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.

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• 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)

Applications Claiming Priority (3)

Publications (2)

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• 2008
  • 2008-07-03 DE DE102008040111A patent/DE102008040111A1/de not_active Withdrawn
• 2009
  • 2009-05-15 AT AT09745823T patent/ATE526449T1/de active
  • 2009-05-15 EP EP09745823A patent/EP2286025B1/fr active Active
  • 2009-05-15 CN CN200980117741.5A patent/CN102027168B/zh active Active
  • 2009-05-15 WO PCT/EP2009/055922 patent/WO2009138491A1/fr active Application Filing

Non-Patent Citations (1)

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