FI116410B - Deflection compensated roll - Google Patents

Description

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Deflection roller Mot böjning compenserad Vals 5

The present invention relates to rolls, particularly rolls of a paper machine or the like. More particularly, the present invention relates to a deflection compensated roll, in particular a composite jacket roll, according to the preamble of claim 1.

10 Such a deflection compensated roll, especially a composite jacketed roll, includes: a stationary roll shaft having a loading cavity for a pressurized medium and a loading arrangement such as a loading shoe, and towards the inside surface of the roll shell; wherein the loading arrangement has recesses open towards the inside surface of the roll shell, which form chambers with the inside surface of the roll shell to which a pressurized medium is introduced.

Various properties in the direction of the circumference of the sheath and of the roll axis are required for a shoe-loaded deflection compensated roll, and in particular for a roll of such roll.

"Deflection compensated rollers are commonly used as nip rolls, and in this case the shape of the roll should remain the same at high nip loads. However, in those cases, when nip pressures are to be profiled in the roll axis direction, the roll roll stiffness must be Typically, deflection-compensated roller sheaths are thicker cast iron sheaths, whereby profiling of nip pressures requires extremely high forces on the roller sheath, which may in some cases make it • advantageous to make the roller sheath slimmer. however, thinning of the nappies.

'Y' 30 Another problem with current deflection compensated rolls is the high weight of the thick roll shell and the disadvantages of this weight. One major disadvantage of the weight of the 116 4 Ί ϋ 2 roll mantle is that the vibration properties of the roll mantle are poor. The previously known so-called. shoe rolls are usually hydraulically deflection compensated zone-adjustable rolls in which the diaper is supported and loaded from a non-rotatable roll center axis by a hydrostatic loading arrangement such as a load shoe row. The load shoe row is also generally divided into zones, whereby the load pressure can be adjusted in the transverse direction of the web, i.e. the MD direction, i.e. in the CD direction, according to the need for profiling. The zone division of such a zone-adjustable shoe roll may be subdivided into individual loading arrangement elements, whereby the number of belt 10 can increase in the roll loading arrangement to more than 60 - examples include the applicant's trademarks SymCD ™ and eight zones - examples include shoe rolls marketed by the applicant under the trademarks SymZ ™, SymZS ™, SymZL ™ and SymZLC ™ 15.

The problem with such deflection-compensated thin-shell rollers, especially composite-shell rolls, is the stability of the circumferential lubricating film of the diaper and the reduction in its strength in the area of the nip and the load exerted on it; '20 between ink pens. The problem is caused by the nipple load between the deflection compensated roll and its counter roll which flattens the diaper roll and bends the load assembly, whereby the roll envelope and the lubricating film between the load application and the thin roll roll are deformed; when at the periphery of the load assembly, the edge gap between the thin-shell roll casing and the load-25 assembly becomes so large that all hydraulic fluid, preferably oil, fed through the load assembly, can escape from said supported edge gaps without forming a lubricating film; ; between the jacket of the diaper roll. Here, the problem is the contact between the thin-shell roll shell and the loading arrangement and the web profiling problems.

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From the patent applications CA 2,227,790 and WO98 / 04844 there are known load-bearing shoes of a thin-skinned flexural compensated roll, each of which has a central lubricating fluid and load pocket and a substantially smaller load-bearing load-bearing shoe on both sides.

It is a primary object of the present invention to provide an improved butter pump compensation roller in which the aforementioned problems in the direction of the roll axis and / or circumference could be eliminated or at least substantially reduced.

This object is achieved by a deflection compensated roll such as those mentioned above, the specific features of which are set forth in the appended claims.

| 1 15 Thus, the invention is based on a new and inventive idea that the profile of a roll shell! in order to improve oscillation in the axial or CD direction of the roll mantle, the pressurized medium is led to a loading arrangement between the roll mantle and the shaft having a plurality of consecutive loading pistons in the CD direction with a pressure space pressure below

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•:: Adjustable for each piston individually or by zone for a few pistons: 1 to 20 groups or all at the same pressure, and one or more sliding elements cooperating with the load piston. Each slide element *; '' Comprises a roll in the axial or CD direction substantially at least two at the nip ;;; The pressure pocket, or profiling chamber, per load piston, and these profiling chambers can each be individually pressurized to provide a profiling pressure. To ensure the lubricating film is stable, the roller sheath and the load !! between the slide each sliding element comprises an MD · or, in the circumferential direction, a nipple at the inlet and outlet sides of one or more recesses. peripheral or lubricant chambers / rows to which lubricant medium is pressurized.

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According to a preferred embodiment of the invention, the profiling medium is supplied to the profiling chambers and the lubricating medium to the peripheral or lubricating chambers. In this case, it is advantageous for the higher pressure to be tracked into the profiling chambers, whereby the pressures in the peripheral chambers are clearly lower than in the profiling chambers. Thus, the load on the diaper outside the nip is reduced and thus the diaphragm flattening is reduced and the lubricating film thickness is equalized.

According to the invention, it is preferable that the hydraulic loading and lubricating medium, preferably the oil, is fed to the loading arrangement along a separate loading and lubricating material line. It is likewise preferred that the profiling medium, preferably the oil, is fed to the loading arrangement along a separate profiling medium line. In this case, it is further preferred that the supply of both the loading and lubricating medium and the profiling medium be effected as capillary supply through the loading arrangement.

According to the invention, it is preferable that the loading element comprises: - one loading piston and one sliding element, - several loading pistons and one sliding element, - several loading pistons and several sliding elements, whereby the loading elements may be as many as the sliding elements or be less than the sliding elements, or: '' - the piston and the sliding element consist of an integral structure.

'' The invention will now be described in more detail by means of a preferred embodiment of the invention, with reference to the accompanying drawings in which 25 ;;; * FIG. 1 is a cross-sectional view of a first preferred embodiment of the invention; 'Inside the flexural compensated composite jacketed roll'. ': Half load arrangement, FIG. 2 is a side elevational view of the loading arrangement of FIG. 1, FIG. 3 is a top plan view of the load assembly of FIGS. 1 and 2; 4 is a top plan view of another embodiment of the loading arrangement of the invention FIG. 5 is a side elevational view of a loading arrangement according to a third embodiment of the invention.

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The deflection compensated roll according to the figures includes a thin-walled jacket 2 rotating about the stationary axis 1, preferably of composite material, which together with the outer surface of the counter roll 3 forms a nip N where the nip load tends to deform the diaper 2. The stationary shaft 10 comprising a row of hydraulically actuated loading pistons 20 in the CD direction, which may be several tens of rolls, to compensate for the deflection of the roll and to load the roll shell against the backing roll. The stationary shaft 1 is provided with a hydraulic loading cavity 4, 4 ', 4 "for each loading piston 20 fed with pressurized medium, preferably hydraulic oil, through a supply channel 5. Each loading piston 20 may have its own pressure supply line 17 and be provided with a roll Through the supply passage 5, the pressurized medium is introduced into the loading cavities 4, 4 ', 4 "to move the loading element 10 radially relative to the axis 1. The loading element 10 consists of a loading piston · · v * 20 of this 20 and one or more sliding elements 22 substantially connected thereto by the pressure obtained by the hydraulic medium in the loading cavities 4, 4 'and 4 ". the loading element 10 is loadable towards the inner surface of the sheath 2 * »» «» * · "to bring the sliding surface 10a of the sliding element 22 against that inner surface of the sheath 2. A lubricant film is formed between the sliding surface 10a and the inner surface 2 of the shell 2 by passing a pressure medium through the sliding surface through the loading element 10. recesses 10a. The recesses F in the sliding surface 10a of the sliding element 22 between the loading element and the sheath 2 form lubricating chambers 12 · '* and 12' with the inner surface of the roll sheath 2, into which lubricating fluid flows from the capillary channels 13. The lubricating chambers 12, 12 'are located on either side of the central row of profiled chambers 11 in the axial or CD direction, separated by the bases 16, on the sliding element 22 according to the invention. There may be several successive lubrication chambers in the CD direction.

Fig. 2 shows a deflection compensated roll loading arrangement 5 according to Fig. 1, consisting of a plurality of successive loading elements 10, each comprising a single loading piston 20 and a sliding element 22, axially cutting the roll at the nip, i.e. the central profiling chambers 11. A pressure medium is introduced into the loading cavity 4 "of each element 10 from a pressure line 17, the pressure of which may be adjustable independently of the pressure of the other loading pistons 10. , along the corresponding profiling pressure lines 18, 18 'and 18 "through capillary channels 14.

! The capillary channels 14 are insulated from the pressure of the loading cavity 4 "by means 6 which are tubular connections allowing fluid flow and radial movement of the element 10, preferably flexible hoses, thereby providing a profiling medium independent of the loading pressure prevailing in the loading cavity 4". The pressure of each pressure line 18, 18 ', 18 "is individually adjustable by means of a control valve which may be located outside the roll in the valve cabinet or in the roll itself, e.g.

: 20 roller ends in integrated valve block. The profiling chambers 11, 11 ', ... have i: at least two per one load element 10. I saw one load bearing- | In the area of the pad 10, a more accurate profile adjustment capability is obtained than solutions of the prior art have been possible because the number of adjustable profiling chambers is greater than the number of loading elements. For example, with a roll of class 10 m having a number of load elements of about 60 and a CD width of a sliding surface 10a of load element 10 typically of about 145 mm, the profile of load element according to the invention is achieved with profiling accuracy of at least half width or takes /, · the cap more accurate. Alternatively, if it is not necessary to increase the profiling accuracy, the length of the element may be increased and the number thereof in the roll may be reduced; '· Without loss of readiness.

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Fig. 3 is a plan view of a sliding surface 10a of the loading element 10 according to Figs. 2 and 3. Generally, the sliding surface 10a of the loading element consists of an edge cap 15, circumferential spacers 16 and axial-I 5 intermediate spacers 19, and recesses 11, 12 located between these bases, the loading element being in contact with a thin oil film on the roll shell. In the slider element structure of Figure 3, the sliding surface 10a consists of three rows of circumferential recesses 11, 12, 12 'having a central row of profiling chambers 11, 1Γ, 11 "located substantially at the nip and lubricating chamber rows 12, 12' on either side of this row. .

Preferably, in the sliding surface structure of the invention, the sliding surface 10a consists of a plurality of rows of spaced apart recesses of the bases 16 which open onto the sliding surface 10a and form a row of central profiling chambers 11 11, 12, 12 'in a row of chambers 11, 12, 12' separating the chambers 11, 12, 12 'axially from one another in the circumferential direction of the roll shell 2 with chambers 11, 12, 12' in the adjacent row, i.e. chambers 11, 12, 12 ' preferably form a brick-walled structure with individual chambers * in parallel rows of chambers 11, 12, 12 '. 'Is axially moved, for example, half of the chamber 11, 12, 12' a measure of comparison "· * of the second row ran the chambers 11, 12, 12 'relationship. In this case, the CD direction over the entire load element 10 of the box is provided with respect to each other in overlapping to-25 telukammioiden thanks to at least one of lubricating chamber 12, 12 'with continuous lubrication effect ;;;' without discontinuity.

': According to the invention, in the loading element 10 at the nip N, a parallel chamber consisting of discrete chambers 11, 12, 12' in the MD direction; 30 can be used to: 8 116 4ί ϋ • profile the axial or CD direction and smooth and reduce the deformation of the track mantle in the MD direction, and • ensure the lubricating sliding film retention in the MD direction within the loading member 10.

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In the embodiment of the invention according to Fig. 3, the chambers 11, 12 and 12 "preferably have three rows in the circumferential or MD direction of the roll casing and at least two chambers in the region of each loading element 10 having independently adjustable fluidization pressure. however, it should be noted that with more than one central row of profiling chambers and four rows of lubricating chambers arranged on either side of the 15 rows of profiling chambers, substantially advancing the object of the invention.

In the solutions described above, each load element 10 consists of a single load piston 20 and an integral sliding element part 22. Within the scope of the invention, it is also possible to have a solution in which a single sliding element 22 extends into the area of several load pistons, e.g. 10 over the length of the 20 * impact area of the load piston, or at its extreme over the entire axial length of the roll shell. Figure 4 illustrates a case where the slider element 22 extends over three !! 'The length of the load piston. The positions of the loading pistons 20, 20a, 20b are shown in dashed lines in Figure 4. The sliding surface 10a of the sliding element 22 contains the invention. . Profiling chambers 11 according to the invention with a number of at least two · · * * piston pistons per 20 piston. In the case of the image, the effect area of one loading piston 20 has three profiling chambers (11a, 11a ', 11a ", 11b, 11b', 11b", etc.).

> «»:,; The pressure exerted on each of the profiling chambers is individually adjustable independently of the pressures of the other profiling chambers. Thus, the profiling width can- '·'; may be selected narrower than the division of the loading pistons 20 of the loading arrangement.

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Preferably, the number of profiling chambers 11 is greater than the number of lubricating chambers 12 in a single row of ointment chambers. This provides, for example, a brick-walled heel pattern which is advantageous to ensure the stability of the lubricating film. When the number of profiling chambers 11 in the sliding element per load piston is three, it is preferable that the number of lubricating chambers in one row of lubricating chambers is one or two. If there were two profiling chambers 11 per one piston, the corresponding preferred number of lubricating chambers would be one.

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Figure 5 shows a third preferred embodiment of the inventive idea. As shown in the sectional view of the embodiment of this embodiment, the strain and lubrication film stability problems of the load assembly can be solved by following the load assembly 10 of the load assembly as a continuous and rigid element throughout the roll width in the CD direction. In this case, the loading arrangement 11 of the inventive idea has its own pressurized fluid supply 17 to the loading cavities 4 of the loading pistons and the lubrication and profiling of the roll shell 2 to have its own pressure. :: fluid supply 18, of which at least the fluid supply 18 associated with profiling is preferably provided with flow and pressure control. The advantage of such an arrangement is that the profile width and the load piston distribution can be separated and the profile chamber distribution up to 10 mm, but in practice long '...' rolls have a sufficient spacing of the order of 50-100 mm; '· · ·' 200 mm. When the chambers are denser than the load pistons 20, there is the advantage that the profiling width 25 can be selected to be narrower than the distribution of such load pistons. Sufficient lubrication film for loading element 10 and '; 'Between the roll shell 2 over the entire range of the loading arrangement is achieved when the loading. The sliding surface 10a of the sealing element 10 has at least three rows of chambers 11, 12 and 12 'in the MD direction, of which the central chamber 11 is imprinted with a projection:' 30 with the most dense nip, i.e. the maximum fluid pressure profiling pressure. In this case, the pressures in the peripheral chambers 12 and 12 'are clearly lower, whereby the load exerted on the roll casing 2 outside the nip is reduced and thus the flatness of the roll casing 2 is reduced and the lubricating film strength is equalized.

By changing the flow of pressurized profiling medium in capillary channels 14 of profiling chambers 11 and capillary channels 13 of lubricating media 12, 12 ', the deformations caused by nip load in diaper 2 can be substantially reduced, i.e., profiled in 2 deformation, i.e., lowering the wave peaks of the sheath 10 2, thereby substantially reducing and even preventing the lubricant from escaping between the sliding surface of the loading element 10 and the inner surface of the sheath 2, thereby ensuring the lubricating sliding film stability.

For profiling of the roll diaper in the CD direction, it is preferable that the maximum pressure of the pressurized medium 15 is provided in the MD row in the middle row of profiling chambers 11, whereby the pressures of the side chambers 12, 12 'are preferably kept substantially lower. Thus, the load on the sheath 2 outside the nip N is reduced and on the other hand the deformation tendency of the load element 10 is reduced. :: decreases in deflection and thus the flattening of the sheath 2 and the or [V 20] of the loading element 10 are reduced and the thickness of the lubricating film between the sheath 2 and the loading element 10 • '··, which together ensure the oil film remains in the sheath 2. '· I and the load element 10.

The invention has been described above only with reference to some preferred embodiments thereof. Of course, this is not intended to limit the invention to such individual embodiments, and as will be apparent to one skilled in the art, many alternatives and variations are possible with the inventive:. '· I within the meaning and scope of the claims as defined in the claims.

; · 30 Thus, it should be noted that 11 11 tA Π) • that the capillary tubes 13, 14 of the lubrication and / or profiling chambers may be provided with a throttle, • that the loading cavities may be combined into a single cavity common to all fluid chambers; • that the drop-off-side and the supply of lubricating channels 12, 12 'reaching the pressure may be the same or regulated separately.

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Claims (15)

A bending compensated roller, in particular with a composite sheath, which roll forms a nip (N) with a counter roll (3) and comprising: a stationary roller shaft (1) and a rotary shaft (1) arranged rotatably about the roller shaft (1). 2), which can be loaded radially with an inner load arrangement acting against the inner surface of the roller sheath (2), to which belong several plungers (20) located in the CD or axial direction, the pressure in the load holding chamber (4) below these can be individually regulated by a pressure medium conveyed to the load shaft (4,4 ', 4') located in the roller shaft (1), and one or more sliding elements (22) connected to the load piston (20), the load piston (20) and the sliding member (22) together form a load member (10), a sliding surface (10a) of the load member (s) (10) located on the inner surface of the roller sheath (2) comprising strips (15,16,17). enclosed recesses (11,12) for receiving tr a medium in these, characterized in that in order to improve the profileability of the roller sheath (2) in the axial or CD direction of the roller sheath (2), each load element (10) comprises a row substantially opposite the nip (N) (11) of profiling chambers, the row comprising for each load piston (20) at least two, 20 with peripheral or MD-directed intermediate strips (19) separated from each other by different depths or profiling chambers (11,1Γ). , which can be pressurized separately. . . Bending compensated roller according to claim 1, characterized in that the load element (10) comprises in the circumferential direction on both sides of the frame. That of profiling chambers (11,11 ') at least one row of lubrication chambers (12,12'), which row comprises one or more recesses or lubrication chambers. 16 11641 (j Bending compensated roller according to claim 1 and / or 2, characterized in that the number of profiling chambers (ΙΙ, ΙΓ) is three for each load piston and the number of lubrication chambers in a row of lubrication chambers (12,12 '). is one or two. 5 5. Bending compensated roll according to any of claims 1-4, characterized in that the pressure is arranged to be greater in the profiling chambers (ΙΙ, ΙΓ) than in the lubrication chambers (12,12 '). Bending compensated roller according to any of claims 1-5, characterized in that the pressure medium is led to a capillary channel (13) opening in the lubrication chamber (12, 12) from the load space (4) between the load element (10) and the shaft. (1), which space communicates with a pressure line (17) through the drum shaft (1) via a drilled bore (5). 15 Bending compensated roller according to any one of claims 1-6, characterized in that the pressure medium is guided via a capillary channel (14), which opens in the profiling chamber (ΙΙ, ΙΓ), insulating the ffan pressure space in the load casing (4 ") along a separate pressure line. (18). 20 t r · 8. Bending compensated roller according to any of claims 1-7, characterized in that the load element (10) comprises a load piston (20) and *,. a sliding element (22). <a Bending compensated roller according to any one of claims 1-7, characterized in that the load element (10) comprises several load pistons (20). _. and a sliding element (22). * · A t · a * t 10. Bending compensated roller according to claim 9, characterized in that ;;; The load member (10) comprises 2-10 load pistons (20,20a, 20b) and a slider (22). 17 116410 11. Bending compensated roller according to any of claims 1-7, characterized in that the load element (10) comprises several load pistons (20,20a, 20b) and several sliding elements (22). 5 12. Bending compensated roller according to any one of claims 1-11, characterized in that the load element (10) comprises the same amount of load pistons (20, 20a, 20b) and sliding element (22). Bending compensated roller according to any of claims 1-11, characterized in that the number of load pistons (20, 20a, 20b) in the load element (10) is smaller than the number of sliding elements (22). Bending compensated roller according to any of claims 1-13, characterized in that the load piston (20) and the sliding element (22) in the load element (10) are formed by an integrated structure. t · · • »I · * t * * I I · M