Transfer Apparatus

Abstract

An apparatus for axially receiving and laterally transferring successive elongated elements. A plurality of element receiving channels are mounted for lateral movement across a given path along which the said elements are delivered to the apparatus. Adjustable switch pipes axially deliver one elongated element to one of said channels while simultaneously directing the leading end of the next subsequent element to another adjacent channel. The element receiving channels and the switch pipes are intermittently operated to transfer the elongated elements sliding in said channels laterally from the said path while permitting uninterrupted axial movement of at least one elongated element from one of said switch pipes into one of said channels.

Description

DESCRIPTION OF THE INVENTION

This invention relates generally to an apparatus for handling elongated elements such as bars, rods, pipes, small shapes, etc., and more particularly to a means for axially receiving successive elements traveling along a given path and for laterally transferring said elements to adjacent equipment for further handling and/or processing.

The invention will hereinafter be described in connection with the handling of hot rolled bars issuing from the final finishing stands of a rolling mill. It is to be specifically understood, however, that this example is being employed for illustrative purposes only, and that the invention may be applied to other like situations, where lateral transfer of successive axially moving elements is desired.

In a rolling mill, bar products issuing from the finishing stands are usually directed axially to a transfer apparatus, the function of which is to bring the bars to rest prior to transferring them laterally onto the receiving end of a cooling bed. The cooling bed thereafter continues the lateral transfer of the bars for a period of time which is sufficient to insure adequate cooling in preparation for subsequent handling steps, which in the usual circumstances involve trimming, cutting to length, straightening and bundling. Those skilled in the art will appreciate the fact that cooling beds represent a substantial investment in both equipment and building space, and that accordingly, cooling beds of minimum length are highly desirable.

With conventional installations, minimum cooling bed length is calculated as the product of the speed at which bars or other elongated elements are axially delivered to the transfer apparatus times the "total cycle time" required for the transfer apparatus to bring the bars to rest and to laterally transfer them onto the receiving end of the cooling bed. Accordingly, if the overall length of a cooling bed is to be reduced without affecting mill delivery speed, the efficiency of the transfer apparatus must be improved by reducing total cycle time.

Experience has indicated that in many conventional installations where kickoff paddles are employed to laterally shift successive bars from an entry table into a sliding notch, from where the bars are picked up and removed by the carryover rack of the cooling bed, the total cycle time of the transfer apparatus is unduly lengthened by the necessity of having to wait until a given product length has come to rest in the sliding notch before lateral transfer of the product onto the receiving end of the cooling bed can begin. Also a gap usually must be created between successive product lengths so as to provide time for the kickoff paddles to pass through that portion of their full cycle of motion when they are in the path of the next successive bar length. The gaps are usually created by accelerating each product length above mill delivery speed, a factor which in turn increases the time required for each product length to subsequently slide to rest. Thus, where product is delivered to the transfer apparatus at a speed of say 3,450 f.p.m. (mill delivery speed of 3,000 f.p.m. plus 15 percent acceleration to produce desired gap), and the total cycle time of the transfer apparatus is about 6.5 seconds, the minimum length of successive cut bars, and hence the shortest possible cooling bed length, it approximately 374 feet.

A general object of the present invention is to avoid the aforementioned difficulties by markedly reducing the cycle time of the transfer apparatus. This is accomplished by providing a plurality of element receiving channels which are movable laterally across the path of axial travel of the elements being handled, and by further employing means for guiding an element into one of said channels while simultaneously directing the leading end of the next subsequent element into another laterally adjacent channel.

Another and more specific object of the present invention is to avoid the use of conventional kickoff paddles, thereby obviating any necessity for accelerating successive product lengths to produce gaps therebetween.

Another object of the present invention is to provide means for laterally transferring elongated elements from a given path of axial travel while the said elements are in the process of sliding to rest.

A further object of the invention is to provide an enclosed path which will allow higher delivery speeds for the small products which might otherwise exhibit a tendency to create cobbles by buckling and rising above the table side guards.

A still further object of the present invention is to axially direct successive elongated elements to laterally adjacent element-receiving channels, thus allowing one element to begin to decelerate by sliding to a halt at the earliest possible moment without interferring with the forward axial movement of the next subsequent element.

These and other objects and advantages of the present invention will become more apparent as the description proceeds with the aid of the accompanying drawings in which:

FIG. 1 is a plan view on a reduced scale showing one embodiment of a transfer apparatus constructed in accordance with the present invention;

FIG. 2 is a view in side elevation on a greatly enlarged scale of the shear-switch combination taken along lines 2-2 of FIG. 1;

FIG. 3 is a plan view of the shear-switch combination shown in FIG. 2;

FIG. 4 is a plan view taken at a location adjacent to the receiving end of a conventional carryover-type cooling bed of a section of the transfer apparatus shown in FIG. 1;

FIG. 5 is a sectional view taken on lines 5-5 of FIG. 4;

FIG. 6--11 are a series of illustrations schematically depicting the operational sequence of the transfer apparatus shown in FIGS. 1--5;

FIG. 12 is a sectional view similar to FIG. 5 showing an alternate embodiment of the transfer apparatus employing hinged cover members overlying each rotatable cylindrical member;

FIG. 13 is a sectional view taken through another embodiment of the transfer apparatus;

FIG. 14 is a sectional view taken along line 14-14 of FIG. 13;

FIG. 15 is a sectional view showing another embodiment of the invention wherein the element receiving channels are defined by endless belt members;

FIG. 16 is a sectional view taken along line 16-16 of FIG. 15;

FIG. 17 is a view showing a specially shaped inclined table roller positioned between the driven belt members of the embodiment depicted in FIGS. 15 and 16; and,

FIG. 18 is another sectional view showing means for providing substantially totally enclosed channels into which successive elongated elements may be delivered.

Referring initially to FIG. 1, there is shown an embodiment of a transfer apparatus according to the present invention generally indicated at 10, one end of which is located adjacent to the last finishing stand 14 of a rolling mill. The other end of the transfer apparatus runs alongside the receiving end of a carryover-type cooling bed 18. The cooling bed 18 is of a conventional design familiar to those skilled in the art, which as can better be seen by references to FIGS. 4 and 5, includes a plurality of spaced laterally extending fixed racks 22 with movable racks 24 interspersed therebetween.

Transfer apparatus 10 is comprised basically of a shear-switch combination 26 which directs the hot rolled mill product from the last mill finishing stand 14 to a plurality of axially aligned rotatable cylindrical members indicated typically at 28. As can best be seen in FIGS. 2 and 3, the shear-switch combination 26 includes a drum shear 30 of the type familiar to those skilled in the art wherein a pair of rotatable blades 30a and 30b are employed to shear axially moving product lengths. Immediately downstream from the shear 30 there is positioned a switch assembly which includes a pair of switch pipes 32 and 34. The receiving ends of the switch pipes 32 and 34 are pivotally connected as at 36 to the rotatable barrel 38 of a switch 40. Barrel 38 is itself provided with a suitably shaped extension 42 having passageways 32a and 34a, the latter being in communication with switch pipes 32 and 34. Passageways 32a and 34a are vertically spaced, as are the receiving ends of the switch pipes 32 and 34. Barrel 38 is intermittently rotated in one direction through increments of 180.degree. by any conventional means such as for example exterior gear teeth meshing with a pinion gear 46 on shaft 48, the latter being driven through a gear reducer 50 by means of a motor 52. The downstream ends 32b and 34b of switch pipes 32 and 34 extend through the rotatable barrel 38' of a second switch 40'. Barrel 38' may also be rotated by means of gear teeth 38' in meshed relationship with a pinion gear 46', the latter being mounted on a shaft 48' which is driven through a gear reducer 50' by a motor 52'. The motors 52 and 52' may if desired be suitably synchronized and interlocked to simultaneously rotate both the upstream and downstream ends of switch pipes 32 and 34 through increments of 180.degree. . Alternatively, the switch 40 and 40' may be sequentially operated intermittently.

Switch 40' is positioned directly upstream from the first of the axially aligned rotatable cylindrical members 28. As can be better seen by reference to FIGS. 4 and 5, each member 28 is provided with a cylindrical body 56, the surface of which is divided by means of radially extending ribs indicated typically at 58 into a plurality of element-receiving channels collectively identified by the reference numeral 60. The ends of each member 28 are enclosed by end plates 62 centrally apertured as at 64 to receive a common drive shaft 66. At least one of the end plates of each member 28 is keyed to the drive shaft as at 68.

Drive shaft 66 may be driven at suitable intervals by any convenient means, such as by sprockets 70 keyed to the shaft as at 72. Drive chains 74 run between sprockets 70 and 71, the latter being driven through gear reducers 76 by motors 78.

The cylindrical members 28 are spaced to accommodate bearings 84 for the main shaft 66, as well as table rollers 86, the latter being driven by motors 88. The table rollers 86 provide a means for propelling stock being directed into the uppermost element-receiving channels 60.

The operation of transfer apparatus 10 will now be described with further reference to FIGS. 6--12. It will be understood that the hot rolled product of a rolling mill issues from the final finishing stand 14 in continuous or semicontinuous lengths at 150 to 5,000 feet, depending on the size of the billet being rolled. Thereafter, the longer lengths are normally subdivided into shorter elements which will fit onto the cooling bed. Accordingly, after emerging from the mill, the leading end of a given product length a is guided along a path 90 (See FIG. 2) into passageway 34a, where it continues through switch pipe 34 into the aligned element-receiving channel 60a of the rotatable cylindrical members 28 (See FIG. 6). At this stage, the switch pipe 32 leading to element-receiving channels 60b is empty. This condition will continue until the minimum product length capable of being handled by the transfer apparatus has passed through shear 30 at which point in time the product is sheared. The action of the shear blades 30a and 30b is such that the newly sheared leading end b' of the next subsequent product length b is directed upwardly along a path 92 (See FIG. 2) into passageway 32a and then on through switch pipe 32. At this particular moment, (See FIG. 7) both switch pipes 32 and 34 contain axially moving product with the tail end a" of element a traveling through switch pipe 34 below the leading end b' of the next subsequent product length b, the latter now traveling through switch pipe 32 on its way to element-receiving notch 60b. This condition will persist until the tail end a" of element a has run through pipe 34, at which point pipe 34 will be empty.

After exiting from switch pipe 34, element a continues to run through element-receiving channel 60a along driven table rollers 86. At the same time, the leading end b' of element b runs the length of switch pipe 32 and enters element-receiving channel 60b. When this condition is reached, switches 40 and 40' are actuated to rotate both the receiving and delivery ends of switch pipes 32 and 34 through 180.degree. in a counterclockwise direction. Simultaneously, shaft 60 and the cylindrical members 28 keyed thereto are indexed in a counterclockwise direction through an angle which is determined by dividing 360.degree. by the number of element-receiving channels 60. In the apparatus herein illustrated, there are 15 channels, hence shaft 60 will be indexed in a counterclockwise direction through an angle of 24.degree. (360.degree. .div.15). This causes the components to be shifted to the positions shown in FIG. 8. In other words, the respective positions of the switch pipes 32 and 34 are now reversed. By indexing the rotatable cylindrical member 28 simultaneously with the 180.degree. rotation of the downstream ends of the switch pipes, communication of switch pipe 32 with channel 60b remains uninterrupted, thus enabling element b to continue running onto the driven table rollers 86. Indexing the cylindrical members 28 also results in the element a in channel 60a being laterally shifted off of the driven table rollers 86. When this occurs, frictional resistance takes over and the element a begins to slide to rest in channel 60a. This enables the lead end b' of element b to overtake and pass the tail end a" of element a while both elements are still in axial motion.

At this point, it is significant to note that with the above-described operation sequence, the newly severed leading end of each successive element is immediately directed to an empty conduit (either switch pipe 32 or 34), which empty conduit is in alignment with an empty receiving element channel 60. This completely obviates the necessity of creating a gap between successive elements by accelerating the stock emerging from the mill. Furthermore, since successive elements are directed along separate but adjacent paths, deceleration of a given element can begin almost immediately without any danger of interferring with a succeeding element.

It should also be understood that although operation of switch 40' must occur simultaneously with the indexing of shaft 60 in order to provide uninterrupted communication between at least one of the switch pipes and one of the channels, simultaneous operation of the upstream switch 40 is not a strict requisite. Actually, switch 40 can be operated any time after the leading end of an element severed by shear 30 has entered one of the switch pipes. Also, it will be evident to those skilled in the art that the downstream ends of the switch pipes need not necessarily be moved through a circular path. Indeed it may be desirable to alter the said path so as to maintain the delivery end of each pipe level with a downstream element receiving channel into which an element is running.

The condition illustrated in FIG. 8 will continue until such time as shear 30 is again actuated to sever element b from the bar continuing to exit from the mill. When shear 30 is actuated, the lead end c' of the next oncoming element c is directed upwardly into the switch pipe 34, while the tail b" of element b continues to run through and out of switch pipe 32 onto the driven table rollers 86, and element a continues to decelerate in channel 60a. This condition, which is shown in FIG. 9, will continue until switch pipe 32 has been emptied, at which point the rotatable cylindrical members 28 will again be indexed through 24.degree. in a counterclockwise direction while simultaneously rotating the switch pipes in the same direction through 180.degree., as indicated in FIG. 10. At this stage of the operational sequence, element c continues to run through pipe 34 into channel 60c; element b has been laterally transferred off of the driven table rollers 86 and has begun to slide to rest in notch 60b; and, element a has now slid to rest in channel 60a. Channel 60a is now in alignment with the first notch 93 on the movable carryover racks 24 of the cooling bed 18. Also, the empty switch pipe 32 has been shifted to a position such that its downstream delivery end is now aligned with the empty element-receiving notch 60d and its upstream receiving end is ready to receive a freshly severed leading end from shear 30.

The next operational sequence is illustrated in FIG. 11 where it can be seen that the carryover racks 24 of the cooling bed 18 have been cycled 360.degree. , the first 180.degree. of which transfers element a into the first notch 94 of the fixed racks 22. While this is being accomplished element b continues to slide to rest in channel 60b. Also at approximately the same time, shear 30 is again actuated to sever element c from the next oncoming bar section d. As shown, the trailing end f" of element c continues to run through switch pipe 34 below the leading end d' of element d, the latter now traveling through switch pipe 32. The foregoing operational sequence may be repeated as long as product continues to issue from the rolling mill.

FIG. 12 shows a slightly modified form of the embodiment previously described, with the addition of curved cover members 96 overlying each rotatable cylindrical member 28. The covers are hinged as at 98 to permit movement between lowered "closed" positions as shown by the solid lines, to raised "open" positions indicated by phantom lines at 96a. The cover members 96 overlie the element-receiving channels 60 in which elements are axially moving and thus serve as a means of insuring that smaller diameter bar products remain contained therein.

Another embodiment of the invention is illustrated in FIGS. 13 and 14 wherein it can be seen that the rotatable cylindrical members 28 are spaced to accommodate modified table rollers 100 mounted on the ends of shafts 102 which are supported by bearings 104 and driven by motors 106. Each roller 100 is provided with a gradually diminishing radius which in turn enables the stock running to the uppermost element-receiving channel 60' to be driven at a speed which is greater than the speed at which the stock in the channel located at 60" is being driven. In other words, one advantage of this arrangement lies in the fact that deceleration of the axially moving elements can take place while the elements are still moving on the table rollers. By employing bullet-shaped rollers 100, the rotatable cylindrical members 28 can be made to overlap the rolls as at 108 (See FIG. 14) thereby decreasing the length of the gaps between the cylindrical member. Also, it will be noted that further confinement of the stock can be achieved by providing the hinged cover members 96 with downwardly depending guides 110 which cooperate with the flanges 58 on the rotatable cylindrical members 28 to provide a substantially continuous side guard on one side of the uppermost element-receiving channel located at 60'.

Another embodiment of the invention is shown in FIGS. 15 and 16 wherein it can be seen that a plurality of element-receiving channels indicated typically by the reference numeral 112 are defined by upstanding ribs 114 supported on endless conveyors 116. The conveyors 116 are provided with rollers 118 which run along tracks 120 extending between wheels 122, the latter having teeth 124 defining semicircular grooves 126 designed to receive the rollers 118. In effect, the wheels 122 act as sprockets which drive the conveyor members 116 laterally in the direction indicated. One or both of the wheels 122 may be driven by any convenient means. As shown in FIG. 16, the upstanding ribs 114 on the conveyor members 116 may be made to overlap relatively small diameter table rollers 128 which are driven by motors 130.

With this conveyor-type arrangement, as opposed to one where the element-receiving channels are supported on rotatable cylindrical members, the length of the conveyor members 116 and the numbers and spacing of the wheels 122 and support tracks 120 can be adjusted to suit a wide range of applications.

FIG. 17 illustrates a still further embodiment of the invention where the conveyors supporting the upstanding ribs 114 are spaced by somewhat truncated conically shaped rollers 132 rotating on inclined axes. These rollers present a horizontal surface to the stock being axially delivered to the apparatus and due to the tapered construction of the rolls, as the conveyors are intermittently advanced in the direction indicated, each separate element undergoes immediate deceleration even prior to being laterally transferred off to the tapered rollers 132.

FIG. 18 shows another embodiment of the invention wherein each upstanding rib 134 on the conveyor members is provided with a laterally disposed flange 136. The flanges 136 act as cover members which enclose the element-receiving channels 138 defined by the upstanding ribs until such time as the conveyor members pass over an underlying curved track 140, which because of its radius of curvature, causes the ribs 134 to be spread apart as at 142. This in effect opens up the previously enclosed element-receiving channel 138 and thus permits stock to be removed therefrom by any convenient means, such as the movable carryover rack 144 of a conventional carryover-type cooling bed.

Having thus described the construction and operation of several embodiments of a transfer apparatus embodying the concepts of the present invention, its advantageous features will now be more readily appreciated by those skilled in the art. For example, the use of the shear-switch combination 26 enables successive bar lengths to be directed to separate but adjacent element-receiving channels which may be supported on either the intermittently rotatable cylindrical members 28 shown in FIGS. 1--13 or the conveyor member shown in the remaining drawings, without the necessity for creating gaps between successive bar lengths. This feature in turn does away with the need for accelerating the product above mill delivery speed and thus substantially simplifies the apparatus. Moreover, by avoiding acceleration, less time is required subsequently for each successive element to slide to rest.

Another advantage of the present arrangement lies in the fact that lateral transfer of the individual bar lengths can take place while a plurality of bars are running out and/or sliding to rest in their respective element-receiving channels. Thus, the time required for each bar to slide to rest can be overlapped with the time required for lateral transfer with the result that the overall cycle time of the apparatus is materially shortened. Calculations indicate that the present invention will reduce the overall transfer time by more than half as compared with more conventional devices. This in turn will enable the overall lengths of the cooling beds to be reduced by approximately one-half, thereby making possible substantial savings in both equipment expenditures and building space.

It is my intention to cover all changes and modifications of the embodiment herein chosen for purposes of the disclosure which do not depart from the spirit and scope of the invention.

Claims

I claim:

1. Apparatus for receiving and laterally transferring a succession of elongated elements moving axially along a given path, said apparatus comprising: transfer means arranged longitudinally along said path, said transfer means having a plurality of adjacent parallel element-receiving channels; a multipath guide means for axially delivering an elongated element into one of said channels while simultaneously directing the leading end of the next subsequent element into another of said channels; and, operating means associated with said transfer means for moving said channels across said path, thereby transferring elements in said channels from said path to a laterally adjacent location.

2. The apparatus as claimed in claim 1 wherein said guide means includes the combination of at least two switch pipes, the said combination being adjustable simultaneously with the operation of said transfer means to continuously maintain communication between at least one of said switch pipes and at least one of said element-receiving channels.

3. The apparatus as claimed in claim 1 further characterized by means for covering the channels on said transfer means in which elongated elements are axially moving.

4. The apparatus as claimed in claim 1 wherein said transfer means includes a plurality of axially aligned rotatable cylindrical members, the said members having circumferentially spaced radially extending ribs defining said element-receiving channels.

5. The apparatus as claimed in claim 1 wherein said transfer means is comprised of endless conveyor members movable laterally across said path, the said conveyor members having spaced ribs defining said element-receiving channels.

6. The apparatus as claimed in claim 4 wherein said transfer means further includes a plurality of driven table rollers extending laterally across said path between said rotatable cylindrical members.

7. The apparatus as claimed in claim 6 further characterized by each said table rollers having a gradually decreasing radius, thereby permitting elongated elements being laterally transferred thereon to experience deceleration prior to being removed therefrom.

8. Apparatus for handling a succession of elongated elements moving axially along a given path, said apparatus comprising: transfer means defining a plurality of element-receiving channels, guide means for axially delivering one elongated element into one of said channels while directing the leading end of the next oncoming element into another of said channels; and, means for simultaneously adjusting both said guide means and said transfer means, the said adjustment permitting uninterrupted axial movement of at least one elongated element between said guide means and said transfer means while transferring elongated elements in said receiving channels laterally relative to said path.

9. The apparatus as claimed in claim 8 further characterized by means for covering the element-receiving channels into which elements are being directed by said guide means.