Note: Descriptions are shown in the official language in which they were submitted.
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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
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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.
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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
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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
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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
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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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