WO2005056279A1 - Dispositif pour serrer des matieres a mouler se presentant sous forme de grains - Google Patents

Dispositif pour serrer des matieres a mouler se presentant sous forme de grains Download PDF

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Publication number
WO2005056279A1
WO2005056279A1 PCT/EP2004/014054 EP2004014054W WO2005056279A1 WO 2005056279 A1 WO2005056279 A1 WO 2005056279A1 EP 2004014054 W EP2004014054 W EP 2004014054W WO 2005056279 A1 WO2005056279 A1 WO 2005056279A1
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WO
WIPO (PCT)
Prior art keywords
mass
oscillator
excitation
dual
vibration
Prior art date
Application number
PCT/EP2004/014054
Other languages
German (de)
English (en)
Inventor
Hubert Bald
Original Assignee
GEDIB Ingenieurbüro und Innovationsberatung GmbH
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Filing date
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Publication of WO2005056279A1 publication Critical patent/WO2005056279A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/02—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space
    • B30B11/022—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space whereby the material is subjected to vibrations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28B—SHAPING CLAY OR OTHER CERAMIC COMPOSITIONS; SHAPING SLAG; SHAPING MIXTURES CONTAINING CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28B1/00—Producing shaped prefabricated articles from the material
    • B28B1/08—Producing shaped prefabricated articles from the material by vibrating or jolting
    • B28B1/087—Producing shaped prefabricated articles from the material by vibrating or jolting by means acting on the mould ; Fixation thereof to the mould
    • B28B1/0873—Producing shaped prefabricated articles from the material by vibrating or jolting by means acting on the mould ; Fixation thereof to the mould the mould being placed on vibrating or jolting supports, e.g. moulding tables
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28B—SHAPING CLAY OR OTHER CERAMIC COMPOSITIONS; SHAPING SLAG; SHAPING MIXTURES CONTAINING CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28B3/00—Producing shaped articles from the material by using presses; Presses specially adapted therefor
    • B28B3/02—Producing shaped articles from the material by using presses; Presses specially adapted therefor wherein a ram exerts pressure on the material in a moulding space; Ram heads of special form
    • B28B3/022—Producing shaped articles from the material by using presses; Presses specially adapted therefor wherein a ram exerts pressure on the material in a moulding space; Ram heads of special form combined with vibrating or jolting

Definitions

  • the invention relates to a device for compacting granular molding materials.
  • Devices of this type are used, for example, for the production of concrete blocks, granular molding material in the form of moist concrete mortar being poured into a mold and compacted by means of vibratory vibrations to form stone blanks which are then allowed to harden.
  • DE 101 54 897 A1 discloses a device for compacting granular molded materials in a mold to form at least one molded body, which is designed as a dual-mass oscillator with which the molded material can be compacted by means of forced vibrations.
  • the two-mass oscillator is formed from a working mass and a cantilever mass, the two masses being coupled to one another by a spring system and oscillating essentially in phase and in opposite directions, the working mass being the mass of an oscillating table for the shape, the shape and the molding material filled therein includes.
  • the dual mass transducer is also supported against a fixed surface by a support spring system.
  • An unbalance vibrator serves as the exciter actuator. With this device, there is no possibility of influencing the excitation power of the unbalance vibrator while maintaining a predetermined compression frequency or of limiting the oscillation path amplitudes, in particular at an excitation frequency in the vicinity of the main natural frequency. Much more is provided there to work considerably above or below the resonance frequency with constant acceleration amplitudes.
  • the object of the invention is to provide a device for compacting granular molding materials, which enables a high compacting performance with a low expenditure of power. This object is achieved in accordance with the features of claim 1.
  • a device for compacting granular molded materials in a mold to at least one molded body which comprises an excitation system with which the molded material can be compressed by means of forced vibrations, a two-mass oscillator being formed from a working mass and a cantilever mass, which is formed by a spring system are coupled to one another and oscillate substantially in phase and in opposite directions, the working mass comprising the mass of a vibrating table for the mold and / or the mass of the mold and the molding material filled therein, and the masses and the spring system of the dual-mass oscillator being coordinated such that the Main natural frequency of the dual mass oscillator in the vicinity of a predetermined one Compression frequency is, and a pressing device, which comprises a pressing plate acting on the molding material in the mold, and preferably a controller by which the excitation power can be changed at a predetermined compression frequency, are provided.
  • the production cycle times can be reduced: With a view to the desired very short production cycle times for a base plate with compacted shaped bodies (in the case of concrete block production in the range of 10 seconds and less), it is of considerable importance within what time at the start of compaction (preferably at least twice per work cycle) the excitation of an oscillation path amplitude can be increased from zero to its predetermined amount. With a specific excitation force that can be applied by the excitation system, the oscillation path amplitude swings up from zero to the target amplitude the faster the closer the excitation frequency is to the main natural frequency. Further embodiments of the invention can be found in the following description and the subclaims. The invention is explained in more detail below on the basis of exemplary embodiments illustrated in the attached figures. Fig.
  • 1a shows the course of an oscillating movement of a working mass and a cantilever mass over time t for a two-mass oscillator.
  • 1b symbolically shows a device comprising a dual-mass oscillator for compacting as an oscillating model.
  • 1 c shows the frequency-dependent course of the oscillation path amplitude and excitation power of a dual-mass oscillator in the region of its main natural frequency.
  • 2 to 4 schematically show embodiments of a device for compacting granular molding materials. As shown in Fig. 1 b, the device comprises a two-mass oscillator 9 with a working mass ma and a cantilever mass mf, both of which are connected by a spring system 24.
  • the working mass ma is connected to a foundation 5 via a support spring system 22.
  • the excitation power and dissipated damping power D may have the same amount here.
  • the spring system 24 is hard in relation to the support spring system 22, so that the spring system 24 essentially determines the main natural frequency fn of the dual-mass oscillator 9, while the influence of the soft support spring system 22 on the main natural frequency of the dual-mass oscillator 9 is practically negligible.
  • the dual-mass oscillator 9 is to be excited to forced vibrations due to its damping power D by an excitation force f (t) 4, which acts on the cantilever mass mf according to FIG. 1b.
  • the excitation force f (t) 4 could also act directly on the working mass ma or the excitation force f (t) could be supported between the masses ma and mf.
  • the model reproduces the conditions when using the dual-mass vibrator 9 in the event of a shock vibration in the event that the corresponding vibrator vibrates freely without the emission of shocks, the damping power D being the same in the (e.g. with several Supporting spring system 22 embodies dissipated power.
  • the model also shows the conditions when using the dual mass vibrator 9 with a harmonic vibration in the event that the corresponding vibrator vibrates freely without the involvement of a press plate during the preliminary vibration, the damping performance D being carried out in the (e.g.
  • the abscissa axes could also represent the common phase angle instead of the common time profile t.
  • the masses ma and mf are - symbolically reduced to one point - each shown in the upper and lower position of the oscillating movements.
  • the oscillation path amplitudes of the working mass ma and the cantilever mass mf are respectively Aa and Af and the corresponding double amplitudes are denoted by Ha and Hf.
  • the vibration path amplitude Af is assumed twice as large in the drawing as the vibration path amplitude Aa.
  • n 2
  • the courses of vibration path amplitudes (ordinate A) and excitation powers (ordinate P) in the vicinity of the main natural frequency fn of the vibration systems are schematically represented over the excitation frequency fe of the excitation systems when using the dual mass vibrator 9 with a harmonic vibration and with a shock vibration.
  • the upper curves show the oscillation path amplitudes Vs and Vd for a single and a dual mass oscillator in the event that the same maximum oscillation path amplitudes Amax are achieved at the main natural frequency fn with comparable damping characteristics (corresponding to comparable damping outputs D or compression outputs).
  • the lower curves represent the associated excitation powers Ps and Pd for one and two mass oscillators, with Ps and Pd having a minimum value at the main natural frequency fn.
  • the curves show that with a comparable converted excitation power Pe, a larger frequency range ⁇ ⁇ fd compared to the frequency range ⁇ ⁇ fs for the vibration table of a single-mass oscillator is permissible for the oscillation table of a dual-mass oscillator when the same oscillation path amplitudes Ao are generated.
  • the curves also show that in the event that only the smaller frequency range ⁇ ⁇ fs is to be used when using a dual-mass oscillator, the excitation power can be limited to a smaller value Pe_d.
  • the course of the vibration path amplitudes Vd and Vs also shows that for excitation frequencies or compression frequencies lying outside the frequency ranges + ⁇ fs or ⁇ ⁇ fd, the excitation forces (Fe) assigned to an excitation power Pe can excite the vibration systems only to vibration amplitude A that corresponds to the value Ao.
  • the frequency ranges + ⁇ fs or + ⁇ fd represent the "usable resonance range" for a given vibration amplitude Ao.
  • the oscillation path amplitudes Ao cannot be reached immediately at the start of a vibration excitation.
  • a vertically operating dual-mass oscillator 9 which serves to carry out a harmonic vibration - in the operating state of the main vibration.
  • the two-mass oscillator 9 comprises a cantilever mass 37 with a piston 10 attached to it as the movable part of a hydraulic linear actuator 12, which in the exemplary embodiment shown is designed as a synchronous cylinder, a working mass ma, consisting of an oscillating table 13, a base plate 14, a mold 15, the Molding material for one or more molded bodies 16 and two clamping devices 18, with which the mold 15 and the base plate 14 can be firmly clamped against the vibrating table 13, as well as a spring system 24, which in this case consists of two leaf springs firmly joined at the outer ends and which for the transmission of spring forces in both vertical directions with the cantilever mass 37 on the one hand and with the working mass ma on the other hand is firmly connected.
  • the spring system 24 is set to "hard” and decisively determines the main natural frequency of the vertically operating two-mass oscillator 9.
  • the working mass ma or the oscillating table 13 is supported against a foundation 5 via a support spring system 22 which is preferably set softly in relation to the spring system 24.
  • a pressing plate 19 is arranged, which can be moved in the vertical direction by means of a hydraulic pressing device 6 and can be subjected to a preselectable pressing pressure.
  • the pressing device 6 consists of a plunger 21, a cylinder body 20 and a control, not shown in the drawing, for loading the Cylinder working spaces.
  • Base plate 14, mold 15 and press plate 19 form a molding device 8.
  • the servo Directional control valve 30 is able to alternately connect the two working spaces of the actuator cylinder 28 to a fluid pressure source 31 with adjustable pressure and a (pressure-less) tank 32.
  • a fluid pressure source 31 with adjustable pressure and a (pressure-less) tank 32.
  • an electrically operated linear actuator as described in FIG. 3, can also be used as the linear actuator 12.
  • the excitation forces are preferably generated with periodic force development profiles that are not sinusoidal, but rather pulse-like.
  • the compression forces are introduced into the molded body 16 with an essentially constant course, so that the compression process generated can also be referred to as harmonic vibration in this case.
  • FIG. 2 shows with the main components of the spring device 26, the press plate 19, the molded body 16, the vibrating table 13 with all the components attached to it, including the support spring system 22, the spring system 24, the cantilever mass 37 with all the components attached to it and with the linear actuator 12 "Vibrating system of the second type" 38, which is used for the main vibration.
  • the spring device 26 or a part thereof could also be supported directly against the vibrating table 13.
  • a somewhat modified "vibration system of the first type" 36 can be in action, which consists of the "Vibration system of the second type” 38 results from the fact that the pressure plate 19 does not rest on the molded body 16 here.
  • the working mass ma and the free-oscillating mass 37 oscillate essentially in phase synchronization and in opposite directions, as shown in FIG. 1, in cycles of the excitation frequency fe, which is close to the main natural frequency of the vertically operating dual-mass oscillator 9 or with the Main natural frequency is specified accordingly.
  • the preferably "soft" adjusted support spring system 22 has only a slight influence on the formation of the main natural frequency of the dual-mass oscillator 9.
  • the vibration path amplitude of the working mass ma which is to be predefined for the vibration of the vibration system of the first type (and second type) at a predetermined vibration frequency is preferably entered into the vibration system by a corresponding regulation of the linear actuator 12 Excitation energy or Excitation power set and maintained. For the process of regulating the target vibration path amplitude, constant measurement of the actual vibration path amplitude is required.
  • the corresponding signal is obtained by a displacement sensor 33 attached to the slide 17, which e.g. can detect the displacement of a corner of the vibrating table 13.
  • the control of the vibration path amplitude is carried out via a controller 52 with the assistance of an appropriate algorithm for the control of the servo-directional valve 30 and for the control of the pressure in the pressure source 31 such that the necessary excitation energy for the linear actuator 12 is determined and implemented for each half-period of vibration ,
  • the two-mass system which cooperates with the main spring system 22 and with the spring device 26 and with the mass of the pressure plate 19 (and the components connected to it) forms a vibration system of the second type which, under the influence of the excitation forces, reacts somewhat differently with respect to the vibration behavior than the vibration system of the first type. This also affects the main natural frequency fn2 of the entire oscillation system of the second type, which, however, is also dominated in this case by the main natural frequency fn of the dual-mass oscillator 9.
  • the two-mass oscillator 9 comprises the working mass ma of the oscillating table 13, which is designed as a shock-oscillating table, the cantilever mass 37 with the linear actuator part 47 attached to it, and the spring system 24.
  • baffle strips 46 are attached to the frame, which are provided with recesses 43, through which bumper strips 41 attached to the upper side of the vibrating table 13 reach and, when an oscillating movement of the vibrating table 13 occurs, abut against the underside of the base plate 14 after overcoming an air gap 44.
  • the base plate 14 rests on the impact strips 46, provided that it does not perform an upward movement caused by the impact and thereby lifts off the impact strips 46.
  • an electrically operated linear actuator 12 is provided. It consists of the "movable linear actuator part” 47 attached to the cantilever mass 37 and of a linear actuator part 48 which is firmly connected to the foundation 5.
  • a displacement sensor 42 is attached to the frame 17, with the aid of which the oscillation displacement amplitude of the oscillating table 13 can be continuously determined.
  • the signal of the oscillation path amplitude which in this case may be the controlled variable, is fed to the controller 52, by means of which, using the controller 50, the oscillation path amplitude according to a predetermined value and at a predetermined value Excitation frequency is regulated.
  • other physical quantities derived from the oscillating movement of the oscillating table 13 in this case the “shock oscillating table” can also be used as control variables.
  • Linear electric motors operated with alternating current are preferably provided as electric linear actuators 12.
  • a special control method is preferably used for the electric linear actuators 12, by means of which the linear actuators 12 are supplied with (or withdrawn) exactly the amount of energy or power required to maintain the controlled variable every half or full period.
  • the regulation of a parameter of the oscillating movement of the oscillating table 13 can also be brought about in that, with a constant supply of excitation power by an excitation actuator, an additional damping actuator can be provided, the damping power of which is regulated.
  • the mode of operation of the device in the case of the pre-vibration and the main vibration is as follows: Periodic excitation forces with a predetermined excitation frequency fe are generated by a corresponding control of the electric linear actuator 12 and are conducted into the free-swinging mass 37 and this is carried out with the excitation frequency Execute executed swinging movements, which is indicated by the double arrow 34.
  • the spring deformation forces transmitted via the spring system 24 are transmitted to the working mass ma and force it to carry out its own oscillating movements, which is symbolized by the double arrow 40. Due to the physical conditions of the dual-mass oscillator 9, the working mass ma and the free-oscillating mass 37 oscillate essentially phase-synchronously and in opposite directions, as shown in FIG.
  • the preferred "soft" Support spring system 22 has hardly any influence on the formation of the main natural frequency of the dual mass oscillator 9.
  • the compression of the molding material takes place under the influence of the impacts introduced into the base plate 14 by the bumper strips 41 and by the impacts generated when the base plate 14 falls back onto the impact strips 46, as well as by the pressing pressure.
  • the support spring system 22 is preferably designed as a rubber buffer and the cantilever masses 37 can, when the excitation forces are introduced from the exciter actuator, directly into the cantilever mass 37 in an extreme case from a proportionate spring mass of the spring system 24 and that attached part of the exciter actuator.
  • the mold 15 can be firmly clamped together with the base plate 14 against a further base which is synchronously oscillating in the horizontal direction, which base e.g. the vibrating table 13 shown in FIG. 2 can be used to carry out the so-called harmonic vibration.
  • the mold 15 together with the molded body 14 and the base or the oscillating table 13 represent the essential part of the working mass ma of a horizontal dual-mass oscillator.
  • This embodiment can also be referred to as "horizontal harmonic table vibration".
  • the same molded bodies 14 in the same mold 15 are additionally compressed either simultaneously or in succession with a vibration of the molding material in the vertical direction, or on the other hand, that in the same device using the same or a different mold 15 molded bodies 16 are compressed in a (also in terms of time) different production process with a vibration of the molding material in the vertical direction.
  • the same molded bodies 14 in the same mold 15 are additionally compressed either simultaneously or in succession with a vibration of the molding material in the vertical direction, or on the other hand, that in the same device using the same or a different mold 15 molded bodies 16 are compressed in a (also in terms of time) different production process with a vibration of the molding material in the vertical direction.
  • FIG. 4 there is also a question of a vibration of the molding material in the vertical direction: a vertical vibration of the shape with impacts of the molding against the “pallet table”, as described in EP 1 118 439 A1, and a vertical impact compression with a shock-vibration table that bumps under the base plate, whereby in both cases any excitation systems including the dual-mass oscillation excitation principle described here can be used.
  • the device shown in FIG. 4 is used to generate horizontal vibratory movements on a mold 15 with molded body 16 using a horizontally operating dual-mass oscillator 9 in the above-mentioned embodiment. form of the "horizontal harmonic table vibration".
  • the left part of the arrangement shown essentially comprises functional groups, which are already shown in FIG. 2.
  • the working mass ma of the horizontally operating dual-mass oscillator 9 essentially comprises the oscillating table 13, which is supported by spring elements 56 against the foundation 5 or a machine part connected to it, the base plate 14, the mold 15 with a molded body 16, the press plate 19, two clamping devices 18 and a coupling device 60.
  • the clamping devices 18, the clamping of the mold 15 against the base plate 14 can be carried out by a switching process and also released again, so that the molded body 14 (in a manner not shown) for the purpose of demolding from the mold 15 by a Relative movement of the press plate 19 and mold 15 can be removed downwards.
  • the (softly adjusted) spring elements 56 are designed here in such a way that, in addition to vertical deformation, they can also be subjected to horizontal deformation, in order to also enable a horizontal oscillating movement 53 of the oscillating table 13 or the working mass ma. Also for the purpose of enabling a horizontal oscillating movement, the pressure plate 19 is not driven directly by the plunger 21 of the pressing device 6, but rather via webs 54 which, when transmitting the pressing force when the working mass ma is vibrating, in the horizontal direction indicated by the double arrow 53 under little Resistance can be deformed elastically.
  • the pressing device 6 is supported (in a manner not shown) via the frame 17 against the foundation 5, similarly as shown in FIG. 2.
  • the vibrating table 13 can also be offset in a different manner or in parallel with the horizontal vibration in order to produce a compression effect in different ways.
  • the working mass ma of the vibrating table 13 is at the same time the working mass of a vertically working two-mass oscillator, which is not fully illustrated in the drawing and which can excite the working mass ma in the vertical direction, symbolized by the double arrow 59.
  • a vertically working two-mass oscillator which is not fully illustrated in the drawing and which can excite the working mass ma in the vertical direction, symbolized by the double arrow 59.
  • the complete vertical two-mass Schwingers assume that it is constructed very similarly and is also operated, as described in Fig. 2.
  • the double arrow 58 indicates the transmission of the vertical excitation forces to the working mass ma, it being assumed with regard to these excitation forces that they are transmitted directly by a spring attached to the oscillating table 13, as is the case with the spring system 24 in FIG. 2 for the harmonic Vibration is shown.
  • the double arrow 58 could, however, also be representative of a vertical shock vibration, in which the bumper strips of another (not shown) shock-vibration table butt against the base plate 14 from below through recesses made in the vibration table 13, as shown in FIG. 3.
  • the shock vibration table could be excited as shown in FIG. 3 or also according to WO 02/38346 A1.
  • the free-swinging mass mf is essentially embodied in FIG.
  • the horizontal oscillating movement 53 can be detected by a sensor 68, which is fastened to a holding element 65, which in turn is firmly connected to the foundation 5.
  • the horizontal vibration path 53 or one of its time derivatives can alternatively also be implemented by a e.g. sensor 74 housed in the vibrating table 13 can be detected, this sensor e.g. is an acceleration sensor.
  • the second linear actuator part 47 is supported at its right end in the vertical direction by a flexible and resilient support body 66 and connected at its left end by means of two rubber-elastic spring elements 72 to the coupling device 60 in the following way:
  • the working mass ma is not noticeably deformed in the horizontal direction by the rubber-elastic spring elements, so that the second linear actuator part 47 can oscillate in the same direction as the oscillating table 13 in the horizontal direction, this common horizontal oscillating movement being indicated by the double arrow 53.
  • the horizontally operating dual-mass oscillator 9 should (like the vertically operating dual-mass oscillator also) preferably operate as a resonant dual-mass oscillator, the excitation frequency or the oscillation frequency being located near or at the location of the main natural frequency of the dual-mass oscillator 9.
  • the oscillation path amplitude or a physical quantity of the working mass ma or the free oscillating mass mf derived therefrom should be controllable according to predetermined values by means of a control loop, in which the information obtained by the sensor 68 or 74 is also included.
  • the horizontally operating dual mass oscillator 9 can be used in the direction of the double arrow 59 in the case of a pre-vibration and / or the main vibration alone or together with a vertically operating vibration exciter for the vibration excitation of the working mass ma. With simultaneous excitation of the working mass ma in the vertical and horizontal directions, excitation of both vibration exciters with the same frequency is recommended. It is advantageous to carry out the oscillation profiles of both oscillation movements with a phase angle difference with a predetermined constant value, the most effective amount for the phase angle difference being best determined by experiments.
  • the transmission of the excitation force developed by the linear actuator 12 to the working mass ma can also take place directly on the mold 15 or on a component connected to it via a coupling device, whereby a "harmonic horizontal form vibration" is realized.
  • the coupling device can be releasably connected to the mold 15 in this case.
  • a horizontal dual-mass oscillator 9 can also act on opposite sides of the vibrating table 13, these two being motion-synchronized, i.e. work in the same direction.
  • the use of a horizontally working dual mass oscillator 9 for the horizontal compression vibration is, among other things.
  • the following amounts for ⁇ u in% result: 25.7 / 14.3 / 9.1 / 6.1 / 4.1.
  • the dash-dotted lines used in Fig. 2 to 4 indicate fasteners for the fixed connection of different components.
  • the dual mass vibrator 9 when using the dual mass vibrator 9, a large part of the vibrating forces of the working mass (vibrating table) to be transmitted to the frame and / or the foundation can be compensated for by the inertial forces of the cantilever mass, which is essentially synchronous in phase and in opposite directions. This means improved vibration protection of the other functional assemblies and the foundation connected to the frame.
  • the main natural frequency fn of the entire oscillation system of the compression device is significantly determined (in the case of shock vibration even more than in the case of harmonic vibration) by the main natural frequency of the dual-mass oscillator 9.
  • the deviation ⁇ ⁇ f can be caused by a product-dependent fluctuation in the working mass ma or by process-related oscillation with and without a ram (with harmonic vibration) or by the need to have to travel through a frequency range during the compression process.
  • the excitation power increases exponentially with the amount of the deviation ⁇ ⁇ f (see also FIG. 1c).
  • the resultant improvement means, with comparable deviations ⁇ ⁇ f or ⁇ ⁇ m, either a reduction in the additional expenditure of excitation power or, with comparable additional expenditure in excitation power, a permissible increase in the deviations + ⁇ f or ⁇ ⁇ m.
  • the ratio of the masses mf to ma can be designed within certain limits with a simultaneous change in the spring constant of the spring system 24 in order to achieve a specific main natural frequency of the two-mass oscillator 9 (see also FIG. 1a).
  • the vibration path amplitudes Aa of mass ma and Af of mass mf also depend on the ratio mf to ma.
  • control variables which can be detected by a sensor and are regulated according to predetermined values using the sensor signal by the controller part of the controller of the excitation system. It is also possible to provide a predeterminable limit amount for the oscillation path amplitude of the working mass ma or the free oscillating mass mf (Aa or Af in FIG.
  • the linear actuators are designed as electrical linear actuators
  • a special control method can be used, by means of which the electrical linear actuators are subjected to a control algorithm, determined beforehand by a control algorithm, in each half or full period, in order to maintain the predetermined amount of the controlled variable required, certain amount of energy or power is supplied.
  • the excitation frequencies can be specified as constant values or as a frequency range to be traversed ( ⁇ f in FIG. 1c).
  • the pressing device can be controlled by an assigned control part or regulated to generate a movement of the pressing plate and a predeterminable pressing pressure, wherein the pressing pressure can also be specified as a process-dependent or time-dependent variable.
  • the excitation actuator is selected from the group comprising an electrical, hydraulic, pneumatic actuator or an unbalance exciter, wherein the excitation actuator can be a linear actuator which can be designed as a linear motor (for example as a three-phase AC linear motor).
  • the unbalance exciter is advantageously adjustable during its rotation.
  • the spring force of the spring device 26 can also be generated by the magnetic field in the air gap of an electric motor, by means of which electric motor the prestress of the press plate in the direction of the vibrating table is preferably also generated at the same time.
  • the electric motor can be an electric linear motor, as is provided in FIG. 3 as a linear actuator 12 and Movable "second linear actuator part" (as it is denoted by 47 in FIG. 3) can generate the prestressing of the press plate with a predeterminable amount.

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  • Ceramic Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Abstract

L'invention concerne un dispositif pour compresser des matières à mouler en grains, dans un moule (15), de manière à obtenir un corps moulé (16), comprenant un système excitateur (7), grâce auquel la matière à mouler peut être comprimée par des ondulations contraintes, un oscillateur à deux masses (9) étant formé par une masse de travail et par une masse libre d'osciller (37), qui sont couplées par un système de ressort (24) et qui oscillent en phase et de manière opposée. La masse de travail comprend la masse d'une table d'ondulation (13) pour le moule et/ou la masse du moule (15) et la matière à mouler contenue dans le moule. Les masses et le système de ressort (24) de l'oscillateur à deux masses (9) sont mises au point, de manière à ce que la fréquence de résonance principale de l'oscillateur (9) soit proche d'une fréquence de serrage prédéterminée. Le dispositif comprend également un dispositif de compression (6) comprenant une plaque de compression (19) agissant sur la matière à mouler se trouvant dans le moule (15), ainsi qu'un dispositif de commande (S) pour le système d'excitation (7), à travers lequel la puissance d'excitation peut être modifiée par l'intermédiaire d'une fréquence de serrage prédéterminée.
PCT/EP2004/014054 2003-12-14 2004-12-10 Dispositif pour serrer des matieres a mouler se presentant sous forme de grains WO2005056279A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10358808.6 2003-12-14
DE10358808 2003-12-14
DE102004048240.3 2004-10-04
DE102004048240 2004-10-04

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005036797A1 (de) * 2005-08-02 2007-02-08 GEDIB Ingenieurbüro und Innovationsberatung GmbH Federsystem zur Erzeugung von Federkräften in zwei entgegengesetzten Richtungen
CN102744766A (zh) * 2012-07-16 2012-10-24 中钢集团洛阳耐火材料研究院有限公司 一种中部带滑块的振动成型机的模头机构及其操作方法
CN103372992A (zh) * 2012-04-17 2013-10-30 三菱综合材料技术株式会社 粉末成形品的制造方法以及粉末成形装置
RU2509646C1 (ru) * 2012-07-05 2014-03-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Российский университет дружбы народов" (РУДН) Вибрационная площадка
WO2016207578A1 (fr) * 2015-06-26 2016-12-29 Centre D'etudes Et De Recherches De L'industrie Du Béton Dispositif de controle en temps reel du fonctionnement d'une presse vibrante produisant des produits en beton a demoulage immediat et installation comprenant un tel dispositif
WO2018152958A1 (fr) * 2017-02-24 2018-08-30 南通市恒达机械制造有限公司 Machine de formation de briques efficace orientée par lots
RU2712460C1 (ru) * 2019-03-21 2020-01-29 Акционерное общество "Научно-производственное предприятие "Алмаз" (АО "НПП "Алмаз") Устройство для виброуплотнения заливки катодно-подогревательных узлов
CN112847738A (zh) * 2021-01-08 2021-05-28 张胜 一种保温型蒸压加气混凝土砌块浇筑成型方法

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DE102008023436A1 (de) 2008-05-14 2009-11-19 Hess Maschinenfabrik Gmbh & Co. Kg Vorrichtung zum Herstellen von Betonsteinen
CN110406123B (zh) * 2019-07-08 2021-05-18 上海赫峰建材科技有限公司 人造石板材的振动压力机设备及使用方法

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DE2950831A1 (de) * 1979-12-18 1981-06-25 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Verfahren zur einstellung, aenderung, insbesondere erhoehung der federrate von blattfederpaketen von elektromagnetischen zweimassen-vibrationsantrieben
EP0079172A2 (fr) * 1981-11-10 1983-05-18 Oy Partek Ab Procédé pour le moulage d'objets à partir d'un mélange à haute viscosité, et un moule pour l'exécution du procédé
GB2134426A (en) * 1983-02-02 1984-08-15 Gen Kinematics Corp A vibratory ram compaction mold forming machine for a foundry
EP0326870A1 (fr) * 1988-02-04 1989-08-09 Foundry Design Corp. (Europe) Procédé et dispositif de compactage de sable de fonderie
DE4434687A1 (de) * 1993-09-29 1995-03-30 Hubert Bald Verfahren zur Steuerung oder Regelung eines Vibrations-Verdichtungssystems zum Verdichten und Formen von Formmassen in Formkästen und Verdichtungssystem zur Anwendung des Verfahrens
US5606231A (en) * 1993-12-04 1997-02-25 Netter Gmbh Vibrating table for masses to be compacted and a vibratory method of compaction for the compaction of concrete
WO2001047698A1 (fr) * 1999-12-24 2001-07-05 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses
WO2002038346A1 (fr) * 2000-11-11 2002-05-16 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif de compactage pour compacter des corps moules en materiaux granuleux et son procede d'utilisation
WO2002038365A1 (fr) * 2000-11-11 2002-05-16 GEDIB Ingenieurbüro und Innovationsberatung GmbH Procede et dispositif de compression de matieres granuleuses
DE10154897A1 (de) * 2001-11-05 2003-05-15 Iff Weimar Anordnung zur Formgebung und Verdichtung von Gemengen
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GB463793A (en) * 1935-08-26 1937-03-30 Alfred Joseph Newport Improvements in and relating to methods of and means for effecting vibration and to apparatus in which vibration is effected
DE2950831A1 (de) * 1979-12-18 1981-06-25 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Verfahren zur einstellung, aenderung, insbesondere erhoehung der federrate von blattfederpaketen von elektromagnetischen zweimassen-vibrationsantrieben
EP0079172A2 (fr) * 1981-11-10 1983-05-18 Oy Partek Ab Procédé pour le moulage d'objets à partir d'un mélange à haute viscosité, et un moule pour l'exécution du procédé
GB2134426A (en) * 1983-02-02 1984-08-15 Gen Kinematics Corp A vibratory ram compaction mold forming machine for a foundry
EP0326870A1 (fr) * 1988-02-04 1989-08-09 Foundry Design Corp. (Europe) Procédé et dispositif de compactage de sable de fonderie
DE4434687A1 (de) * 1993-09-29 1995-03-30 Hubert Bald Verfahren zur Steuerung oder Regelung eines Vibrations-Verdichtungssystems zum Verdichten und Formen von Formmassen in Formkästen und Verdichtungssystem zur Anwendung des Verfahrens
US5606231A (en) * 1993-12-04 1997-02-25 Netter Gmbh Vibrating table for masses to be compacted and a vibratory method of compaction for the compaction of concrete
WO2001047698A1 (fr) * 1999-12-24 2001-07-05 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses
US20030113397A1 (en) * 2000-08-10 2003-06-19 Hubert Bald Compressing device for performing compression operations on shaped bodies made of grainy materials
WO2002038346A1 (fr) * 2000-11-11 2002-05-16 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif de compactage pour compacter des corps moules en materiaux granuleux et son procede d'utilisation
WO2002038365A1 (fr) * 2000-11-11 2002-05-16 GEDIB Ingenieurbüro und Innovationsberatung GmbH Procede et dispositif de compression de matieres granuleuses
DE10154897A1 (de) * 2001-11-05 2003-05-15 Iff Weimar Anordnung zur Formgebung und Verdichtung von Gemengen

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005036797A1 (de) * 2005-08-02 2007-02-08 GEDIB Ingenieurbüro und Innovationsberatung GmbH Federsystem zur Erzeugung von Federkräften in zwei entgegengesetzten Richtungen
CN103372992A (zh) * 2012-04-17 2013-10-30 三菱综合材料技术株式会社 粉末成形品的制造方法以及粉末成形装置
RU2509646C1 (ru) * 2012-07-05 2014-03-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Российский университет дружбы народов" (РУДН) Вибрационная площадка
CN102744766A (zh) * 2012-07-16 2012-10-24 中钢集团洛阳耐火材料研究院有限公司 一种中部带滑块的振动成型机的模头机构及其操作方法
CN102744766B (zh) * 2012-07-16 2014-07-30 中钢集团洛阳耐火材料研究院有限公司 一种中部带滑块的振动成型机的模头机构及其操作方法
WO2016207578A1 (fr) * 2015-06-26 2016-12-29 Centre D'etudes Et De Recherches De L'industrie Du Béton Dispositif de controle en temps reel du fonctionnement d'une presse vibrante produisant des produits en beton a demoulage immediat et installation comprenant un tel dispositif
FR3037844A1 (fr) * 2015-06-26 2016-12-30 Centre D'etudes Et De Rech De L'industrie Du Beton Dispositif de controle en temps reel du fonctionnement d'une presse vibrante produisant des produits en beton a demoulage immediat et installation comprenant un tel dispositif.
WO2018152958A1 (fr) * 2017-02-24 2018-08-30 南通市恒达机械制造有限公司 Machine de formation de briques efficace orientée par lots
RU2712460C1 (ru) * 2019-03-21 2020-01-29 Акционерное общество "Научно-производственное предприятие "Алмаз" (АО "НПП "Алмаз") Устройство для виброуплотнения заливки катодно-подогревательных узлов
CN112847738A (zh) * 2021-01-08 2021-05-28 张胜 一种保温型蒸压加气混凝土砌块浇筑成型方法

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