 181 secured to the bottom of the lower die slide 41 and as the lower spindle rotates in 4a counterclockwise FIG. 8, it will be seen that the die mechanism will be caused to move between the extremes of travel indicated in phantom line positions at 182 and 183. The cam 68, which may have a 30 duration of operation,.will then engage the punch top 65 when the dies are moving at approximately the speed of the work W. The return springs 75 and 76 will return the dies to their original position after the .gear segment 189 disengages'the rack 181. it'will be understood that other suitable die accelerator mechanisms may be provided either driven from the lower spinvdle 5 o-r from a separate accelerator.

This embodiment of the invention is applicable in cases where the material or work W (such as paper) being punched cannot because of its characteristics pull or push the

die punch carrier

40, 41. The motion imparted to the dies would normally be synchronized ro the work speed, but it cases where the material has not yet been formed, i.e. is fiat and somewhat flexible, the motion may be slightly faster than the work travel.

It can now be seen that the punching mechanism which will accomplish such a wide variety of punching of strip formed or partly formed travelling stock comprises a die slide mounted in the throat of the roll stand for short distance movement with the work. The work is guided through the die which includes the spring loaded punch. When the spanking cam actuates the punch, such is driven into the work locking the die to the work Vfor movement therewith. The die is then moved from beneath the cam and the return springs release the work from the die. Return springs a-re also employed to reposition the die beneath the cam for the next punching operation. The configuration and speed of rotation of the cam or the illustrated clutch mechanisms control the spacing of the perforations. Such punching mechanism then comprises a slight modification Iof the roll stand with the forming rolls removed.

The lower spindle may be left in place when used to drive the dies or removed and replaced by a stub shaft, depending upon space requirements, and certain modifications other than those illustrated will be apparent to one skilled in the art. For example, the top spindle4 may be reinforced to reduce deection and the

housings

2 and 3 may be modified to permit greater vertical adjustment of the top spindle. Also, the spacing between the stands in the mill may be varied if desired.

In any event, it can now be seen that there is provided a punching mechanism which will place holes of various shapes at various. spacings into elongated sections before, after or during the forming operation in a conventional rolling mill without greatly increased space requirements and by inexpensive modification of one of the rolling mill stands.

Other modes of applying the principle of the invenpush or pull the direction as viewed inY tion may be employed, change being made as regards the details described, provided the features stated in any of the following claims or the equivalent of such be employed. v

I, therefore particularly point out and distinctly claim as my invention:

1. A punching mechanism for elongated travelling work comprising a standard roll forming mill housing including an outboard and drive housing with a spindle journalled therebetween, a die having a work path therethrough and including movable male and cooperating female die elements, track mounting said die for short.

distance linear movement with thework, a spanking cam mounted on said spindle for rotational movement in synchronism with the speed of the travelling Work, and means operative resiliently to hold said die and thus said movable male die element in operative position adjacent said cam until removed therefrom by travel of said die with such work.

2. A punching mechanism as set forth in claim 1 including means mounted in said die interposed between said spanking cam and said male die element operative to change the direction of force exerted by said spanking cam.

3. A punching mechanism as set forth in claim 2 wherein said male die element comprises a substantially horizontally disposed punch, and said last mentioned means comprises a linear cam in engagement with said punch.

4. A punching mechanism as Set forth in claim 1 wherein said male die element comprises a vertically extending punch directly beneath said spanking cam when said die is resiliently held in `operative position.

5. A punching mechanism as set forth in claim 1 including spring means operative to urge said movable male die element toward said spanking cam and away from such work.

6. A punching mechanism as set forth in claim 5 including stop means on said male die element operative to limit the movement thereof toward said spanking cam.

7. A punching mechanism for a roll forming machine comprising a modified roll stand having at least one transverse roll spindle, a die mechanism having a work tance movement with the work, a cam mounted on said spindle, and spring means operative resiliently to hold said die mechanism in operative position adjacent to and beneath said cam. Y p

8. A lpunching mechanism as set forth in claim 7 wherein said die mechanism comprises male and female die elements on opposite sides of such work path, said cam being operative to drive said male element into such work to lock said die mechanism to such work for movement therewith and thus to remove said die mechanism from such operative position with respect to said cam.

9. A punching mechanism as'set forth in claim 8 including spring return means for said male element operative to release said die mechanism from said work when said male element clears said cam.

10. A punching mechanism as set forth in claim 7 wherein said stand includes a drive housing and an outboard housing with said spindle journalled therein, means in said drive housing operative to drive said spindle at a controlled speed.

11. A punching mechanism as set forth in claim 7 wherein said stand includes a drive housing and an outboard housing with said spindle and track means extending transversely of said spindle between said housings accommodating said die mechanism for such movement with the work.

12. A punching mechanism as set forth in claim 11 including support means for said track means removably secured to said stand between said housings.

13. A punching mechanism as set forth in Yclaim 1) including means on said drive and outboard housings vertically to adjust said spindle.

and

journalled therebetween,

cluding a clutch mechanism operative selectively to r0- tate said spindle and thus said cam.

References Cited UNITED STATES PATENTS Vermeulen 83-320 X Candee 83-319 X Yoder 83-320 X Whistler et al. 83-628 X McNabb 83-314 X Bognar 83-319 X ANDREW R. JUHASZ, Primary Examiner.

Claims

7. A PUNCHING MECHANISM FOR A ROLL FORMING MACHINE COMPRISING A MODIFIED ROLL STAND HAVING AT LEAST ONE TRANSVERSE ROLL SPINDLE, A DIE MECHANISM HAVING A WORK PATH THERETHROUGH MOUNTED ON SAID STAND FOR SHORT DISTANCE MOVEMENT WITH THE WORK, A CAM MOUNTED ON SAID SPINDLE, AND SPRING MEANS OPERATIVE RESILIENTLY TO HOLD SAID DIE MECHANISM IN OPERATIVE POSITION ADJACENT TO AND BENEATH SAID CAM.
15. A PUNCHING MECHANISM AS SET FORTH IN CLAIM 7 INCLUDING CLUTCH MEANS OPERATIVE SELECTIVELY TO ROTATE SAID CAM.