FI116538B - Storage arrangement for paper / board machine roller - Google Patents

Description

χ 116538

Paper / board machine roll bearing arrangement

The present invention relates to a bearing arrangement for a deflection compensated roll of a paper / board machine or a post-processing machine, which roll includes a roll shell bearing rotatably rotated about a stationary roll axis. One particular object of the invention is a bearing arrangement for a composite jacket deflection compensated roll.

Rollers forming a dewatering press nip, smoothing nip or calendering nip with a counter roll are commonly used in paper machines. For these uses, it is important that the nip line pressure distribution, i.e. the profile in the axial direction of the rolls, is made constant, or that this profile is adjustable as desired, for example to control the transverse moisture profile and / or thickness profile (caliber). To this end, various flex-compensated rolls 15 are known in the prior art which are intended to influence the line pressure distribution of the nip.

Of particular interest for profiling are deflection compensated rolls, the sheath of which is sufficiently adaptable to be able to react to the pressure exerted by the loading elements, even when the element / chamber distribution is dense. Fiber-reinforced diaphragms of plastic composite or thin metal are preferred.

• · · • j. A variety of deflection compensated rolls for a paper machine are known in the art.

• «« ·: * '*: These rollers generally comprise a solid or tubular stationary roll axis and • a roller sheath rotatably arranged around it. Between said shaft and the casing there are • * · * · * · *. The hydraulically-loaded elements acting on the inner surface of the jacket and / or: '' '; a pressure medium chamber or set of chambers so that the axial profile of the diaper at the nip can be adjusted or adjusted as desired. Generally, nipples formed by such rolls, such as press nips or calendering nipples, are loaded with loading forces applied to the shaft pins of the deflection compensated roll and its counter roll.

Deflection-compensated rolls may be so-called "roll-offs". load-bearing rolls in which the roll shell is generally mounted at its ends on the shaft such that the ends of the roll shell cannot move radially relative to the shaft or so-called. load arms- 116538 2 towers rolls in which the stroke length of the piston-cylinder elements of the hydraulic load elements is adapted such that it also provides sufficient nip opening and closing movement even without the need for powered load arms acting on the roll shaft ends. In such non-load bearing rolls 5, hydraulic loading elements acting against the inner surface of the roll shell provide not only deflection compensation and profiling but also the actual nip pressure load. A disadvantage of the prior art load-bearing deflection-compensated rolls is the complexity of the structure and the difficulty of providing sufficient stroke length for the stationary center shaft and roll piston cylinder elements and providing sufficient nip loading and compensation forces. In particular, the end areas of the roll mantle have proven to be particularly problematic in this respect. The end zone bearings can be implemented by rolling or sliding bearings.

In the impact-sliding roller bearing, the bearings are implemented with 4 ... 8 hydrostatic slide bearings which move in the direction of the nipple by an impact. The position of the shoes is adjusted by the required loading pressure. FI patent 98320 discloses an impact stroke deflection roller sliding bearing in which the roll shell can be displaced relative to the roll axis both in the plane of the main loading direction and in a lateral bearing plane perpendicular thereto. An embodiment of such an impact or moving sheath roll is described in more detail below in connection with Figs. 1-3. you.

However, with the current impact plain bearing, it is not practically possible to perform • <* • strokes due to the inclination of the side shoes.

j \ ·; 25: "*; The striking rolling bearing technology is capable of effecting a somewhat larger I * * stroke with a structure in which the roll shell is rotatably mounted on bearings '' fitted over the ring members fitted between the ring members and the central axis, generally actuated by an angle; 30 cylinder units to effect the impact. There are two pistons on the side of the nip and on the opposite side of the nip in order to transfer the required force through the bearing into the sheath. The pistons are mounted at corners to minimize the need for space.

Such a solution has been described in the applicant's previous patent FI 79177. In addition to the difficulty of achieving the minimum load, the rolling stock has the disadvantage of being speed-limited, which has increased the interest in roller bearings. In addition, the solution of FI 79177 is not suitable for composite jacket, since achieving the minimum load on a spherical roller bearing is particularly difficult for a composite jacket because the mass of the composite jacket (about 1000 kg) is very much less than . Also, the composite sheath does not need to profile the end region with a bearing such as a cast iron sheath.

10 In the shock-free plain bearing roller, the bearings are made with hydraulic plain bearings, which are always positioned in the same position by means of a control valve. The required impact is achieved by separate off-roll loading cylinders. From Finnish patent application no. 20001099 is a known solution for roller bearings without impact. Such a solution is described in more detail below with reference to FIG.

It is an object of the present invention to provide a bearing solution which achieves sufficient stroke lengths and, at the same time, effective bearing which is not speed limited. It is another object of the invention to provide a deflection compensated roll of a paper-20 / board machine or a post-processing machine comprising a roller sheath of composite material which is rotatably mounted around a stationary roll axis.

• · «5 • f * | In order to achieve the objects of the invention, the bearing system according to the invention is characterized by the features set forth in the characterizing part of claim 1. Biscuits; the composite jacketed roll according to the invention is characterized by

I I V

the matters set forth in the characterizing part of claim 6.

The invention will now be described in more detail in the accompanying drawings; Figures 1 and 2 are schematic sectional views of a prior art sliding-bearing tubular roll, 4116538 Figure 3 is a schematic view of a prior art arrangement for supporting a roll diaper in a load direction that allows movement of the roll mantle relative to Fig. 5 is a schematic view of another prior art arrangement for supporting a roll diaper in a load direction that holds the roll mantle relative to the roll axis; Fig. 5 schematically shows a vertical section of a roll equipped with a bearing arrangement 10 according to the invention;

Figures 1 and 2 are schematic sectional views of a prior art sliding-bearing tubular roll 15 with Figure 1 being a vertical sectional view of the roll and Figure 2 being a sectional view taken along line II-II of the roll of Figure 1. In Figures 1 and 2, the deflection compensated roll is generally designated 110 and comprises a stationary roll shaft 111 on which is rotatably mounted a roll shell 112 supported by hydraulic loading elements 117 on the roll shaft. Hydraulic Loading Elements 117. · · *. acting in the nip plane direction and adjusting the roll casing 112. . shape and control the axial nip profile of the roll. Hydraulic pressure medium. . applying pressure lines 117a either individually to each element 117 or otherwise:,. man for groups 117.

i '· 25. The bearings of roll 110 are implemented by means of sliding bearing elements, of which in the direction of the load, in the case of the roll according to Figures 1 and 2 in the nip plane, the sliding bearing elements 114 and 114a are denoted. First, pairs of sliding bearing elements 114a act in the direction of the nip, i.e. against the load, and the second sliding bearing elements 114a act in the opposite direction. In the embodiment of Figures 1 and 2, it is further shown that the roller 110 is also provided with sliding bearing elements 115,115a acting transverse to the direction of loading and acting in opposite directions. Roller 110 is a fully sliding bearing roller which is also provided with axially acting 116538 5-inch plain bearing elements 116,116a which are supported by oil film on the roll ends 113,113a. As shown in Figures 1 and 2, the radially acting sliding bearing elements 114,115,114a, 115a are supported on the inner surface of the roll shell 112 via an oil film. In the illustration of Fig. 1, the radially oriented sliding bearing ribs 114,114a, 115,115a are arranged in pairs such that each of the sliding bearing ribs is arranged in two axially adjacent directions. However, from an operational point of view, such an arrangement is not a prerequisite, since the bearings can also be implemented, for example, with one of the plain bearing elements only.

10

Figure 2, in turn, shows that the plain bearing elements 114,114a, 115, 115a are arranged to act in the load direction and in the transverse direction thereto. In the example of Fig. 2, the plain bearing elements 114,114a are adapted to act radially in different angular positions.

15

Figure 3 is a schematic sectional view of one prior art arrangement for roller bearing with impact plain bearing.

Also shown in Fig. 3 is the roll axis denoted by reference numeral 111 and the roll mantle by reference numeral 112. The roll mantle 112 is supported against the inner surface 122 of the roll mantle by sliding bearing elements 114,115 acting in opposite directions such that the first sliding bearing element 114 is loaded. the roll casing 112 towards the external load exerted on the roll casing, i.e. towards the. nip and the second sliding bearing element 115 in the opposite direction, respectively.

: vj 25: ··; In the structure of Figure 3, the plain bearing elements 114,115 are provided with pressurized cavity compartments 61, 62, and for each of the plain bearing elements 114,115 are mounted body members 63, 63a of the roller shaft 111 which project to said sliding bearing members. the cavities 61, 62 of the body elements with respect to which the body members 63, 63a are sealed by means of seals 70, 71 so that the sliding bearing elements 114,115 can move relative to the body bodies 63,63a. The plain bearing elements 114, 115 are conventional in construction, provided with oil pockets 64, - 65 on their outer surface, which are connected to the pressure spaces 61.62 through capillary bores 66, 67 passing through the plain bearing elements. Thus, from the pressure spaces 61.62, oil is allowed to flow through the slots of capillary port 116538 6 into oil pockets 64, 65 to form an oil film between the sliding bearing elements 114,115 and the inner surface 122 of the roll shell.

Fig. 4 illustrates an arrangement according to application 20001099 for engaging roller bearing 5 without shock. The figure shows a stationary roller shaft 1 rotatably arranged with a roller sheath 2, the external loading of which is denoted by the reference F. The bearings acting on the load plane include an anti-load sliding bearing element 3 connected to the cavities 12 and a sliding bearing acting on the load direction. 10 cavity space 13. These load bearing sliding bearing elements 3, 4 are controlled by a control valve 7 which is mechanically coupled to the sliding bearing element 3 and receives its control directly from the movements of the element. When the element is subjected to external load, the pressure flow through valve 7 under its element cavity 12 immediately increases, while the opposing element 4 is kept at a minimum pressure. In this case, the sheath and shaft of the roller-15 do not move relative to each other. The operation of such a shock-free bearing is described in more detail in the aforementioned FI application 20001099 and is not further described herein. The side bearing of the roll shell is implemented by means of the side bearing elements 5 and 6 in a manner known per se, for example according to FI patent 98320, and its operation is no longer described in more detail.

.:. Figures 5-6 illustrate schematically a sectional view of the solution according to the invention. * ··. tona. According to Figures 5-6, the bearing arrangement 170 according to the invention includes a non-rotatable load ring 162,: '' mounted on a fixed central shaft 161. > 25 about which a sliding bearing is arranged, in which the embodiment shown. · · · Includes hydrostatic sliding bearing elements 164 acting in the main loading direction KK and corresponding sliding bearing elements 165 acting in the transverse direction, having oil pockets 166 on the sliding surface of the sliding bearing elements. the pair acts in the direction of the main load and the other pair acts in the direction of the main load. The number of elements may be greater or less than this. In this case, the roll shell 160 remains substantially stationary with respect to the load ring 162, but also moves with the load ring 162 in the K-K plane of the main loading direction relative to the roll shaft 161.

The load ring 162 is supported on the roll shaft 161 by means of power units comprising cylinder bores 169 formed in the ring portion 162 which are movably fitted with hydraulic pistons 163,173 supported on the roll shaft 161. According to Figs. such that their direction of action substantially coincides with the direction of the load plane KK. The arrangement further comprises guide members or side bearings 171 disposed on opposite sides of the roll axis 161 with respect to the load movement, which maintain the load movement of the load ring 162 substantially linear. Fig. 6 shows hydraulic load elements with reference numeral 117 and elements forming counter-zone with reference numeral 117b. Reference numeral 116 describes axially acting plain bearing elements 15.

When it is desired to move the roll towards or away from the counter roll, it is done by moving the ring in the load plane by means of power units. The pressure medium is introduced into the space 172 beneath the second hydraulic piston 163, e.g., through the shaft 161 or by separate tubes. 20 The pistons 163 are closed and there is no oil flow through to the outside of the tire. Tire. ···. gas moves relative to axis 161. At the same time the diaper moves. The transfer distance is maximal at the stroke X allowed by the piston 163. Power plant placement. '·. the ring between the bearing elements is advantageous for space reasons whereby the roll diameter: no need to enlarge.

25th · *. The arrangement according to Figs. 5-6 allows even large stroke lengths of the load ring, in the load plane K-K direction, e.g., on the order of greater than ± 60 mm or more:. since the power units are positioned such that their direction of action substantially coincides with the direction of the load plane K-K. In the prior art impact roller bearing arrangement, the angular positioning of the power units causes problems with respect to the length of the stroke, and furthermore, the roller bearings are speed-limited, which is overcome by the solution of the present invention employing slip-oscillation around the load ring. The plain bearing can also be implemented without impact, e.g. as a hydrodynamic bearing or a hybrid bearing, in which small oil pockets or grooves are formed on the outer surface acting as a bearing surface of the load ring.

«1»

Claims (9)

A storage arrangement for a bending compensated roller for a paperboard machine or finishing machine, said roller having a roller shaft rotatably mounted around a stationary roller shaft, comprising: an arrangement (170) adapted to the end section of the stationary roller shaft (161) ) which is arranged to move radially relative to the roller shaft, between the load ring (162) and the roller shaft (161) arranged load members (163, 173) viewed in the direction of the load movement (KK) on opposite sides of the roller shaft, which load means provide the load ring ( 162) the desired load movement, and relative to the load movement seen in transverse direction p opposite sides of the roller shaft (161) arranged control means (171), which maintain the load movement substantially linear, characterized in that the supporting layer (160) of the roller sleeve (160) is formed inside the load ring (16). that between men and the load ring does not exist v sential rela-tive 15 movement. Storage arrangement according to claim 1, characterized in that the sliding bearing is realized as a hydrodynamic bearing. Storage arrangement according to claim 1, characterized in that the sliding bearing:, is realized as a hydrostatic shock-free bearing (164). • · · »• * * Storage arrangement according to claim 1, characterized in that the sliding bearing •, · · is realized as a hybrid bearing. : 'V 25 Storage arrangement according to any of the preceding claims, characterized in that the control means (171) is a sliding bearing. »» I »T. * # 6. Bending-compensated roller for a paper / cardboard machine or finishing machine: '; A roller, which has a rotatably mounted roller sheath (160) of composite material around a stationary roller shaft (151), between which roller sheath (160) and shaft (161) [. a hydraulic load element (171) is provided, the roller bearing comprising one. . adapted load ring (162) arranged within the end section of the stationary roller shaft (161), which is arranged to move radially relative to the roller shaft, wherein between the load ring (162) and the roller shaft (161) is arranged load means (163, 173). in the direction of the load movement (KK) on opposite sides of the roller shaft, which load means achieves the desired load movement of the load ring, and relative to the load movement seen transversely on opposite sides of the roller shaft, regulating means (171) which maintain the load movement Consequently, around the load ring, the inner supporting support bearing (164) of the roller sheath (160) is formed, so that substantial relative movement does not occur between the manifold and the load ring. 7. Vais according to claim 6, characterized in that the hydraulic load elements (117) can be controlled individually or in groups of several elements. 8. Load ring for the storage of a bending compensated roller for a paper / board machine or finishing machine, said roller having a rotatably mounted roller sheath (161) rotatably mounted, said load ring (162) being arranged to move radially relative to the roller shaft (161) by means of the roller shaft (161) as seen in the direction of the load movement (KK) on opposite sides of the load shaft (163, 173) arranged to effect the desired load movement of the load ring (162), whereby the internal bores are made in the load ring (161) (169) for receiving the load means, characterized in that the outer surface of the load ring (161) has bores for receiving the sliding bearing elements (164; 165). »• ·:, f: Load ring according to claim 8, characterized in that the sliding bearing members if: (164) receiving the outer surface bores are four, placed in pairs on both sides of the main load direction (KK) such that a pair of the sliding bearing elements arranged therein (164) act in the direction of the main load and the other pair towards the main load direction, and that the inner bore (169) of the load ring (162) is arranged in a position between the respective sliding bearing elements (164). * * * * * *; ·. 30 »• ·» I