US3138089A

US3138089A - Anti-deflection roll

Info

Publication number: US3138089A
Application number: US250423A
Authority: US
Inventors: Shelton J Fred
Original assignee: Beloit Corp
Current assignee: Beloit Corp
Priority date: 1963-01-09
Filing date: 1963-01-09
Publication date: 1964-06-23
Anticipated expiration: 1981-06-23

Description

June 23, 1964 J F. sHELToN ANTI-DEFLECTION ROLL 4 Sheets-Sheet l Filed Jan. 9, 1963 INVENTOR. Jfaed YZQZOZ ATTORNE S June 23, 1964 1 F. sHELToN 3,138,089

ANTI-DEFLECTIONROLL Jaed fzgaaojz A TORNE YS June 23, 1964 j F, SHELTON 3,138,089

ANTI-DEFLECTION ROLL Filed Jan. 9, 1963 4 Sheets-Sheet 3 INVENTOR @2f @f 45 Jfiqed ne/m72 BY w Af/TOREYS June 23, 1964 Filed Jan. 9, 1965 J F. SHELTON 3,138,089

ANTI-DEFLECTION ROLL 4 Sheets-Sheet 4 A TTORNE YS United States Patent O 3,138,089 ANTl-DEFLECTIUN RLL .l Fred Shelton, Beioit, Wis., assigner to Beloit Corporation, Beloit, Wis., a corporation of Wisconsin Filed Jan. 9, 1963, Ser. No. 250,423 17 Claims. (Cl. 100-162) This invention relates to apparatus for mounting a roll whose centroidal axis is subject to deection, and more particularly, to an apparatus for mounting a roll that is subjected to a load tending to effect central deflection of the roll axis.

Although the instant invention may be useful in a number of arts, including textile treating or calendering, plastic handling and sheet metal handling industries, the invention is particularly useful in the paper making art and will be described primarily in connection therewith. In general, the instant invention relates to apparatus for mounting a roll shell having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to the loads applied to a shell during use. In paper machines there are a number of different types of rolls, of substantial size (i.e. substantial length) which are subjected to loads tending to deflect such rolls generally. For example, in press couples, calender stacks, etc. the web passes through a nip between a pair of rolls whereat the web is subjected to pressures. The pressures thus applied at such 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. If 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 may be completely overcome so that it is deliected in the direction of the nip. On the other hand, certain press rolls and, for example, the king roll or bottom roll in a calender stack may not be provided with backup means and the pressures or load thus applied to the nip for a calender stack king roll (as an example) tend to deflect the same centrally downwardly. Such deflection results in undesirable application of forces across the nip and other undesirable operating features; and such deflection is often corrected in paper machines by crowning of the king roll. The crowning of the roll requires accurate and expensive finishing of the roll surface so as to obtain a slightly greater roll diameter in the central portion of the roll; but such crowning is carried out on the basis of a predetermined set of force conditions and may not be satisfactory for operating under a different set of force conditions. In addition, a crowned roll will have a somewhat greater circumference in the crowned region (usually at the center) than at the uncrowned regions of the roll, and this results in a slightly greater surface speed at the outer periphery of the roll in the crowned region. Such surface speed differences in the operation of certain nips result in undesirable operating characteristics in many instances, It will thus be seen that crowning of rolls often does not afford satisfactory operation for many different types of operating conditions.

It Will be appreciated that one may think of most of these various pressure rolls in terms of the outer annularly cross-sectioned functional component or shell thereof. The instant invention affords a simple but unique mounting arrangement for a shell subject to a load tending to cause deection of its centroidal axis. An important aspect of the instant invention involves the use of force couples for applying internal counter-deflection moments to the shell in response to the application of the load to the shell in such a manner as to more or less automatically resist or minimize deflection of the roll when it is subjected to various loads. This is accomplished through the use of allochiral mounting means secured to the ends of the shell, but extending inwardly from the ends of 3,138,089 Patented June 23, 1964 the shell to be supported at locations disposed inwardly of the shell ends from the points at which these mounting means are secured to the ends of the shell. 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 of a paper machine at opposite sides of the roll shell). These members are referred to herein as allochiral for the reason that they are opposed right and left hand structures although not necessarily entirely symmetrical in every detail. The general concept as well as more specific aspects of this type of roll shell mounting arrangement are described in copending applications of Edgar l. Justus Serial No. 102,571, filed April 12, 1961 (now U.S. Patent No. 3,097,590) and Serial No. 154,801, led November 24, 1961 (now U.S. Pat-ent No. 3,097,591) which are owned by the assignee of the instant invention and which disclosures are incorporated herein by reference.

The instant invention aifords a unique improvement in l roll shell mounting structures embodying the basic concepts of the aforesaid Justus roll structures. Although in use the roll shells and their mounting structures are of suicient size and complexity to make analyses of the various forces involved comparatively difficult, it has been found that the application of such internal counterdeflection moments to the shell via the internal allochiral mounting means or annular internal shell means results in the generation of localized, substantial force moments at connections between the roll shell ends and such mounting means and/or the inwardly positioned connections between such mounting means and the shaft means, and such localized moments tend to reduce the operating life of roll supporting arrangements of this type. The proposal, for example, in the aforesaid Justus application Serial No. 102,571, in FIGURE 5 thereof, concerning the use of solid elastomer or the like elements interposed between the allochiral mounting means and the shaft means has helped to solve this problem; but the instant invention affords an improved solution to the problem, which also broadens the area of potential use for the instant roll shell mounting structures. In the instant invention, assemblies in the form of a plurality of generally radially aligned axially thin flexible juxtaposed laminae are mounted at the aforesaid positions of localized high force moments; and the use of such structures in the locations indicated results in a substantial increase in the operating life of the instant roll mounting structures, and it also makes possible the use of heat exchange fluids within the shell for at least limited control of the operating temperatures for the roll and the shell surface. Although it is not desired to limit the invention to any particular theory, it is believed that the aforesaid laminate assemblies possess the unique property of fully supporting radially aligned loads while accommodating relative tilting to a limited extent between the axes 0f the shaft means and the axes of the allochiral mounting means (and, therefore, the axis of the shell per se). Moreover, the aforesaid laminate assemblies are preferably made of thin flexible metal laminae which are not particularly affected by temperature changes and/or heat exchange fluids used for effecting temperature changes. Such laminate assemblies have been found to abosrb not only the type of localized high force moment that is continuously generated during rotation of the shell by virtue of a tendency toward slight misalignment between the axes of the shell and shaft means` but also these laminated assemblies are particularly well adapted to absorb force moments generated by the differences in coeflicients of thermal expansion which might be involved in the materials used in the roll shell mounting structure and/ or temperature changes which may occur during operation so as to effect relative expansion or shrinkage among the various structural elements of the overall roll arrangement.

It is, therefore, an important object of the instant invention to provide an improved roll mounting structure.

It is another object of the instant invention to provide an improved arrangement for mounting a roll shell having a substantial lengthto-diameter ratio in order to correct for tendencies toward deflection of the roll shell axis as a result of loads applied thereto.

Yet another object of the instant invention is to provide a roll shell having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in `response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto for rotatably mounting the shell, a plurality of generally radially aligned axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, and allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-de- Flection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

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 l is a diagrammatic illustration showing a rolled shell in sectional elevation for an assembly embodying the invention;

FIGURE 1A is a diagrammatic view of a conventional calender stack of the type described in the aforesaid Justus patents, showing the roll 11 of FIGURE 1 as the king roll;

FIGURE 2 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 1;

FIGURE 3 is an essentially diagrammatic illustration of deflection curves involved in a consideration of the instant invention;

FIGURE 4 is a fragmentary detail sectional elevational view showing the roll structure at the right hand end of the shell in FIGURE 1;

FIGURE 5 is a detail elevational view showing the mounting of the inner shell means on the shaft means taken from the rear of the view shown in FIGURE 4;

FIGURE 6 is a fragmentary detail view taken substantially along the line A-A of FIGURE 4;

FIGURE 7 is a fragmentary detail View taken substantially along the line B-B of FIGURE 4; and

FIGURE 8 is a fragmentary detail view of the steel sandwich or laminate assembly of the invention taken generally along the line C-C of FIGURE 4.

As shown on the drawings:

In FIGURE 1, it will be seen that the assembly of the instant invention, indicated generally by the reference numeral 10 is adapted to mount a roll shell 11 whose centroidal axis in the unloaded condition of the roll (indicated at C-11 in FIGURES 2 and 3) is subject to dellection. As will be appreciated, the extent of deflection and crown has been greatly exaggerated in FIGURES 2 and 3 for the purpose of simplifying the nature of the disclosure. As indicated diagrammatically in FIGURES 2 and 3, the axis C-11 is a centerline for the shell 11 which would be substantially straight and horizontal in the View shown, if the shell 11 were not subjected to any loading forces including the load of its own weight. The shell 11 is, however, subjected to a load across its entire width, including the load of its weight and the load of an upper press roll or a plurality of superimposed calender rolls not `shown but indicated diagrammatically by the arrows 12a and 12b at the quarter points and 12e` at the center of the shell in the region of a press nip N-l that is formed with the upper peripheral surface of the shell 11. It will be appreciated that the load applied across the nip N-l would ordinarily be substantially uniform for each unit of width across the full width of the roll, but the overall load is indicated here diagrammatically only by the arrows 12a, 12b and 12C. As indicated diagrammatically in FIGURE 3, in the case of a conventionally mounted roll shell the load 12 would result in a conventional deflection curve D-11 in the roll shell axis. As indicated in FIGURE 1A, the load may be applied in a calender stack by

superimposed rolls

101, 102, 103 and 104.

The shell 11 is, however, mounted in accordance with the instant invention on shaft means here indicated as a through shaft 14 coaxially received by the shell 11 and extending completely therethrough for rotatably mounting the shell 11. The ends of the shaft 14a and 14b, respectively, extending outwardly from the ends 11a and 11b of the shell 11 are suitably mounted for rotation in bearings shown diagrammatically at 15 and 16 suitably mounted in

bearing housings

17 and 18.

The through shaft means 14 is advantageously formed of end portions 14a and 14b of reduced size received by the bearings 15 and 16 and an enlarged central portion 14C providing greater structural strength. In the embodiment of the instant invention, it will be seen that the bearings 15 and 16 may be in the form of only a single bearing at each end of the roll shaft 14 suitably mounted in

xed housings

17 and 18 in the case of the through shaft 14, as shown. Also, it may be advantageous in certain instances to be able to apply force couples to the through shaft 14 as shown, and this is done by the use of pairs of bearings indicated diagrammatically at 15a and 15b at one end and diagrammatically at 16a and 16b at the other end mounted in the

housings

17 and 18 which may be mounted for limited movement about pivots 19 and 20, respectively, and equipped with suitable moving, force applying means indicated diagrammatically at 21 and 22 for effecting limited pivotal movement of the

housing

17 and 18 and thereby applying force couples to the shaft 14 via the pairs of bearings 15a, 15b at one end and 16a, 16h at the other end. It will also be appreciated that the shaft means 14 may be divided into two allochiral sections rather than a through shaft, with these sections extending inwardly an appreciable distance in order to mount the shell 11 in the manner shown in FIGURE 1; and in such instance the bearing pairs 15a, 15b and 16a, 16h would ordinarily be provided for cantileverly mounting such separate, allochiral shaft means. These various structures for mounting the shaft means are described in detail in the aforesaid Justus applications.

It will be seen that the ends 11a and 11b of the shell 11 are provided with annular heads 23 and 24 secured in the ends of the shell 11 by conventional means such as the threaded bolts indicated, for rigid assembly with the shell 11. The heads 23 and 24 may and preferably do extend to close running relation with the reduced end portions 14a and 14b of the shaft means 14 and 0 ring seals 25 and 26 held in position by annular glands 27 and 28, respectively, cooperate with the inner periphery of the heads 23 and 24 to form a suitable seal with the reduced end portions 14a and 14b of the shaft 14 so as to provide a sealed chamber X within the shell 11.

The specific aspects of the mounting for the shell 11 on the shaft means 14 will be described in greater detail hereinafter; but it is important to note that this mounting arrangement is particularly advantageous in that it is adapted to be structurally operative over a substantial temperature range and in the presence of heat exchange fluids such as steam, refrigerants, etc. which may be fed into o1' passed through the chanber X within the shell 11.

Although any conventional means for feeding heat ex change fluid into the chamber X and for withdrawing the same therefrom may be used in the practice of the instant invention, it is preferable that such means be arranged co-axially with the shaft means. One conventional type of arrangement is shown diagrammatically in FIGURE 1, wherein steam from a suitable source S is fed through a conventional inlet line 3i? through the housing 17 and into an axial bore 31 in the shaft via a conventional rotary (and flexible, if necessary) connection at 32, in well known arrangements indicated only diagrammatically herein. The steam passes through the axial bore 31 in the shaft means 14 and then through radial outlets (indicated diagrammatically at 33) into the chamber X and in the chamber X the steam is applied directly to the interior of the metal shell 11 so as to effectively control at least to some extent the temperature of the shell 11, and particularly the temperature of the shell at the nip N-l or the operating outer peripheral surface of the shell 11. Condensate is then removed by a conventional diper 34 feeding up through a radial tube 3S into a conventional condensate line 36 concentric with the axial bore 31 and feeding back out through a conventional rotary connection at 37 and into a condensate receptacle C. It will be appreciated that cooling liquid or refrigerant can also be passed through the chamber X in a comparable manner using comparable structures for purposes of controlling the shell temperature by cooling.

It will be appreciated that the various methods of mounting the shaft means 14 hereinbefore described as well as the various methods of introducing and removing heat exchange lluids into an operating roll shell are not as such a part of the instant invention but the instant invention provides a mounting means which is uniquely adapted for using and obtaining the advantages of the use of these various structural and operational devices.

It will also be seen that the end heads 23 and 24 on the shell 11 mount allochiral mounting means in the form of inner shells 49 and 41 in rigid assembly with the heads 23 and 24, respectively, being secured thereto by suitable means such as the threaded bolts indicated in FIGURE 1 at 40a and 41a, respectively. As such the allochiral

inner shells

40 and 41 are cantileverly mounted on the shell 11. As used herein, the terms cantilevered and cantileverly refer to a supporting arrangement for 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 or supported by such base member i.e., as in the mounting of a conventional cantilever beam. It will be seen that the shaft means 14 is radially spaced from the interior of the shell 11 and the allochiral mounting means or

inner shells

40 and 41 are secured solely to the shell 11 at the ends thereof via the heads 23 and 24 forming a rigid connection. The

inner shells

40 and 41 thus extend from this cantilever mounting on the heads 23 and 24 appreciably, axially inwardly from the shell ends between and radially spaced from the shell 11 and the shaft means 14. As here shown, the inner shells 46 and 41 extend inwardly approximately to the quarter points of the shell 11, at which locations the inner shells 4t) and 41 are secured to

assemblies

42 and 43 each formed of a plurality of generally radially aligned axially thin flexible juxtaposed laminae which are in turn mounted on the shaft means 14 via

rings

44 and 45, respectively, in rigid assembly with the shaft means 14.

Referring now specifically to the detail view of FIG- URE 4, it will be seen that the annular head 24 is in rigid assembly with the shell end 11b via a plurality of peripherally spaced threaded bolts 24a, 24a, etc.; and the head 24 is secured by another plurality of peripherally spaced

bolts

41a, 41a to the outer end 41h of the inner shell or mounting means 41. A suitable lightweight shield 50 covers the bolt heads. In FIGURE 4 the gland 2S and O-ring seal 26 providing a seal between the shaft portion 14b in the head 24 are shown in greater detail.

The inner shell 41 is preferably of a solid, annular crosssection as here shown, but it may have other structures of sufcient strength to carry out the function here contemplated, so long as the mounting means 41 extend from the rigid cantilever mounting on. the head 24 axially inwardly appreciably, and While intermediate and in spaced relation (radially) with respect to the shaft means 14 and the inner periphery 11x of the shell 11. The inner vshell 41 is thus one of two allochiral, co-axially spaced'mounting means (40 and 41), which, is secured rigidly to the shell 11 solely at its outer end 41h and radially spaced from the shell axially inwardly from its outer end 41b; and as will be explained, the inner shell 41 is mounted on the shaft 14 solely at its inner endl 41C and radially spaced from the shaft 14 axially outwardly from its end 41C.

At the inner end 41C of the inner shell 41, it Will be seen from FIGURES 4 and 6 that the generally annular, radially aligned face (shown fragmentarily in FIGURE 6) is provided with peripherally spaced' alternating recesses 61a, 6112, 61C, etc. and projections 62a, 621;, 62C, etc. (which are shown in section in the elevational view of FIGURE 6), but which are each provided with threaded apertures 63a, 63b, 63C, etc. for receiving threaded bolts 64a, 64b, etc. In comparing FIGURE 4 and FIG- URE 6, it will be seen that, in the upper sectional view of the inner shell 41 in FIGURE 4, the recess 61aA is shown, while in the lower sectional view of the inner shell 41 in FIGURE 4 the projection 62]c is shown with the threaded aperture 63f receiving the threaded bolt 64f therein.

Referring to FIGURE 8 it will be seen that this view shows a fragmentary elevational view of the steel sandwich or laminate assembly indicated generally at 43, taken along the line C-C of FIGURE 4, showing a plurality of peripherally spaced holes for receiving the bolts of the 64 series, such holes being designated in the 65 series by the same letters of the alphabet. It will thus be seen that the peripherally spaced bolts of the 64 series secure the steel sandwich 43 to the generally radially aligned inner face of the inner shell 4t), in rigid assembly by the bolts of the 64 series.

Next, comparing FIGURES 4 and 7, it will be seen that the shaft means 14 mount a generally radially aligned annular head 45. The head 45 has a generally radially aligned face 45a shown in elevation in FIGURE 7 which generally opposes the radially aligned face at the inside end of the inner shell 41 and the face 45a of the head 45 is provided with a plurality of recesses 66a, 66h, etc. which are peripherally spaced and positioned toV receive the heads on the bolts of the 64 series previously described. Intermediate the recesses of the 66 series on the face 45a of the head 45 there are peripherally spaced

projections

671', 67j, 67k, etc. each being provided With a threaded aperture 681", 68]', etc. (indicated alphabetically) for receiving a threaded bolt designated by the corresponding letter of the alphabet in the 69 series. It will thus be seen that in the lower right hand portion of FIGURE 4 the recess 66]c is shown accommodating the bolt head for the bolt 64f; and in the upper right hand portion of FIGURE 4 the head 45 is shown insection with the projection 671' having the threaded apertures 681' receiving the threaded bolt 691', which has a bolt head 701' that is received in the previously described recess 61a of the inner shell. The bolt 691l is also provided with a threaded nut 711', and it passes through a suitable aperture 721 in the steel sandwich 43. The various other peripherally spaced apertures of the 72 series that are positioned intermediate the apertures of the 65 series in the steel sandwich 42 are shown in FIGURE 8.

The bolts of the 69 series thus secure peripherally spaced portions of the steel sandwich 42 (alternating between the peripherally spaced portions secured to the inner shell 41) to the shaft ring 45 in rigid assembly. The shaft ring 45 is also mounted in rigid assembly on the shaft 14, e.g. via the key indicated at 73 in FIGURE 4.

It will thus be seen that the steel sandwich or assembly 43 is secured (rigidly) to the inner shell 41 by bolts 69 peripherally spaced from the bolts 64 and also spaced from the ring 45, shaft 14 and shell 11 (such that the bolts 69 are connected solely to the inner shell 41 and the sandwich 43); and the steel sandwich is secured (rigidly) to the shaft ring 45 by bolts 64 peripherally spaced from the bolts 69 and also spaced from the inner shell 41 and shell 11 (such that the bolts 64 are connected solely to the steel sandwich 43 and the ring 45).

Referring briefly to FIGURE 5, it will be seen that this shows a full elevation view of the inner shell 41 mounted on the shaft 14, in a view which may be considered to be taken from behind the corresponding elements shown in FIGURE 4, which is thus a view that fshows the peripherally spaced bolt series 64 and 69 which are employed with the elements shown in FIGURES 6 through 8.

Referring again briefly to FIGURES l, 2 and 3, it will be seen that the weight of the shell proper 11, and the load 12 applied thereto, is carried flrst in its entirety on the

inner shells

40 and 41 via the rigid connection thereto afforded by the heads 23 and 24. Next, it will be seen that the entire load of the shell 11, load 12, heads 23 and 24 and

inner shells

40 and 41 is carried solely, and

4appreciably axially inwardly from the shell ends by the co-axially spaced

allochiral sandwich assemblies

42 and 43, with which the

inner shells

40 and 41 are rigidly connected. The

sandwich assemblies

42 and 43 are also rigidly connected to the shaft 14 via the

rings

44 and 45 in the manner hereinbefore described. The

sandwich assemblies

42 and 43, however, form a bridge between their (rigid) connections to the

rings

44 and 45 and their (rigid) connections to the

inner shells

40 and 41, respectively, so that the

sandwich assemblies

42 and 43 may resist the radial load applied thereto, while still being capable of limited flexing or resilience in other directions.

It will thus be appreciated that in the embodiment of FIGURE l, the shell 11 is supported interiorly or from within solely on the shaft 14, via the

inner shells

40 and 41 and the

sandwich assemblies

42 and 43. This arrangement results in generally allochiral moments M-1 and M-2 indicated diagrammatically in FIG. 2. As indicated in FIGURE 2, the left hand moment M-l is developed initially in the annular sleeve 40 by virtue of the downward radial force component in the head 23 (carrying approximately one-half of the load of the shell 11) and the upward resisting radial force component at the center line of the sandwich assembly 42. Although there is no direct radially aligned connection between the sandwich assembly 42 and the middle interior of the shell, indicated at llc, the moment or force couple M-1 necessarily results in the formation of a corresponding moment -1 in the main shell body 11c, which may be indicated diagrammatically in FIGURE 2 by the

force couple arrows

42 and 42. The corresponding force arrangement for the opposite moment M-2 is also indicated in FIG- URE 2.

It will be appreciated that the resulting end moments M'-1 and M2 acting on the body of the shell 11 tend to bow the shell 11 upwardly in the center portion 11e` as indicated in dotted lines at 11e in FIGURE 2 on the exaggerated deflection curve MC resulting7 from such end moments, which curve is also shown in the diagram of FIGURE 3 in contrast with the conventional deflection curve D-11. It will also be appreciated that the greater the overall load 12 that is applied to the working surface (at N-1) of the shell body, the greater the end moments M-1 and M-Z, and thus the greater the tendency for the end moments to bow or deflect the shell body upwardly at the central portion 11e thereof. This is thus the theoretical explanation for the self-correcting character of the instant roll assembly in response to variations in the load applied to the shell. In other words, if the load increases the so-called normal deflection curve D-11 (referring to FIGURE 3) would deflect downwardly to a greater extent, but the end moments would also increase and this would result in the automatic correction effect of this assembly whereby the end moment deflection curve MC is moved upwardly, in the diagramamtic showing of FIG- URE 3. In each case, the two curves D-11 and MC substantially cancel each other out and the centroidal axis of the shell, indicated in a solid line R-11 in FIGURE 3, assumes a substantially straight line configuration conforming generally with the true center line C-11, with various light peaks RA and RB at the quarter points. These so-called peaks RA and RB are actually so small as to be negligible in most uses, even though they represent the maximum final deflection from the true center line C-11. It has been found that the self-correcting counter deflection effect is obtained in the most advantageous manner if the rigid connection between the shell 11 and the inner

annular members

40 and 41 is made substantially at the extremities of the shell (here via the heads 23 and 24) and the entire load is transmitted from such

annular shell members

40 and 41 to the shaft 14 at approximatey the quarter points of the shell 11 (and preferably appreciably axially inwardly about 20 to 30% from the opposite ends of the shell 11).

It will be appreciated that the axis of the shaft 14 will tend to tilt or slope downwardly from the supporting bearing means 16, for example, toward the middle of the shaft 14 (generally as indicated along the line D-11 in FIGURE 3) as a result of the total load applied to the shaft 14; and the axis of the annular inner shell 41 at the right hand side of FIGURE l will tend to tilt or slope downwardly in the opposite direction (or outwardly toward the supporting bearing means 16 by virtue of the moment M-2 applied thereto), so the sandwich assembly 43 thus resists the radial load applied thereto but accommodates relative axial misalignment or tilting between the inner shell 41 and the shaft 14. It will be appreciated that with continuous rotation of the shell 11 on the shaft 14, there will be a continuous flexing or momental type of action that must be absorbed in one or more members carrying the radial load here involved. Thus, if the inner shell 41 were rigidly connected to the shaft 14 at the location of the sandwich assembly 43 and also rigidly connected tothe shell 11 through the head 24, these two rigid connections would have to share this flexing action, which is believed to cause premature failure of roll assemblies under certain operating conditions. In contrast, however, the instant invention is based upon the concept of employing the sandwich assembly 43 as the yielding member in the assembly so that little or no flexing action must be absorbed in the head 24 and substantially all of such action is absorbed in the sandwich assembly 43. In addition, it will be appreciated that the complexity of the flexing action and/or additional forces that are involved in this operation is greatly increased in the case of a driven roll, for the reason that stopping, starting, speed changes, and/or load changes will cause additional complications in the so-called flexing action which must be absorbed in a radial load supporting member. Thus, as shown in FIGURE 1, the roll shell 11 may be driven by any conventional suitable drive means, here indicated diagrammatically at D, connected to the shaft 14. When the drive means are operating against a load resisting rotation of the shell 11, it will be appreciated that an additional generally downward (also generally radially aligned) force component is introduced into the system, and this force component must also be absorbed by the

sandwich assemblies

42 and 43, which are uniquely satisfactory for this purpose.

The sandwich assemblies are preferably made of very thin annular steel sheets; and such

steel sandwich assemblies

42 and 43 operate satisfactorily in ambient temperatures of as much as 600 F. (in the event it is desired to heat the shell 11) and this affords a distinct advantage over previously known supporting elements which could not be operated at such temperatures.

It will also be appreciated that rolls employing the instant

steel sandwich structures

42 and 43 can be readily assembled and disassembled in the field for repairs and maintenance. In the instant arrangement, the heads 23 and 24 are first removed, then the shell 11 may be removed so that maintenance can be attended to in connection with the remainder of the structure (which would then have the appearance that is shown fragmentarily in FIGURE The steel sandwiches 42 and 43 are very thin axially, preferably being made of approximately 1/32 of an inch thick cold rolled steel sheets. As a typical example, using a press roll shell 11 having an outer diameter of 34 inches and an inner diameter of 27 inches with an operating length or face of 206 inches, the inner shells preferably have an outside diameter of about 26 inches and an inside diameter of about 19 inches with an axial dimension or length of approximately 431/2 inches from the inner face of the heads 23 and 24 to the center line of the steel sandwiches 42 and 43. The steel sandwich is thus approximately 26 inches in outside diameter, 19 inches in inside diameter and 1% inches in axial dimension, being built up of approximately 56 cold rolled steel sheets lying in complete contact with each other and secured by the bolts of the 64 and 69 seri-es hereinbefore described. It will be appreciated, however, that the

steel sandwich assemblies

42 and 43 can be modified to obtain certain advantages. For example, each of the steel sandwich sheet elements may be plated around the bolt hole to induce a gap between the elements. Also very thin washers may be employed to induce an actual gap between each of the annular elements or between groups of such annular elements. It will thus be seen that the

steel sandwich assemblies

42 and 43 are composed of a multiplicity of axially thin steel elements that are substantially co-planar, i.e., that are all lying in generally radial planes and because of their very limited axial dimension and the compact structure of the sandwich assemblies, the sandwich assemblies per se may be thought of as lying inl substantially a radial plane (for receiving the load). The multiplicity of radially aligned elements may be provided with a plurality of very thin spacers (at the location of the bolts, preferably) which may be used to permit greater flexing actionl in the assemblies, without subtracting to any significant extent from the ability of the

assemblies

42 and 43 to carry the radial load.

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.

I claim as my invention:

1. In combination, a rotatable roll shell having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto mounting the shell, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, and allochiral mounting means eachv secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

2. In combination, a roll shell having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto, bearing means carrying the shaft means for co-rotation with the shell, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, and allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

3. In combination, a roll shell having a substantial lengthto-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto, bearing means .carrying the shaft means for co-rotation with the shell, drive means connected to the shaft means for controlling rotation thereof, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and' outwardly of the middle of the shell, and allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

4. A mounting for each end of a paper making machine roll shell having a substantial length-to-diameter ratio, comprising rotatable shaft means, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, sleeve means spaced radially from the shaft means and the shell interior secured to the shell rigidly and solely at one end and secured tothe shaft solely through a rigid connection with said plurality of laminae, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

5. A drive mounting for one end of a paper making machine roll shell having a substantial length-to-diameter ratio, comprising a rotatably mounted shaft, drive means for rotating the shaft, a plurality of generally radially extending, axially aligned and axially tl'nn flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, sleeve means spaced radially from the shaft means and the shell interior secured to the shell rigidly and solely at one end and secured to the shaft solely through a rigidl connection with said plurality of laminae, thereby applying internal counter-deilection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

6. In combination, 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 spaced radially inwardly of said shell and extending within the shell appreciably inwardly axially of the shell ends, allochiral shaft means each having an outer end rotatably mounted outside one end of said shell and extending within the shell appreciably inwardly axially, and a plurality of axially thin flexible juxtaposed laminae mounting each of said inner ends of the mounting means at a location appreciably inwardly axially of the shell on one of said shaft means to afford limited tilting therebetween and thereby applying internal counter-deflection moments to said shell in response to the application of a load to said shell.

' 7. In combination, 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 spaced radially inwardly of said shell and extending within the shell appreciably inwardly axially of the shell ends, allochiral shaft means each having an outer end rotatably mounted outside one end of said shell and extending within the shell appreciably inwardly axially, an assembly formed of a plurality of axially thin flexible juxtaposed laminae positioned within the shell appreciably axially inwardly from each end thereof, first means securing each assembly to the shaft means adjacent thereto, and second means spaced from the llrst means securing the inner ends of said mounting means to the assembly, whereby said shell is carried on said shaft means via said assemblies to afford limited tilting between the shaft means and the shell axis and thereby applying internal counter-deflection moments to said shell in response to the application of a load to said shell.

8. In combination, 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 spaced radially inwardly of said shell and extending within the shell appreciably inwardly axially of the shell ends to present generally annular irst faces, allochiral shaft means each having an outer end rotatably mounted outside one end of said shell and extending within the shell appreciably inwardly axially, heads mounted on the inner ends of the shaft means to present second generally annular faces spaced from the ilrst, an annular assembly formed of a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted between the spaced first and second faces inwardly from each end of the roll shell, rst means spaced from the heads securing the assemblies to the mounting means, and second means spaced from the first means and from the mounting means securing the assemblies to the heads, whereby said shell is carried on said shaft means via said assemblies to afford limited tilting between the shaft means and the shell axis and thereby applying internal counter-deflection moments to said shell in response to the application of a load to said shell.

9. A mounting for each end of a paper making machine roll shell having a substantial length-to-diameter ratio, comprising rotatable shaft means, a plurality of generally radially extending, axially aligned and axially thin ilexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, sleeve means spaced radially from the shaft means and the shell interior secured to the shell rigidly and solely at one end, first means spaced from the shaft securing said sleeve means to said plurality of laminae, and second means spaced from said first means and said sleeve means securing said plurality of laminae to said shaft means, said plurality of laminae being the sole connection between said sleeve means and said shaft means, thereby applying internal counter-detlection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

10. A mounting for each end of a paper making machine roll shell having a substantial length-to-diameter ratio, comprising rotatable shaft means, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, sleeve means spaced radially from the shaft means and the shell interior secured to the shell rigidly and solely at one end, a first set of peripherally spaced means spaced from the shaft and securing said sleeve means to said plurality of laminae, and a second set of peripherally spaced means interposed between and spaced from the means of said rst set and spaced from said sleeve means securing said shaft to said plurality of laminae, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

1l. In combination, a rotatable roll shell having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto mounting the shell, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means, allochiral sealing means interposed between the shell ends and the shaft means to define a chamber within the Shell, and means for feeding heat transfer fluid into said chamber for controlling the roll temperature.

12. In combination, a rotatable press roll, a rotatable roll shell in nip-defining relation therewith having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto mounting the shell, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, and allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

13. In combination, a rotatable press roll, a rotatable roll shell in nip-defining relation therewith having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto mounting the shell, a plurality of generally radially extending, axially aligned and axially thin flexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means, allochiral sealing means interposed between the shell ends and the shaft means to define a chamber within the shell, and means for feeding heat transfer fluid into said chamber for controlling the operating temperature at the nip.

14. In a paper machine calender, a plurality of superimposed rotatable calender rolls, a bottom rotatable calender roll shell supporting said superimposed calender rolls, said calender rolls and said shell each having a substantial length-to-diameter ratio and centroidal axes subject to deflection in response to a load, axially aligned shaft means in the shell and in spaced relation thereto mounting the shell, a plurality of generally radially extending, axially aligned and axially thin ilexible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, and allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby Iapplying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means.

15. In combination, a rotatable roll shell having a substantial length-to-diameter ratio and whose centroidal axis is subject to deflection in response to a load applied to the shell, axially aligned shaft means in the shell and in spaced relation thereto mounting the shell, a plurality of generally radially extending, axially aligned and axially thin exible juxtaposed laminae mounted on said shaft means appreciably axially inwardly of each shell end and outwardly of the middle of the shell, allochiral mounting means each secured to one of such plurality of laminae and extending therefrom between and radially spaced from the shell and shaft means and secured solely to the shell at the end thereof by a rigid connection, thereby applying internal counter-deflection moments to said shell in response to the application of a load thereto and thereby affording limited tilting between the shell and shaft means, allochiral sealing means interposed between the shell ends and the shaft means to define a chamber within the shell, and means concentric with the shaft means for feeding steam into the chamber and withdrawing condensate therefrom to control the roll temperature.

16. In combination, a rotatable roll shell whose centroidal axis is subject to deflection in response to a load applied to said shell, shaft means in the shell and in radially spaced relation thereto for mounting the shell, co-axially spaced allochiral assemblies of a multiplicity of axially thin flexible juxtaposed laminae positioned appreciably axially inwardly from the shell ends, allochiral mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate the shell and the shaft means, rst means securing each assembly to the shaft means, and second means spaced from the first means securing each assembly to the mounting means adjacent thereto, whereby the radial load of such mounting means is transmitted to the shaft means through said assemblies, each such mounting 14 means being secured rigidly to the shell solely at its outer end and mounted on the shaft means via said assemblies 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 f 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.

17. In combination, a rotatable roll shell whose centroidal axis is subject to deflection in response to a load applied to said shell, shaft means in the shell and in radially spaced relation thereto mounting the shell, drive means connected to the shaft means for rotating the same to drive the roll shell, co-axially spaced allochiral assemblies of a multiplicity of axially thin exible juxtaposed laminae positioned appreciably axially inwardly from the shell ends, allochiral mounting means surrounding the shaft means and extending appreciably axially inwardly of each of the shell ends intermediate the shell and the shaft means, rst means securing each assembly to the shaft means, and second means spaced from the first means securing each assembly to the mounting means adjacent thereto, whereby the radial load of such mounting means is transmitted to the shaft means through said assemblies, each such mounting means being secured rigidly to the shell solely at its outer end and mounted on the shaft means via said assemblies 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.

References Cited in the le of this patent UNITED STATES PATENTS 825,344 Pearse July l0, 1906 1,662,006 Kimrnich Mar. 6, 1928 1,698,160 Hall Jan. 8, 1929 2,651,241 Hornbostel Sept. 8, 1953 2,676,387 McArn Apr. 27, 1954

Claims

1. IN COMBINATION, A ROTATABLE ROLL SHELL HAVING A SUBSTANTIAL LENGTH-TO-DIAMETER RATIO AND WHOSE CENTROIDAL AXIS IS SUBJECT TO DEFLECTION IN RESPONSE TO A LOAD APPLIED TO THE SHELL, AXIALLY ALIGNED SHAFT MEANS IN THE SHELL AND IN SPACED RELATION THERETO MOUNTING THE SHELL, A PLURALITY OF GENERALLY RADIALLY EXTENDING, AXIALLY ALIGNED AND AXIALLY THIN FLEXIBLE JUXTAPOSED LAMINAE MOUNTED ON SAID SHAFT MEANS APPRECIABLY AXIALLY INWARDLY OF EACH SHELL END AND OUTWARDLY OF THE MIDDLE OF THE SHELL, AND ALLOCHIRAL MOUNTING MEANS EACH SECURED TO ONE OF SUCH PLURALITY OF LAMINAE AND EXTENDING THEREFROM BETWEEN AND RADIALLY SPACED FROM THE SHELL AND SHAFT MEANS AND SECURED SOLELY TO THE SHELL AT