• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a cast axle (11) for the roller (10) of a fiber web machine. The cast axle (11) comprises two end sections (19, 20) and a profile section (21) between the end sections (19, 20). Each end portion (19, 20) comprises a change region (31) over which the axle journal (24) changes to the profile part (21). The change range (31) extends to the load area (32) of the axis (11). The invention also relates to a roller (10) of the fiber web machine equipped with a cast axle (11).
    公开号:AT517790A2
    申请号:T50901/2016
    申请日:2016-10-05
    公开日:2017-04-15
    发明作者:
    申请人:Valmet Technologies Inc；
    IPC主号:
    专利说明:

    CAST AXLE FOR ROLLERS OF A FIBERMAKING MACHINE AND ROLLED EQUIPMENT WITH A CASTED AXLE
    The invention relates to a cast axle for the roller of a fiber web machine, which axis are assigned to two end sections and a profile section between the end sections, and each end section is assigned a range of change in which the axle pin assigned to the axle changes to the profile section. The invention also relates to a roller of the fiber web machine equipped with a cast axle.
    The molded axle comprising the molded axle is mainly used in the rolls of the fiber web machine in which the axle is not rotatable. The axis remains stationary, while the roller jacket mounted around the axle rotates. The cross-sectional profile of the profile part is usually of its basic shape I and in practice the main axis of the I-profile is in the loading direction of the roller. So even a thin I-profile can carry large loads, while the total mass of the axle remains low. In the so-called. Biegungskompensierten rollers, as in the shoe roll and its counter roll of the roll shell is supported and loaded by the fact that the pressures of the loading elements, which are arranged between the roll shell and the axis are controlled so that the line of contact of the roll shell with the Counter roll is as straight as possible.
    In the known deflection-compensated rolls, the cross-sectional profile of the axis is almost constant over the whole length of the nip width. The aforementioned load elements are located on the width of the nip. An attempt is made to keep the support distance of the axle tight so that the roller construction is as light as possible and low in cost. The well-known axis has a short range of change, in which the axle pin associated with the axle changes to the profile part. In practice, the cross section of the axis changes rapidly when the I-profile, which is large in terms of its cross-section, changes in terms of rotational symmetry and in terms of its diameter compared with the profile part to a small journal. In this case, when the nip is loaded with loading elements, the changes in shape of the axle are performed in a short range in which the cross section changes. Thus, the stresses in the range of change increase, which in turn results in thick-walled and so heavy constructions. In addition, a change range on a short route is difficult to achieve by casting technology. The journal and the range of change must also be rotated, which in turn increases the manufacturing cost. Turning a large axis requires a large lathe.
    The object of the invention is to produce a novel cast axle for the roller of the fiber web, which is lighter than before, but with the stresses caused by the change in shape being less than before. The characterizing features of this inventive axis can be found in the attached patent claim 1. In addition, the object of the invention to produce a novel cast axle equipped with a roller of a fiber web machine whose support distance is shorter than before The characterizing features of this axis according to the invention can be found in the attached patent claim 10. In the invention, the range of change of the axis is realized in a new and surprising manner, whereby local voltage spikes can be avoided. At the same time, the casting of the axle becomes easier and the need for machining is reduced. So the roller is well resilient, while the stresses are shared more evenly than before on the axle.
    In the following the invention will be described in detail with reference to the accompanying drawings describing the embodiments of the invention, in which in Fig. 1 a formed by the shoe roll and the deflection-compensated counter roll
    Langnipanordnung is viewed from the machine direction forth, in Fig. 2a, a Langnipanordnung is shown as a schematic drawing of FIG. 1 as a cross section, in Fig. 2b, a bend compensated according to the invention
    Counter roller as a cross section of a cast axle and is shown axonometrically
    3 shows a shoe roll according to the invention viewed from the side of the axle,
    In Fig. 4, a second shoe roll according to the invention viewed from the side of the axis is shown.
    In Fig. 1, a Langnipanordnung a fiber web machine is shown in principle, which is formed from the shoe roll 10 and from its counter-roller 14. The shoe roll is associated with a non-rotatable pressure axle 11 and a load-bearing pressure shoe 12 supported on the pressure axle 11. The shoe roll is associated with an elastic belt casing 13, which is arranged around the pressure axis 11. The shoe roll together with the counter-roller 14 between them a Langnip through which the fiber web is passed to press the fiber web. The pressure shoe 12 extends substantially over the entire width of the Langnips. Normally, a deflection-compensated counter roll is used which is pressed against the shoe roll into the circle of its belt mantle. The aforementioned pressure shoe 12 is designed to follow the shape of the roll shell of the deflection-compensated counter roll. In Fig. 1, the shoe roll 10 is in the lower position, although the shoe roll is normally in the upper position. In Fig. 1, the loading elements of the deflection-compensated counter roll 14 are not shown. In addition to the shoe roll, the deflection compensated roll may function as a counter roll for, for example, a hard shell-equipped press roll or the thermal roll of the calender. In addition, the shoe roll itself is a deflection-compensated roll.
    In Fig. 2, rolls 10 and 14 for the long-nip assembly are viewed from the ends. The direction of rotation of the belt jacket is indicated by an arrow. In Fig. 2a, a loading element 16 is shown for the shoe roll 10, which are close together on the route of the pressure shoe 12 (Fig. 1). Also in the machine direction, there may be two loading elements in succession. With the help of the loading elements 16, the pressure shoe 12 is forced to the counter roll 14. Between the sheaths of the rolls, the fiber web to be pressed normally remains between two press rolls or between the press felt and the counter roll (not shown). Also, the counter roll 14 has loading elements 17, by means of which the shape of the roll shell 15 can be forced into the shape of the pressure shoe 12 of the belt roller 10. It can be made straight with the help of the cooperation of the counter-roller and the shoe roll of the Langnip and thereby the guided through the long-nip fiber web is pressed as uniformly as possible over its entire width.
    In Fig. 2b, the known cast axle 18 for the roller of the fiber web machine is shown. The illustrated axis 18 may also be formed as the pressure axis 11 of the shoe roll 10. In Fig. 3 and 4, the axis 11 is assigned two end portions 19 and 20. Between the end portions 19 and 20, a profile part is arranged, whose cross-sectional profile is here I from its basic shape. In the direction of the major axis of the cross-sectional profile of the axle, the axle carries the load well, although the 'waist' of the tread is narrow. The main axis is represented by a dashed dot line. The spars of the I-profile correspond to the outer parts of the jacket so they are convex at the ends, wherein the shape of the axis of the shape of the inner surface of a circular roll mantle corresponds. In the other spar there is additionally a recess 22 in which the loading elements are arranged. The bearing of the roll mantle is supported at the two ends on the axis, while the loading elements are arranged substantially along the length of the entire profiled axis. Thus, the distance between the axis and the roll shell can be kept as desired and also the desired profile can be controlled. The importance of bending the axle is emphasized when the roller is in the lower position, with the axle bent both by the load and by its own mass.
    In Figs. 3 and 4, the axis 11 according to the invention is shown from the side. Each end portion 19 and 20 is assigned a change range 31 in which the axis 11 associated axle 24 is changed to a profile part 21. According to the invention, the change range 31 extends to the load area 32 of the axle 11. More specifically, the change range 31 extends in the axial direction at least on the axis 11 in the region of the arranged
    Loading element 16. Generally speaking, the loading area is the area between the outermost parts of the outermost loading elements, here the outermost cylinders. In practice, the cross-sectional profile of the axle has been changed in a surprising manner at the roll ends, where one or more loading elements in the fluent shape-changing region are outside the standard cross-sectional profile of the axle. In Figs. 3 and 4, the change region 31 extends in the axial direction on two to three axes 11 in the region of the arranged outermost loading element. Thus, the range of change was considerably extended in comparison with the known solution. Generally speaking, the length s of the change range 31 in the axial direction is 0.4-1.6, more preferably 0.6-1.2 times the diameter R of the axle 11. The load capacity of the axle relative to the mass is still improved. In practice, voltage spikes are set lower and distributed more evenly over larger areas while the mass of the axis decreases at the same time. In addition, the flowing and streamlined shapes are favorable in terms of casting technology. More specifically, the range of change is fluent convex.
    At the left end of Figs. 3 and 4, an end portion 19 cast opening 33 is shown, which extends from the end of the journal 24 to the change region 31. A corresponding opening is also located in the opposite end portion 20. The opening relieves the axis and in addition can be realized through the opening easily the implementation in the roll interior. Preferably, the opening 33 opens in the change region 31 on two opposite sides of the profile part 21. This facilitates, for example, the bushings such as the leadership of the hoses of the loading elements. In addition, the
    Cross section of the journal 24 conventionally rotationally symmetrical (Fig. 3) or a polygon (Fig. 4). In this case, the shape of the journal can be optimized and required for the support machining operations can be performed as shooting. Thanks to a flowing and long range of change, the convex end section requires no machining. This reduces the need for machining the axis. Surprisingly, therefore, the end portion of the axis for shortening the profile part is used by the change region 31 of the end portion 19 and 20 extends to the loading portion 32 of the roller 11 and 18. In other words, the change region 31 extends at least into the region of the outermost loading element 16, here the outermost loading cylinder. The spars of the axle at this point are longer than normal, because in the known axis, the profile portion extends from the center further outward than the load cylinder (Fig. 1). In the solution according to the invention, the part of the axle supporting the outermost loading cylinder can remain more outward than the rails at the same point in the direction of the radius. The extension of the range of change of the end portion of the loading part of the roller allows smaller than before, but more widely than previously distributed stresses in the journal and the end portion. It is spared, in comparison with the abruptly changing end section, in the weight of the mentioned structures.
    The axis 11 shown in Fig. 4 has in the cross-sectional profile of the profile part 21 an additional reinforcement 23 so that the bending stiffness of the axis 18 is greater than without additional reinforcement 23. In other words, the
    Cross-sectional profile is different in the profile part of the axis compared to the end sections of the cross-sectional profile of the axis. The end portions have a journal 24 which includes a mating surface 25 for storage. The mating surface 25 changes to an I-profile profile part 21, which has an additional reinforcement 23. Thanks to the additional reinforcement, the bending stiffness of the axle increases. In other words, the axle is bent less than before, with the addition of the additional reinforcement leaving the other sizing of the roller pairs unchanged, although the rollers are extended. This avoids additional dimensioning and machining.
    Preferably, the dimension of the additional reinforcement 23 si is selected such that the flexural rigidity of the axle 18 is 25-75%, preferably 35-55% greater than without additional reinforcement 23. The required safety margins are achieved even by a relatively slight increase in flexural rigidity.
    4, another axis according to the invention is shown. Here, the profiled part 21a is provided with an additional reinforcement 23 equipped central part 26 and on its sides at the change areas 31 limiting adjustment areas 28. The axis has maximum gains. The final part is sort of standard for the size in question and the strength of the profile part always varies according to the additional reinforcement and its length chosen. In Fig. 3, the profile portion is so-called normal without the additional reinforcement to be shown in Fig. 4. In FIG. 4, the change in the cross-sectional profile of the axis 18 from the profile portion 26 to the end portion 27 is linear in the adjustment range 28. In this case, the cross-sectional profile of the axis gradually changes gradually, the local voltage peaks can be avoided. Preferably, in the adjustment region 28, the change in the cross-sectional profile of the axis 18 from the profile portion 26 to the end portion 27 is almost tangential. At the same time, the stress distribution of the bent axis becomes ideal without high stress concentrations. In addition, the molten metal can flow without hindrance.
    The additional reinforcement is arranged in the middle region of the profile part of the axle. More specifically, the additional thickness 23 is located approximately in the area of the nip 29. For example, in a six-meter-long axis, the additional reinforcement may, for example, be located in the middle at a distance of one meter from the two edges or, for example, in the roller of greater load two meters from the center towards both edges. Generally speaking, the longer the path of the additional gain from the axis, the stiffer the axis. In addition to the length, the size of the additional gain can be changed. While one type of mold can be used to set the adjustment range by adjusting the length for the additional thickness. Thus, with the help of two different additional molds, in addition to conventional molds of stiffness and length, different axes can be cast without manual processing or remeasurement of the molds. At the same time, the end portions 19 and 20 of the axle may be constant in the axes of the same diameter.
    New and surprising additional molds are formed from mold moldings that cover the conventional mold in part of the way. In other words, in addition to the end sections and basic shape having profile parts now own Gussformausrüstungen available. With
    Help of the casting set are formed in the axis adjustment and additional reinforcement profiles. Thus, at least three types of mold set may comprise a mold according to the invention comprising the whole roll by means of connectors of at least the end, setting and auxiliary reinforcement equipments. With the aid of the adjustable casting set, the cross-sectional profile of the axis is significantly changed, which depends on the conventional millimeter-length deviations in the cross-sectional profile, which are attributable to the emissions of the casting. In practice, the change is several tens of millimeters.
    In Fig. 2, an axis according to the invention is shown as a cross section. On the left side of the main axis of the axis 18, the auxiliary reinforcement 23 according to the invention is shown with the aid of a thin plastic line, while the spars 30 remain on the right side without additional reinforcement. Here, the additional reinforcement 23 is arranged on the inner surfaces of the I-profile associated spars 30. Thus, the tops of the spars can be the same on all axes, while the additional mass points inwards. Preferably, the additional gain is equal to the two bars arranged. The properties of the axle can be adjusted by different sized additional reinforcements on the bars. In general, it can be stated that the axle has an I-profile comprising an upper and a lower beam. Between the spars is a footbridge. The additional reinforcement is a reinforcement formed by the expansion, which is a thickening of the spars of the I-profile preferably in the direction of the radius inwards. In spite of the differences in the sectional lines in Fig. 2b, the additional reinforcement is a fixed part of the axle and it is formed during the casting of the axle.
    The invention thus also relates to a cast axle equipped with a cast axle of a fiber web machine. The roll 10 or 14 is associated with a non-rotatable shaft 11 or 18 associated with two end portions 19 and 20 and a tread portion 21 between the end portions 19 and 20. In most cases, the cross-sectional profile of the profile part of its basic shape I. In this cross-sectional profile of the profile part 21, the additional reinforcement 23 is designed so that the flexural strength of the axle 11 or 18 is greater than without additional reinforcement 23. Otherwise, the axis corresponds to the text described above.
    With the aid of the characteristics of the range of change of the axis, the additional reinforcement of the axis or both, the field of application of the roll can be extended without a larger roll size or a larger counter roll being selected. Also, the need for dimensioning is no longer available or at least significantly lower, which reduces costs. In addition, the additional reinforcement gives more flexural rigidity to the axle with little change. In practice, the need for machining the axis will be lower and also the journals machined by turning. Only the only change is the blank resulting from casting. The increase in mass is also limited because the profile of the axle changes only in part of the track. The formation of additional reinforcement requires few additional resources, since only one mold for the setting range and a second mold for the middle portion must be purchased for the existing mold sets. Accordingly, the flowing range of change of the end portion is favorable and its need for machining is low.
    In practice, with the help of previously described molds in the cast frame, a mold can be made in which the axis is cast in one go. After removal of cast frames, required surface machining is performed, whereafter the axle is ready to be fitted and bonded to the roll mantle to a bend compensated roll.
    权利要求:
    Claims (12)
    [1]
    PATENT CLAIMS 1 Cast axle for the roller of a fibrous web, to which axis (11, 18) two end sections (19, 20) and one profile section (21) are assigned between the end sections (19, 20) and each end section (19, 20) Change range (31) is assigned, in which the axle (11, 18) associated with the axle pin (24) is changed into a profile part (21), characterized in that the change range (31) on the load area (32) of the axis ( 11, 18).
    [2]
    2 axis according to claim 1, characterized in that extending the change region (31) in the axial direction at least on the axis (11, 18) in the region of the arranged load element (16).
    [3]
    3 axis according to claim 1 or 2, characterized in that the change region (31) in the axial direction on two to three axes (11, 18) in the region of the arranged outermost loading element (16).
    [4]
    4 axis according to one of the claims 1 - 3, characterized in that the change region (31) is suitably convex.
    [5]
    5 axis according to claim 1-4, characterized in that the end portion (19, 20) is associated with a molded opening (33) extending from the end of the journal (24) to the change region (31).
    [6]
    6 axis according to claim 5, characterized in that the opening (33) opens in the change region (31) on the two opposite sides of the profile part (21).
    [7]
    7 axis according to one of the claims 1-6, characterized in that the length s of the change region (31) in the axial direction is 0.4 - 1.6, more preferably 0.6 - 1.2 times the diameter R of the axis ( 11, 18).
    [8]
    8 axis according to one of the claims from 1 to 7, characterized in that the cross section of the axle journal (24) is a polygon.
    [9]
    9 axis according to one of the patent claims 1-8, characterized in that the convex end portion is not machined.
    [10]
    A cast axle roller of a fiber web machine, said roller (10, 14) having a non-rotatable shaft (11, 18) having two end portions (19, 20) and a tread portion (21) between said end portions (19, 20) , and each end section (19, 29) is assigned a change area (31) in which the axle pins (24) assigned to the axle (11, 18) change into a profile part (21), characterized in that the change area (31) to the load area (32) of the axis (11, 18) extends.
    [11]
    11. Roller according to claim 10, characterized in that the axle (11, 18) is an axle (11, 18) according to one of the claims 2-9.
    [12]
    12 roller according to claim 10, characterized in that the roller is a shoe roll (10).
    类似技术:
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    同族专利:
    公开号 | 公开日
    AT517790B1|2018-11-15|
    DE102016118745A1|2017-04-13|
    FI127174B|2017-12-29|
    CN107059459A|2017-08-18|
    FI20155720A|2017-04-14|
    AT517790A3|2018-01-15|
    CN107059459B|2019-07-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3624880A|1970-06-08|1971-12-07|Beloit Corp|Piston and end dam sealing apparatus for adjustable deflection rolls|
    FI75217C|1986-11-10|1988-05-09|Valmet Oy|BOEJNINGSREGLERAD VALS.|
    DE19724911A1|1997-06-12|1998-12-17|Voith Sulzer Papiermasch Gmbh|Web press unit|
    CN102517960B|2012-01-10|2014-03-19|山东昌华造纸机械有限公司|Boot type squeezing device|
    DE102013210496A1|2013-06-06|2014-12-11|Voith Patent Gmbh|Roller and production of a roller axle|
    FI10710U1|2014-10-24|2014-12-05|Valmet Technologies Inc|Fiber web machine roller|FI128724B|2018-10-12|2020-11-13|Valmet Technologies Oy|Belt roll of a fibre web machine|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FI20155720A|FI127174B|2015-10-13|2015-10-13|Molded shaft for fiber web machine roll and molded fiber machine roll|
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