EP2012988A1 - Dispositif de réalisation d'agglomérés de béton au moyen d'un dispositif vibreur et d'un actionneur - Google Patents

Dispositif de réalisation d'agglomérés de béton au moyen d'un dispositif vibreur et d'un actionneur

Info

Publication number
EP2012988A1
EP2012988A1 EP07728227A EP07728227A EP2012988A1 EP 2012988 A1 EP2012988 A1 EP 2012988A1 EP 07728227 A EP07728227 A EP 07728227A EP 07728227 A EP07728227 A EP 07728227A EP 2012988 A1 EP2012988 A1 EP 2012988A1
Authority
EP
European Patent Office
Prior art keywords
fluid
aktuator
membrane
mold
actuator
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.)
Withdrawn
Application number
EP07728227A
Other languages
German (de)
English (en)
Inventor
Rudolf Braungardt
Holger Stichel
Swen Dietrich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kobra Formen GmbH
Original Assignee
Kobra Formen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kobra Formen GmbH filed Critical Kobra Formen GmbH
Publication of EP2012988A1 publication Critical patent/EP2012988A1/fr
Withdrawn legal-status Critical Current

Links

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
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/12—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving reciprocating masses
    • B06B1/14—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving reciprocating masses the masses being elastically coupled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/10—Characterised by the construction of the motor unit the motor being of diaphragm type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators

Definitions

  • the invention relates to a device for the production of concrete blocks with a vibrator and a suitable for a vibrator actuator.
  • US Pat. No. 6,352,236 B1 (Columbia) shows an apparatus for the production of concrete shaped blocks, in which motor-driven crankshafts deflect a form against an air bellows spring from a rest position downwards via linkage. The provision is made by the bellows spring upwards.
  • a device with an excitation of a vibratory suspended form by fluid-actuated cylinder is known from WO 01/47698 A1, which is constructed very expensive. Shakers prove to be particularly effective according to the principle of shock vibration, in which the blow bars are beaten from below against a vibrating table. However, such vibrators also cause high wear on molds and molding machine and a high noise level during the Rüttelvorgangs. From EP 1 050 393 A2 or EP 1 080 858 A2, devices are known in which a plurality of piezo elements are used as actuators for exciting shaking movements of a vibrating table arrangement.
  • the present invention has for its object to provide an apparatus for producing concrete blocks with a simple structure, effective and low-wear shaker and a suitable actuator for this purpose.
  • the use of a hydraulically actuable actuator with a closed by a flexible membrane fluid chamber proves to be particularly advantageous for the vibrator of a device for the production of concrete blocks in closed above by pressure plates of a Auflast worn mold cavities resting on a vibrating table arrangement.
  • the membrane is preferably metallic, in particular made of spring steel or a comparably long-term on alternating bending claimable and at the same time elastically flexible material.
  • the flexible diaphragm actuator does not require any sliding or rolling parts to move, and therefore does not show significant wear in the cycling of the shaking motion in a typical shaker frequency range of 30 Hz to 150 Hz.
  • the limited by the Aufwölb sadness the membrane amplitude of the shaking motion is favorably correlated in this application with the applied Hinttelkraft by preferably at a fluid pressure between 100 bar and 500 bar transverse dimensions of the membrane are between 50 mm and 250 mm, which in turn displacement paths Allow vertexes of the membrane in a favorable for solidification of the concrete amount amplitude range of advantageously between 0.2 mm and 4 mm and thereby allow high forces for high accelerations.
  • a force transmission is advantageously carried out by a coupling to the actuator in the region of the vertex of the curvature of the membrane, for which in this area advantageously a force-transmitting mechanical element is connected to the membrane.
  • Hydraulic actuators with a membrane are known as such and z. As used in DE 38 31 928 C2 for stabilizing rotating axes or in DE 2451228 A1 as electrohydraulic vibrator.
  • a plurality of actuators of the type described are provided, which act in a preferred embodiment on a mold frame laterally outside the stone field area, ie the area with the mold cavities of the mold, wherein the mold frame is advantageously clamped vertically with a Rüttelan extract which rests against the underside of the mold cavities so that the excitation of the mold frame is transferred to vertical jarring movements in vertical jarring movements of the vibrating table assembly, which in turn are introduced into the concrete amount.
  • the mold is subdivided into a mold frame remaining in the molding machine and into a mold insert which can be interchangeably inserted therein, in which one or more Rere form nests are formed.
  • the actuators of the vibrator preferably act on the mold frame.
  • an elastic deformation is transmitted by changing the bulge of the membrane by the force-transmitting element in a movement of an imbalance mass relative to the mold.
  • the vibrator acts as an unbalance vibrator and does not need to be supported against the machine frame.
  • the movement of the imbalance mass relative to the mold can take place under the action of the fluid against a restoring spring force.
  • the movement can be in one or two
  • a stop may additionally or alternatively also be provided for the movement of the mold relative to the machine frame.
  • the vibrator is stably supported in the forming machine against vertical displacement in the case of the vertical vibratory forces exerted on the vibrating table arrangement or the forming frame.
  • the vibrating table arrangement or the frame clamped with the latter is supported via additional supporting elements, via which in particular the weight of the masses moved in total during the agitation can be wholly or partially, advantageously at least predominantly statically intercepted.
  • the Haittelaktuatoren can be relieved to a corresponding extent of static forces.
  • the additional support elements allow a limited vertical movement of the vibrating table arrangement at least to the extent of the intended vibration amplitude of the actuators.
  • the additional support elements can this, z. B.
  • the support elements are variably adjustable.
  • provision may be made for means for automatically adjusting the additional support elements to be provided prior to the start of a shaking operation, which set a reference position of the shaking device that is independent of the weight of the supported masses.
  • the Rüttelaktuato- ren must then apply essentially only the force for oscillating deflection of the vibrator or moving through this vibrator or the mold frame.
  • a variable setting of the additional support elements may, for. B. be given by the fact that documents such support elements are mechanically vertically adjustable or that are provided with pressure medium, in particular compressed air acted upon elements over which a height adjustment is given.
  • position sensors or position sensors can be provided on the additional support elements on the mold frame, on the vibrating table arrangement or preferably on the vibration actuators or components correlated with their position.
  • a height adjustment of the housing of the actuators in the molding machine or an adjustability of the connection of the actuators can be provided with the assembly to be shaken.
  • the deflection of the mold takes place from a rest position assumed before the shaking operation against a restoring force acting in addition to the weight force of the moving masses.
  • the restoring force increases with increasing deflection from the rest position.
  • the restoring force may be directed against a deflection from the rest position upwards and / or downwards.
  • the restoring force can be achieved by elastic elements, for. B. spring elements are applied, which support a harmonic oscillation of the moving masses.
  • the movement of the mold relative to the mold frame of the molding machine to be considered fixed may be upwards and / or preferably downwards against a stop.
  • actuators of the vibrating device can be acted upon together with the same fluid pressure or individually with different time-varying fluid pressures. This can be given in particular via the individual actuators individually associated control valve arrangements in supplying and / or discharging fluid lines in conjunction with a control device.
  • the control valve arrangements may advantageously be integrated in housings of the actuators.
  • the limitation of the fluid chamber of a hydraulic actuator by a flexible, archable membrane is of particular advantage for an oscillator for generating a directional oscillating movement, in particular for generating low-amplitude shaking movements with high force.
  • the transfer of the oscillating membrane movement to a component to be vibrated is advantageously carried out via at least one force-transmitting element, which is advantageously coupled to the membrane in the region of the vertex of its curvature.
  • the excitation to an oscillating movement of the membrane takes place under the influence of a control device, which preferably acts on a valve arrangement with at least one controllable valve in the flow path of the hydraulic fluid.
  • a fluid line arrangement for guiding the fluid advantageously contains at least one fluid in the fluid chamber conducting first fluid line and separated at least one fluid from the fluid chamber leading away second fluid line.
  • a plurality of first fluid lines are in fluidic parallel connection and a plurality of second fluid lines provided in parallel.
  • the parallel-connected fluid lines preferably open separately into the fluid chamber.
  • the parallel-connected fluid lines are branched off at their ends facing away from the fluid chamber from a manifold, which is preferably designed as a loop.
  • the first and second fluid conduits advantageously open at separate positions in the fluid chamber.
  • the alternate supply and discharge of fluid in the chamber creates a scavenging effect which prevents overheating or otherwise adversely affecting the fluid in the fluid chamber.
  • the first and second fluid lines advantageously open into the fluid chamber in the edge area of the membrane, wherein in the preferred embodiment, with a plurality of first and a plurality of second fluid lines, first and second fluid lines advantageously follow one another alternately along the circumference of the membrane.
  • the valve arrangement advantageously contains separate controllable valves both in the first and in the second fluid lines, wherein in the case of a plurality of fluid lines connected in parallel, preferably in each case a separate valve is arranged in a plurality of, in particular all parallel fluid lines.
  • the multiple valves in parallel fluid lines are simultaneously controlled individually or individually.
  • individually controllable valves in parallel fluid lines can be provided in an advantageous development, the flow resistance of the individual fluid lines and / or preferably the flow resistance of the open valves staggered to choose different.
  • the hydraulic fluid is an electrorheological fluid and the valves are designed as electrically controllable gap valves. guided, in which a flow channel as a narrow gap between two electrically insulated from each other insulated electrodes.
  • a flow channel as a narrow gap between two electrically insulated from each other insulated electrodes.
  • the flow channel between the electrodes is preferably designed as an annular gap.
  • the fluid chamber is preferably made flat, wherein the membrane and the chamber are advantageously rotationally symmetrical preferably round and the transverse extent in the surface of the membrane at least 10 times, in particular at least 20 times, preferably at least 30 times the mean chamber height in Direction of the surface normal of the membrane is.
  • the membrane is preferably metallic, in particular consisting of spring steel.
  • the thickness of the membrane is advantageously the same size at the edge and in the middle, and the membrane is preferably formed from a sheet metal blank. In a preferred embodiment, the thickness of the
  • Membrane in the buckling deformable region lying radially between the edge restraint and the vertex of the arch can be reduced at one or more radius sections, whereby stress peaks in the material of the membrane can be reduced during deformation.
  • the areas of reduced thickness are preferably formed rotationally symmetrical about a central axis of the membrane.
  • a force-transmitting element In order to couple a force-transmitting element to the membrane, it can have a breakthrough in the region of the vertex of the curvature, by which such a force-transmitting element is attached to the membrane via a fastening element located on the side of the fluid chamber of the membrane.
  • a solid wall of the fluid chamber opposite the membrane can have a depression in the area of the fastening element.
  • the fluid chamber can be closed on two opposite sides by a respective membrane. Under the pressure of supplied fluid, the two membranes bulge in the opposite direction.
  • the inherent elasticity of the membrane may be supported by a restoring force of an integrated in the actuator and / or an external spring element.
  • two fluid chambers are provided which are alternately pressurized with fluid and act on the same component in the opposite direction.
  • the two fluid chambers can be arranged in a fixed mutual connection in a common actuator housing.
  • the directions of the bulges of the two membranes are oppositely directed, in particular with mutually facing membranes of the two fluid chambers.
  • the two diaphragms are coupled via a common rigid element and connected to mechanical transmission means for transmitting the bi-directionally coupled by fluid force coupled movement of the membranes to a component to be vibrated to Rüttelmos-.
  • a guide for the lateral support of the imbalance mass, the vibrating plate, the vibration or a coupled with the movement of the component in the vertical movement relative to the Housing provided an actuator, such a guide can be designed in particular as a plain bearing, as a rolling bearing or preferably as a magnetic bearing.
  • a special guide within the actuator can be dispensed with.
  • FIG. 5 is a side sectional view of the actuator of FIG. 2,
  • FIG. 6 is an enlarged detail of FIG. 6,
  • FIG. 8 is a further sectional view with control valves
  • FIG. 10 is an enlarged detail of FIG. 10,
  • FIG. 13 shows the fluid system according to FIG. 12 for a flushing process
  • Fig. 14 is an assembly of parts of another advantageous
  • Fig. 15 the assembled actuator of FIG. 14 in an oblique view
  • FIG. 16 shows a first section through the actuator according to FIG. 15
  • FIG. 17 shows a further section through the actuator according to FIG. 15 and a hydraulic system
  • Fig. 18 is a sectional view of another advantageous embodiment of an actuator
  • Fig. 20 shows a detail of a molding machine with additional
  • Fig. 1 shows an oblique perspective view schematically a section of a molding machine for the production of concrete blocks by solidifying a concrete amount under the action of shaking movements.
  • a mold frame FR is arranged at a substantially constant height.
  • a mold insert FE is used interchangeable with several mold cavities.
  • a vibrating table arrangement RT with a stone board can be moved vertically by means of traversing devices VE between an upper position shown in the sketch, in which a stone board resting on the vibrating table arrangement RT closes the lower openings of the mold cavities of the mold insert FE, and a lowered position, on the other hand, in which the solidified concrete blocks including the stone board can be removed from the forming machine and a new stone board can be inserted.
  • An on-load device with a ballast basic body AK is vertically movably guided via vertical guides VF of the machine frame MR.
  • Devices for vertically moving the load-bearing device can be integrated in the vertical guides VF, for example in the form of magnetic linear drives, or can be in the form of common displacement devices, eg hydraulic lifting cylinders, which are not shown in FIG.
  • the printing plates DP dip into upper openings of the mold cavities of the mold insert FE and press on a concrete in the mold cavities.
  • the filling of the mold cavities of the mold insert FE is carried out at the raised position of the vibrating table arrangement RT as sketched and in relation to the outlined position of the Auflastvoriques raised position, wherein the pressure plates DP vertically enough from the upper Opened openings of the mold cavities are spaced to allow filling of mold cavities with humid concrete amount by means of a filling carriage.
  • the pressure plates DP are brought by lowering the Auflastvoroplasty in the upper openings of the mold cavities in the position sketched in Fig. 1.
  • the vibrating table arrangement RT is in the example outlined by means of the displacement device VE, which are advantageously designed as lockable hydraulic cylinder braced against the mold frame FR by the Rüttel- table arrangement RT is pressed with the stone board to the lower side of the mold insert and this in the recording supported vertically of the mold frame.
  • the type of bracing of the vibrating table assembly RT against the mold frame FR is not the subject of the present invention.
  • the croquttelaktuatoren RA force the mold frame and the tension of the vibrating table assembly on an oscillating vertical motion as a shaking movement.
  • the vibrating actuators RA are advantageously formed as hydraulically actuated actuators with fluid chambers, which are closed on at least one side by a flexible membrane.
  • the Garttelaktuatoren are advantageously designed in such a way that they can both exert an upward force on the mold frame FR and a vertically downward force.
  • the Rüttelaktuatoren RA are designed for bidirectional working. Particularly advantageous embodiment of such bidirectionally acting Hinttelaktuatoren are still explained in detail on subsequent figures.
  • FIG. 2 shows an oblique view of a particularly advantageous embodiment of a bidirectionally acting Studttelaktuators.
  • FIGS. 3 to 13 show different views of this preferred embodiment of a bidirectionally acting vibration actuator.
  • Fig. 2 the fully assembled Haittelaktuator is shown, which is an actuator housing with a base plate GP, a first middle part MG1, a second middle part MG2, a clamping ring KR2 and a Cover plate contains DP, which are firmly connected by multiple vertical screw.
  • recesses GA are provided, which reach up to the clamping ring KR2 and in which a mechanical transmission device for transmitting shaking movements is guided vertically displaceable.
  • the mechanical transmission device consists in the example sketched out of a vibration sensor SA, connecting bolt VB and a shaker connection plate RP, which are screwed tightly together and can carry out vertical vibration movements in the direction of the arrow relative to the actuator housing.
  • a connection TA is provided for a fluid line leading from the vibration actuator to a fluid sink, in particular a fluid tank, at a lower pressure than the fluid supply.
  • a first flexible membrane ME1 of a first fluid chamber, between the clamping ring KR2 and the cover plate DP, a second flexible membrane ME2 of a second fluid chamber is indicated.
  • Fig. 3 shows the Rüttelaktuator of FIG. 2 in a partially disassembled state.
  • the base plate GP are as recesses against a bearing plane for the membrane ME1 the fluid chamber FK1 with circular boundary and in this a recess BT1 and fluid-conducting channels PK for supplied fluid and TK for fluid to be derived recognizable.
  • the base plate shows connection structures VG for screwing the various housing parts and mounting structures BV for mounting the actuator housing on a base.
  • the cover plate DP with the clamping ring KR2 and the membrane ME2 between them and the Rüttelan gleichplatte RP and the connecting pin VB are drawn from the rest of the housing with middle parts MG1 and MG2 lifted.
  • the given view of the upper surface of the second housing middle part MG2 shows the upwardly open recesses GA, in which side arms of the vibration sensor SA are guided vertically displaceable.
  • Portions of control valves PV2 for supplying fluid into the upper fluid chamber and control valves TV2 for discharging fluid from the upper fluid chamber protrude beyond the upper abutment surface of the second housing middle part MG2.
  • These sections of the control valves engage in corresponding bores of the clamping ring KR2, as can be seen in detail from the following figures.
  • the vibration sensor SA has in the sketched embodiment, a central strut and four guided in the recesses GA side arms and is guided in this way reliably within the housing and centered.
  • the vibration sensor is considered to be dimensionally stable in itself.
  • the structure of the vibration absorber SA may be stiffened by gusset plates between the central strut and side arms.
  • a fastening element BE2 is sketched, which serves for fastening the vibration sensor in a breakthrough through the second membrane ME2 in the middle.
  • the division in Fig. 3 does not correspond to the assembly order.
  • FIG. 4 shows another partial arrangement of elements of the vibrating actuator according to FIG. 2.
  • the middle parts MG1, MG2 are omitted.
  • the mechanical transmission device with vibration sensor SA, connecting bolt VB and Rüttelan gleichplatte RP is drawn completely composed.
  • the first membrane ME1 is sketched resting on the contact surface of the base plate GP. Breakthroughs PB for supplying fluid into the channels PK and the first fluid chamber bounded by the membrane ME1 and openings TB for discharging fluid via the channels TK from the fluid chamber can be seen in the membrane ME1.
  • the central strut ZS of the vibration sensor SA is connected to the membranes ME1 and ME2 via fastening elements, which are not visible in this view.
  • the transmission device engages around the cover plate DP by means of the connecting bolts VB.
  • Fig. 4 does not correspond to the sequence of assembly and is merely illustrative of the mutual assignment of various components.
  • FIG. 5 shows a first section through the housing of the Klattelaktuators of FIG. 2.
  • the transmission device is not cut cut in this sketch. A facing the viewer connecting pin of the transmission device is not shown.
  • the fluid chamber FK1, FK2 can be seen, which have a diameter DK in the surface of the membranes.
  • the central strut of the vibration sensor is firmly bolted to both membranes via fastening elements BE1 and BE2 in the region of the vertexes of the bulges of the membranes.
  • the membranes ME1, ME2 extend beyond the diameter DK of the fluid chambers and are firmly clamped in these protruding sections between housing parts of the actuator housing.
  • the fluid chambers show in the region of the fasteners depressions, in which the fasteners can dip.
  • the height of the fluid chambers in the direction of the surface normal of the membranes or in the region of the fastening elements, the distance between the fastening element and the course of the recess in the solid wall of Fluidkam- is small compared to the diameter of the fluid chambers.
  • the diameter of the fluid chambers is at least 10 times, in particular at least 20 times, preferably at least 30 times, the mean chamber height in the direction of the surface normals of the membranes.
  • the two fluid chambers can be dimensioned differently, but are preferably constructed the same as outlined the same.
  • ring pipes PR for the supply of fluid and TR for the discharge of fluid can be seen.
  • the ring lines are advantageously designed as circumferential grooves in the contact surfaces of the first and second housing middle part MG1, MG2.
  • Fig. 6 shows a further sectional view of the Haittelaktuators according to Fig. 2, in which case the cutting plane is guided through the terminals TA and PA and the center axis of the vibration sensor SA. In this illustration, the vibration sensor SA is shown cut. Recognizable again is the structure of the fluid chambers. From the enlarged section of Fig. 6 of FIG. 7, the fluid connections PA for the supply and TA for the discharge of fluid from the ring lines PR and TR can be seen in detail.
  • Fig. 8 shows a further sectional view of the Haittelaktuators of FIG. 2, in which case the cutting plane through the control valves PV1 and PV2 for the control of the supply of fluid in the fluid chambers FK1 and FK2 is set.
  • the control valves PV1 in the first housing middle part MG1 for supplying fluid into the first fluid chamber FK1 and the control valves PV2 in the second housing middle part MG2 and also guided through the clamping ring KR2 connect the feeding ring line PR with the feeding channels PK in the base plate GP or the cover plate DP.
  • the individual control valves PV1, PV2 are shown as equally dimensioned in the sketch shown, but may also have different dimensions.
  • the cutting plane is set by control valves TV2 for the controlled discharge of fluid from the fluid chambers.
  • the control valves TV2 connect the outgoing channels TK in the baseplate GP and the coverplate DP via the openings TB in the membranes to the ring line TR in the second middle housing part MG2.
  • the ring line TR is arranged offset radially against the ring line PR.
  • 11 shows in detail the fluid-conducting connection from the first fluid chamber FK1 via the outgoing channel TK to a control valve TV1.
  • FIG. 12 schematically shows a complete fluid line system of the vibrating actuator according to FIG. 2, which has a fluid line connection PA for the supply of fluid via the ring line PR and the control valves PV1, PV2 and the channels PK into the fluid chambers FK1 and FK2, respectively a fluid line Connection port TA for discharging fluid from the fluid chambers FK1 and FK2 via the outgoing channels TK, the control valves TV1, TV2 and the ring line TR comprises.
  • control valves PV1 are operated in push-pull with the control valves PV2 and in common mode with the control valves TV2, which are in turn controlled in push-pull with the control valves TV2.
  • the fluid chamber FK1 and the fluid chamber FK2 are alternately pressurized with fluid under high pressure via the valves PV1 and PV2 and the fluid chambers FK2 and FK1 are alternately pressure-relieved via the valves TV2 and TV1.
  • the alternating bulging of the membranes ME1 or ME2 causes an oscillating movement of the vibration sensor SA relative to the housing of the actuator, which can be transmitted via the transmission devices to a component to be vibrated to vibrate movements.
  • the connection of the actuator housing to the machine frame and the connection of the vibrating connection plate RP to the assembly to be shaken are interchangeable.
  • a displacement or position sensor which is not included in the preceding figures can advantageously be part of a control circuit and enable a targeted path-time control of the vibration sensor or the bulging of the individual diaphragms.
  • a displacement or position sensor can also serve to define a specific reference position of the vibration sensor. This can also be advantageous in a Rüttelak- tuator with only one fluid chamber.
  • FIG. 12 flow directions of the fluid through open valves TV1 and PV2 as arrows are shown for an operating cycle with pressurization of the second fluid chamber FK2 and depressurization of the first fluid chamber FK1 located. Locked valves PV1 and TV2 are shown with a broken line.
  • Fig. 13 shows the fluid conduit system in a state in which all the valves TV1, TV2, PV1, PV2 are opened and fluid flows through both fluid chambers FK1, FK2, whereby occasional or regular purging of the fluid chambers to prevent deposits is possible.
  • FIG. 14 an assembly drawing of a further advantageous embodiment is outlined, which is characterized in particular by a different valve arrangement and a shorter in the direction of movement design.
  • Fig. 15 shows the parts of Fig. 14 in the assembled state, wherein a second valve block VBA is omitted for the representation of the fluid outlets.
  • FIGS. 16 and 17 show sectional views of the actuator of FIG. 15 in sectional planes through the fluid conduits leading to and exiting from (FIG. 17) and through the side arms SAA (FIG. 16).
  • a valve arrangement may, for example, contain one or more valve blocks VBE, VBA of conventional design of hydraulic control valves which supply fluid supplied from a fluid source under high pressure alternately to one of the two fluid chambers KL1 or KL2 or fluid alternately from one of the two fluid chambers derive a fluid sink lower fluid pressure
  • VBE valve blocks
  • VBA of conventional design of hydraulic control valves which supply fluid supplied from a fluid source under high pressure alternately to one of the two fluid chambers KL1 or KL2 or fluid alternately from one of the two fluid chambers derive a fluid sink lower fluid pressure
  • the movement of the membranes under the action of the pressurized fluid is transferred to a vibrating plate RPL via a vibration sensor SAL which is firmly coupled to both membranes and has outwardly projecting arms SAA. wherein in the example sketched a coupling of the vibrating plate to the vibration sensor via vertical extensions PF of the vibrating plate takes place in place of the connecting bolt VB.
  • the sketched further embodiment includes, in the first embodiment of the kind described in FIGS. 2 to 13, a base plate GPL and a cover plate DPL which respectively have recesses as chamber walls of a first fluid chamber KL1 and a second fluid chamber KL2 and bores to fluid inlets E1, E2 and fluid outlets A1, A2 have.
  • the fluid chambers are covered by flexible membranes ML1 and ML2, which are pressed and sealed via first and second spacers DK1, DK2 as middle parts by bolts SBL against the base plate GPL or cover plate DPL.
  • the membranes ML1 and ML2 are in their middle via a connecting element, such.
  • the inherently rigid vibration receiver projects with arms pointing outward from a central body through recesses AB of the spacer body DK1 and is vertically movable therein within the intended shaking movement, which is indicated in FIG. 16 by the column SSL
  • fluid is supplied under high pressure from a fluid source to the inlet E1 and thus to the first fluid chamber KL1 whose fluid outlet A1 is blocked by the second valve block VBA.
  • the inlet E2 to the second fluid chamber is separated from the fluid source by the first valve block VBE and the outlet A2 is opened to the fluid sink via the second valve block VBA.
  • the first and second diaphragms bulge while the chamber volume of the chamber is increased.
  • both valve blocks are switched so that fluid from the high pressure fluid source is supplied to the second fluid chamber KL2 via the now open inlet E2 and fluid is discharged from the first fluid chamber KL1 to the fluid sink Inlet E1 and outlet A2 are locked so that the membranes move down with the vibration sensor.
  • the valve blocks can contain valves with simple switching behavior or, for further control possibilities, regulating valves (servo valves).
  • FIG. 17 in addition to the section through the fluid lines of the vibration actuator according to FIG. 15 and FIG. 16, a hydraulic system is schematically sketched.
  • a fluid is provided at high pressure on an output line QV of the hydraulic source HQ by a hydraulic source HQ, in particular a motor-operated hydraulic pump.
  • a reservoir SP for the hydraulic fluid at the outlet of the hydraulic source ensures a constant even with irregular fluid removal pressure.
  • the output of the hydraulic source HQ is directed to a servovalve SW, which is connected to two fluid input terminals E1 and E2 of the Rüttelaktuators via bidirectional lines.
  • the servo valve device SVV which may be part or substitute for the valve block VBE according to FIG. 15, is actuated by a control device HS.
  • fluid pressures PK1 and PK2 can be variably controlled at the hydraulic connections E1 and E2, respectively, of the vibration actuator, wherein in particular the pressures PK1 and PK2 are different and, in the typical operating mode of the vibration actuator, in phase opposition.
  • the outputs A1 and A2 of the fluid chambers KL1 and KL2 in connection with a switchable shut-off valve SCV individually opened or closed become.
  • the control of the switching valve SCV also takes place via the control device HS.
  • the individual chambers KL1 and KL2 can be depressurized via the valve arrangement VBA and the switching valve, the hydraulic fluid being conducted via a return line RL to the return port QR of the hydraulic source.
  • the opening of the outputs A1 and / or A2 through the valve assembly VBA and the switching valve assembly SCV flushing both chambers.
  • the servo valve arrangement SVV can supply or remove hydraulic fluid under defined pressure PK1 or PK2 from each of the two fluid chambers KL1 or KL2 via their hydraulic inlet E1 or E2. Extracted hydraulic fluid is also supplied to the return port QR of the hydraulic source HQ.
  • the individual pressures PK1 and PK2 at the inputs E1 and E2 are monitored by pressure sensors and evaluated in the control device HS, via these pressures a defined time course of the pressurization and about a defined time course of the movement of a coupled to the vibrating plate RPL load LA by the control device HS can be specified.
  • the control of the movement of the load can take place via a control circuit, for which a movement sensor is connected to the load LA or the vibrating plate RPL, which measures the position and / or acceleration of the load and transmits it to the control device HS.
  • FIG. 18 shows, in a view corresponding to FIG. 17, a further advantageous embodiment of a vibrating device, in which, essentially in contrast to the vibrating device according to FIG. 17, only one fluid chamber KL1 is provided.
  • the membrane ME1 closing off at the top can bulge upwards and the vibration sensor SAL fastened to this membrane can be displaced upwards.
  • the plate spring package TF is supported for example on a cover plate DPF, which is rigidly connected to the base plate GPL.
  • the disc spring assembly may also be provided another spring arrangement.
  • the disc spring package has the advantage that a high return force can be applied over a short deflection path and the inertia of the spring arrangement is very low.
  • the embodiment with only one fluid chamber and a restoring spring arrangement is particularly advantageous in cases where only a defined, optionally variable and / or controllable by a control device after a particular time course acceleration force is needed upwards and for the downwardly accelerated restoring force a spring arrangement such
  • the cup spring package TF possibly in conjunction with a downwardly acting weight of a fastened on the vibrating plate RPL load sufficient.
  • a position sensor PSE is connected to the vibrating plate RPL in FIG. 18, which determines the varying distance of the vibrating plate RPL with respect to the cover plate DPF or another reference fixed with respect to the cover plate DPF during a shaking process.
  • a predeterminable sequence of movement of the vibrating plate RPL relative to the cover plate DPF can be precisely adjusted in a particularly advantageous embodiment and in particular a specific time profile with, for example, varying frequency and / or amplitude can be specified.
  • a further advantageous embodiment is outlined in FIG. 19.
  • the vibrator is not designed to generate a force between the housing of the Hinttelaktuators and a displaceable thereto vibrating plate and connected to this load, but the vibrator is designed as unbalance vibrator with linearly displaceable vibrating compound MV.
  • the vibrating device according to FIG. 19, like the vibrating device according to FIG. 18, is equipped with only one fluid chamber KL1, on the upper diaphragm of which the imbalance mass MV is fastened. The acceleration of the unbalanced mass MV upwards again takes place by applying the fluid chamber KL1 with fluid under increased pressure and counter to a return spring in the form of a plate spring package TF.
  • a guide not shown in the sketch for lateral support of the unbalanced mass is provided in its vertical movement within the housing, which can be designed in particular as a slide bearing, as a rolling bearing or preferably as a magnetic bearing.
  • Such a guide can also be provided in the other embodiments of the actuator for the vibrating plate, the vibration sensor or a coupled with their movement component Especially in cases where a connected to the vibrating plate load, in particular a mold frame or a mold in a machine frame in a Vertical guide is performed, can account for a special leadership within the actuator.
  • a position sensor MSE is provided, which determines the distance between the housing of the Hinttler issued and the relative to this moving unbalanced mass MV mediates and thus allows control of a defined movement of the unbalanced mass MV relative to the housing by controlling the pressure curve of the fluid in the fluid chamber KL1.
  • FIG. 20 schematically shows an example of this.
  • the mold frame FR is in turn by means of Rüttelaktuatoren RA, which are supported against the machine frame or a foundation, stimulated to vertical jarring movements.
  • An additional support element AE in the form of an air spring bellows exerts a vertically supporting force on the mold frame. By feeding or discharging compressed air into the air bag AE, the vertical position of the mold frame can be varied.
  • the additional support member AE is set in the form of the air spring bellows so that the Haittelaktuatoren, in the example of the preceding figures, the vibration sensor SA the Haittelaktuatoren occupy a reference position, preferably a Referenzpositi- on, in which the total weight of the mold frame, vibrating table assembly, mold insert is intercepted with concrete amount and Auflastvorides by the additional support device AE and the Trottelaktuatoren are in a rest position corresponding to pressureless fluid in both fluid chambers.
  • the vibratory actuators can also be provided for other purposes than in molding machines for the production of concrete blocks or elsewhere in such molding machines, in particular advantageously e.g. - Test bench tests: (shaker, hydropulse actuator, fatigue testing, materials testing)

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Ceramic Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Reciprocating Pumps (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

L'invention concerne un dispositif vibreur équipant un dispositif destiné à la réalisation d'agglomérés de béton par compactage d'un mélange de béton dans un moule (FE) soumis à des vibrations. Selon l'invention, on utilise un actionneur hydraulique (RA) comportant une chambre de fluide (FK) délimitée par une membrane souple (ME). Dans un mode de réalisation préféré, l'invention concerne un actionneur approprié.
EP07728227A 2006-04-22 2007-04-18 Dispositif de réalisation d'agglomérés de béton au moyen d'un dispositif vibreur et d'un actionneur Withdrawn EP2012988A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610018810 DE102006018810A1 (de) 2006-04-22 2006-04-22 Vorrichtung zur Herstellung von Betonformsteinen mit einer Rütteleinrichtung und Aktuator
PCT/EP2007/053765 WO2007122152A1 (fr) 2006-04-22 2007-04-18 Dispositif de réalisation d'agglomérés de béton au moyen d'un dispositif vibreur et d'un actionneur

Publications (1)

Publication Number Publication Date
EP2012988A1 true EP2012988A1 (fr) 2009-01-14

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EP07728227A Withdrawn EP2012988A1 (fr) 2006-04-22 2007-04-18 Dispositif de réalisation d'agglomérés de béton au moyen d'un dispositif vibreur et d'un actionneur

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EP (1) EP2012988A1 (fr)
DE (1) DE102006018810A1 (fr)
WO (1) WO2007122152A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008011272A1 (de) * 2008-02-26 2009-08-27 Institut für Fertigteiltechnik und Fertigbau Weimar e.V. Betonsteinfertiger mit harmonischer Vibration durch Formerregung
NL2005171C2 (nl) * 2010-07-29 2012-01-31 Boer Staal Bv Den Inrichting voor het verdichten van korrelvormige massa zoals betonspecie.

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
FR2067955A5 (fr) * 1969-11-24 1971-08-20 Prodilog
US3653296A (en) * 1969-12-12 1972-04-04 John H Ransom Lab Inc Fluid powered oscillatory drive
DE2451228A1 (de) * 1974-10-29 1976-05-06 Schneider Co Optische Werke Elektrohydraulischer vibrator
SU856796A1 (ru) * 1979-11-16 1981-08-23 Рижский Ордена Трудового Красного Знамени Политехнический Институт Устройство дл уплотнени бетонных смесей в форме
SU1556765A1 (ru) * 1988-06-06 1990-04-15 Винницкий политехнический институт Гидравлический вибратор
DE19921145B4 (de) * 1999-05-07 2008-01-10 Kobra Formen Gmbh Rüttelantrieb für eine Form
DE19940119A1 (de) * 1999-08-24 2001-03-01 Kobra Formen & Anlagenbau Gmbh Rüttelantrieb

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007122152A1 *

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DE102006018810A1 (de) 2007-10-25
WO2007122152A1 (fr) 2007-11-01

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