FI120970B - Power take-off drive - Google Patents

Description

Power take-off drive

The invention relates to a drive arrangement of a fiber web reel arranged to continuously wind the fiber web around a reel roll into 5 machine rolls, the drive arrangement having a transfer device for moving the first coupling part to the Y coupled position and in a coupled position, said coupling members are arranged to transmit rotational energy between the machine roll and the center drive by means of a power-10 transmission shaft.

A roller winder is a device that winds material produced as a continuous fibrous web into a roll of a machine. In a fiber web production process, the reel winder is usually the first sub-process in which continuous production is interrupted sequentially in a continuous manner. The machine reel is formed around a reel core 15 serving as a reel core, i.e. one fiber web on the reel has a beginning and an end. A constant trend in the industry is the steady increase in the size of machine rolls, which causes a constant need for development of the fasteners. In practice, the sizing of a reel roll determines the maximum size of the reel. However, since it is a dynamic environment, the fibrous web is a rollable material susceptible to various faults, the role of the reeler in maintaining the efficiency of a paper or board machine is very significant. One reason behind the continued growth of machine reel size is the desire to have fewer disruptive or distracting start-ups and endings for fiber web production.

The method disclosed in Fl patent 91383 (EP 0483092 B1) once shifted the size of machine rolls to a new order of magnitude when it was possible to construct the top of the machine roll in a manner consistent with the properties of the roll of fibrous web. The importance of the first part is emphasized when the amount of fibrous web to be wound up is increased because the first part serves as the "" basis "of the roll structure. One of the technological advancements here was the advanced primary and secondary center roll drive torque generated by the machine roll, which allowed the use of versatile winding parameters in the construction of the machine roll. The prior art prior to this solution was the so-called prior art. a pope reel, in which the machine roll was constructed by pressing against the winding cylinder driving the machine roll, whereby the machine roll was formed by friction between the winding cylinder and the machine roll.

In one embodiment of the aforementioned patent, a drive unit is used to connect the primary and secondary center drive drives to engage the reel core 2, which is the core of the machine reel, while driving by means of a cylinder arrangement associated with the gear. This arrangement is described in patent F1 81321 B (the same patent family includes, inter alia, US 5,069,394). This operating arrangement is engageable and detachable by means of a cylinder device.

5 In the description of the present invention, the following designations are used for ease of explanation: the machine direction (MD) is called the X direction, the cross direction (CD) is called the Y direction, and the elevation is called the Z direction. The XY plane is thus substantially horizontal. The upstream direction of the fibrous web is called the upstream direction and the downstream direction of the upstream direction of the fibrous web. The Rul spooler is referred to herein as the reel spool, but could equally well be called the spool spool.

It is a further object of the invention to further develop the drive arrangement of the reel so that it is more versatile for use with different types of reel lids. One particular application is reel-up rollers, which have a selectable function of machine roll oscillation, whereby the machine roll and the winding cylinder are rotated a few angles back and forth in the XY plane about the virtual vertical axis passing through the nip between the machine roll and the winding cylinder. In this particular embodiment, the object is to provide an arrangement in which the drive-side first coupling member can be reliably and releasably coupled or disengaged to or from the reel of the reel to be oscillated. A further object is to allow greater freedom of movement for the interconnected assembly of the first coupling member and the second coupling member. It is a further object of the invention to provide an arrangement in which the interference to the winding process possibly caused by the change of drives during the winding process is minimized.

The arrangement according to the invention is characterized in that the transmission shaft between the first coupling part and the gear is arranged so that there can be translation in the X direction and rotation in the XY plane between the rotation axis 30 of the first coupling part and the gear output shaft.

Here, the transmission shaft between the first coupling part and the center drive gear is arranged to be flexible or movable so that there can be translation in the X direction and rotation in the XY plane between the rotation axis of the first coupling part and the gear output shaft. By means of translation, the first coupling member remains in the correct position in the X direction relative to the second coupling member, 3 if, for example, due to oscillation, the second coupling member moves or moves in the X direction. Further, by means of translation, the first coupling part can be displaced along its entire length in the X direction, as compared to a situation where the reel roll and the winding cylinder are in a straight state, i.e. with zero oscillation. Correspondingly, by rotation in the XY plane 5, the first coupling part and the second coupling part remain concentric with respect to each other. Thus, for example, the tooth forces between the first coupling part and the second coupling part remain small and there is no abrasion between the teeth.

According to a preferred embodiment, the drive arrangement is implemented such that at least two hinges are provided on the transmission shaft to provide said flexibility, at which the direction of the axis of rotation of the drive shaft may change. In this way, the desired mobility and / or flexibility is achieved by a relatively simple structure.

In the following, the invention will be described in more detail with reference to the accompanying drawings, in which: Fig. 1 shows a top view of a reel drive arrangement generally, Fig. 2 shows a detailed arrangement of Fig. 1, Fig. 3 shows an alternative embodiment of an operating arrangement; an embodiment for locking the transmission shaft.

Fig. 1 illustrates an operating arrangement 2 of a fibrous web winder 1. The engaging roller 1 is adapted to continuously wind the fibrous web W around a reel roll 5 into a machine roll 6. The operating arrangement comprises a transfer device 25 . The solid line represents the components as they are in the upright position and the dashed line shows only the reel roll 5a and the operating system components connected thereto in one of its possible trajectories in the X-direction oscillation. In this case, the oscillation axis O of the reel reel, for example, is a 30 Z-directional line intersecting the centerline C. With the first coupling part 29 and the second coupling part 59 in a mutually engaged position, said coupling parts 29, 59 are arranged to transmit rotational energy between the machine roll 6 and the center drive 7, 8 via a transmission shaft 20 and a gear 3. Energy moves in different directions during different stages of the winding. During normal winding, the center drive 7, 8 feeds energy in the direction of the machine roll 35, whereby the torque is in the tightening direction. Upon completion of the machine roll 6, the rotation of the machine roll 6 is stopped by a braking or anti-rotation torque, whereby the center drive 7, 8 respectively functions as a generator.

Figure 2 shows a detail of Figure 1. It illustrates in more detail how the transmission shaft 20 between the first coupling part 29 and the gear 3 is arranged so that the rotation axis 290 of the first coupling part 29 and the rotation axis 320 of the gear 3 output shaft 32 can be translated and rotated. in the XY plane. Thus, the transmission shaft allows the transmission between the gear unit 3 and the second coupling part 59 at the end of the reel 5. In Figure 2, the position of the rotation axis 290 at an oscillated position is shown by reference numeral 290a.

Figure 2 illustrates one embodiment of an operating arrangement in which at least two pivots 22, 24 are provided on the transmission shaft 20 to provide the aforementioned flexibility, whereby the direction of rotation axis 200 of the transmission shaft 20 may change at the joint 22, 24. Thus, the transmission shaft 20 is formed, in addition to the articulations 15, for example three shaft portions with a first coupling part 29, then a joint 22, an intermediate shaft 23, a second joint 24 and an outermost output shaft 32 at the end of the reel spool. lateral displacement, and rotation, whose rotation point may preferably be, for example, the same as the rotation axis O of the oscillation 20.

The drive arrangement of Figure 2 is implemented in accordance with a preferred embodiment (shown in Figure 4) such that at least one of said hinges 22, 24 comprises a flap coupling. The lamella coupling is a torsionally rigid coupling, which however allows some angular and axial error. In the La Mel coupling, the torque 25 is often transmitted via metal parts. In addition to a wide range of couplings, there are a number of suitable articulated or coupling solutions, of which it is primarily recommended to choose a solution which acts as a constant velocity axis, i.e. the rotation angle between the ends of the shaft remains constant regardless of the angle. Thereby, regardless of the angle of rotation and 30 oscillation positions, the machine roll is always subjected to a constant torque, whereby the roll structure can also be utilized.

Figure 3 shows another embodiment as an operating arrangement. According to this second embodiment, a guide joint 27 is provided in the area of the same or adjacent shoulder 571 35 with the locking levers 72, 82 engaging the bearing housing 57 of the reel roll 5. As used in this specification, the term '' equal shoulder region 5 '' means a region in the width, or Y direction, that is a region between adjacent diameter changes in the region of a reel roll having varying portions of varying diameters and a bearing housing. This is illustrated in Figure 3 by 2-dotted dashes 571. These '' equal shoulder areas '' include 5 such as the axle neck area where the crane hooks generally lift the reel roller, the reel groove area in the reel roller bearing housing, the midline side of the reel groove in the reel bearing housing, etc. This feature provides technical effect. wherein the locking of the reel roll and the pivot point 270 of the guide joint 27 are substantially adjacent. The locking levers 72, 82 pi-10 engage the bearing housing 57 in either direction X and thereby position the reel roll 5 in X-oscillating structures such as the roller carriages, wherein also the pivot point of the first coupling part 82 pivotally engaged with the roller carriages straight. Hereby, the various translation / rotation or rotation / translation type load cases are almost eliminated, which in turn has a positive effect on the life of the structure.

The driving arrangement 2 according to Fig. 3 comprises a guide link 27 for controlling the rotation of the first coupling part 29 of the rotation axis 290 in the XY plane whose pivot point 270 of the steering link 27 is arranged to be located relative to the first coupling portion 29. In this operating arrangement, the first coupling part 29 is arranged to be moved between the control joint 27 and the thrust bearing 28. Further, according to this embodiment, the distance between the control joint 27 and the end of the drive shaft 20, the central drive 7, 8, may be fixed or variable.

Figure 3 also shows a possible embodiment for bearing the first coupling part 29. The first coupling part 29 is rotatably arranged by bearings so as to be able to transmit the energy of rotation between 7, 8 and the machine roll 6. According to a further embodiment, at least one of the bearings is arranged as a thrust bearing 28, whereby it is capable of transmitting not only the radial load 30 but also the axial (Y direction) load which is displaced from the to maintain the power needed. This switching movement is performed during production run on the primary drive-secondary drive type reel during the changeover operation when the secondary drive is connected to the rotating reel reel. Correspondingly, in such reel models in which the entire winding is performed in a single drive, said coupling movement is performed on a reel which is stopped. For illustrative purposes, except for the first clutch part 29 and the thrust bearing 28, no other structure of the transmission shaft (20) is shown.

The operating arrangement also comprises a transfer device 25 for moving the first coupling part 29 to a position 5 disengaged in the Y direction and a second coupling member 59 belonging to the reel 5 5 from the uncoupled position. the transfer device 25 may be arranged to be located outside the thrust bearing 28 as shown in the embodiment 10 of Figure 3.

Figure 5 shows a coarse detection example of an embodiment where the pivot 22, 24 of the transmission shaft 20 is arranged to be lockable, wherein the rotation axes 290, 200, 320 of the transmission shaft-related parts 29, 20, 32 are substantially concentric when in the locked state. Further, the locking is arranged to be unlocked 15 when the first coupling member 29 is engaged in the second coupling member 59. This feature prevents the assembly of the transmission shaft 20, the first coupling member 29 and the hinges 22, 24 from uncontrollably moving position. Such a situation may occur if the retractor 1 is of the type 20 in which the changeover is performed in flight, i.e. the so-called reel is first rolled. in the initial winding mode and the rest of the winding in so called the secondary drive. If the reel is of the type in which the entire reel is performed in one drive, the center drive, i.e. the first coupling member, is pushed to the second stopped member 59. This temporary removal of flexibility by locking the joint or joints is not necessarily necessary. The embodiment may be implemented in one or more or all of the pivot shafts depending on the selected pivots. This choice of solution is influenced by the type of joint and other structure, and in particular the susceptibility of the structure to deviate from its balance relative to its axis of rotation is one of the most significant factors. Preferably, in particular, the first joint 22, 24 from the gear in the direction of the first coupling part 30 is arranged to be lockable, since the effect of that joint on balance or potential imbalance is greatest.

In the embodiment shown in Fig. 5, the joint locking is provided hydraulically or by other pressure medium (such as compressed air) or by an electromechanically controllable, partially conical hub 33. 5, the left hinge 22 is locked in the "open" state, with the hub 33 in its locked position not facing the conical surfaces 33a, 33b but allowing the hinge 22 7 to bend. Similarly, the hub of the right hinge 24 is in the "closed" state, with the conical surfaces 33a, 33b in contact with each other. A conical hub is one of the easiest ways to implement such functionality, but a similar function can be accomplished by other means, such as ball-like, cylindrical 5 or similar locking elements, or by various electromagnetic arrangements.

According to a further embodiment, the first coupling part 29 can be coupled at any point in the oscillation cycle, i.e., the second coupling part 59 being at any point in its X-axis path. Such an operating arrangement includes, inter alia, a alignment means by which the direction of rotation axis 290 of the first coupling portion 29 can be substantially coaxial with the axis of rotation of the reel roll. Herein, "substantially coaxial" means, for example, coaxiality that does not interfere with the coupling of the first and second coupling members. This is, of course, dependent on the geometry of the first coupling portion 29 and the second coupling portion 59. Also in this embodiment, there is preferably some kind of alignment means which in the X-direction moves the first coupling part 29 to the position corresponding to the oscillation of the second coupling part 59.

As will be apparent to one skilled in the art, the inventions are not limited to the embodiments described above. The expressions describing the existence of the features contained in the claims, for example, "operating system has a transfer device", are transparent so that the presentation of the features does not exclude the existence of other features not set forth in the independent and independent claims.

25 8

Reference numerals used in the drawings: 1 drive roller 2 operating arrangement 20 transmission shaft 5 200 rotation shaft 22 joint 24 joint 25 transmission device 27 steering joint 10 270 pivot point 28 thrust bearing 29 first coupling part 3 gear 15 32 output shaft 320 rotation shaft 33 hub 33a, 33b tapered surfaces 1 5.5a shoulder space 59 second coupling member 9 6 machine roller 7 first center drive 72 locking levers 8 second center drive 5 82 locking levers C centerline W fiber web

Claims (14)

10 An operating arrangement (2) of a fibrous web winder (1) adapted to continuously wind the fibrous web (W) around a reel roll (5) into a machine reel (6), wherein the operating arrangement comprises a first coupling 5 (29) for moving in and out of the uncoupled position with the second coupling part (59) of the reel (5), the first coupling part (29) and the second coupling part (59) being in a mutually engaged position, said coupling parts (29, 59) energy between the machine roll (6) and the center drive (7, 8) by the transmission shaft (20) 10, characterized in that the transmission shaft (20) between the first coupling part (29) and the gear (3) is arranged so that the first coupling part (29) ) there may be translation in the X direction between the axis of rotation (290) and the axis of rotation (320) of the output shaft (32) of the gear unit (3) in the XY plane. Driftarrangemang enligt patent krav 1, a rotation knob (22, 24) for an analog transmission (20) for an elasticity of color, rotationsaxelns (200) for a rotating knob (22, 24). Drive arrangement according to Claim 1, characterized in that at least two pivots (22, 24) are provided on the transmission shaft (20), at which the axis of rotation (200) of the transmission shaft (20) can change at the joint (22, 24). Driftarrangemang enligt patentkrav 2, a rotary deck having an abutment of said ledger (22, 24). 15 Drive arrangement according to Claim 2, characterized in that at least 20 of said hinges (22, 24) are lamella couplers. ··· • teaspoon 4. Driftarrangemang enligt patent krav 1, kännetecknat av att driftarrange-manget (2) innefattar en första kopplingsdel (29) hos styrleden (27) för att styra rotationsaxelns (290) vridning i XY-planet, hauling styrleds (27) and (c) sida i förhällande till den första kopp-lingsdelen (29). Drive arrangement according to Claim 1, characterized in that the drive arrangement (2) comprises a first articulation joint (27) for controlling the rotation of the first coupling part (29) in the XY plane of the steering joint (27). ) pivot: The point (270) is arranged relative to the first coupling part (29) ··· 25 on the center line (C). Driftarrangemang enligt patentkrav 4, a rotary deck (29) and a fly fly bar (27) and a tricycle (28). • · · • • • • • •::. ·. 25 6. Driftarrangemang enligt patentkrav 4, kännetecknat av att styrleden (27) [1] som kopplas till tamburvalens (5) 1. som kopplas till tamburvalens (5) ) lagerhus (57). • · ··· Operating arrangement according to Claim 4, characterized in that the first coupling part (29) is arranged to be displaced between the control joint (27) and the thrust bearing **: (28). • »• ·« • · ·. ···! Operating arrangement according to Claim 4, characterized in that the guide joint (27) is arranged in the same shoulder distance (571) as the locking * · * jaws (72, 82) to be connected to the bearing housing (57) of the reel roller (5). . ··· • · · · ··· 11 7. Driftarrangemang enligt patentkrav 4, kännetecknat av att avständet mel- * ·; : 30 Ian styrleden (27) och transmissionsaxelns (20) ände mot navdriften (7, 8) föränderligt. · •::::: 8. Driftarrangemang enligt patentkrav 1, kännetecknat av att transmissionsa- • xeln (20) anordnad som en Axel med constant hastighet. • · · ··· Drive arrangement according to Claim 4, characterized in that the distance between the control joint (27) and the end of the drive shaft (20), which is centered (7, 8), is constant or variable. Drive arrangement according to claim 1, characterized in that the transmission shaft (20) is arranged as a constant speed shaft. Driftarrangemang enligt patentkrav 1, kännetecknat av att flyttanordningen (25) anordnats pä trycklagrets (28) mittlinjes (C) sida. 35 13 Drive arrangement according to claim 1, characterized in that the transfer device (25) is arranged to be located on the center line (C) of the thrust bearing (28). Driftarrangemang enligt patentkrav 4, kännetecknat av att flyttanordningen (25) anordnats att spare belägen utanför trycklagret (28). Drive arrangement according to claim 4, characterized in that the transfer device (25) is arranged to be located outside the thrust bearing (28). 11. Driftarrangemang enligt patent krav 1, rotationsaxarna (290, 200, 320) hos delarna (29, 20, 32) som ansluter till transmissionsaxeln and fatigue-to-slurry slurry slurry. Drive arrangement according to Claim 1, characterized in that the pivot (22, 24) of the transmission shaft (20) is arranged to be locked, the axes of rotation (290, 200, 320) of the transmission shaft-related parts (29, 20, 32) being substantially co-axial while in locked state. 12. Driftarrangemang enligt patent krav 11, ankle padnat av attäsningen and 10, with the aid of a centreringsorgan (33) which conforms to a hydrauliskt eller med tandem tryckmedium, säsom tryckluft. Drive arrangement according to Claim 11, characterized in that the locking device 15 is arranged hydraulically or by means of a partially conical hub (33) which can be controlled by means of a pressure medium, such as compressed air. Driftarrangemang enligt patent krav 11, the telescoping mechanism is provided with an appropriate conformation to the centering ring body (33) of the electromechanical assembly 15. Drive arrangement according to Claim 11, characterized in that the locking is arranged in an electromechanically controllable part with a conical hub (33). The operating arrangement according to claim 11, characterized in that the locking: ·:: is arranged to be unlocked when the first coupling part (29) is connected to the second coupling part (59). • (12) (29) och den andra kopplingsdelen (59) i den kopplat platplat f f var f var var var till, var, var, den, den, den, den 20 den (20) an den den vä 9 vä (9) och växeln (3) anordnad att spare elastic, save att hans high translation x-riktningen och rota-5 tion i xy-planet mellan den första kopplingsdelens (29) rotationsaxel (290) och rotationsaxeln (320) hos växelns (3) utgängsaxel (32) ). 14. Driftarrangemang enligt patentkrav 11, kännetecknat av att läsningen and anordnad attoppnas dä den första kopplingsdelen (29), and proceed to the copilt account den andra kopplingsdelen (59). 20 • · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · English · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · • · 1 · · · · · · · · ·