FI116081B - Deflection-compensated roll for paper / board or finishing machine - Google Patents

Description

116081

Deflection-compensated roll for paper / board or finishing machine

The present invention relates to a deflection compensated roll of a paper / board or finishing machine having a stationary roll axis and a roll casing rotatable therewith supported by sliding bearing elements on a roll axis which is loaded in at least one substantially radial direction of the roll. which sliding bearing elements are provided with hydraulic pressure medium supply means for loading the sliding bearing elements with a hydraulic pressure medium, with the hydraulic pressure medium supply means being tracked by means of which the sliding bearing elements are displaceable against the radially applied load, in a substantially stationary drive position relative to the roll axis.

15 Such a roller is known, for example, from the applicant's patent application FI 20001099.

Such a roll is illustrated in Figure 5 of the prior art. In it, a stationary shaft 2 ', at the ends of the shaft, is fitted with sliding bearing elements 5', 6 ', 7' which are loaded by a hydraulic pressure medium fed against the inner surface of the roll. Hydraulic pressure medium. The feed means include control means by which the sliding bearing elements 5 ', 6' acting in the direction of the external load (nip load) are loaded so that the roll shell 3 'can move radially relative to the shaft or remain substantially stationary with respect to the shaft.

»* * ·: * 25 Such rollers, in which the roll shell is imaged to move relative to the axis, have-; a gingival situation occurs when the diaper has been moved to an extreme position (eg, lowered). In this way, the so-called emergency lubrication lines 14 ', 15' are taken into active use, i.e. through the lines: · the hydraulic pressure medium (lubricant) is fed through a corresponding control system "". Than with a normal moving diaphragm roll. Lubricant flow channel 9b ',. conveys lubricant between the inner surface of the roll shell and the bearing element, is * »: ti '' formed on the bearing element 5 ', 6' between the pressure chamber and the sliding surfaces. Previously, I * '· ·' assumed a leak from the emergency lubrication line to however, due to the structure of the bearing element; * · | however, significant leakage may occur when the oil is directed along the easy path, i.e., from the pressure space 9 'of the element 5' through the control valve 20 'to the hydraulic pressure medium feed line 11 ', in which case lubricant there is not enough contact between the inside surface of the roll shell and the bearing element and the bearing may be damaged.

It is an object of the present invention to eliminate the above disadvantage.

To accomplish the above purpose, the present invention is characterized in that the control means include control means for supplying a continuous flow of lubricant formed by hydraulic pressure medium between the inner surface of the roll shell and the sliding bearing elements at all positions of the roll shell.

Such a new type of pressure medium / lubricant control system achieves that lubricant adequacy is assured, in particular in the roll, the function of which can be optionally changed between impact or movable and non-impact or fixed-shell operation.

Preferred embodiments of the present invention are set forth in the dependent claims.

The present invention will now be described in more detail with reference to the accompanying drawings Fig. 1 shows a schematic side view of a roll according to the invention, «. Figure 2 is a sectional view taken along line II-II of Figure 1, i * * *

Figure 3A is a side elevational view of a first control valve operating on a roll; * with the diaper in percussion mode, * # * ·,. Figure 30B is a side elevational view of the control valve of the element I <',,' 'on the opposite side of the element of Figure 3A with the roll sheath in the striking position *; * lassa, • »f I 1; * * * Figure 4A is a side elevational view of a first control valve operating on a roller> | 1 in diaper-free condition, 116081 3

Fig. 4B is a side elevational view of the operating valve of the element on the opposite side of the element of Fig. 4A with the roll sheath in the non-stroke condition, and Fig. 5 shows a cross-section of the prior art roll.

Figures 1 and 2 thus show a roll according to the invention, designated by the reference numeral 1. Roll 1 comprises a stationary shaft 2 around which a rotatable wheel is arranged! a roll shell 3 to which an external load F is applied substantially in the radial direction of the roll 1. The load F is formed, for example, by means of a counter roll, leaving a nip between the shells of these rolls through which, for example, a paper web is passed. The roll shell 3 is supported around the shaft 2 by means of the hydrostatic slide bearing elements 5.5a, 6,6a and 7 which are loaded by hydraulic pressure medium P.

Between the inner surface 3a of the roll shell 3 and the sliding surfaces of the sliding bearing elements 15, a lubricant layer is introduced by passing lubricant pressure medium P from the pressure elements 9,9a, 10,10a of the bearing elements to the bearing elements through channels 9b, 9c, 10b, 10c. In addition, the longitudinal nip profile of the roller 1 can be adjusted by means of load elements 8 arranged on the shaft 2 in the longitudinal direction of the shaft 2. In the following, the control of the sliding bearing elements 5, 5a, 6, 6a acting mainly in the direction of the plane F of the external load acting on the position of the roll shell 20 3 will be focused.

I I <i ·; Fig. 2 shows that the roller 1 is provided with an outer at both ends of the shaft 2. *: a first pair of sliding bearing elements 5, 5a,, i · operating against a half load F, disposed on the shaft 2 at a circumferential distance from each other. Then, the loading direction of these elements 5 and 5a relative to each other is the inner pin of the roll shell 3; 3a is at an angle. The load level (external load F) on the roll shell 3 runs between these plain bearing elements 5 and 5a, whereby the cumulative effect of the load on the plain bearings acts as a counter-force to the external load F. The corresponding sliding bearing element ' 5, 5a is a second pair of sliding bearing members 6, 6a operating in the opposite direction. It should be noted that the sliding bearing of the external load F may be implemented instead of four sliding bearing elements, for example by two. * ·. element, as disclosed, for example, in FI20001099.

> ·

»I I

116081 4

The shaft 2 is preferably provided with sliding bearing elements 7 (Fig. 1) acting transverse to the plane of the external load F to support the roll shell 3 laterally relative to the actual direction of movement of the roll shell 3.

In the illustrated embodiment, the plain bearing elements are loaded as follows. Figures 2, 3A and 3B show the impact state of the roller 1 in which the roller shell 3 moves relative to the axis. The hydraulic pressure medium P is supplied by means of the hydraulic pressure medium P feed means to the pressure chamber 9 formed on the sliding bearing element 5 and the chamber 9a formed on the sliding bearing element 5a through a first control valve 20 according to the invention. Similarly, the hydraulic pressure medium P is supplied by means of supply means to a pressure chamber 10 formed on a slide bearing element 6 on the opposite side of the shaft 2 and a chamber 10a formed on the slide bearing element 6a via a second control valve 30 according to the invention.

The above-mentioned hydraulic pressure medium feed means include control valves 20 and 30 according to the invention arranged in connection with the sliding bearing elements 5 and 6, with reference to the first control valve 20 (and the second control valve 30) shown in Fig. 3A (and 3B). The valve 20 (30) includes an elongated spindle pin 22 (32) which can be introduced at its first end into mechanical engagement with a sliding bearing element 5 (6). Spindle pin 22. * (32) is arranged in a cylindrical space formed partly along its longitudinal path along axis 2. The spindle pin 22 (32) can also be advantageously fitted to the shaft element 2 (not shown) attached to the shaft 2 ». In this case, the cylindrical space is preferably formed by a separate sleeve-like piece fitted to the body part, whereby the 25-pin spindle 22 (32) and the sleeve-like part form a separate valve. Cylinder mount. ' ·. two slider portions 23 (33) and 24 (34) arranged to move with the mandrel 22 (32) are also arranged in this space. The skate sections 23 (33) and 24 (34) are arranged in a karatapine. (22 (32) longitudinally spaced apart, however, with one of the slides 24 in the region of the other end of the spindle pin 22 (32) .The bottom of the end skate 24 (34) of the cylindrical space 21 (31) '30; beneath is preferably mounted a spring 27 (37) which in part: '.. loads the spindle pin 22 (32) against the bearing element 5 (6).

((Slider portions 23 (33) and 24 (34) define a supply space 21 (31) between which the hydraulic pressure medium P can be supplied alternatively either by the first supply channel '·': 35 hubs 12 (13) or the second supply channel 14 (15) The inlets of the first supply channel 116081 5 12 (13) are disposed in an annular groove 25 (35) formed in a cylindrical space The inlets of the second supply channel 14 (15) are radially extending channels 26a (36a) formed in the wall of the cylindrical space pieces) communicating with the second supply channel 14 5 (15) through, for example, an annular connecting channel 26 (36) .The radial channels 26a (36a) may be distributed at even intervals in the circumferential direction of the wall to the cylindrical wall. (35) is that high flow loads are eliminated in the feed space 21 (31) In this case, a large amount of pressure medium flows from the outlet conduit 16a (17a) 10 through the valve space 21 (31) to the radial conduits 26a (36a) and further to the second supply conduit 14 (15). The radial channels change the flow direction of the pressure medium so that unfavorable flow loads are eliminated. In another of the above-mentioned embodiments using a sleeve-like piece, the radial passages may be formed by bores 15 passing through the sleeve wall, which lead, for example, to an annular groove formed between the outer surface of the sleeve and the body of the bearing element. The annular groove 25 (35) and the radial passageways 26 (36) are located in a cylindrical space such that the skid portion 23 (33) moves at least partially past the radial passageways 26 (36) and the skid portion 24 (34) moves at least partially past the annular passageway 26 (36). pressure medium P vir, the background of the invention. This control function is explained in more detail • * · ';; 'Below. In the supply space 21 (31) delimited by the slider portions 23 (33) and 24 (34), there is also an outlet channel 16 (17) through which the hydraulic pressure medium P supplied to the space is supplied to the pressure chamber 9 (10) and still on the sliding surfaces of the element and • | between the inner surface 3a of the roll shell 3. The outflow channel 16 (17) has a

'25 branch 16a (17a). Hydraulic pressure medium P through channel duct 16a (17a)

: "; in the circumferential direction of the roller 1 is fed to the pressure chamber 9a (10a) of the adjacent sliding bearing element 5a (6a). Thus, substantially equal loading pressures are obtained on the bearing element pair 5, 5a (6, 6a).

According to Figures 2, 3A and 3B, the pressure medium P is supplied to the control valve 20 via a corresponding second supply channel 14. Thus, the inlet control channel 20 for the input of the second supply channel 14 is formed by radial channels 26a located closer to the bearing element 5. Similarly, the pressure medium P is supplied to the control valve 30 by the second #. through the supply channel 15. The inlet control valve 30 35 of the second supply channel 15 is formed by radial channels 36a located closer to the bearing element 6. The pressures of the pressure medium P supplied to the feed ducts 14 and 15 are controlled by the regulating means 14a and 15a arranged in the ducts. The pressures in the pressure spaces 9 and 10 are preferably monitored by means of pressure sensors 71 and 73 or the like connected to separate pressure measuring lines 70 and 72. The actuators 14a and 15a receive their control 5 either on the basis of the measurement results obtained from the pressure sensors 71 and 73, for example via hydraulic or electrical connection 74 and 75 or on line load calculation, whereby the pressure sensors 71 and 73 are used to verify the actual line load.

When the roller 1 is to be driven strikingly, the pressure difference between the second supply channels 14 and 15 and the interconnecting channels 14b and 15b leading to the pressure spaces 9 and 10 of the sliding bearing elements is controlled such that the bearing elements 5 and 6 and thus the spindles 22 and 32 23.24 and 33.34 move. The spindles 22 and 32 with their skates 23,24 and 33, 34 move to their extreme positions. This extreme position is determined, for example, by an annular lock 28, 38 or a counter part against which the ring surface of the slide 23, 33 rests, located near the mouth of the cylindrical space. At the same time, the flow path P from the radial channels 26a and the corresponding radial channels 36a to the inlet space 21, 31 is then fully directed to the space 21, 31 and further to the outlet 20 through the channels 16 and 17 and associated channel inserts 16a and 17a. 5, 5a and 6, 6a. Counter valves 40 and 50 close as pressure rises in pressure spaces 9 and 10. The passage of pressure medium P is indicated in the figures by a dashed line with arrow I.

7 116081

Figures 4A and 4B show an operational example of the valves 20 and 30 of Figures 3A and 3B when the roll shell 3 is guided without impact. The roll shell 3 is displaced substantially downward in the downward direction in the load plane direction of the external force F. This is accomplished by reducing or substantially removing the amount (pressure) of pressure medium to be fed through at least one of the supply channels 14, i.e., the loading pressures of the slide bearing element 5 and 5a. The opposite pair of Liu gold bearing elements 6, 6a is loaded as shown in Figure 3B. This in turn contributes to the grip of the roll shell 3 in its position parallel to the level of the external load F.

10

The bearing element 5 moving with the roll shell 3 mechanically engages the spindle pin 22 by moving the spindle pin 22 and the slides 23 and 24 to the position shown in Figure 4A.

According to Fig. 4A, the slide 23 has moved completely in front of the radial channels 26a located closer to the sliding bearing 5 and the end slide 24 has slid at least partially away from the annular groove 25 in the deeper cylindrical space 21. The supply channel 14 for the sliding element 20 is thus completely closed. The supply channel 12 and the flow path (opening X2) to the slide element and further to the pressure spaces 9 and 9a have been opened. Thus, pressure medium P can be supplied through the first feed passage 12 to at least maintain the holding pressure on the bearing elements 5 and 5a, and thus to provide lubricant-20 lubricant between the inner surface 3a of the roll shell 3 and the sliding surfaces of the bearing element 5. In a preferred embodiment, the valve dimensions are selected such that when the slide member 23 (33) closes the connection from the second supply channel 14 (15) to the outlet channel 16 (17), the connection from the first supply channel 12 (13) to the channel 16 (17) 32) after a certain business trip.

The dimensions of the valve 20 (and 30) are chosen such that the flow path (from opening X2) formed between the annular groove 25 and the end chute 24 is preferably adjustable, at about 3 millimeters. The adjusting margin of the control valve 20 (30) makes it possible to compensate for changes in external loads and bearing forces which otherwise tend to move the roll shell 3 from its substantially stationary position. The adjustment margin (corresponding to the distance the sheath moves when the pressures are applied) can be: '': less than 3 millimeters, but the adjustment margin also has another function, · ·, which requires a travel of about 3 millimeters. With a 3 mm adjustment margin you can! * ', provides a mounting space for shaft-mounted abrasion pads on which the sheath rests': 35 lowers when hydraulic pressures are lost (eg during power failure).

8 116081 This causes the bearing elements to sink to the bottom and the sheath to be supported by wear pieces. The corresponding structure is also preferably provided by a control valve 30 arranged in connection with the plain bearing element 6.

The above arrangement of control means provides the advantage that the pressure chamber of the sliding bearing elements (closest to element 5 and 6) can completely close such leakage channels or leakage paths whether the roller sheath 3 is struck or not. Thus, in practice, only the lubricant supply channels (9b and 10b) of the bearing element remain the exit path of the hydraulic pressure medium P. This 10, in turn, ensures sufficient lubricant between the inner surface 3a and the sliding surfaces.

Claims (7)

116081 A deflection compensated roll (1) of a paper / board or finishing machine having a stationary roll shaft (2) and a roll sleeve (3) 5 rotatably supported therewith by sliding bearing elements (5, 6, 7). a shaft (2) being loaded on the roll shell (3) in at least one substantially radial direction (F) of the roll (1), the slide bearing elements being provided with means for supplying hydraulic pressure medium (P) to load the slide bearing elements (5, 6, 7) with hydraulic pressure medium P) in which the means for supplying the hydraulic pressure medium (P) are provided with control means by means of which the sliding bearing elements (5, 6, 7) can be loaded against the radial load (F) so that the roll casing (3) to move to different operating positions relative to the roll axis (2) or to remain in a substantially fixed position relative to the roll axis (2), characterized in that the brows includes control means for supplying a continuous flow of lubricant between the inner surface (3a) 15 of the roll shell (3) and the slide bearing elements (5, 6, 7) in all positions of the roll shell (3). Roll according to Claim 1, characterized in that the control means comprise a control valve (20,30) associated with the sliding bearing elements (5,6), which is connected to the first supply channel (12,13) of the hydraulic pressure medium (P) to hold the roll shell substantially in a stationary position; coupling means (22, 25, 26, 27, 40; 32, 35, 36, 37, 50) arranged on the second supply channel (14, * 15) for moving the roll jacket 3 optionally relative to the shaft (2) in connection with the control valve (20, 30), 25 wherein the first supply channel (12,13) is openable by a sliding bearing element (5,6). ''; and the second supply channel (14,15) can be closed, and by means of which coupling means (22, 25, 26, 27,40; 32, 35, 36, 37, 50) the second supply channel (14,15) can be opened by the sliding bearing element (5, 6) for loading and first feeding; Channel I (12,13) can be closed. y 30 i · .. A roll according to claim 1 or 2, characterized in that the control means: ''; comprises a valve (20, 30) having a cylindrical shaft arranged in connection with the shaft (2). A space, an elongated mandrel pin (22, 32) extending from the first end; , mechanically connected to the sliding bearing element (5, 6) and arranged in a *: 35 partial longitudinal distance into the cylindrical space, two slider portions (23, 24; 33, 34), which are followed in the cylindrical space by the spindle pin (22, 32). 116081 for moving the hen, with the slider portions (23, 24; 33, 34) delimiting the supply space (21, 31), the first supply channel (12,13) and the second supply channel (14,15), of which the hydraulic pressure medium (P) is optionally provided (23, 24; 33, 34) guided to the feed space (21, 31), and an outlet channel (16,16a; 17,17a) through which the hydraulic pressure medium (P) can be fed from the feed space (21, 31) to the slide bearing elements. (5, 5a; 6, 6a). Roll according to Claim 2 or 3, characterized in that the control valve (20,30) has an adjustable clearance (X2) when driving the roll shell (3) in a fixed operating position. Roll according to Claim 4, characterized in that the adjusting clearance (X2) is preferably at most about 3 millimeters. Roll according to one of the preceding claims 2 to 6, characterized in that pressure control means (14a, 15a) and connecting ducts (14b) connected to the pressure spaces (9,10) of the sliding bearing element (4, 6) are arranged in connection with the second supply channel (14,15). , 15b) provided with a non-return valve (40, 50). Roll according to one of the preceding claims 2 to 6, characterized in that when the flap part (23, 33) closes the connection from the second supply channel (14,15) to the outgoing channel (16,17), the connection from the first supply channel (12,13) is opened. . i to the channel (16, 17) after a certain travel of a karat pin (22, 32). • $ * Ψ »· * I>» * * * • · · ♦ i f 116081