WO2001047698A1 - Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses - Google Patents

Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses Download PDF

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Publication number
WO2001047698A1
WO2001047698A1 PCT/DE2000/004632 DE0004632W WO0147698A1 WO 2001047698 A1 WO2001047698 A1 WO 2001047698A1 DE 0004632 W DE0004632 W DE 0004632W WO 0147698 A1 WO0147698 A1 WO 0147698A1
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WO
WIPO (PCT)
Prior art keywords
spring
excitation
forces
mass
compression
Prior art date
Application number
PCT/DE2000/004632
Other languages
German (de)
English (en)
Inventor
Hubert Bald
Original Assignee
GEDIB Ingenieurbüro und Innovationsberatung 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
Priority claimed from DE19962887A external-priority patent/DE19962887A1/de
Priority claimed from DE10039028A external-priority patent/DE10039028A1/de
Application filed by GEDIB Ingenieurbüro und Innovationsberatung GmbH filed Critical GEDIB Ingenieurbüro und Innovationsberatung GmbH
Priority to EP00990584A priority Critical patent/EP1242234B1/fr
Priority to CA002396499A priority patent/CA2396499A1/fr
Priority to AT00990584T priority patent/ATE251544T1/de
Priority to DK00990584T priority patent/DK1242234T3/da
Priority to DE50004031T priority patent/DE50004031D1/de
Publication of WO2001047698A1 publication Critical patent/WO2001047698A1/fr

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Classifications

    • 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
    • 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
    • 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

Definitions

  • Compression device for carrying out compression processes on molded bodies made of conforming substances
  • the invention relates to a compression device operated with vibration vibrations for molding and compacting molded materials in mold recesses from molded boxes to molded bodies, the molded bodies having an upper side and a lower side, via which the compressive forces are introduced.
  • the molding material is located in the mold recesses before the compression process, initially as a volume of granular constituents loosely adhering to one another, which are formed into solid molded bodies only during the compression process by the action of compression forces on the top and bottom.
  • the volume mass can e.g. consist of moist concrete mortar, in foundry molding machines made of molding sand and in sintered molding machines made of metal particles or other sintered particles.
  • the compression device can also be used to further compress preformed sintered part shaped bodies.
  • the invention relates particularly to such vibration compaction devices which operate comparatively quietly and with low energy consumption for the compaction.
  • the low-noise mode of operation requires, on the one hand, that the compression takes place by using essentially harmonic (sinusoidal) vibration forces and, on the other hand, that the molding box has no noticeable inherent movements relative to the other components involved in the vibration.
  • the molding box must be able to be clamped against such a machine element that participates in the vibration vibrations.
  • Such a machine element is, for example, the swing table located under the molding box.
  • the requirement for compression with low energy consumption is met in that the mass-spring system involved can also oscillate in or at least in the vicinity of the resonance frequency f 0 of this system.
  • the resonance frequency mode of operation leads to a very effective compression because of the so-called resonance effect due to the very high accelerations that can be achieved if it is ensured that the molded body is also subjected to the high values for the vibration acceleration derived from the resonance mode.
  • One side, e.g. the top of the molded body 226 is acted upon by a press plate 250, via which press plate the molded body has a special “average pressing force”, hereinafter also referred to simply as pressing force, even during the pressing
  • press plate is able to absorb the vibrational forces introduced from the other side (e.g. underside), which press plate is also able to carry out a displacement movement relative to the other side of the molded body, for the purpose of its tracking while reducing the compression height during the compression process and possibly also for
  • the other side e.g. the underside of the molded body 226 is also acted upon by a base plate 25 294, in addition to the pressing force which can be applied by the pressing plate, with vibrating forces which are generated and initiated by a movement generation system 240.
  • the base plate 294 in turn is supported against the vibrating table 211 of the vibrating mass system.
  • the motion generation system 240 is formed by a vibration
  • the vibrating mass system 207 is supported via springs 217 against the frame 204 (or against the floor on which the frame is loaded by gravity).
  • the oscillating mass system comprises the masses of several components that oscillate, including the oscillating table 211, the base plate 294, the molding box 213, the molding (s) 226 and the components of the clamping device 298 for the molding box that are intended to resonate.
  • the drive device 215 is used to generate excitation forces with a predeterminable excitation frequency and takes over the transmission of the excitation energy, which is needed for starting and maintaining the vibrations of the mass-spring system, as well as for the transmission of the compression energy and that energy which is necessary to cover various friction loss energies.
  • the excitation to be transmitted is used to generate excitation forces with a predeterminable excitation frequency and takes over the transmission of the excitation energy, which is needed for starting and maintaining the vibrations of the mass-spring system, as well as for the transmission of the compression energy and that energy which is necessary to cover various friction loss energies.
  • the 20 34 679 A1 (the meaning of which will be discussed again later) consists in that the forces directed through the vibrating table 211 are supported in two different ways (to the frame).
  • the springs 217 transmit the (average) pressing force and the superimposed dynamic mass forces of the oscillating mass-spring system 207 + 217 and at the same time also serve as a memory for the temporary change.
  • At least some of the power transmission elements included in the power flow circuit can form an oscillatable mass-spring system which has at least one first resonance frequency f 0 , which resonance frequency 5 can be excited by the specific excitation frequency of the drive device.
  • the mass-spring system 207 + 217 with its resonance frequency f Q it is provided that the mass-spring system 207 + 217 with its resonance frequency f Q to be operated.
  • the molded body 226 itself is included in the resonating mass-spring system.
  • the compression of the molded body 226 should take place through the action of the impact acceleration from impacts between the base plate 294 and the underside of the molded body or between the front side 5 272 of the press plate 250 and the top of the molded body (see, for example, column 3, lines 1 to 21).
  • the molded body 226 executes free-flight movements (gap L) relative to the oscillating mass system 207 (see, for example, column 9, lines 40 to 52 or claim 1). It is therefore a "shaking compactor", so to speak.
  • the excitation force is generated by a directional vibrator 118 serving as an excitation actuator with two unbalanced bodies, a good efficiency in energy conversion in the actuator itself is obtained, but the problem arises that the excitation force cannot be switched on and off quickly enough , Since the oscillating mass system 207 must not be in motion during the process of replacing the finished molded body with the initially undensified loose molding material (for the next molded body to be compressed) within the molding box, the acceleration and braking that would then be required would then be ongoing of the directional vibrator mean an unused dead time in the manufacturing process and also an energy destruction.
  • EP 0 870 585 A1 describes a compression device in which the compression of a molded body takes place with simultaneous application of a pressing pressure and a vibration by means of sinusoidal vibration acceleration.
  • the pressing pressure can be controlled by a hydraulic pressing force device 6 and the vibration (the vibration) is carried out by a hydraulic-mechanical mass-spring system, which is formed by the vibrating table 1, the molding box 14, the molding body 17, the movable part 2 of the hydraulic exciter 3, and by the compressible hydraulic medium, which is located between the movable part 2 of the exciter and the drive means 7 (electromechanical control element).
  • the vibration during the compression can be carried out in such a way that the hydraulic-mechanical mass-spring system vibrates in the vicinity or exactly at its resonance frequency f 0 and thereby (due to the accelerations "a") generates mass forces which are generated by the hydraulic pressing force device 6 Press force are superimposed. It also follows that, in contrast to DE 44 34 679 A1, the pressing pressure (generated by the hydraulic pressing force device 6 and transmitted via the hydraulic cylinder 5, 6) is not a pressure interrupted between two oscillating movements of the hydraulic-mechanical mass-spring system, but a print with a constant component and with an alternating component superimposed on it.
  • a force flow circuit leading over the "frame to be assumed” is moreover to be assumed because the compressible hydraulic medium embodying the spring of the mass-spring system can only develop forces in one direction (only pressure forces).
  • the swinging back of the mass of the mass-spring system must therefore be effected because of the desired high oscillation frequency in addition to the gravity also involved by means of a force that is supported via the molded body (and via the hydraulic pressing force device 6) against a frame.
  • the volume of the medium is part of the hydraulic-mechanical mass-spring system to be vibrated with a resonance frequency f 0 , the compressible hydraulic medium being used as a spring (later also referred to as the main system spring).
  • excitation energy In order to bring about and maintain the vibrations of the hydraulic-mechanical mass-spring system, excitation energy must be supplied in portions in the cycle of the excitation frequency. The while maintaining the Energy to be supplied with vibrations covers the energy losses which are removed from the system by damping and friction, as well as by the energy requirement for the compression of the molded body. According to the most general ideas of the invention disclosed, the excitation energy is to be supplied exclusively in a hydraulic manner, in such a way that the excitation energy is released in hydraulic form directly to the relevant (hydraulically designed) spring element of the system.
  • the excitation energy is added in portions in that the energy portions are introduced into the oscillating hydraulic-mechanical mass-spring system by the "dynamic hydraulic volume flows" to be generated discretely and in time with the excitation frequency (column 2, lines 38 to 40).
  • the energy coupling to be carried out in portions can logically only take place through the "dynamic hydraulic volume flows” associated with increasing pressure.
  • the “dynamic hydraulic volume flows” are to be produced with the assistance of an “electro-hydraulic control element” or a “servomechanism 7, 8” become.
  • This particular measure of energy coupling must therefore contain a certain meaning of the invention, which is not described, however.
  • the size of the alternating volumes required for the excitation and to be exchanged is also specified for a predetermined oscillation travel amplitude.
  • the exciter actuator must be operated with an unnecessarily large periodic alternating volume flow, which not only entails an increased energy loss as a disadvantage, but also the necessity for the servo device (for example a servo valve) to generate the alternating volumes accordingly large to dimension.
  • the periodic alternating volume flow would have to assume its greatest value just shortly before the transition from the first movement part to the second movement part, in order to drop to the value zero immediately thereafter.
  • This requirement cannot be met with real servo valves, especially at the high frequencies required (up to 100 Hz). Rather, the controlled transition from a maximum volumetric flow to a zero volumetric flow requires a certain time in which the control cross section of the servo valve is reduced, with a high pressure being built up on the servo valve due to the maximum oscillation speed that is throttled in the servo valve and one represents significant energy loss.
  • Fluid volume increases the exchange volume to be exchanged by the servo device, which can account for up to 50% of the otherwise only required exchange volume and what causes throttling losses if the excitation pressure is not fully relaxed when the upper oscillation path amplitude is reached when the subsequent volume change occurs when the downward movement begins.
  • a compression device for carrying out compression processes on molded bodies (108) made of conforming substances by introduction of essentially harmonic (sinusoidal) vibrational forces in the molded body to be compressed, with an oscillatable mass-spring system (136) with a main system spring (150, 970) with one or more natural frequencies and with an excitation device (144 ), by means of which the mass-spring system can be excited to forced vibrations, from which vibrations the vibrational forces are derived, the compression device further comprising:
  • a controller (190) for the control or regulation of the excitation device, and wherein the vibrating table is part of the vibrating mass of the mass-spring system, on which vibrating table the force of the main system spring and the exciter associated with the excitation device Actuator generated excitation force is acting.
  • the compression device defined above is further characterized in that the main system spring (150, 970) is designed as a hydraulic spring with a compressible fluid volume (140, 906) that separately acting organs for generating the excitation force (135, 980) and the spring force of the main system spring (150, 914) are provided, and that the force flow paths for the excitation force and the spring force are at least partially running separately.
  • the main system spring (150, 970) is designed as a hydraulic spring with a compressible fluid volume (140, 906) that separately acting organs for generating the excitation force (135, 980) and the spring force of the main system spring (150, 914) are provided, and that the force flow paths for the excitation force and the spring force are at least partially running separately.
  • the compression device defined above is further characterized in that the main system spring is designed as a single mechanical spring or as a resultant spring composed of several mechanical individual springs, that separate-acting organs for generating the excitation force (135, 980) and the spring force of the main system spring are provided, and that the force flow paths for the excitation force and the spring force of the main system spring are at least partially running separately.
  • a hydraulic alternating volume pump generator When using a hydraulic exciter actuator, a hydraulic alternating volume pump generator is provided in different variants in a special embodiment of the invention.
  • the "dynamic hydraulic volume flows" required to generate the excitation forces or the hydraulic alternating volumes to be exchanged are not generated by modulating or modulating the volume flow derived from a pressure source by an electro-hydraulic control element or a servo mechanism portioned, but that one uses a hydraulic alternating volume pump generator as part of the excitation device.
  • the alternating volume pump generators provided with a mechanical pump piston drive, the amounts of the alternating hydraulic volumes to be exchanged are essentially independent of the pressure prevailing in the hydraulic exciter actuator.
  • Output volumes ejected and reintroduced are generated by pump pistons (or, more generally speaking, by the displacement elements of displacement pumps known in principle), the pump pistons (or the displacement elements) being moved with predetermined strokes, preferably constant with mechanical means, whereby the strokes are mechanically derived from rotating (electric or hydraulic) drive motors.
  • the possibility of keeping the strokes constant during the excitation of the mass-spring system does not rule out that the strokes of the reciprocating pistons can also be changed in a predetermined manner, or that the alternating volumes can be changed by changing the useful stroke of the reciprocating pistons, as in an axial piston pump that can be regulated with regard to the displacer volume.
  • the alternating volumes introduced into the fluid volume to generate the excitation force can also be varied in that the stroke of the alternating volume pump generator is kept constant, but that only part of the alternating volume corresponding to a pump stroke is introduced into the fluid. Volume is introduced.
  • the pump movements of the pump pistons can be generated differently depending on the type of alternating volume pump generators, for which the following examples stand:
  • the strokes of the pump pistons can be generated by the oscillating movements of unbalance vibrators, preferably directional vibrators, the frequency of the strokes being changed by the speed of the drive motors and the path length of the strokes by the known means for changing the vibration amplitudes of the vibrators.
  • the strokes of the pump pistons can also be created and changed, as is the case in hydraulic pumps, e.g. happens in radial pumps or axial pumps. In the case of the pumps which are to be modified somewhat, all that needs to be done is to ensure that the ejected alternating volume can flow back into the cavity of the pump cylinder when a pump piston returns.
  • the size of the exchanged alternating volumes remains constant because the stroke paths of the alternating volume pump generator cannot be influenced retrospectively by the influence of the dynamic pressure of the exciter actuator (due to the dynamic inertial forces). Nevertheless, the dynamic pressure of the exciter actuator can have an effect on the alternating volume pump generator in such a way that the pump piston is driven on its way back by the dynamic pressure, as a result of which the average power output of the drive motor of the alternating volume pump generator is reduced. Because of precisely this retroactive effect, this type of coupling for the excitation energy under certain conditions also causes an automatic synchronization of the excitation frequency and the oscillation frequency of the mass-spring system or an automatic synchronization of the phase position of both types of oscillations.
  • the drive motor of the alternating volume pump generator only needs to be controlled or regulated with regard to its rotational frequency. Any deviation in the synchronism of the phase relationship between the rotational frequency and the oscillating frequency of the mass-spring system is compensated for by the elasticity of the electrical field, in particular the rotating field or the traveling field of an AC motor (slip), or its effect is mitigated.
  • a switchable member is provided between the outlet of the cylinder space of the alternating volume pump generator and the inlet of the space closing off the fluid volume of the hydraulic exciter actuator, with which at least the fluid volume exchange can be restricted or interrupted.
  • a bypass path should also be switchable with the same switching process, by means of which the alternating volumes can be diverted to another container.
  • FIG. 1 shows a compression device in a general embodiment, the part shown below the line AB in FIGS. 4 to 8 being shown in a different, special embodiment, so that the part of the compression device shown in FIG. 1 below the dividing line AB is replaced by the partial representations of Figures 4 to 8.
  • FIG. 2 illustrates a first variant
  • FIG. 3 shows a second variant of an alternating volume pump generator, which is identified in FIG. 1 as frame 160, which frame symbolizes a control part in FIGS. 1 and 9, which together with the exciter actuator entire excitation device forms.
  • FIG. 1 shows a compression device in a general embodiment, the part shown below the line AB in FIGS. 4 to 8 being shown in a different, special embodiment, so that the part of the compression device shown in FIG. 1 below the dividing line AB is replaced by the partial representations of Figures 4 to 8.
  • FIG. 2 illustrates a first variant
  • FIG. 3 shows a second variant of an alternating volume pump generator, which is identified in FIG. 1 as frame 160
  • FIG. 9 shows a further variant of a compression device, in which the hydraulic linear motor of the excitation actuator is arranged coaxially with respect to the hydraulic cylinder of the main system spring.
  • the reference numerals beginning with the number “1” represent the same organs or features as in FIG. 1.
  • FIG. 10 an enlarged scale in FIG 9 detail marked with Q is shown together with a connected hydraulic circuit.
  • 100 denotes the frame of the compaction device, which has to transmit forces of different types and which is supported against the floor 104 by springs 102 serving as vibration isolators.
  • the molded body 108 to be compressed is located in a molded box 106 open at the top and bottom, on the upper side of which the press plate 110 of the press device 112 rests.
  • the undersides of the molded box and the molded body lie on a base plate or sports plate 122, which in turn rests on the vibrating table 124.
  • Two clamping devices 126 with clamping elements 130 movable in the direction of the double arrow 132 for the purpose of clamping and releasing are provided in order to enable an exchange of the base plate and / or the molding box.
  • the molding box 106 and the base plate 122 are clamped against the vibrating table 124, so that they form a physical unit with the latter.
  • the hydraulic press device 112 consists of a cylinder 114, a piston 116 and a press drive device 118 which is connected to the pressure fluid of the cylinder via a hydraulic line 120 and to the central controller 190 via a line 192.
  • the pressing device supports the forces transmitted via the pressing plate 110 against the frame.
  • the press drive device 118 can also be designed in such a way that it is connected to a pressure source which keeps a predeterminable pressure constant in the case of differently delivered or absorbed volume flows.
  • the vibrating table 124 together with other components moving synchronously with it, which mainly include the molding box 106, the clamping device 126, the base plate 122, and the oscillating piston 134, belong to a vibrating mass system 136 which represents the mass of an oscillatable mass-spring system.
  • the dynamic mass forces generated when the vibrations of the mass-spring system are carried out are supported against the frame via the main system spring 150.
  • the main system spring of the mass-spring system simultaneously represents an energy converter and energy store, since it continuously converts the kinetic energy of the oscillating mass system 136 into spring energy (and vice versa).
  • the main system spring 150 is embodied by a pressure fluid volume 140 of a certain size V ⁇ , at least part of the pressure fluid volume being clamped between the oscillating piston 134 and the walls of the cylinder 138.
  • the dynamic mass forces are supported against the frame 100 via the cylinder 138.
  • the vibrating mass system 136 can be used to perform the
  • Vibration compression operation to be performed to generate vibratory movements 152 are forced.
  • the forces for carrying out the oscillating movements are generated by a movement generation system 142 (which in principle can be configured very differently).
  • the latter consists at least of the two components main system spring 150, which takes over the generation of the main forces and the excitation device 144 for supplying the drive energy for excitation and maintenance of the vibrations and for the compression work.
  • the excitation device itself comprises the excitation actuator (shown generally in FIG. 1 by a rectangle 135) for generating the excitation forces and the excitation control 160 for energy supply and energy control of the excitation actuator.
  • the excitation controller 160 is indicated schematically by a frame which represents different embodiments.
  • connection point 196 in the line 194 from the central control 190 to the excitation control 160 and the connection point 162 in the operative connection between the excitation control 160 and the excitation actuator 135 are intended to further clarify the interchangeability of the exciter control 160 function carrier.
  • the excitation actuator 135 is arranged such that it supports the excitation forces with a movable part against a component of the vibrating mass system 136, preferably against the vibrating table 124, and with a fixed part against the frame 100 (the movable part and the fixed part are shown in FIG Fig. 1 not shown). It can be seen that the force flow paths of the main system spring 150 and the exciter actuator 135 run at least partially separately, so that there can never be a direct coupling of the spring forces and the excitation forces as in the named prior art. It can also be seen that the excitation force is not supported against the compressible fluid volume 140 of the main system spring 150 when it is generated.
  • the partial representations of FIGS. 4 to 8 show that the function carriers main system spring and exciter actuator can be implemented using absolutely different means.
  • the excitation actuator 135 works in such a way that energy portions are supplied to it in time with the frequency specified by the excitation control 160, which is symbolically represented by the operative connection 164.
  • the exciter actuator is a hydraulic actuator, for example a hydraulic linear motor
  • alternating pump generators There are three different types of alternating pump generators, two of them will be explained with reference to Figures 2 and 3. (In the third variant, the exciter actuator is operated with an electric linear motor that works similarly to that described under FIG. 7).
  • the periodic excitation forces are at least approximately designed as harmonic excitation forces.
  • the easiest way to do this is to use alternating-volume pump generators with the inclusion of an unbalance vibrator or with the operation of a hydraulic displacement pump.
  • the mass-spring system can be excited within certain limits to harmonic vibrations with any frequencies and any vibration path amplitudes. This also applies to the case of the compression vibration to be carried out, the vibrations of the mass-spring system being influenced by the components of the pressing device 112 and by the molded body 108 itself, for example by its spring force.
  • the mass-spring system with its excitation device 144 is designed in such a way that it is well under the resonance frequency f 0 , but also in the resonance frequency f ⁇ or in the vicinity, even under the load of the press device with a predetermined pressing force passed over the molded body of f Q (above and below) can be operated.
  • the resonance mode is characterized, among other things, by the fact that very high accelerations of the vibrating table are achieved here, which are required especially with the compression provided here with harmonic vibratory forces, and at the same time relatively low excitation forces have to be generated in the resonance mode.
  • the molded body before it is compacted consists of a molded material made from loosely adhering granular components, such as moist concrete mortar. After compaction has been completed, the molded body is pushed out of the molding box and transported away in a manner known per se, and the empty molding box is again filled with undensified molding material in a known manner.
  • the pressing device 112 is also involved in the process of changing the mold box contents in a manner known per se, in that the piston 116 together with the pressing plate 110 is able to perform an upward and downward lifting movement.
  • the compression process begins with the pressing plate 110, which is moved downward by the pressing device, touching the top of the molding material. From this moment of the lifting movement of the press plate 110, the press plate moves further downward while exerting a predeterminable pressing pressure on the resulting molded body as the compression increases. At the beginning of the compression caused by the pressure plate 110 or to any other Ren time beginning or ending, the compression is carried out by a joint action of pressure and vibration on the molded body.
  • a particularly effective compression can be brought about if the vibration is carried out at 5 the resonance frequency or in the vicinity of the resonance frequency f 0 . For this reason, a process sequence is provided during the compression process, during which the resonance frequency f 0 is approximated or reached or passed at least once. Since often different components of the molding compound with their different behaviors during compression different fit them-
  • 20 140 is formed by several sub-volumes that can be separated from one another by switchable check valves. If the desired change in the spring rate is required, the corresponding check valves then only have to be opened or closed. A continuous change in the spring rate can also be provided in that part of the pressure fluid volume 140 is formed by a cylinder whose cylinder space is formed by
  • a piston which is displaceable in the cylinder in a predetermined manner is changed.
  • the vibration must be switchable on and off, e.g. when changing the mold box content. It must be possible to switch the vibration on and off very quickly in the sense of high productivity of the entire production system. To meet this requirement, measures are provided which will be described later with the aid of further figures.
  • the bottom 104 could also be included for the transmission of the power flows, as is shown in FIG. 9.
  • the force flows especially the dynamic mass forces, are complete to flow through the frame 100 and the vibrations of the frame through springs
  • pistons 116 and 134 in FIG. 1 can be designed as double-acting pistons.
  • FIG. 2 shows an exciter control 200 with an alternating volume pump generator, including an unbalance vibrator 240, in a schematic form.
  • the entire exciter control can be connected to a compression device according to FIG. 1 at the connection points 162 and 196 which are also present there, the excitation control 200 being the exciter control symbolized in FIG. 1 by the frame 160 replaced.
  • Two unbalances 204 are forced by their drive motors 202 to rotate in opposite directions and thus set the base plate 208 of the common frame in a directional oscillation, which is indicated by the double arrow 206.
  • the base plate 208 is also softly supported in a manner not shown in the drawing by means of springs against the cylinder housing 214.
  • Two pump pistons 210 are fastened to the base plate 208 and work together with two cylinder spaces 216 of the cylinder housing 214.
  • the cylinder spaces are connected to one another by a connecting line 220 and are connected to the outside via a line 222 with the involvement of the device 226 at the connection point 162.
  • the oscillating movement of the pump pistons 210 forces the pressurized fluid volume 218, which is under a prestressing pressure, and with each downward stroke under increased pressure an exchange volume of a predetermined size via the connection point 162 to the pressurized fluid volume of the exciter actuator 135, which operates hydraulically in this case 1 and to record an exchange volume emitted by the pressure fluid volume of the exciter actuator with each upward stroke.
  • a very specific portion of excitation energy can thus be delivered to the mass-spring system of FIG. 1.
  • the drive motors 202 are acted upon by a control unit 230, with which, for example, the rotational frequency can be influenced in such a way that it corresponds to the resonance frequency f 0 of the compression device in FIG. 1.
  • the control device 230 is also connected to the central control 190 via the connection point 196.
  • the size of the exchange volume to be exchanged with the hydraulically operated exciter actuator 135 in FIG. 1 must be able to be varied for various reasons, and the possibility must also be included of completely preventing the volume exchange and thus the oscillating movement of the compression device. Different solutions are provided for this task according to the invention.
  • the vibration amplitude of the vibrator can be varied between the value zero and the maximum value using means known per se and not described further here.
  • r> 3 is an excitation controller 300 illustrated in schematic form a hydraulic pump as an alternating volume pumping generator.
  • the entire exciter control can be connected via two connection points 162 and 196 to a compression device according to FIG. 1 at the connection points 162 and 196 also present there, the exciter control 300 being the exciter symbolized by the frame 160 in FIG. Control replaced.
  • a circular cam disk 310 can be driven in rotation by a drive motor M about a shaft 304 rotatably mounted in the pump housing, which is symbolized by the arrow 308.
  • the axis of rotation of the cam is arranged around an eccentric section 306 outside the center of the cam circle.
  • the drive motor M is acted upon by a control device 330, with which, for example, the rotational frequency of the cam plate 310 can be influenced in such a way that it corresponds to the resonance frequency f ⁇ of the compression device in FIG. 1.
  • the control unit 330 is also connected to the central control 190 via the connection point 196.
  • two corresponding possibilities are provided in the exciter controller 300.
  • the stroke of the pump piston 324 can be changed by changing the eccentric section 306 (possible down to the value zero).
  • the other solution works similarly to that with respect to the solution described in FIG. 2, in which the fluid volume exchange between the pressure fluid volume 326 and the pressure fluid volume of the excitation actuator can be restricted or interrupted.
  • Device 340 has the same task as device 226 in FIG. 2.
  • FIG. 4 shows a variant of a compression device according to FIG. 1 with the vibrating table 124, in which variant the excitation actuator 480 for generating the excitation forces and the main system spring 470 are designed differently compared to a compression device according to FIG. 1 with a hydraulic excitation actuator are.
  • the main system spring 470 is represented by the individual springs of two equally large pressurized fluid volumes 478, each of which is enclosed between its own oscillating piston 474 and cylinder 476.
  • the exciter actuator 480 is formed by the actuator piston 482, which is fastened to the vibrating table 124 by means of the piston holder 484, by the actuator cylinder 486 and by the actuator pressure fluid volume 488, which is connected to the exciter by means of the operative connection 164.
  • Controller 160 is connected.
  • alternating-volume pump generators such as e.g. which can be used as described in FIGS. 2 and 3.
  • the excitation forces are transmitted in FIG. 4 in such a way that they are guided between the vibrating table 124 and the frame 100 in a special force flow path which is parallel to those leading over the individual springs (478) Power flow paths runs. Due to this measure, excitation forces and dynamic mass forces cannot be coupled in one and the same volume of pressurized fluid.
  • FIG. 5 shows a variant of a compression device according to FIG. 1 with the vibrating table 124, in which variant the excitation actuator 580 for generating the excitation forces and the main system spring 570 are configured differently from FIG. 1.
  • the main system spring 570 is embodied by two equally large pressurized fluid volumes 578, each of which is enclosed between its own oscillating piston 574 and cylinder 576.
  • the excitation actuator 580 is formed by a directional vibrator 584 whose amplitude is adjustable and which is fastened directly to the vibrating table 124 without a force-transmitting connection to the frame 100.
  • the control of the two drive motors 582 via which the speed can also be controlled, takes place via the active connection 164 through the excitation controller 160.
  • FIG. 6 shows a variant of a compression device according to FIG. 1 with the vibrating table 124, in which variant the excitation actuator 680 for generating the excitation forces and the main system spring 670 are configured differently from FIG. 1.
  • the main system spring 670 is embodied by two equally large pressurized fluid volumes 678, which are each enclosed between their own oscillating piston 674 and cylinder 676.
  • the exciter actuator 680 comprises a directional vibrator 681, which is softly supported against the frame 100 by springs 682.
  • the control of the two drive motors 683 via which the speed can also be controlled, takes place via the active connection 164 by the excitation controller 160.
  • the directional vibrator 681 does not have to be adjustable in terms of its oscillation amplitude and can remain in constant oscillation.
  • the activation and deactivation of the excitation forces generated by the directional vibrator on the vibrating table 124 and the control of the size of the excitation energy portions to be transmitted with each oscillating movement of the directional vibrator is carried out by means of a hydraulically operated coupling device 684 which is also associated with the excitation actuator with a hydraulic switching element 685, the latter being controlled by the central control 190 via the line 686.
  • the hydraulic coupling device 684 comprises a double-acting piston 687 which can be moved up and down in the cylinder space of the cylinder 688 by the oscillating movements of the directional vibrator to which it is attached.
  • alternating volumes which are parts of the pressurized fluid volumes of the two cylinder spaces 672 and 673 separated by the piston, are exchanged with the hydraulic switching element 685.
  • the hydraulic switching element 685 can be operated in different versions: In a first mode of operation, it creates a short-circuit path for the exchange volumes to be exchanged, so that practically no excitation forces are transmitted from the directional vibrator to the vibrating table during the upward and downward movement of the piston 687.
  • the hydraulic switching element 685 provides a (preferably continuously adjustable) narrowed short-circuit path with a predeterminable throttling effect.
  • throttling the volume flows of the exchangeable volumes to be exchanged, the transferable amplitudes of the oscillating movement of the directional vibrator and the transferable excitation forces or the transferable excitation energy portions are reduced in a predeterminable manner.
  • the short-circuit path is completely blocked, with the result that the oscillating movements or the excitation forces of the directional vibrator are transmitted to the oscillating table 124 with full amplitude or in maximum size. For the transmission of excitation forces on one own power flow path applies something similar, as described in the description of Figure 4.
  • FIG. 7 shows a variant of a compression device according to FIG. 1 with the vibrating table 124, in which the exciter actuator 780 for generating the excitation forces and the main system spring 770 are configured differently from FIG. 1.
  • the main system spring 770 is embodied by two equally large pressurized fluid volumes 778, each of which is enclosed between its own oscillating piston 774 and cylinder 776.
  • the excitation actuator 780 is an electric linear motor, consisting of 10 a movable part 782 and a stationary part 783.
  • the excitation forces are generated in an air gap 784 by alternating magnetic fields and are supported on the one hand against the vibrating table 124 and on the other hand against the frame 100.
  • the size of the excitation forces, the stroke amplitude of the movable part and the excitation frequency are determined by the excitation control 160, which is connected to the linear motor via the operative connection
  • FIG. 8 shows a variant of a compression device according to FIG. 1 with the vibrating table 124, in which variant the excitation actuator 880 for generating the excitation forces and the main system spring 870 are designed differently from FIG. 1.
  • the main system spring 870 is embodied by two equally large pressurized fluid volumes 878, each of which is enclosed between its own oscillating piston 874 and cylinder 876.
  • the excitation actuator 880 is a hydraulic linear motor, consisting of a movable part 882 designed as a piston and a stationary part 883 designed as a cylinder.
  • the excitation forces are generated in the pressure fluid volume 884 by the exchange of dynamic hydraulic alternating volumes via the active components - Connection 164 to the excitation controller 160.
  • the excitation controller 160 contains an electro-hydraulic servomechanism which, in accordance with the control information received from the central controller 190, dynamically generates hydraulic alternating volumes with predeterminable frequency and size and with predeterminable exciter energy portions ,
  • the excitation forces are supported on the one hand against the vibrating table 124 and on the other hand against the frame 100.
  • 9 shows a variant of a compression device which, like the variants according to FIGS. 4 and 8, works with a hydraulic spring and with a hydraulic exciter.
  • the construction of the entire compression device is similar to that of FIG. 1.
  • the reference numerals beginning with the number 1 therefore designate the same features with the functions assigned to them as in FIG. 1.
  • the features which are different in comparison to FIG 9 begin, are all arranged below the vibrating table 124.
  • the force flow of all the forces involved is via the cylinder part 902.
  • the cylinder part is firmly connected to the foundation 10 904.
  • the foundation can be viewed as part of the frame 100 and is also the carrier of the force flow paths of all the compression forces involved.
  • the cylinder part 902 contains cylinder spaces or fluid volumes for two different hydraulic 15 linear motors:
  • the compressible fluid volume 906 represents the energy-storing part of the main system spring 970 and, with its compression module, is decisive for the resonance frequency of the mass-spring system with the vibrating mass System 136, which also includes the 908 oscillating piston.
  • the fluid volume 906 together with the oscillating piston 908 forms the main system spring 970.
  • the actuator 0 fluid volume 914 forms together with the actuator piston 916 and the cylinder part 902 the hydraulic linear motor of the excitation actuator 980, with which linear motor the excitation forces are generated. with which the frequency and amplitude of the compression vibration are determined.
  • the oscillating piston is fixed to the oscillating table 124 and the actuator piston is fixedly connected to the oscillating piston.
  • the fluid volume 906 and the actuator fluid volume 914 could also be interchanged.
  • the exciter actuator 980 is connected to the exciter controller 160 by means of the operative connection 164.
  • the excitation control (instead of the symbolic frame 160 interchangeable between the connection points 162 and 196) can be designed as an alternating volume pump generator; however, it can also contain an electro-hydraulic servo mechanism, which is connected on the one hand to a pressure source (preferably with an essentially constant pressure) and, on the other hand, exchanges dynamic hydraulic alternating volumes with the frequency and size that can be specified and with predefinable excitation energy portions with the linear motor , 5
  • the oscillating table 124 or the oscillating piston should be held at an average altitude that can be predetermined with a variable or constant value, as is achieved by the dimension "Z" is symbolized.
  • the average altitude can be defined, for example, by the reference vibration position at which the vibration speed has its maximum value and the vibration acceleration has the value zero.
  • vibration travel amplitudes + A and -A can be defined, whereby the vibration travel amplitudes + A and -A can have remarkably different values depending on various parameters.
  • the fluid volume 906 should be compressed by approximately the amount -A with a negative oscillation path amplitude -A.
  • a compensation volume dispenser 920 is provided. It consists of a cylinder housing 922, a compensating piston 926, a compensating spring 928 and a compensating volume 924 and is connected to the fluid volume 906 via a line 930. While a compression amount> zero of the fluid volume prevails, the compensating piston 926 is pressed into a mechanically formed end position against the force of the compensating spring 928.
  • a compensating volume dispenser could also be replaced by a correspondingly controlled valve, which draws the volume flow during the upward stroke from a pressure source and returns the volume flow during the downward stroke into the pressure source itself or into another container.
  • a displacement measuring system is provided for the detection of the oscillating path of the vibrating table 124 or the oscillating piston 908, consisting of a first sensor part 910 and a second sensor part 912. The result of this path measurement is (in a manner not shown in the drawing) the central control 190 fed and processed there.
  • a hydraulic regulating volume dispenser 940 is provided in order to be able to keep the vibrating table 124 or the vibrating piston 908 in the predeterminable average altitude or reference path position despite leakage losses and other disturbing factors. This can lead a control volume flow into the fluid volume 5 906 via line 942 and, if necessary, also discharge it from it, in such a way that the predetermined average altitude is kept constant.
  • the control volume dispenser 940 in the selected example has a pressure source S, a check valve C and a valve V, through which valve the necessary metering of the control volume flow is carried out.
  • the valve V which is controlled by the central control 190 via the active line 944, is an actuator of a closed control loop of a level control device, with which the average altitude or vibration path reference position is continuously regulated to a predetermined value.
  • a compression device offers several advantages, namely that the main system spring 970 is not loaded with the excitation forces, or the actuator fluid volume is not loaded with the forces of the main system spring.
  • the power flow of all three forces involved is combined in the oscillating piston, but due to the separate generation of the excitation forces in a separate excitation actuator, there is no superimposition of excitation forces and spring forces derived from the dynamic mass forces in the excitation actuator.
  • the hydraulic linear motor of the excitation actuator and the spring cylinder of the main system spring are arranged concentrically in FIG. 9 and also centrally symmetrically to the oscillating table 124. Because of the possible symmetrical application of force by dynamic mass forces resulting from the spring function and excitation forces, there can be no jamming effect on the pistons involved and the compression acceleration acts symmetrically on the entire mold box 106, which is particularly important when the mold box is divided into many individual molds.
  • FIG. 10 shows the detail identified by the circle “Q” in FIG. 9 with a modification such that an annular groove 950 is provided in the inner cylinder of the cylinder part 902 and is filled with a fluid volume 952.
  • the fluid volume 952 can unite with the fluid volume 906 when the oscillating piston 908 is moved to a higher position.
  • an additional hydraulic circuit 954 is shown, the Line part 956 communicates with the fluid volume 952 via a fluid line 962.
  • FIG. 10 shows a different, purely mechanical-hydraulic variant of a level control device compared to FIG. 9, with which the average height position or vibration travel reference position of the vibration table 124 is adjusted to one by the position of the cylinder control edge 958 the ring groove predetermined value is regulated and in which the function of the compensation volume dispenser described in Fig. 9 is also realized.
  • the oscillating piston 908 has a piston control edge 960 on its underside, which separates the fluid volume 952 from the fluid volume 906 at the same height (as drawn) as the cylinder control edge 958.
  • the reference position of the oscillating table 124 is also defined with the height of the oscillating piston shown.
  • the cylinder control edge 958 represents a measure of the target position of the oscillation travel reference position.
  • PLV is a pressure limiting valve which, at a pressure> p L in the line part 956, a volume flow the way in opens the container T.
  • S2 represents a fluid source with a constant pressure ⁇ p L.
  • a check valve CV prevents fluid backflow from the line part 956 into the fluid source.
  • the function of the level control device is as follows: after the piston control edge 960 has passed the oscillation travel reference position during a downward oscillating movement of the oscillating piston 908, the compression of this fluid volume begins with a separated fluid volume 906 and the oscillating movement reaches its lower reversal point after Covering the route -A. As soon as the piston control edge 960 has again passed the oscillation travel reference position during the subsequent upward oscillating movement, a compensating volume flow begins to flow into the fluid volume 906 from the source S2 until the oscillating piston 908 after the distance + has been covered A has reached the upper reversal point.
  • the upward strokes can be of any size within a certain range, corresponding to the distance + A due to the energy portions supplied via the actuator piston.
  • this level control device could be carried out with a similar construction with a slightly different version:
  • the piston control edge (960) is not on the oscillating piston 908 and the cylinder control edge 958 is not attached to the inner cylinder associated with the oscillating piston 908. Rather, the piston control edge (960) is now realized on another piston and the cylinder control edge 958 on another inner cylinder belonging to the other piston, the cylinder control edge on the other cylinder also being realized by the lower plane surface of another ring groove (or through radial bores).
  • a different fluid volume (similar to 906 in FIG. 10) is also contained in the other inner cylinder as a spring medium, which adjoins the underside of the other piston.
  • Another hydraulic circuit constructed like circuit 954 in FIG.
  • the organs of the exciter actuator and the main system spring are arranged either above or below the oscillating table. Instead of a single molded body or casting mold model, several can be provided at the same time.
  • the relative position of the main system spring and exciter actuator can be interchanged, which e.g. for Fig. 9 would mean that 908 is the actuator piston and that 916 is the oscillating piston.
  • the dash-dot lines shown there, e.g. line 879 in FIG. 8 symbolizes a fixed connection between two components.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Press Drives And Press Lines (AREA)
  • On-Site Construction Work That Accompanies The Preparation And Application Of Concrete (AREA)
  • Processing Of Solid Wastes (AREA)

Abstract

L'invention concerne un dispositif de compression permettant d'effectuer des opérations de compression sur des corps moulés à base de matières granuleuses. A cet effet, lesdites matières granuleuses, par ex. du mortier au béton humide, sont moulées dans des cavités (106) de châssis de moulage, par vibrations et pression de compression, pour donner lieu à des corps moulés. L'invention vise à mettre au point un dispositif de compression fonctionnant avec un faible niveau sonore et une faible consommation d'énergie. Afin de parvenir à une compression à faible niveau sonore, il est prévu de fixer par serrage les châssis de moulage (106) sur la table vibrante (124) et de veiller à ce que le système masse-ressort oscillant qui induit les vibrations, présente un processus vibratoire harmonique. Une faible consommation d'énergie et une compression efficace sont possibles de par l'utilisation d'une fréquence d'oscillations se situant au moins en partie dans la gamme des fréquences du système masse-ressort. L'invention concerne en outre des améliorations, notamment en termes de conception de l'excitateur-actionneur et de sa configuration dans le flux des forces impliquées. Ce dispositif de compression s'utilise dans des machines pour produire des blocs en béton, des machines de moulage de fonderie et des machines de moulage de produits frittés.
PCT/DE2000/004632 1999-12-24 2000-12-27 Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses WO2001047698A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP00990584A EP1242234B1 (fr) 1999-12-24 2000-12-27 Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses
CA002396499A CA2396499A1 (fr) 1999-12-24 2000-12-27 Dispositif de compression pour effectuer des operations de compression sur des corps moules a base de matieres granuleuses
AT00990584T ATE251544T1 (de) 1999-12-24 2000-12-27 Verdichtungseinrichtung zur durchführung von verdichtungsvorgängen an formkörpern aus kornförmigen stoffen
DK00990584T DK1242234T3 (da) 1999-12-24 2000-12-27 Komprimeringsindretning til gennemførelse af en komprimeringsproces på formlegemer af granulære materialer
DE50004031T DE50004031D1 (de) 1999-12-24 2000-12-27 Verdichtungseinrichtung zur durchführung von verdichtungsvorgängen an formkörpern aus kornförmigen stoffen

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19962887.4 1999-12-24
DE19962887A DE19962887A1 (de) 1999-12-24 1999-12-24 Verfahren und Vorrichtung für ein Verdichtungssystem
DE10039028A DE10039028A1 (de) 2000-08-10 2000-08-10 Verfahren und Vorrichtung für ein Verdichtungssystem
DE10039028.5 2000-08-10

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WO2001047698A1 true WO2001047698A1 (fr) 2001-07-05

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EP (1) EP1242234B1 (fr)
AT (1) ATE251544T1 (fr)
CA (1) CA2396499A1 (fr)
DE (1) DE50004031D1 (fr)
DK (1) DK1242234T3 (fr)
ES (1) ES2208464T3 (fr)
WO (1) WO2001047698A1 (fr)

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WO2005056279A1 (fr) * 2003-12-14 2005-06-23 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif pour serrer des matieres a mouler se presentant sous forme de grains
WO2005056201A1 (fr) * 2003-12-14 2005-06-23 GEDIB Ingenieurbüro und Innovationsberatung GmbH Vibrateur de battage de pieux pour des articles battus
DE102008011272A1 (de) 2008-02-26 2009-08-27 Institut für Fertigteiltechnik und Fertigbau Weimar e.V. Betonsteinfertiger mit harmonischer Vibration durch Formerregung

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US7923739B2 (en) 2009-06-05 2011-04-12 Cree, Inc. Solid state lighting device
US8598602B2 (en) 2009-01-12 2013-12-03 Cree, Inc. Light emitting device packages with improved heat transfer
US9111778B2 (en) 2009-06-05 2015-08-18 Cree, Inc. Light emitting diode (LED) devices, systems, and methods
US8860043B2 (en) 2009-06-05 2014-10-14 Cree, Inc. Light emitting device packages, systems and methods
US8269244B2 (en) 2010-06-28 2012-09-18 Cree, Inc. LED package with efficient, isolated thermal path
WO2012109225A1 (fr) 2011-02-07 2012-08-16 Cree, Inc. Composants et procédés pour l'éclairage à l'aide de diodes électroluminescentes (del)
CN105170438B (zh) * 2015-10-15 2017-08-04 哈尔滨工程大学 一种水下圆柱壳宽带激振的装置

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DE1250323B (de) * 1967-09-14 RINO Werke o HG Maschinen fabrik Bammental bei Heidelberg Maschine zum Her stellen von Formlingen, insbesondere von dünnen Platten aus Beton od dgl
NL8004995A (nl) * 1980-09-03 1982-04-01 Lalesse Staalbouw B V Werkwijze en inrichting ter vervaardiging van een vormling uit aardvochtige betonspecie met lage water/cement verhouding.
NL8004985A (nl) * 1980-09-03 1982-04-01 Leonard Teerling Inrichting en werkwijze voor het verdichten van korrelige materialen, door zowel symmetrische als asymmetrische cyclische belastingen.
DE3724199A1 (de) * 1987-07-22 1989-02-02 Kloeckner Humboldt Deutz Ag Ruettelanlage zur herstellung von formkoerpern durch verdichtung
EP0620090A1 (fr) * 1993-04-07 1994-10-19 Den Boer Staal B.V. Installation de compactage
DE4434679A1 (de) * 1993-09-29 1995-03-30 Hubert Bald Verdichtungssystem zum Formen und Verdichten von Formstoffen zu Formkörpern in Formkästen
DE4332921A1 (de) * 1993-09-28 1995-03-30 Kloeckner Humboldt Deutz Ag Rüttelanlage zur Herstellung von Formkörpern durch Verdichtung
EP0870585A1 (fr) * 1997-04-09 1998-10-14 Den Boer Staal B.V. Méthode et dispositif pour le compactage d'une matière granuleuse telle que du mortier de béton

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1250323B (de) * 1967-09-14 RINO Werke o HG Maschinen fabrik Bammental bei Heidelberg Maschine zum Her stellen von Formlingen, insbesondere von dünnen Platten aus Beton od dgl
NL8004995A (nl) * 1980-09-03 1982-04-01 Lalesse Staalbouw B V Werkwijze en inrichting ter vervaardiging van een vormling uit aardvochtige betonspecie met lage water/cement verhouding.
NL8004985A (nl) * 1980-09-03 1982-04-01 Leonard Teerling Inrichting en werkwijze voor het verdichten van korrelige materialen, door zowel symmetrische als asymmetrische cyclische belastingen.
DE3724199A1 (de) * 1987-07-22 1989-02-02 Kloeckner Humboldt Deutz Ag Ruettelanlage zur herstellung von formkoerpern durch verdichtung
EP0620090A1 (fr) * 1993-04-07 1994-10-19 Den Boer Staal B.V. Installation de compactage
DE4332921A1 (de) * 1993-09-28 1995-03-30 Kloeckner Humboldt Deutz Ag Rüttelanlage zur Herstellung von Formkörpern durch Verdichtung
DE4434679A1 (de) * 1993-09-29 1995-03-30 Hubert Bald Verdichtungssystem zum Formen und Verdichten von Formstoffen zu Formkörpern in Formkästen
EP0870585A1 (fr) * 1997-04-09 1998-10-14 Den Boer Staal B.V. Méthode et dispositif pour le compactage d'une matière granuleuse telle que du mortier de béton

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005056279A1 (fr) * 2003-12-14 2005-06-23 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif pour serrer des matieres a mouler se presentant sous forme de grains
WO2005056201A1 (fr) * 2003-12-14 2005-06-23 GEDIB Ingenieurbüro und Innovationsberatung GmbH Vibrateur de battage de pieux pour des articles battus
DE102008011272A1 (de) 2008-02-26 2009-08-27 Institut für Fertigteiltechnik und Fertigbau Weimar e.V. Betonsteinfertiger mit harmonischer Vibration durch Formerregung
WO2009106297A2 (fr) 2008-02-26 2009-09-03 Institut Fuer Fertigteiltechnik Und Fertigbau Weimar E.V. Dispositif de fabrication de parpaings en béton à vibrations harmoniques par excitation du moule

Also Published As

Publication number Publication date
DE50004031D1 (de) 2003-11-13
ATE251544T1 (de) 2003-10-15
CA2396499A1 (fr) 2001-07-05
EP1242234A1 (fr) 2002-09-25
EP1242234B1 (fr) 2003-10-08
ES2208464T3 (es) 2004-06-16
DK1242234T3 (da) 2004-02-16

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