Structure between driving transmission and roll

Abstract

The invention concerns a connecting structure (10) between a driving transmission (11) and a roll (100) driven through it. The driving transmission (11) includes an input shaft (12) in the drive, whereby through the input shaft (12) the drive is transferred to toothed gears and further to the roll jacket (100a) of the driven roll (100) to rotate it. The roll (100) includes a central static shaft (100b) and a bearing (G) to support it. In order to allow axial and radial motions of the roll's (100) roll jacket when the driving transmission (11) is in the fixed position, a seal (25) including a sliding ring (30) is fitted in between the driving transmission (11) and the roll (100).

Description

FIELD OF THE INVENTION

[0001] The invention concerns a structure between a driving transmission and a roll.

BACKGROUND OF THE INVENTION

[0002] Known in the art is a bellows seal structure between a driving transmission and a variable crown roll. In this application, a variable crown roll means one where the roll jacket can be loaded along its length into the desired shape by using hydraulic pressure or hydraulic loading shoes. The central shaft at which the hydraulic counter-pressure is directed or where the hydraulic loading shoes are located, is a fixed and static shaft. To allow radial and axial motions for the roll jacket of the variable crown roll used in the connection between the driving transmission and the roll, a state-of-the-art solution allows the said motions by using a bellows-like seal structure made of rubber between the driving transmission and the roll. In the known state-of-the-art solution the bellows are fitted in between the end face of a toothed gear surrounding the shaft of the variable crown roll of the driving transmission and a body structure joined to the driven roll after the sleeve shaft of the toothed gear.

[0003] The bellows allow large radial motions between the roll structure and the transmission. The rubber bellows are joined by band clamps both with the transmission and with the body part connected to the roll jacket. The transmission oil is located inside the bellows in a space between the bellows and the static central shaft. The rubber bellows are attached by hose clamps between the roll and the toothed gear.

[0004] The bellows do not adapt so well to reception of axial motion, radial motion and torsion at high speeds and with big diameters. Should the bellows tear or the clamp break, the resulting leakage will be so big that the entire paper machine must be stopped, so the problem will also come as a surprise, and not as a controlled one.

OBJECTS AND SUMMARY OF THE INVENTION

[0005] The present application presents a seal solution of an entirely new type for the driving transmission and roll. The roll may be a variable crown roll in a paper machine, which includes a static, non-rotary central shaft and a joining hydraulically loaded pressure chamber or joining hydraulically loaded loading shoes, which are used or which bring about a pressure in the pressure chamber which is used for loading the roll jacket and for controlling in the roll nips the bending shape of the roll jacket. Through the driving transmission the drive is transferred first from the sleeve shaft through the body part to the roll flange and then to the roll jacket. Bends caused by the hydraulic pressure or by loading applied by the loading shoes are permitted on the central shaft itself. The idle bearing on the drive side of the static shaft is preferably located in connection with the driving transmission.

[0006] The sealing between the integrated roll transmission and the roll must receive

[0007] axial motion, the roll jacket may move a distance equal to clearances between bearings

[0008] radial motion, eccentricity caused by bending of the roll

[0009] torsion, a motion caused by backlashes in the gear clutch.

[0010] The new seal solution is formed by a sealing ring. The excellency of the structure is based on low friction and on a light-weight sliding ring material, which in addition includes wear-resistant seals in both the axial and radial directions. The sliding ring is located between two lateral sealing rings, whereby the place is determined axially. The sliding ring is dimensioned so that any eccentricity between central lines of the shaft introduced by the transmission and by the loading of the roll will cause no problems for its operation, as the sliding ring may move in its position in the radial direction. A small grease filling is placed in the space remaining inside the sliding ring and the rings to attend to lubrication of seals in the axial direction with the aid of centrifugal force. The seal located on the outer diameter of the sliding ring gets its lubrication from oil inside the transmission. Dimensioning of the seal surface is sufficiently long, so that an axial motion of the jacket will not prevent the operation.

[0011] All rings rotate at the rotational speed of the roll. The sliding ring gets into a constant small radial motion, the extent of which depends on the loading of the roll and on the magnitude of the estimated eccentricity. The seal solution is suitable for diameters of all sizes, it is also suitable for both low and high surface velocities. The sliding ring and the seal materials are chosen so that they will withstand well the wear in question. The sealing solution does not aim at an entirely leakage-free solution, but at controlled leakage. From the space outside the sealing a hose/pipe extends in which the leakage can be observed, and wearing of the seals can be foretold so that the suitable time for maintenance can be planned in advance.

[0012] The new solution allows sealing of new high-speed machines.

BRIEF DESCRIPTION OF THE FIGURES

[0013] In the following, the invention will be described with reference to a preferable embodiment shown in the figures in the appended drawings, but the intention is not to restrict the invention to this embodiment only.

[0014] FIG. 1 is an illustrative view of the target area of the invention.

[0015] FIG. 2A is an end view of the driving transmission.

[0016] FIG. 2B is a cross-sectional view along line I-I in FIG. 2A.

[0017] FIG. 3 shows the seal on a larger scale at area A in FIG. 2B.

DETAILED DESCRIPTION OF THE INVENTION

[0018] FIG. 1 illustrates the target area of the invention as a connecting structure 10 in between a driving transmission 11 and a roll 100. The drive is supplied e.g. from an electric motor to the input shaft 12 of driving transmission 11, and the drive is transferred further through the driving transmission 11 and toothed gears to the roll jacket 100a of roll 100. Roll 100 includes a non-rotary static central shaft 100b. The central shaft 100b is supported at both ends by idle bearings G, which are preferably ball bearings and which allow the central shaft 100b to bend due to loads. The central shaft 100b of roll 100 includes a pressure chamber or, instead of this, loading shoes as shown in the figure, preferably hydraulic loading shoes K1, K2 . . . , which can be brought into contact with the inner surface of roll jacket 100a and which are used or which bring about a pressure in the pressure chamber which is used for loading the roll jacket in the roll nip N1 between rolls 100 and 200. When the roll jacket is loaded with a hydraulic pressure or by the loading shoes K1, K2, radial transfers will occur between the roll structure and the driving transmission 11 and axial transfers will also occur in the drive. To allow permission of these between the driving transmission 11 and the driven roll 100, the structure according to the invention uses a separate seal 25 according to the invention, which includes a sliding ring 30. The roll 100 may be e.g. a variable crown roll of a paper machine or a board machine, that is, a roll with compensation for bending.

[0019] FIG. 2A is an end view of the driving transmission. FIG. 2B is a cross-sectional view along line I-I in FIG. 2A. Of roll 100 the figure shows the end face on the driving transmission side.

[0020] Referring to FIGS. 2A and 2B the following is a description of the connecting structure 10 between driving transmission 11 and the roll 100 driven through the transmission. Roll 100 is preferably a so-called variable crown roll, that is, a roll where bending is compensated for. This means that the roll jacket can be loaded directly by hydraulic pressure or by hydraulic loading shoes K1, K2 The pressure chamber or the loading shoes are located inside the roll jacket between the static or fixed central shaft 100b and the roll jacket 100a. The static shaft 100b is supported on bearing G, which is a so-called idle bearing, which allows angular changes in the static shaft 100b caused by loading. The driving transmission 11 includes a box-section body R. The drive is brought e.g. from an electric motor to input shaft 12. Input shaft 12 includes a toothed gear or teeth 13. The input shaft is supported by bearings 14 and 15 to rotate in boxsection body R. Through teeth 13 the drive is transferred further to a toothed gear 16 surrounding the static shaft 100b through its teeth 16a, which are functionally connected with the teeth 13 of input shaft 11. Toothed gear 16 includes inner teeth 16b. Toothed gear 16 is supported on body R by bearings 17, 18. At one side of bearing 18 there is a cover plate 19 to keep the bearing 18 in place. Bearings 17 and 18 are located at both sides of the circumferential teeth 16a of toothed gear 16. Through the inside teeth 16b of toothed gear 16 the drive is transmitted to sleeve shaft 20 by way of its circumferential teeth 21a. At the other end of sleeve shaft 20 there are outer circumferential teeth 21b, from which the drive is transmitted further by way of teeth 23 of the flange plate 22 to flange plate 22. A ring plate 24 is attached by screws R1 to flange plate 22. The ring plate 24 includes a body part 24a located at right angles against the geometrical central axis X of shaft 100b and a body part 24b in the direction of the geometrical central axis X. Body part 24b includes a first stop face 24c1, for a seal 25 according to the invention, for its sliding ring 30 and for a ring seal 31 and a second stop face 24c2 for a second seal 26 connected with the leakage oil space 33.

[0021] The sliding ring 30 of seal 25 is located in the body 27 of the seal case and it contains a seal cavity 28, preferably an annular groove. In the seal cavity 28 and in grooves U1 and U2 of the seal case body 27 lateral seals 29a1,29a2 are located, which come against sliding ring 30. The body 27 of the sealing case includes a basic body 27a, a ring plate 27b and a fastening screw R2. Screw R2 is brought through the ring plate 27b and further through basic body 27a and further to the face surface of toothed gear 16. Sliding ring 30 may preferably be of a plastic material. An advantageous rubber O-ring seal 31 is located in the end face of sliding ring 30. The function of seal 31 is to prevent transmission oil from flowing past it and, on the other hand, it allows the formation of a slide surface, so that an axial motion (L2) is allowed between the driving transmission and the roll jacket. Sliding ring 30 is dimensioned so that when it is located in the seal cavity 28, a free space D will form in between the bottom t of seal cavity 28 and face surface n of sliding ring 30, in which free space a lubricant, such as lubricating oil/grease, is placed and which space D allows roll jacket 100a to move in the radial direction. The cavity space D is located in such a way in the structure that it is situated closer to the central axis X of rotation than the first stop face 24c1. Hereby the filling grease placed in cavity space D will tend under the influence of the centrifugal force to move towards the seal surfaces, whereby the arrangement attends to the lubrication of the seal surfaces. Motion of the seal's sliding ring 30 under the influence of the centrifugal force towards the bottom t of seal cavity D also moves lubricant from space D on to the surfaces to be lubricated.

[0022] The structure according to the invention also includes an outer ring 32, whereby a leakage oil space 33 is formed after the seal 25 between the outer ring and the seal 25. The leakage oil space 33 is connected with a leakage oil channel 34, which is preferably e.g. connected back to the transmission. The leakage oil channel 34 may be formed by a transparent leakage oil pipe, through which the quantity of leakage oil occurring during the operation can be observed. Leakage oil channel 34 may also be provided with a measuring device/sensor that indicates the quantity of leakage oil exactly and which will alarm the machine operator should the said quantity of leakage oil exceed a certain established limit value. If the flow of leakage oil is observed only visually, the by-pass pipe is preferably made of a transparent material or it has a transparent window, through which any flow of leakage oil can be observed.

[0023] By bringing the drive to the input shaft in the structure according to the invention, the drive is transmitted further to toothed gear 16 and further to sleeve shaft 20 and through this further to flange plate 22, which is joined further to roll 100 to rotate the roll jacket 100a of the variable crown roll. In this way rotation is achieved for toothed gear 16, whereby the rotational speed as regards the said toothed gear 16 and the associated seal 25 is the same as for the driven roll 100 and its roll jacket 100a.

[0024] FIG. 3 shows seal 25 on a larger scale in the target area of the invention. Seal 25 is formed by the following structure. Seal 25 is an annular structure around central shaft 100b. Seal 25 includes an annular sliding ring 30, which is located in the seal cavity 28 of seal case 27. Annular lateral seals 29a1 and 29a2 are also located in grooves U1 and U2 of the seal case 27 of seal cavity 28. An O-ring seal 31 is located in a peripheral grove U3 in the end face of sliding ring 30. In the structure according to the invention, a free space D is formed, into which lubricant/grease is placed so that when the seal case body 27 rotates together with the other structure, the centrifugal force will cause the lubricant/grease to move in a radial direction outwards, and in this way the side surfaces of both the lateral seals 29a1, 29a2 and of the sliding ring 30 will be lubricated. The transmission oil proper performs lubrication of O-ring seal 31 when it is located against its stop face 24c1. Stop face 24c1 is made so long that O-ring seal 31 may slide along it due to axial motions (L2) of the roll jacket. The axial motion (arrow L2) and the radial motion (arrow L1) of the roll's 100 jacket 100a are passed on by way of flange plate 22 to ring plate 24 and thus to body part 24b. Ring plate 30 receives the radial motion, and the axial motion is taken into account by making stop face 24c1 long enough, whereby O-ring 31 will travel along stop face 24c1. In operation, sliding ring 30 and the seal 31 located in its end face will rotate. Seal 31 prevents transmission oil from flowing past it. Seals 29a1 and 29a2 prevent transmission oil from flowing into space D.

[0025] The sliding ring seal 30 is preferably made of a plastic material and it is wear resistant, it tolerates heat well and it is also oil resistant and has good sliding qualities.

Claims

1. A connecting structure comprising: a driving transmission (11) and a roll (100) connected through it, which driving transmission (11) includes an input shaft (12) in the drive, whereby the drive is transmitted through the input shaft (12) to toothed gears and further to the roll jacket (100a) of the driven roll (100) to rotate this, and which roll (100) includes a central static shaft (100b) and a bearing (G) to support it, wherein in order to allow axial and radial motions of the roll's (100) roll jacket when the driving transmission (11) is located in the fixed position, a seal (25) including a sliding ring (30) is fitted between the driving transmission (11) and the roll (100).

2. Connecting structure according to claim 1, wherein the drive is transferred through the teeth (13) of the input shaft (12) to a central toothed gear (16) by way of its teeth (16a), from which toothed gear (16) the drive is transferred further to a sleeve shaft (20), whereby the internal teeth (16b) of the toothed gear (16) are functionally connected with the circumferential teeth (21a) of the sleeve shaft (20), and the drive is transmitted further from the sleeve shaft (20) through second outer circumferential teeth (21b) to a flange plate (22), whereby the teeth (23) of the flange plate (22) are functionally connected with the teeth (21b) of the sleeve shaft (20), and in that the flange plate (22) is connected to the roll jacket (100a) of the driven roll (100) rotating it, that the sliding ring (30) is fitted into the body (27) of the seal case, which body is located in the end face of toothed gear (16), and that the sliding ring (30) is located in the seal cavity (28) of seal case (27), which cavity is preferably an annular groove and in its side surfaces includes grooves (U1, U2), in which lateral seals (29a1,29a2) are located and which will be situated against the side surfaces of the sliding ring (30).

3. Connecting structure according to claim 1, wherein a free space (D) remains between the sliding ring (30) and the bottom (t) of the seal cavity (28), in which space lubricant/grease may be placed, whereby when the seal case body (27) is rotating lubricant will be moved with the aid of centrifugal force towards the sliding ring (30) and the seals (29a1,29a2) in order to bring about lubrication between the sliding ring (30) and the structures connected with it.

4. Connecting structure according to claim 1, wherein the sliding ring (30) in a peripheral groove (U3) in its end face includes a seal (31), preferably a rubber seal, which is situated against the stop face (24c1), whereby the stop face (24c1) is located in a ring plate (24) of the flange plate (22) connected with the shaft (100), and the ring plate (24) includes a body part (24a) located at right angles against the central axis (X) of the shaft (100) and a body part (24b) in the direction of the central axis (X), whereby the stop face (24c1) is formed in the body part (24b) and it is chosen so that a sufficient travelling distance is made possible for the axial motion (L2) of the roll's (100) roll jacket (100a).

5. Connecting structure according to claim 1, wherein the sliding ring (30) is an annular part and it is located in the roll (100) around the shaft (100b), whereby with the aid of the free space (D) in the seal cavity (28) the sliding ring (30) of seal (25) is allowed to move in the radial direction (L1) and radial and axial motions (L1 and L2) of the roll's (100) roll jacket (100a) are allowed.

6. Connecting structure according to claim 1, wherein a leakage oil space (33) after the seal (25) includes a leakage oil channel (34), through which the leakage oil flow can be observed either visually or by using a measuring device, whereby when the leakage oil flow exceeds a certain predetermined limit value, an alarm indicating the said excess can be given to the machine operator.

7. Connecting structure according to claim 1, wherein the sliding ring (30) is of a plastic material.