CA2029514A1

CA2029514A1 - Deflection adjustment roll

Info

Publication number: CA2029514A1
Application number: CA002029514A
Authority: CA
Inventors: Mario Biondetti
Original assignee: Mario Biondetti; Sulzer-Escher Wyss Ag; Sulzer-Escher Wyss Gmbh
Current assignee: Sulzer Escher Wyss AG; Sulzer Escher Wyss GmbH
Priority date: 1989-11-08
Filing date: 1990-11-07
Publication date: 1991-05-09
Also published as: DE8914037U1; IT9021785A0; IT9021785A1; IT1243851B; FI905146A0; DE4015237A1

Abstract

ABSTRACT OF THE DISCLOSURE

Deflection adjustment roll having a roll shell which is rotatable around a stationary support, and is supported by means of bearing elements in a pressure plane, which provides mobility at the ends of the roll shell. The roll shell is rotatably seated on a stationary guide element, which has an elongated opening with parallel guide surfaces in which the support is movable in the pressure plane. In order to exert an additional, maximal force on the roll shell in the area of the guide element, at least one pressure chamber is provided in the free space between the support and the guide element, which can be supplied with pressure means, with pressure thereto being controllable through bores in the support. The pressure chamber is formed by a piston-shaped attachment on the support which engages a cylindrical bore in the guide element, and forms a piston/cylinder guide which is sealed by its sliding fit or by means of a seal ring surrounding the piston-shaped attachment.

Description

DEFLBCTIO~ ADJIJ8~M13NT ROLI
BACKGROUND OF THE INVENTION
1. Field of the Invention The present invention relates to deflection adjustment rolls which i~clude a stationary support, a roll ~hell which is rotatable around the support, and at: least one bearing element located between the support and t:he roll shell. The at least one bearing element exerts pressure in a pressure plane on the interior of the roll shell at a location where the ends of the roll shell are rotatably ~ealed on guide elements. Each guide element includes a guide opening having two parallel guide surfaces which extend along the support and allow movement of the guide element in the pressure plane in relation to the support. At least one pressure chamber is provided in the area of the guide opening of each guide element, which applies pressure in the direction of the pressure plane.

2. Discussio~ ~ the Background ~n~ Material Information Known deflection adjustment rolls include disadvantages that the present invention overcomes.
For example, U.S. Patent No. 4,213,232 and DE 3,138,365, the disclosures of which are incorporated by reference in their entireties, are directed to deflection adjustment rolls which include a cylindrical bore in the support in the direction of the pressure plane, and which presses on the innPr surface of the guide element inside the guide opening.
In this way, pressure is exerted at the ends of the roll shell, for example, for receiving the weight of the roll shell itself and o~ the roll or press elements which are movable together with the roll shell, so that the bearing elements only need to correct variations of the pressure. However, the disadvantages associated with rolla of this type reside in the ~"
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fact that the support is weakened because of the cylindrical bore and that the forces which can be introduced via the guide element are limited. More speci~ically, in this type of deflection adjustment roll, the cross-section of the - 5 cylindrical bore in the support should not be made too large in order not to weaker. the support. Moreover, due to such size limitation, the maximum exertable pressure in the cham~er is limited.
It is also known from DE 3,539,428, the disclosure of lo which is hereby inoorporated by reference in its entirety, to provide the entire guide opening as a pressure chamber.
However, in such a situation, the opening must be axially sealed on both sides with sealing washers. Although an optimally large effective pressure sur~ace is created by such an arrangement, it is necessary that the sealing washer have a relatively large surface to permit a particular inclination o~ the support with respect to the roll shell because of de~lection. Moreover, the sealing washer requires the ability to move in a radial direction, so that the pressure of the hydraulic medium in the pressure chamber is limited and cannot be selected to be optimally high. Accordingly, the force which can be generated is also limited.
In accordance with EP 332,594, the disclosure of which is hereby incorporated by reference in its entirety, the last-mentioned disadvantages are avoided in that piston/cylinder guides are provided inside the openings of the guide device.
The piston/cylinder guides consist o~ cup-shaped attachments on a slanted support with which piston-shaped necks on the inside of the guide opening are in engagement. However, these attachments require considerable space within the guide openings, so that the stroke of the guide device or of the roll shell with respect to the support is limited. So as to .~

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achieve the best possible use of the guide opening for creating the greatest possible force, two cup-shaped attachments are provided on each side, thP pressure directions of which have a particular inclination with respect to the pressure plane. Therefore, these attachments must be slightly movable laterally in order to functic)n properly, which requires an additional seal between attachment and support, and thereby limits the usable pressure.
SUMMARY OF THE INVENTION
lo It is an object of the present invention to overcome the disadvantages associated with deflection adjustment rolls as discussed above in such a way that it is possible to introduce a greater force on the ends of the roll shell via the guide device without requiring the weakening of the support, without reducing the pressure of the pressure medium and without limiting the stroke of the guide device. This object is attained in accordance with the present invention by providing at least one piston-shaped attachment on the ~upport, which togekher with a corresponding cylindrical bore in the guide element, forms a piston/cylinder guide which represents the pressure chamber.
Although the effective surface in such an arrangement is slightly less than optimalt sealing of the pressure chamber is considerably simpler and more effective than with axial sealing washers and can advantageously be attained either by means of the sliding fit of the piston/cylinder guide or by a sealing ring surrounding the circumference of the piston, 80 that a higher pressure in the hydraulic means can be employed for creating the same thrust. No weakening of the cross-section of the support is needed in this situation, and the full stroke of the guide elements is preserved. In this connection, the free space in the guide opening oriented towards the press, as well a~ the guide opening facing away from the support, can be advantageously provided with a pressure chamber which then exerts a force in the pressure plane, but opposite to the pressure direction.
The above-noted objects are achieved by providing a deflection adjustment roll including a stationary support, a roll shell rotatable around the support, and at least one supporting element located between the support and the roll shell which exerts pressure in a pressure plane on the lo interior of the roll shell. The roll shell includes ends which are rotatably seated on guide elements, with each o~ the guide elements including a guide opening having two parallel guide sur~aces which extend along the support and which allow movement of the guide element in the pressure plane in relation to the support. At least one pressure chamber is located in the area o* the guide opening for each of the guide elements which has a pressure direction which extends in the pressure plane, with the pressure chamber being ~ormed by at least one piston/cylinder guide which comprises at least one plston-shaped attachment positioned ad;acent the support and a corresponding cylindrical bore in the guide element.
The deflection adjustment roll in accordance with the present invention may include a pressure line extending in the ~upport which terminates in the pressure chamber.
~he piston-shaped attachment may be sealed against the cylindrical bore by an annular seal surrounding the piston-æhaped attachment. The annular seal may comprise an O-ring.
Pressure chambers may be positioned on opposite sides of the support in the guide opening o~ the guide element.
Separate pressure lines may extend in the support and terminate in the pressure chambers.

Moreover, a capillary bore may connect the pressure chamber with the outer chamber, and the pressure line may include a gas buffer.
Additionally, means ~orming a pressure line may supply hydraulic pressure to the at least one pressure chamber, or compressible pneumatic pressure to the at least one pressure chamber.
Also, the guide element may be composed of two parts fixedly connected with each other along thPir saparating surface.
BRIEF DESCRIPTION OF THE DRAWINGS
Other characteristics, and advantages of the invention will become clear from the descripti~n which follows with reference to the annexed drawings, which are given by way of non-limiting examples only, in which:
Fig. 1 illustrates an axial section of one end of a deflection adjustment roll, and Fig. 2 illustrates a radial section o~ this exemplary embodiment.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
In the exemplary embodiment illustrated in the drawings, where like parts are designated with like reference numerals, a de~lection adjustment roll 1, which may be designed a as solid roll, hollow roll or also as a deflection adjustment roll exerts pressure in a pressure plane P on a counter roll 2.
The deflection adjustment roll 1 includes a support 5, sea~ed pivotably, but fixed against rotation, by means of a pivot bearing 4 in a seat 3. A pipe-shaped roll shell 6 is rotatably seated on hydraulic bearing elements 7 around the support 5. These bearing elements may be, as described in U.S. Patent No. 3,802,044, the disclosure of which is , . . :, ., ............ , . ..... . ~ . . ~ ... . ~

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incorporated by reference in its entirety, in the form of hydrostatic bearing elements, which are supported on a pressure chamber 8 in the support, and are movable in the pressure plane P, or in another suitable form, for example as hydrodynamic bearing elements or as a prlessure cushion. By supplying a hydraulic pressure medium to t:he pressure chamber 8 via a line 9 in the support, the beari:ng elements 7 exert a pressure force on the inside of the roll shell 6, and thus on the counter roll 2. The pressure force can be varied by adjusting the pressure.
In such deflection adjustment rolls, the roll shell 6 is movable over its entire length in the pressure direction with respect to the support 5. This mobility is achieved at the ends of the roll shell 6 in that the roll shell is rotatably seated by means of a suitable bearing 16, which can be in the form of a friction bearing or advantageously a sel:E-aligning roller bearing, on a guide element lO. The guide element lO
is fixed against rotation, and is provided with an elongated opening 11 which is limited by parallel, plane side walls 12.
The cross section of the support is designed in such a way that free spaces 13 and 14 are created on the pressure side on the side of the counter roll as well as on the opposite side in the interior of the guide element 10, in which the support 5 is movable in the pressure direction P or in the opposite direction.
The support 5 is position~ed with little play in the area of the guide element lO between the guide surfaces 12 of the guide element 10. In the exemplary embodiment shown, the support 5 has a diameter in the area o~ the guide element 10 which corresponds to the width of the opening ll in the guide element 10, so that the support 5, together with the opening 11 or the guide slot, has a sliding fit, so that no -: .

' interfering seal is required between the support and the guide element at this location, and the opening has the largest -possible dimensions for housing the pressure chamber.
The roll shell 6 is advantageously sealed towards the exterior at its ends, for example, by means of sealing plates 17 and sealing washexs 18, to prevent the out~low of hydraulic pressure medium ~rom the interior of the roll, particularly from the bearing elements 7.
-It is attained by means of the method described that the ends of the roll shell 6 are also freely movable in a ;particular area in the pressure plane P. In connection with such rolls, it is often advantageous if the force exerted on the counter roll 2 need not be provided by the support elements 7 alone, but additional force is exerted on the roll shell 6 at the ends of the roll shell in the area ~f the guide elements 10. To achieve this, piston-like attachments 24 and 25 are provided, as shown in the embodiment illustrated in Figs. 1 and 2, on the support 5 in the area of the guide element 10. These engage cylindrical bores 26 and 27 of the guide element 10, and together with the guide element form pressure chambers 20 and 21, which can be supplied with hydraulic or pneumatic pressure medium from the direction of the support 5 via lines 22 and 23.
In the illustrated example, the entire inner surf~ce of the opening 11 of the guide element does not act as a pressure surface but only the somewhat smaller piston or cylindrical cross-section. But since a piston/cylinder guide can be sealed considerably simpler and more e~fectively, even at higher pxessure~, than the ~ree spaces of the guide elements that are sealed by sealing washers, this is in no way a disadvantage. Such seals can be formed by a sliding ~it of the cylinder/piston guides themselves, or for example as . ,, .:, . .

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simple 0-rings 15 and 19, which are disposed in an annular groove surrounding the pistons 24 and 25 on the outside or in the additional cylindrical bores 26 and 27 on the inside.
It is advantageous to provide a particular inclination between the piston and bore, which should be present anyway in piston/cylinder guides with large surfaces, and which, in contrast to extended sealing washers, can easily be realized with annular seals, as described in U.S. Patent No. 3,802,044.
Noreover, it is advantageous that a weakening of the support lo cross-section is nst necessary. Advantageously, the suxfaces of the piston/cylinder guides, i.e. the cross-sections of the pressure chambers 20 and 21, are selected to be as large as possible and are not limited to a circular cross-section. The pressure chambers can also be oval or elliptical, while still permitting very effective annular sealing even with higher pressures, or can be rectangular with rounded corners. In this manner, the opening ll of the guide element :L0 can be almost completely fi]led with pressure chambers 20 and 21 aating in the pressure plane or in the opposite direction, apart from the fact of the small space requirement for the annular seal 15 and 19, so that the surfaces on which the pressure acts are as large as possible. Accordingly, as high as possible a pressure force can be generated.
Furthermore, with a larger cross-sectional surface, the possibility of inclination of the piston 25 with respect to the cylinder 27 is greater, so that an inclination o~ the support 5 with respect to the guide element lO due to deflection o~ the roll may possibly be already caught by the annular seals 15 and 19, without the need ~or special provisions and without hindering the sealing effect and the permissible pressure, particularly if twisting can be reduced to a minimum by providing the bearing 16 as a self-aligning . ;-:, .. . .

., , , . . ' . ," :: ` . . ' . ' ' . ~ . ' , . ", ~ . ' '` ' , , . , " ' . .: .' ' ' ' '' . , ' :~ "' . ,, ' . - ' roller bearing. In this connection, it is also advantageous to provide such a pressure chamber 20 with a piston/cylinder guide not only in the free space 13 of the pressure side of the support 5, but also in the other free space 14 on the opposite side of the support, and acting in the opposite direction to the pressure direction P, ~where both pressure chambers are separately supplied with pressure medium via the lines 22 and 23, and can be separately controlled with different pressures.
lo It is advantageous that the guide element 10 is automatically protected against twisting with respect to the support 5 by means of the piston/cylinder guides, so that there is no need for separate twist protection. In connection with the described embodiments it is also advantageous to provide capillary bores, such as capillary bore 28, from the pressure chambers 20 and 21 to the outer chamber, wh:ich permit venting o~ the pressure chambers and a continuous weak oil circulation, and thereby assure pressure adjustment in the pressure chambers 20 and 21. It is possible that the required leakage can already be formed by the sliding fit of the piston/cylinder guides 24, 26; 25, 27 or by the annular seals 15, 19. `
Furthermore, a gas buffer may be provided in the pressure medium supply lines 22 and 23, which causes a particular elasticity of the pressure in the pressure chambers 20 and 21.
However, there is no need for the intended leakage through the above-mentioned capillary bores if a campressible medium, ~or example gas or air, is used, which is compressed to the re~uired pressures in the pressure chambers. The compressibility of the pressure means in this case permits mobility of the roll shell with respect to the support.
To ease the mounting of the guid~ elements 10 of the _ g _ ;~

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support 5, the guide elements 10 may be constructed of two parts which are seated on both sides on the support 5, so that the attachments 24 and 25 engage the respective bores 26 and 27, after which the two parts are solidly connected into a ; 5 single guide element along their separating surface 28, for example, by screwing or welding.
The attachments 24 and 25 can be in the form of integrated parts of the support 5, or as parts placed on the support 5 and connected with it in a suitable manner, for example by welding or screwing. i!~
This application is related to Swiss Application No. 04 028/89-0, whose priority is claimed, the disclosure and drawings of which are incorporated by reference thereto in their entirety.
Although the invention has been described with re~erence to particular means, materials and embodiments, it is to be understood that the invention is not limited to the particulars disclosed and extends to all equivalents within the scope of the claims. ;
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Claims

1. A deflection adjustment roll comprising:
a stationary support;
a roll shell rotatable around said support;
at least one supporting element located between said support and said roll shell which exerts pressure in a pressure plane on the interior of the roll shell;
said roll shell having ends which are rotatably seated on guide elements, with each of said guide elements including a guide opening including two parallel guide surfaces which extend along said support and allow movement of the guide element in the pressure plane in relation to the support; and at least one pressure chamber being located in the area of the guide opening for each of said guide elements having a pressure direction which extends in the pressure plane, said pressure chamber being formed by at least one piston/cylinder guide which comprises at least one piston-shaped attachment positioned adjacent said support and a corresponding cylindrical bore in said guide element.

2. The deflection adjustment roll in accordance with claim 1, wherein a pressure line extending in the support terminates in the pressure chamber.

3. The deflection adjustment roll in accordance with claim 1, wherein said piston-shaped attachment is sealed against the cylindrical bore by an annular seal surrounding said piston-shaped attachment.

4. The deflection adjustment roll in accordance with claim 2, wherein said piston-shaped attachment is sealed against the cylindrical bore by an annular seal surrounding said piston-shaped attachment.

5. The deflection adjustment roll in accordance with claim 3, wherein said annular seal comprises an o-ring.

6. The deflection adjustment roll in accordance with claim 4, wherein said annular seal comprises an O-ring.

7. The deflection adjustment roll in accordance with claim 1, including pressure chambers on opposite sides of said support in said guide opening of said guide element.

8. The deflection adjustment roll in accordance with claim 2, including pressure chambers on opposite sides of said support in said guide opening of said guide element.

9. The deflection adjustment roll in accordance with claim 3, including pressure chambers on opposite sides of said support in said guide opening of said guide element.

10. The deflection adjustment roll in accordance with claim 7, wherein separate pressure lines extend in the support and terminate in said pressure chambers.

11. The deflection adjustment roll in accordance with claim 8, wherein separate pressure lines extend in the support and terminate in said pressure chambers.

12. The deflection adjustment roll in accordance with claim 1, wherein a capillary bore connects the pressure chamber with an outer chamber.

13. The deflection adjustment roll in accordance with claim 2, wherein said pressure line includes a gas buffer.

14. The deflection adjustment roll in accordance with claim 2, wherein said pressure line includes a gas buffer.

15. The deflection adjustment roll in accordance with claim 10, wherein said pressure lines include a gas buffer.

16. The deflection adjustment roll in accordance with claim 11, wherein said pressure lines include a gas buffer.

17. The deflection adjustment roll in accordance with claim 1, wherein means forming a pressure line supplies hydraulic pressure to said at least one pressure chamber.

18. The deflection adjustment roll in accordance with claim 1, wherein means forming a pressure line supplies compressible pneumatic pressure to said at least one pressure chamber.

19. The deflection adjustment roll in accordance with claim 1, wherein said guide element is composed of two parts fixedly connected with each other along their separating surface.

20. The deflection adjustment roll in accordance with claim 2, wherein said guide element is composed of two parts fixedly connected with each other along their separating surface.