EP2286025B1 - Mécanisme d'agitation - Google Patents

Mécanisme d'agitation Download PDF

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Publication number
EP2286025B1
EP2286025B1 EP09745823A EP09745823A EP2286025B1 EP 2286025 B1 EP2286025 B1 EP 2286025B1 EP 09745823 A EP09745823 A EP 09745823A EP 09745823 A EP09745823 A EP 09745823A EP 2286025 B1 EP2286025 B1 EP 2286025B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
shaking device
frequency
piston unit
roll
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP09745823A
Other languages
German (de)
English (en)
Other versions
EP2286025A1 (fr
Inventor
Christoph Link
Elmer Dr WEISSHUHN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Patent GmbH
Original Assignee
Voith Patent GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP2286025A1 publication Critical patent/EP2286025A1/fr
Application granted granted Critical
Publication of EP2286025B1 publication Critical patent/EP2286025B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21F—PAPER-MAKING MACHINES; METHODS OF PRODUCING PAPER THEREON
    • D21F1/00—Wet end of machines for making continuous webs of paper
    • D21F1/18—Shaking apparatus for wire-cloths and associated parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses

Definitions

  • the invention relates to a shaking device for reciprocating a roll of a machine for producing and / or treating a fibrous web along an axis of the roll.
  • the fibrous web may in particular be a paper or board web.
  • a resonant oscillator which comprises an active vibrator part which is in contact with a passive vibrator part of greater length, which mainly determines the resonant frequency and consists of a liquid column contained in a resonant tank, whose amount to change the resonant frequency by an adjustable Part is continuously changeable.
  • one or more damper devices are provided to change the amplitude in addition to energy-storing resonant springs whose damper members allow a variable damping.
  • the invention has for its object to provide an improved shaker of the type mentioned. It should be ruled out in a simple and reliable manner, in particular substantially that reaction forces are introduced into the foundation. In addition, the energy consumption should be reduced to a minimum.
  • a shaking device for reciprocating a roller of a machine for producing and / or treating fibrous web along an axis of the roller, in which the roller is resiliently coupled to form a vibration system with a counterweight.
  • means are provided in order to drive the vibration system comprising the roller and the counterweight at its resonance frequency.
  • a practical area for the Resonance frequency can be between 3 and 20 Hz, in particular between 5 and 10 Hz.
  • a aligned with the roll axis hydraulic cylinder / piston unit is provided, the piston with the roller, coupled and the cylinder is movably mounted along the roll axis to form the oscillating counterweight along the roll axis, wherein the roller on both sides of the piston provided enclosed volumes of particular synchronous cylinder / piston unit resiliently, for example hydraulically coupled with the counterweight comprising the cylinder.
  • the two elastically coupled together masses can oscillate in the vibration system formed against each other. For practical reasons, preferably the same or approximately the same masses are provided. However, the two elastically coupled together masses can also be in a mutual ratio of 3: 1 to 1: 3.
  • the cylinder of the cylinder / piston unit expediently comprises a shell which increases the mass, in particular a concrete casing.
  • the adjusting springs effecting the elastic coupling can therefore be realized, in particular, as pure oil springs by the enclosed volumes in a particularly uniform hydraulic cylinder.
  • the hydraulic oscillator is preferably operated at the natural or resonant frequency.
  • the drive means of the shaking device advantageously comprise means for the cyclical pressure supply of the cylinder / piston unit.
  • the drive means of the shaking device may in particular comprise a servo valve.
  • the cylinder / piston unit can be acted upon via the drive means of the shaker so that energy losses caused by damping and / or friction are compensated again by a corresponding pressure increase, in particular at the maximum pressure at the reversal point.
  • the associated increase in volume can be compensated for example after half a path length ( ⁇ ), that is at zero pressure at the reversal point.
  • the cyclical pressure supply can take place in particular via the servo valve.
  • the drive means of the shaking device preferably comprise a control and / or regulating device, which may be provided in particular for controlling the servo valve.
  • the drive means of the shaking device comprise displacement sensors for detecting the stroke of the roller and / or the stroke of the counterweight.
  • the relevant path signals can then be supplied to the control and / or regulating device.
  • control and / or regulating device provided in particular for controlling the servo valve is designed so that the excitation frequency with which the oscillation system is acted upon is automatically determined from the reference frequency in defined steps is varied up and / or down until the sum of the strokes of the roller and the counterweight has reached a maximum.
  • the predetermined, for example, computational frequency can be varied in particular in small steps.
  • the resonant frequency of the vibration system can be permanently or temporally checked by a minimum variation (+/-) of the predeterminable frequency and thus an associated total stroke change.
  • the predetermined frequency is preferably the changing circumstances, such as temperature or. Friction conditions, adaptively adaptable.
  • control and / or regulating device can in particular also be designed so that the travel and the actuating time of the servo valve are kept constant during the variation of the exciter frequency.
  • control and / or regulating device is designed so that after determination of the resonant frequency of the vibration system, the stroke of the counterweight is defined by the preferably supplied at the reversal point or in the reverse range of the cylinder / piston unit volume.
  • control and / or regulating device may in particular be designed such that the cylinder / piston unit is supplied with a volume corresponding to a respective desired stroke value specification.
  • the stroke is defined by the volume preferably supplied at the reversal point or in the reversal region. From the control and / or regulating device, the amount is set according to the Hubsollwertvorgabe.
  • control and / or regulating device is designed so that the resonant frequency of the vibration system for adjusting the shaking frequency via an on and off preferably from the same volume on the two piston sides of the cylinder / piston unit is variable ,
  • the variation of the natural frequency can thus take place by switching on or off of preferably equal volumes on both sides of the piston (four-way valve).
  • the shaking frequency can be set gradually.
  • the volumes on the two piston sides of the cylinder / piston unit can be varied continuously via parallel movable hydraulic cylinders.
  • both volumes of the two hydraulic cylinders are simultaneously adjusted by equal amounts.
  • the counterweight can be held by two adjustable Justierfedern in or about in the middle of the total stroke.
  • the energy loss can also be supplied by other means.
  • the roller forming the mass or the counterweight can be excited to oscillate from the outside ("pushing").
  • so-called mechanical shakers, hydraulic cylinders and / or electromagnets can be used.
  • the control via the servo valve is eliminated.
  • the method described for the automatic determination of the resonance frequency can also be used.
  • the leakage quantity In the case of a leak-prone oil system, the leakage quantity must be replaced by a subsequent dosing so that the trapped volumes are kept approximately constant. Leakage is detected when the sum of the strokes of the roller and the counterweight becomes smaller and / or the resonance frequency drops with the same loss energy supplied.
  • the hydraulic adjusting springs can be replaced by adjusting springs of any kind. As far as the loss energy is concerned, this can be compensated by pushing, for example.
  • a mechanical system with adjusting springs can be realized. By switching on and off further adjustment springs frequency jumps can be realized.
  • Fig. 1 shows a schematic representation of an exemplary embodiment of a shaking device 10 according to the invention for reciprocating a mass m 1 having a roller 12 along an axis 14 thereof.
  • the roller 12 is a Roller of a machine for producing and / or treating a fibrous web, in particular paper or board web.
  • the roller 12 is spring-elastically coupled to a counterweight 16 for forming a vibration system.
  • the two masses of the roller 12 and the piston 22 on the one hand and the counterweight 16 on the other hand at least substantially the same size, ie m 1 ⁇ m 2 .
  • means 18 are provided to drive the roller 12 together with the piston 22 and the counterweight 16 comprehensive vibration system at the resonant frequency.
  • an aligned with the roll axis 14 hydraulic cylinder / piston unit 20 is provided, the piston 22 with the roller 12 and mechanically coupled and the cylinder 24 is mounted to form the oscillating counterweight 16 along the roll axis 14 movable.
  • the roller 12 via the both sides of the piston 22 provided enclosed volumes V L , V R of the preferably uniform cylinder / piston unit 20 is resiliently coupled to the cylinder 24 comprehensive countermass 16.
  • the cylinder 24 of the cylinder / piston unit 20 may comprise a mass-increasing shroud, in particular concrete sheathing.
  • the cylinder 24 may be cast around with the sheathing material, preferably concrete.
  • the drive means 18 of the shaking device may in particular comprise means for the cyclical pressure supply of the cylinder / piston unit 20.
  • the drive means 18 of the shaking device in particular for the cyclical pressure supply of the cylinder / piston unit 20, may comprise a servo valve 26.
  • the cylinder / piston unit 20 can be acted upon by the drive means 18 of the shaking device in particular so that caused by damping and / or friction energy losses are compensated by a corresponding pressure increase, in particular at the maximum pressure at the reversal point.
  • the associated increase in volume can be compensated again after about half a wavelength ( ⁇ ), that is to say at zero pressure at the point of reversal.
  • the cyclical pressure supply preferably takes place via the servo valve 26.
  • the drive means 18 of the shaking device may include a control and / or regulating device 28.
  • the drive means 18 of the shaker device can have displacement sensors 30, 32 for detecting the stroke of the roller 12 and / or the stroke of the counterweight 16.
  • the control and / or regulating device 28, which is provided in particular for activating the servo valve 26, can also be embodied such that the frequency of excitation, which is applied to the oscillation system, is automatically determined by starting from a predefinable frequency f in defined small steps is varied up and / or down until the sum of the strokes of the roller and the counterweight has reached a maximum.
  • the resonant frequency of the oscillation system can be permanently or temporally checked by a minimum variation (+/-) of the predeterminable frequency f and thus an associated total deviation change.
  • the predefinable frequency f is adaptively adaptable to the changing circumstances, such as temperature or friction conditions.
  • control and / or regulating device 28 may in particular also be designed so that the actuating path and the positioning time of the servo valve 26 are kept constant during the variation of the exciter frequency.
  • control and / or regulating device 28 may also be designed such that after the resonant frequency of the vibration system has been determined, the stroke of the countermass 16 is defined by the volume supplied preferably at the reversal point of the cylinder / piston unit 20.
  • control and / or regulating device 28 is also conceivable, in which the cylinder / piston unit 20 is supplied with a volume corresponding to a respective desired stroke value preset s.
  • control and / or regulating device 28 may in particular also be designed such that the resonant frequency of the vibration system for adjusting the shaking frequency can be varied by connecting or disconnecting equal volumes on the two piston sides of the cylinder / piston unit 20.
  • the volumes can also be varied steplessly by parallel movable hydraulic cylinders.
  • both volumes of the two hydraulic cylinders are simultaneously adjusted by equal amounts.
  • the counterweight 16 can be held via two adjustable Justierfedern 34, 36 in or approximately in the middle of the total stroke.
  • the energy used to compensate for the loss energy can also be supplied in another way.
  • the mass 12 comprising the roller 12 or the counterweight 16 can be excited from outside to oscillate (pushing on).
  • the control via the servo valve 26 is omitted in this case.
  • the method described for the automatic determination of the resonance frequency can also be used.
  • the leakage quantity In the case of a leak-prone oil system, the leakage quantity must be replaced by a subsequent dosing so that the trapped volumes are kept approximately constant. A leakage is detected when the sum of the strokes of the roller 12 and the counterweight 16 is smaller and / or the resonance frequency drops at the same supplied loss energy.
  • the hydraulic adjusting springs can be replaced by adjusting springs of any kind.
  • the energy required for compensation can be introduced into the system, for example, by pushing.
  • a mechanical system with adjusting springs can thus be realized.
  • By adding additional Justierfedern frequency jumps can be realized.
  • FIG. 2 are for an exemplary embodiment of the example in the Fig. 1 reproduced hydraulic resonance oscillator, the cylinder pressure and the dead volume over the frequency indicated.
  • the cylinder pressure and the dead volume over the frequency are indicated.
  • the counterweight 16 may include, for example, a cast with concrete hydraulic cylinder.
  • the springs are realized, for example, as pure oil springs, that is to say by the enclosed volumes in the synchronous hydraulic cylinder.
  • the hydraulic oscillator should always be operated in the resonant or natural frequency. Energy losses due to damping and friction are compensated by increasing the pressure, for example, at the maximum pressure at the point of reversal. The associated increase in volume is compensated for again after half a wavelength ( ⁇ ), that is, at zero pressure at the point of reversal.
  • ⁇ wavelength
  • the control of the servo valve 26 via a control and / or regulating device 28.
  • the control and / or regulating device varies the predetermined (computational) frequency f in small steps (+/-), up to the sum of the two strokes Sm 1 and Sm 2 or the two cylinder pressures a maximum is detected, for example, the travel and the travel time of the servo valve 26 are kept constant. This automatically determines the exact resonance frequency.
  • the stroke is defined by the volume preferably supplied at the reversal point. From the control and / or regulating device 28, the amount is set according to the Hubsollwertvorgabe s.
  • the variation of the natural frequency takes place by switching on or off of equal volumes V R and V L on both sides of the piston (four-way valve). So can gradually the Shaking frequency can be adjusted.
  • the volumes can be varied continuously by parallel movable hydraulic cylinders.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Road Paving Machines (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Treatment Of Fiber Materials (AREA)

Claims (14)

  1. Dispositif agitateur (10) pour le déplacement d'avant en arrière d'un rouleau (12) d'une machine de fabrication et/ou de traitement d'une bande fibreuse le long d'un axe (14) du rouleau (12), dans lequel le rouleau (12) est accouplé de manière élastique à ressort à un contrepoids (16) pour former un système oscillant et des moyens d'entraînement (18) sont prévus pour entraîner le système oscillant comprenant le rouleau (12) et le contrepoids (16) à sa fréquence de résonance,
    caractérisé en ce
    qu'une unité cylindre-piston (20) hydraulique alignée avec l'axe du rouleau (14) est prévue, dont le piston (22) est accouplé au rouleau (12) et dont le cylindre (24) est monté pour former le contrepoids (16) oscillant le long de l'axe du rouleau (14), le rouleau (12) étant accouplé de manière élastique à ressort au contrepoids (16) entourant le cylindre (24) par le biais des volumes (VL, VR) inclus prévus de chaque côté du piston (22) de l'unité cylindre-piston (20) notamment à volumes identiques.
  2. Dispositif agitateur (10) selon la revendication 1,
    caractérisé en ce que
    le cylindre (24) de l'unité cylindre-piston (20) comprend une enveloppe augmentant le poids, notamment une enveloppe en béton.
  3. Dispositif agitateur (10) selon la revendication 1 ou 2,
    caractérisé en ce que
    les moyens d'entraînement (18) comprennent des moyen pour l'alimentation cyclique en pression de l'unité cylindre-piston (20).
  4. Dispositif agitateur (10) selon la revendication 3,
    caractérisé en ce que
    les moyens d'entraînement (18) comprennent notamment une servovanne (26) pour l'alimentation en pression cyclique de l'unité cylindre-piston (20).
  5. Dispositif agitateur (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'unité cylindre-piston (20) peut être sollicitée par le biais des moyens d'entraînement (18) de telle sorte que les pertes d'énergie causées par l'amortissement et/ou le frottement soient à nouveau compensées par une augmentation correspondante de la pression, notamment lors d'un maximum de pression au point d'inversion.
  6. Dispositif agitateur (10) selon la revendication 4,
    caractérisé en ce que
    les moyens d'entraînement (18) comprennent notamment pour la commande de la servovanne un dispositif de commande et/ou de régulation (28).
  7. Dispositif agitateur (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les moyens d'entraînement (18) comprennent des capteurs de position (30, 32) pour détecter la course du rouleau (12) et/ou la course du contrepoids (16).
  8. Dispositif agitateur (10) selon la revendication 6,
    caractérisé en ce que
    le dispositif de commande et/ou de régulation (28) prévu notamment pour la commande de la servovanne (26) est réalisé de telle sorte que pour déterminer automatiquement la fréquence de résonance du système oscillant la fréquence d'excitation avec laquelle le système de résonance est sollicité est modifiée vers le haut et/ou vers le bas en pas définis à partir d'une fréquence (f) prédéfinissable, jusqu'à ce que la somme des courses du rouleau (12) et du contrepoids (16) ait atteint un maximum.
  9. Dispositif agitateur (10) selon la revendication 8,
    caractérisé en ce que
    la fréquence de résonance du système oscillant peut être contrôlée de manière permanente ou à intervalles temporaires par une variation minime (+/-) de la fréquence prédéfinissable (f) et donc une variation de course totale associée peut être contrôlée en termes de variations et en ce que la fréquence prédéfinissable (f) peut être adaptée de manière adaptative aux données variables, comme par exemple la température ou les conditions de frottement.
  10. Dispositif agitateur (10) selon la revendication 8 ou 9,
    caractérisé en ce que
    le dispositif de commande et/ou de régulation (28) est réalisé de telle sorte que lors de la variation de la fréquence d'excitation, la course de réglage et le temps de réglage de la servovanne (26) soient maintenus constants.
  11. Dispositif agitateur (10) selon la revendication 8, 9 ou 10,
    caractérisé en ce que
    le dispositif de commande et/ou de régulation (28) est réalisé de telle sorte qu'après la détermination de la fréquence de résonance du système oscillant, la course du contrepoids (16) est définie par le volume alimenté de préférence au point d'inversion dans l'unité cylindre-piston (20).
  12. Dispositif agitateur (10) selon la revendication 11,
    caractérisé en ce que
    le dispositif de commande et/ou de régulation (28) est réalisé de telle sorte que l'unité cylindre-piston (20) soit alimentée avec un volume correspond à une valeur de consigne de course prédéfinie (s) respective.
  13. Dispositif agitateur (10) selon l'une quelconque des revendications 6 ou 8 à 12,
    caractérisé en ce que
    le dispositif de commande et/ou de régulation (28) est réalisé de telle sorte que la fréquence de résonance du système oscillant puisse être variée pour ajuster la fréquence d'agitation par le biais d'une activation ou d'une coupure de volumes identiques (VL1, VR1) des deux côtés du piston de l'unité cylindre-piston (20).
  14. Dispositif agitateur (10) selon l'une quelconque des revendications 1 à 12,
    caractérisé en ce que
    les volumes des deux côtés du piston de l'unité cylindre-piston (20) peuvent être variés en continu par le biais de cylindres hydrauliques déplaçables en parallèle.
EP09745823A 2008-05-16 2009-05-15 Mécanisme d'agitation Not-in-force EP2286025B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008001831 2008-05-16
DE102008040111A DE102008040111A1 (de) 2008-05-16 2008-07-03 Schüttelvorrichtung
PCT/EP2009/055922 WO2009138491A1 (fr) 2008-05-16 2009-05-15 Mécanisme secoueur

Publications (2)

Publication Number Publication Date
EP2286025A1 EP2286025A1 (fr) 2011-02-23
EP2286025B1 true EP2286025B1 (fr) 2011-09-28

Family

ID=41180552

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09745823A Not-in-force EP2286025B1 (fr) 2008-05-16 2009-05-15 Mécanisme d'agitation

Country Status (5)

Country Link
EP (1) EP2286025B1 (fr)
CN (1) CN102027168B (fr)
AT (1) ATE526449T1 (fr)
DE (1) DE102008040111A1 (fr)
WO (1) WO2009138491A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102182729B (zh) * 2011-05-15 2013-05-01 浙江大学 基于伺服阀并联的大流量高频响电液振动装置及控制方法
EP2898145B1 (fr) * 2012-09-18 2018-05-23 Voith Patent GmbH Mécanisme à secousses et procédé d'activation pneumatique d'un mécanisme à secousses
CN106040071A (zh) * 2016-07-08 2016-10-26 上海大学 一种静平衡振荡机构
CN114280921B (zh) * 2021-12-15 2023-11-14 浙江华章科技有限公司 一种摇振装置参数优化方法、装置及存储介质

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE681896C (de) 1936-07-06 1939-10-04 Submarine Signal Co Schuettelvorrichtung fuer Langsiebpapiermaschinen
DE1982687U (de) 1964-10-01 1968-04-04 Beumer Maschf Bernhard Resonanzschwinger mit mechanischem antrieb.
DE4020881A1 (de) 1989-11-09 1991-05-16 Joergen Brosow Resonanzschwinger
CN2059441U (zh) * 1989-11-28 1990-07-18 山东省寿光县第二造纸厂 偏振筛浆机
DE4324595C1 (de) 1993-07-22 1994-12-15 Escher Wyss Gmbh Schüttelbock
JP3531278B2 (ja) * 1995-03-31 2004-05-24 神鋼電機株式会社 振動装置
DE19704730A1 (de) 1997-02-07 1998-08-13 Voith Sulzer Papiermasch Gmbh Schüttelvorrichtung
DE102004037993A1 (de) 2004-08-05 2006-03-16 Voith Paper Patent Gmbh Schüttelvorrichtung

Also Published As

Publication number Publication date
WO2009138491A1 (fr) 2009-11-19
DE102008040111A1 (de) 2009-11-19
EP2286025A1 (fr) 2011-02-23
CN102027168B (zh) 2013-08-14
CN102027168A (zh) 2011-04-20
ATE526449T1 (de) 2011-10-15

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