EP0400510A1 - Apparatus with vibrating table for making concrete products - Google Patents

Apparatus with vibrating table for making concrete products Download PDF

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Publication number
EP0400510A1
EP0400510A1 EP90110009A EP90110009A EP0400510A1 EP 0400510 A1 EP0400510 A1 EP 0400510A1 EP 90110009 A EP90110009 A EP 90110009A EP 90110009 A EP90110009 A EP 90110009A EP 0400510 A1 EP0400510 A1 EP 0400510A1
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EP
European Patent Office
Prior art keywords
shafts
vibrating table
motor
pulleys
installation according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP90110009A
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German (de)
French (fr)
Inventor
Daniel Marius Ancrenaz
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M.A.B.
Original Assignee
M.A.B.
Balbinot SA
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Publication date
Application filed by M.A.B., Balbinot SA filed Critical M.A.B.
Publication of EP0400510A1 publication Critical patent/EP0400510A1/en
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the present invention relates to vibrating tables fitted to the presses used for the manufacture of concrete products, such as, for example, pavers, blocks, curbs, and others.
  • Conventional presses are generally equipped with a vibration device for the concrete itself, conventional and consisting of a single table driven in the vertical direction by unbalance vibrators, synchronized with one another and driven in rotation by motors, in particular electric motors.
  • the vertical unidirectional vibration force cannot be adjusted independently of the speed of rotation of the unbalances during the different phases of the vibratory cycle of the production of a product.
  • the intensity of the force, the amplitude of the displacement of the table and the accelerations transmitted to the mold and to the concrete which it contains are determined only by the only speed of rotation, possibly variable, always determined once for all and not susceptible of any other adaptation.
  • the machines used are almost always versatile, that is to say intended for the manufacture of a very wide variety of products for which it is often impossible to obtain favorable manufacturing conditions for various products, both at the level of quality than that of the optimal duration of the manufacturing cycle.
  • the present invention aims to achieve, by seeking to optimize as simply as possible the physical conditions of the pre-vibration, intended essentially for the proper filling of the molds, and of the vibration proper intended to ensure good compaction. of the material before final solidification.
  • the duration of pre-vibration and vibration is of the order of a third of the duration of the complete cycle.
  • the engines are started and eventually braking and stopping before restarting and restraining for the actual vibration.
  • the vibrating table 1 carrying a molding board 2 is usually carried by a frame 3 with the interposition of damping pads 4.
  • the table 1 is animated in vibration by four lines of shafts 5 to 8 superimposed in pairs and equipped with weights or unbalances 51, 61, 71, 81 fixed on these shafts.
  • the support bearings of these shafts are carried by two housings 9, 10 axially offset, comprising bearings lubricated by bubbling in an oil bath.
  • the housings 9, 10 are rigidly fixed under the bearing face of the table 1. Between the two housings 9, 10, the connection between each part of each shaft 5 to 8 is ensured by an elastic transmission with floating shaft 11 and designed to withstand the very severe stress conditions under acceleration and impact.
  • the shafts 5 to 8 are also connected, each end, to a drive device described below by an equally elastic transmission 12.
  • one acts on the vibration frequency by playing on the drive speed of the shafts 5 to 8 without the need for repetitive stops and restarts, and one acts on the vibratory force (acceleration) by playing on the relative positions unbalances 51, 61, 71, 81 without the need either to interrupt the rotation in each pre-vibration-vibration cycle.
  • each shaft 5 to 8 supported in a housing 13 receiving the necessary bearings is equipped with a toothed drive pulley 52, 62, 72, 82.
  • a toothed drive pulley 52, 62, 72, 82 At each of these pulleys drive, and supported by the housing 13, is associated in the same horizontal plane on the outside with the shaft lines 5 to 8, a crazy toothed pulley 53, 63, 73, 83 ( Figure 3).
  • a double notched belt 14 passes successively over and under each contiguous pulley, as in FIG. 3.
  • This belt 14 is intended for driving in rotation the pulleys 52, 62, 72, 82 carried by the lines of shafts 5, 6, 7, 8, the idler pulleys 53, 63, 73, 83 providing the belt 14 with an optimal winding arc on the drive pulleys 52, 62, 72, 82.
  • the path of the belt 14 relative to the pulleys 52, 62, 72, 82 and 53, 63, 73, 83 gives them a sense of opposite rotation at each level of the two stages of shafts 5, 6, 7, 8.
  • the resulting vibration imparted to the table 1 is therefore unidirectional and in the vertical direction.
  • the motors 15, 15 ′ are supported by a fixed frame 16, in the same way as the casing 13, completely independent of the frame 3 of the press.
  • the motors (or the motor and the gear) 15, 15 ′ are carried by a slide 17 movable axially relative to the casing 13 and to the fixed chassis 16 and controllable in displacement by a jack 18.
  • FIGS. 4A to 4D schematically illustrate this result where a maximum vibration in intensity is obtained in position A of the slide and minimum in position D, the positions C and B corresponding to intermediate values.
  • the motors 15, 15 ′ are assumed to be rotating when the unbalances produce their maximum effect downwards.
  • Figures 4B to 4D show in the upper part what happens when moving to positions B, C and D respectively by the effect of the tension induced on the toothed belt (assuming that the motor is at a standstill, which is never necessary).
  • the situation is illustrated at a given instant during walking, but when the passage into the corresponding position A, B, C or D has been carried out.
  • the solution proposed by the invention meets the current requirements of industrial production operations: reliability, precision and performance.
  • the synchronization of rotation of the unbalanced shafts, ensured by the toothed belt, makes it possible to avoid the usual pinion trains whose lubrication is not compatible with high speeds of rotation and a satisfactory longevity.
  • the bearing support casings contain only the necessary special bearings, the unbalances being fixed at the outside of these casings, on the ends of intermediate shafts.
  • the double notched belt is maintenance-free and has a long service life.
  • the loads it induces on the bearings are low and the maximum linear speed can be very high to produce a vibration frequency of up to 100 Hz. It also allows automatic movement of the motors without mechanical components other than the slide to cylinder, fast and precise movement allowing continuous adjustment of the vibration force between a maximum value and a zero value.

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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)

Abstract

Quatre arbres porteurs de balourds sont disposés selon quatre lignes parallèles superposées par paire et portent en bout chacun une poulie crantée (52, 62, 72, 82) d'entrainement. Une courroie à double crantage (14) animée par un moteur (15) passe alternativement sous et sur les poulies (62, 52) de la première paire, sur un renvoi (15′) et sur et sous les poulies (72, 82) de la seconde paire. Des poulies folles (53, 63, 73, 83) associées à chaque arbre assurent un bon enroulement de la cour­roie (14). Le moteur (15) et le renvoi (15′) sont déplaçables latéralement sur un coulisseau (17) par rapport aux lignes d'arbres, ce qui permet de varier en continu la position respective des balourds de chaque paire d'arbres et, par là, l'intensité de la force de vibration résultante entre une valeur nulle et une valeur maximale.Four unbalance bearing shafts are arranged in four parallel lines superimposed in pairs and each carry a notched pulley (52, 62, 72, 82) at the end. A double-notched belt (14) driven by a motor (15) passes alternately under and over the pulleys (62, 52) of the first pair, over a transmission (15′) and over and under the pulleys (72, 82) of the second pair. Idler pulleys (53, 63, 73, 83) associated with each shaft ensure good winding of the belt (14). The motor (15) and the transmission (15′) can be moved laterally on a slider (17) relative to the lines of shafts, which makes it possible to continuously vary the respective position of the unbalances of each pair of shafts and, by there, the intensity of the resulting vibration force between a zero value and a maximum value.

Description

La présente invention est relative aux tables vibrantes équipant les presses utilisées pour la fabrication de produits en béton, tels, par exemple, que pavés, blocs, bordures, et autres.The present invention relates to vibrating tables fitted to the presses used for the manufacture of concrete products, such as, for example, pavers, blocks, curbs, and others.

Les presses conventionelles sont généralement équipées d'un dispositif de vibration du béton lui-même conventionnel et constitué d'une table unique animée dans le sens vertical par des vibrateurs à balourd, synchronisés entre eux et entrainés en rotation par des moteurs,notamment électriques.Conventional presses are generally equipped with a vibration device for the concrete itself, conventional and consisting of a single table driven in the vertical direction by unbalance vibrators, synchronized with one another and driven in rotation by motors, in particular electric motors.

Dans ces dispositifs, la force de vibration unidirectionnelle verticale n'est pas réglable indépendamment de la vitesse de rotation des balourds au cours des différentes phases du cycle vibratoire de la fabri­cation d'un produit. Ainsi, l'intensité de la force, l'amplitude du dépla­cement de la table et les accélérations transmises au moule et au béton qu'il contient sont-elles déterminées seulement par la seule vitesse de rotation, éventuellement variable, toujours déterminée une fois pour toutes et non susceptible d'autre adaptation.In these devices, the vertical unidirectional vibration force cannot be adjusted independently of the speed of rotation of the unbalances during the different phases of the vibratory cycle of the production of a product. Thus, the intensity of the force, the amplitude of the displacement of the table and the accelerations transmitted to the mold and to the concrete which it contains are determined only by the only speed of rotation, possibly variable, always determined once for all and not susceptible of any other adaptation.

Les machines utilisées étant presque toujours polyvalentes, c'est-à-dire destinées à la fabrication d'une très large diversité de produits pour lesquels il est bien souvent impossible d'obtenir des condi­tions de fabrication favorables pour divers produits, aussi bien au niveau de la qualité qu'à celui de la durée optimale du cycle de fabrication.The machines used are almost always versatile, that is to say intended for the manufacture of a very wide variety of products for which it is often impossible to obtain favorable manufacturing conditions for various products, both at the level of quality than that of the optimal duration of the manufacturing cycle.

Les réglages effectués dans l'état actuel des choses sur certaines phases de la fabrication (durée de prévibration, nombre de coups d'agitateur du tiroir de remplissage ou encore durée de la vibration finale) sont insuffisants et inadéquats.The adjustments made in the current state of things during certain phases of manufacturing (pre-vibration duration, number of agitator strokes of the filling drawer or duration of the final vibration) are insufficient and inadequate.

On vient à conclure que c'est sur les dispositifs de vibration eux-mêmes, présentant trop de limites ou d'insuffisances, qu'il y a lieu d'intervenir et de les modifier et perfectionner pour répondre aux exigences d'une fabrication de qualité certaine et selon des conditions optimales réduisant le coût final.We come to conclude that it is on the vibration devices themselves, with too many limits or inadequacies, that it is necessary to intervene and modify and perfect them to meet the requirements of a manufacturing of certain quality and under optimal conditions reducing the final cost.

C'est ce but que vise à atteindre la présente invention, en cherchant à optimaliser aussi simplement que possible les conditions physi­ques de la pré-vibration, destinée essentiellement au bon remplissage des moules, et de la vibration proprement dite destinée à assurer un bon compac­tage du matériau avant solidification définitive. Il y a donc intérêt à pouvoir, autrement que par l'intervention sur la seule vitesse de rotation des balourds, agir pour chaque phase sur les paramètres déterminants que sont la force liée directement à l'accélération, et l'amplitude du déplacement transmis aux moules.It is this aim which the present invention aims to achieve, by seeking to optimize as simply as possible the physical conditions of the pre-vibration, intended essentially for the proper filling of the molds, and of the vibration proper intended to ensure good compaction. of the material before final solidification. There is therefore an advantage in being able, other than by operating on the unbalance rotation speed alone, to act for each phase on the determining parameters which are the force directly linked to the acceleration, and the amplitude of the displacement transmitted to the mussels.

Ainsi, souvent, avec les installations conventionelles, pour un cycle moyen complet de 10 à 15 s, la durée de prévibration et de vibration est de l'ordre du tiers de la durée du cycle complet. On procède au démarrage des moteurs et éventuellement à un freinage et un arrêt avant de redémarrer et refreiner pour la vibration proprement dite.Thus, often, with conventional installations, for a complete average cycle of 10 to 15 s, the duration of pre-vibration and vibration is of the order of a third of the duration of the complete cycle. The engines are started and eventually braking and stopping before restarting and restraining for the actual vibration.

Entre ces deux phases, seule la vitesse de rotation des arbres à balourds a subi une modification, tout le reste restant en l'état.Between these two phases, only the speed of rotation of the unbalanced shafts has undergone a modification, all the rest remaining in the state.

Sur une durée de fonctionnement d'une mn on arrive à avoir besoin d'une dizaine, sinon plus, de phases de démarrage et de freinage aussi la puissance installée est-elle extrêmement importante. La solution qui consisterait à utiliser des fréquences de vibration variables, indé­pendamment du régime des moteurs impliquerait des variateurs de fréquence énormes. Les variateurs existants ne sont d'ailleurs pas conçus pour une telle fonction.Over an operating period of one minute, you get to need ten, if not more, starting and braking phases, so the installed power is extremely important. The solution which would consist in using variable vibration frequencies, independently of the engine speed would involve enormous frequency variators. Existing drives are not designed for such a function.

Devant ces insuffisances, il a été proposé d'utiliser des masselottes réglables en position sur l'arbre en rotation. Mais du fait du régime vibratoire, la liaison réglable des masselottes sur l'arbre prend rapidement du jeu et, dans un souci de longévité, cette solution est à proscrire.In view of these shortcomings, it has been proposed to use weights which are adjustable in position on the rotating shaft. But because of the vibratory regime, the adjustable linkage of the flyweights on the shaft quickly takes play and, for the sake of longevity, this solution is to be avoided.

On a également proposé un décalage relatif des masselottes ou des balourds au moyen de trains de pignons et planétaires lubrifiés par bain d'huile dans ces carters. Cette technique limite considérablement la vitesse de rotation des arbres porteurs des masselottes ou balourds et la fréquence maximale de vibration ainsi obtenue n'est pas compatible avec la réalisation de produits très compacts tels que bordures et pavés, pour lesquels une fréquence de 75 Hz (soit 4500 tours/mn) est au moins nceessaire.It has also been proposed a relative offset of the counterweights or unbalances by means of pinion and planetary trains lubricated by oil bath in these casings. This technique considerably limits the speed of rotation of the shafts carrying weights or unbalances and the maximum frequency of vibration thus obtained is not compatible with the production of very compact products such as curbs and pavers, for which a frequency of 75 Hz (i.e. 4500 rpm) is at least necessary.

L'invention avec ses caractéristiques qui font l'objet des revendications et autres avantages non encore évoqués est exposée dans la description qui suit et pour l'intelligence de laquelle on se référera aux dessins, dont :

  • - les figures 1, 2 et 3 montrent respectivement en vue de bout selon le plan AA de la figure 2, en vue longitudinale de côté, et en vue de bout selon la flèche F de la figure 2, une installation à table vibrante conforme à l'invention,
  • -la figure 4A illustre schématiquement le fonctionnement du dispositif d'entrainement de la même installation.
  • - et les figures 4B, 4C et 4D, ce fonctionnement dans les positions respec­tives B, C et D portées à la figure 4A.
The invention with its features which are the subject of the claims and other advantages not yet mentioned is set out in the description which follows and for the understanding of which reference will be made to the drawings, of which:
  • - Figures 1, 2 and 3 show respectively in end view along the plane AA of Figure 2, in longitudinal side view, and in end view according to arrow F of Figure 2, a vibrating table installation according to the invention,
  • FIG. 4A schematically illustrates the operation of the drive device of the same installation.
  • - And Figures 4B, 4C and 4D, this operation in the respective positions B, C and D shown in Figure 4A.

Comme on le voit notamment aux figures 1 et 2, la table vibrante 1 porteuse d'une planche de moulage 2, est de façon usuelle portée par un bâti 3 avec interposition de tampons amortisseurs 4.As can be seen in particular in FIGS. 1 and 2, the vibrating table 1 carrying a molding board 2 is usually carried by a frame 3 with the interposition of damping pads 4.

Selon l'invention, la table 1 est animée en vibration par quatre lignes d'arbres 5 à 8 superposés par paire et équipés de masselottes ou balourds 51, 61, 71, 81 fixés sur ces arbres. Les paliers de support de ces arbres sont portés par deux carters 9, 10 décalés axialement, comportant des roulements lubrifiés par barbotage dans un bain d' huile. Les carters 9, 10 sont fixés rigidement sous la face d'appui de la table 1. Entre les deux carters 9, 10, la liaison entre chaque partie de chaque arbre 5 à 8 est assurée par une transmission élastique à arbre flottant 11 et conçue pour résister aux très sévères conditions de sollicitation en accéleration et aux chocs. Les arbres 5 à 8 sont par ailleurs reliés on bout chacun à un dispositif d'entrainement décrit ci-après par une trans­mission également élastique 12.According to the invention, the table 1 is animated in vibration by four lines of shafts 5 to 8 superimposed in pairs and equipped with weights or unbalances 51, 61, 71, 81 fixed on these shafts. The support bearings of these shafts are carried by two housings 9, 10 axially offset, comprising bearings lubricated by bubbling in an oil bath. The housings 9, 10 are rigidly fixed under the bearing face of the table 1. Between the two housings 9, 10, the connection between each part of each shaft 5 to 8 is ensured by an elastic transmission with floating shaft 11 and designed to withstand the very severe stress conditions under acceleration and impact. The shafts 5 to 8 are also connected, each end, to a drive device described below by an equally elastic transmission 12.

Selon l'invention, on agit sur la fréquence de vibration en jouant sur la vitesse d'entrainement des arbres 5 à 8 sans nécessité d'arrêts et redémarrages répétitifs, et on agit sur la force (accélération) vibratoire en jouant sur les positions relatives des balourds 51, 61, 71, 81 sans nécessité non plus d'interrompre la rotation dans chaque cycle prévibration-vibration.According to the invention, one acts on the vibration frequency by playing on the drive speed of the shafts 5 to 8 without the need for repetitive stops and restarts, and one acts on the vibratory force (acceleration) by playing on the relative positions unbalances 51, 61, 71, 81 without the need either to interrupt the rotation in each pre-vibration-vibration cycle.

Comme on le voit mieux aux figures 2 et 3, chaque arbre 5 à 8, supporté dans un carter 13 recevant les roulements nécessaires, est équipé d'une poulie crantée d'entrainement 52, 62, 72, 82. A chacune de ces poulies d'entrainement, et supportée par le carter 13, est associée dans le même plan horizontal du côté extérieur aux lignes d'arbres 5 à 8, une poulie crantée folle 53, 63, 73, 83 (figure 3). Une courroie à double crantage 14 passe successivement sur et sous chaque poulie contiguë, comme à la figure 3. Cette courroie 14 est destinée à l'entrainement en rotation des poulies 52, 62, 72, 82 portée par les lignes d'arbres 5, 6, 7, 8, les poulies folles 53, 63, 73, 83 assurant à la courroie 14 un arc d'enroule­ment optimal sur les poulies d'entrainement 52, 62, 72, 82.As best seen in Figures 2 and 3, each shaft 5 to 8, supported in a housing 13 receiving the necessary bearings, is equipped with a toothed drive pulley 52, 62, 72, 82. At each of these pulleys drive, and supported by the housing 13, is associated in the same horizontal plane on the outside with the shaft lines 5 to 8, a crazy toothed pulley 53, 63, 73, 83 (Figure 3). A double notched belt 14 passes successively over and under each contiguous pulley, as in FIG. 3. This belt 14 is intended for driving in rotation the pulleys 52, 62, 72, 82 carried by the lines of shafts 5, 6, 7, 8, the idler pulleys 53, 63, 73, 83 providing the belt 14 with an optimal winding arc on the drive pulleys 52, 62, 72, 82.

Au moins un moteur rotatif 15 coopérant avec une poulie de renvoi 15′, ou deux moteurs 15, 15′, disposés axialement de part et d'autre du carter 13 et d'axes horizontaux de préférence décalés verticalement l'un par rapport à l'autre assure l'entrainement et le défilement continu de la courroie crantée 14.At least one rotary motor 15 cooperating with a return pulley 15 ′, or two motors 15, 15 ′, arranged axially on either side of the casing 13 and of horizontal axes preferably offset vertically one relative to the the other ensures the continuous drive and running of the toothed belt 14.

Comme on le voit, le cheminement de la courroie 14 par rapport aux poulies 52, 62, 72, 82 et 53, 63, 73, 83 leur imprime un sens de rotation opposé à chaque niveau des deux étages d'arbres 5, 6, 7, 8. La vibration résultante conférée à la table 1 est donc unidirectionnelle et dans le sens vertical.As can be seen, the path of the belt 14 relative to the pulleys 52, 62, 72, 82 and 53, 63, 73, 83 gives them a sense of opposite rotation at each level of the two stages of shafts 5, 6, 7, 8. The resulting vibration imparted to the table 1 is therefore unidirectional and in the vertical direction.

Le ou les moteurs 15, 15′ sont supportés par un châssis fixe 16, de mem̂e que le carter 13, indépendant totalement du bâti 3 de la presse. Les moteurs (ou le moteur et le renvoi) 15, 15′ sont portés par un coulisseau 17 mobile axialement par rapport au carter 13 et au châssis fixe 16 et commandable en déplacement par un vérin 18.Or the motors 15, 15 ′ are supported by a fixed frame 16, in the same way as the casing 13, completely independent of the frame 3 of the press. The motors (or the motor and the gear) 15, 15 ′ are carried by a slide 17 movable axially relative to the casing 13 and to the fixed chassis 16 and controllable in displacement by a jack 18.

Par le truchement du vérin 18, un déplacement relatif des axes de rotation des moteurs 15, 15′ par rapport au carter 13 tout en maintenant l'entraxe constant, va provoquer sur la courroie crantée 14, en prise avec les poulies,notamment d'entrainement 52, 62, 72, 82, une traction qui induit sur ces poulies un décalage angulaire, donc un décalage angulaire relatif entre les balourds portés par les arbres situés au même niveau. Ce déphasage entre les balourds agit directement et indépendamment de la vitesse de rotation des moteurs 15, 15′ sur la force verticale de la vibration résultante, qui peut ainsi être réglée de façon continue entre une valeur maximale pour une position extrême du coulisseau 17 et une valeur nulle pour l'autre position extrême.By means of the jack 18, a relative displacement of the axes of rotation of the motors 15, 15 ′ with respect to the casing 13 while keeping the center distance constant, will cause the toothed belt 14, in engagement with the pulleys, in particular to drive 52, 62, 72, 82, a traction which induces on these pulleys an angular offset, therefore a relative angular offset between the unbalances carried by the shafts located at the same level. This phase shift between the unbalances acts directly and independently of the speed of rotation of the motors 15, 15 ′ on the vertical force of the resulting vibration, which can thus be adjusted continuously between a maximum value for an extreme position of the slide 17 and a zero value for the other extreme position.

Les figures 4A à 4D illustrent schématiquement ce résultat où l'on obtient une vibration maximale en intensité en position A du coulisseau et minimale en position D, les positions C et B correspondant à des valeurs intermédiaires. A la figure 4A, les moteurs 15, 15′ sont supposés en rotation au moment où les balourds produisent vers le bas leur effet maximal. A partir de cette position A, les figures 4B à 4D montrent en partie supérieure ce qui se passe lors du déplacement vers les positions B, C et D respectivement par l'effet de la tension induite sur la courroie crantée (en supposant que le moteur est à l'arrêt, ce qui n'est jamais nécessaire). En partie inférieure de ces figures, on illustre la situation à un instant donné pendant la marche, mais lorsque le passage dans la position correspondante A, B, C ou D a été effectué .FIGS. 4A to 4D schematically illustrate this result where a maximum vibration in intensity is obtained in position A of the slide and minimum in position D, the positions C and B corresponding to intermediate values. In FIG. 4A, the motors 15, 15 ′ are assumed to be rotating when the unbalances produce their maximum effect downwards. From this position A, Figures 4B to 4D show in the upper part what happens when moving to positions B, C and D respectively by the effect of the tension induced on the toothed belt (assuming that the motor is at a standstill, which is never necessary). In the lower part of these figures, the situation is illustrated at a given instant during walking, but when the passage into the corresponding position A, B, C or D has been carried out.

De ce qui précède, on voit que la solution proposée par l'in­vention répond aux impératifs actuels d'une exploitation industrielle en production : fiabilité, précision et performance. La synchronisation de rotation des arbres à balourds, assurée par la courroie crantée, permet d'éviter les trains de pignons habituels dont la lubrification n'est pas compatible avec de grandes vitesses de rotation et une longévité satisfai­sante. Dans le cas présent, les carters supports de paliers ne renferment que les roulements spéciaux nécessaires, les balourds étant fixés à l'extérieur de ces carters, sur les extrémités d'arbres intermédiaires.From the above, it can be seen that the solution proposed by the invention meets the current requirements of industrial production operations: reliability, precision and performance. The synchronization of rotation of the unbalanced shafts, ensured by the toothed belt, makes it possible to avoid the usual pinion trains whose lubrication is not compatible with high speeds of rotation and a satisfactory longevity. In the present case, the bearing support casings contain only the necessary special bearings, the unbalances being fixed at the outside of these casings, on the ends of intermediate shafts.

La courroie à double crantage ne nécessite aucun entretien et sa durée de vie est élevée. Les charges qu'elle induit sur les paliers sont faibles et la vitesse linéaire maximale peut être très élevée pour produire une fréquence de vibration pouvant atteindre 100 Hz. Elle permet en outre une manoeuvre automatique du déplacement des moteurs sans organes mécaniques autres que le coulisseau à vérin, déplacement rapide et précis permettant en marche un réglage continu de la force de vibration entre une valeur maximale et une valeur nulle.The double notched belt is maintenance-free and has a long service life. The loads it induces on the bearings are low and the maximum linear speed can be very high to produce a vibration frequency of up to 100 Hz. It also allows automatic movement of the motors without mechanical components other than the slide to cylinder, fast and precise movement allowing continuous adjustment of the vibration force between a maximum value and a zero value.

Claims (9)

1.- Installation à table vibrante pour la fabrication de pro­duits en béton, comprenant une table vibrante (1) montée élastiquement (4) sur un bâti (3) et animée en vibration par des arbres (5, 6, 7, 8) supportés dans de carters (9, 10) liés à la table (1) et porteurs de balourds (51, 61, 71, 81), caractérisée par le fait que les arbres (5, 6, 7, 8) sont disposés selon quatre lignes parallèles superposées deux à deux par paires (5, 7 et 6, 8) et sont porteurs en bout chacun d'une poulie crantée (52, 62, 72, 82) coopérant avec une courroie à double crantage (14) entrainée par au moins un moteur rotatif (15) disposé latéralement par rapport aux lignes d'arbres et d'axe parallèle à celles-ci, la courroie (14) passant alternativement respectivement sous et sur ou sur et sous les poulies (52, 62) de la première paire d'arbres, puis autour d'un renvoi (15′) d'axe parallèle à celui du moteur (15) et disposé par rapport aux lignes d'arbres du côté opposé à celui de ce moteur (15) avant de repasser alternativement respectivement sur et sous ou sous et sur les poulies (72, 82) de la seconde paire d'arbres, et revenir s'enrouler sur le moteur (15), le moteur (15) et le renvoi (15′) étant supportés par un coulisseau (17) déplaçable transversalement par rapport aux lignes d'arbres (5, 6, 7, 8) pour varier la position angulaire relative des balourds (51, 61, 71, 81) de chaque paire d'arbres.1.- Installation with vibrating table for the manufacture of concrete products, comprising a vibrating table (1) elastically mounted (4) on a frame (3) and animated in vibration by supported shafts (5, 6, 7, 8) in casings (9, 10) linked to the table (1) and carrying unbalances (51, 61, 71, 81), characterized in that the shafts (5, 6, 7, 8) are arranged in four lines parallels superimposed two by two in pairs (5, 7 and 6, 8) and each carry at the end a toothed pulley (52, 62, 72, 82) cooperating with a double notched belt (14) driven by at least a rotary motor (15) disposed laterally with respect to the lines of shafts and axes parallel to them, the belt (14) passing alternately under and over or over and under the pulleys (52, 62) of the first pair of shafts, then around a return (15 ′) with an axis parallel to that of the motor (15) and arranged with respect to the lines of shafts on the side opposite to that ui of this motor (15) before alternately passing respectively on and under or under and on the pulleys (72, 82) of the second pair of shafts, and return to wind on the motor (15), the motor (15 ) and the return (15 ′) being supported by a slide (17) movable transversely relative to the lines of shafts (5, 6, 7, 8) to vary the relative angular position of the unbalances (51, 61, 71, 81 ) of each pair of trees. 2.- Installation à table vibrante selon la revendication 1, caractérisée par le fait que le renvoi (15′) se présente sous la forme d'un second moteur.2.- vibrating table installation according to claim 1, characterized in that the return (15 ′) is in the form of a second motor. 3.- Installation à table vibrante selon la revendication 1 ou la revendication 2, caractérisée par le fait que de part et d'autre de chaque paire d'arbres, est disposée une poulie crantée (53, 63, 73, 83) montée folle et d'axe parallèle à ces arbres pour assurer un arc d'enrou­lement suffisant de la courroie (14) sur chaque poulie d'arbre (52, 62,72, 82) porteur de balourd.3.- vibrating table installation according to claim 1 or claim 2, characterized in that on either side of each pair of shafts is arranged a toothed pulley (53, 63, 73, 83) mounted madly and axis parallel to these shafts to ensure a sufficient winding arc of the belt (14) on each shaft pulley (52, 62,72, 82) carrying imbalance. 4.- Installation à table vibrante selon l'une quelconque des revendications 1 à 3, caractérisée par le fait que les axes du moteur (15) et du renvoi (15′) sont décalés dans le sens vertical pour assurer un enroulement optimal de la courroie (14) sur les poulies d'entrainement des arbres (52, 62, 72, 82).4.- vibrating table installation according to any one of claims 1 to 3, characterized in that the axes of the motor (15) and of the return (15 ′) are offset in the vertical direction to ensure optimal winding of the belt (14) on the drive pulleys of the shafts (52, 62, 72, 82). 5.- Installation à table vibrante selon l'une quelconque des revendications 1 à 4, caractérisée par le fait que le déplacement du coulisseau (17) est commadé par un vérin (18).5.- vibrating table installation according to any one of claims 1 to 4, characterized in that the movement of the slide (17) is controlled by a jack (18). 6.- Installation à table vibrante selon l'une quelconque des revendications 1 à 5, caractérisée par le fait que les balourds (51, 61, 71, 81) sont montés sur les arbres (5, 6, 7, 8) à l'extérieur des carters (9, 10).6.- vibrating table installation according to any one of claims 1 to 5, characterized in that the unbalances (51, 61, 71, 81) are mounted on the shafts (5, 6, 7, 8) at l outside of the housings (9, 10). 7.- Installation à table vibrante selon l'une quelconque des revendications 1 à 6, caractérisée par le fait qu'entre les carters (9, 10) la liaison sur chaque ligne d'arbre (5, 6, 7, 8) est assurée par une trans­mission élastique à arbre flottant (11).7.- vibrating table installation according to any one of claims 1 to 6, characterized in that between the housings (9, 10) the connection on each shaft line (5, 6, 7, 8) is provided by an elastic floating shaft transmission (11). 8.- Installation à table vibrante selon l'une quelconque des revendications 1 à 7, caractérisée par le fait que les arbres (5, 6, 7, 8) sont reliés en bout au dispositif moteur (15) par une transmission élastique (12), solidaire des poulies crantées (52, 62, 72, 82).8.- vibrating table installation according to any one of claims 1 to 7, characterized in that the shafts (5, 6, 7, 8) are connected at the end to the motor device (15) by an elastic transmission (12 ), integral with the toothed pulleys (52, 62, 72, 82). 9.- Installation à table vibrante selon l'une quelconque des revendications 1 à 8, caractérisée par le fait que les arbres (5, 6, 7, 8) en bout sont supportés dans un carter fixe (13).9.- Installation vibrating table according to any one of claims 1 to 8, characterized in that the shafts (5, 6, 7, 8) at the end are supported in a fixed housing (13).
EP90110009A 1989-06-02 1990-05-26 Apparatus with vibrating table for making concrete products Ceased EP0400510A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8907564A FR2647705B1 (en) 1989-06-02 1989-06-02 VIBRATING TABLE INSTALLATION FOR THE MANUFACTURE OF CONCRETE PRODUCTS
FR8907564 1989-06-02

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EP (1) EP0400510A1 (en)
CA (1) CA2017041A1 (en)
FR (1) FR2647705B1 (en)

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EP0600526A1 (en) * 1992-12-03 1994-06-08 Antonio Poyatos Diaz Vibrating arrangement for machinery
EP0692317A1 (en) 1994-07-13 1996-01-17 Daniel Ancrenaz Device for generating vibrations, particularly for a press-table used for the manufacture of concrete products
DE19511895A1 (en) * 1995-03-31 1996-10-02 Karl Rekers Maschinen Und Stah Vibration generator for in particular vibrating stations of stone molding machines
DE4210507C2 (en) * 1991-04-03 2002-11-07 Josef Cron Device for adjusting at least two unbalances rotating on unbalanced shafts in their unbalanced position relative to one another
FR2852648A1 (en) * 2003-03-20 2004-09-24 Eurocopter France Anti-vibratory device for use in aircraft with rotatable wing e.g. helicopter, has controllable mobile equipment holding control system and sliding along symmetrical axis for driving phase lag of rotors with off-centered weights
CN100436860C (en) * 2005-02-17 2008-11-26 欧洲直升机公司 An antivibration device having rotary flyweights and an epicyclic geartrain
CN104963997A (en) * 2014-07-21 2015-10-07 摩尔动力(北京)技术股份有限公司 Interface balance system

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AU3474599A (en) 1998-04-17 1999-11-08 Emerson Electric Co. Vibratory screen separator
US6321610B1 (en) * 1999-08-08 2001-11-27 Kabushiki Kaisha Kei Vibration apparatus for a variable amplitude type vibration table
US6866603B2 (en) * 2002-12-17 2005-03-15 The Goodyear Tire & Rubber Company Counter-rotational drive belt system and method
DE10306791A1 (en) * 2003-02-18 2004-08-26 Bomag Gmbh Vibration exciter device
DK176725B1 (en) * 2003-07-04 2009-05-04 Kvm Industrimaskiner As Method for making a vibration table for concrete casting machines and a vibration loaf made according to the method
RU2619572C1 (en) * 2015-12-16 2017-05-16 федеральное государственное бюджетное образовательное учреждение высшего образования "Брянский государственный инженерно-технологический университет" Device for mould fixing to shaking table
CN109732743A (en) * 2019-01-31 2019-05-10 浙江广天构件股份有限公司 A kind of removable vibration device of die station

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DE3113693A1 (en) * 1981-04-04 1982-10-21 Weber Maschinentechnik Gmbh, 5928 Laasphe Vibration generator for a controllable vibratory plate
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Cited By (12)

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Publication number Priority date Publication date Assignee Title
DE4210507C2 (en) * 1991-04-03 2002-11-07 Josef Cron Device for adjusting at least two unbalances rotating on unbalanced shafts in their unbalanced position relative to one another
EP0600526A1 (en) * 1992-12-03 1994-06-08 Antonio Poyatos Diaz Vibrating arrangement for machinery
EP0692317A1 (en) 1994-07-13 1996-01-17 Daniel Ancrenaz Device for generating vibrations, particularly for a press-table used for the manufacture of concrete products
FR2722444A1 (en) * 1994-07-13 1996-01-19 Ancrenaz Daniel VIBRATION DEVICE FOR PRESS TABLE USED FOR THE PRODUCTION OF CONCRETE PRODUCTS
DE19511895A1 (en) * 1995-03-31 1996-10-02 Karl Rekers Maschinen Und Stah Vibration generator for in particular vibrating stations of stone molding machines
EP0734785A1 (en) * 1995-03-31 1996-10-02 Firma Dipl.-Ing. Karl Rekers, Maschinen- und Stahlbau Vibratory device for moulding building blocks
FR2852648A1 (en) * 2003-03-20 2004-09-24 Eurocopter France Anti-vibratory device for use in aircraft with rotatable wing e.g. helicopter, has controllable mobile equipment holding control system and sliding along symmetrical axis for driving phase lag of rotors with off-centered weights
WO2004087343A1 (en) * 2003-03-20 2004-10-14 Eurocopter Anti-vibratory device with rotary compensation weights
US7582032B2 (en) 2003-03-20 2009-09-01 Eurocopter Anti-vibratory device with rotary compensation weights
CN100436860C (en) * 2005-02-17 2008-11-26 欧洲直升机公司 An antivibration device having rotary flyweights and an epicyclic geartrain
CN104963997A (en) * 2014-07-21 2015-10-07 摩尔动力(北京)技术股份有限公司 Interface balance system
CN104963997B (en) * 2014-07-21 2018-02-09 摩尔动力(北京)技术股份有限公司 Interface balance system

Also Published As

Publication number Publication date
FR2647705B1 (en) 1991-08-30
CA2017041A1 (en) 1990-12-02
US5067358A (en) 1991-11-26
FR2647705A1 (en) 1990-12-07

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