• 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:
    A plant for moving a roll of a material web-making machine in the axial direction, and this plant comprises - a first shaft (11) and a second shaft (12) both of which are arranged to rotate, - a first eccentric one on the first shaft (11) Mass (15), - at the second shaft (12) a second eccentric mass (16), and - control members (19) for effecting and controlling a phase difference between the first mass (15) and the second mass (16), the Control members (19) are formed by an actuator (20) which is arranged separately from the shafts (11, 12) between the masses (15, 16), wherein the actuator (20) is a linear actuator, in the axial direction in the area the masses (15, 16) is arranged.
    公开号:AT14584U1
    申请号:TGM364/2014U
    申请日:2014-10-16
    公开日:2016-02-15
    发明作者:Seppo Kupiainen；Jukka-Pekka Lepistö
    申请人:Valmet Technologies Inc；
    IPC主号:
    专利说明:

    description
    APPARATUS FOR THE AXIAL MOVEMENT OF A ROLLER OF A MATERIAL RAIL MANUFACTURER
    The invention relates to a plant for moving a roll of a material web-making machine in the axial direction, and this plant comprises [0002] - a first shaft and a second shaft, both of which are arranged for rotation, [0003] on the first shaft, a first eccentric mass, - on the second shaft, a second eccentric mass, and [0005] regulating means for effecting and controlling a phase difference between the first mass and the second mass, these regulating members being constituted by an actuator which is arranged separately from the waves between the masses.
    Finnish Patent Specification No. 117293 and Finnish Utility Model Publication No. 7860 describe two different apparatuses for moving a roll of a web-forming machine in the axial direction. Both systems are based on rotating mass pairs and the phase difference between their eccentric masses. By controlling the phase difference, the amplitude and frequency of the vibration to be generated by the system can be changed. In this way, the desired axial movement of the roller is achieved.
    In both systems, the phase difference is caused with complicated devices requiring a lot of mounting space. Also, the facilities are difficult to attend because of their placement. Further, the plants contain numerous components, which increases the acquisition and operating costs, and finally, the power of the equipment is limited, which limits the size of the masses and thus the achievable with the plant force.
    This invention is therefore based on the object zaffaffen a moving to a roll of a web-forming machine serving in the axial direction novel system, which is compared to the previous of simpler construction, but in their function more versatile and efficient. The characterizing features of this invention will be apparent from the appended claims. In the system according to the invention, the phase difference between the masses is produced in a new and surprising manner. More specifically, a control element is used which is novel in its construction and arrangement. It can then be moved with a lower force than previously greater Massenals than before, making the control of the phase difference with simultane- ously better performance designed more accurate and reliable. In addition, the system is more compact and easier to maintain than the previous systems.
    In the following the invention with reference to the accompanying, some Ausfüh¬rungsformen the invention showing drawings will be described in detail. In the drawings: Fig. 1 is a schematic drawing of the system according to the invention in cross section; Fig. 2 is a principal longitudinal section in the plane A-A in Fig. 1; FIG. 3 shows a schematic drawing of a second embodiment of the actuator of the system according to the invention; FIG. FIG. 4 shows a schematic drawing of a third embodiment of the actuator of the system according to the invention; FIG. 5 shows a schematic drawing of a cross section of a second embodiment of the system according to the invention.
    The plant according to the invention is used especially in the material web manufacturing machines especially for oscillating the so-called breast roll. In other words, the breast roll provided for supporting the wire is moved in the axial direction. For example, in Längeiebmaschinen the fiber suspension is injected directly behind the breast roll on the screen, which is moved by moving the breast roll and the screen in the transverse direction of the material web-making machine. In the process, shearing forces are brought into effect in the fiber suspension on the sieve, so that the fibers are distributed more uniformly on the sieve. In the plant, a linear damped vibration system with a degree of freedom is used. The excitatory excitement is served by eccentric pairs. The mass pairs have eccentric masses which are arranged on shafts. The shafts of the mass pairs are perpendicular to the axis of rotation of the breast roll. The Arbeitsbewe¬gung the system is generated by giving the rotating eccentric masses a Pha¬sen difference. In addition, the length and frequency of the working movement can be regulated by changing the said phase difference. The system is thus controllable. Mass pairs, which are located in completely opposite phases, then cancel each other out, whereby the system is motionless. Effect on the working movement also have the rotational speeds of the masses.
    In Fig. 1, a roll 10 of a web-forming machine is partially shown. The roll 10 here is a breast roll, and the plant according to the invention connected thereto is shown in cross-section. The breast roll, in short the roll 10, is located at both ends in bearings which allow movements of the roll 10 in its axial direction. The axial movement that can be generated with the system is approx. 10 - 50 mm. Regardless of the embodiment, the plant includes a first shaft 11 and a second shaft 12, both of which are rotatable. Matching bearings are used to support the shafts. In addition, the shafts 11 and 12 are mounted on a movable carriage 13, which is connected via a drive rod 14 with the roller 10. Thus, acting on the roller only an axial force, which moves the roller in the desired manner back and forth.
    To generate the oscillation rotating eccentric masses, between which a phase difference was generated, arranged on the waves. Generally speaking, a first eccentric mass 15 is arranged on the first shaft 11 and a second eccentric mass 16 on the second shaft 12. However, said masses belong to different mass pairs, the vibration system functioning in the aforesaid manner. The mass pairs are denoted by the reference numerals 17 and 18 in FIGS. 1 and 5. Further, the system includes control means 19 for establishing and controlling the phase difference between the first mass 15 and the second mass 16. In the invention, the control members 19 are constituted by an actuator 20 which is disposed separately from the shafts 11 and 12 between the masses 15 and 16. In addition, the actuator 20 is a linear actuator, which is arranged in the axial direction in the region of the masses 15 and 16. First, the actuator is simple in its construction, can be controlled precisely and works quickly. Second, with the actuator, greater forces and even moments than heretofore can be transmitted without additional torque acting on the shafts. The friction occurring in the system are lower than before, and the storage of the waves is facilitated and the durability improved. Next, the waves can be made thinner than before or on the gegen¬wärtigen waves larger masses can be arranged than before. If the external dimensions remain the same, the performance of the system can be increased.
    The drive rod 14 has a thrust bearing 21 which permits rotation of the roller 10, that is, the drive rod 14 does not rotate while the shaft 22 of the roller 10 is rotating. In addition, the carriage 13 is supported via slide bearings 23 on the frame of the system. In the embodiment shown, hydrostatic sliding bearings are used, that is, the carriage slides on a lubricant film. Along with the roller 10, moving parts in the system are the ones of the drive rod 14 and the carriage 13, the masses and the shafts. Because of the stroke length and the frequency of the roll movement, the system is also referred to as a vibrating or shaking device.
    Fig. 2 shows in principle the system according to the invention in longitudinal section. The first shaft 11 is formed here in full length, and at its two ends bearings 24, preferably rolling bearings, arranged. The first shaft 11 and the first mass 15 are non-rotatable, for example, by a wedge 25. Accordingly, the second shaft 12 is formed by two stub shafts 26 supported around the first shaft 11. In other words, the shafts 11 and 12 are arranged coaxially with each other. Both eccentric masses then rotate about the same axis of rotation, but the mutual storage allows the formation of phase difference between the masses. Since the mutual movement of the masses is temporary and slow and the angle of rotation is low, even plain bearings can be used, thereby simplifying the construction of the equipment and facilitating the maintenance.
    Both masses have their own gear. More precisely, the first gearwheel 27 is located at one end of the first mass 15. The second gearwheel 28 is located at the opposite end of the second mass 16. The said gearwheels serve to transmit the rotational movement to the second masses of the mass pairs. More specifically, belonging to the plant two mass pairs, each with two eccentric masses. The second masses 15a and 16a of the mass pairs are arranged on separate shafts 11a and 12a, the construction of which corresponds to that described above. These masses also have gears 27a and 28a which mesh with the gears 27 and 28 of the corresponding opposed masses 15 and 16, respectively. At the individual end faces, the interventions of the gears keep the mutual positions of the masses within the mass pair unchanged, but allow the formation of a phase difference between the masses of the mass pair. In this case, the phase difference between the mass of two different mass pairs is also transmitted as a phase difference of the second masses of the mass pairs, so that the functional principle of the system is realized. In Figs. 1 and 5, the directions of rotation of the masses are indicated by arrows.
    The system is preferably powered by a single electric motor, which is arranged separately from the carriage. The engine is thus arranged stationary. Shown is the electric motor 29 in its principle in Fig. 2-4. In practice, a single electric motor can be easily controlled. If required, a transmission is used in conjunction with the electric motor. With the control elements, only the phase difference of the masses is regulated, of which the control of the electric motor is independent. Thus, the control of the system without kom¬pliziert ancillary equipment designed simply and accurately.
    In the drawings, the apparatuses used to control the electric motor and the control means, which may be simple thanks to the control devices according to the invention, have been omitted. In practice, the control of the electric motor by a frequency converter, the control of the control organs by conventional controller. In addition to the pairs of masses 17 and 18, springs 30 are arranged on the carriage 13 so that the installation forms a functional oscillator (FIGS. 1 and 5). The frequency of the oscillator is in the range of about 10 Hz, while the critical point is at about 0.5-1.0 Hz. The system is therefore operated in the supercritical frequency range. When the system is switched on, the mass pairs are first accelerated beyond the critical point, after which the stroke length is adjusted to the desired value by controlling the phase difference.
    The system thus has two mass pairs 17 and 18 which are rotatably supported on the carriage 13. In practice, the phase difference of the mass pairs controls the movement of the carriage and thus the length of the stroke to be generated. Each mass pair consists of two eccentric masses, each of which has approximately a quarter of the space for the other mass. In addition, the masses are arranged over a section of each other, so that now considerably larger masses can be used than before. However, the masses are sized to achieve the required phase difference. When arranging the masses on the same axis of rotation, a rotation angle of about 90 ° is required. In practice, the mass pairs rotate always in the same way to each other and so that in all Situati¬onen the vertical eccentric forces are canceled. In Fig. 1 are in the mass pairs 17 and 18, the masses 15, 15a and 16, 16a against each other, wherein the carriage 13 has its maxi¬male stroke length. The two-pointed arrows in FIGS. 1 and 5 illustrate the reciprocating movement of the carriage 13.
    The actual phase difference is thus generated with the actuator, which is arranged between the masses separated from the waves, that is, the force of the actuator acts directly on the masses and not indirectly through the waves. As a result, the system is simplified in its construction and allows the use of larger masses than before. In the Ausfüh¬rungsformen in Fig. 2-4 gears of the masses are used. The more detailed construction and operation of the actuators will be discussed in more detail below.
    In addition to its previously simpler construction, the actuator 20 for Mo¬mentübertragung between the masses 15 and 16 is set up. Due to the torque transmission between the masses of the individual mass pairs, the torque required for rotation is thus transmitted to all masses. The torque transmission in the system is represented by a dashed line in FIG. To the shaft 11 a, the electric motor 29 is coupled here. In practice, a coupling is arranged between the electric motor and the shaft, which allows a movement of the carriage while the electric motor remains in place (not shown in the drawings). Together with the shaft 11a, the mass 15a and the gear 27a fastened thereto rotate. The engaged gear 27 transmits the torque to the mass 15 and keeps the masses of this mass pair synchronized with each other. The moment transmission according to the invention with the actuator 20 takes place as follows. Generally speaking, the actuator 20 is arranged between the mutually opposite ends of the masses 15 and 16. Here, the actuator is disposed between the gears 27 and 28 of the masses 15 and 16 of the individual mass pairs. Also, as the actuator rotates, the torque is transmitted to the gear 28 and thence to the mass 16 and via the gear 28a to the mass 16a. In the phase shown, the masses of the individual mass pairs are synchronized miteinander and the mass pairs corresponding in opposite phases (sic) .When rotating the mass pairs then cancel their effects on each other, and the stroke length of the system is zero. Thus, the masses can be first accelerated to the desired speed with a single electric motor, and only then can the phase difference between the masses with the actuator be adjusted.
    Regardless of the embodiment, the actuator 20 is arranged in the axial direction in the region of the masses 15 and 16. Thus, the mass system primarily determines the dimensions of the system. In addition, the actuator can be arranged in the space determined by the masses, whereby the system is even more compact and easier to maintain. GemäßFig. 1 and 5, the actuator can even be installed in existing systems.
    If the phase difference is zero, the actuator transmits the torque unchanged between the masses. However, the actuator according to the invention also causes a Phasenunterschied while passing the moment. In the embodiments in FIGS. 2-4, the actuator 20 comprises a connecting shaft 31 and adjusting gears 32 and 33 disposed thereon. These adjusting gears 32 and 33 are in contact with the gears 27 and 28 associated with the masses 15 and 16 the moment are transmitted. In addition, the actuator has an arrangement 34 for creating and controlling phase difference between the adjusting gears 32 and 33. Thus, a phase difference can be formed for the masses. In practice, the arrangement can be implemented in various ways.
    In the embodiment of Fig. 2, the connecting shaft 31 is unitary, i. durchge¬hend, and between their two ends and the Einstellzahnrädern 32 and 33, a riser fit 35 is arranged. The connecting shaft 31 is rotatably mounted on the system. In the same camps and the Einstellzahnräder 32 and 33 are stored. However, the connecting shaft 31 can be axially moved in the support sleeve 36. The connecting shaft 31 also has a mounting groove 37, and the locking member corresponding thereto is disposed on the adjusting gear. Alternatively, the groove may be formed on the adjusting gear, wherein the connecting shaft then has a riser thread. The grooves may also be formed on both components, in which case, for example, a wedge inserted in the grooves transmits the moment. Splice fits are present at both ends of the connecting shaft, but their inclinations have different directions of rotation. In this case, when moving the connecting shaft in the axial direction, a phase difference between the Einstellzahnrädern 32 and 33 is generated, but the moment is constantly transmitted. Of the Einstellzahnrädern the Phasenun¬terschied is transmitted to the gears and thus to the rotating eccentric masses. Thus, a precise and effective regulation of the Pha¬senunterschiedes is thus achieved with a simple actuator. The connecting shaft 31 is moved here with a rotation-free bushing 38, whose bearings support the rotating connecting shaft for their part and cope well with the axial load. The sliding bushing 38 here also forms a functional piston rod with a piston when a cylinder chamber 39 is arranged around the sliding bushing. This creates a double-acting cylinder to which a pressure medium, for example hydraulic oil, can be supplied. In the described actuator, only the connecting shaft and the adjusting gears rotate. The remaining components remain in place or merely move linearly. In Fig. 2, in dashed lines, the housing 40, in which the actuator can be in a constant oil bath, is shown in principle. This construction is also advantageous because it takes up little space, and the force generated by the cylinder is concentric with the connecting shaft. This avoids the formation of bending moments on / in the actuator and its components. The following is an example of the design of the control elements: The gears of the eccentric masses each have 80 teeth. Correspondingly, the adjusting gears each have 20 teeth. The transmission ratio then amounts to 4. The gradients of the connecting shaft covers, which have a different direction of rotation, descend 180 °, so that the total rotation is 360 °. With the aforementioned transmission ratio 4, a mutual rotation of the gears of the masses in their maximum of 90 ° is achieved. In this case, the size of the phase difference varies between 0 ° and 90 ° .Due to the transmission ratio can be generated with a smaller moment than before a Phasenunterschied. On the other hand, with the torque available today, a phase difference can be generated for larger eccentric masses than heretofore.
    Also in the embodiments in Fig. 3 and 4, a connecting shaft 31 is present, which consists of two auxiliary shafts 41 and 42, however. The auxiliary shafts 41 and 42 are rigidly secured to the adjusting gears 32 and 33, but the riser fitting 35 is disposed between the auxiliary shafts 41 and 42 and the actuator. In Fig. 3, riser sleeves 43 are provided on the auxiliary shafts 41 and 42 as extensions, which are connected to the sliding bushing 38. The riser fitting is arranged between the bushings mentioned. In this case, a phase difference is generated by axial displacement of the sliding bush 38 between the adjusting gears 32 and 33. Again, the sliding bush 38 is moved with a double acting cylinder forming the actuator containing the cylinder chamber 39.
    In the embodiment in Fig. 4, the double-acting cylinder is replaced by a Gewind¬spindel 44, with the displacement bush 38 is displaced. The threaded spindle 44 functions as a translation, so that even with a small electric motor 45, the Verschiebe¬ bushing 38 can be moved. In practice, the force need only be greater than the internal friction of the actuator. The lead screw achieves a highly accurate and easily controlled phase difference control that is slower than a double acting cylinder. Any other suitable component can be used to effect linear motion. In Fig. 3 and 4, the masses and waves are not shown.
    Generally speaking, the movement of the actuator is linear. In practice, the control member associated with the actuator moves linearly. The movement of the control element, such as the above-mentioned sliding bush, is effected, for example, hydraulically or by a threaded spindle.
    Fig. 5 shows a second embodiment of the system according to the invention. Functionally identical parts are assigned the same reference numerals as in FIG. The functional principle also corresponds to that of FIG. 1, even if the shafts and eccentric masses are arranged deviating therefrom. The shafts 11 and 12 are here arranged separately on parallel lines. Also, the function of the control elements corresponds to the above-described. However, now an intermediate gear 46 is used, with which the directions of rotation matching can be set up. Here, as in the other embodiments described, the control elements transmit the torque, that is, that of the drive device, such as one
    Electric motor, generated moment is transmitted via the control organs from one mass pair to another. The transmission is done from the scope of the rotational movement so that miterigerer force than previously larger masses than previously can be kept under control. In Fig. 5 the gear of the left mass pair 17 is assigned the Einstellzahnrad 32 of the first Stell¬gliedendes. Also at the other end of the actuator is an adjustment gear that is in contact with the intermediate gear 46 so that the torque is transmitted from one pair of masses to the other. The actuator may ha¬ben full length as in Fig. 1-4, but may be arranged in this variant only at one or the other end of the masses. This further simplifies the construction of the actuator.
    The plant according to the invention is of simple construction and can be assembled from simple components. The number of their rotating components is low and they are stored friction. The control of the phase difference happens steplessly and quickly. The plant according to the invention is highly reliable and easy to set up and maintain. In addition, simple components, such as einlichlicher squirrel cage motor can be used. The size of the phase difference can be regulated independently of the electric motor. In addition, damage can be avoided in the event of a fault thanks to the automatic return of the setting. Further, the erfindungs¬gemäße system is more compact than the previous and requires little installation space.
    权利要求:
    Claims (8)
    [1]
    Claims 1. A plant for moving a roll of a web-forming machine in the axial direction, and this plant comprises - a first shaft (11) and a second shaft (12), both of which are set for rotation, - on the first shaft (11 ) a first eccentric mass (15), - at the second shaft (12) a second eccentric mass (16), and - control members (19) for effecting and regulating a phase difference between the first mass (15) and the second mass (16) in that the control members (19) are constituted by an actuator (20) arranged separate from the shafts (11, 12) between the masses (15, 16), characterized in that the actuator (20) is a linear actuator incorporated in axial direction in the region of the masses (15, 16) is arranged.
    [2]
    2. Arrangement according to claim 1, characterized in that the actuator (20) transmits the moment between the masses (15, 16).
    [3]
    3. Plant according to claim 1 or 2, characterized in that the actuator (20) between the opposite end of the masses (15, 16) is arranged.
    [4]
    4. Plant according to claim 1, characterized in that the shafts (11,12) are arranged coaxially with each other.
    [5]
    Installation according to claim 1, characterized in that the shafts (11, 12) are arranged separately on parallel lines.
    [6]
    6. Installation according to claim 1, characterized in that the actuator (20) has a connecting shaft (31) and theseies Einstellzahnräder (32, 33), in contact with the masses (15, 16) gehall¬den gears (27, 28) and an assembly (34) for generating and controlling the phase difference between the tuning gears (32, 33)
    [7]
    A plant as claimed in claim 6, characterized in that the connecting shaft (31) is uniform and has a riser fitting (35) between its ends and the adjusting gears (32, 33).
    [8]
    8. Installation according to claim 6, characterized in that the connecting shaft (31) of two auxiliary shafts (41, 42) is formed and between the auxiliary shafts (41,42) and the actuator each have a riser fit (35) is arranged. For this 5 sheets of drawings
    类似技术:
    公开号 | 公开日 | 专利标题
    DE602004008968T2|2008-06-19|DEVICE FOR MOVING A ROLLER OF A PAPER MACHINE
    AT14584U1|2016-02-15|Apparatus for axially moving a roll of a web-forming machine
    DE974232C|1960-10-27|Hydraulic displacement device, pump or motor, especially for gearboxes
    DE10051271B4|2015-07-16|In their compression ratio adjustable piston internal combustion engine with integrated Verstellaktuator
    DE102008050576A1|2010-04-08|Device for generating a circular oscillation or a directed oscillation with continuously adjustable oscillation amplitude or exciter force
    DE19615697B4|2006-04-20|Needle bar drive of a needle machine
    EP1624102A2|2006-02-08|Shaking device for reciprocatingly moving a body along an axis thereof
    EP2258488A2|2010-12-08|Drive unit for an elongated oscillating body
    DE2609411A1|1976-09-30|DEVICE FOR CONTROLLING THE MOVEMENT OF THE WEFT GRIPPERS OF WEAVING MACHINES
    DE2633578A1|1977-02-17|VIBRATOR WITH CHANGEABLE CENTRIFUGAL FORCE FOR SOIL COMPACTION ROLLERS
    EP1305121B1|2004-10-13|Controllable vibration generator
    EP1396292A1|2004-03-10|Drive system for a cold pilger mill
    EP2475814B1|2014-03-26|Device for needling a fibrous web
    EP0844976B1|2000-12-13|Device for pivoting a roller for a moving web
    DE102010055549B4|2019-01-31|Output unit for the control and power take-off of a VCR engine with eccentrically mounted crankshaft
    WO2009019111A1|2009-02-12|Device for needling a fibrous web
    WO1998035094A1|1998-08-13|Shaker
    DE202008015357U1|2009-02-12|Apparatus for moving a roll of a web-forming machine
    DE102006029241A1|2007-12-27|Device for generating vibrations
    EP3205760B1|2018-04-04|Double bed warp knitting machine
    EP3665330B1|2021-09-22|Tamping assembly for tamping sleepers of a track
    EP0870870A2|1998-10-14|Apparatus for moving a band, in particular for moving a transport band in an installation to dewater a web
    WO2015158660A1|2015-10-22|Mowing cutter drive
    EP1832718A1|2007-09-12|Device for camshaft adjustment
    EP0272522A1|1988-06-29|Crank gearing for reciprocating piston motor
    同族专利:
    公开号 | 公开日
    DE202014104908U1|2014-10-28|
    FI10683U1|2014-11-13|
    CN204343096U|2015-05-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE9104746U1|1991-04-18|1991-05-29|J.M. Voith Gmbh, 7920 Heidenheim, De|
    EP1624102A2|2004-08-05|2006-02-08|Voith Paper Patent GmbH|Shaking device for reciprocatingly moving a body along an axis thereof|
    DE202008015357U1|2007-11-26|2009-02-12|Metso Paper, Inc.|Apparatus for moving a roll of a web-forming machine|
    FI7860A|1919-12-12|Hänglås med ringbygel|CN107225077B|2016-03-24|2019-01-18|武汉科技大学|A kind of unidirectional pulse forcer|
    CN106015459B|2016-06-16|2019-03-05|南京航空航天大学|It is centrifuged actuator|
    CN107497655B|2017-08-23|2020-04-03|昆明理工大学|Torsional chaotic vibration exciter|
    CN110777556A|2019-10-28|2020-02-11|华南理工大学|Breast roll shaking device and amplitude adjusting method|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FI20136026|2013-10-17|
    [返回顶部]