ES2208464T3 - COMPRESSION INSTALLATION TO EXECUTE COMPRESSION PROCESSES ON GRINDING MATERIAL MOLDING BODIES. - Google Patents

Abstract

The invention relates to a compressing device for performing compression operations on shaped bodies made of grainy materials. The grainy materials, e.g. wet concrete mortar, are formed into shaped bodies in the mold recesses (106) of the mold boxes by applying vibrations and compression pressure. The invention aims at providing a low-noise low-energy consuming compressing device. In order to achieve a low-noise compression operation, said mold box (106) and vibrating table (124) are rigidly clamped together and harmonic vibrating operation of the vibrating mass-spring-system is ensured. Reduced energy use and effective compression is promoted by applying a vibrating frequency, said frequency being at least partially in the range of the resonance frequency of the mass-spring system. The invention also relates to improvements, more particularly with respect to the design of the exciter actuator and the arrangement thereof in the flow of forces involved. The device is used in concrete machines, foundry-casting machines and sinter-casting machines.

Description

Compression installation to execute processes of compression on molding bodies of granular materials.

The invention relates to an installation of compression operated with vibratory oscillations, to mold and compress molding materials into box molding recesses molding to form molding bodies, presenting the bodies of molding an upper side and a lower side, through which compression forces are applied. In this procedure the molding material is found, before the compression process in molding recesses, first as a volumetric mass of loose granular components that are joined by adhesion, which are not they mold during the compression process to form bodies of fixed molding until compression forces act on the side upper and lower side. The volumetric mass can be compound, by using the compression facility in machines for manufacturing finished concrete products (for example pavers), for example wet concrete mortar, in machines molding sand casting molding, and in machines molding of sintered parts of metal or other particles sintered particles. Through the use in molding machines of sintered parts, the compression installation can also be used to further compress parts molding bodies precast sintered.

Very especially the invention relates to those vibration compression installations, which work comparatively with low noise and reduced energy consumption for compression With this the low operating mode in Noise demands, on the one hand, that compression occurs through the application of fundamentally harmonic vibratory forces (sinusoidal) and, on the other hand, that the molding box is not present no remarkable own movement in relation to the other pieces constructive involved in the swing. To meet the requirement quoted lastly, the molding box must be able to look at a machine element of this type, which participates in the  vibratory oscillations As a machine element of this type it is suitable, for example, the oscillating table located below the molding box The requirement of a compression with low consumption of energy is met by means of which the system of participant dock-mass can range from, or at least in the vicinity of the resonance frequency f_ {o} of this system. The operating mode at resonance frequency leads with it, because of the so-called resonance effect by the very high accelerations that can be achieved with this, to very effective compression, if the body is also guaranteed molding is subjected to the high values derived from resonance operation for oscillatory acceleration.

The following state of the art is covered by EP 0 870 585 A1, and to describe the status General document DE 44 34 679 A1 is of interest. Because the structural establishment of an installation of compression of that genre, which should be associated with the invention, not is sufficiently represented in EP 0 870 585 A1, the structural characteristics are mentioned below fundamentals, included in the total force flow of a compression installation according to the invention, making reference to figure 2 of document DE 44 34 679 A1.

- On one side, for example on the upper side of the molding body 226, a press plate 250 is applied, to through whose pressing plate is applied to the molding body a special "average pressing force" called Simplified continuation also pressing force, even during the compression process, whose pressing plate can absorb vibratory forces applied from the other side (for example the bottom side), whose pressing plate can additionally also execute a translation movement with relationship to the other side of the molding body, and precisely with the purpose of monitoring during height reduction of compression during the compression process and, if necessary, also to execute the necessary movements usually during handling of the molding body or the molding box, whose pressing plate has been assigned to generate the force pressing and / or to execute a translation movement, a 264 pressing force installation (if necessary, operated hydraulically), and whose pressing plate transfers forces transmitted thereto to a frame 204 of the installation of compression. [The "average pressing force" special here applied is obtained, apart from a proportion of transmitted force constantly, especially of the impulses applied by the plate base 294 to the molding body and transmitted by the body of molding, and by its nature is not a static pressing force nor of continuous action].

- On the other side, for example on the lower side of the molding body 226, is applied by a base plate 294, in addition of the pressing force applicable by the pressing plate, also vibratory forces that are generated and applied by a motion generating system 240. Motherboard 294 is supported by its side again on the 211 oscillating table of the mass system oscillating

- Motion generating system 240 is formed by a 207-217 mass-spring system, which executes vibratory oscillations, whose mass is defined by a oscillating mass system 207, and by means of an installation of drive to generate the excitation forces to excite oscillations in the oscillating mass system 207 or in the system of spring-mass 207 + 217.

- The oscillating mass system 207 is supported by through springs 217 in the frame 204 (or on the ground, on the that loads the frame with its gravity). Docks 217 assume with it both the function of energy storage during the oscillatory operation of the oscillating mass system or the mass-spring system, as the function of the application of the pressing force. The oscillating mass system it comprises the masses of several constructive pieces that also oscillate, among others the oscillating table 21, the base plate 294, the molding box 213, molding body (s) 226 and components, fixed for rocking, of the fixing installation 298 for the molding box.

- Drive installation 215 is used to generate excitation forces with an excitation frequency preset and assumes the transmission of excitation energy, which It is used for commissioning and maintenance of oscillations of the mass-spring system, as well as for the transmission of compression energy and that energy, that is needed to cover various loss energies by friction. The excitation energy to be transmitted is subjected to the drive installation, by using an actuator of the exciter 238, at least once to an energy conversion, transforming a first form of energy into a second form of energy, whose second form of energy is transmitted as energy from excitation to the oscillating mass system.

- The application of vibratory forces or vibration pulses and pressing force superimposed on these are done in such a way that all forces or impulses of vibration are guided in a closed circuit of force flow, being linked to this force flow circuit (located between the pressing plate 250 and springs 217 of the mass system oscillating) frame 204 (and also the bottom). A particular feature worthy of the structural establishment of the compression system according to figure 2 of the DE document 44 34 679 A1 (whose meaning will be discussed again later) is that the forces applied by the oscillating table 211 are applied by two different paths (towards the frame). Springs 217 transmit the pressing force (average) and the superimposed dynamic mass forces of the system dock mass 207 + 217 and serve with it, at the same time, also as warehouses for intermediate conversion of kinetic energy of the oscillating system of oscillating masses 207 in elastic energy (and vice versa). Hydraulic pistons 228 They transmit the forces of excitement. The flow circuit of force is guided in this case, therefore, on the section between the swing table 211 and frame 204, for two paths parallel It can also be said that the forces applied through of the springs 217, on the one hand, and the excitation forces by other side are coupled parallel to the mass of the system of spring-mass 207 + 217.

- It is understood that at least some of the force transmission elements confined in the circuit force flow can form a system of spring mass with swing capacity, which It has at least a first resonant frequency f_ {o}, whose resonance frequency can be excited by certain excitation frequency of the installation of drive In the compression installation of document DE 44 34 679 A1 in Figure 2 (according to column 15, lines 3 to 16), The 207-spring mass-system is planned 217 is operated at its resonance frequency f_ {o}. Without However, it is not intended that the molding body 226 itself be also confined in the mass-spring system that It oscillates in resonance. Rather, compression of the molding body 226 by the action of the acceleration of shock, because of the shocks between the motherboard 294 and the bottom side of the molding body, or between the front side 272 of the plate pressing 250 and the upper side of the molding body (see for example column 3, lines 1 to 21). At the same time the body of molding 226 thereby executes free flight movements (column L) in relation to the oscillating mass system 207 (see for example column 9, lines 40 to 52 or claim 1). It is about so much, so to speak, of a "compression installation by vibration ".

The compression installation described by the Document DE 44 34 679 A1 differs from the genre of facilities compression, defined by EP 0 870 585 A1, also by the following:

- A compression class cannot be executed such, in which the mass of the molding body 226 itself is included in the force flow circuit of a system of mass-spring, which is operated at its frequency of resonance f_ {o}.

- Whenever the excitation force is generated by means of a directional vibrator 118, which acts as an actuator of the exciter, with two imbalance bodies, you get a good degree of efficiency during energy conversion on one's own actuator, however, the problem arises that the force of excitation cannot connect and disconnect with enough speed. Because during the exchange process, to perform inside the molding box, of the molding body finished by the loose molding in principle not compressed (for the following molding body to compress), the oscillating mass system 207 cannot be in motion, acceleration and braking of directional vibrator, which is usually needed afterwards, it would mean an unused downtime during the process of manufacturing and also an energy absorption.

EP 0 870 585 A1 describes a compression installation, in which the compression of a body of molding occurs, with the simultaneous application of a pressure of pressing and vibration, by means of oscillatory acceleration that runs sine. (The following designations of particularities are partly adapted to the terminology used in the explanation of document DE 44 34 679 A1). The pressure of Pressing can be controlled by a force installation of 6 hydraulic pressing, and vibration (oscillation) is executed by means of a mass-spring system hydraulic-mechanical, which is formed by the table oscillatory 1, the molding box 14, the molding body 17, the moving part 2 of the hydraulic exciter 3, and by means compressible hydraulic, which is between the movable part 2 of the exciter and drive means 7 (control body electromechanical).

Vibration during compression can run in such a way that the system of hydraulic-mechanical spring mass oscillate approximately or exactly at your resonant frequency f_ {o} and with it (through accelerations "a") generate inertia forces, which are superimposed on the pressing force generated by the installation of hydraulic pressing force 6. It also follows that here, unlike in the DE 44 34 679 A1, the pressing pressure (generated by installing hydraulic pressing force 6 and transmitted through the hydraulic cylinder 5, 6) is not a interrupted pressure between two oscillatory movements of the system hydraulic-mechanical mass-spring, but a pressure with a constant proportion and with a proportion changing superimposed on it.

In order to establish a comparison with relation to the force flow circuit also present in this compression installation, for the "resulting forces" (= pressing force + excitation forces + inertia forces dynamics) directed through the molding body 17 (mass 17), with the force flow circuit of the compression installation According to document DE 44 34 679 A1, reference is made to the Observation offered in EP 0 870 585 A1 (column 2, line 41) on a compression installation according to the document EP 0 620 090, in which the "resulting forces" directed at through the molding body 15 shown there (product 15) is apply to frame 1, 2 shown there. From here it can be deduced (which really is also something obvious to the technician) that the "resulting forces", directed at the installation of compression according to EP 0 870 585 A1 through the molding body 17, are thereby linked to a circuit of flow of force, that the "resulting forces" are applied, by one side through the pressing force installation 6 hydraulic, and on the other hand through the hydraulic exciter 3, to a "frame to accept". A force flow circuit that leads through the "frame to accept" must already be accepted by the rest, mandatory, because the hydraulic means compressible that gives body to the springs of the system mass-spring can only generate forces in a sense (pressure forces only). The inverse oscillation of the mass of the mass-spring system must be produced by Therefore, because of the high frequency of oscillation sought, apart from the gravity that also cooperates, additionally also by means of such a force, which is applied to the frame to through the molding body (and through the force installation 6 hydraulic press).

For the analysis of the operating mode of the compression installation according to EP 0 870 585 A1, is of special importance that (unlike the installation of compression according to DE 44 34 679 A1), the circuit of force flow only be guided on a single flow path of force, in the section between the oscillating table 1 and the "frame to accept ", whose force flow path leads through of the movable part 2, the compressible hydraulic means [which is disposed between the movable part 2 and the drive means 7 or the electro-hydraulic control element 7 (column 4, lines 18 to 21)] and exciter 3. The compressible hydraulic medium Participate here in two functions. On the one hand it is part of hydraulic exciter 3, and precisely by means of which the volume of the medium is driven, with the help of the drive 7 and of the control 11, with "hydraulic volumetric currents dynamics "(column 2, lines 38 to 40), whereby the moving part (2) of the exciter (3) is forced to execute oscillatory movements, and by means of which the oscillatory exciter movement and excitation forces (dynamic volumetric currents are liquid volumes added to the beat of the excitation frequency to the volume of the medium and extracted again). On the other hand the volume of the medium It is part of the mass-spring system hydraulic-mechanical to convert in oscillations to a resonance frequency f_ {o}, using the hydraulic means compressible as a spring (later also called spring main system).

Consequently, it can also be said that the force flow path of the "resulting forces" is guided between the molding body 17 and the "frame to be accepted" through the functional support "moving part 2", as a transmission part of force of the hydraulic exciter 3 (see also column 1, line 47 and 48), and through the middle functional support as springs of the hydraulic-mechanical mass-spring system, whose functional supports are connected by consecutive connection (serial connection) . This reference behavior is also expressed in claim 1 (column 6, lines 1 to 8), by means of which it is expressed that, on the one hand, the hydraulic-mechanical mass-spring system comprises the components "moving part 2" and "compressible hydraulic means" and that, on the other hand, the "compressible hydraulic means" is available between the "moving part 2" and the "drive 7" and, consequently, is therefore connected to the "moving part 2" . From this it can be deduced that the technical teaching made clear in EP 0 870 585 A1 is expressly based on a serial connection of the functional supports "construction piece that transmits excitation forces" (from the exciter for the generation of excitation forces ) and "mass-spring system springs that must operate at their resonance frequency", or even in an application of the excitation forces to the hydraulic means of the system springs.

On the disclosures of the invention in the EP 0 870 585 A1 the following may also be noted: with in order to cause and maintain the oscillations of the system hydraulic-mechanical spring mass is necessary excitation energy feed, in portions, to the beat of the excitation frequency. The energy to feed during the maintenance of the oscillations it covers with it the energy losses, which is extracted from the system by damping and friction, as well as through the need for energy of compression of the molding body. According to the ideas of the more general invention made patent should occur the excitation energy supply exclusively in form hydraulic, and precisely in such a way, that the excitation energy Hydraulically delivered directly to the elastic organ decisive (hydraulically configured) system. feeding in portions of the excitation energy is produced with it, by means that the energy portions are implanted by "dynamic hydraulic volumetric currents" to be generated discreetly and in line with the excitation frequency (column 2, lines 38 to 40) in the mass-spring system hydraulic-mechanical oscillatory. With it, the energy coupling to perform in portions can only occur logically through the "volumetric currents dynamic hydraulics "together with increasing pressure. deduces among other things from the observations in column 1, lines 33 to 50 and in column 3, lines 19 to 22, must be generated the "dynamic hydraulic volumetric currents" with the cooperation of a "control body electro-hydraulic "or a" servomechanism 7, 8 ". This special measure of the power coupling must therefore contain a certain importance of the invention, which however it is not described.

It can be established, with the critical analysis of operating mode of a compression installation according to the EP 0 870 585 A1, which precisely the application of the particularity of the serial connection of the functional supports above, or the application of the particularity of the application of the excitation forces to the hydraulic means of the main dock of the system, together with the chosen class and before quoted excitation energy coupling, houses some inconveniences and therefore are worthy of improvements, to in this way reduce energy consumption and also the costs of manufacturing.

The problems are further exacerbated by the following circumstances: as already stated in the document EP 0 870 585 A1 (column 3, line 54 to column 4, line 8), and as the technician also knows, frequencies can and should be generated very elevated in such a compression installation and, precisely at high frequencies, the resonance effect with its greater accelerations again. Without However, the dynamic "a" accelerations of the masses oscillating mass-spring system or forces Vibratory increase with the square of the frequency. These high dynamic forces of inertia still overlap the necessary pressing forces and excitation forces, and the high "resulting forces" that are deduced from this must driving through the hydraulic springs and, of this way, also through the exciter. This means practically for a compression installation according to EP 0 870 585 A1, that the "volumetric currents dynamic hydraulics "must be generated by the organ of 7 electro-hydraulic control or by the servomechanism, under the influence and burden of pressures caused in the middle by the "resulting forces", and naturally also under the load of high frequencies provided (up to 100 Hz). Of the problems that are hidden in the known state of the art according to EP 0 870 585 A1 and to be eliminated by the present invention, they are intended to be extracted continue and contemplate more accurately 3 problems.

a) How can it be verified for a system of mass-spring that is excited with an amplitude of pre-set excitation force, to generate forced amplitudes, with the use of the formula for amplification of amplitudes in dependence on the frequency of excitation (which can be represented as a diagram in the so-called resonance curve), for the excitation oscillatory in the range of the natural frequency a considerably lower excitation force, compared to the maximum value of the dynamic oscillatory force to be applied by means of the main dock of the system. Because it would be wanted claim the resonance effect, precisely also in the margin of the excitation frequency that can be traveled, and because the maximum values of the oscillatory forces dynamics increase with the square of the excitation frequency, very high maximum elastic forces are obtained, for which the suspension cylinder must be designed (with a maximum pressure preset), in relation to its cylinder cross section. With the dimension of the suspension cylinder sized for oscillatory forces is established however, with amplitude of preset oscillatory path, also the dimension of the Variable volumes needed and replaced for excitation. As a consequence of this technical behavior, the actuator of the exciter must be operated with a volumetric current unnecessarily large periodic variable, which as an inconvenience Not only does it mean a greater loss of energy, but also the need to size with the corresponding dimension the servo installation (for example a servo valve), to generate the Variable volumes

b) With the principle of using a volume of common liquid for the exciter actuator and for the spring main system fluidic another source is obtained, for a considerable loss of excitation power, of the following circumstances: in the first part of the oscillatory movement descending a variable volume must be released from the camera of the cylinder, and precisely until that point is reached approximately in the center of the entire oscillatory path descending, in which the compression chamber of the fluidic spring it must be closed tightly, so that then during the second part of the downward movement you can compress the compression volume and thereby materialize the elastic function The transition between the first part of movement to the second part of the movement occurs without However, precisely in a situation where the plunger of suspension has developed its maximum swing speed. By this, with a theoretically volumetric current control optimal, just before the transition between the first part of the movement and the second part of the movement, the current Volumetric periodic variable should adopt its maximum value, stop right after dropping to zero. This requirement cannot comply with real servo valves, especially high required frequencies (up to 100 Hz). Rather you need the controlled trancision between a maximum volumetric current and the zero volumetric current a certain time, in which reduces the cross section of servo valve control, settling, because of the maximum reached of the speed of oscillation in the servo valve, a high pressure that is throttled in the servo valve and represents a high loss of energy. The strangled energy during this process must be fed again during the oscillatory movement ascending to the oscillatory system, from the actuator of the exciter, in addition to the energy of excitation that must be fed in addition (= useful energy and others energy losses internal to the system), which apart from the loss of energy also means an increase in complexity of the device

c) Another unwanted effect is obtained from the use of a volume of common liquid for the actuator of the exciter and for the main fluidic spring of the system, that in the phase of the oscillatory path in which the common cylinder should act as an actuator of the exciter, during the necessary application of pressure on the volume of the liquid is also compresses the volume of the spring liquid, whereby in the volume of spring fluid, undesirably, develops an elastic function (power supply) and by means of which the pure actuation of force of the actuator, possible of the on the contrary, it is coupled to the elastic function of the main spring of the system. This coupling is unwanted, since among other things causes a phase shift, additional and also variable, between the excitation force and the oscillatory movement. Apart from this, by compressing the spring current volume, the variable volume to be replaced is increased by installation servo, which can be up to 50% of the variable volume only otherwise necessary and what causes losses for throttling, with a depression of exciter pressure not Completely performed upon reaching the upper amplitude of the oscillatory path, during the volume change below when the downward movement begins.

Of the document NL-A-8 004 985 a known installation for compressing granular materials, to form molding bodies by applying vibratory forces fundamentally harmonics, in which a fixed mold is used during compression, in which a plate of upper and lower press, among which the granular material. The lower press plate is supported for this on the ground through springs, which can also be used to adjust the amplitude of vibration. The docks do not represent no accumulator for the kinetic energy of the vibratory mass, in such a way that according to this there is no recovery of energy On the contrary, the vibration itself is only generated by hydraulic pressure to drive pistons joined with the pressing plates.

Of the document DE-A-37 24 199 a installation for compressing granular materials to form molding bodies by shock compression, in which an oscillating table isolated through springs in relation to the soil, operated through decompensations, is arranged a mold through which a weight is arranged in a frame cover subjected to elastic hydraulic forces, oscillating Also all these pieces.

The mission of the invention consists, for the chosen genre of compression facilities that work with harmonic compression forces and with the resonance effect, in avoid the aforementioned unwanted effects or reduce their impact. The mission solution is described by the two claims independent 1 and 2.

This is planned: an installation of compression to execute compression processes in the bodies of molding (108), from granular materials, by means of application of fundamentally harmonic vibratory forces (sinusoidal) in the molding body to be compressed, with a system of spring mass (136) with oscillation capacity, with a main system spring (150, 970) with one or more natural frequencies and with an excitation installation (144) that can be adjusted for its excitation frequency, by which can be excited the mass-spring system to produce forced oscillations, whose oscillations are derive the vibratory forces, also comprising the compression installation:

- a pressing plate (110) that can undergo a pressing force,

- an oscillating table (124),

- a mold (106) fixedly connected to the table oscillatory, at least during compression vibration, in whose mold can accommodate the molding body between the plate pressing and oscillating table,

- a control (190) for the control or regulation of the excitation installation, and forming the table oscillatory part of the oscillating mass of the system spring mass, on whose oscillating table the force of the main spring of the system and the excitation force, generated by an actuator of the exciter belonging to the excitation installation.

According to claim 1, the installation of compression defined above is also characterized because the main system spring (150, 970) is configured as a hydraulic spring with a volume of liquid (140, 906) compressible, because organs that act separately are planned for generating the excitation force (135, 980) and the elastic force of the main spring (150, 914) of the system, and because the force flow paths for the force of excitation and elastic force run at least partially separated.

According to claim 2, the installation of compression defined above is also characterized by means that the main system spring is configured as a single mechanical spring or as a spring, resulting compound of several mechanized insulated springs, of which organs are provided that act separately for the generation of the force of excitation (135, 980) and elastic force of the main spring of the system, and that the force flow paths for the excitation force and elastic force of the main spring of the system run at least partially separated.

Subordinate claims define other advantageous configurations of the invention.

The mission solution is based on the acknowledgment that the problems that occur in the state of the technique can be eliminated by decoupling the excitation forces, both of the excitation forces and of elastic forces and additionally by separating the organs of the excitation function and the elastic function. Forced by this, in the present invention may deviate, seen from the state of the art, only as a form of execution hydraulic exciter and spring that appears as possible, and can conveniently run exciter and spring in any combination, both mechanically and hydraulically. The principle that from here it follows from the possibility of replacing the dock hydraulic by a mechanical spring (and vice versa), finds its expression already in independent claim 2 and represents also the commonality that unites the two claims 1 and 2.

The main advantages of the compliant solution to the invention are deduced from the elimination or reduction of negative effects on the state of the art, as described previously in points a) to c): great savings are obtained in excitation energy and complexity of devices for installation of excitement The control of the entire excitation installation is simplifies by decoupling elastic forces and excitation forces, which is expressed only by means of that the excitation force generation can now be extended for the entire double amplitude (= 2A in Figure 9). Besides this no a superposition of inertia forces of the system is allowed mass-spring and excitation forces on a force flow path leading through the spring Main system Rather the excitement forces are they drive on a special force flow path, which runs between the oscillating table and the frame in parallel with the force flow path, which leads through the spring Main system For the solution according to the claim 1, this means that the excitation force, during its generation, it is not applied on the volume of liquid compressible from the main spring of the system, and for the solution according to claim 2 this means that the force of excitation, during its generation, is not applied in such a way on the main spring of the system, which increases energy cumulative by the main system spring by action of The excitement force.

For the application of an exciter actuator hydraulic is planned, in a special configuration of the invention, a variable volume hydraulic pump generator in Different variables For this the "volumetric currents dynamic hydraulics "or the variable hydraulic volumes to replace, necessary for the generation of the forces of excitation, are not generated by means of the current volumetric, derived from a pressure source, is modulated or Portion through a control body electro-hydraulic or a servomechanism, but that a variable volume hydraulic pump generator is used as part of an excitation installation. In the generators variable volume pump hydraulics, equipped with a mechanical pump piston drive, the contributions of Variable hydraulic volumes to replace are fundamentally independent of the pressure exerted, in each case, by the hydraulic exciter actuator. Variable volumes expelled by these towards their exit and introduced again are generated by pump pistons (or speaking very generally, by compression organs compression pumps in principle known), the pump pistons (or the organs of compression) with preset races that can be maintained constant, preferably, with mechanical means, being the races derived mechanically by drive motors rotary (electric or hydraulic).

The possible constant maintenance of runs during the excitation of the system mass-dock does not rule out that the races of the lifting pistons can also be modified according to a mode preset, or that the variable volumes can be modified by the modification of the useful stroke of the lifting pistons, such as an adjustable axial piston pump with relation to the volume of the compressor. Variable volumes introduced to generate the excitation force in the volume of liquid can also be varied, by means of which, although the run  of the variable volume pump generator remains constant, only part of the volume is introduced into the liquid volume variable corresponding to the pump stroke. As an example for a regulatory process of this type to be executed refers to the modification of the useful stroke of the lifting piston, in a conventional diesel engine injection installation.

The pump plunger pump movements they can be generated differently depending on the class of the variable volume pump generators, for which The following examples:

- pump plunger strokes can generated by the oscillating movements of vibrators of imbalance, preferably directional vibrators, being able to vary the frequency of the races by the number of drive motor revolutions and the length of career path through known means to Modify the oscillation amplitudes of the vibrators.

-Pump piston strokes can also be generated and modified, as is done in hydraulic pumps, by example in radial pumps or axial pumps. In the pumps to vary something, respectively, there should be only the concern of that the variable volume ejected, during the reverse travel of a pump plunger, can also flow back into the hollow space cattle from the pump cylinder.

The size of the variable volumes replaced remains constant, since the elevation paths of the variable volume pump generator cannot be influenced, with retroactive effect, by the influence of dynamic actuator actuator pressure (required by dynamic forces and inertia). However, also the pressure exciter actuator dynamics can have an effect retroactive on the variable volume pump generator, such so that the pump piston is driven in its return travel by dynamic pressure, by means of which the delivery of average power of the pump generator drive motor variable volume Because of precisely this retroactive effect, This kind of coupling produces for excitation energy, under certain conditions, also an automatic synchronization between the excitation frequency and the oscillation frequency of the mass-spring system or a synchronization automatic phase difference of the two kinds of oscillations The drive motor of the pump generator variable volume just have to be controlled or regulated with it with relation to its frequency of rotation. A possible deviation from guidance synchronous phase difference between the frequency of rotation and the oscillation frequency of the system spring mass is compensated by the elasticity of the electric field, especially the rotating field or field migrating an AC motor (slip), or attenuates its impact.

To meet the requirement of a connection and quick disconnection of the actuator from the exciter, in case the variable volume pump generator does not have a proper installation to modify the length of the travel of the runs (preferably up to zero), according to the invention is provided between the cylinder chamber outlet of the variable volume pump generator and the input of the chamber, which closes the liquid volume of the exciter actuator hydraulic, a connectable organ with which it can be limited or interrupt at least the exchange of liquid volume. From advantageously you must be able to connect, with the same process of switching, also a bypass path through which Variable volumes can be diverted to another container.

The following explains in more detail the invention based on figures 1 to 10. Figure 1 shows a compression installation in a general execution, representing the part shown below the A-B line in the Figures 4 to 8 in another kind of special execution, in such a way that the part of the compression installation, shown in the figure 1 below the A-B separation line, it replaced by partial representations of figures 4 to 8. Figure 2 illustrates a first variant and Figure 3 a second variant of a variable volume pump generator, which is characterized in figure 1 as frame 160, frame that symbolizes in figures 1 and 9 a control part, which forms the complete compression installation together with the actuator of the exciter Figure 9 shows another variant of an installation of compression, in which the hydraulic linear motor of the actuator of the exciter is coaxially arranged relative to the cylinder Hydraulic system main spring. As for Figures 2 to 8, for figure 9 it is valid that the symbols of reference beginning with the figure "1" represent the same organs or particularities as in figure 1. In figure 10 a detail marked in the figure has been reproduced on a larger scale 9 with Q, together with a connected hydraulic circuit.

In figure 1 the frame has been marked with 100 of the compression installation, which has to transmit forces of different kind and that rests on the ground 104 through springs 102 that serve as oscillation insulators. In a box of molding 106 open above and below is the body of molding 108 to be compressed, on whose upper side the pressing plate 110 of the pressing installation 112. The lower sides of the molding box and the molding body are placed on a base plate or transport plate 122, which at its once it is placed on the oscillating table 124. They are planned two fixing installations 126 with tensioning elements 130, which can move in the direction of the double arrow 132 for the purpose to fix and loosen, to make possible a plate replacement base and / or molding box. At least during the process of compression, molding box 106 and base plate 122 are fixed on the oscillating table 124, such that they form with the same a body unit

The hydraulic pressing installation 112 is it consists of a cylinder 114, a piston 116 and an installation of pressing drive 118, which is connected through a hydraulic pipe 120 with the cylinder pressure liquid and, to through a pipe 192, with central control 190. The Pressing system applies the transmitted forces to the frame through the press plate 110. The installation of pressing drive 118 can also be configured in such a way mode, which is connected to a pressure source, which maintains constant a preset pressure with different currents volumetric delivered or received.

The oscillating table 124 belongs, together with other constructive pieces that move in sync with her to those that belong mainly molding box 106, installation of  fixing 126, base plate 122 and suspension piston 134, to a oscillating mass system 136, which represents the mass of a mass-spring system with oscillation capacity. The dynamic inertia forces generated during the execution of the oscillations of the mass-spring system are apply, through the main dock 150 of the system, in the frame. The main dock of the system system mass-spring represents at the same time a energy converter and an energy accumulator as it converts continuously the kinetic energy of the oscillating mass system 136 in elastic energy (and vice versa). In the case of the figure 1, the main spring 150 of the system takes shape by means of a volume of pressure liquid 140 of a magnitude V o determined, with at least part of the volume of the pressure liquid between the suspension piston 134 and the walls of cylinder 138. Dynamic inertia forces are applied to the frame 100 through cylinder 138.

The oscillating mass system 136 can be seen forced, in order to execute the compression process, to be carried out using a vibration, to generate movements  oscillators 152. The forces to execute the movements oscillators are generated by a motion generating system 142 (which in principle can be configured very different). The latter consists of at least the two components main dock 150 of the system, which assumes the generation of main forces, and the excitation installation 144 for feed the drive energy to excite and maintain the oscillations and for compression work. The installation of excitation itself comprises the exciter actuator (represented very generally in figure 1 by a rectangle 135) to generate the excitation forces, and the exciter control 160 for supply the energy and control the actuator energy of the exciter The exciter control 160 is indicated schematically by a rack, which represents different shapes of execution. With connection point 196 in pipe 194, enter the central control 190 and the exciter control 160, and the point of connection 162 at the effective junction between the exciter control 160 and the actuator of the exciter 135, we want to clarify even more the possibility of replacing the functional support control of the exciter 160.

The actuator of the exciter 135 is arranged such that it applies the excitation forces, with a part mobile to a constructive part of the oscillating mass system 136, preferably with oscillating table 124, and with a fixed part at frame 100 (the movable part and the fixed part have not been represented in figure 1). It can be seen that the force flow paths of the main spring 150 of the system and the actuator of the exciter 135 run at least partially apart, so that no there may be a direct coupling between the elastic forces and the excitation forces, as in the cited state of the technique. It can also be seen that the excitation force is not applied, during its generation, to the volume of liquid 140 compressible from the main spring 150 of the system. The partial representations of figures 4 to 8 show how functional supports main spring system and actuator exciter can be materialized with absolutely means different.

The actuator of the exciter 135 works in such a way so that portions of energy are fed to the beat of the preset frequency by exciter control 160, which it has been symbolically represented by effective union 164. In the event that the exciter actuator is an actuator hydraulic, for example a hydraulic linear motor, is produced at through effective connection 164, to be indicated later as a pipe hydraulics, a dynamic exchange of variable volumes with the preset frequency between the exciter actuator and a generator variable volume pump, available in the control of the exciter 160. As variable volume pump generators can consider three different classes, of which two are explained with base in figures 2 and 3. (In the third variant the actuator of the exciter is powered by an electric linear motor, which works from similar to that described in figure 7).

In an ideal case, the excitation forces periodic are configured at least approximately as forces of harmonic excitation. The easiest way to achieve this is with the use of variable volume pump generators, using also an imbalance vibrator or with the mode of operation of a hydraulic compression pump. At first the mass-spring system can be excited, inside of certain limits, to create harmonic oscillations with any frequency and any amplitude of oscillation. This is also valid in the case of compression vibration at feed, and the oscillations of the mass-spring system by the components of the pressing installation 112 and by the molding body 108 itself, for example by its elastic force. In any case the mass-spring system with its installation of excitation 144 is designed in such a way that it can work even under the load of the pressing installation with a force preset pressing, driven through the molding body, well beyond the resonant frequency f_ {o}, but also at the resonance frequency f_ {o} or in the vicinity of the f_ {o} (above or below). As is known, the resonance operation stands out among other things, too because here very high accelerations of the table are reached oscillatory, which are necessary precisely with compression here provided with harmonic vibratory forces, and must be generated in resonance operation at the same time excitation forces relatively small

In case the compression installation Be part of a concrete stone machine (where Compressed molding bodies are subsequently reverted to form concrete stones), the molding body before its compression consists of a molding material with components loose granules that are joined by adhesion, such as wet concrete mortar. Once the compression is complete, ejects the molding body, in a way known to itself, from the molding box and transported to another site and the box of molding is filled again, also in a known way, with uncompressed molding material. In the process of changing the molding box content also participates in a way known by itself the pressing installation 112, by means of that with this the piston 116 together with the pressing plate 110 is able to execute a lifting movement, which leads to up and down. The compression procedure begins after the filling of the molding box 106 with molding material, so that pressing plate 110, moved down by the pressing installation, be placed on the upper side of the molding material From this moment of the lifting movement of the pressing plate 110, it moves further down exerting a preset pressing pressure on the body of molding that is emerging, with increasing compression of it. At the beginning of the compression produced by the pressing plate 110 or beginning or ending at any other time you want, the compression is executed by a joint pressure action of pressing and vibration on the molding body.

An especially effective compression can be triggered if the vibration is performed at the resonant frequency or near the resonant frequency f_ {o}. For this reason it has planned during the compression process a development of procedure, during which the frequency approaches or reaches of resonance f_ {o}, or it is exceeded. Because often different components of the molding mass with its different behavior modes require, during compression, differences vibration frequencies adjusted to them, it has also planned to change the frequency during the compression process of vibration, and with it the case also the amplitude of the oscillatory path As compression progresses you should also Compressive force be adaptable. In order to maintain a repeatable temporal development of the parameters, is planned by both vary the magnitude of at least one of the parameters frequency, amplitude of the oscillatory path or force of pressed, according to a preset temporary function. In other configuration of the invention is provided, instead of a point of resonance defined primarily by the coefficient of elasticity of the volume of the pressure liquid 140, create one or several more resonance points by modifying the elasticity coefficient. This requirement can be met by means that the determined quantity V_ {o} of the volume of the pressure liquid 140 is formed by several sub-volumes, which can be separated from each other by pluggable lock valves. With a modification desired elasticity coefficient is only necessary then Open or close the corresponding blocking valves. Too a continuous modification of the coefficient of elasticity, by means of which a part of the volume of the liquid of pressure 140 is formed by a cylinder, whose cylinder chamber be modified by a plunger, which can move in the cylinder in a preset way. In order to modify the resonance frequency it is also possible to modify the mass oscillating (with the vibrator stopped). This can be done through that additional masses are automatically coupled and decoupled (not shown in the drawing).

The vibration must be able to connect and disconnect, for example by changing the contents of the box molding The connection and disconnection of the vibration must be able run very quickly in the sense of a high Productivity of the entire production facility. To accomplish this requirement measures are planned, which are described later Based on other figures.

For the transmission of force flows soil 104 could also be naturally included, as shown in figure 9. In order to avoid vibrations in the ground, provided for figure 1, however, circulating the flows of force especially of dynamic forces of inertia completely through frame 100, and isolate frame vibrations, by springs 102, in relation to the ground. It should also be noted that pistons 116 and 134 in figure 1, as well as other pistons in the other figures can be configured as double plungers action.

A schematic figure shows a figure control of exciter 200 with a volume pump generator variable, with the inclusion of an imbalance vibrator 240. A through two connection points 162 and 196 all the control of the exciter to a compression installation according to the Figure 1, at connection points 162 and 196 also there present, replacing the exciter control 200 the control of the exciter symbolized in figure 1 by frame 160. Two masses centrifuges 204 are forced by their drive motors 202 to rotate synchronously in the opposite direction and thus make the base plate 208 of the common frame swings directed, which is indicated by the double arrow 206. The motherboard 208 is further supported gently in a manner not shown in the drawing, through springs, on cylinder housing 214. About the motherboard 208 has been fixed two pump plungers 210, which cooperate with two chambers of cylinder 216 of the housing of the cylinder 214. The cylinder chambers are joined together via a junction pipe 20 and are connected out to through a pipe 222, including the apparatus 226, to connection point 162. Through the oscillatory movement of the pump piston 210 is forced to the volume of pressure liquid 218, which is subject to a previous tension pressure, to be delivered with each downward stroke under greater pressure a volume of preset magnitude exchange, through the connection point 162, to the volume of pressure fluid of the actuator of the exciter 135 in figure 1 that works hydraulically in this case, and with each ascending race will also welcome a volume of exchange delivered by the volume of liquid pressure exciter actuator. With each exchange volume exchanged during a downward run can be delivered, of this way, a very determined portion of excitation energy at mass-spring system of figure 1.

The drive motors 202 are driven by a control apparatus 230, with which it can be influenced by example in the frequency of rotation, so that it corresponds with the resonance frequency f_ {o} of the installation of compression of figure 1. Control apparatus 230 is also joined on the other hand, through connection point 196, with the central control 190. The magnitude of the exchange volume, to exchange with actuator actuator 135 driven hydraulically in figure 1, it must be able to vary by different reasons, the possibility of preventing completely the exchange of volume and, with it, the movement Oscillating compression installation. For this mission it They have provided different solutions according to the invention. For side the oscillation amplitude of the vibrator can be varied, with means known to themselves and not described here in more detail, between the zero value and the maximum value. On the other hand there is the possibility of limiting or interrupting the volume exchange of liquid between the volume of pressure liquid 218 and the actuator of the exciter 135. The equipment for devices for measures mentioned last must be indicated by a apparatus 226 and its connection in terms of control, through the point of connection 196, to central control 190.

In figure 3 it has been represented schematic a control of the exciter 300 with a hydraulic pump as a variable volume pump generator. Through two points connection 162 and 196 all exciter control can be connected to a compression installation according to figure 1, in the connection points 162 and 196 also available there, replacing exciter control 300 symbolized exciter control in figure 1 by frame 160. In a pump housing 302 a cam disc 310 can be operated, which rotates about an axis 304 rotatably mounted on the pump housing, by means of a drive motor M, which has been symbolized by the arrow 308. The axis of rotation of the cam disc is arranged around an eccentric section 306 outside the center of the cam circle During a rotation of the cam disc is forced to a pump piston 320 to execute oscillatory movements in the cylinder chamber 322, which is symbolized by the arrow double 324. As a consequence of the oscillatory movements of the pump piston 320 is forced to the volume of pressure liquid 326, which is subject to a previous tension pressure, to be delivered in each compression stroke under a higher pressure a volume of preset magnitude exchange, through the connection point 162, to the volume of pressure fluid of the actuator of the exciter 135 supposedly hydraulically actuated in figure 1 and to receive, in each reverse race, also again an exchange volume delivered by the volume of pressure fluid of the actuator of the exciter With each exchange volume, exchanged in one compression stroke, a portion of very determined energy to the mass-spring system of Figure 1

The drive motor M is driven by a control apparatus 330, with which one can influence, for example, the frequency of rotation of cam disc 310, such that corresponds to the resonant frequency f_ {o} of the compression installation of figure 1. The control apparatus 330 it is also connected on the other hand, through the connection point 196, with central control 190. In this case too, to be able to vary the magnitude of the exchange volume, to be exchanged for the volume of liquid of the actuator actuator pressure in the Figure 1, are provided in the control of exciter 300 two corresponding possibilities. In the first solution you can modify the stroke of the pump piston 324, by means of which modify the eccentric section 306 (possible to zero). The another solution works similarly to the solution described with relation to figure 2, in which the volume exchange of liquid between the volume of pressure liquid 326 and the volume of pressure fluid of the exciter actuator can be limited or interrupt This imposes the same mission on the device 340 as  to apparatus 226 of Figure 2.

Figure 4 shows a variant of a compression installation according to figure 1 with the table oscillator 124, in which variant the actuator of the exciter 480 for  generate the excitation forces and the main spring of the system 470, compared to a compression installation according to the Figure 1 with a hydraulic exciter actuator, are configured otherwise. In figure 4 the main spring of the 470 system takes shape by means of two insulated springs volumes of pressure liquid 478 of the same magnitude, which are respectively confined between a suspension piston 474 and a 476 cylinder of its own. The actuator of the exciter 480 is formed by the actuator piston 482, which is fixed by means from the piston holder 484 to the oscillating table 124, by the cylinder of the actuator 486 and by the volume of actuator pressure fluid 488, which is connected by means of an effective connection 164 with the exciter control 160. As already described for Figure 1, they can also be used in figure 4 as controls of exciter (instead of symbolic frame 160 interchangeable between connection points 162 and 196), volume pump generators variable such as those described by figures 2 and 3. As in the compression installation of Figure 1, in Figure 4 the transmission of the excitation forces occurs in such a way, which are guided between the oscillating table 124 and the frame 100 on a special force flow path, which runs in parallel with the force flow paths that lead to through isolated springs (478). Forced by this measure no a coupling of excitation forces and forces can be reached dynamic inertia in the same volume of pressure liquid.

Figure 5 shows a variant of a compression installation according to figure 1 with the table oscillator 124, in which variant the actuator of the exciter 580 for  generate the excitation forces and the main spring of the system 570, compared to figure 1, are configured from another mode. In figure 5 the main spring of the 570 system takes shape by two volumes of pressure liquid 578 thereof magnitude, which are confined respectively between a suspension piston 574 and a cylinder 576 of its own. The actuator of the exciter 580 is formed by a directional vibrator 584 whose amplitude can be adjusted, which is directly linked to the oscillatory table 124 without a union with force transmission with the frame 100. The drive of the two drive motors 582, through which the number of revolutions, is realized through the effective union 164 by the exciter control 160. For the transmission of the forces of excitation on a flow path of own force is applicable something similar to that described in the description of figure 4.

Figure 6 shows a variant of a compression installation according to figure 1 with the table oscillator 124, in which variant the actuator of the exciter 680 for  generate the excitation forces and the main spring of the system 670, compared to figure 1, are configured from another mode. In figure 6 the main spring of the 670 system takes shape by means of two volumes of pressure liquid 678 thereof magnitude, which are confined respectively between a suspension piston 674 and a cylinder 676 of its own. The actuator of the exciter 680 comprises on the one hand a directional vibrator 681, which rests gently through springs 682 on frame 100. The drive of the two drive motors 683, through of which the number of revolutions can also be controlled, it is done through effective bonding 164 by controlling the exciter 160. The directional vibrator 681 does not have in this case that be adjustable in its amplitude of oscillation and can remain constantly on swing. The connection and disconnection of excitation forces generated by the directional vibrator on the oscillating table 124 and the control of the magnitude of the portions of excitation energy, to be transmitted with each movement oscillator of the directional vibrator, is performed by means of a coupling system 684 hydraulically operated, also still belonging to the actuator of the exciter, in connection with a hydraulic connection member 685 that is activated at through pipe 686 from central control 190.

Hydraulic coupling system 684 it comprises a double action plunger 687, which can move up and down using the oscillatory movements of the  directional vibrator, to which it is fixed, in the cylinder chamber 688. During the oscillation of the directional vibrator 681, exchange variable volumes, which are part of the volumes of liquid pressure from the two chambers of cylinder 672 and 673 separated by the piston, with the hydraulic connection member 685. The hydraulic connection member 685 can operate in different versions: in a first mode of operation create for variable volumes to exchange a short circuit path, of such that during the upward and downward movement of the Piston 687 virtually no force is transmitted from excitation from the directional vibrator on the oscillating table. In a second mode of operation, the connecting member 685 hydraulic makes available a short circuit path more narrow (preferably continuously adjustable) with an action of preset choke. By strangling the volumetric currents of the variable volumes to be exchanged are presumably reduce the transmissible amplitudes of the oscillatory movement of the directional vibrator and the forces of transmissible excitation or portions of excitation energy transmissible In a third mode of operation the path of short circuit is completely blocked, which has as consequence that oscillatory movements or forces of Directional vibrator excitation are transmitted, in all its amplitude or with its maximum magnitude, on the oscillatory table 124. For the transmission of excitation forces on a path of own force flow something similar to the description of figure 4.

Figure 7 shows a variant of a compression installation according to figure 1 with the table oscillator 124, in which the actuator of the exciter 780 for generate the excitation forces and the main spring of the system 770, compared to figure 1, are configured from another mode. In figure 7 the main spring of the 770 system takes shape by two volumes of pressure liquid 778 thereof magnitude, which are confined respectively between a suspension piston 774 and a cylinder 776 of its own. The actuator of the exciter 780 is an electric linear motor, composed of one part mobile 782 and a stationary part 783. The excitation forces are generate in a 784 air gap using magnetic variable fields and are applied, on the one hand to the oscillating table 124 and on the other hand to the frame 100. The magnitude of the excitation forces, the career amplitudes of the moving part and the frequency of excitation are set by exciter control 160, which it is connected to the linear motor through the effective connection 164. For the transmission of excitation forces on a path of own force flow something similar to the description applies of figure 4. In an electric linear motor you can also be considered an advantage the fact that this can lead to perform a direct conversion of electrical energy into energy of excitement.

Figure 8 shows a variant of a compression installation according to figure 1 with the table oscillator 124, in which variant the actuator of the exciter 880 for  generate the excitation forces and the main spring of the system 870, compared to figure 1, are configured from another mode. In figure 8 the main spring of the 870 system takes shape by two volumes of pressure liquid 878 thereof magnitude, which are confined respectively between a suspension piston 874 and a cylinder 876 own. The actuator of the exciter 880 is an electric linear motor, composed of one part mobile 882 configured as a piston and a stationary part 883 configured as cylinder. The excitation forces are generated in the volume of pressure liquid 884 by exchanging dynamic hydraulic variable volumes, through the union effective 164 with exciter control 160. Control of exciter 160 contains in this case a servomechanism electro-hydraulic, which generates, based on the control information obtained by central control 190, dynamic hydraulic variable volumes with frequency and magnitude presettable and with portions of excitable energy presettable. The excitation forces are applied on the one hand to the table oscillatory 124 and on the other hand to frame 100. For the transmission of excitation forces over a flow path of its own force something similar to the description of the figure 4.

Figure 9 shows a variant of a compression facility that works, similar to those variants according to figures 4 and 8, with a hydraulic spring and With a hydraulic exciter. The structure of the entire installation of Compression is similar to that of Figure 1. The symbols of reference beginning with the number 1 characterize therefore the same features with the functions assigned to them than in figure 1. The peculiarities of another type in comparison with figure 1, which start with the number 9, are arranged all below the oscillatory table 124. The flow of force of all the forces involved circulates through the part of the cylinder 902. The part of the cylinder is fixedly connected with the foundation 904, like the frame 100 open down. The foundation can be considered in this case as a part of the frame 100 and is also support of the force flow paths of All compression forces.

The cylinder part 902 contains chambers of the cylinder or fluid volumes for two different linear motors Hydraulic: the volume of compressible liquid 906 represents the power storage part of the main dock of the system 970 and with its compression module is decisive for the frequency of resonance of the mass-spring system with the system of oscillating masses 136, to which the piston of suspension 908. The volume of liquid 906 forms, together with the suspension piston 908, the main spring of the 970 system. The liquid volume 914 of the actuator forms, together with the piston of the actuator 916 and the cylinder part 902, the hydraulic linear motor of the actuator of the exciter 980, whose linear motor is generated the excitation forces, with which frequency is established and amplitude of compression vibration. The suspension piston is fixedly connected with the oscillating table 124 and the piston of the Actuator is fixedly connected with the suspension piston. The liquid volume 906 and actuator liquid volume 914 They could also be exchanged.

The actuator of the exciter 980 is connected by means of effective connection 164 with control of exciter 160. The exciter control (interchangeable instead of the frame symbolic 160 between connection points 162 and 196) may be executed as a variable volume pump generator; but may also contain a servomechanism electro-hydraulic, which on the one hand is connected to a pressure source (preferably with pressure fundamentally constant) and, on the other hand, exchange volumes dynamic hydraulic variables with frequency and magnitude preset and with portions of excitation energy preset With the linear motor.

The oscillating table 124 or the suspension piston must be maintained in an average height position, preset with a variable or constant value, as symbolized by the magnitude "Z". During the execution of oscillatory movements, the average height position can be defined for example by that position of reference of the oscillatory path, in which the oscillation speed has its maximum value and the acceleration of oscillation the value zero. With reference to this position of oscillatory path reference, amplitudes can be defined of oscillatory travel + A and -A (together with accelerations of positive and negative oscillation), being able to have the amplitudes of the oscillatory path + A and -A different values, as is worthy of mention, depending on various parameters. At least for the execution of oscillatory movements in resonant operation the volume of liquid 906 must be compressed, with an amplitude of negative oscillation -A, approximately at the value -A.

During the execution of an oscillatory movement in the positive direction (in the direction of the oscillation amplitude + A) it may happen that, upon reaching a compression value = zero of volume of liquid, the amplitude of swing "+ A". To avoid in this case the formation of a The use of a volume dispenser is planned compensation 920. It consists of a cylinder housing 922, a suspension piston 926, a compensation spring 928 and a compensation volume 924, and is connected through a pipe 930 with liquid volume 906. While a value of > zero compression of the liquid volume, the piston of compensation 926 is pressed against the force of the spring of compensation 928 in a mechanically formed end position. During an upward oscillatory movement the piston moves of compensation, at the latest when a value of compression = zero of liquid volume 906, by force of  compensation spring from its final position, by means of which flows a volumetric current from the volume of compensation 924 up to liquid volume 906. With a value of compression upward after inversion the movement oscillatory at its highest point, one moves in reverse volumetric current from the volume of liquid 906 to the volume of compensation 924, and precisely while the compensation plunger it is again in the final position drawn, so after (apart from leakage losses) it starts again at the same time, a compression of the volume of liquid 906. In another form of execution, a compensation volume dispenser could also replaced by a correspondingly controlled valve, which extracts the volumetric current during the upward stroke from a pressure source and returns the volumetric current, during the downward run, to the source of pressure itself or to other container

A measurement system of routes for the detection of the oscillatory route of the table oscillatory 124 or suspension piston 908, composed of a first sensory part 910 and a second sensory part 912. The result of this route measurement is fed (in a way not represented in the drawing) to central control 190 and there it is. In order to maintain the oscillating table 124 or the piston of 908 suspension, despite leakage losses that occur and other disturbing factors, in the position in height or position of reference of the preset average oscillatory path, has been 940 hydraulic regulator volume dispenser provided. East can feed a current through pipe 942 volumetric regulator up to the volume of liquid and, given the case, also evacuate it, so that the position in Pre-set average height remains constant. The dispenser of regulator volume 940 presents in the chosen example a source of pressure S, a check valve C and a valve V, through whose valve is carried out the necessary current dosing volumetric regulator. The V valve, which is activated through the effective pipe 944 from central control 190, is an actuator of a closed regulator circuit of a regulatory installation of the level, with which the position in height is continuously regulated average or reference position of the oscillatory path to a default value.

A compression installation according to the Figure 9 offers several advantages, which are precisely:

- the main system spring 970 is not loaded with the excitation forces, respectively, the volume of actuator fluid is not charged with spring forces Main system The force flow of all forces involved is unified in the suspension piston, because of the generation of excitation forces that occurs separately in an actuator of the exciter itself, but in the actuator of the exciter does not occur an overlap of excitation forces and of elastic forces derived from inertial forces dynamic

- During the sizing of the cylinder actuator is not necessary to take into account the dimensioning of the suspension piston, which must generate forces of another order of magnitude, especially in resonance operation.

- Unlike in the installation of compression according to figure 8, in figure 9 the linear motor hydraulic exciter actuator and suspension cylinder of the main dock of the system are concentric and are arranged, with it, also with central symmetry with respect to the oscillatory table 124. Because of the possible symmetric application of force of dynamic inertia forces, generated by the operation of the springs, and excitation forces cannot therefore there is no seizing effect on the pistons involved and compression acceleration acts symmetrically over the entire molding box 106, which is important above all to divide the molding box into many insulated molds.

Figure 10 shows the detail marked on the Figure 9 with the circle "Q" with a variation, so that in the inner cylinder of the part of the cylinder 902 is provided an annular groove 950, which is filled with a volume of liquid 952. The volume of liquid 952 can be attached to the volume of liquid 906 with a suspension piston 908 moved to a position higher. Apart from this a hydraulic circuit is also shown Additional 954, whose pipe portion 956 is connected to the volume of liquid 952 through a liquid pipe 962. Figure 10 In total, it shows a different variant from the one in Figure 9, which works purely mechanically-hydraulically, of a level regulation installation, with which the height position or travel reference position average oscillatory of the oscillatory table 124 at a value, preset by the position of the control edge of the cylinder 958 of the annular groove, and in which at the same time also materializes the operation of the volume dispenser of compensation described in figure 9. Suspension piston 908 it has a piston control edge 960 on its underside that, in the same height position (as drawn) that the control edge of cylinder 958, separates liquid volume 952 of liquid volume 906. With the height position drawn from the suspension piston also defines the reference position of the oscillatory path of the oscillatory table 124. Thus the 958 cylinder control edge represents a sizing for the nominal position of the travel reference position oscillatory. The hydraulic circuit works as follows way: PLV is a pressure relief valve that, with a pressure> \ rho_ {L} in the pipe portion 956 of a volumetric current, opens the path in the vessel T. S2 represents a source of liquid with a constant pressure < \ rho_ {L}. A CV check valve prevents a current inverse of liquid from pipe part 956 to the source of liquid.

The operation of the regulation facility Level is as follows. After the control edge of the piston 960 during a downward oscillatory movement of the plunger of suspension 908, has passed through the reference position of the oscillatory path, starts with liquid volume 906 separated the compression of this volume of liquid and the movement oscillatory reaches its lower investment point, after traveling the section -A. As for, during the oscillatory movement ascending to apply then the piston control edge 960 has passed again through the reference position of the route oscillatory, a volumetric current of compensation from source S2 to within the volume of liquid 906, and precisely until the suspension piston 908 has reached the upper investment point after crossing the section + A. During the subsequent downward race, after that in the liquid volume 906 has established a pressure> \ rho_ {L}, a volumetric current flows from the volume of liquid 906, through the pressure relief valve PLV, to container T, and precisely until the control edge of piston 960 has passed through the reference position again of oscillatory travel. In this procedure, the races ascending can have any magnitude within a frame determined, corresponding to section + A, by means of portions of energy fed through the plunger of the actuator

The same function of this installation of level regulation could be executed, with a mode of similar operation, also with a somewhat modified version: here the piston control edge (960) is not applied to the suspension piston 908 and cylinder control edge 958 no is applied to the inner cylinder belonging to the piston of suspension 908. Rather, the edge of piston control (960) in another piston and the control edge of the cylinder 958 to another inner cylinder, belonging to the other piston, the control edge of the cylinder being materialized in the other cylinder, also by the lower flat surface of another annular groove (or by radial holes). Also in the another inner cylinder is contained another volume of liquid (similar to 906 in Figure 10) as an elastic means, which limits with the inferred side of the other plunger. There is also another hydraulic circuit, structured as circuit 954 of the figure 10, but the other hydraulic circuit with its liquid pipe (like liquid pipe 962) is now connected to the other volume of liquid, while the volume of liquid contained in the other annular groove is connected to the liquid volume 906 (= elastic medium) through a pipe. In the configured version of another way you have to pay attention that the other piston is attached also with the oscillating table 124, and oscillates synchronously with  the suspension piston 908.

For all the execution variants described of the invention the following are still applicable Declarations: the actuator and spring actuator organs main system are arranged at the same time either by above or below the oscillating table. Instead of a single Molding body or cast mold model can be several of them planned at the same time. Relative position between the main system spring and the exciter plunger can be exchanged, which for example would mean for the figure 9 that 908 would be the actuator piston and that 916 would be the suspension piston Very generally it is applicable for all figures that the dashed lines and points shown there, as per example line 879 in figure 8, symbolize a fixed union between The two constructive pieces.

Claims (19)

1. Installation to compress materials granules, forming molding bodies (108), by means of application of fundamentally harmonic vibratory forces, with a mass-spring system (136) with oscillation capacity with one or several natural frequencies, comprising a main system spring (150, 970) for the Continuous conversion between kinetic energy of the system spring mass (136) and elastic energy and a mass that presents an oscillating table (124), on which the force acts elastic of the main spring of the system (150, 970), and a mold (106) to accommodate the molding body (108), fixedly connected with the oscillating table (124) at least during compression, an excitation installation (144) adjustable in as for its natural frequency, with an exciter actuator for excite the spring-mass system (136) and produce forced oscillations, from which forces can be derived vibratory, acting the elastic force generated by the exciter actuator on the oscillating table (124) and being located the excitation frequency for the oscillations, either in  the natural frequency or in its vicinity, or being able to adjust within a frequency range, within which it is located less a natural frequency, a control (190) to control or regulate the excitation installation (144), being the main dock of the system (150, 970) a hydraulic spring with compressible liquid volume (140, 906), the forces transmitted by the pressing plate (110), on the one hand, and transmitted forces by the main dock of the system (150, 970), on the other hand, to a frame (100) by which they are guided on a flow path closed forces the forces involved in compression, characterized in that the actuator of the exciter (144) and the main spring of the system (150, 970) are configured separately from each other, and the flow paths of force of the excitation force and of the elastic force run at least partially apart. 2. Installation to compress materials granules, forming molding bodies (108), by means of application of fundamentally harmonic vibratory forces, with a mass-spring system (136) with oscillation capacity with one or several natural frequencies, comprising a main system spring (150, 970) for the Continuous conversion between kinetic energy of the system spring mass (136) and elastic energy and a mass that presents an oscillating table (124), on which the force acts elastic of the main spring of the system (150, 970), and a mold (106) to accommodate the molding body (108), fixedly connected with the oscillating table (124) at least during compression, an excitation installation (144) adjustable in as for its natural frequency, with an exciter actuator for excite the spring-mass system (136) and produce forced oscillations, from which forces can be derived vibratory, acting the elastic force generated by the exciter actuator on the oscillating table (124) and being located the excitation frequency for the oscillations, either in  the natural frequency or in its vicinity, or being able to adjust within a frequency range, within which it is located less a natural frequency, a control (190) to control or regulate the excitation installation (144), a pressing plate (110) to apply the force of the molding body (108) to the mold (106), the forces transmitted by the pressing plate (110), on the one hand, and transmitted forces by the main dock of the system (150, 970), on the other hand, to a frame (100) by which they are guided on a flow path closed forces the forces involved in compression, characterized in that the actuator of the exciter (144) and the main spring of the system (150, 970) are configured separately from each other, and the flow paths of force of the excitation force and of the elastic force run at least partially apart, being The main spring of the system (150, 970) is configured as a single mechanical spring or as a resulting spring, consisting of several isolated mechanical springs. 3. Installation according to claim 1 or 2, characterized in that a force transmission member (908) is provided between the main spring of the system (970) and the oscillating table (124) and the force transmission member cannot be loaded at least on a part of the oscillatory path, covered during the execution of the upper amplitude of the oscillatory path (+ A), by means of the elastic force of the main spring of the system, by means of which a free path (+ A) of the force transmission organ, - an exchange facility being planned of special volume (920), when using a main spring of the hydraulic system (970) for filling or emptying the volume of the cylinder (+ A), which can be generated by free travel (+ A) of the suspension piston (908), the piston being suspension (908) assigned to the force transmission body and being identical to it, - and being provided, when using a dock main mechanical system, a separation of the organ from force transmission from the single spring or from the spring resulting. 4. Installation according to one of claims 1 to 3, characterized in that the kinetic energy of the mass of the spring-mass system is only provided with the kinetic energy of the downward directed oscillation speed, for conversion into an elastic energy of the main dock of the system. 5. Installation according to one of claims 1 to 4, characterized in that the dynamic elastic forces are applied to the oscillating table, through the force transmission member (908) at a central point thereof, and - in the case that only one exciter actuator, the excitation forces are applied to the oscillating table through the same transmission body of force (908), and - in the event that two or more are provided exciter actuators, excitation forces are applied at the central point in relation to its force vector resulting. 6. Installation according to claim 5, characterized in that the force transmission member (908) connected to the oscillating table is also part of a guiding installation (902; 908), with which the mass of the oscillating table is forced to execute exclusively vertical translational movements (152), both dynamic elastic forces and excitation forces being transmitted, in the case that only one actuator of the exciter is provided, by means of that part of the force transmission member that is part of the same time of a guided installation. 7. Installation according to claim 6, characterized in that an exciter actuator (980) is provided, whose excitation forces are only transferred to the oscillating table (124) with a single actuator (916), and because both the forces Dynamic elastics such as excitation forces are transmitted by that part of the force transmission member (908), which is part of a guiding installation (902; 908). 8. Installation according to one of claims 1 to 7, characterized in that the elasticity coefficient of the main spring of the system is adjustable. 9. Installation according to one of claims 1 to 8, characterized in that the pressing force can be generated in a variable manner by means of a pressing installation (112), the pressing installation being controlled or regulated by means of a central control (190). 10. Installation according to claim 3, characterized in that with the use of a main spring of the hydraulic system (970) with a volume of spring liquid (906), a level regulation installation (940) is provided, with which a preset average height (Z) position of the suspension piston (908) is adjusted or regulated. 11. Installation according to claim 10, characterized - because the position in height (Z) average presettable is regulated by feeding a current volumetric adjustment to a volume of spring liquid (906) or the evacuation of a volumetric regulation current from the volume of spring liquid (906), and by including the measurement result of a measurement installation for set the actual value of the position in height (Z), controlling or regulating depending on the result of the measurement of a hydraulic installation (940), with which it is modified the magnitude and / or the direction of the volumetric current of regulation, or - because the position in height (Z) average presettable is adjusted by the cooperation of an edge of control (958) as mechanical dimensioning of the position in height, using the control edge along with another mechanical control feature (960), configured as edge or surface, as part of a hydraulic installation to modify a cross-section of volumetric current, the modification of a cross-section of volumetric current by a relative movement, derived from the movement oscillatory, of the control edge (958) and the characteristic of control (960), and applying the compression of the liquid volume of the spring (906) upon reaching a cross section of the volumetric current = zero. 12. Installation according to claim 10 or 11, characterized in that a compensating volume dispenser (920) is used for the delivery of a compensation volume, for increasing the volume of liquid (906) of the main system spring (970) hydraulic during the execution of an ascending oscillatory movement (in the sense of amplitude + A). 13. Installation according to one of claims 1 to 12, characterized in that an actuator of the hydraulic exciter is provided, which can be driven with variable volumes, generating variable volumes by means of a variable volume pump generator (160) assigned to the excitation installation , - either from a pump piston (210), whose pumping movement is mechanically derived from the movement oscillator of an imbalance vibrator (240), - or from a pump piston (320), whose pumping movement is mechanically derived from an organ of rotary drive (310), - or from a pump piston, whose movement of pumping is derived from the movement of the moving part of an engine electric linear 14. Installation according to one of claims 1 to 9, characterized in that the excitation forces are forces derived from the inertia forces of an imbalance vibrator, which are applied from the imbalance vibrator in the mass of the oscillating table (124) , and precisely by means of which the imbalance vibrator frame (584) is directly and rigidly connected with the mass of the oscillating table (124), or by means of which the imbalance vibrator (681) is gently supported (tuning deep) through springs (682) in the frame (100) or on the ground, and because the transmission of oscillatory movements and excitation forces from the imbalance vibrator to the mass of the oscillating table occurs by connecting of a coupling installation (684), which is equipped with one of the principles mentioned below, for the creation of a coupling union, and precisely - by mechanical coupling, - through the use of magnetic forces, - with the use of viscous media with electrically connectable shear loads, - hydraulically by using a or two embedded oil columns, whether or not they can be moved movable oil columns embedded in chambers of the cylinder (672, 673), through the cooperation of an organ of hydraulic connection (685). 15. Installation according to one of claims 1 to 9, characterized in that the excitation forces are applied between the mass of the oscillating table (124), on the one hand, and the frame (100) on the other hand, and because the actuator of the Exciter (780) is an electric linear motor (782, 783). 16. Installation according to claim 1, characterized in that the main spring of the system (140) takes shape by means of a volume of pressure liquid (140), embedded at least partially in a cylinder body, and because the elasticity coefficient can be modified by a modification of the magnitude of the volume of pressure liquid, - either by means of the magnitude of the volume of pressure liquid (140) consists of several sub-volumes, which can be separated from each other via pluggable lock valves, - or by means of a part of the volume of pressure liquid (140) is embedded in a cylinder, whose chamber of the cylinder can be modified by means of a movable piston in the cylinder according to a preset mode, running the displacement of the piston preferably by means of a spindle drive screwed. 17. Installation according to one of claims 1 to 16, characterized in that a hydraulic linear motor is provided as an actuator of the exciter (980) and because the hydraulic linear motor is symmetrically arranged at the center of the oscillating table (124) and, in the configuration of the main spring of the system as a hydraulic spring (970), concentrically to it. 18. Installation according to one of claims 1 to 17, the compression installation of a casting molding machine being part, characterized by the combination of the following particularities, - the granular material is intended for molding function of a cast mold model, - at least one cast mold model is housed in the mold and fixedly attached to the mass of the system mass-spring, and oscillates with it, -grain material to compress and mold to less on its underside by the contours of the model of foundry mold is ready, already before the process of compression, next to the cast iron model and / or above of the same. 19. Installation according to one of claims 1 to 18, characterized in that the compression system is part of a sintering parts molding machine.