WO2007122152A1

WO2007122152A1 - Device for producing moulded concrete blocks comprising a vibration device and actuator

Info

Publication number: WO2007122152A1
Application number: PCT/EP2007/053765
Authority: WO
Inventors: Rudolf Braungardt; Holger Stichel; Swen Dietrich
Original assignee: Kobra Formen Gmbh
Priority date: 2006-04-22
Filing date: 2007-04-18
Publication date: 2007-11-01
Also published as: DE102006018810A1; EP2012988A1

Abstract

The invention relates to a vibration device in a device for producing moulded concrete blocks by compacting a concrete mixture in a mould (FE) and by vibrating said mould. According to the invention, a hydraulic actuator (RA) comprising a fluid chamber (FK), which is delimited by a flexible membrane (ME), is used. A preferred embodiment for an actuator suitable for said invention is also described.

Description

Apparatus for the production of concrete blocks with a vibrator and actuator

The invention relates to a device for the production of concrete blocks with a vibrator and a suitable for a vibrator actuator.

Economically-favorable devices for the production of concrete blocks use vibrating devices to stimulate a vibrating table arrangement to essentially vertical shaking movements. In a positioned on the Rütteltischanordnung form with one or more mold cavities a concrete amount is filled, to which the Rüttelbewegungen the vibrating table assembly are transmitted, whereby this is solidified into dimensionally stable concrete form bricks.

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.

To stimulate the Rüttelbewegungen the vibrating table assembly unbalance shaker with rotating shafts are in use, such. As described in WO 2004/069504 A1.

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.

Solutions according to the invention are described in the independent claims. The dependent claims contain advantageous refinements and developments of the invention.

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 Auflasteinrichtung 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 Aufwölbbarkeit the membrane amplitude of the shaking motion is favorably correlated in this application with the applied Rüttelkraft 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.

Preferably, 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 Rüttelanordnung 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. Preferably, 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.

In a first advantageous embodiment, 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

Directions against a stop. A stop may additionally or alternatively also be provided for the movement of the mold relative to the machine frame.

In a preferred embodiment, 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. In a preferred embodiment, 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. As a result, the Rüttelaktuatoren 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. be designed as a body made of elastomer, as air spring bellows or similar. In a particularly advantageous embodiment, the support elements are variably adjustable. In particular, 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. For adjustment to the reference position, 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. Alternatively or in addition to the adjustment of the additional support elements, 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.

During the shaking movement, it can be advantageously provided that 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. Advantageously, 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.

Several 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. In a preferred embodiment, 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. As a result, 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. In particular, with 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.

In a particularly advantageous embodiment, 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. By an electric field directed predominantly transversely to the flow direction, the flowability of the electrorheological fluid in the gap can be reduced so much that the valve can be regarded as blocking. The flow channel between the electrodes is preferably designed as an annular gap. Such valves in conjunction with electrorheological fluid in hydraulic systems are known per se, for. From a project on highly dynamic electrorheological servo drives at the RWTH Aachen by Dipl.-Ing. Michael Zaun as a clerk.

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.

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.

To restore the bulged membrane under the action of the fluid, 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. In a particularly advantageous embodiment, two fluid chambers are provided which are alternately pressurized with fluid and act on the same component in the opposite direction. In particular, the two fluid chambers can be arranged in a fixed mutual connection in a common actuator housing. Advantageously, the directions of the bulges of the two membranes are oppositely directed, in particular with mutually facing membranes of the two fluid chambers. Advantageously, 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 Rüttelbewegungs-.

In a preferred embodiment, 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. In particular, in cases where a load connected to the vibrating plate, in particular a mold frame or a mold is guided in a machine frame in a vertical guide, a special guide within the actuator can be dispensed with.

The invention is illustrated below with reference to preferred embodiments with reference to the figures still in detail. Showing:

1 is a schematic section of a molding machine,

2 shows a preferred exemplary embodiment of a bidirectionally acting actuator in an oblique view,

3 is a partially disassembled view of the actuator,

4 coupled fluid chambers without connecting housing part,

5 is a side sectional view of the actuator of FIG. 2,

6 is a side sectional view in another sectional plane,

7 is an enlarged detail of FIG. 6,

8 is a sectional view with control valves,

9 is an enlarged detail of FIG. 8, 10 is a further sectional view with control valves,

11 is an enlarged detail of FIG. 10,

12 shows a complete fluid line system within the actuator housing,

13 shows the fluid system according to FIG. 12 for a flushing process

Fig. 14 is an assembly of parts of another advantageous

Execution of an actuator

Fig. 15 the assembled actuator of FIG. 14 in an oblique view

16 shows a first section through the actuator according to FIG. 15

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

19 is a sectional view of an unbalance vibrator

Fig. 20 shows a detail of a molding machine with additional

support elements, 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.

In a machine frame MR, a mold frame FR is arranged at a substantially constant height. In a receptacle of the mold frame FR from below 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. On the main body AK of the Auflastvorrichtung a the respective mold insert FE associated and adapted pressure plate assembly is attached, which carries on stamps ST printing plates DP. 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 Auflastvorrichtung 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. After filling the mold cavities, the pressure plates DP are brought by lowering the Auflastvorrichtung 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.

An excitation of the vibrating table arrangement RT to vertical Rüttelschwingungen, which are transmitted in the concrete amount in the mold cavities of the mold insert FE, takes place in the sketched embodiment indirectly by excitation of the mold frame FR to vertical Rüttelschwingungen. The mold frame FR is centered horizontally in the machine frame MR for this purpose and vertically movable in the amount of vertical shaking movements.

To stimulate the mold frame FR to vertical shaking movements several Rüttelaktuatoren RA are supported on stable supports RS against the machine frame or a foundation supporting this.

The Rüttelaktuatoren 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. In the example shown, the Rüttelaktuatoren 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 Rüttelaktuatoren are still explained in detail on subsequent figures.

Instead of bidirectionally operating Rüttelaktuatoren RA and Rüttelaktuatoren can be provided, which exert only vertically upward forces on the mold frame FR. A vertical return of the mold frame can be done solely by the weight of FR frame, Rüttel- table arrangement RT, mold insert FE with concrete amount and Auflastvorrichtung with pressure plate assembly. In yet another embodiment may be given additional restoring elements, in particular spring elements between the machine frame and the mold frame or within the actuator, which exert an additional downward force on the mold frame FR.

Fig. 2 shows an oblique view of a particularly advantageous embodiment of a bidirectionally acting Rüttelaktuators. The following FIGS. 3 to 13 show different views of this preferred embodiment of a bidirectionally acting vibration actuator.

In Fig. 2, the fully assembled Rüttelaktuator 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. In the second housing middle part MG2 of the actuator housing housing 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 PA for a supply of hydraulic fluid under high pressure from a fluid source, in particular a pump, is provided in the first housing middle part MG1. In the second housing middle part MG2, 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. Between the base plate GP and the housing middle part MG1, 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. In 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 Rüttelanschlussplatte 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. At the upper end of the central strut of the vibration sensor, 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. In this illustration, the middle parts MG1, MG2 are omitted. The mechanical transmission device with vibration sensor SA, connecting bolt VB and Rüttelanschlussplatte 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. Also Fig. 4 does not correspond to the sequence of assembly and is merely illustrative of the mutual assignment of various components.

5 shows a first section through the housing of the Rüttelaktuators 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.

In the partially sectioned view according to FIG. 5, 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. In an advantageous embodiment, 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.

In the cut part of the view of the housing, 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 Rüttelaktuators 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 Rüttelaktuators 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.

From the enlarged section IX of Fig. 8 of FIG. 9, the confluence of the valves PV1 through the opening PB in the membrane ME1 in the channel PK can be seen. The sketch does not take into account the structure of the control valves preferably shown as annular gap valves in detail. The representation of the control valves is only to be understood schematically. From Fig. 9, the attachment of the center strut of the vibration sensor SA in a central opening MB of the membrane ME1 by means of the fastener BE1 recognizable. For this purpose, for example, a threaded rod or a bolt with terminal threads can be guided through a hollow central body of the vibration sensor. In Fig. 9, the dimension HK is entered for the chamber height.

In a further sectional view through the Rüttelaktuator of FIG. 2 of FIG. 10, 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.

In operation, the 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. As a result, 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.

In addition, in the actuator housing, 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. Such 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.

In 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.

In 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 In order to achieve a flushing fluid flow, fluid inlets E1 and E2 and fluid outlets A1 and A2 are advantageously provided separately at the fluid chambers.

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. B. a bolt BBL firmly together and connected to a clamped between the two membranes vibration sensor SAL. 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.

In operation, in a first portion of a cycle of periodic vertical shaking movement via the first valve block VBE 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. At the same time, 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. As a result, the first and second diaphragms bulge while the chamber volume of the chamber is increased. Most fluid chamber KL1 and reduction of the chamber volume of the second fluid chamber KL2 while moving the vibration sensor SAL upward. For a second portion of a cycle of periodic shaking motion, 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. As is indicated schematically, the valve blocks can contain valves with simple switching behavior or, for further control possibilities, regulating valves (servo valves).

In 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. In this case, 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. By means of the servo valve device SVV, 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. On the one hand, 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. On the other hand can be done through 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. By pressurizing this fluid chamber KL1, the membrane ME1 closing off at the top can bulge upwards and the vibration sensor SAL fastened to this membrane can be displaced upwards. It is essential that the shift against one down resetting spring force takes place, which is advantageously applied in the example shown by a cup spring package TF. The plate spring package TF is supported for example on a cover plate DPF, which is rigidly connected to the base plate GPL.

Instead of 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 For example, the cup spring package TF, possibly in conjunction with a downwardly acting weight of a fastened on the vibrating plate RPL load sufficient.

As a further special feature, 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. With the measurement signal of the position sensor, 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. In this embodiment, the vibrator is not designed to generate a force between the housing of the Rüttelaktuators 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. By a vibrational motion imposed on the unbalanced mass MV relative to the housing of the vibrator formed by the base plate GPL and cover plate DPM, the center of gravity of the entire vibrator is periodically displaced and this center of gravity displacement for unbalance vibrators is commonly transmitted to an object to which the vibrator is attached. In a preferred development, 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.

In the embodiment of FIG. 19, in turn, a position sensor MSE is provided, which determines the distance between the housing of the Rüttlereinrichtung 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.

In the example outlined in FIG. 19, it is provided as a further special feature that the movement of the imbalance mass downwards and / or upwards, d. H. in the direction of the fluid chamber and / or is limited away from this by stopping the unbalanced mass MV, the fastener with which the unbalanced mass is attached to the membrane, or other with the movement of the unbalanced mass MV fixedly coupled element to a lower stop surface FUA or an upper stop surface FOA. This causes in the respective direction of movement of the unbalanced mass MV an abrupt termination of the movement and thus shocks in the Rüttelbewegung with respect to the fundamental frequency of the movement of the unbalanced mass MV higher harmonic components.

The detection of a reference position of the vibration sensor or the membrane may be particularly advantageous in a molding machine, which has additional, adjustable support elements for the Rüttelaktuatoren to Rüttelbewegatoren to be stimulated module. 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. After filling the mold cavity of the mold insert FE with concrete amount and lowering the Auflastvorrichtung with in the upper openings of the mold cavities dipping pressure plates DP, the additional support member AE is set in the form of the air spring bellows so that the Rüttelaktuatoren, in the example of the preceding figures, the vibration sensor SA the Rüttelaktuatoren 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 Auflastvorrichtung by the additional support device AE and the Rüttelaktuatoren 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)

- automotive industry, mechanical engineering, aerospace: vibration control, damping, vibration damping, active chassis, replacement for springs (eg gas springs), driving element - medicine: production of pharmaceutical products, mixing of chemical components (liquid, solid)

- Food industry: food production

- construction industry: manufacture of concrete products, compaction of concrete or concrete-like products - chemical industry: mixing of various components (e.g., polyol and isocyanate)

The features mentioned above and in the claims as well as the figures which can be seen in the figures are both individually and in different ways. ner combination advantageously feasible. The invention is not limited to the exemplary embodiments described, but can be modified in many ways within the scope of expert knowledge. In particular, the number and arrangement of Rüttelaktuatoren can be optimized differently in each case. Deviating from the described rest position, reference positions can also be defined differently. Supporting devices may in particular also be mechanically vertically adjustable and designed differently, for example as a body made of elastomeric material. The mold frame can additionally be supported upwards by spring elements or damping elements. The Rüttelaktuatoren can also act as in known arrangements typically directly on the Rütteltischanordnung.

Claims

Claims:

1. Apparatus for the production of concrete blocks by solidifying a

Concrete quantities in a form, which has upwardly and downwardly open mold nests and during a shaking on a the

Mold cavity bottom rattle shakable pad rests and their upper openings are covered by immersing in the mold cavity pressure plates, with a vibrator with at least one actuator for generating shaking the shape with the concrete amount relative to a machine frame and closing the mold cavity bottom

Underlay, characterized in that the actuator has at least one fluid chamber, that at least one side of the fluid chamber is formed by a flexible membrane, which along its edge connected to an actuator housing and depending on the fluid pressure in the fluid chamber occupy different curvature positions, that the

Membrane in the region of the apex of the buckle is supported force transmitting and that the fluid chamber can be acted upon by a variable with a vibrating pressure of the fluid.

2. Apparatus according to claim 1, characterized in that in the region of the apex of the curvature of the membrane, a force-transmitting element is coupled to the membrane, which transmits a change in the curvature of the membrane in a movement of an imbalance mass relative to the mold.

3. A device according to claim 1, characterized in that in the region of the apex of the curvature of the membrane, a force-transmitting element is connected to the membrane, which is a change in the Wölbung transmits the membrane in a movement of the mold with the concrete amount relative to the machine frame.

4. Device according to one of claims 1 to 3, characterized in that a plurality of actuators are provided.

5. Apparatus according to claim 4, characterized in that the plurality of actuators are arranged laterally outside of a Steinfeldbereichs the mold.

6. The device according to claim 5, characterized in that the mold is divided into a mold frame and a replaceable held in this mold insert, and that the actuators between the molding machine and mold frame are arranged.

7. Device according to one of claims 1 to 6, characterized in that additional support means are provided which support the mold in a vertical rest position against the machine frame and allow a limited vertical deflection of the mold from the rest position sen.

8. Apparatus according to claim 7, characterized in that the additional support means are variably adjustable.

9. Device according to one of claims 1 to 8, characterized in that a spring arrangement is provided which counteracts an upward movement of the mold a progressively increasing restoring force.

10.Vorrichtung according to any one of claims 4 to 9, characterized in that the plurality of actuators are individually acted upon with different Fluiddrük- ken.

11.Vorrichtung according to one of claims 4 to 10, characterized in that the actuators each own control valve arrangements are assigned.

12. The device according to claim 11, characterized in that the control valve arrangements are integrated into the housing of the actuators.

13.Aktuator for producing a directed movement of a force-transmitting element with a substantially incompressible fluid-filled fluid chamber, which is acted upon by variable pressure of the fluid, wherein at least one side of the chamber is formed by a flexible membrane which along its edge with the housing of the actuator is connected and can assume different curvature positions depending on the fluid pressure in the fluid chamber.

14.Aktuator according to claim 13, characterized in that in the region of the apex of the curvature of the membrane, a force-transmitting element is coupled to the membrane.

15.Aktuator according to claim 13 or 14, characterized in that the expansion of the fluid chamber in the surface of the membrane at least the

10 times, in particular at least 20 times, preferably at least 30 times the mean chamber height in the direction of the surface normal of the membrane.

16.Aktuator according to any one of claims 13 to 15, characterized in that fluid supplying first lines and fluid discharging second lines open separately in the fluid chamber.

17.Aktuator according to one of claims 13 to 16, characterized in that a valve arrangement contains separately controllable valves in fluid supplying first lines and fluid discharging second lines.

18.Aktuator according to claim 17, characterized in that a plurality of individual valves connected in parallel with respect to the fluid flow are arranged in the first and / or the second lines.

19.Aktuator according to claim 18, characterized in that parallel-connected individual valves are constructed the same.

20.Aktuator according to claim 18, characterized in that parallel-connected individual valves are dimensioned differently and individually controllable.

21.Aktuator according to any one of claims 13 to 20, characterized in that the first and / or second lines open in an edge region of the membrane in the fluid chamber.

22. Actuator according to claim 21, characterized in that first lines and second lines are interleaved, in particular alternately arranged successively along the edge region.

23. Actuator according to one of claims 13 to 22, characterized in that a valve arrangement is integrated in the housing of the actuator.

24.Aktuator according to any one of claims 13 to 23, characterized in that the fluid is an electrorheological fluid.

25.Aktuator according to claim 24, characterized in that the valve arrangement contains electrically controllable gap valves.

26.Aktuator according to any one of claims 13 to 25, characterized in that a sensor arrangement for detecting the membrane curvature or a correlated size is provided.

27.Aktuator according to one of claims 13 to 26, characterized in that a control device controls the supply or discharge of fluid in a control loop with the signal of the sensor arrangement as actual size.

28.Aktuator according to one of claims 13 to 27, characterized in that the fluid chamber has two opposing membranes.

29.Aktuator according to any one of claims 13 to 28, characterized in that two separately controllable O fluid chambers are provided with the same movement means of the membranes.

30.Aktuator according to claim 29, characterized in that the membrane of the two fluid chambers are aligned facing each other.

31.Aktuator according to claim 29 or 30, characterized in that the two fluid chambers in opposite set working alternately with fluid under pressure can be acted upon.

32.Aktuator according to one of claims 29 to 31, characterized in that a common force-transmitting element is coupled to the membranes of the two fluid chambers in their respective vertex region of the curvature.

33.Aktuator according to any one of claims 29 to 32, characterized in that the first and second lines of the two fluid chambers are branched off from common supply and removal manifolds.

34.Aktuator according to claim 33, characterized in that the collecting lines contain ring lines.

35.Aktuator according to claim 34, characterized in that the ring lines are integrated into the actuator housing.

36. Apparatus according to claim 1 with an actuator according to one of claims 13 to 35.