EP2286025A1 - Shaking device - Google Patents

Shaking device

Info

Publication number
EP2286025A1
EP2286025A1 EP09745823A EP09745823A EP2286025A1 EP 2286025 A1 EP2286025 A1 EP 2286025A1 EP 09745823 A EP09745823 A EP 09745823A EP 09745823 A EP09745823 A EP 09745823A EP 2286025 A1 EP2286025 A1 EP 2286025A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
shaking device
frequency
counterweight
piston unit
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.)
Granted
Application number
EP09745823A
Other languages
German (de)
French (fr)
Other versions
EP2286025B1 (en
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/en
Application granted granted Critical
Publication of EP2286025B1 publication Critical patent/EP2286025B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 body along an axis thereof, in particular a roller of a machine for producing and / or treating a fibrous web.
  • the fibrous web may in particular be a paper or board web.
  • a shaking device known from WO 98/35094 A1
  • the relevant body is coupled to two eccentric drives whose eccentric positions are adjustable relative to each other for adjusting the stroke of the body movement.
  • a comparable shaking device is also described in EP 1 624 102 B.
  • a shaker for shaking heavy rolls of a paper machine in which a vibration motor is connected via a connecting element with the mass to be shaken, which in Direction of the forced movement controllable, variable in length and in particular is elastically deformable.
  • a resonant oscillator which comprises an active vibrator part, which is in contact with a passive vibrator part of greater length to form a coupling oscillator, the
  • Resonance frequency mainly determined and from one in one
  • 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 body along an axis thereof, in particular a roller of a machine for the production and / or treatment of fibrous web specified, in which the body is resiliently coupled to form a vibration system with a counterweight.
  • means are provided to drive the body and the counter mass comprehensive vibration system at its resonant 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 body axis hydraulic cylinder / piston unit is provided, the piston coupled to the body and the cylinder is movably mounted along the body axis to form the oscillating counterweight along the body axis, wherein the body on both sides of the piston provided enclosed volumes of particular gleichaueren Cylinder / piston unit resiliently, for example hydraulically, coupled to 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 cylinder with the sheathing material, preferably concrete be surrounded.
  • 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 intrinsic 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 body and / or the stroke of the counterweight.
  • the relevant path signals can then be supplied to the control and / or regulating device.
  • the 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 body 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 predefinable frequency is preferably adaptable to the changing circumstances, such as temperature or friction conditions.
  • 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.
  • the 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.
  • the control and / or regulating device can in particular be designed so that the cylinder / piston unit is supplied to a respective Hubsollwertvorgabe corresponding volume.
  • 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 body forming the mass or the counterweight can be excited to oscillate from the outside ("pushing"), for example, so-called mechanical shakers, hydraulic cylinders and / or electromagnets can be used, in which case actuation via the servo valve is dispensed with.
  • the method described for the automatic determination of the resonance frequency can also be used.
  • 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 body and the countermass 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 is a schematic representation of an exemplary embodiment of a shaking device according to the invention
  • 2 shows a diagram in which, for an exemplary embodiment of the hydraulic resonance oscillator of the shaking device according to FIG. 1, the cylinder pressure and the dead volume are indicated over the frequency
  • FIG. 3 is a diagram in which, for a further exemplary embodiment of the hydraulic resonance oscillator
  • Fig. 1 shows a schematic representation of an exemplary embodiment of a shaking device 10 according to the invention for reciprocating a one
  • Mass r ⁇ ii having body 12 along an axis 14 thereof.
  • the body 12 is one Roller of a machine for producing and / or treating a fibrous web, in particular paper or board web.
  • the axis 14 in the present case is the roll axis.
  • the body 12 is resiliently coupled to a counterweight 16 for forming a vibration system.
  • the two masses of the body 12 and the piston 22 on the one hand and the counterweight 16 on the other hand at least substantially the same size, so r ⁇ ii «
  • means 18 are provided to drive the body 12 together with the piston 22 and the counterweight 16 comprehensive vibration system at the resonant frequency.
  • an aligned with the body axis 14 hydraulic cylinder / piston unit 20 is provided, the piston 22 with the body 12 and mechanically coupled and the cylinder 24 is mounted to form the oscillating counterweight 16 along the body axis 14 movable.
  • the body 12 via the both sides of the piston 22 provided enclosed volumes V L , V R of the preferably synchronous 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 with the sheathing material preferably concrete, be surrounded.
  • 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 body 12 and / or the stroke of the counterweight 16.
  • control and / or regulating device 28 provided in particular for controlling the servo valve 26 may be designed such that the automatic
  • the exciter frequency which is applied to the vibration system, starting from a predetermined frequency f in defined small steps up and / or down is varied until the sum of the strokes of the body 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.
  • the 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 body 12 comprising mass or the counterweight 16 are excited from the outside to the oscillation (pushing).
  • 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 body 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.
  • the cylinder pressure and the dead volume over the frequency are indicated for a further exemplary embodiment of the hydraulic resonance oscillator.
  • the body 12 may be, for example, a roller
  • the counterweight 16 may comprise, for example, a hydraulic cylinder cast around with concrete.
  • 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.
  • the stroke SI ⁇ , Sm 2 (see Fig. 1) of the two masses 12, 16 is detected by way of displacement sensors 30, 32.
  • 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 (+/-), until the sum of the two strokes SITH and Sm 2 or the two cylinder pressures a maximum is detected, wherein, 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)

Abstract

The invention relates to a shaking device (10) for moving a member (12) back and forth along an axis (14) thereof, in particular a roller of a machine for producing and/or treating a fiber web. In the shaking device, the member (12) is coupled elastically to a counterweight (16) for the purposes of forming an oscillating system, and means (18) are provided for driving the oscillation system, which comprises the member (12) and the counterweight (16), at the resonance frequency thereof.

Description

Schüttelvorrichtung shaking
Die Erfindung betrifft eine Schüttelvorrichtung zum Hin- und Herbewegen eines Körpers entlang einer Achse desselben, insbesondere einer Walze einer Maschine zur Herstellung und/oder Behandlung einer Faserstoffbahn. Bei der Faserstoffbahn kann es sich insbesondere um eine Papier- oder Kartonbahn handeln.The invention relates to a shaking device for reciprocating a body along an axis thereof, in particular a roller of a machine for producing and / or treating a fibrous web. The fibrous web may in particular be a paper or board web.
Bei derartigen Schüttelvorrichtungen kann es dazu kommen, dass Reaktionskräfte in das Fundament eingeleitet werden. Ein weiteres Problem besteht darin, dass sich ein relativ hoher Energieverbrauch ergeben kann.In such shakers, it may happen that reaction forces are introduced into the foundation. Another problem is that a relatively high energy consumption can result.
Aus der DE-PS 681 896 ist bereits eine Schüttelvorrichtung für Langsiebpapiermaschinen bekannt, bei der der Siebtisch mit einem Ausgleichsgewicht elastisch verbunden ist, wodurch ein zwei in Resonanz stehende Massen umfassendes Schwingsystem gebildet wird.From DE-PS 681 896 a shaking device for long-screen paper machines is already known, in which the forming table is elastically connected to a balance weight, whereby a two standing in resonance masses comprehensive oscillating system is formed.
Bei einer aus der WO 98/35094 A1 bekannten Schüttelvorrichtung ist der betreffende Körper mit zwei Exzenterantrieben gekoppelt, deren Exzenterlagen zur Einstellung des Hubs der Körperbewegung gegeneinander verstellbar sind. Eine vergleichbare Schüttelvorrichtung ist auch in der EP 1 624 102 B beschrieben.In a shaking device known from WO 98/35094 A1, the relevant body is coupled to two eccentric drives whose eccentric positions are adjustable relative to each other for adjusting the stroke of the body movement. A comparable shaking device is also described in EP 1 624 102 B.
Aus der EP 0 635 601 A1 ist ein Schüttelbock zum Schütteln von schweren Walzen einer Papiermaschine bekannt, bei der ein Schwingungsmotor über ein Verbindungselement mit der zu schüttelnden Masse verbunden ist, das in Richtung der Zwangsbewegung kontrollierbar, längenveränderbar und insbesondere federelastisch verformbar ist.From EP 0 635 601 A1 a shaker for shaking heavy rolls of a paper machine is known in which a vibration motor is connected via a connecting element with the mass to be shaken, which in Direction of the forced movement controllable, variable in length and in particular is elastically deformable.
In der EP 0 500 765 B1 ist ein Resonanzschwinger beschrieben, der einen aktiven Schwingerteil umfasst, der unter Bildung eines Koppelschwingers mit einem passiven Schwingerteil größerer Länge in Berührung steht, der dieIn EP 0 500 765 B1, a resonant oscillator is described, which comprises an active vibrator part, which is in contact with a passive vibrator part of greater length to form a coupling oscillator, the
Resonanzfrequenz hauptsächlich bestimmt und aus einer in einemResonance frequency mainly determined and from one in one
Resonanzbehälter enthaltenden Flüssigkeitssäule besteht, deren Menge zurResin tank containing liquid column, the amount of the
Änderung der Resonanzfrequenz durch einen verstellbaren Teil kontinuierlich veränderbar ist.Change in the resonant frequency by an adjustable part is continuously variable.
Bei einem in dem DE-GBM 1 982 687 beschriebenen Resonanzschwinger sind zur Veränderung der Schwingweite neben Energie speichernden Resonanzfedern ein oder mehrere Dämpfervorrichtungen vorgesehen, deren Dämpferglieder eine veränderbare Dämpfung ermöglichen.In a resonant oscillator described in DE-GBM 1 982 687 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.
Der Erfindung liegt die Aufgabe zugrunde, eine verbesserte Schüttelvorrichtung der eingangs genannten Art zu schaffen. Dabei soll auf einfache und zuverlässige Art und Weise insbesondere im Wesentlichen ausgeschlossen sein, dass Reaktionskräfte in das Fundament eingeleitet werden. Zudem soll der Energieverbrauch auf ein Minimum reduziert werden.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.
Erfindungsgemäß wird diese Aufgabe gelöst durch die Merkmale des Anspruchs 1.According to the invention, this object is achieved by the features of claim 1.
Es wird also eine Schüttelvorrichtung zum Hin- und Herbewegen eines Körpers entlang einer Achse desselben, insbesondere einer Walze einer Maschine zur Herstellung und/oder Behandlung von Faserstoffbahn, angegeben, bei der der Körper zur Bildung eines Schwingungssystems federelastisch mit einer Gegenmasse gekoppelt ist. Zudem sind Mittel vorgesehen, um das den Körper sowie die Gegenmasse umfassende Schwingungssystem bei dessen Resonanzfrequenz anzutreiben. Ein in der Praxis sinnvoller Bereich für die Resonanzfrequenz kann zwischen 3 und 20 Hz, insbesondere zwischen 5 und 10 Hz liegen.It is therefore a shaking device for reciprocating a body along an axis thereof, in particular a roller of a machine for the production and / or treatment of fibrous web specified, in which the body is resiliently coupled to form a vibration system with a counterweight. In addition, means are provided to drive the body and the counter mass comprehensive vibration system at its resonant frequency. A practical area for the Resonance frequency can be between 3 and 20 Hz, in particular between 5 and 10 Hz.
Aufgrund dieser Ausbildung wird unter anderem erreicht, dass keine den Prozess störenden Reaktionskräfte in das Fundament eingeleitet werden. Zudem ist der Energieverbrauch für den Antrieb der Schüttelvorrichtung deutlich reduziert.On the basis of this training, it is achieved, inter alia, that no reaction forces disturbing reaction forces are introduced into the foundation. In addition, the energy consumption for driving the shaker is significantly reduced.
Mit dem Körper bzw. der Walze, gegebenenfalls mitsamt Kolbenstange, einerseits und der Gegenmasse andererseits ergibt sich eine Art Resonanzschwinger mit zwei Massen.With the body or the roller, possibly together with the piston rod, on the one hand and the counterweight on the other hand results in a kind of resonant oscillator with two masses.
Bevorzugt ist eine mit der Körperachse ausgerichtete hydraulische Zylinder/Kolben-Einheit vorgesehen, deren Kolben mit dem Körper gekoppelt und deren Zylinder zur Bildung der schwingenden Gegenmasse entlang der Körperachse beweglich gelagert ist, wobei der Körper über die beiderseits des Kolbens vorgesehenen eingeschlossenen Volumina der insbesondere gleichgängigen Zylinder/Kolben-Einheit federelastisch, beispielsweise hydraulisch, mit der den Zylinder umfassenden Gegenmasse gekoppelt ist.Preferably, a aligned with the body axis hydraulic cylinder / piston unit is provided, the piston coupled to the body and the cylinder is movably mounted along the body axis to form the oscillating counterweight along the body axis, wherein the body on both sides of the piston provided enclosed volumes of particular gleichgängigen Cylinder / piston unit resiliently, for example hydraulically, coupled to the counterweight comprising the cylinder.
Die beiden federelastisch miteinander gekoppelten Massen können in dem gebildeten Schwingungssystem gegeneinander schwingen. Dabei sind aus Praxisgründen bevorzugt gleiche oder etwa gleiche Massen vorgesehen. Die beiden federelastisch miteinander gekoppelten Massen können jedoch auch in einem gegenseitigen Verhältnis von 3:1 bis 1 :3 liegen.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.
Der Zylinder der Zylinder/Kolben-Einheit umfasst zweckmäßigerweise eine die Masse erhöhende Ummantelung, insbesondere eine Betonummantelung. Dabei kann der Zylinder mit dem Ummantelungsmaterial, vorzugsweise Beton, umgössen sein. Die die federelastische Kopplung bewirkenden Justierfedern können also insbesondere als reine Ölfedern durch die eingeschlossenen Volumina in einem insbesondere gleichgängigen Hydraulikzylinder realisiert sein.The cylinder of the cylinder / piston unit expediently comprises a shell which increases the mass, in particular a concrete casing. In this case, the cylinder with the sheathing material, preferably concrete, be surrounded. 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.
Wie bereits erwähnt, wird der hydraulische Schwinger bevorzugt in der Eigenoder Resonanzfrequenz betrieben.As already mentioned, the hydraulic oscillator is preferably operated at the intrinsic or resonant frequency.
Die Antriebsmittel der Schüttelvorrichtung umfassen vorteilhafterweise Mittel zur zyklischen Druckversorgung der Zylinder/Kolben-Einheit. Dabei können die Antriebsmittel der Schüttelvorrichtung insbesondere ein Servoventil umfassen.The drive means of the shaking device advantageously comprise means for the cyclical pressure supply of the cylinder / piston unit. In this case, the drive means of the shaking device may in particular comprise a servo valve.
Gemäß einer bevorzugten praktischen Ausführungsform der erfindungsgemäßen Schüttelvorrichtung ist die Zylinder/Kolben-Einheit über die Antriebsmittel der Schüttelvorrichtung so beaufschlagbar, dass durch Dämpfung und/oder Reibung bedingte Energieverluste durch eine entsprechende Druckerhöhung insbesondere beim Druckmaximum im Umkehrpunkt wieder ausgeglichen werden. Die damit verbundene Volumenvergrößerung kann zum Beispiel nach einer halben Weglänge (π), das heißt bei dem Druck Null im Umkehrpunkt wieder ausgeglichen werden.According to a preferred practical embodiment of the shaking device according to the invention, 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 (π), that is at zero pressure at the reversal point.
Die zyklische Druckversorgung kann insbesondere über das Servoventil erfolgen.The cyclical pressure supply can take place in particular via the servo valve.
Die Antriebsmittel der Schüttelvorrichtung umfassen bevorzugt eine Steuer- und/oder Regeleinrichtung, wobei diese insbesondere zur Ansteuerung des Servoventils vorgesehen sein kann.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.
Von Vorteil ist insbesondere auch, wenn die Antriebsmittel der Schüttelvorrichtung Wegsensoren zur Erfassung des Hubs des Körpers und/oder des Hubs der Gegenmasse umfassen. Die betreffenden Wegsignale können dann der Steuer- und/oder Regeleinrichtung zugeführt werden. Von Vorteil ist insbesondere auch, wenn die insbesondere zur Ansteuerung des Servoventils vorgesehene Steuer- und/oder Regeleinrichtung so ausgeführt ist, dass zur automatischen Ermittlung der Resonanzfrequenz des Schwingungssystems die Erregerfrequenz, mit der das Schwingungssystem beaufschlagt wird, ausgehend von einer vorgebbaren Frequenz in definierten Schritten nach oben und/oder nach unten variiert wird, bis die Summe der Hübe des Körpers und der Gegenmasse ein Maximum erreicht hat. Dabei kann die vorgegebene, zum Beispiel rechnerische Frequenz insbesondere in kleinen Schritten variiert werden.It is also particularly advantageous if the drive means of the shaking device comprise displacement sensors for detecting the stroke of the body and / or the stroke of the counterweight. The relevant path signals can then be supplied to the control and / or regulating device. It is also of particular advantage if the 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 body and the counterweight has reached a maximum. In this case, the predetermined, for example, computational frequency can be varied in particular in small steps.
Weiterhin kann die Resonanzfrequenz des Schwingungssystems permanent oder in zeitlichen Abständen durch eine minimalste Variation (+/-) der vorgebbaren Frequenz und damit eine verbundene Gesamthubveränderung auf Veränderungen überprüfbar sein. Hierbei ist die vorgebbare Frequenz bevorzugt den sich ändernden Gegebenheiten, wie beispielsweise Temperatur oder Reibungsverhältnisse, adaptiv anpassbar.Furthermore, 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. In this case, the predefinable frequency is preferably adaptable to the changing circumstances, such as temperature or friction conditions.
Die Steuer- und/oder Regeleinrichtung kann insbesondere auch so ausgeführt sein, dass bei der Variation der Erregerfrequenz der Stellweg und die Stellzeit des Servoventils konstant gehalten werden.The 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.
Damit kann dann automatisch die genaue Resonanzfrequenz gefunden werden.This will then automatically the exact resonance frequency can be found.
Gemäß einer zweckmäßigen praktischen Ausführungsform ist die Steuer- und/oder Regeleinrichtung so ausgeführt, dass nach erfolgter Ermittlung der Resonanzfrequenz des Schwingungssystems der Hub der Gegenmasse durch das bevorzugt am Umkehrpunkt bzw. im Umkehrbereich der Zylinder/Kolben- Einheit zugespeiste Volumen definiert wird. Dabei kann die Steuer- und/oder Regeleinrichtung insbesondere so ausgeführt sein, dass der Zylinder/Kolben- Einheit ein einer jeweiligen Hubsollwertvorgabe entsprechendes Volumen zugespeist wird. Ist also die genaue Resonanzfrequenz über die Steuer- und/oder Regeleinrichtung aufgefunden, wird der Hub durch das bevorzugt am Umkehrpunkt bzw. im Umkehrbereich zugespeiste Volumen definiert. Von der Steuer- und/oder Regeleinrichtung wird die Menge entsprechend der Hubsollwertvorgabe eingestellt.According to an expedient practical embodiment, the 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. In this case, the control and / or regulating device can in particular be designed so that the cylinder / piston unit is supplied to a respective Hubsollwertvorgabe corresponding volume. Thus, if the exact resonance frequency is found via the control and / or regulating device, 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.
Von Vorteil ist insbesondere auch, wenn die Steuer- und/oder Regeleinrichtung so ausgeführt ist, dass die Resonanzfrequenz des Schwingungssystems zur Einstellung der Schüttelfrequenz über ein Zu- bzw. Abschalten bevorzugt von gleichen Volumina auf den beiden Kolbenseiten der Zylinder/Kolben-Einheit variierbar ist.It is particularly advantageous if the 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 ,
Die Variation der Eigenfrequenz kann also durch Zu- bzw. Abschalten von vorzugsweise gleichen Volumina auf beiden Kolbenseiten stattfinden (VierZweiwegeventil). So kann schrittweise die Schüttelfrequenz eingestellt werden.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). Thus, the shaking frequency can be set gradually.
Gemäß einer alternativen vorteilhaften Ausführungsform sind die Volumina auf den beiden Kolbenseiten der Zylinder/Kolben-Einheit über parallel verfahrbare Hydraulikzylinder stufenlos variierbar. Insbesondere werden dabei beide Volumina der beiden Hydraulikzylinder gleichzeitig um gleiche Beträge verstellt.According to an alternative advantageous embodiment, the volumes on the two piston sides of the cylinder / piston unit can be varied continuously via parallel movable hydraulic cylinders. In particular, both volumes of the two hydraulic cylinders are simultaneously adjusted by equal amounts.
Die Gegenmasse kann über zwei einstellbare Justierfedern in oder etwa in der Mitte des Gesamthubs gehalten werden.The counterweight can be held by two adjustable Justierfedern in or about in the middle of the total stroke.
Wird ein leckagefreies Ölsystem vorausgesetzt, kann die Verlustenergie auch auf anderem Weg zugeführt werden. So können beispielsweise der die eine Masse bildende Körper oder die Gegenmasse von außen zur Oszillation angeregt werden („Anschieben"). Dazu können beispielsweise so genannte mechanische Shaker, Hydraulikzylinder und/oder Elektromagnete eingesetzt werden. In diesem Fall entfällt die Ansteuerung über das Servoventil. Das beschriebene Verfahren zur automatischen Ermittlung der Resonanzfrequenz kann dabei ebenfalls angewendet werden. Bei einem leckagebehafteten Ölsystem muss die Leckagennenge durch eine Nachdosierung ersetzt werden, damit die eingeschlossenen Volumina etwa konstant gehalten werden. Eine Leckage wird erkannt, wenn bei gleicher zugeführter Verlustenergie die Summe der Hübe des Körpers und der Gegenmasse kleiner wird und/oder die Resonanzfrequenz abfällt.If a leak-free oil system is assumed, the energy loss can also be supplied by other means. For example, the body forming the mass or the counterweight can be excited to oscillate from the outside ("pushing"), for example, so-called mechanical shakers, hydraulic cylinders and / or electromagnets can be used, in which case actuation via the servo valve is dispensed with. The method described for the automatic determination of the resonance frequency can also be used. 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 body and the countermass becomes smaller and / or the resonance frequency drops with the same loss energy supplied.
Prinzipiell lassen sich die hydraulischen Justierfedern durch Justierfedern beliebiger Art ersetzen. Was die Verlustenergie betrifft, so kann diese beispielsweise durch Anschieben kompensiert werden. Für eine definierte Frequenz kann so ein mechanisches System mit Justierfedern realisiert werden. Durch Zu- und Abschalten weiterer Justierfedern sind Frequenzsprünge realisierbar.In principle, 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. For a defined frequency, a mechanical system with adjusting springs can be realized. By switching on and off further adjustment springs frequency jumps can be realized.
Weitere Merkmale und Vorteile der Erfindung ergeben sich aus der Zeichnung; in dieser zeigen:Further features and advantages of the invention will become apparent from the drawing; in this show:
Fig. 1 eine schematische Darstellung einer beispielhaften Ausführungsform einer erfindungsgemäßen Schüttelvorrichtung; Fig. 2 ein Diagramm, in dem für eine beispielhafte Ausführungsform des hydraulischen Resonanzschwingers der Schüttelvorrichtung gemäß Figur 1 der Zylinderdruck sowie das Totvolumen über der Frequenz angegeben sind; und Fig. 3 ein Diagramm, in dem für eine weitere beispielhafte Ausführungsform des hydraulischen Resonanzschwingers derFig. 1 is a schematic representation of an exemplary embodiment of a shaking device according to the invention; 2 shows a diagram in which, for an exemplary embodiment of the hydraulic resonance oscillator of the shaking device according to FIG. 1, the cylinder pressure and the dead volume are indicated over the frequency; and FIG. 3 is a diagram in which, for a further exemplary embodiment of the hydraulic resonance oscillator
Zylinderdruck sowie das Totvolumen über der Frequenz angegeben sind.Cylinder pressure and the dead volume over the frequency are specified.
Fig. 1 zeigt in schematischer Darstellung eine beispielhafte Ausführungsform einer erfindungsgemäßen Schüttelvorrichtung 10 zum Hin- und Herbewegen eines eineFig. 1 shows a schematic representation of an exemplary embodiment of a shaking device 10 according to the invention for reciprocating a one
Masse rτii aufweisenden Körpers 12 entlang einer Achse 14 desselben. Im vorliegenden Fall handelt es sich bei dem Körper 12 beispielsweise um eine Walze einer Maschine zur Herstellung und/oder Behandlung einer Faserstoffbahn, insbesondere Papier- oder Kartonbahn. Die Achse 14 ist im vorliegenden Fall die Walzenachse.Mass rτii having body 12 along an axis 14 thereof. For example, in the present case, the body 12 is one Roller of a machine for producing and / or treating a fibrous web, in particular paper or board web. The axis 14 in the present case is the roll axis.
Der Körper 12 ist zur Bildung eines Schwingungssystems federelastisch mit einer aufweisenden Gegenmasse 16 gekoppelt. Beim vorliegenden Ausführungsbeispiel sind die beiden Massen des Körpers 12 und des Kolbens 22 einerseits und der Gegenmasse 16 andererseits zumindest im Wesentlichen gleich groß, also rτii «The body 12 is resiliently coupled to a counterweight 16 for forming a vibration system. In the present embodiment, the two masses of the body 12 and the piston 22 on the one hand and the counterweight 16 on the other hand at least substantially the same size, so rτii «
Zudem sind Mittel 18 vorgesehen, um das den Körper 12 samt Kolben 22 sowie die Gegenmasse 16 umfassende Schwingungssystem bei dessen Resonanzfrequenz anzutreiben.In addition, means 18 are provided to drive the body 12 together with the piston 22 and the counterweight 16 comprehensive vibration system at the resonant frequency.
Dabei ist eine mit der Körperachse 14 ausgerichtete hydraulische Zylinder/Kolben- Einheit 20 vorgesehen, deren Kolben 22 mit dem Körper 12 spielfrei und mechanisch gekoppelt und deren Zylinder 24 zur Bildung der schwingenden Gegenmasse 16 entlang der Körperachse 14 beweglich gelagert ist. Dabei ist der Körper 12 über die beiderseits des Kolbens 22 vorgesehenen eingeschlossenen Volumina VL, VR der vorzugsweise gleichgängigen Zylinder/Kolben-Einheit 20 federelastisch mit der den Zylinder 24 umfassenden Gegenmasse 16 gekoppelt. Der Zylinder 24 der Zylinder/Kolben-Einheit 20 kann eine die Masse erhöhende Ummantelung, insbesondere Betonummantelung, umfassen. Dabei kann der Zylinder 24 mit dem Ummantelungsmaterial, vorzugsweise Beton, umgössen sein.In this case, an aligned with the body axis 14 hydraulic cylinder / piston unit 20 is provided, the piston 22 with the body 12 and mechanically coupled and the cylinder 24 is mounted to form the oscillating counterweight 16 along the body axis 14 movable. In this case, the body 12 via the both sides of the piston 22 provided enclosed volumes V L , V R of the preferably synchronous 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. In this case, the cylinder 24 with the sheathing material, preferably concrete, be surrounded.
Die Antriebsmittel 18 der Schüttelvorrichtung können insbesondere Mittel zur zyklischen Druckversorgung der Zylinder/Kolben-Einheit 20 umfassen.The drive means 18 of the shaking device may in particular comprise means for the cyclical pressure supply of the cylinder / piston unit 20.
Dabei können die Antriebsmittel 18 der Schüttelvorrichtung insbesondere zur zyklischen Druckversorgung der Zylinder/Kolben-Einheit 20 ein Servoventil 26 umfassen. Die Zylinder/Kolben-Einheit 20 ist über die Antriebsmittel 18 der Schüttelvorrichtung insbesondere so beaufschlagbar, dass durch Dämpfung und/oder Reibung bedingte Energieverluste durch eine entsprechende Druckerhöhung insbesondere beim Druckmaximum im Umkehrpunkt wieder ausgeglichen werden. Die damit verbundene Volumenvergrößerung kann nach etwa einer halben Wellenlänge (π), das heißt bei einem Druck Null im Umkehrpunkt wieder ausgeglichen werden.In this case, 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 (π), that is to say at zero pressure at the point of reversal.
Wie bereits erwähnt, erfolgt die zyklische Druckversorgung vorzugsweise über das Servoventil 26.As already mentioned, the cyclical pressure supply preferably takes place via the servo valve 26.
Insbesondere zur Ansteuerung dieses Servoventils 26 können die Antriebsmittel 18 der Schüttelvorrichtung eine Steuer- und/oder Regeleinrichtung 28 umfassen.In particular, for driving this servo valve 26, the drive means 18 of the shaking device may include a control and / or regulating device 28.
Zudem können die Antriebsmittel 18 der Schüttelvorrichtung Wegsensoren 30, 32 zur Erfassung des Hubs des Körpers 12 und/oder des Hubs der Gegenmasse 16 aufweisen.In addition, the drive means 18 of the shaker device can have displacement sensors 30, 32 for detecting the stroke of the body 12 and / or the stroke of the counterweight 16.
Auch kann die insbesondere zur Ansteuerung des Servoventils 26 vorgesehen Steuer- und/oder Regeleinrichtung 28 so ausgeführt sein, dass zur automatischenAlso, the control and / or regulating device 28 provided in particular for controlling the servo valve 26 may be designed such that the automatic
Ermittlung der Resonanzfrequenz des Schwingungssystems die Erregerfrequenz, mit der das Schwingungssystem beaufschlagt wird, ausgehend von einer vorgebbaren Frequenz f in definierten kleinen Schritten nach oben und/oder nach unten variiert wird, bis die Summe der Hübe des Körpers und der Gegenmasse ein Maximum erreicht hat.Determining the resonant frequency of the vibration system, the exciter frequency, which is applied to the vibration system, starting from a predetermined frequency f in defined small steps up and / or down is varied until the sum of the strokes of the body and the counterweight has reached a maximum.
Ferner kann die Resonanzfrequenz des Schwingungssystems permanent oder in zeitlichen Abständen durch eine minimalste Variation (+/-) der Vorgebbaren Frequenz f und damit eine verbundene Gesamthubveränderung auf Veränderungen überprüfbar sein. Hierbei ist die vorgebbare Frequenz f den sich ändernden Gegebenheiten, wie beispielsweise Temperatur oder Reibungsverhältnisse, adaptiv anpassbar. Dabei kann die Steuer- und/oder Regeleinrichtung 28 insbesondere auch so ausgeführt sein, dass bei der Variation der Erregerfrequenz der Stellweg und die Stellzeit des Servoventils 26 konstant gehalten werden.Furthermore, 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. In this case, the predefinable frequency f is adaptively adaptable to the changing circumstances, such as temperature or friction conditions. In this case, the 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.
Die Steuer- und/oder Regeleinrichtung 28 kann insbesondere auch so ausgeführt sein, dass nach erfolgter Ermittlung der Resonanzfrequenz des Schwingungssystems der Hub der Gegenmasse 16 durch das bevorzugt am Umkehrpunkt der Zylinder/Kolben-Einheit 20 zugespeiste Volumen definiert wird.In particular, the 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.
Es ist insbesondere auch eine solche Ausführung der Steuer- und/oder Regeleinrichtung 28 denkbar, bei der der Zylinder/Kolben-Einheit 20 ein einer jeweiligen Hubsollwertvorgabe s entsprechendes Volumen zugespeist wird.In particular, such an embodiment of the 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.
Überdies kann die Steuer- und/oder Regeleinrichtung 28 insbesondere auch so ausgeführt sein, dass die Resonanzfrequenz des Schwingungssystems zur Einstellung der Schüttelfrequenz über ein Zu- bzw. Abschalten von gleichen Volumina auf den beiden Kolbenseiten der Zylinder/Kolben-Einheit 20 variierbar ist.In addition, the 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.
Grundsätzlich können die Volumina auch durch parallel verfahrbare Hydraulikzylinder stufenlos variiert werden. Insbesondere werden dabei beide Volumina der beiden Hydraulikzylinder gleichzeitig um gleiche Beträge verstellt.In principle, the volumes can also be varied steplessly by parallel movable hydraulic cylinders. In particular, both volumes of the two hydraulic cylinders are simultaneously adjusted by equal amounts.
Die Gegenmasse 16 kann über zwei einstellbare Justierfedern 34, 36 in oder etwa in der Mitte des Gesamthubs gehalten werden.The counterweight 16 can be held via two adjustable Justierfedern 34, 36 in or approximately in the middle of the total stroke.
Wird ein leckagefreies Ölsystem vorausgesetzt, kann die zur Kompensation der Verlustenergie dienende Energie auch auf andere Art zugeführt werden. So kann beispielsweise die den Körper 12 umfassende Masse oder die Gegenmasse 16 von außen zur Oszillation angeregt werden (Anschieben). Es sind beispielsweise auch so genannte mechanische Shaker, Hydraulikzylinder, Elektromagnete und/oder dergleichen denkbar. Die Ansteuerung über das Servoventil 26 entfällt in diesem Fall. Das beschriebene Verfahren zur automatischen Ermittlung der Resonanzfrequenz kann dabei ebenfalls angewendet werden.If a leak-free oil system is assumed, the energy used to compensate for the loss energy can also be supplied in another way. Thus, for example, the body 12 comprising mass or the counterweight 16 are excited from the outside to the oscillation (pushing). There are, for example, so-called mechanical shakers, hydraulic cylinders, electromagnets and / or the like conceivable. 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.
Bei einem leckagebehafteten Ölsystem muss die Leckagemenge durch eine Nachdosierung ersetzt werden, damit die eingeschlossenen Volumina etwa konstant gehalten werden. Eine Leckage wird erkannt, wenn bei gleicher zugeführter Verlustenergie die Summe der Hübe des Körpers 12 und der Gegenmasse 16 kleiner wird und/oder die Resonanzfrequenz abfällt.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 body 12 and the counterweight 16 is smaller and / or the resonance frequency drops at the same supplied loss energy.
Prinzipiell lassen sich die hydraulischen Justierfedern durch Justierfedern beliebiger Art ersetzen. Was die Verlustenergie angeht, so kann die zur Kompensation erforderliche Energie beispielsweise durch Anschieben in das System eingebracht werden. Für eine definierte Frequenz f kann so ein mechanisches System mit Justierfedern realisiert werden. Durch Zuschalten von weiteren Justierfedern sind Frequenzsprünge realisierbar.In principle, the hydraulic adjusting springs can be replaced by adjusting springs of any kind. As far as the loss energy is concerned, the energy required for compensation can be introduced into the system, for example, by pushing. For a defined frequency f, a mechanical system with adjusting springs can thus be realized. By adding additional Justierfedern frequency jumps can be realized.
In dem Diagramm gemäß Fig. 2 sind für eine beispielhafte Ausführungsform des beispielsweise in der Fig. 1 wiedergegebenen hydraulischen Resonanzschwingers der Zylinderdruck sowie das Totvolumen über der Frequenz angegeben. Dabei ist die vorliegende Ausführungsform durch die folgenden Werte definiert:In the diagram according to FIG. 2, for an exemplary embodiment of the hydraulic resonance oscillator shown, for example, in FIG. 1, the cylinder pressure and the dead volume are indicated over the frequency. Here, the present embodiment is defined by the following values:
Masse des hier beispielsweise durch eine Walze gebildeten Körpers 12 3000 kgMass of the body formed here for example by a roller 12 3000 kg
Gegenmasse 16 3000 kg, z.B. Beton, D = 1 ,4 m x 1 m Walzenhub 20 mmCounterweight 16 3000 kg, e.g. Concrete, D = 1, 4 m x 1 m Roll stroke 20 mm
Wirksame Kolbenfläche 0,006 m2 Effective piston area 0.006 m 2
In dem Diagramm gemäß Fig. 3 sind für eine weitere beispielhafte Ausführungsform des hydraulischen Resonanzschwingers der Zylinderdruck sowie das Totvolumen über der Frequenz angegeben. Dabei ist die vorliegende Ausführungsform durch die folgenden Werte definiert: Masse des hier beispielsweise durch eine Walze gebildeten Körpers 12 3000 kg Gegenmasse 16 3000 kg, z.B. Beton, D = 1 ,4 m x 1 mIn the diagram according to FIG. 3, the cylinder pressure and the dead volume over the frequency are indicated for a further exemplary embodiment of the hydraulic resonance oscillator. Here, the present embodiment is defined by the following values: Mass of the body formed here for example by a roller 12 3000 kg counterweight 16 3000 kg, eg concrete, D = 1, 4 mx 1 m
Walzenhub 10 mmRoller stroke 10 mm
Wirksame Kolbenfläche 0,0123 m2 Effective piston area 0,0123 m 2
Es werden also zwei gegeneinander schwingende Massen, nämlich insbesondere der Körper 12 und die Gegenmasse 16, über beispielsweise hydraulische Federn gekoppelt, wobei bevorzugt gleiche Massen vorgesehen sind. Bei dem Körper 12 kann es sich beispielsweise um eine Walze handeln, während die Gegenmasse 16 beispielsweise einen mit Beton umgossenen Hydraulikzylinder umfassen kann. Die Federn sind zum Beispiel als reine Ölfedern, das heißt durch die eingeschlossene Volumina im gleichgängigen Hydraulikzylinder realisiert. Der hydraulische Schwinger soll stets in der Resonanz- bzw. Eigenfrequenz betrieben werden. Energieverluste durch Dämpfung und Reibung werden durch Druckerhöhung zum Beispiel bei dem Druckmaximum im Umkehrpunkt ausgeglichen. Die damit verbundene Volumenvergrößerung wird etwa nach einer halben Wellenlänge (π), das heißt bei dem Druck Null im Umkehrpunkt, wieder ausgeglichen. Der Hub SIΓΠ , Sm2 (vgl. Fig. 1 ) der beiden Massen 12, 16 wird über Wegsensoren 30, 32 erfasst. Die Ansteuerung des Servoventils 26 erfolgt über eine Steuer- und/oder Regeleinrichtung 28. Die Steuer- und/oder Regeleinrichtung variiert die vorgegebene (rechnerische) Frequenz f in kleinen Schritten (+/-), bis bei der Summe der beiden Hübe SITH und Sm2 oder der beiden Zylinderdrücke ein Maximum erkannt wird, wobei zum Beispiel der Stellweg und die Stellzeit des Servoventils 26 konstant gehalten werden. Damit wird automatisch die genaue Resonanzfrequenz ermittelt.So there are two mutually oscillating masses, namely in particular the body 12 and the counterweight 16, coupled via, for example, hydraulic springs, wherein preferably the same masses are provided. The body 12 may be, for example, a roller, while the counterweight 16 may comprise, for example, a hydraulic cylinder cast around with concrete. 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 (π), that is, at zero pressure at the point of reversal. The stroke SIΓΠ, Sm 2 (see Fig. 1) of the two masses 12, 16 is detected by way of displacement sensors 30, 32. 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 (+/-), until the sum of the two strokes SITH and Sm 2 or the two cylinder pressures a maximum is detected, wherein, for example, the travel and the travel time of the servo valve 26 are kept constant. This automatically determines the exact resonance frequency.
Ist die genaue Resonanzfrequenz von der Steuer- und/oder Regeleinrichtung 28 ermittelt, wird der Hub durch das bevorzugt am Umkehrpunkt zugespeiste Volumen definiert. Von der Steuer- und/oder Regeleinrichtung 28 wird die Menge entsprechend der Hubsollwertvorgabe s eingestellt. Die Variation der Eigenfrequenz findet durch Zu- bzw. Abschalten von gleichen Volumina VR und VL auf beiden Kolbenseiten statt (Vier-Zweiwegeventil). So kann schrittweise die Schüttelfrequenz eingestellt werden. Alternativ dazu können die Volumina durch parallel verfahrbare Hydraulikzylinder stufenlos variiert werden. If the exact resonance frequency is determined by the control and / or regulating device 28, 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. Alternatively, the volumes can be varied continuously by parallel movable hydraulic cylinders.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
10 Schüttelvorrichtung10 shaker
12 Körper12 bodies
14 Körperachse14 body axis
16 Gegenmasse16 countermass
18 Antriebsmittel18 drive means
20 Zylinder/Kolben-Einheit20 cylinder / piston unit
22 Kolben22 pistons
24 Zylinder24 cylinders
26 Servoventil26 servo valve
28 Steuer- und/oder Regeleinrichtung28 control and / or regulating device
30 Wegsensor30 way sensor
32 Wegsensor32 displacement sensor
34 Justierfeder34 adjusting spring
36 Justierfeder36 adjusting spring
f Frequenzvorgabe mi Masse des Körpers nri2 Masse des Gegenkörpersf frequency specification mi mass of the body nri2 mass of the opposing body
PL Druckverlauf, linksPL pressure curve, left
PR Druckverlauf, rechtsPR pressure curve, right
R ServoventilR servo valve
S HubsollwertvorgabeS Hub setpoint specification
Sm1 Hub des Körpers [graphisch]Sm1 stroke of the body [graphic]
Sm2 Hub der Gegenmasse [grapisch] t ZeitSm2 stroke of counterweight [grapish] t time
VL Volumen, linksV L volume, left
VLI Zusatzvolumen, linksVLI additional volume, left
VR Volumen, rechtsVR volume, right
VRI Zusatzvolumen, rechtsVRI additional volume, right
W Wegeventil W way valve

Claims

SchüttelvorrichtungPatentansprüche SchüttelvorrichtungPatentansprüche
1. Schüttelvorrichtung (10) zum Hin- und Herbewegen eines Körpers (12) entlang einer Achse (14) desselben, insbesondere einer Walze einer Maschine zur Herstellung und/oder Behandlung einer Faserstoffbahn, bei der der Körper (12) zur Bildung eines Schwingungssystems federelastisch mit einer Gegenmasse (16) gekoppelt ist und Mittel (18) vorgesehen sind, um das den Körper (12) sowie die Gegenmasse (16) umfassendeA shaking device (10) for reciprocating a body (12) along an axis (14) thereof, in particular a roll of a machine for making and / or treating a fibrous web, wherein the body (12) is resilient to form a vibratory system is coupled to a counterweight (16) and means (18) are provided to the body (12) and the counterweight (16) comprising
Schwingungssystem bei dessen Resonanzfrequenz anzutreiben.To drive vibration system at the resonant frequency.
2. Schüttelvorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass eine mit der Körperachse (14) ausgerichtete hydraulische2. shaking device according to claim 1, characterized in that a with the body axis (14) aligned hydraulic
Zylinder/Kolben-Einheit (20) vorgesehen ist, deren Kolben (22) mit dem Körper (12) gekoppelt und deren Zylinder (24) zur Bildung der schwingenden Gegenmasse (16) entlang der Körperachse (14) beweglich gelagert ist, wobei der Körper (12) über die beiderseits des Kolbens (22) vorgesehenen eingeschlossenen Volumina (VL, VR) der insbesondere gleichgängigenCylinder / piston unit (20) is provided, the piston (22) coupled to the body (12) and the cylinder (24) for forming the oscillating counterweight (16) along the body axis (14) is movably mounted, wherein the body (12) over the both sides of the piston (22) provided enclosed volumes (V L , V R ) of the particular gleichgleichigen
Zylinder/Kolben-Einheit (20) federelastisch mit der den Zylinder (24) umfassenden Gegenmasse (16) gekoppelt ist.Cylinder / piston unit (20) is resiliently coupled to the cylinder (24) comprising counterweight (16).
3. Schüttelvorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Zylinder (24) der Zylinder/Kolben-Einheit (20) eine die Masse erhöhende Ummantelung, insbesondere Betonummantelung, umfasst.3. shaking device according to claim 2, characterized in that the cylinder (24) of the cylinder / piston unit (20) comprises a mass-increasing sheathing, in particular concrete sheathing comprises.
4. Schüttelvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Antriebsmittel (18) Mittel zur zyklischen Druckversorgung der Zylinder/Kolben-Einheit (20) umfassen.4. shaking device according to one of the preceding claims, characterized in that the drive means (18) comprise means for cyclically supplying pressure to the cylinder / piston unit (20).
5. Schüttelvorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass die Antriebsmittel (18) insbesondere zur zyklischen Druckversorgung der Zylinder/Kolben-Einheit (20) ein Servoventil (26) umfassen.5. shaking device according to claim 4, characterized in that the drive means (18) in particular for the cyclical pressure supply of the cylinder / piston unit (20) comprise a servo valve (26).
6. Schüttelvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Zylinder/Kolben-Einheit (20) über die Antriebsmittel (18) so beaufschlagbar ist, dass durch Dämpfung und/oder Reibung bedingte Energieverluste durch eine entsprechende Druckerhöhung insbesondere beim Druckmaximum im Umkehrpunkt wieder ausgeglichen werden.6. shaking device according to one of the preceding claims, characterized in that the cylinder / piston unit (20) via the drive means (18) can be acted upon by damping and / or friction-related energy losses by a corresponding pressure increase, in particular at the maximum pressure at the reversal point be compensated again.
7. Schüttelvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Antriebsmittel (18) insbesondere zur Ansteuerung des Servoventils eine Steuer- und/oder Regeleinrichtung (28) umfassen.7. shaking device according to one of the preceding claims, characterized in that the drive means (18) in particular for controlling the servo valve comprises a control and / or regulating device (28).
8. Schüttelvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Antriebsmittel (18) Wegsensoren (30, 32) zur Erfassung des Hubs des Körpers (12) und/oder des Hubs der Gegenmasse (16) umfassen.8. shaking device according to one of the preceding claims, characterized in that the drive means (18) displacement sensors (30, 32) for detecting the stroke of the body (12) and / or the stroke of the counterweight (16).
9. Schüttelvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die insbesondere zur Ansteuerung des Servoventils (26) vorgesehene Steuer- und/oder Regeleinrichtung (28) so ausgeführt ist, dass zur automatischen Ermittlung der Resonanzfrequenz des Schwingungssystems die Erregerfrequenz, mit der das Schwingungssystem beaufschlagt wird, ausgehend von einer vorgebbaren Frequenz (f) in definierten Schritten nach oben und/oder nach unten variiert wird, bis die Summe der Hübe des Körpers (12) und der Gegenmasse (16) ein Maximum erreicht hat.9. shaking device according to one of the preceding claims, characterized in that the particular for controlling the servo valve (26) provided for control and / or regulating device (28) is designed so that the automatic detection of the resonant frequency of the vibration system, the exciter frequency, with the Vibration system is acted upon, starting from a predefinable frequency (f) is varied in defined steps up and / or down until the sum of the strokes of the body (12) and the counterweight (16) has reached a maximum.
10. Schüttelvorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass die Resonanzfrequenz des Schwingungssystems permanent oder in zeitlichen Abständen durch eine minimalste Variation (+/-) der Vorgebbaren Frequenz (f) und damit eine verbundene Gesamthubveränderung auf Veränderungen überprüfbar ist und dass die vorgebbare Frequenz (f) den sich ändernden Gegebenheiten, wie beispielsweise Temperatur oder Reibungsverhältnisse, adaptiv anpassbar ist.10. shaking device according to claim 9, characterized in that the resonant frequency of the vibration system permanently or at intervals by a minimum variation (+/-) of the predeterminable frequency (f) and thus a total associated change in the change is verifiable and that the predetermined frequency ( f) is adaptively adaptable to changing circumstances, such as temperature or friction conditions.
11. Schüttelvorrichtung nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass die Steuer- und/oder Regeleinrichtung (28) so ausgeführt ist, dass bei der Variation der Erregerfrequenz der Stellweg und die Stellzeit des Servoventils (26) konstant gehalten werden.11. shaking device according to claim 9 or 10, characterized in that the control and / or regulating device (28) is designed so that when the variation of the excitation frequency of the travel and the travel time of the servo valve (26) are kept constant.
12. Schüttelvorrichtung nach Anspruch 9, 10 oder 11 , dadurch gekennzeichnet, dass die Steuer- und/oder Regeleinrichtung (28) so ausgeführt ist, dass nach erfolgter Ermittlung der Resonanzfrequenz des Schwingungssystems der Hub der Gegenmasse (16) durch das bevorzugt am Umkehrpunkt der Zylinder/Kolben-Einheit (20) zugespeiste Volumen definiert wird.12. shaking device according to claim 9, 10 or 11, characterized in that the control and / or regulating device (28) is designed so that after the determination of the resonant frequency of the vibration system, the stroke of the counterweight (16) by the preferred at the reversal point of Cylinder / piston unit (20) supplied volume is defined.
13. Schüttelvorrichtung nach Anspruch 12, dadurch gekennzeichnet, dass die Steuer- und/oder Regeleinrichtung (28) so ausgeführt ist, dass der Zylinder/Kolben-Einheit (20) ein einer jeweiligen Hubsollwertvorgabe (s) entsprechendes Volumen zugespeist wird. 13. shaking device according to claim 12, characterized in that the control and / or regulating device (28) is designed so that the cylinder / piston unit (20) is fed to a respective Hubsollwertvorgabe (s) corresponding volume.
14. Schüttelvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Steuer- und/oder Regeleinrichtung (28) so ausgeführt ist, dass die Resonanzfrequenz des Schwingungssystems zur Einstellung der Schüttelfrequenz über ein Zu- bzw. Abschalten von gleichen Volumina (Vu,14. shaking device according to one of the preceding claims, characterized in that the control and / or regulating device (28) is designed so that the resonant frequency of the vibration system for adjusting the shaking frequency via an on or off of equal volumes (Vu,
VRi) auf den beiden Kolbenseiten der Zylinder/Kolben-Einheit (20) variierbar ist.V R i) on the two piston sides of the cylinder / piston unit (20) is variable.
15. Schüttelvorrichtung nach einem Ansprüche 1 bis 13, dadurch gekennzeichnet, dass die Volumina auf den beiden Kolbenseiten der Zylinder/Kolben-Einheit (20) über parallel verfahrbare Hydraulikzylinder stufenlos variierbar sind. 15. shaking device according to one claims 1 to 13, characterized in that the volumes on the two piston sides of the cylinder / piston unit (20) via continuously movable hydraulic cylinders are continuously variable.
EP09745823A 2008-05-16 2009-05-15 Shaking device Active EP2286025B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008001831 2008-05-16
DE102008040111A DE102008040111A1 (en) 2008-05-16 2008-07-03 shaking
PCT/EP2009/055922 WO2009138491A1 (en) 2008-05-16 2009-05-15 Shaking device

Publications (2)

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

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EP09745823A Active EP2286025B1 (en) 2008-05-16 2009-05-15 Shaking device

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EP (1) EP2286025B1 (en)
CN (1) CN102027168B (en)
AT (1) ATE526449T1 (en)
DE (1) DE102008040111A1 (en)
WO (1) WO2009138491A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102182729B (en) * 2011-05-15 2013-05-01 浙江大学 Large-flow high-frequency response electrohydraulic vibration device based on parallel servo valves and control method
EP2898145B1 (en) * 2012-09-18 2018-05-23 Voith Patent GmbH Shaking unit and method for the pneumatic excitation of a shaking unit
CN106040071A (en) * 2016-07-08 2016-10-26 上海大学 Static balance oscillating mechanism
CN114280921B (en) * 2021-12-15 2023-11-14 浙江华章科技有限公司 Method and device for optimizing parameters of shaking device and storage medium

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Publication number Priority date Publication date Assignee Title
DE681896C (en) 1936-07-06 1939-10-04 Submarine Signal Co Shaking device for fourdrinier paper machines
DE1982687U (en) 1964-10-01 1968-04-04 Beumer Maschf Bernhard RESONANCE VIBRATOR WITH MECHANICAL DRIVE.
DE4020881A1 (en) 1989-11-09 1991-05-16 Joergen Brosow RESONANCE SWINGARM
CN2059441U (en) * 1989-11-28 1990-07-18 山东省寿光县第二造纸厂 Polarization strainer
DE4324595C1 (en) 1993-07-22 1994-12-15 Escher Wyss Gmbh Shaker
JP3531278B2 (en) * 1995-03-31 2004-05-24 神鋼電機株式会社 Vibration device
DE19704730A1 (en) 1997-02-07 1998-08-13 Voith Sulzer Papiermasch Gmbh Shaker
DE102004037993A1 (en) 2004-08-05 2006-03-16 Voith Paper Patent Gmbh shaking

Non-Patent Citations (1)

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Title
See references of WO2009138491A1 *

Also Published As

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CN102027168A (en) 2011-04-20
EP2286025B1 (en) 2011-09-28
WO2009138491A1 (en) 2009-11-19
DE102008040111A1 (en) 2009-11-19
ATE526449T1 (en) 2011-10-15
CN102027168B (en) 2013-08-14

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