Search Images Maps Play YouTube News Gmail Drive More »
Sign in
Screen reader users: click this link for accessible mode. Accessible mode has the same essential features but works better with your reader.

Patents

  1. Advanced Patent Search
Publication numberUS3097591 A
Publication typeGrant
Publication dateJul 16, 1963
Filing dateNov 24, 1961
Priority dateNov 24, 1961
Publication numberUS 3097591 A, US 3097591A, US-A-3097591, US3097591 A, US3097591A
InventorsEdgar J Justus
Original AssigneeBeloit Iron Works
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Anti-deflection roll
US 3097591 A
Abstract  available in
Images(1)
Previous page
Next page
Claims  available in
Description  (OCR text may contain errors)

July 16, 1963 E. l JUsTUs 3,097,591

ANTI-DEFLECTION ROLL Filed Nov, 24, 1951 PRIDE ABT United States Patent O 3,097,591 ANTI-DEFLECTIN RGLL `Edgar J. Justus, Beloit, Wis., assigner to Beloit Iron Works, Beloit, Wis., a corporation 'of Wisconsin Filed Nov. 24, 1961, Ser. No. 154,801 8 Claims. (Cl. 10U-155) This invention relates to apparatus for mounting a roll whose centroidal axis is subject to deflection, and more particularly, to an apparatus lfor mounting a roll that is :subjected to a load .tending to effect central deflection of Vthe roll axis.

Although `the instant invention may be useful in a In paper machines there are a number of press couples, calender stacks, etc. the web passes through `ainipfbetween a pairof rolls whereat the web is subjected :to pressu-res. The pressures thusapplied to Vsuch nip tend `to `load `the rolls defining the nip and -to deflect the axes of these rolls in a direction generally away from the nip.

tlf one of the rolls defining a nip is backed up by other rolls or'other means, its tendency to deflect away from @the ,nip is reduced `or maybe completely overcome so that it is deected in-the directionof the nip. On the other hand, certain press rolls and, for example, the king roll or bottomroll in a calender stack may not be provided with backup means and the pressures or load thus `appliedito the nip for a calender stack king roll (as an example) tendsto deflect the samecentrally in a direction Aaway=from the load (which is usually downwardly) Such deflection results in anundesirable application of forces across lthe `nip and other undesirable operating features; and suchA deflection is often corrected' in paper machines by crowning of the king-roll. The crowning of the rollrequires-accurate and expensive finishing of the roll surface so -astoobtain a 4slightly greater roll diameter in the. Central portion ofthe roll; but such crowning is carrried out-on the -basis of a ,predetermined set of force conditions and-may not be satisfactory for operation under a dilferent-setofforce conditions. Accordingly, crowningiof rolls often does not afford satisfactory operation for many different-types -of operating conditions. In addition, the surface speed of the portion of the roll having a greater `diameteris actually faster than the surface `speed of ythe portion ofthe roll'having a relativelysmaller diameter, when `the roll is rotating, and Ithis difference in surface speeds ata'point of contact between the web and the roll (such as at a nip) may result in undesirable phenomena.

In arts such as the coating of paper or fabrics with plastic materials, pressure or calender rollsare also used. In addition, paint mixing .systems or the like -are also subject to `'the lbuild up of forces in `the central portion of pressure nips which tend to cause central deflection of the rolls and resultin non-uniform and/or other undesirable conditions across the width of such pressure nips.

`.It will be appreciated that one may think ofmost of these various pressure rolls in terms :ofthe outer annularly cross sectioned functional component or shell thereof. The instant inventioniaifords a simple but unique mounting :arrangement for a roll shell subject to a loa-d tending to cause deflection of its centroidal axis. One important aspect of the instantlinvention involves-the useof force couples for applying internal ,counter-deflection moments to the shell in response t-o the application of the load to the shell in such a manner as to more or less automatically resist or lminimize deliection of the roll when it is subr6 CC jected to varying loads. This is accomplished through the useof -allochiral mounting means cantileverly secured to theends of the shell, but extending inwardly from the ends of the shell at locations disposed inwardly of the shell ends `from the points at which these mounting means are secured to the ends of the shell, The mounting means are cantileverly mounted in that they are secured at or near the ends of the shell, but extend into the shell with- Y out being directly connected to the shell at their -inner ends, yby radially aligned means securing the inner ends of the mounting devices to an interior portion of the shell itself. These mounting means are allochiral in-that they are right hand and left hand members mounted at opposite ends of the shell (or looking-in the machine direction at opposite -sides of the roll shell). These members are referred to herein as allochiral for Ithe reason that they are opposed right and left hand assemblies although not necessarily entirely symmetrical -in every det-ail.

The ruse of a pair of bearings Vto rotatably `receive a stub shaft extending outwardly from the end of the roll `for the purpose of applying a force couple thereto, wherein one of the bearings is xed and the other movable, as shown in the prior art, for example, in Goulding vU.S. Patent No. 2,611,150. The Goulding mounting arrangement calls for a pair of bearings for each of the stub shafts at opposite ends of the roll. In addition, the prior art in the form of Hornbostel U:S. Patents Nos. 2,648,122 and 2,651,103 shows the mounting of va roll shell on a through shaft using mounting elements-that arepositioned 'inwardly from the ends of the shell, but which aiforda direct (radially aligned force) connection between the through shaft and the shell lat the mounting element positions inwardly from the Iends of the shell.

In the instant invention, however, the advantages of applying a counter-deflection moment to the shell are obtained without the necessity of using a pair of `bearings at each end of the roll, and without thenecessity of providing means forapplying a force couple to each of such pairs of bearings. The application of a counter-deflection moment to the shell in the instant invention is effected by the use of a unique and simple arrangement of allochiral mounting V( and force couple applying) means preferably inthe form of annular members which are secured to the ends of the shell but which extend inwardly rather than outwardly of the ends of `theshell.

The basic idea of the use of such .inwardly ,turned mounting members is disclosed and claimedin my application Serial No. 102,571, Vfiled April 12, 1961which is incorporated herein byreference. This is a continuationin-part of such application.

These mounting members are carried at a location Vvinwardly from their outer extremities ,and the Vends of the shell by means of allochiral shaft means which, in the present invention, are cantileverly mounted atopposite ends of the shell so as to extendinwardlyfromlhe shell to engage the inner ends of the hereinbefore described mounting means. Bearings are preferably provided at the-inner end of the allochiral shaft means ,forrotatabl-y supporting and engaging the inner ends of such mounting means; but it will be appreciated that the engagement between the inner ends of the mounting -means and the inner ends ofthe shaft means may be rigid or resilient, connected for corotation, if the outer ends of the allochiral shaft means are each cantileverlymounted on a plurality of bearings. Still Aanother advantage of the instant invention resides in the fact that, when the preferred arrangement of the invention is used with bearings providing for relative rotation between the inner ends of the Vallochiral shaft means and the inner ends of theV movement toward and away from the load applied to the roll shell. In this latter arrangement the roll shell itself may be loaded toward or away from an exterior load applied thereto merely by the application of force through movable means associated with the allochiral shaft means.

In any event, substantially the entire weight of the shell and any load applied thereto is carried by the cantileverly mounted allochiral shaft means at the previously described locations inwardly from the shell ends. And the internal mounting means (preferably annular mounting members) which are to effect the internal counter-deflection moments in the shell are mounted on and fully supported by the allochiral shaft means at the aforesaid locations inwardly from the shell ends, but these annular members are not connected directly to the interior of the shell radially opposite to the positions at which they are mounted on the shaft means. Instead, these annular mounting members extend outwardly from the locations at which they are carried by the shaft means and they are in turn cantileverly secured -to the shell at the ends thereof (although not necessarily the exact extremities of the shell) in such a manner that the internal counter-deflection moment is applied to the shell via these annular mounting members in response to the application of a load -to the shell. This results in a greatly simplified, sturdy assembly which is essentially self correcting with respect to its tendency to resist the normal deflection to which the conventionally mounted rolls are subjected under load.

Itis, therefore, an important object of the instant invention to provide an improved anti-deflection roll and/or anti-deflection assembly for the mounting of a roll shell subject to a load.

It is another object of the instant invention to provide an improved roll assembly wherein force couples are applied to effect internal counter-deflection moments via simple, sturdy and effective members positioned internally of the shell ends.

Yet another object of the instant invention is to provide a rotatable roll shell whose axis is subject to deflection in response to a load applied to said shell, allochiral mounting means each having an outer end rigidly and cantileverly secured to one end of the shell and having an inner end extending within the shell inwardly of the shell ends, and allochiral shaft means each having an outer end cantileverly mounted outside one end of the shell and extending within the shell to engage the inner end of the mounting means secured to such shell end and to thereby support the weight of said shell inwardly from the ends of the shell, thereby applying internal counterdeflection moments to said shell in response to the application of the load to said shell.

Other and further objects, features and advantages of the present invention will become apparent to those skilled in the art from the following detailed disclosure thereof and the drawings attached hereto and made a part hereof.

On the drawings:

FIGURE 1 is a diagrammatic illustration showing the two lower rolls of the stack of rolls, illustrating in exaggerated form the manner in which such rolls may be dellected during specific correlation among essential control factors in a calender stack of the prior art;

FIGURE 2 is a diagrammatic illustration similar to FIGURE l, but showing the roll shells in sectional elevation for an assembly embodying the invention;

FIGURE 3 is an essentially diagrammatic view showing the alignment of internal counter-deflection moments of the type effected in the operation of the assembly of FIGURE 2; and

FIGURE 4 is an essentially diagrammatic illustration of deflection curves involved in a consideration of Ithe instant invention.

As shown on the drawings:

In FIGURE l, .a bottom portion of a calender stack, indicated generally by the reference numeral 10, is shown comprising a king roll 11 at the bottom mounted on suitable bearings 12 and 13 which are in turn firmly secured to a fixed mounting such as a floor F. Immediately above the king lroll 11 is a calender roll 14 which, in turn, is mounted for rotation in bearings 15 and 16. Actually, the roll 11 is provided with a left hand stub shaft 11a or shaft element which is rotatably received by the left hand bearing 12 anda right hand stub shaft 11b which is rotatably received by the right hand bearing 13. The roll 14 is also provided with a left hand stub shaft 14a rotatably received by the left hand bearing `15 and a right hand stub shaft 14h rotatably received by the right hand bearing 16.

As will be noted, the axis X-11 for the roll 11 is deflected downwardly (shown in exaggerated manner) below a horizontal or center line C-11 at the middle of the roll 11 and this is caused by the load applied to the roll 11 by the weight of the roll 14 (and any other rolls thereabove). This weight is transmitted through the sheet of paper (shown in exaggerated thickness at W-1) passing through the nip N1 between the rolls 11 and 14. In the callender 10, however, the central portion of the top surface or the roll 11 is still crowned so as to extend a distance R-11 above the outer extremities of the roll 11, and the bottom surface of the roll 11 is downwardly bowed still a greater distance D11. 'Ihe amount of operating crown R-11 depends upon the amount of original crown formed on the roll 11 and the total weight `of the calender stack of rolls 14, etc. mounted thereabove. As will be appreciated, if it is desired to operate ,a calender with substantially no operating crown (R-11) in the king roll 11, the initial crown of the king roll 11 and the total weight of the calender rolls 14, etc. are correlated Iso as to obtain substantially no operating crown. If, however, it then becomes desirable to make a change in the operation of the prior art calender by using less calender rolls in the stack, then a greater operating crown R-11 will be obtained. This may possibly result in an undesirable pressure distribution at the portion of the web W-1 passing through the nip N-l. The same is true with respect to variations in load which may be applied to any other crowned roll in a paper machine or other device.

In many of such prior yart devices, the crown initially formed on the roll being subjected tothe load is just sufficient to permit the roll to deflect in response to this predetermined load to such an extent that the roll presents a ysubstantially flat (usually horizontal) nip defining surface. It will be appreciated that any variation from such predetermined load will, however, necessarily result in a deviation from the desired flat or level contour of the operating surface or nip defining line of the roll (herein designated 11C).

Referring now to FIGURE 2, it will be seen that the assembly 20 of the instant invention is adapted to mount a roll shell 21 whose centroidal axis in the unloaded condition of the roll (indicated at C-21 in FIGURES 2, 3 :and 4) is subject to deflection. As will be appreciated, lthe extent of deflection and crown has been greatly exaggerated in FIGURE l and will also be exaggerated in the description of FIGURES 2, 3 and 4 for the purpose of simplifying the nature of the disclosure. As indicated diagrammatically in FIGURES 2, 3 and 4, the axis C-21 is ,a center line for the shell 21 which would be `a substantially straight, horizontal line in the views shown, if the shell 21 were not subjected to any loading forces including the load of its own weight. The roll 21 is, however, subjected to a load across its entire width, including the load of its weight and the load of la first upper press roll 22 forming a press nip N-2 therewith.

As indicated in FIGURE 2, a web W-2 is trained through the nip N-2 lin the manner shown for the bottom two rolls of a calender stack. It will be appreciated that the nip N2 may also be a nip between two press rolls (such as the rolls 21 and 22) through which a felt may travel with or without a web thereon. For the instant purposes, however, ythe load is indicated diagrammatically as being applied uniformly .across the entire width (or length) of the shells 21 and 22, by the vuse of arrows 23a land 23h at the quarter points land 23e at the mid point. It will .beappreciated that the load V(Le. 23a, 23th, 23C, etc.) applied to the top of the roll 22 may resultffrom additional rolls ofa calender stack or it may result solely from Ithe weight .of the roll l2.2 itself; and this lload (23a, 2317, etc.) 4is assumed 4for the moment toibe applied uniformly across .the -top ofthe lower roll Z1 (although it will be appreciated that the actual numerical figures for the load, for example, in pounds per inch of nip width, will probably be different at -the top surface of the roll 21 from the load figures at the top` surface of the roll 22 which Vare i represented diagrammatically in FIGURE 2). It will alsobelappreciated that, as indicated diagrammatically in FIGURE 4, `in the caseof a conventionally mounted roll shell the 4load 23a, b, etc. `which is here assumed to be applied .uniformly across 4the nip N-2 at the top of the roll Z1 ,would result in Ia conventional deliection curve lX41 in Athe shell axis.

The shell 2.1 is, however, mounted in accordance with the instant invention on generally co-axially spaced, separate Yand independent allochiral shaft means or elements 24a .and 24h, which are held against rotation and Vfully supported by rfixed mounting blocks 25a and y25b, respectively.

Each of these cantileverly mounted shaft-elements 24a and.Z4b extends vfrom its cantilever mounting 25a and 2517, respectively, outside the ends 2i1d and 21e of the Shell 21a for the roll 21 appreciably axially inwardly of and radially spaced .from the shell '21a to approxi-mately the quarter points (which are lgenerallyaligned with the yforce arrows 23a and 23h). At the inner end of each of the shaft elements 24a and `24h are mounted` co-axially spaced allochiral annular bearing elements 26a and 2Gb. The .bearing elements 26a and 2Gb are shown diagrammatically since they may .lbe of conventional structure, but it will be understood that spherical roller bearing assemblies are preferredlfor use in the invention, since these bearing assemblies are known to be resistant to a radially applied load, but capable of limited yielding to a pivotal or momental movement of thetype described and desired herein.l

'The roll Z1-comprises a-generally annu-larly cross sectioned :functioning body portion or shell 21a plus generally co-axially spaced, allochiral turned-inmounting means or vendportions 2lb and 21C, respectively (which may be referred'to as sleevesor inner shells). .Although the shell 21a may be integrally formed with the yturned-in portions l2lb and I2t1c, in the embodiment here shown the end portions 2lb and 21C :are separate elements which are secured to the ends 21d andi-1e of the/shell 21a by means of bolts or similar means b. The turned-in ends 2lb and 211c'are cantileverly secured to and rigid with the respective endsZld and 21e of the shell 21 and extend appreciably 4 axiallyinwardl-y of the end portions of the shell,21 surrounding -butwithout engaging the shell 21 directly opposite 'their inner extremities Zlf and 21g, respectively `(i.e. soas to be radially spaced from the shell axially inwardly fromlsuch-ends). Instead, the inner extremities 2.11 and 21g `engage/the bearing assemblies 26a and 26h, respectively, and the entireweight of the roll 21, plus the load (23a, 23h, 23e, etc.) applied thereto is carried by the bearing assemblies 26a and 2Gb positioned interiorly vfrom the `ends of the shell 21a atapproxi-matelylthe quarter points. The

turned-in ends 2lb and 21C are'thus radially spaced from inner ends of the cantileverly mounted turned-in ends 2lb and y21C by the bearings 26a and 26th results in the creation of generally allochiral moments M-1 and .M-Z indicated diagrammatically in FIGURE 3; with the moment arm in each case being oneof the turned-in ends 2lb and 21C, respectively; the forces at the inner end of the moment arm being applied via the bearing assemblies 26a and 26h, respectively; and the opposite forces for the moment arms Ziband 21e being applied at the outer ends, here shown as the :arrows designated 21]' and 21k, respectively. Although the forces resisting the load applied to the roll 21 viathe bearing assemblies 26a and 26b are not applied directly to the interior of the shell 21a opposite the bearings 21a and 2lb, it will be appreciated that Iwithin the shell 21a there is created a secondary moment -M-1, shown at 'one side of FIGURE 3 and a secondary moment yl\/l-2 at the oppositeend of the roll, and this secondary moment is represented diagrammatically at the left hand side of FIGURE 3 by the oppositely directed arrows designated 21j and 26'a; and at the right hand side of FIGURE 3 by the oppositely directed arrows designated 26b and 21k. These secondary moments M-1 and M-2 are actually zapplied to the annular'bodyof the shell 21a so as to tend to bow the centroidal axis thereof upwardly in the middle, as indicated diagrammatically in FIGURE 3 by the dotted line MC. The dotted line MC which is also indicated in FIGURE irepresents in exaggerated manner the shape of the centroidal axis of the roll which might result if the only forces applied to the shell were those of the moments 4M-1 and ML2. `It will be appreciated, however, that a load (including the weight of the roll 21) is simultaneously being applied to the roll 21 tending to deflect the centroidal axis of the same downwardly along the line X-21 shownin FIGURE 4. The net result is a general cancellation -between the t-wo curves X-21 and MC, which results in aconiguration Y-21 shown in solid lines in FIGURE 4 that is actually a substantially straight line conforming A:generally with the true center line C-Zl, with very slight peaks RA and RBy at the quarter points.

As described in detail with mathematical calculations in my copending application Serial No. 102,571, led April :12, 1961,.-an increase in the overall load 23 applied to the top of the roll y21 results not only in a tendency to increase the deflection of the load cunve X-21, but alsoresults in a tendency to increase the upward deection curve MC resulting 'from the application of thecounter- `deflection moments, so the net result is little or no change in the final configuration Y-'Zl-ofthe roll axis. As shown in FIGURE A4 the configuration Y-Zl has greatly exaggerated peaks RA and RB, although in actual practice it will'be appreciated that such peaks are only a negligible distance,\if any, away from the true centerline C-Zl of the shell.

Ashere shown, in the case of the roll 21, the roll 21 may represent a'king or bottom roll in a calender stack and this is the roll which will ordinarily be driven and is ordinarily not mounted for movement toward and away from the other rolls of the stack. For this reason the roll 21 is shown on xed mountings 25a and 25h, although it will be appreciated that under appropriate circumstances the roll Z1 could besuitably mounted on bearings 26a and 2Gb which could be movedor urgedto a ylimited extent in one direction or another, in accordance with the mounting arrangement which ywill be described for the upper roll l22 hereinafter.

Also, it Vwill be noted that the mounting arrangement shown for the roll 21-fdoes permit suitable drive means therefor. Such drive means are here shown as comprising a suitable drive motor or other means, indicated diagrammatically at the box M, connected to a drive shaft 27 which extends through a bore 28 axially aligned through the mounting 25h and the cantileverly mounted shaft 24th. The drive shaft 27 is splined at its inner end 27a and-is received in a splined socket 29a in an internal head member 29 that is secured to the inner end 21g of the turned-in mounting memberlzlc. The-head 29-is, spaced )from the bearings 2612 and the inner end of the cantileverly mounted shaft 2411, so that the only mounting for the turned-in end 21C on the shaft element 2lb is lvia the bearing assembly 2Gb.

Referring now to the top roll 22 shown in FIGURE 2, it will be seen that this roll under no load at all has the theoretical centroidal axis or center line C-22, although it will be appreciated that the roll 22 is subjected to a load across its entire width, which may consist solely of the weight of the roll itself or, as indicated diagrammatically herein, consists of the weight of the roll itself plus the load 23 (i.e. 23a, 23b, 23e, ete.) which is assumed to be uniformly applied Vacross the top of the roll 22.

The shell 22 comprises a generally annularly cross sectioned functioning body portion 22a plus integral, allochiral turned-in end portions 22b and 22e, respectively. The shell 22 is here formed integrally with turned-in end portions 22h and 22C, for example, by conventional casting techniques for metal which result in the formation of such annularly cross sectioned turned-in (i.e. cantilevered) members 22b and 22e each encircling one of a pair of allochiral cantileverly mounted shaft elements 30a and 30h, which have mounted at their inner ends 31a and 3111 suitable bearing assemblies 32a and 32h respectively which engage the inner extremities 22d and 22e of the cantileverly mounted turned-in ends 22b and 22C of the roll 22.

As `will be appreciated, the effect -of the load 23 applied to the roll 22 (assumed for the moment to be mounted in the total absence of any counteracting forces from the roll 21) is to tend to cause an overall downward deflection in the centroidal axis comparable to the line X-2t1 indicated diagrammatically in FIGURE 4. In like manner, the cantileverly mounted turned-in ends 22b and 22e` will tend to create counterdeflection moments in the manner already described in connection with FIGURES 3 and 4 `as they relate to the roll 21. The net result is thus a centroidal axis for th-e roll 22 which will have the general configuration Y-21 shown in FIGURE 4.

An additional feature here shown in connection with the roll 22 (which will be -described in detail immediately hereafter) permits limited movement -or at least urging of the bearing assemblies 32a and 32b toward and away from the nip N-2. It will thus be appreciated that if forces are applied to the bearings 32a and 3219 tending to urge the same upwardly and away from the nip N-2, this may create what amounts to an increase in the load 23 applied to the top of the roll 22. It will be appreciated, of course, that if the load 23 is free to ride upwardly slightly as in the case of calender stack rolls, there may not be an overall increase in the effect of the load 23 against the top of the roll 22, and there would thus only be a slight decrease in the pressure applied by the roll 22 at the nip N-2 Vand against the bottom roll 21. If, however, the load =23 is effectively increased by the tendency to urge the bearlings 32a and 32h upwardly, then the self correcting effect of the mounting for the roll 22 will become apparent, for the reason that the moment curve in the roll will increase to counteract the tendency for the increase in the deflection curve, as already described in connection with FIGURE 4.

On the other hand, if it is desired to increase the pressure on the nip N-2, the net result will be what is comparable to a substantial reversal in the curves indicated in FIGURE 4, for the reason that the immovable bottom roll 21 may then function as the means for applying a substantially uniform load upwardly against the bottom of the roll shell 22. This will result in a substantially more uniform pressure across the width of the nip N-2, even though the total pressure across the width of the nip N-2 is increased. It will be appreciated that if the bearings for the roll 22 were mounted exteriorly of the ends of the shell 22a and the increase in load just proposed were applied to these bearings in this exterior lo-V cation, the net result would be a tendency to bend the outer ends of the axis of the roll downwardly and perhaps crush a paper web along the edges of the nip N-2 '8 without being able to apply adequate additional nip pressure in the middle of the nip N-2.

As indicated in FIGURE `2, the preferred method of applying the urging force to the bearings 32a and 32b against the roll 22 in either direction comprises a pivotal mounting for each of the cantileverly mounted shafts 30a and 30h. As here shown, allochiral uprights 35a and 35b are mounted to fixed supports such as the blocks 25a and 25h and carry at their upper ends pivots 36a and 36b, which in turn receive the exterior ends of the cantileverly mounted shafts 30a and 30b for pivotal or swinging motion.

Although the element or arm (here indicated at 37a and 37b, respectively) for effecting the necessary limited movement or force application to the pivotally mounted shaft means 30a and 30h may extend in alignment or at an angle to the axis of the shaft elements 30a and 30h, the arms 37a and 37b, respectively, are here shown as integral with the shaft means 30u and 30b, respectively, and extending upwardly. Force applying means 38a and 3Sb are indicated diagrammatically in FIGURE 2 acting upon the arms 37a and 37b, respectively. It Will be appreciated that the force applying means -may comprise diaphragms or suitable fluid actuated motors for limited movement and/or force application to the arms 37a and 37b, all of which fluid motor devices are well known in the art and need not be described in further detail herein.

It will be appreciated also that the overall assembly for the cantilever mounting and the force application or limited movement of the shaft element 30a is separate and independent for corresponding mounting for the shaft element 30h. This permits an additional selective variation in the operation of the assembly.

As here shown, the bearing assemblies 26a, 26b and 32a, 32h are mounted at substantially the quarter points for the shells 21 and 22 which they carry. These bearing assemblies need not be mounted precisely at the quarter point in each case, although it has been found preferable that they be mounted approximately at the quarter point. In any event, it will be appreciated that the bearing assemblies should be mounted inwardly from the ends of the shell substantially 20 to 30% of the shell length in order to obtain the desired application of internal counter-deflection moments to the shell in response to the actual application of load to the shell and/or the effective application of load to the shell as a result of limited movement of and/ or the application of forces to these bearing assemblies via the actuation of movable force applying means (eg. 38a and 38h) to the cantileverly mounted shafts (eg. `30a and 30h).

It will be understood that modifications and variations may be effected without departing `from the spirit and scope of the novel concepts of the present invention.

As used herein, the terms cantilevered and cantileverly refer to a supporting arrangement lfor a member mounted on a given base element wherein one portion of such member is secured to and supported by such base element and another portion of such member extends away from such one portion and is not otherwise secured to or supported by such base element, i.e., as in the mounting of a conventional cantilever beam.

I claim as my invention.

1. In combination, a roll shell Whose centroidal axis is subject to deflection in response to a load applied to said shell, separate and independent allochiral co-axially spaced shaft means in each end of the shell and rotatably mounting the shell, and allochiral co-axially spaced mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate the shell and the shaft means, each such mounting means being secured rigidly to the shell solely at its outer end and mounted on the shaft means solely at its inner end appreciably axially inwardly of the shell ends, each said mounting means being radially spaced from the shaft means axially outwardly from its inner end mounted on the shaft means and being radially spaced from the shell axially inwardly from its outer end secured to the shell, `thereby applying 'internal counter-deflection moments to said shell .in response to the application of a load to said shell.

2. In combination, a roll `shel-l whose centroidal axis is subject to defiection in response to a load applied to said shell, said shell having a substantial length-to-diameter ratio, separate and independent allochiral coaxially spaced shaft means in each end of the shell and radially spaced from the shell for rotatably mounting the shell, and allochiral co-axially spaced mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate the shell and the shaft means, each such mounting means being secured rigidly to the shell solely at its outer end and mounted on the shaft means solely at its inner end appreciably axially inwardly of the shell ends, each said mounting means being radially spaced from the shaft means axially outwardly from its inner end mounted on the shaft means and being radially spaced from the shell axially inwardly `from its outer end secured to the shell, thereby applying internal counter-deflection moments to said shell in response to the application of a load to said shell, said shell being supported from within solely on said shaft means via said mounting means.

3. In combination, a roll shell whose centroidal axis is subject to deflection in response to a load applied to said shell, separate and independent allochiral co-axially spaced shaft means in each end of the shell and radially spaced from the shell, co-axially spaced allochiral bearing means mounted on said shaft means lapprecialbly axially inwardly of the shell ends for rotatably mounting the shell, separate and independent allochiral support means connected to each said shaft means outside the ends of the shell, and allochiral co-axially spaced mounting means surrounding the shaft means and extending appreciably Iaxially inwardly of each of the shell ends intermediate the shell and the shaft means, each such mounting means being secured rigidly Ito the shell solely at its outer end and mounted on the shaft means lvia said bearing means solely at its inner end `alpprecialbly axially inwardly of the shell ends, each said mounting means ybeing radially spaced ffrom the shaft mea-ns axially 4outwardly from its inner end mounted on the shaft means :and being radially spaced from the shell axially inwardly from its outer end secured to the shell, thereby applying internal counter-deection moments to said shell in response to the `application of a load to said shell.

4. In combination, a roll shell whose centroidal axis is subject to deflection in response to a load applied to said shell, separate and independent allochiral co-axially spaced shaft means in each end of the shell and radially spaced from the shell, allochiral movable means connected to said shaft mea-ns beyond the shell ends and accommodating limited relative movement between the allochiral shaft means, co-axially spaced allochiral bearing means each carried by one of said allochiral shaft means appreciably axially inwardly of the shell ends for rotatably mounting the shell, and allochiral co-axially spaced mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate Ithe shell and the shaft means, each such mounting means being secured rigidly to the shell solely at its outer end and mounted on the shaft means via said bearing means solely at its inner end apprecialbIy axially inwardly of the shell ends, each said mounting means being radially spaced Ifrom the shaft means axially outwardly from its inner end mounted on the shaft means and being radially spaced from the shell axially inwardly from its outer end secured to the shell, thereby applying internal counter-deection moments to said shell in response to the application of a load to said shell, said shell :1.0 4being-supported fnom 'within solely `on said -shatmean's via said mounting means .and said bearing means.

5. In combination, a roll shell whose centroidal axis is subject to ideectioniin response `to a load applied to said shell, separate 4and independent allochiral co-axially spaced shaftmeans in each end 'of the shell and `radially spaced from Vthe shell, allochiral supportmeansswingably mounting saidsha'ft means beyond the shell ends and accommodating limited relative movement between the allochiral shaft means, co-axially spaced allochiral bearing means each canried by one of said allochiral shaft means appreciably axially inwardly ofthe shell ends for rotatably mounting the shell, and allochiral coaaxially spaced mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate Ithe shell and the shaft means, each such mounting means being secured rigidly to the shell solely at its outer end and mounted on lthe shaft means via said bearing means solely at its inner end appreciably axially inwardly of the shell ends, each said mounting means being [radially spaced from the shaft means axially outwardly `from its inner end mounted lon the shaft means and being radially spaced from the shell axially inwardly from its outer end secured to the shell, thereby -applying internal counter-deection moments to said shell in response to the application of a load to said shell, said shell being supported from within solely on said shaft means via said mounting means and said bearing means.

6. In combination, a roll shell whose centroidal axis is subject to deflection in response to a load applied to said shell, a second troll in nip-defining relationship with said shell and applying a load to said shell tending to effect such deflection, separate and independent allochiral coaxially spaced shaft means in each end of the shell and nadially spaced from the shell for rotatably mounting the shell, and allochiral cosaxially spaced mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate the shell and the shaft means, each such mounting means being secured rigidly to the shell solely at its outer end and mounted on fthe shaft means solely at its inner end appreciably axially inwardly of the shell ends, each said mounting means being radially spaced from the shaft means axially outwardly from its inner end mounted on the shaft means and being radially spaced from the shell axially inwardly from its outer end secured to the shell, thereby 4applying internal counter-deiiection moments to said shell in response to the application of a load to said shell.

7. The combina-tion of two polls claimed in claim 6 wherein each such nells is separately .and independently mounted on separate and independent aliochinal co-axially spaced shaft means in each end of the shell and radially spaced 'from the shell, co-laxially spaced allochiral bearing means mounted on said shaft means appreciably axially inwardly of the shell ends for rotatably mounting the shell, sepamate and independent allochinal support means connected to each said shaft means outside the ends of the shell, and 4allochiral co-axially spaced mounting means surrounding fthe shaft means and extending appreciably 4axially inwardly of each of the shell ends intermediate the shell and ythe shaft means, each such mounting means 4being secured rigidly to `the shell solely at its outer end and mounted on the shaft means, via said bearing means 'solely at its inner end appreoiably axially inwardly of the shell ends, each said mounting means being nadially spaced from the shaft means 'axially outwardiy from its inner end mounted on the lshaft means and being radially spaced from the shell axially inwandly from its outer end secuned to the shell, thereby applying internal counter-deiiection moments to said shell 'in response lto the application of a load to said shell.

8. The combination of rtwo rolls claimed in claim 7 wherein means are provided on said support means for 1 1 effecting limited relative movement between the allol 2,611,150 chiral shaft means for at least one of said rolls. 2,648,122 2,651,103 References Cited in the le of this patent UNITED STATES PATENTS 5 2,404,269 Bennett July 16, 1946 801,814

2,587,627 Kauiman Mar. 4, 1952 12 Goulding Sept. 23, 1952 Hombostel Aug. 11, 1953 Hornbostel Sept. 8, 1953 FOREIGN PATENTS Great Britain Sept. 24, 1958

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2404269 *Mar 13, 1945Jul 16, 1946Bennett Hilda MaryWheel for vehicles
US2587627 *Dec 26, 1944Mar 4, 1952Lovell Mfg CoWringer
US2611150 *Apr 26, 1949Sep 23, 1952Wingfoot CorpApparatus and method for performing sheeting or coating operations on or with plastic material
US2648122 *Aug 4, 1950Aug 11, 1953Beloit Iron WorksAntideflection roll
US2651103 *Apr 9, 1948Sep 8, 1953Beloit Iron WorksAntideflection roll assembly
GB801814A * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3273492 *Oct 16, 1963Sep 20, 1966Beloit CorpSuction roll counter-deflector
US3512727 *Mar 13, 1968May 19, 1970Valmet OyPressure roll beam in a longitudinal sheet cutter
US3611917 *Jun 3, 1968Oct 12, 1971Dominion Eng Works LtdCalender stack with swimming roll
US4372205 *Oct 3, 1980Feb 8, 1983M.A.N.-Roland Druckmaschinen AktiengesellschaftApparatus for bending a pressure roll of a rotary printing press
US4487122 *Nov 4, 1983Dec 11, 1984Gravure Research Institute, Inc.Deflection compensating roll for providing uniform contact pressure
US4635861 *Feb 7, 1985Jan 13, 1987Gebruder Buhler AgRoller mill
US4658621 *Dec 3, 1984Apr 21, 1987Sulzer-Escher Wyss AgRolling apparatus
US5291826 *Mar 26, 1992Mar 8, 1994J. M. Voith GmbhTension bars for roll press for paper making machine
US8206277 *Jun 26, 2012Hewlett-Packard Development Company, L.P.Idler roller assembly having a roller and a shaft the roller being formed such that it remains parallel to contacted media despite deflection of the shaft
US8312909Apr 14, 2008Nov 20, 2012Futura S.P.A.Device for treating paper webs
US20090273133 *Oct 27, 2008Nov 5, 2009Sutton Donald CRoller
US20100181040 *Apr 14, 2008Jul 22, 2010Fabio PeriniDevice for treating paper webs
DE3040891A1 *Oct 30, 1980May 14, 1981Beloit CorpNasspresse mit laenglichem pressspalt
DE10058272B4 *Nov 23, 2000Jun 9, 2005Oskar Dilo Maschinenfabrik KgWalze einer Arbeitsmaschine
DE10226720A1 *Jun 14, 2002Jan 8, 2004Kampf Gmbh & Co MaschinenfabrikLagerung für Walzen von Rollenschneid- und Wickelmaschinen
DE10341119A1 *Sep 5, 2003Mar 31, 2005Voith Paper Patent GmbhBreitstreckwalze
EP0149108A2 *Dec 6, 1984Jul 24, 1985Sulzer-Escher Wyss AGRoller assembly
EP1371587A2 *Jun 12, 2003Dec 17, 2003Kampf GmbH & Co. MaschinenfabrikBearing for rollers of slitting or winding machines
WO2009010999A1 *Apr 14, 2008Jan 22, 2009Futura S.P.A.Device for treating paper webs
Classifications
U.S. Classification100/155.00R, 100/162.00B, 492/7
International ClassificationB65H27/00, D06C15/08, D21G1/02, D06B23/02, F16C13/00
Cooperative ClassificationB65H2404/1372, B65H2404/14, F16C13/024, D06B23/021, D21G1/0206, B65H27/00, B65H2404/1371, D06C15/08
European ClassificationF16C13/02H2, D21G1/02B, B65H27/00, D06B23/02C, D06C15/08